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11859600 | DESCRIPTION OF EMBODIMENTS First Embodiment FIG.1shows an example of the configuration of a liquid feed pump1according to the first embodiment of the present invention and a liquid chromatography device which uses the liquid feed pump1. InFIG.1, the liquid feed pump1includes, as main components, a first plunger pump101, a second plunger pump102, a first electromagnetic valve81, a second electromagnetic valve82, a purge valve311, a controller50, a motor driver106, an electromagnetic valve driver107, and a purge valve driver312. The first plunger pump and the second plunger pump are connected in series. The first plunger pump101includes a first pump head111. The first pump head has a first suction path10, a first discharge path103, and a first pressure chamber12. A first check valve4is located on the first suction path10and a second check valve5is located on the first discharge path103and these check valves restrict the direction in which the solvent flows. The second plunger pump102includes a second pump head112. The second pump head112has a second suction path104, a second discharge path11, and a second pressure chamber13. The second check valve5and the second suction path104are connected by a connection flow channel24. In other words, the first plunger pump101and the second plunger pump102are connected in series and the first plunger pump101is located on the upstream side. The first plunger pump101holds the first plunger2as a pressurizing part by a bearing71in a slidable manner. The second plunger pump102holds the second plunger3as a pressurizing part by a bearing72in a slidable manner. A first seal61prevents liquid leakage from the first pressure chamber12and a second seal62prevents liquid leakage from the second pressure chamber13. The first suction path10is located on the lower limit point side of the first pressure chamber12and the second suction path104is located on the lower limit point side of the second pressure chamber13. The first discharge path103is located on the upper limit point side of the first pressure chamber12and the second discharge path11is located on the upper limit point side of the second pressure chamber13. The meanings of the lower limit point and upper limit point will be explained later. The purge valve311is connected downstream of the second plunger pump102. The purge valve311changes the direction of flow of the solvent discharged from the liquid feed pump1to either an injector53side or a drain tank313side. The rotation of a first electric motor211is decelerated by a speed reduction device221and converted into a linear motion by a direct acting device231to move the first plunger2back and forth. The rotation of a second electric motor212is decelerated by a speed reduction device222and converted into a linear motion by a direct acting device232to move the second plunger3back and forth. Considering that the speed reduction device221and direct acting device231are combined to amplify the rotative power of the first electric motor211and convert it into linear motion power, they may be called a power transmission mechanism device in a broad sense. Concrete examples of the speed reduction devices221and222include a spur gear, pulley, epicyclic gear and worm gear. A major reason that the speed reduction devices are provided is to increase the electric motor torque and if an electric motor has a capability to generate a sufficient torque, they are not always needed. Concrete examples of the direct acting devices231and232are a ball screw, cam and rack pinion and so on. The structures of the speed reduction device and direct acting device are not limited in embodying the present invention. When the first plunger pump101sucks a solvent, either the first electromagnetic valve81or the second electromagnetic valve82is open and the other valve is closed and either a first solvent511or a second solvent512is sucked. The solvent being sucked is passed through an interflow part91, the first check valve4, and the first suction path10and sucked into the first pressure chamber12. The solvent sucked into the first pressure chamber12is compressed as the first plunger2ascends. The “ascent” of the plunger represents movement in the direction in which the solvent in the pressure chamber is compressed or discharged (rightward movement inFIG.1) and the “descent” represents the direction in which the solvent is sucked (leftward movement in FIG.1). If the pressure of the compressed solvent is larger than the pressure in the second pressure chamber13, the solvent flows through the first discharge path103, second check valve5, connection flow channel24and second suction path104into the second pressure chamber13and is discharged from the second discharge path11. A first pressure sensor105measures the pressure of the solvent in the first pressure chamber12and a second pressure sensor160measures the pressure of the solvent in the second pressure chamber13. The controller50gives a command value to the motor driver106, electromagnetic valve driver107, and purge valve driver312according to signals from the first pressure sensor105and second pressure sensor60. The motor driver106gives driving electric power to the first electric motor211and second electric motor212according to the command value from the controller50. The electromagnetic valve driver107gives driving electric power to the first electromagnetic valve81and second electromagnetic valve82according to the command value from the controller50. The purge valve driver312gives driving electric power to the purge valve311according to the command value from the controller50. The solvent discharged from the liquid feed pump1is injected with a sample as the object of analysis by an injector53. The solvent injected with the sample enters a separation column54and is separated into components. After that, a detector55detects the absorbance, fluorescent intensity, refraction index and so on according to each component of the sample. The separation column54is filled with microparticles and due to the fluid resistance produced as the solvent flows in gaps between microparticles, a load pressure of tens of megapascals to more than one hundred megapascals is generated in the liquid feed pump1. The magnitude of the load pressure differs depending on the diameter of the separation column54and the flow rate. When analysis using the first solvent511is changed to analysis using the second solvent512, before analysis using the second solvent512the first electromagnetic valve81is changed from the open state to the closed state, and then the second electromagnetic valve82is changed from the closed state to the opens state. Consequently, inside the liquid feed pump1(first check valve4, first suction path10, first pressure chamber12, first discharge path103, connection flow channel24, second suction path104, second pressure chamber13, second discharge path11) and inside the injector53, separation column54, detector55, and piping connecting them, the first solvent511is replaced by the second solvent512. At this time, by shortening the time required to replace the solvent, the number of analyses which can be conducted in a given time can be increased. FIG.2is a diagram which illustrates the method of operation in which the liquid feed pump1replaces the solvent from the first solvent511to the second solvent512. Operation of the liquid feed pump1for solvent replacement includes the following steps: (a) normal liquid feed using the first solvent, (b) transition from normal liquid feed to solvent replacement, (c) solvent replacement liquid feed to replace the first solvent by the second solvent, (d) transition from solvent replacement to normal liquid feed, and (e) normal liquid feed after change to the second solvent. Normal liquid feed means a liquid feed method by which the solvent discharged from the liquid feed pump1is made to flow to the injector53, separation column54and detector55and the sample is analyzed. The graphs inFIG.2are graphs which show changes over time in first plunger2displacement, second plunger3displacement, discharge flow rate, discharge pressure, the state of the first electromagnetic valve81, the state of the second electromagnetic valve82, and the state of the purge valve, in order from top to bottom. The discharge flow rate is the flow rate of discharge from the liquid feed pump1and the discharge pressure is the pressure detected by the second pressure sensor60. It is here assumed that in terms of plunger displacement, the ascent direction (rightward inFIG.1) is positive and the descent direction (leftward inFIG.1) is negative and in terms of discharge flow rate, discharge is positive and suction is negative. In the normal liquid feed step, the purge valve311is connected to the injector53side to let the solvent discharged from the liquid feed pump1flow to the injector53, separation column54and detector55. At this time, since pulsation of the discharge flow rate causes a decline in detection accuracy, the discharge flow rate must be constant. In zone a where the first plunger2descends and sucks the solvent, and zone b where the first plunger2ascends and compresses the solvent, the solvent is not discharged from the first pressure chamber12and thus the second plunger3ascends and discharges the solvent. After that, in zone c where the second plunger3descends and sucks the solvent, the first plunger2ascends and discharges the solvent to be sucked by the second plunger3and the solvent to be discharged to the pump downstream. After that, in zone d, the first plunger2ascends and discharges the solvent and the second plunger3stops. These motions keep the discharge flow rate from the liquid feed pump1constant. As the discharge flow rate is kept constant, the discharge pressure also becomes constant. In the normal liquid feed step, the first plunger2and second plunger3both move with reference to the lower limit point. The lower limit point represents the lowest position in the range in which the plunger can move in the pressure chamber. On the other hand, the upper limit point, which will appear in the explanation given later, represents the highest position in the range in which the plunger can move in the pressure chamber. In contrast, the bottom dead point/top dead point generally mean the both ends of the plunger stroke. Therefore, as the stroke range changes, the bottom dead point and top dead point also change. In this specification, the lower limit point/upper limit point are used in a meaning different from the bottom dead point/top dead point unless otherwise described. InFIG.2, first, with the first electromagnetic valve81open, the second electromagnetic valve82closed, and the purge valve311connected to the injector53side, normal liquid feed is performed and the first solvent511is fed to the injector53side. In the transition step, under this condition, the first plunger2and the second plunger3are once stopped and the purge valve311is switched to the drain tank313side. Then, after the first plunger2ascends to the upper limit point, the second plunger3ascends to the upper limit point. Then, the first electromagnetic valve81is changed to the closed state and the second electromagnetic valve82is changed to the closed state. In the solvent replacement step, under this condition, while the second plunger3remains stopped, only the first plunger2reciprocates between the upper limit point and lower limit point so that the solvent in the liquid feed pump1is replaced from the first solvent511to the second solvent512. At this time, the discharge flow rate is intermittent, thereby causing pressure pulsation. However, as compared with the fluid resistance in the separation column54, the fluid resistance in the piping connecting the purge valve311and the drain tank313is small and thus the maximum pressure during solvent replacement is smaller than the pressure during normal liquid feed. In addition, since sample analysis is not conducted during solvent replacement and no solvent flows into the separation column54and detector55, there is no problem even if pulsation of the flow rate and pressure occurs. In the transition step from solvent replacement to normal analysis, the first plunger2and the second plunger3have to return to the lower limit point. First, the first plunger2moves to the lower limit point. Then, while the first plunger2is again moving to the upper limit point, the second plunger3moves to the lower limit point. At this time, if the second plunger3moves to the lower limit point while the first plunger remains stopped, the solvent would be sucked into the second pressure chamber13from the downstream side of the liquid feed pump1. In order to prevent this, the first plunger2moves to the upper limit point. Then, the first plunger2again moves to the lower limit point. After that, the purge valve311is switched to the injector53side to start normal liquid feed. FIG.3is a diagram which schematically explains the flows generated in the second pressure chamber13with the ascent of the first plunger2and the solvent replacement in the solvent replacement process shown inFIG.2. For the convenience of description, the second pressure sensor60is omitted. When the first plunger2descends, the second check valve5is closed and no flow is generated in the second pressure chamber13. A flow is generated in the second pressure chamber13only when the first plunger2ascends. The second seal62has a spring621to fasten the second plunger3to let it have a pressure resistance (the first seal61also has one), though omitted inFIG.1. The solvent is filled in a space44for the spring621and at the time of solvent replacement, the solvent in the space44must be replaced. The flow of the solvent coming from the second suction path104is divided into a flow42passing through the gap between the second plunger3and the second pressure chamber13and going to the tip of the second pressure chamber13and a flow43going through the gap between the second plunger3and the second pressure chamber13to the seal vicinity space44. The flow43going to the seal vicinity runs in the seal vicinity space44(flow45) and then passes through the gap between the second plunger3and the second pressure chamber13(flow46) and goes to the tip of the second pressure chamber13. The flow46joins the flow42and flows out of the second pressure chamber13through the discharge path11. The second suction path104is located on the lower limit point side of the second pressure chamber13. The second discharge path11is located on the upper limit point side of the second pressure chamber13. In this structure, when the second plunger3is stopped near the upper limit point, the gap between the second plunger3and the second pressure chamber13is long in the longitudinal direction and the fluid resistance is large. Consequently, the combined fluid resistance of the flows43,45, and46becomes close to the fluid resistance of the flow42, so the flow rate of the flow43becomes large. Consequently, the speed of solvent replacement in the seal vicinity space44is increased and the speed of solvent replacement in the entire second pressure chamber13is also increased. FIG.4is a diagram which schematically explains the flows when the second plunger3stops at the lower limit point. When the second plunger3stops at the lower limit point, the distance from the outlet of the second suction path104to the space of the second pressure chamber13above the second plunger3is short, so the fluid resistance of the flow42is smaller than in the case ofFIG.3. Consequently, the flow rate of the flow43into the seal vicinity space44becomes small, so the solvent in the seal vicinity space44is hard to replace and the time of the solvent in the entire second pressure chamber13is slow. Unlike the operation described referring toFIGS.2to3, in the solvent replacement process, the solvent can also be replaced by reciprocating movement of the second plunger3between the upper limit point and lower limit point. This operation may be said to be an intermediate mode between the ones inFIG.3andFIG.4. Therefore, solvent replacement is quicker than inFIG.4but slower than inFIG.3(which will be explained referring toFIG.5). For this reason, the operation described referring toFIG.2toFIG.3can be said to be preferable. FIG.5shows the result of calculation of temporal change in the solvent replacement ratio in the second pressure chamber13in a fluid simulation. The figure shows the solvent replacement ratio in the second pressure chamber13in the case that the second plunger3stops at the upper limit point (solid line), in the case that it stops at the lower limit point (broken line) and in the case that it reciprocates between the upper limit point and lower limit point (chain line). It is known fromFIG.5that when the second plunger3stops at the upper limit point, the solvent can be replaced most quickly. FIG.6is a diagram which schematically explains the flows generated in the second pressure chamber13and the solvent replacement when the second suction path104is located on the upper limit point side of the second pressure chamber13and the second discharge path11is located on the upper limit point side of the second pressure chamber13. In this structure, since the volumetric capacity of the tip of the second pressure chamber13is large, most of the flow of the solvent coming from the second suction path104passes through the tip of the second pressure chamber13and flows out through the second discharge path11and the flow rate of the flow42going from the gap between the second plunger3and the second pressure chamber13to the seal vicinity space44is small. Therefore, the solvent in the seal vicinity space44is hardly replaced. However, when the second plunger3is nearer to the upper limit point, the volumetric capacity of the tip of the second pressure chamber13is smaller and the flow rate of the flow42going to the seal vicinity space44is larger. Therefore, in the arrangement of the second suction path104and the second discharge path11as shown inFIG.6too, solvent replacement is made most quickly in the case that the second plunger3stops at the upper limit point. FIG.7is a diagram which schematically explains the flows generated in the second pressure chamber13and the solvent replacement when the second suction path104is located on the lower limit point side of the second pressure chamber13and the second discharge path11is located on the lower limit point side of the second pressure chamber13. In this structure, since the tip area of the second pressure chamber13is remotest from both the second suction path104and the second discharge path11, the tip area of the second pressure chamber13becomes a stagnation area and virtually no flow is generated. However, when the second plunger3is nearer to the upper limit point, the volumetric capacity of the tip of the second pressure chamber13is smaller. Therefore, in the arrangement of the second suction path104and the second discharge path11as shown inFIG.7too, solvent replacement is made most quickly in the case that the second plunger3stops at the upper limit point. FIG.8is a diagram which schematically explains the flows generated in the second pressure chamber13and the solvent replacement when the second suction path104is located on the upper limit point side of the second pressure chamber13and the second discharge path11is located on the lower limit point side of the second pressure chamber13. In this structure, the flow of the solvent coming from the second suction path104is divided into a flow48passing through the tip of the second pressure chamber13and then going through the gap between the second plunger3and the second pressure chamber13to the discharge path11, and a flow42going directly into the gap between the second plunger3and the second pressure chamber13. After the flow42runs in the seal vicinity space44(flow45), it passes through the gap between the second plunger3and the second pressure chamber13(flow46) and goes to the second discharge path11. When the second plunger3stops at the upper limit point, the gap between the second plunger3and the second pressure chamber42is long in the longitudinal direction and the fluid resistance is large. Consequently, since the combined fluid resistance of the flows42,45, and46is close to the fluid resistance of the flow48, the flow rate of the flow42is large. Consequently, the solvent replacement in the seal vicinity space44is quick and the solvent replacement in the entire second pressure chamber13is also quick. Therefore, in the arrangement of the second suction path104and the second discharge path11as shown inFIG.8too, solvent replacement is made most quickly in the case that the second plunger3stops at the upper limit point. First Embodiment: Conclusion In the liquid feed pump1according to the first embodiment, at the time of solvent replacement, the second plunger3stops at the upper limit point (or its vicinity) and the first plunger2slides back and forth. Consequently, the solvent replacement speed can be higher than in the case that the second plunger3stops at the lower limit point (FIG.4) and in the case the it reciprocates from the upper limit point to the lower limit point. This effect is the same regardless of whether the second suction path104and the second discharge path11are each located either on the upper limit point side or on the lower limit point side. In the liquid feed pump1according to the first embodiment, the life of the second seal62is longer when the second plunger3is stopped at the time of solvent replacement, than when the second plunger3is moved. Furthermore, as explained later in connection with the third embodiment which will be described later, pressure loss on the suction side is smaller in the first plunger pump101than in the case that at the time of solvent replacement the first plunger2stops and only the second plunger3moves, so solvent cavitation hardly occurs. Second Embodiment FIG.9is a diagram which illustrates the method of operation in which the liquid feed pump1according to the second embodiment of the present invention replaces the solvent from the first solvent511to the second solvent512. The configuration of the liquid feed pump1is the same as in the first embodiment. In the second embodiment, the normal liquid feed step is carried out with the upper limit point as a reference position. Next, usingFIG.9an explanation will be made focusing on the different point from the first embodiment. In the normal liquid feed step, the first plunger2and second plunger3both move with reference to the upper limit point. First, with the first electromagnetic valve81open, the second electromagnetic valve82closed, and the purge valve311connected to the injector53side, normal liquid feed is performed and the first solvent511is fed to the injector53side. In the transition step, under this condition, the first plunger2and the second plunger3are once stopped and the purge valve311is switched to the drain tank313side. Then, after the first plunger2ascends to the upper limit point, the second plunger3ascends to the upper limit point. After that, the first electromagnetic valve81is changed to the closed state and the second electromagnetic valve82is changed to the closed state. In the solvent replacement step, under this condition, while the second plunger3remains stopped, only the first plunger2reciprocates between the upper limit point and lower limit point so that the solvent in the liquid feed pump1is replaced from the first solvent511to the second solvent512. In the transition step from solvent replacement to normal analysis, first the first plunger2descends and then while the first plunger2is moving to the upper limit point again, the second plunger3descends for a required distance. After that, the purge valve311is switched to the injector53side to start normal liquid feed. When the plunger is driven with reference to the upper limit point in the normal liquid feed step and then solvent replacement is made as shown inFIG.9, the time for transition from the normal liquid feed step to the solvent replacement step (period of the transition step) is shorter than in normal liquid feed with reference to the lower limit point. This is because there is no need to move the plunger from the lower limit point to the upper limit point. Therefore, if the period of transition from normal liquid feed to solvent replacement is required to be shortened, operation as shown inFIG.9is advantageous. Third Embodiment FIG.10is a diagram which illustrates the method of operation in which the liquid feed pump1according to the third embodiment of the present invention replaces the solvent from the first solvent511to the second solvent512. The configuration of the liquid feed pump1is the same as in the first embodiment. In the third embodiment, unlike the first embodiment, in the solvent replacement step, the first plunger2is stopped at the upper limit point and only the second plunger3is driven. Next, usingFIG.10an explanation will be made focusing on the different point from the first embodiment. In the method of operation as shown inFIG.10, the transition step from normal liquid feed to solvent replacement and the transition step from solvent replacement to normal liquid feed are the same as in the first embodiment. In the solvent replacement step, the first plunger2remains stopped and only the second plunger3reciprocates between the upper limit point and lower limit point. Since the first plunger2remains stopped, the life of the first seal61is longer than in the first embodiment in which the first plunger2is driven. Fourth Embodiment FIG.11is a diagram which illustrates the method of operation in which the liquid feed pump1according to the fourth embodiment of the present invention replaces the solvent from the first solvent511to the second solvent512. The configuration of the liquid feed pump1is the same as in the first embodiment. In the fourth embodiment, at the time of solvent replacement, reciprocating sliding motion of the first plunger2and reciprocating sliding motion of the second plunger3are performed alternately. Next, usingFIG.11an explanation will be made focusing on the different point from the first embodiment. In the method of operation as shown inFIG.11, the transition step from normal liquid feed to solvent replacement and the transition step from solvent replacement to normal liquid feed are the same as in the first embodiment. In the solvent replacement step, first the first plunger2descends from the upper limit point to the lower limit point and then ascends to the upper limit point again. At this time, the second plunger2remains stopped at the upper limit point. Then, while the first plunger2remains stopped at the upper limit point, the second plunger3descends from the upper limit point to the lower limit point and then ascends to the upper limit point again. Reciprocating sliding motion of the first plunger2and reciprocating sliding motion of the second plunger3are repeated in this way to replace the solvent. Operation as shown inFIG.11generates flows into the seal vicinity space as shown inFIG.3both in the first pressure chamber12and second pressure chamber13and in both the chambers the solvent can be replaced effectively. In addition, since the first plunger2and the second plunger3move for the same distance in the solvent replacement step, the load applied to the first seal61and the load applied to the second seal62are almost the same and thus the average seal life is longer than when only one of the plungers is driven as in the first to third embodiments. FIG.11shows an example that the period of movement of the first plunger2and the period of movement of the second plunger3are switched after each reciprocation, but it is not always necessary to switch between the first plunger2and the second plunger3after each reciprocation. For example, switching may be done every two times of reciprocation or a modified mode of operation, for example, in which after the first plunger2reciprocates twice, the second plunger3reciprocates once, may be adopted. In other words, when one of the first plunger2and second plunger3reciprocates, the other should temporarily stop. Fifth Embodiment FIG.12is a diagram which illustrates the method of operation in which the liquid feed pump1according to the fifth embodiment of the present invention replaces the solvent from the first solvent511to the second solvent512. The configuration of the liquid feed pump1is the same as in the first embodiment. In the fifth embodiment, at the time of solvent replacement, the first plunger2reciprocates between the upper limit point and lower limit point and the second plunger3slightly moves in the opposite direction to movement of the first plunger2with reference to the upper limit point. Next, usingFIG.12an explanation will be made focusing on the different point from the first embodiment. In the method of operation as shown inFIG.12, the transition step from normal liquid feed to solvent replacement and the transition step from solvent replacement to normal liquid feed are the same as in the first embodiment. In the solvent replacement step, first the first plunger2descends from the upper limit point to the lower limit point. Then, at the same time when the first plunger2ascends to the upper limit point again, the second plunger3slightly descends. After that, in conjunction with reciprocation of the first plunger2between the upper limit point and lower limit point, the second plunger3repeatedly ascends and descends in the opposite direction to movement of the first plunger2. In the transition step from solvent replacement operation to normal analysis, first the first plunger2moves to the lower limit point and the second plunger3moves to the upper limit point. After that, as in the first embodiment, while the first plunger2is moving to the upper limit point again, the second plunger3moves to the lower limit point and then the first plunger2again moves to the lower limit point. FIG.13is a diagram which schematically shows the flows in the second pressure chamber13with the descent of the second plunger3in the solvent replacement process when the first plunger2ascends. As the second plunger3descends, a flow47which pulls the solvent toward the second seal62is generated. At this time, as the descent of the second plunger3makes the gap between the second plunger3and the second pressure chamber13longer, when the effect that the flow47joins the flow43is relatively larger than the effect that the flow toward the direction of the flow42becomes easier, the flow43into the seal vicinity space43becomes larger. Consequently, solvent replacement in the entire second pressure chamber13becomes quicker. As for the motions of the first plunger2and second plunger3as shown inFIG.12, their respective roles may be reversed (the first plunger2slightly moves with reference to the upper limit point and the second plunger3reciprocates between the upper limit point and lower limit point) or their roles may be changed alternately every reciprocation or every several times of reciprocation. Sixth Embodiment FIG.14is a diagram which illustrates the method of operation in which the liquid feed pump1according to the sixth embodiment of the present invention replaces the solvent from the first solvent511to the second solvent512. The configuration of the liquid feed pump1is the same as in the first embodiment. In the sixth embodiment, at the time of solvent replacement, the first plunger2reciprocates between the upper limit point and lower limit point and the second plunger3slightly moves in the same direction as the first plunger2with reference to the upper limit point. Next, usingFIG.14an explanation will be made focusing on the different point from the first embodiment. In the method of operation as shown inFIG.14, the transition step from normal liquid feed to solvent replacement and the transition step from solvent replacement to normal liquid feed are the same as in the first embodiment. In the solvent replacement step, at the same time when the first plunger2descends from the upper limit point to the lower limit point, the second plunger3slightly descends. After that, at the same time when the first plunger2ascends toward the upper limit point, the second plunger3ascends to the upper limit point. Then, in conjunction with reciprocation of the first plunger2between the upper limit point and lower limit point, the second plunger3repeatedly ascends and descends in the same direction as the first plunger2. The other points are the same as in the fifth embodiment. FIG.15is a diagram which schematically shows the flows in the second pressure chamber13with the ascent of the second plunger3in the solvent replacement process when the first plunger2ascends. The ascent of the second plunger3generates a flow48which pulls the solvent toward the tip of the second pressure chamber13. Consequently, the flow42becomes larger and the flow going toward the tip area of the second pressure chamber13in the stagnation area becomes larger so that the solvent replacement in the entire second pressure chamber13becomes quicker. As for the motions of the first plunger2and second plunger3as shown inFIG.14, their respective roles may be reversed (the first plunger2slightly moves with reference to the upper limit point and the second plunger3reciprocates between the upper limit point and lower limit point) or their roles may be changed alternately every reciprocation or every several times of reciprocation. Variations of the Present Invention The present invention is not limited to the above embodiments but includes various variations. For example, the above embodiments have been described in detail for easy understanding of the present invention; however the present invention is not limited to a structure which includes all the elements described above. An element of an embodiment may be replaced by an element of another embodiment or an element of another embodiment may be added to the elements of an embodiment. For some of the elements of each embodiment, addition of another element, deletion, or replacement can be made. As a derivation from the abovementioned embodiments, the zone in which the plunger reciprocates need not be strictly between the upper limit point and lower limit point and the position at which the plunger stops need not be the upper limit point. For example, in the first embodiment, if the first plunger2moves with reference to below the upper limit point to replace the solvent, the time of transition from normal liquid feed to solvent replacement is shorter. Similarly, if the position at which the second plunger3stops is below the upper limit point, the time of transition from normal liquid feed to solvent replacement is shorter. If the time assigned to solvent replacement is fixed, the solvent replacement ratio may be increased by shortening the transition time using such a drive method to replace the solvent. In the configuration of the liquid feed pump1inFIG.1, the shapes of the elements of the first plunger pump101and those of the second plunger pump102need not be the same. For example, the outside diameter of the second plunger3may be smaller than the outside diameter of the first plunger. In addition, the depth of the second pressure chamber13(maximum stroke of the second plunger3) may be shorter than the depth of the first pressure chamber12. The method of operation should be selected appropriately according to various parameters related to the pump shape, including the inside diameter and length of the cylinder, the volumetric capacity of the seal portion and the volumetric capacity of the tip stagnation area, so that solvent replacement is shortest. In the above embodiments, as the mechanism to change the solvent to be introduced into the liquid feed pump1, the first electromagnetic valve81and second electromagnetic valve82are given as an example, but any other appropriate mechanism may be used to change the solvent. The relative merits and demerits of the effect of the solvent replacement described in each embodiment differ depending on the liquidity of the solvent to be introduced. Therefore, by appropriately selecting the method of operation according to each embodiment depending on the type of solvent, the time required for solvent replacement can be shortened. LIST OF REFERENCE SIGNS 1: liquid feed pump2: first plunger3: second plunger4: first check valve5: second check valve10: first suction path11: second discharge path12: first pressure chamber13: second pressure chamber50: controller53: injector54: separation column55: detector | 36,847 |
11859601 | DETAILED DESCRIPTION Fluid End Assembly Turning now toFIGS.3-80, a high pressure pump50is shown inFIG.3. The pump50comprises a fluid end assembly52joined to a power end assembly54. The power end assembly54is described in more detail in U.S. patent application Ser. No. 17/884,691, authored by Keith et al., and filed on Aug. 10, 2022, the entire contents of which are incorporated herein by reference (hereinafter “the '691 application”). In alternative embodiments, the fluid end assembly52may be attached to other power end designs known in the art. The fluid end assembly52is described herein. Fluid is routed throughout the fluid end assembly using a fluid routing plug132. The fluid routing plug132and various embodiments thereof are described herein. Fluid End Section Turning toFIGS.4-8, the fluid end assembly52comprises a plurality of fluid end sections56positioned in a side-by-side relationship, as shown inFIGS.6-8. Each fluid end section56is attached to the power end assembly54using a plurality of stay rods58, as shown inFIGS.4and5. Preferably, the fluid end assembly52comprises five fluid end sections56positioned adjacent one another. In alternative embodiments, the fluid end assembly52may comprise more or less than five fluid end sections56. In operation, a single fluid end section56may be removed and replaced without removing the other fluid end sections56from the fluid end assembly52. Housing of Fluid End Section Turning toFIGS.10-16, each fluid end section56comprises a horizontally positioned housing60having a longitudinal axis62extending therethrough, as shown inFIGS.10and11. The housing60has opposed front and rear surfaces64and66joined by an outer intermediate surface68. A horizontal bore70is formed within the housing60and interconnects the front and rear surfaces64and66, as shown inFIGS.14and15. The horizontal bore70is sized to receive various components configured to route fluid throughout the housing60, as shown inFIG.9. The various components will be described in more detail later herein. Continuing withFIGS.10-16, the housing60is of multi-piece construction. The housing60comprises a first section72joined to a second section74and a third section76by a plurality of first fasteners78, as shown inFIGS.15and16. By making the housing60out of multiple pieces rather than a single, integral piece, any one of the sections72,74, and76may be removed and replaced with a new section72,74, and76, without replacing the other sections. For example, if a portion of the second section74begins to erode or crack, the second section74can be replaced without having to replace the first or third sections72and76. In contrast, if the housing60were one single piece, the entire housing would need to be replaced, resulting in much more costly repair to the fluid end assembly52. First Section of Housing Turning toFIGS.17-21, the first section72is positioned at the front end of the housing60and includes the front surface64. During operation, fluid within the first section72remains at relatively the same high pressure. Thus, the first section72is considered the static or constant high pressure section of the housing60. The first section72is configured to be attached to a plurality of the stay rods58, as shown inFIGS.19-21. Thus, each fluid end section56is attached to the power end assembly54via the first section72of the housing60. Continuing withFIGS.17and18, each first section72comprises the front surface64joined to a rear surface80. The surfaces64and80are interconnected by a portion of the outer intermediate surface68and a portion of the horizontal bore70. The outer intermediate surface68of the first section has the shape of a rectangular prism with a plurality of notches82formed within the front surface64. A notch82is formed within each corner of the first section72such that the front surface64has a cross-sectional shape of a cross sign having radiused corners. The notches82are configured to receive a first end84of each stay rod58, as shown inFIG.21. With reference toFIGS.17-21, a plurality of passages86are formed in the first section72. Each passage86interconnects the rear surface80and a medial surface88of the first section72. The medial surface88is defined by the plurality of notches82. Each passage86comprises a counterbore87that opens on the rear surface80, as shown inFIG.16, and is configured to receive a corresponding one of the stay rods58. When installed within the first section72, the first end84of each stay rod58projects from the medial surface88and into the corresponding notch82, as shown inFIG.21. Continuing withFIGS.19-21, a threaded nut90 is installed on the first end84of each stay rod58within each notch82. The nut90 is a three-piece nut, also known as a torque nut, that facilitates the application of high torque required to properly fasten the fluid end section56to the power end assembly54. The nut90 is described in more detail in the '691 application. In alternative embodiments, a traditional 12-point flange nut similar to the flange nut230, shown inFIGS.27and28, may be installed on the first end84of each stay rod58instead of the nut90. Continuing withFIGS.19-22, a sleeve94is disposed around a portion of each stay rod58and extends between the rear surface80of the first section72and the power end assembly54, as shown inFIG.3. A dowel sleeve93is inserted into each counterbore87formed in each passage86, as shown inFIG.22. When installed therein, a portion of the dowel sleeve93projects from the rear surface80of the first section72. A counterbore95is formed within the hollow interior of the sleeve94for receiving the projecting end of the dowel sleeve93, as shown inFIG.22. The dowel sleeve93aligns the sleeve94and the passage86concentrically. Such alignment maintains a planar engagement between the rear surface80of the first section72and the sleeve94. When the nut90 is torqued against the medial surface88of the first section72, the sleeve94abuts the rear surface80of the first section72, rigidly securing the first section72to the stay rod58. Turning back toFIGS.14-16, and18, a plurality of threaded openings96are formed in the rear surface80of the first section72. The openings96surround an opening of the horizontal bore70, as shown inFIG.18. Each opening96is configured to receive a corresponding one of the first fasteners78used to secure the sections72,74, and76together, as shown inFIGS.15and16. A plurality of dowel openings98are also formed in the rear surface80adjacent the openings96, as shown inFIGS.14and18. The dowel openings98are configured to receive first alignment dowels100, as shown inFIG.14. The first alignment dowels100assist in properly aligning the first section72and the second section74during assembly of the housing60. Continuing withFIG.14, a pair of upper and lower discharge bores102and104are formed within the first section72and interconnect the intermediate surface68and the horizontal bore70. The upper and lower discharge bores102and104shown inFIG.14are collinear. In alternative embodiments, the bores102and104may be offset from one another and not collinear. Each bore102and104may include a counterbore106that opens on the intermediate surface68. Each counterbore106is sized to receive a portion of a discharge fitting adapter504, as shown inFIG.9. The fitting adapter504spans between the discharge bore102or104and a discharge fitting108attached to the outer intermediate surface68of the first section72. Continuing withFIG.14, a groove110may be formed in the side walls of the counterbore106for receiving a seal112. The seal112engages an outer surface of the fitting adapter504to prevent fluid from leaking between the first section72and the discharge fitting108, as shown inFIG.9. With reference toFIGS.17and18, a plurality of threaded openings114are formed in the intermediate surface68and surrounding the opening of the upper and lower discharges bores102and104. The threaded openings114are configured to receive a plurality of threaded fasteners116configured to secure a discharge fitting108to the first section72, as shown inFIG.9. Continuing withFIGS.14and15, the walls surrounding the horizontal bore70within the first section72and positioned between the front surface64and the upper and lower discharge bores102and104are sized to receive a front retainer118and a discharge plug120, as shown inFIG.9. The discharge plug120seals fluid from leaking from the front surface64of the housing60, and the front retainer118secures the discharge plug120within the first section72of the housing60. Continuing withFIGS.14and15, internal threads122are formed in the walls of the first section72for mating with external threads124, shown inFIGS.76and77, formed on an outer surface of the front retainer118. In contrast, an outer surface of the discharge plug120faces flat walls of the first section72. A small amount of clearance may exist between the plug120and the walls of the first section72. Continuing withFIGS.14and15, a groove125may be formed in such walls for receiving a seal126configured to engage an outer surface of the discharge plug120, as shown inFIG.9. The seal126prevents fluid from leaking around the discharge plug120during operation. A locating cutout128may further be formed in the walls that is configured to receive a locating dowel pin130. As will be described later herein, the locating dowel pin130is used to properly align the discharge plug120within the housing60. Continuing withFIGS.14and15, the walls surrounding the horizontal bore70and positioned between the upper and lower discharge bores102and104and the rear surface80of the first section72are sized to receive a portion of a fluid routing plug132, as shown inFIG.9. This area of the walls surrounding the horizontal bore70includes a counterbore134that opens on the rear surface80. The counterbore134is sized to receive a wear ring136, as shown inFIG.9. The wear ring136has an annular shape and is configured to engage a first seal386installed within an outer surface of the fluid routing plug132, as shown inFIG.9. In alternative embodiments, the first section72may not include the counterbore134or the wear ring136and instead may be sized to directly engage the first seal386installed within the fluid routing plug132. Continuing withFIG.9, in addition to the above mentioned components, the first section72is also configured to house a discharge valve138. The components discussed above and installed within the first section72will be described in more detail later herein. Second Section of Housing Turning toFIGS.23and24, the second section74of the housing60is configured to be positioned between the first and third sections72and76and has a cylindrical cross-sectional shape. During operation, fluid pressure within the second section74remains at relatively the same pressure. The pressure is lower than that within the first section72. Thus, the second section74may be referred to as the static or constant low pressure section of the housing60. The second section74comprises opposed front and rear surfaces140and142joined by a portion of the outer intermediate surface68and a portion of the horizontal bore70. Continuing withFIGS.15,16,23, and24, a plurality of passages144are formed in the second section74. The passages144surround the horizontal bore70and interconnect the front and rear surfaces140and142, as shown inFIGS.15and16. Each passage144is configured to receive a corresponding one of the first fasteners78used to secure the sections72,74, and76of the housing60together. Continuing withFIGS.14,23, and24, a plurality of dowel openings146are formed in the front surface140of the second section74, as shown inFIG.23. The dowel openings146align with the dowel openings98formed in the rear surface80of the first section72and are configured to receive a portion of the first alignment dowels100, as shown inFIG.14. Likewise, a plurality of dowel openings148are formed in the rear surface142of the second section74, as shown inFIG.24. The dowel openings148are configured to receive a portion of second alignment dowels150, as shown inFIG.14. The second alignment dowels150are configured to align the second section74and the third section76during assembly. Continuing withFIGS.14,15,23and24, a first annular groove152is formed in the front surface140of the second section74such that it surrounds an opening of the horizontal bore70, as shown inFIG.23. The first groove152is positioned between the horizontal bore70and the plurality of passages144and is configured to receive a first seal154, as shown inFIGS.14and15. Likewise, a second annular groove156is formed in the rear surface142of the second section74and positioned between the horizontal bore70and the plurality of passages144, as shown inFIG.24. The second groove156is configured to receive a second seal158, as shown inFIGS.14and15. The seals154and158shown inFIGS.14and15are O-rings. The seals154and158prevent fluid from leaking between the first and second sections72and74and between the second and third sections74and76during operation. Continuing withFIGS.14,23, and24, a pair of upper and lower suction bores160and162are formed within the second section74and interconnect the intermediate surface68and the horizontal bore70. The upper and lower suction bores160and162shown inFIG.14are collinear. In alternative embodiments, the bores160and162may be offset from one another and not collinear. Continuing withFIGS.9and14, the suction bores160and162are each configured to receive a suction conduit166, as shown inFIG.9. The suction conduit166comprises a first connection member164configured to mate with the housing60. Each suction bore160and162opens into a counterbore168sized to receive a portion of the first connection member164. Internal threads170are formed in a portion of the walls surrounding the counterbore168for mating with external threads172, shown inFIG.78, formed on the first connection member164. Continuing withFIGS.9and14, a groove174is formed in the walls surrounding the counterbore168and configured to receive a seal176, as shown inFIG.9. The seal176engages an outer surface of the first connection member164to prevent fluid from leaking from the housing60during operation. The suction conduits166will be described in more detail later herein. Continuing withFIGS.9,14, and15, the walls surrounding the horizontal bore70within the second section74are configured to receive a majority of the fluid routing plug132, as shown inFIG.9. A small amount of clearance may exist between the walls of the second section74and an outer surface of the fluid routing plug132. Third Section of Housing Turning toFIGS.14-16,25and26, the third section76of the housing60is positioned at the rear end of the housing60and includes the rear surface66. The third section76has a generally cylindrical cross-sectional shape. Fluid pressure within the third section76varies during operation. Thus, the third section76may be referred to as the dynamic or variable pressure section of the housing60. Continuing withFIGS.25and26, the third section76comprises a front surface178joined to the rear surface66of the housing60by a portion of the outer intermediate surface68and a portion of the horizontal bore70. The outer intermediate surface68of the third section76varies in diameter such that the third section76comprises a front portion180joined to a rear portion182. Continuing withFIGS.15,16,25, and26, the front portion180has a constant outer diameter and has a plurality of passages184formed therein. The passages184interconnect the front surface178and a medial surface186of the third section76. The passages184align with the plurality of passages144formed in the second section74and the threaded openings96formed in the first section72of the housing60, as shown inFIGS.14and15. The passages184are configured to receive the first fasteners78used to secure the sections72,74, and76together. Continuing withFIGS.14and25, a plurality of dowel openings188are formed in the front surface178of the third section76, as shown inFIG.25. The dowel openings188are configured to receive a portion of second alignment dowels150, as shown inFIG.14. The second alignment dowels150are configured to properly align the third section76within the second section74during assembly. Continuing withFIGS.25and26, the rear portion182of the third section76comprises a neck190joined to a shoulder192. The neck190interconnects the front portion180and the shoulder192. The shoulder192includes the rear surface66of the housing60. The neck190has a smaller outer diameter than that of the front portion180and the shoulder192to provide clearance for the plurality of passages184formed in the front portion180. With reference toFIGS.25and26, a plurality of first threaded openings194are formed in the rear surface66of the third section76. The first threaded openings194are configured to receive a plurality of second fasteners196, as shown inFIG.29. The second fasteners196are configured to secure a stuffing box198and a rear retainer200to the third section76of the housing60, as shown inFIG.29. The stuffing box198and the rear retainer200will be described in more detail later herein. With reference toFIGS.26and32, a plurality of second threaded openings202are also formed in the rear surface66of the third section76, as shown inFIG.26. The second threaded openings202are configured to receive a plurality of third fasteners204. The third fasteners204are configured to secure a retention plate206to the rear surface of the housing60, as shown inFIG.32. The retention plate206will be described in more detail later herein. A plurality of dowel openings207are also formed in the rear surface of the third section76. The dowel openings207are configured to receive third alignment dowels242, as shown inFIG.39. Turning back toFIGS.9,14,15, and25, a counterbore208is formed in the walls surrounding the horizontal bore70within the third section76and opens on the front surface178. The counterbore208is configured to receive a hardened insert210, as shown inFIG.9. The insert210will be described in more detail later herein. The insert210engages portions of the fluid routing plug132when the fluid routing plug132is installed within the housing60, as shown inFIG.9. The walls surrounding the horizontal bore70between the counterbore208and the medial surface186of the third section76are further configured to receive a suction valve guide212. A suction valve214is also installed within the third section76of the housing60. The suction valve214and suction valve guide212will be described in more detail later herein. Continuing withFIGS.9,14,15,25, and26, the walls surrounding the horizontal bore70within the neck190of the rear portion182are sized to receive at least a portion of a reciprocating plunger216, as shown inFIG.9. The portion of the horizontal bore70extending through the neck190has a uniform diameter and opens into a first counterbore218formed in the shoulder192, as shown inFIGS.14and15. The first counterbore218is sized to receive a portion of the stuffing box198, as shown inFIG.9. The first counterbore218opens into a second counterbore220, of which opens on the rear surface66of the housing60, as shown inFIGS.14,15, and26. The second counterbore220is sized to receive a wear ring222and a seal224, as shown inFIG.9. The wear ring222and the seal224each have an annular shape. When such components are installed within the housing60, the wear ring222surrounds the seal224, and the seal224engages an outer surface of the stuffing box198. Assembly of Housing Turning toFIGS.27-29, the housing60is assembled by threading a first end226of each of the first fasteners78into a corresponding one of the threaded openings96formed in the first section72. Once installed therein, the first fasteners78project from the rear surface80of the first section72. The second and third sections74and76may then be slid onto the fasteners78projecting from the first section72using the corresponding passages144and184. The first and second alignment dowels100and150help to further align the sections72,74, and76together during assembly. Continuing withFIGS.27-29, when the second and third sections74and76are installed on the fasteners78, a second end228projects from the medial surface186of the third section76, as shown inFIG.29. A flange nut230is installed on the second end228and torqued against the medial surface186, tightly securing the sections72,74, and76together. When the housing60is assembled, a footprint of the rear surface142of the second section74is entirely within a footprint of the rear surface80of the first section72, as shown inFIG.29. Continuing withFIGS.27-29, the first fastener78shown in the figures is a threaded stud. In alternative embodiments, other types of fasteners known in the art may be used instead of a threaded stud. For example, screws or bolts may be used to secure the sections together. In further alternative embodiments, the nut may comprise the three-piece nut90, shown inFIGS.19-21. Continuing withFIGS.27-29, to remove a section72,74, or76, the nut230is unthreaded from the second end228of each first fastener78. The sections72,74, and76may then be pulled apart, as needed. If the first section72is being replaced, the first fasteners78are also unthreaded from the threaded openings96. The components installed within the housing60may also be removed, as needed, prior to disassembling the housing60. Components Attached to Rear Surface of Housing Turning toFIGS.29-32, in addition to the housing60, the fluid end section56comprises a plurality of components attached to the rear surface66of the housing60. Such components are configured to receive the plunger216. The various components include the retention plate206, the stuffing box198, and the rear retainer200, previously mentioned. The components further comprise a plunger packing300, and a packing nut290. Retention Plate Continuing withFIGS.29-32, the retention plate206has a cylindrical cross-sectional shape and is sized to cover the rear surface66of the housing60and the wear ring222and the seal224, as shown inFIG.29. The retention plate206holds the wear ring222and the seal224within the housing60in the event the stuffing box198needs to be removed. Continuing withFIGS.29-32, the retention plate206comprises opposed front and rear surface237and238joined by a central opening239formed therein. A plurality of first passages234are formed in the retention plate206and surround the central opening239of the plate206. The first passages234align with the first threaded openings194formed in the rear surface66of the housing60and are configured to receive the plurality of second fasteners196. Continuing withFIGS.30-32, a plurality of second passages236are also formed in the retention plate206. The second passages236align with the second threaded openings202formed in the rear surface66of the housing60and are configured to receive the third fasteners204, as shown inFIG.32. A third fastener204is threaded into one of the second threaded openings202and turned until it sits flush with the rear surface238of the retention plate206, as shown inFIG.32. Continuing withFIGS.30-32, a plurality of dowel openings240are formed in the retention plate206for receiving third alignment dowels242, as shown inFIG.39. The third alignment dowels242assist in properly aligning the retention plate206and the stuffing box198on the housing60during assembly. Turning back toFIG.29, since fluid does not contact the retention plate206during operation, the retention plate206may be made of a different and less costly material than that of the housing60or the stuffing box198. For example, the retention plate206may be made of alloy steel, while the housing60and stuffing box198are made of stainless steel. Stuffing Box Turning toFIGS.29,33,34, and39, the stuffing box198comprises opposed front and rear surfaces244and246joined by an outer intermediate surface248and a central passage250formed therein. The stuffing box198further comprises a front portion252joined to a rear portion254. The front portion252has a smaller outer diameter than the rear portion254such that a medial surface256is formed between the front and rear surfaces244and246. The front portion252includes the front surface244of stuffing box198, and the rear portion254includes the rear surface246of the stuffing box198. An internal shoulder272is formed within the walls surrounding the central passage250within the rear portion254of the stuffing box198. Continuing withFIGS.33,34, and39, a plurality of passages258are formed within the rear portion254of the stuffing box198and interconnect the medial surface256and the rear surface246. The passages258are configured to align with the plurality of first passages234formed in the retention plate206and the plurality of first threaded openings194formed in the rear surface66of the housing60, as shown inFIG.29. Continuing withFIGS.33,34, and39, a plurality of dowel openings260may be formed in the medial surface256of the stuffing box198. The dowel openings260are configured to receive at least a portion of the third alignment dowels242to properly align the stuffing box198on the retention plate206and the housing60during assembly, as shown inFIG.39. Likewise, a plurality of dowel openings268may be formed in the rear surface246of the stuffing box198for receiving fourth alignment dowels270, as shown inFIG.39. The fourth alignment dowels270assist in properly aligning the rear retainer200on the stuffing box198during assembly. Continuing withFIG.39, the stuffing box198is installed within the third section76of the housing60such that the front portion252is disposed within the horizontal bore70and the medial surface256abuts the rear surface238of the retention plate206. The outer intermediate surface248of the front portion252of the stuffing box198engages the seal224. The seal224prevents fluid from leaking between the housing60and the stuffing box198. Continuing withFIG.39, during operation, the seal224wears against the outer intermediate surface248of the front portion252. Should the front portion252begin to erode, the stuffing box198may be removed and replaced with a new stuffing box198. Likewise, the seal224wears against the wear ring222during operation. The wear ring222is preferably made of a harder and more wear resistant material than the housing60, such as tungsten carbide. Should the wear ring222begin to erode, the wear ring222can be removed and replaced with a new wear ring222. Trapping the seal224between replaceable parts protects the housing60over time. Rear Retainer Turning toFIGS.29,35,36, and39, the rear retainer200comprises opposed front and rear surfaces276and278joined by an outer intermediate surface280and a central passage282formed therein. A plurality of passages284are formed in the rear retainer200and surround the central passage282. The passages284interconnect the front and rear surfaces276and278of the rear retainer200and are configured to align with the passages258formed in the rear portion254of the stuffing box198, as shown inFIG.29. A plurality of dowel openings286are formed in the front surface276of the rear retainer200for receiving a portion of the fourth alignment dowels270, as shown inFIG.39. Continuing withFIGS.35,36,39, and40, an internal shoulder279is formed within the walls surrounding the central passage282of the rear retainer200. Internal threads288are formed in the walls surrounding the central passage282and positioned between the internal shoulder279and the rear surface278. The internal threads288are configured to receive a packing nut290, as shown inFIG.39. The walls positioned between the internal shoulder279and the front surface276are flat and include one or more lube ports292. The lube port292interconnects the central passage282and the outer intermediate surface280of the rear retainer200, as shown inFIG.40. Plunger Packing and Packing Nut Continuing withFIG.39, fluid is prevented from leaking around the plunger216during operation by a plunger packing300. The plunger packing300is installed within the stuffing box198and comprises a plurality of packing seals302sandwiched between first and second metal rings304and306. The first metal ring304abuts the internal shoulder272formed within the stuffing box198and the second metal ring306extends into the central passage282formed in the rear retainer200. The second metal ring306is known in the art as a “lantern ring”. One or more passages303, shown in FIG.29, may be formed in the second metal ring306and fluidly connect with the one or more lube ports292formed in the rear retainer200. During operation, oil used to lubricate the plunger216and plunger packing300is supplied through the lube port292and second metal ring306. With reference toFIGS.37-39, the plunger packing300is retained within the stuffing box198and the rear retainer200using the packing nut290. The packing nut290comprises opposed front and rear surfaces308and310joined by an outer intermediate surface312and a central passage314formed therein. External threads316are formed in a portion of the outer intermediate surface312for engaging the internal threads288formed in the rear retainer200, as shown inFIG.39. When the packing nut290is installed within the rear retainer200, the front surface308of the packing nut290engages and compresses the plunger packing300, as shown inFIG.39. When compressed, the packing seals302of the plunger packing300tightly seal against an outer surface of the plunger216. Continuing withFIG.39, during operation, the packing nut290may be tightened, as needed, to ensure adequate compression of the packing seals302against the plunger216. At least a portion of the packing nut290projects from the rear surface278of the rear retainer200to provide clearance to turn the packing nut290, as needed. The central passage314formed in the packing nut290is sized to closely receive the plunger216. A groove318may be formed in the walls surrounding the central passage314for receiving a seal320. The seal320shown inFIG.39is an O-ring. The seal320prevents fluid from leaking around the plunger216during operation. Assembly of Components on Rear Surface of Housing Turning back toFIG.29, the front surface276of the rear retainer200abuts the rear surface246of the stuffing box198such that the plurality of passages284align with the plurality of passages258formed in the stuffing box198. A second fastener196is installed within a corresponding one of the aligned first threaded openings194and passages234,258, and284. A first end294of the second fastener196threads into the first threaded opening194and a second end296projects from the rear surface278of the rear retainer200. A nut298is threaded onto the second end296and torqued against the rear surface278, tightly securing the stuffing box198and the rear retainer200to the third section76of the housing60. Continuing withFIG.29, the nut298shown in the figures is 12-point flange nut. In alternative embodiments, the nut may comprise the three-piece nut90, shown inFIGS.19-21. The second fastener196shown in the figures is a threaded stud. In alternative embodiments, the second fastener196may comprise other fasteners known in the art, such as a bolt or screw. Continuing withFIG.29, the stuffing box198and rear retainer200are attached to the housing60after the retention plate206has first been attached to the rear surface66of the housing60. The plunger packing300may be installed within stuffing box198either before or after the stuffing box198is attached to the housing60. After all the components are assembled, the packing nut290is threaded into the rear retainer200until it engages the plunger packing300. With reference toFIGS.29and39, when the retention plate206, the stuffing box198, and rear retainer200are attached to the housing60, the central opening239of the retention plate206and the central passages250and282of the stuffing box198and the rear retainer200form an extension of the horizontal bore70. Likewise, the interior of the plunger packing300and the central passage314of the packing nut290also form extensions of the horizontal bore70. The plunger216is installed within the fluid end section56through the rear surface310of the packing nut290. During operation, the plunger216reciprocates within the horizontal bore70, creating the variance in fluid pressure within the fluid end section56during operation. With reference toFIGS.3,39, and40, during operation, reciprocal movement of the plunger216is driven by a pony rod322installed within the power end assembly54. A clamp324secures the plunger216to the pony rod322such that the plunger216and pony rod322move in unison. Components Installed within the Housing Turning toFIGS.40-79, the various internal components of the housing60will now be described in more detail. Fluid is routed throughout the housing60by the fluid routing plug132. The timing of movement throughout the fluid routing plug132is controlled by the suction valve214and the discharge valve138. Movement of the valves214and138is guided by the suction valve guide212and the discharge plug120. Fluid Routing Plug Turning toFIGS.40-59, the fluid routing plug132comprises a body330having a suction surface332and an opposed discharge surface334joined by an outer intermediate surface336. A central longitudinal axis338extends through the body330and the suction and discharge surfaces332and334. When the fluid routing plug132is installed within the housing60, at least a portion of the discharge surface334is positioned within the first section72of the housing60, and at least a portion of the suction surface332is positioned within the third section76of the housing60, as shown inFIGS.40and41. Continuing withFIGS.43-59, the body330further comprises a plurality of suction fluid passages340. The suction passages340interconnect the intermediate surface336and the suction surface332of the body330, as shown inFIG.48. The connection is formed within a blind bore342formed within the suction surface332of the body330. The blind bore342may be referred to as an axially-blind bore342because it is blind along the longitudinal axis338of the body330. During operation, fluid entering the housing60through the suction bores160and162flows into the suction passages340of the fluid routing plug132and into the axially-blind bore342. From there, fluid flows towards the suction surface332of the body330and out of the fluid routing plug132. Three suction fluid passages340are shown inFIGS.43-59. In alternative embodiments, more or less than three suction fluid passages340may be formed within the body330. Continuing withFIGS.49and50, each suction passage340has a generally oval or tear drop cross-sectional shape. An opening344of each suction passage340on the intermediate surface336comprises a first side wall346joined to a second side wall348by first and second ends350and352. The first and second side walls346and348are straight lines of equal length S, and the first and second ends350and352are circular arcs, as shown inFIG.50. Continuing withFIG.50, the first end350of the opening344has a radius of R1with a center at C1, and the second end352has a radius of R2with a center at C2. The first end350is larger than the second end352such that R1>R2. The first and second side walls346and348are tangent to the first and second ends350and352and have an included angle, σ. Continuing withFIG.50, the opening344has a centerline354that connects the centers C1and C2of the first and second ends350and352. The centerline354has a length E and is parallel with the central longitudinal axis338. A cross-sectional shape of each suction passage340throughout the length of the body330corresponds with the shape of each opening344, as shown inFIG.55. Each suction passage340is sized and shaped to maximize fluid flow through the passage340and minimize fluid turbulence and stress to the body330of the fluid routing plug132. With reference toFIGS.55and56, each suction fluid passage340extends between the axially-blind bore342and the intermediate surface336such that each suction passage340comprises a longitudinal axis356. The longitudinal axis356extends through the center C1of the first end350of the opening344and intersects the central longitudinal axis338, as shown inFIG.56. Continuing withFIGS.43-59, the body330further comprises a plurality of discharge fluid passages360. The discharge passages360interconnect the suction surface332and the discharge surface334of the body330and do not intersect any of the suction passages340. Rather, the discharge and suction passages360and340are in a spaced-relationship. In operation, fluid exiting the body330at the suction surface332is subsequently forced into the discharge passages360, towards the discharge surface334of the body330, and out of the fluid routing plug132. Three discharge fluid passages360are shown inFIGS.43-59. In alternative embodiments, more or less than three discharge fluid passages360may be formed within the body330. Continuing withFIGS.43,46, and48, the suction surface332of the body330comprises an outer rim362joined to the axially-blind bore342by a tapered seating surface366, as shown inFIGS.46and48. Likewise, the discharge surface334comprises an outer rim368joined to a central base370by a tapered seating surface372, as shown inFIGS.43and48. Continuing withFIGS.43,46, and48, each discharge passage360opens at a first opening374on the outer rim362of the suction surface332and opens at a second opening376on the central base370of the discharge surface334. The second openings376surround a blind bore378formed in the central base370of the discharge surface334. The blind bore378is configured to engage a tool used to grip the fluid routing plug132, as needed. For example, the walls of the blind bore378may be threaded. The central base370may also be slightly recessed from the tapered seating surface372such that a small counterbore380is created. The counterbore380helps further reduce any turbulence of fluid exiting the second openings376. Continuing withFIG.54, a position of the first and second openings374and376of each discharge passage360may be determined relative to a plane containing a line382that is perpendicular to the central longitudinal axis338. The first opening374, when projected onto the plane, is positioned at a first distance F1from the central longitudinal axis338and at a first angle φ1relative to the line382. The second opening376, when projected onto the plane, is positioned at a second distance F2from the central longitudinal axis338and at a second angle φ2relative to the line382. The first and second distances F1and F2shown inFIG.54are different. Likewise, the first and second angles φ1and φ2shown inFIG.54are different. In alternative embodiments, the first and second angles φ1and φ2may be different, but the first and second distances F1and F2may be the same. In further alternative embodiments, the first and second angles φ1and φ2may be the same, but the first and second distances F1and F2may be different. In even further alternative embodiments, the first and second distances F1and F2may be the same, and the first and second angles φ1and φ2may be the same. With reference toFIGS.51-53and56-59, each discharge passage360has an arced cross-sectional shape. The length of the arc may gradually increase between the suction and discharge surfaces332and334, as shown inFIGS.51-53. In alternative embodiments, the discharge passages360may have different shapes and sizes. Turning back toFIGS.44and48, a first annular groove384is formed in the outer intermediate surface336of the body330for housing the first seal386. The first groove384is positioned adjacent the discharge surface334and is characterized by two sides walls388joined by a base390. When the fluid routing plug132is installed within the housing60, the first seal386engages an outer surface of the wear ring136installed within the first section72of the housing60, as shown inFIGS.40and41. During operation, the first seal386wears against the wear ring136. If the wear ring136begins to erode, the wear ring136may be removed and replaced with a new wear ring136. The wear ring136has an annular shape and may be made of a harder and more wear resistant material than the housing60. For example, the housing60may be made of stainless steel and the wear ring136is made of tungsten carbide. With reference toFIGS.42,44, and48, a second annular groove392is formed in the outer intermediate surface336of the body330for housing a second seal394. The second groove392is positioned adjacent the suction surface332and is characterized by a plurality of side walls396joined by a base398, as shown inFIG.42. Four side walls396are shown inFIG.42such that the groove392has a rounded shape. When the fluid routing plug132is installed within the housing60, the second seal394engages an outer surface of the hardened insert210, as shown inFIG.42. During operation, the second seal394wears against the insert210. If the insert210begins to erode, the insert210may be removed and replaced with a new insert210. Continuing withFIGS.42,44, and48, the outer intermediate surface336of the body330further comprises an annular shoulder400formed in the body330. The shoulder400is positioned between the opening344of the suction passages340and the second groove392. When the fluid routing plug132is installed within the housing60, the shoulder400abuts a front surface416of the insert210, as shown inFIG.42. Axial movement of the fluid routing plug132towards the rear surface66of the housing60is prevented by the engagement between the shoulder400and the insert210. During operation, the shoulder400may wear against the insert210. If either feature begins to wear, the fluid routing plug132and/or the insert210may be removed and replaced with a new fluid routing plug132and/or insert210. Continuing withFIGS.40,41,44, and48, the outer intermediate surface336of the body330adjacent the first groove384is characterized as a first cylindrical surface404. Likewise, the outer intermediate surface336adjacent the annular shoulder400is characterized as a second cylindrical surface406. The first cylindrical surface404has a maximum outer diameter that is equal or almost equal to a maximum outer diameter of the second cylindrical surface406. The surfaces404and406are configured to closely face the walls surrounding the horizontal bore70within the second section74of the housing60, as shown inFIGS.40and41. Continuing withFIGS.40,41,44,48, and49, the outer intermediate surface336of the body330further comprises a first bevel408joined to a transition surface410formed in the body330. The first bevel408and the transition surface410are positioned between the first cylindrical surface404and the openings344of the suction passages340. The outer intermediate surface336of the body330slowly tapers outward from the transition surface410to the second cylindrical surface406. Continuing withFIGS.40and41, when the fluid routing plug132is installed within the housing60, the first bevel408provides clearance between the outer intermediate surface336of the fluid routing plug132and an opening of the suction bores160and162. Such clearance gives way to an annular fluid channel412formed between the housing60and the fluid routing plug132. The shape of the outer intermediate surface336of the fluid routing plug132between the first and second cylindrical surfaces404and406helps direct fluid flowing from the suction bores160and162into the openings344of the suction passages340while minimizing fluid turbulence. Turning back toFIG.42, the outer intermediate surface336of the body330further comprises a second bevel414formed in the body330. The second bevel414is positioned between the suction surface332and the second groove392. The second bevel414provides clearance to help install the fluid routing plug132within the housing60and the insert210. Hardened Insert With reference toFIGS.42and60-63, the insert210has an annular shape and comprises opposed front and rear surfaces416and418joined by inner and outer intermediate surfaces420and422. The insert210further comprises a first bevel426formed in the inner intermediate surface420adjacent the front surface416, as shown inFIG.63. The first bevel426provides clearance to assist in installing the fluid routing plug132within the insert210within the housing60, as shown inFIG.42. The insert210also comprises a second bevel424formed in the outer intermediate surface422adjacent the rear surface418. The second bevel424provides clearance to assist in installing the insert210within the counterbore208formed in the third section76of the housing60, as shown inFIG.42. The insert210is made of a harder and more wear resistant material than the housing60. For example, if the housing60is made of stainless steel, the insert210may be made of tungsten carbide. Suction and Discharge Valves With reference toFIGS.40,41, and64-67, the flow of fluid throughout the housing60and the fluid routing plug132is regulated by the suction and discharge valves214and138. The suction valve214is configured to engage the suction surface332, and the discharge valve138is configured to engage the discharge surface334of the fluid routing plug132such that the surfaces332and334function as valve seats. The valves214and138are similar in shape but may vary in size. As shown inFIGS.40and41, the discharge valve138is slightly large than suction valve214. Continuing withFIGS.64-67, the discharge valve138is shown in more detail. The suction valve214has the same features as the discharge valve138so only the discharge valve138is shown in more detail in the figures. The discharge valve138comprises a stem402joined to a body428. The body428comprises an outer rim430joined to a valve insert432by a tapered seating surface434. An annular cutout436formed within the seating surface434is configured to house a seal438, as shown inFIG.67. Continuing withFIGS.40and41, during operation, the seating surface434and the seal438engage the seating surface372of the discharge surface334and block fluid from entering or exiting the discharge passages360, as shown inFIG.40. Likewise, the seating surface434and the seal438on the suction valve214engage the seating surface366of the suction surface332and block fluid from entering or exiting the suction passages340, as shown inFIG.41. Continuing withFIGS.40and41, when the seating surfaces434and372are engaged, the valve insert432extends partially into the counterbore380formed in the discharge surface334. Fluid exiting the second openings376of the discharge passages360contacts the insert432, pushing the discharge valve138away from the discharge surface334before flowing around the seating surface434of the discharge valve138. Such motion enlarges the area for fluid to flow between the seating surfaces372and434before fluid reaches the surfaces372and434, thereby reducing the velocity of fluid flow within such area. The lowered fluid velocity between the surfaces372and434causes any wear to the valve138or214to be concentrated at the insert432instead of the crucial sealing elements, thereby extending the life of the valve138or214. Likewise, the insert432on the suction valve214extends partially into the opening of the axially-blind bore342. Fluid within the axially-blind bore342contacts the insert432before flowing around the seating surface434and seal438of the suction valve214. Such motion enlarges the area for fluid to flow between the seating surfaces366and434before fluid reaches the surfaces366and434, thereby reducing the velocity of fluid flow within such area. Continuing withFIGS.64-67, the stem402projects from a top surface440of the body428of the valve138or214. The outer rim430surrounds the stem402and is spaced from the stem402by an annular void442. A groove444is formed in the outer rim430for receiving a portion of a spring446, as shown inFIGS.40and41. Continuing withFIGS.40and41, during operation, the valves138and214move axially along the longitudinal axis62of the housing60between open and closed positions. In the closed position, the seating surface434and the seal438of each of the valves138and214tightly engage the corresponding seating surface372or366of the fluid routing plug132and the valve insert432is disposed within the corresponding bore380or342. In the open position, the seating surface434and the seal438are spaced from the corresponding seating surface372or366of the fluid routing plug132and the valve insert432is spaced from the corresponding bore380or342. Suction Valve Guide With reference toFIGS.40,41, and68-71, axial movement of the suction valve214is guided by the suction valve guide212. The suction valve guide212comprises a thin-walled skirt448joined to a body450by a plurality of support arms452. The skirt448comprises a tapered upper section454joined to a cylindrical lower section456. The plurality of arms452join the tapered upper section454to the body450. A plurality of flow ports458are formed between adjacent arms452such that fluid may pass through the suction valve guide212during operation. Continuing withFIGS.40and41, the suction valve guide212is installed within the housing60such that the tapered upper section454engages a tapered surface455of the walls surrounding the horizontal bore70. Such engagement prevents further axial movement of the suction valve guide212within the housing60. When the suction valve guide212is installed within the housing60, the skirt448covers the walls of the housing60positioned between the flow ports458and the fluid routing plug132. During operation, fluid wears against the skirt448, thereby protecting the housing60from wear and erosion. If the skirt448begins to erode, the suction valve guide212can be removed and replaced with a new guide212. Continuing withFIGS.40,41, and68-71, the body450of the suction valve guide212is tubular and is centered within the skirt448. A tubular insert460is installed within the body450, as shown inFIG.71. The insert460is configured to receive the stem402of the suction valve214, as shown inFIGS.40and41. During operation, the stem402moves axially within the insert460and wears against the insert460. An annular cutout462formed in the stem402, shown inFIGS.66and67, provides space for any fluid or other material trapped between the stem402and the insert460. The insert460is made of a harder and more wear resistant material than the body450thereby extending the life of the suction valve guide212. For example, if the body450is made of stainless steel, the insert460may be made of tungsten carbide. Continuing withFIGS.40and41, a spring446is positioned between the outer rim430of the suction valve214and the plurality of arms452such that the spring446surrounds at least a portion of the body450of the suction valve guide212. During operation, the spring446biases the suction valve212in a closed position, as shown inFIG.41. Fluid pushing against the valve insert432moves the suction valve214axially to compress the spring446and move the suction valve214to an open position, as shown inFIG.40. Discharge Plug With reference toFIGS.40,41, and72-75, axial movement of the discharge valve138is guided by the discharge plug120. The discharge plug120comprises a pair of legs464joined to a body466. The body466comprises a front portion468joined to a rear portion470by a medial portion472. The medial portion472has a larger outer diameter than both the front and rear portions468and470. An outer surface of the medial portion472engages the seal126installed within the first section72of the housing60, as shown inFIGS.40and41. The pair of legs464are joined to the medial portion472and extend between the medial portion472and the discharge surface334of the fluid routing plug132. Continuing withFIGS.40,41, and72-75, a dowel opening474is formed in the outer surface of the medial portion472for receiving the locating dowel pin130. The discharge plug120is installed within the first section72of the housing60such that the locating dowel pin130is installed within the dowel opening474formed in the medial portion472and the locating cutout128formed in the first section72of the housing60. Such installation aligns the discharge plug120within the housing60so that the pair of legs464do not block the openings of the upper and lower discharge bores102and104. Continuing withFIGS.40and41, the locating cutout128may be large enough to provide sufficient clearance for installation of the locating dowel pin130within the locating cutout128. The locating cutout128is sized to allow maximum clearance for assembly, but still maintain an acceptable rotational position of the discharge plug120. For example, the cutout128may be a maximum of 15 degrees wide along the circumference of the horizontal bore70. Continuing withFIG.75, an axially-blind bore476extends within the body466and opens on the rear portion470of the body466. The bore476is sized to receive a tubular insert478. The tubular insert478is similar to the tubular insert460installed within the suction valve guide212. The tubular insert478is configured to receive the stem402of the discharge valve138, as shown inFIGS.40and41. Continuing withFIGS.40,41, and75, during operation, the stem402moves axially within the tubular insert478. A plurality of passages480are formed in the body466and interconnect the bore476and an outer surface of the medial portion472. During operation, any fluid or other material trapped within the bore476exits the discharge plug120through the passages480. A spring446is positioned between the medial portion472of the plug120and the outer rim430of the discharge valve138, as shown inFIGS.40and41. The spring446biases the discharge valve138in the closed position, as shown inFIG.40. Fluid pushing against the valve insert432moves the discharge valve138axially to compress the spring446and move the discharge valve138to an open position, as shown inFIG.41. Continuing withFIGS.40,41,72, and75, the front portion468of the body466is sized to be disposed within a counterbore482formed within the front retainer118. When disposed therein, a rear surface484of the front retainer118abuts an outer surface of the medial portion472of the discharge plug120, as shown inFIGS.40and42. Such engagement holds the discharge plug120in place between the front retainer118and the fluid routing plug132. A blind bore486is formed in an outer surface of the front portion468of the plug120. The blind bore486is configured to engage a tool used to help install or remove the plug120from the housing60. For example, the bore486may have threaded walls. Front Retainer With reference toFIGS.40,41,76, and77, the front retainer118comprises opposed front and rear surfaces488and484joined by an outer surface having external threads124and a horizontal bore490formed therein. The horizontal bore490comprises a hex portion492that opens in the counterbore482, as shown inFIGS.40and41. The hex portion492is configured to mate with a tool used to thread the front retainer118into the housing60until it abuts the discharge plug120, as shown inFIGS.40and41. An annular void494is formed within the front surface488of the front retainer118. The annular void494decreases the weight of the front retainer118, making it easier to thread into the housing60. Discharge Conduits and Manifold With reference toFIG.41, each discharge fitting108comprises a support base502and a connection end512. A discharge fitting adapter504is installed within the counterbore106formed in the upper and lower discharge bores102and104. When installed, the seal112engages an outer surface of the fitting adapter504. A groove505is formed with the discharge fitting108for receiving a second seal507. The second seal507likewise engages an outer surface of the fitting adapter504. Continuing withFIG.41, the support base502is sized to abut the outer intermediate surface68of the first section72of the housing60. The support base502comprises a plurality of passages506, shown inFIG.29, configured to align with the threaded openings114formed in the intermediate surface68and surrounding the discharges bores102and104. The threaded fasteners116are installed within the aligned passages506and openings114and tightened to secure the discharge fitting108to the first section72. With reference toFIGS.3and41, the connection end512of the discharge fitting108is configured to mate within one or more discharge conduits500included in an upper or lower discharge manifold514or516, as shown inFIG.3. The upper and lower discharge manifolds514and516are supported on rack518, as shown inFIG.3. The fluid end assembly52is disposed within the interior open area of the rack518. The rack518supports the upper and lower discharge manifolds514and516in a spaced position from the discharge bores102and104. As a result, each discharge conduit500has an angled or bent shape. In operation, fluid discharges from the housing60through upper and lower discharge bores102and104and is carried to the corresponding upper or lower discharge manifolds514or516by the discharge fittings and conduits108and500. Suction Conduits and Manifold With reference toFIGS.41and78, each suction conduit166comprises the first connection member164joined to a second connection member520by threads, as shown inFIG.78. The first and second connection members164and520may be made of a metal or hardened material. Continuing withFIG.78, the first connection member164comprises upper portion524joined to a lower portion526. External threads172are formed on a portion of the lower portion526for mating with the internal threads170formed in the suction bores160or162. The seal176installed within the housing60engages a cylindrical outer surface of the lower portion526below the external threads172. The upper portion524has a larger outer diameter than the lower portion526and is positioned outside of the housing60. The lower portion526abuts the counterbore168of the suction bores160and162of the second section74of the housing60. With reference toFIGS.3and78, the second connection member520is configured to mate with one or more connection members or hoses528formed on an upper or lower suction manifold530or532. The upper and lower suction manifolds530and532are supported on the rack518adjacent the discharge manifolds514and516. The connection members or hoses528may be flexible so that they may bend, as needed, to properly interconnect the suction conduits166and the suction manifolds530and532. In operation, fluid is drawn into the housing60from the suction manifolds530and532via the connection members528, the suction conduits166, and the upper and lower suction bores160and162. Assembly of Fluid End Section and Assembly Turning toFIGS.9,29,79, and80, prior to assembling the housing60, the wear ring136is preferably first pressed into the counterbore134formed in the first section72of the housing60. Likewise, the hardened insert210is pressed into the counterbore208formed in the third section76of the housing60. The seals126,112, and176may also be installed within the first and second sections72and74of the housing60. The wear ring222and seal224may also be installed within the third section76of the housing60prior to assembling the housing60. Following installation of the above described components, the housing60may be assembled as described above. Thereafter, the retention plates206, stuffing box198, rear retainer200, plunger packing300, and packing nut290may be attached to the rear surface66of the housing60. The inner components of the housing60are inserted within the housing60through the front surface64of the first section72. The inner component may be installed prior to attaching the components to the rear surface66of the housing60, if desired. Following assembly of each fluid end section56, each section56is attached to the power end assembly54using the stay rods58. Each fluid end section56and its various components are heavy and cumbersome. Various tools or lifting mechanisms may be used to assemble the fluid end assembly52and attach it to the power end assembly54, creating the high pressure pump50. Operation of Fluid End Assembly Turning back toFIGS.40and41, in operation, retraction of the plunger216out of the housing60pulls fluid from the upper and lower suction bores160and162into the suction passages340within the fluid routing plug132. Fluid flowing through the suction passages340and into the axially-blind bore342pushes on the valve insert432of the suction valve214, causing the valve214to compress the spring446and move to an open position, as shown inFIG.40. When in the open position, fluid flows around the suction valve214and the suction valve guide212and into the open horizontal bore70within the third section76of the housing60. Continuing withFIG.41, extension of the plunger216further into the housing60pushes against fluid within the open horizontal bore70and forces the fluid towards the suction surface332of the fluid routing plug132. Such motion also causes the suction valve214to move to a closed position, sealing the opening of the axially-blind bore342. Because the bore342is sealed, fluid is forced into the discharge passages360. Fluid flowing through the discharge passages360contacts the valve insert432on the discharge valve138, causing the discharge valve138to compress the spring446and move into an open position, as shown inFIG.41. When in the open position, fluid flows around the discharge valve138and into the upper and lower discharge bores102and104. Because fluid exiting the discharge passages360has been compressed by extension of the plunger216into the housing60, such fluid has a higher fluid pressure than that entering the housing60through the suction bores160and162. During operation, the plunger216continually reciprocates within the housing60, pressuring all fluid drawn into the housing60through the suction bores160and162. Pressurized fluid exiting the housing60through the upper and lower discharge bores102and104is delivered to the upper and lower discharge manifolds514and516in communication with each of the fluid end sections56. Pressurized fluid within the discharge manifolds514and516is eventually delivered to the wellhead18, as shown inFIG.2. ALTERNATIVE EMBODIMENTS Turning toFIGS.81-119, alternative embodiments of fluid routing plugs that may be used with the fluid end assembly52are described in more detail. The alternative embodiments of fluid routing plugs are shown installed within alternative embodiments of fluid end sections inFIGS.81-119. Such fluid end section embodiments are described in more detail in U.S. patent application Ser. No. 17/884,712, authored by Thomas, et al., and filed on Aug. 10, 2022, the entire contents of which are incorporated herein by reference. To the extent any features of the alternative fluid end section embodiments are the same or nearly the same as features of the fluid end section56, for ease of reference, such features will be given the same reference numbers as those described above. Likewise, to the extent any features of the fluid routing plug132and the various fluid routing plug embodiments are the same or nearly the same, such features will be given the same references numbers herein, for ease of reference. With reference toFIGS.81-100, another embodiment of a fluid routing plug600is shown. The fluid routing plug600is installed within another embodiment of a housing602. The housing602comprises an integral first and second section604joined to the third section76, as shown inFIG.81. The fluid routing plug600comprises a body606having a suction surface608and an opposed discharge surface610joined by an outer intermediate surface612, as shown inFIGS.84-87. The suction and discharge surfaces608and610are generally identical to the suction and discharge surfaces332and334of the fluid routing plug132. Continuing withFIGS.81-100, a central longitudinal axis613extends through the body606and the suction and discharge surfaces608and610, as shown inFIG.87. When the fluid routing plug600is installed within the housing602, most of the plug600is installed within the integral section604, but at least a portion of the suction surface608is positioned within the third section76of the housing602, as shown inFIG.81. Continuing withFIGS.84-100, the body606further comprises a plurality of suction fluid passages614. The suction passages614interconnect the intermediate surface612and the suction surface608of the body606, as shown inFIG.87. The connection is formed within an axially-blind bore616formed within the suction surface608of the body606. The suction passages614are generally identical to the suction passages340formed in the fluid routing plug132, but the passages614are oriented differently within the body606. Continuing withFIGS.88and89, an opening618of each suction passage614on the intermediate surface612comprises a first side wall620joined to a second side wall622by first and second ends624and626. The first and second side walls620and622are straight lines of equal length S, and the first and second ends624and626are circular arcs, as shown inFIG.89. Continuing withFIG.89, the first end624of the opening618has a radius of R1with a center at C1, and the second end626has a radius of R2with a center at C2. The first end624is larger than the second end626such that R1>R2. The first and second side walls620and622are tangent to the first and second ends624and626and have an included angle, σ. The opening618is oriented such that the center C1of the first end624is a perpendicular distance D from the central longitudinal axis613. Continuing withFIG.89, the opening618has a centerline628that connects the centers C1and C2of the first and second ends624and626. The centerline628has a length E and forms an angle x with the central longitudinal axis613, further orienting the opening618. A cross-sectional shape of each suction passage614throughout the length of the body606corresponds with the shape of each opening618, as shown inFIGS.84and87. Each suction passage614is sized and shaped to maximize fluid flow through the passage614and minimize fluid turbulence and stress to the body606of the fluid routing plug600. With reference toFIGS.91and97, each suction fluid passage614extends between the axially-blind bore616and the intermediate surface612such that each suction passage614comprises a first longitudinal axis630and a second longitudinal axis632. The first longitudinal axis630extends through the center C1of the first end624of the opening618, as shown inFIG.89. Like the center C1, the first longitudinal axis630is offset a perpendicular distance D from the central longitudinal axis613. The first longitudinal axis630does not intersect, is not parallel to, and is not co-planar with the central longitudinal axis613. The second longitudinal axis632extends through point P, shown onFIG.91. The second longitudinal axis632may intersect and be co-planar with the central longitudinal axis613, as shown inFIGS.91and97. The configuration of the suction passages614encourages a vortex type fluid flow about the central longitudinal axis613of the body606, thereby reducing fluid turbulence and erosion during operation. Continuing withFIGS.85-87, the body606further comprises a plurality of discharge fluid passages634. The discharge passages634interconnect the suction surface608and the discharge surface610of the body606and do not intersect any of the suction passages614. The discharge passages634are generally identical to the discharge passages360formed in the fluid routing plug132, but the passages634are oriented differently within the body606. With reference toFIGS.85,86,90,92, and93, each discharge passage634opens at a first opening636on an outer rim638of the suction surface608, as shown inFIGS.92and93, and opens at a second opening640on a central base642of the discharge surface610, as shown inFIGS.85and86. A position of the first and second openings636and640of each discharge passage634may be determined relative to a plane containing a line644that is perpendicular to the central longitudinal axis613, as shown inFIG.90. The first opening636, when projected onto the plane, is positioned at a first distance F1from the central longitudinal axis613and at a first angle φ1relative to the line644. The second opening640, when projected onto the plane, is positioned at a second distance F2from the central longitudinal axis613and at a second angle φ2relative to the line644. The first and second distances F1and F2shown in FIG.90 are different. Likewise, the first and second angles φ1and φ2shown in FIG.90 are different. In alternative embodiments, the first and second angles φ1and φ2may be different. In further alternative embodiments, the first and second angles φ1and φ2may be the same, but the first and second distances F1and F2may be different. In even further alternative embodiments, the first and second distances F1and F2may be the same, and the first and second angles φ1and φ2may be the same. With reference toFIGS.94-100, each discharge passage634has an arced cross-sectional shape. The length of the arc may gradually increase between the suction and discharge surfaces608and610, as shown inFIGS.94-96. At least a portion of each discharge passage634intersects a plane containing the central longitudinal axis613of the body606, as shown inFIG.97. Continuing withFIGS.97-100, the configuration of the discharge passages634encourages a vortex type flow of fluid about the central longitudinal axis613of the body606, thereby reducing fluid turbulence during operation. The shape of each discharge passage634thus maximizes fluid flow and minimizes stress to the body606of the fluid routing plug600during operation. Turning to backFIG.87, the intermediate surface612comprises a first sealing surface650positioned adjacent the discharge surface610and a second sealing surface652positioned adjacent the suction surface608. The first and second sealing surfaces650and652each extend around the entire intermediate surface612in an endless manner and surround the longitudinal axis613of the body606. Turning back toFIG.81, the first sealing surface650engages a first seal654installed within a groove656formed in the integral section604of the housing602. The second sealing surface652engages a second seal660installed within the counterbore208formed in the third section76of the housing602. The second seal660is surrounded by a wear ring662. Engagement of the first and second sealing surfaces650and652with the first and second seals654and660prevents fluid from leaking around the fluid routing plug600during operation. Because the first and second seals654and660are installed within the housing602, no grooves are formed in the fluid routing plug600for housing a seal. Continuing withFIG.87, the intermediate surface612of the fluid routing plug600further comprises a first bevel664and a second bevel666. The first bevel664is positioned between the first sealing surface650and the suction passages614, and the second bevel666is positioned between the suction passages614and the second sealing surface652. The bevels664and666are configured to engage the first and second beveled surfaces668and670formed in the walls of the integral section604of the housing602, as shown inFIGS.82and83. Axial movement of the fluid routing plug600towards the stuffing box198is prevented by engagement of the first and second bevels664and666with the first and second beveled surfaces668and670, as shown inFIG.81. Continuing withFIG.82, when the fluid routing plug600is installed within the housing602, the first bevel664seats against the first beveled surface668. The bevel664and the beveled surface668meet at a non-right angle. Such angle reduces stress in the fluid routing plug600and the housing602during operation. The bevel664and the beveled surface668remain engaged during the forward and backwards stroke of the plunger216. Turning toFIG.83, in contrast to the first bevel664, the second bevel666is sized to be spaced from the second beveled surface670when the fluid routing plug600is initially installed within the housing602, as shown by a gap672. The gap672provides space for the fluid routing plug600to expand during operation. As the plunger216retracts backwards away from the housing602, a significant amount of load is applied to the first bevel664. The applied load causes the fluid routing plug600and the integral section604to deform, allowing the second bevel666to eventually engage the second beveled surface670. Upon engaging the second beveled surface670, the load being applied to the first bevel664is shared with the second bevel666, thereby decreasing the load applied to the first bevel664. Without the gap672, the fluid routing plug600may not have enough room to deform, potentially causing damage to the fluid routing plug600and the housing602over time. As the plunger216extends forward into the housing602, the second bevel666will return to its deformed state, re-creating the gap672. The gap672will repeatedly be created and closed during operation as the plunger216reciprocates. In addition to providing space for the fluid routing plug600to deform, the gap672also provides a gas and fluid relief area during the forward stroke of the plunger216. Continuing withFIG.82, the intermediate surface612of the fluid routing plug600further comprises a transition bevel674. The transition bevel674extends between the first sealing surface650and the first bevel664, as shown inFIG.87. The transition bevel674does not engage the first beveled surface668. The transition bevel674helps reduce friction between the fluid routing plug600and the housing602during installation. Turning toFIG.101, another embodiment of a housing682having the fluid routing plug600installed therein is shown. The housing682is identical to the housing602, but the integral section604has been split into a first section684joined to a second section686by a plurality of fasteners (not shown). Splitting the integral section604into two sections allows a wear ring688to be installed within a counterbore690formed in the first section684. The first seal654is also installed within the counterbore690. The wear ring668surrounds the first seal654and provides a barrier between the walls of the housing682and the first seal654, during operation. The wear ring688and the first seal654are held within the counterbore690by joining the second section686to the first section684of the housing682. During operation, if either the first seal654or the wear ring688beings to wear and erode, the first seal654and/or the wear ring688can be removed and replaced with a new first seal654and/or wear ring688. Using the wear ring688helps prevent wear or damage to the housing682during operation. Turning toFIGS.102and103, another embodiment of a fluid routing plug700is shown. The fluid routing plug700is shown installed within the housing682. The fluid routing plug700is identical to the fluid routing plug600, but it comprises another embodiment of an intermediate surface702. Instead of a first sealing surface650, the intermediate surface702comprises a first groove704for housing the first seal654. Thus, the first seal654is installed within the fluid routing plug700instead of the counterbore690. The counterbore690only houses the wear ring688. Thus, the counterbore690may vary in size depending on components to be installed therein. The first seal654engages the wear ring688installed within the counterbore690. During operation, if either the first seal654or the wear ring688beings to wear and erode, the first seal654and/or the wear ring688can be removed and replaced with a new first seal654and/or wear ring688. Turning toFIGS.104and105, another embodiment of a fluid routing plug750is shown installed within the housing602. The fluid routing plug750is identical to the fluid routing plug600, but it comprises another embodiment of an intermediate surface752. Instead of a second sealing surface652, the intermediate surface752comprises a second groove754for housing the second seal660. Thus, the second seal660is installed within the fluid routing plug750instead of the counterbore208of the third section76. Only the wear ring662is installed within the counterbore208. The second seal660engages the wear ring662. During operation, if either the second seal660or the wear ring662begins to wear and erode, the second seal660and/or the wear ring662can be removed and replaced with a new second seal660and/or wear ring662. In alternative embodiments, a fluid routing plug may have both the first and second seals654and660installed within grooves formed in the fluid routing plug. Turning toFIGS.106-112, another embodiment of a fluid routing plug800is shown. The fluid routing plug Boo is identical to the fluid routing plug600, but it comprises another embodiment of an intermediate surface802. The fluid routing plug800is shown installed within another embodiment of a housing804. The housing804is identical to the housing60, but it includes another embodiment of a second section806. An outer intermediate surface of the second section806is shaped like the second section686, shown inFIG.100, but the interior walls of the second section806are modified, as described below. Continuing withFIGS.107-112, instead of the first bevel664, the intermediate surface802of the fluid routing plug800comprises a cylindrical section808joined to a transition section810by a landing bevel812, as shown inFIG.112. The cylindrical section808and the landing bevel812are configured to engage a landing bevel counterbore814formed in the second section806of the housing804, as shown inFIG.111. Continuing withFIG.111, the landing bevel812is configured to only contact the landing bevel counterbore814at a single point or very small engagement length. The cross-sectional profile of the landing bevel812is thus characterized as a splined curve. In operation, the varying fluid pressures in and around the fluid routing plug800cause the plug800to stretch or deform as the plunger216reciprocates. The landing bevel812and landing bevel counterbore814are sized so that the surfaces more fully engage as the fluid routing plug800stretches or deforms during operation. Such engagement supports the housing804and fluid routing plug Boo when in their highest state of loading, thereby reducing stress and increasing the life span of such components. Continuing withFIGS.106-110, the intermediate surface802further comprises the first groove704for housing the first seal654, as shown inFIG.111, and comprises the second sealing surface652. However, the fluid routing plug800does not comprise the second bevel666. The intermediate surface802merely tapers outwardly from the transition section810to the second sealing surface652. The intermediate surface802between the suction passages314and the second sealing surface652is sized to closely face the walls of the second section806of the housing804. Axial movement of the fluid routing plug800within the housing804is prevented by engagement of the landing bevel812and the landing bevel counterbore814, as shown inFIG.111. Turning toFIGS.113-119, another embodiment of a fluid routing plug900is shown. The fluid routing plug900is identical to the fluid routing plug800, but it comprises another embodiment of an intermediate surface902. The intermediate surface902is like the intermediate surface802, with a few modifications. The fluid routing plug900is shown installed within another embodiment of a housing904. The housing904is identical to the housing60, but it comprises another embodiment of a second section906. Continuing withFIGS.114-119, the intermediate surface902comprises a cylindrical section908joined to a transition section910by a landing bevel912. In contrast to the landing bevel812, the landing bevel912joins the cylindrical section908at a sharper angle. However, at least a portion of the landing bevel912is still a splined curve. A relief914is also formed in the walls of the housing904adjacent a landing bevel counterbore916. The relief914allows the landing bevel counterbore916to be formed in the walls of the housing904at a sharper angle. The shape of the landing bevel counterbore916is a straight bevel. The modified configuration of the landing bevel912and the landing bevel counterbore916allows the surfaces to more fully engage during operation. Specifically, more surface area of the landing bevel912engages more surface area of the landing bevel counterbore916as the fluid routing plug900stretches and deforms during operation. Distributing the load during operation over a larger surface area reduces the stresses within the housing904and the fluid routing plug900. Continuing withFIGS.114-119, a first groove918for housing a first seal920is formed within the cylindrical section908. In contrast to the first groove704, the first groove918extends a greater length of the cylindrical section908and houses a larger first seal920. By increasing the size of the seal920installed within the fluid routing plug900, the area of the intermediate surface902contacted by high pressure fluid is reduced, thereby reducing the total stress applied to the fluid routing plug900during operation. Continuing withFIGS.114-119, the transition section910of the intermediate surface902has a smaller outer diameter than that of the fluid routing plug800. The smaller diameter increases the size of the annular fluid channel412formed between the fluid routing plug900and the walls of the housing904surrounding the suction bores160and162, as shown inFIG.113. The walls of the housing904surrounding the suction bores160and162may include one or more bevels922to further increase the size of the annular fluid channel412. The increase in size of the annular fluid channel412helps optimize fluid flow within the housing094. Continuing withFIGS.117and119, to account for the smaller diameter of the transition section910, the intermediate surface902further comprises a step924positioned between the suction passages614and the second sealing surface652, as shown inFIG.117. The step924increases the outer diameter of the intermediate surface902so that the second sealing surface652engages the second seal660, as shown inFIG.113. The fluid routing plugs and corresponding fluid end sections described herein have various embodiments of fluid passages, intermediate surfaces, and corresponding housing sections. While not specifically shown in a figure herein, various features from one fluid routing plug or fluid end section embodiment may be included in another fluid end section embodiment. In alternative embodiments, features of one of the various fluid routing plugs and corresponding housings described in the '529 application, previously incorporated herein by reference, may be included in one or more of the various fluid routing plugs and/or housings described herein. One of skill in the art will appreciate that the various housing and components described herein may have different shapes and sizes, depending on the shape and size of the various components chosen to assemble each fluid end section. One or more kits may be useful in assembling a fluid end assembly out of the various fluid end sections described herein. A single kit may comprise a plurality of one of the various embodiments of housings and fasteners described herein. The kit may further comprise a plurality of one or more of the various inner components described herein. The kit may even further comprise a plurality of one or more of the various components attached to the various housings described herein. The various features and alternative details of construction of the apparatuses described herein for the practice of the present technology will readily occur to the skilled artisan in view of the foregoing discussion, and it is to be understood that even though numerous characteristics and advantages of various embodiments of the present technology have been set forth in the foregoing description, together with details of the structure and function of various embodiments of the technology, this detailed description is illustrative only, and changes may be made in detail, especially in matters of structure and arrangements of parts within the principles of the present technology to the full extent indicated by the broad general meaning of the terms in which the appended claims are expressed. | 84,352 |
11859602 | DETAILED DESCRIPTION OF CERTAIN ILLUSTRATIVE EMBODIMENTS Hereinafter, exemplary embodiments of the present invention will be described in detail so that those of ordinary skill in the art to which the present invention pertains can easily carry it out with reference to accompanying drawings. However, the present invention may be embodied in many different forms, and is not limited to these embodiments described herein. In the drawings, the thickness of layers, regions, etc., are exaggerated for clarity. Like reference numerals designate like elements throughout the specification. When a part of a layer, film, coating, etc. is referred to as being “on” another constituent element, it includes not only the case of “on top of” another constituent element but also the case where another constituent element is disposed therebetween. Throughout the specification, when a part “comprises” certain constituent elements, it means that the part may include other constituent elements, without excluding other constituent elements, unless otherwise specifically indicated, and “combination” means mixing, polymerization, or copolymerization. Hereinafter, the electroosmotic pump according to an exemplary embodiment of the present invention will be explained referring toFIG.1toFIG.4. FIG.1is a schematic diagram illustrating an electroosmotic pump according to an exemplary embodiment of the present invention. Referring toFIG.1, the electroosmotic pump100includes a membrane11; a first electrode13which is provided on one surface of the membrane11, including a porous support including an insulator and an electrochemical reaction material formed on the porous support; and a second electrode15which is provided on the other surface of the membrane11, including a porous support including an insulator and an electrochemical reaction material formed on the porous support. The first electrode13and the second electrode15are connected to a power supply part17. The first electrode13and the second electrode15may be connected to the power supply part17by, for example, a lead wire, but the connecting means is not limited thereto as long as they can be electrically connected. The membrane11is installed in fluid pathway parts19and19′ through which fluid is moved, and it may have a porous structure to enable the movement of a fluid and ions therethrough. The membrane11may be a frit-type membrane manufactured by sintering spherical silica with heat, but the membrane is not limited thereto, and any material such as a porous silica or porous alumina that can cause an electrokinetic phenomenon by a zeta potential may be used. The spherical silica used in the formation of the membrane may have a diameter of about 20 nm to about 500 nm, specifically about 30 nm to about 300 nm, and more specifically about 40 nm to about 200 nm. When the diameter of the spherical silica is within the above range, the electroosmotic pump may be able to generate a greater pressure. The membrane11may have a thickness of about 20 μm to about 10 mm, specifically about 300 μm to about 5 mm, and more specifically about 1000 μm to about 4 mm. When the thickness of the membrane11is within the above range, the membrane can exhibit sufficient strength to withstand a mechanical impact being applied during the manufacture, use, or storage of the electroosmotic pump, and it can also exhibit a sufficient flow amount to be used as a pump for drug delivery. The first electrode13and the second electrode15respectively include a porous support including an insulator and an electrochemical reaction material formed on the porous support. In particular, the porous support including an insulator which are included in the first electrode13and the second electrode15respectively may be the same as or different from each other, and the electrochemical reaction material which are included in the first electrode13and the second electrode15respectively may be the same as or different from each other. The first electrode13and the second electrode15may facilitate effective movement of the fluid and ions by having a porous structure. The insulator forming the porous support may include at least one selected from the group consisting of a ceramic not showing conductivity, a polymer resin not showing conductivity, glass not showing conductivity, and a combination thereof, but the insulator is not limited thereto. As such, when a porous support including an insulator is used in the first electrode13and the second electrode15, the electrochemical reaction material used in the first electrode13and the second electrode15is consumed or detached after a long-time operation of the electroosmotic pump, and thus, even when the porous support is exposed, the side reaction (e.g., water electrolysis) that had conventionally occurred due to the exposure of carbon paper or carbon woven-fiber when the carbon paper or carbon woven-fiber were used does not occur, and thereby unnecessary current consumption and power consumption can be prevented. By doing so, an electroosmotic pump which has a stable operation characteristic, excellent lifespan stability, excellent electrical efficiency, and that can reduce manufacturing cost can be implemented. The ceramic not showing conductivity may include at least one selected from the group consisting of rockwool, gypsum, ceramics, cement, and a combination thereof, and specifically at least one selected from the group consisting of rockwool, gypsum, and a combination thereof, but the ceramic not showing conductivity is not limited thereto. Meanwhile, the ceramic not showing conductivity may be, for example, a sintered material of a ceramic powder or natural porous ceramic, but the ceramic not showing conductivity is not limited thereto. The polymer resin not showing conductivity may include at least one selected from the group consisting of: a synthetic fiber, which is selected from the group consisting of polypropylene, polyethylene terephthalate, polyacrylonitrile, and a combination thereof; a natural fiber, which is selected from the group consisting of wool, cotton, and a combination thereof; a sponge; a porous material derived from a biological organism (e.g., bones of a biological organism); and a combination thereof, but the polymer resin not showing conductivity is not limited thereto. The glass not showing conductivity may include at least one selected from the group consisting of glass wool, glass frit, porous glass, and a combination thereof, but the glass not showing conductivity is not limited thereto. The porous support may conventionally have a form of a non-woven fabric, woven fabric, sponge, or a combination thereof, but the form of the porous support is not limited thereto as long as the support has porosity thus enabling transport of a fluid and ions. The porous support may have a pore size of about 0.1 μm to about 500 μm, specifically about 5 μm to about 300 μm, and more specifically of about 10 μm to about 200 μm. When the pore size of the porous support is within the above range, a fluid and ions can effectively move, and thus the stability, lifespan characteristic, and efficiency of the electroosmotic pump can be effectively improved. The porous support may have porosity of about 5% to about 95%, specifically about 50% to about 90%, and more specifically about 60% to about %. When the porosity of the porous support is within the above range, a fluid and ions can effectively move, and thus the stability, lifespan characteristic, and efficiency of the electroosmotic pump can be effectively improved. As the electrochemical reaction material, any material that can form a pair of reactions where an anode and a cathode can give and take positive ions (e.g., hydrogen ions (W)) and simultaneously constitute a reversible electrochemical reaction during the electrode reactions, such as silver/silver oxide and silver/silver chloride, can be used. Specifically, the electrochemical reaction material may include at least one selected from the group consisting silver/silver oxide, silver/silver chloride, MnO(OH), polyaniline, polypyrrole, polythiophene, polythionine, a quinone-based polymer, and a combination thereof. When the electrochemical reaction material as described above is used, oxidation and reduction are possible by a method other than water electrolysis, and thus the stability, lifespan characteristic, and efficiency of the electroosmotic pump can be effectively improved. The electrochemical reaction material may be formed by electrodeposition or coating on a porous support including the insulator using methods such as electroless plating, plating, vacuum deposition, coating, a sol-gel process, etc., but the methods are not limited thereto, and the electrochemical reaction material may be formed on a porous support including the insulator using an appropriate method according to the kinds of the electrochemical reaction material being used. The power supply part17is connected to the first electrode13and the second electrode15to provide power so that an electrochemical reaction can occur in the first electrode13and the second electrode15, and the electrochemical reaction of the first electrode13and the second electrode15can occur by the transport of positive ions. The power supply part17can alternately supply the polarity of a voltage to the first electrode13and the second electrode15, and in particular, what is meant by the power supply part17alternately supplying the polarity of a voltage may include the meaning that the current is alternately supplied in opposite directions. By such a process, the electroosmotic pump100can generate a pressure (pumping power) by the movement of a fluid, and simultaneously, the consumption and regeneration of the electrochemical reaction material of the first electrode13and the second electrode15can repeatedly occur. For example, the power supply part17may include a DC voltage supply part (not shown) that supplies a DC voltage to each of the first electrode13and the second electrode15. Additionally, the power supply part17may include a voltage direction conversion part (not shown) that alternately converts the polarity of the DC voltage supplied to each of the first electrode13and the second electrode15at predetermined times. From the above, it is possible to continuously change the voltage applied to each of the first electrode13and the second electrode15to an opposite polarity at predetermined times. The fluid pathway parts19and19′ provide the movement pathway of a fluid that moves in both directions with the membrane11, the first electrode13and the second electrode15disposed therebetween. In particular, the fluid pathway parts19and19′ may have a container shape where a fluid is filled inside (e.g., a cylindrical shape), but the shape is not limited thereto. The fluid not only can fill in the fluid pathway parts19and19′, but also the membrane11and the first and second electrodes13and15. Each of the fluid pathway parts19and19′ may have openings20and20′ for the transfer of pressure (pumping power) respectively. For example, the openings20and20′ may be formed on any one space or both spaces of the spaces divided into two parts by the membrane11and the first and second electrodes13and15, and thereby provide the pressure (pumping power) by the movement of a fluid to the outside. FIG.2AandFIG.2Bare schematic diagrams illustrating reversible electrode reactions in an electroosmotic pump according to an exemplary embodiment of the present invention, and subsequent movements of ions and a fluid. Referring toFIG.2AandFIG.2B, when a voltage is differently supplied to the first electrode13and the second electrode15, for example, with a difference in the polarity of a voltage through the power supply part17, a voltage difference occurs between the first electrode13and the second electrode15. By such a voltage difference, as a result of an electrode reaction, positive ions (Mx+) are produced in the anode, and as the positive ions (Mx+) move toward the cathode, they move along with a fluid thereby generating a fluid movement amount and a pressure (pumping power). When power is supplied to the first electrode13and the second electrode through the power supply part17, the anode and the cathode can be changed by alternately supplying the polarity of a voltage, and as a result, the movement direction of ions and a fluid, and the direction of the pressure (pumping power) and the fluid amount, can be changed. When the role of the electrode which had served as an anode is changed to serve as a cathode due to the alternating supply of the voltage polarity, the electrochemical reactive material which was consumed when the electrode was used as an anode can be recovered as the electrode is used as a cathode, and vice versa, thereby enabling the continuous operation of the electroosmotic pump. Taking a case where a silver/silver oxide is used as an electrochemical reaction material and an aqueous solution is used as a fluid as an example, a reaction as shown in Reaction Scheme 1 occurs in an anode and a reaction as shown in Reaction Scheme 2 occurs in a cathode. In this case, the positive ions which move are hydrogen ions (H+), and hydrogen ions (H+) have a relatively rapid speed of ion transport and thus the transport speed of the fluid which moves along with the ions can be rapid as well, thus being able to effectively improve the performance of the electroosmotic pump100. Ag(s)+H2O→Ag2O(s)+2H++2e−[Reaction Scheme 1] Ag2O(s)+2H++2e−→Ag(s)+H2O [Reaction Scheme 2] In a case where a material other than the silver/silver oxide is used in the first electrode13and second electrode15as an electrochemical reaction material and a material other than an aqueous solution is used as a fluid, it is natural that the oxidation/reduction reaction scheme may vary accordingly, and the positive ions being produced and transported may vary. FIG.3is an exploded perspective view of an electroosmotic pump according to an exemplary embodiment of the present invention, andFIG.4is a cross-sectional view of the electroosmotic pump illustrated inFIG.3. Referring toFIG.3andFIG.4, the membrane11may be in the form of a disc. In particular, a coating material, a barrier sheet, an adhesive sheet, etc. may be bonded onto the external circumferential surface of the membrane11to prevent fluid leakage. Additionally, the first electrode13and second electrode15may have a disc shape so as to correspond to the shape of the membrane11, and in particular, a coating material, a barrier sheet, an adhesive sheet, etc. may also be bonded onto the external circumferential surface of the first electrode13and the second electrode15to prevent fluid leakage. The first fluid pathway part (19, seeFIG.1) may include a first cap33of the hollow space to be bonded to the first electrode13. Additionally, the second fluid pathway part (19′, seeFIG.1) may include a second cap53of the hollow space to be bonded to the second electrode15. Between the two ends of the first cap33and the second cap53, the end where the first electrode13and the second electrode15are located and the end which is located at the opposite end may be connected to a first tube40and a second tube40′, where a fluid can be transported. The first tube40and second tube40′ may be, for example, silicone tubes, but the tube material is not limited thereto. The electroosmotic pump100may include a first contact strip31which is to be integrated into the external circumferential surface of the first electrode13. Additionally, the electroosmotic pump100may include a second contact strip51which is to be integrated into the external circumferential surface of the second electrode15. The first contact strip31and the second contact strip51may each be connected to the power supply part17, and thereby deliver a voltage or current to the first electrode13and the second electrode15, respectively. The first contact strip31and the second contact strip51may include a conductive material. Specifically, first contact strip31and the second contact strip51may include silver (Ag), copper (Cu), etc., but the elements are not limited thereto. The first contact strip31and the second contact strip51, as shown inFIG.3, may be in a circular form where the first electrode13and the second electrode each external circumferential surface are integrated thereinto, but the form is not limited thereto. In another exemplary embodiment, the present invention provides a fluid pumping system including the electroosmotic pump. The fluid pumping system may be formed in a structure that is generally used in the art, and thus specific details are omitted herein. MODE FOR CARRYING OUT THE INVENTION Hereinafter, the present invention will be described in more detail with reference to examples and comparative examples. However, these examples and comparative examples are for illustrative purposes only and are not intended to limit the scope of the present invention. EXAMPLES Example 1: Preparation of Polyethylene Terephthalate (PET) Non-Woven Fabric Electrode Coated with Silver (Ag) 10 g of polyethylene terephthalate non-woven fabric (Huvis, LMF degree) with a thickness of 0.2 mm was washed with an aqueous NaOH solution (1.6 g NaOH/100 mL water) at room temperature for 30 minutes, washed several times with distilled water, conditioned with an aqueous solution of polyethylene glycol (PEG 1000, 0.08 g polyethylene glycol/100 mL water), and washed again with distilled water. While repeating stirring and washing, the resultant was subjected to a sensitization process using SnCl2(0.8 g SnCl2/100 mL water) for 5 minutes and then to an activation process using PdCl2(0.04 g PdCl2/100 mL water) for 30 minutes. Then, the resultant was subjected to an acceleration process using a 10% aqueous HCl solution at room temperature for 30 minutes and then washed with distilled water. The polyethylene terephthalate non-woven fabric, which underwent pretreatment processes, was put in a silver solution composed of silver nitrate, sodium hydroxide, and ammonia, and a reducing solution where sodium hypophosphite were dissolved, and subjected to electroless plating for 1 hour in total. The polyethylene terephthalate non-woven fabric coated with silver was anodized under a potential difference of 2 V at both ends using a silver plate as a counter electrode so as to produce Ag2O particles on the surface, and the same was used as a porous electrode for the electroosmotic pump. FIG.5is an electron microscope image of an electrode manufactured according to Example 1. By observing the morphology of the silver and silver oxidecoated on the polyethylene terephthalate non-woven fabric fromFIG.5, it can be confirmed that the silver/silver oxide is very uniformly distributed while maintaining overall porosity. Example 2: Preparation of Electroosmotic Pump An electroosmotic pump having the same shape as those ofFIG.3andFIG.4was prepared. The membrane was prepared by loading spherical silica (diameter 300 nm) in a mold to be formed into a coin shape with an exterior diameter of 8 mm and a thickness of 1 mm by applying a load of 1 ton and sintering at 700° C. The electrodes prepared in Example 1 were processed into a circular shape having an exterior diameter of 8 mm and stacked up on both sides of the membrane, and subsequently, a contact strip and a cap were installed, and the exterior was sealed using an epoxy resin. Comparative Example 1: Preparation of Carbon Paper Electrode Coated with Silver (Ag) Carbon paper with a thickness of 0.28 mm (Toray, Japan, THP-H-090) was subjected to plasma treatment in a low pressure plasma device for 1 hour. The plasma-treated carbon paper was installed in an electroplating tank and coated with silver at a current density of 30 mA/cm2for 10 minutes. The silver-coated carbon paper was transferred into a different electroplating tank and anodized at a current of 15 mA/cm2such that an electrode where an Ag2O layer was coated on the surface was prepared. The electrode was prepared as a circular electrode with an exterior diameter of 8 mm. Comparative Example 2: Preparation of Electroosmotic Pump An electroosmotic pump was prepared in the same manner as in Example 2, except that the electrodes prepared in Comparative Example 1 were used instead of the electrodes prepared in Example 1. Test Example 1: Evaluation of Performance of Electroosmotic Pump A potential difference of 2 V was applied to each of the two electrodes of the electroosmotic pumps prepared in Example 2 and Comparative Example 2 at alternate intervals of 1 minute for 10 minutes, and the resulting current response characteristics were evaluated. Additionally, a potential difference of 2 V was applied to each of the two electrodes of the electroosmotic pumps prepared in Example 2 and Comparative Example 2 at alternate intervals of 1 minute for 14 hours, and the resulting current response characteristics were evaluated. The current characteristic curve of the electroosmotic pump prepared in Example 2 for a period of 14 hours is shown inFIG.6, the current characteristic curve of the electroosmotic pump prepared in Comparative Example 2 for a period of 10 minutes is shown inFIG.7, and the current characteristic curve of the electroosmotic pump prepared in Comparative Example 2 for a period of 14 hours is shown inFIG.8, respectively. According to what is shown inFIG.6, it was confirmed that, in the electroosmotic pump prepared in Example 2, a constant current flow was maintained even after a long-time operation. Meanwhile, according to what is shown inFIGS.7and8, in the electroosmotic pump prepared in Comparative Example 2, the current flow therein was maintained for about 10 minutes, but the current rapidly increased as the operation time increased thereby increasing the power consumption. From the above results, it was confirmed that, in the electroosmotic pump prepared in Comparative Example 2, as the operation time became longer, the carbon paper was exposed due to the consumption or detachment of the silver/silver oxide (i.e., the electrochemical reaction material), and the exposed carbon paper caused a side reaction (e.g., electrolysis of water) thereby rapidly increasing the power consumption of the electroosmotic pump. As a result, it was confirmed that the electroosmotic pump prepared in Example 2 was superior with respect to stability, lifespan characteristic, and efficiency, compared to that of the electroosmotic pump prepared in Comparative Example 2. Although the preferred embodiments of the present invention have been described above, the present invention is not limited thereto, and it will be apparent to those skilled in the art that various changes and modifications may be made within the scope of the claims, the detailed description of the invention, and the accompanying drawings. As described above, the electroosmotic pump according to the present invention includes electrodes containing a porous support including an insulator and an electrochemical reaction material formed on the porous support, and as a result, even after a long-time operation, neither a side reaction due to the consumption or detachment of the electrochemical reaction material nor a subsequent increase in current consumption or power consumption occurs, thereby enabling the improvement of stability, lifespan characteristics, and efficiency. | 23,533 |
11859603 | DETAILED DESCRIPTION The present disclosure provides a 3D-printed oil separation assembly100for use in a reciprocating compressor. As used herein, the term “3D-printed” refers to a structure, component or assembly at least a portion of which is 3D-printed, or a related process using a structure, component or assembly having at least a portion which has been 3D-printed. With reference to the Figures, reciprocating compressors generally include a partition member10which separates the suction chamber20and the crankcase chamber30. The partition member10includes at least one opening12through which oil and refrigerant may flow. To reduce or hinder the flow of oil from the crankcase chamber30to the suction chamber20through the opening12, an oil separation assembly100in accordance with the present disclosure is positioned relative to the opening12so as to create a serpentine or discontinuous flow path between the suction chamber20and the crankcase chamber30. In an embodiment, a reciprocating compressor may be a high pressure reciprocating compressor. As shown in the embodiments described herein, a 3D-printed oil separation assembly100comprises a coalescing structure which is a baffled structure, a demisting structure, or combination thereof, and at least one securing structure to hold the coalescing structure in position. At least a portion of either the coalescing structure, at least one securing structure, or both, is 3D-printed. In an embodiment, at least a portion of the coalescing structure of a 3D-printed oil separation assembly100is 3D-printed. A “baffled structure,” as used herein, is a structure having at least two, or, preferably, a plurality of obstructions (e.g., baffles) which deflects or obstructs flow of gases or liquids. Nonlimiting examples of suitable baffled structures include a structure having serpentine channels, a structure containing a series of baffles, and like structures. A “demisting structure,” as used herein, is a material, unit, assembly or combination thereof used to enhance the removal of liquid droplets of oil from the gaseous refrigerant stream. Nonlimiting examples of suitable demisting structures include materials such as mesh-type coalescers, including wire mesh-type coalescers (e.g., steel wool), mesh-type materials made of natural or synthetic fibers, other similar mesh-like materials, steel or stainless mesh. Coalescing structures (e.g., baffled structures and/or demisting structures) may be 3D-printed. In an embodiment, at least a portion of the coalescing structure is 3D-printed. In a further embodiment, the coalescing structure is substantially or wholly 3D-printed. In still a further embodiment, the coalescing structure is wholly 3D-printed. In the embodiment shown inFIGS.1A-1B, the 3D-printed oil separation assembly100comprises a coalescing structure which is a baffled structure40and, in the embodiment shown inFIG.1B, optionally, a demisting structure40′. In the embodiments shown inFIG.2, the 3D-printed oil separation assembly100comprises a coalescing structure which is one more demisting structures40′. In other embodiments, the 3D-printed oil separation assembly100may have a coalescing structure comprising both a baffled structure40and a demisting structure40′, or further still, in some embodiments, a baffled structure40may be formed of, or may itself form, a demisting structure40′. Similarly, the number of coalescing structures, and particular arrangement of coalescing structures, can vary depending on the particular configuration and/or operating parameters of the reciprocating compressor and the desired oil separating result. Turning now to the Figures, a 3D-printed oil separation assembly100generally includes at least one coalescing structure positioned adjacent to the opening12on one or both sides of the opening12and at least one securing structure44which secures the at least one coalescing structure in position. With particular reference toFIG.1A, shown is an exemplary 3D-printed oil separation assembly100in accordance with embodiments of the present disclosure. In the embodiment shown, the 3D-printed oil separation assembly100includes a single coalescing structure which comprises a baffled structure40. The baffled structure40is positioned on the crankcase side of the opening12. Specifically, in the embodiment shown, the coalescing structure is a single baffled structure40comprising a shell or outer wall41and at least two, or, in the embodiment shown, a plurality of baffles42in an alternating sloping arrangement. That is, a first baffle42ahas a first slope and a first free end and a first secured end and a second baffle42bhaving a second free end and a second secured end, such that the first and second free ends and first and second secured ends are oppositely disposed, and the first free end is closer to the second secured end than the first secured end to the second free end. In the embodiment shown, the baffles42are connected to the outer wall41at an angle from 5°, or 10°, or 15° to 20°, or 25°, or 30° in order to provide the sloping orientation. As shown perhaps more clearly inFIG.1B, the baffles42are sloped such that any flow from the crankcase chamber30to the suction chamber20will be uphill. While this configuration serves to create additional resistance for flow from the crankcase chamber30to the suction chamber20(relative to baffles being sloped in the opposite direction, that is, such that flow from the crankcase chamber30to the suction chamber20is “downhill”), it will be understood that different configurations and arrangements of baffles can be used, such as, for example, contoured baffles, straight baffles, “downhill” baffles, and combinations thereof. In an embodiment, the distance between the free end of a given baffle and the outer wall41is at least 1.5× the diameter of the opening12. In an embodiment, the distance between the free end of a baffle42and the secured end of a subsequent baffle42(d) is greater than or equal to a cross-sectional area of the opening12at a given location, e.g., at the partition10or at a location near the baffles at issue. In some embodiments, the distance d is from greater than or equal to a cross-sectional area of the opening12, or 1.5× a cross-sectional area of the opening12, or 2× a cross-sectional area of the opening12, or 2.5× a cross-sectional area of the opening12to 3× a cross-sectional area of the opening12, or 3.5× a cross-sectional area of the opening12, or 4× a cross-sectional area of the opening12, or 4.5× a cross-sectional area of the opening12, or 5× a cross-sectional area of the opening12. In the embodiment shown, the coalescing structure, or in the present embodiment, baffled structure40, has a total thickness (T). In an embodiment, the coalescing structure has a T from 0.5 in, or 1 in to 1.5 in, or 2 in. In further embodiments, the total thickness T may be specifically selected or designed based on the size of the opening12and/or the capacity, performance or other metric of the compressor, the design or material of the at least one coalescing structure, the efficiency, performance, or other metric of the oil separation assembly100, and/or combinations thereof. As shown inFIG.1A, the coalescing structure, and, more particularly, the baffled structure40is positioned such that at least a portion of the coalescing structure is contained within the opening12. That is, in the embodiment shown inFIG.1A, a portion of the coalescing structure, and particularly the shell or outer wall41of the baffled structure40is in contact with the walls of the opening12. However, in further embodiments, such as shown inFIG.1B, the coalescing structure, and, particularly, the baffled structure40, may be completely contained within the crankcase chamber30or, in other embodiments, within the suction chamber20. As shown inFIG.1B, a demisting structure40′ may optionally be used in combination with a baffled structure40to form a coalescing structure. In the embodiment shown inFIG.1B, the demisting structure40′ is shown as positioned on the suction chamber-side of the opening12, with the baffled structure40positioned on the crankcase chamber-side of the opening12. In further embodiments, a demisting structure40′ may be provided on the crankcase chamber-side of the opening12or both sides of the opening12. In still further embodiments, a baffled structure40may be at least partially filled with a demisting structure40′ and/or itself at least partially made using a demisting structure40′. In the embodiments shown inFIGS.1A-1B, the baffled structure40is at least partially 3D-printed, or preferably substantially 3D-printed. In a further embodiment, the baffled structure40is wholly 3D-printed. In further embodiments, and with respect toFIG.1B, at least a portion of the demisting structure40′ may be 3D-printed. In an embodiment, at least a portion of the demisting structure40′ may be 3D-printed in addition to at least a portion of the baffled structure40being 3D-printed. In a further embodiment, at least a portion of the baffled structure40is 3D-printed and the demisting structure40′ is a mesh-type coalescer, such as steel wool. The 3D-printed oil separation assembly100further includes at least one securing structure44which secures the coalescing structure in position relative to the opening12. In the particular embodiment shown inFIG.1B, the at least one securing structure44secures both the baffled structure40and demisting structure40′ in position relative to the opening12, with the demisting structure40′ secured on the suction chamber-side of the opening12and the baffled structure40secured on the crankcase chamber-side of the opening12. The at least one securing structure44may be a single component or an assembly which is secured in operable relation with the coalescing structure so as to secure the coalescing structure relative to the opening12. As shown inFIG.1B, the at least one securing structure44is a securing assembly comprising a first support44a, a second support44band a locking structure44c. More particularly, in the embodiment shown, the at least one securing structure44includes a first support44awhich is a plate, a second support44bwhich is also a plate, and a locking structure44cwhich is a locking stud. As illustrated specifically inFIG.1B, the first support44ais on the suction chamber-side of the opening12and adjacent with the partition member10. While in the embodiment shown, the first support44ais in contact with the demisting structure40′, in other embodiments, particularly if no portion of a coalescing structure is on the suction chamber-side of the opening12, the first support44amay contact the partition10directly. In further embodiments, one or more structures may be positioned between the first support44aand the coalescing structure or partition member10so that the first support44ais in indirect contact with the coalescing structure or partition member10. For example, one or more structures which provide additional strength to the partition10or one or more structures which cushion or protect the partition10may be provided. Similarly, the second support44bis on the crankcase chamber-side of the baffled structure40and adjacent the outer surface of the baffled structure40so as to sandwich the baffled structure40between the partition member10and the second support44b. Again, while in the embodiment shown the second support44bis shown to be in direct contact with the baffled structure40, in further embodiments, one or more additional structures (e.g., strengthening structure, protective structure, cushioning structure) may be provided between the baffled structure40and the second support44bso that the second support44bis in indirect contact with the baffled structure40. Likewise, in embodiments in which no portion of a coalescing structure is on the crankcase chamber-side of the opening12, the second support44bmay directly or indirectly contact the partition10. In being positioned adjacent the baffled structure40′ on the crankcase side, the second support44balso serves as a first barrier to prevent or limit large oil droplets from passing into the coalescing structure and therefore through the opening12. The locking stud44cpasses through the first support44a, the demisting structure40′, the opening12, the baffled structure40and the second support44band, along with washers and lock nuts44d, for example, tightens the first and second supports44a,44btoward one another. The portions of the coalescing structure, i.e., the demisting structure40′ on the suction chamber-side and the baffled structure40on the crankcase chamber-side, are thereby compressed against the partition member10and secured in position relative to the opening12. While in the embodiment shown, and otherwise generally throughout the description of the drawings, the first support44ais discussed and described with respect to the suction chamber-side of the oil separation assembly and the second support44bis discussed and described with respect to the crankcase chamber-side of the oil separation assembly, it will be understood that the first and second supports44a,44bmay be used interchangeably as permitted. FIG.2shows a second embodiment of a 3D-printed oil separation assembly100′ for use in a reciprocating compressor in accordance with embodiments of the present disclosure. In the embodiment shown, the 3D-printed oil separation assembly100′ includes a coalescing structure positioned entirely within the crankcase chamber30with a securing structure44at least partially contained within the opening12. That is, in the embodiment shown inFIG.2, the securing structure44has a portion which is in contact with the walls of the opening12. As withFIGS.1A-1B, the coalescing structure is composed of at least one of a baffled structure or demisting structure. In an embodiment, the coalescing structure is shown as a single demisting structure40′; however, in further embodiments, it will be appreciated that the coalescing structure may be a single baffled structure. In embodiments in which the coalescing structure is a demisting structure40′, at least a portion of the demisting structure40′ is 3D-printed. In further embodiments, particularly those in which the coalescing structure is a demisting structure40′, the demisting structure40′ is wholly 3D-printed. The coalescing structure, or, in the embodiment shown inFIG.2, the demising structure40′, has a total thickness (T′). In an embodiment, the demisting structure40′ has a T′ from 1 in, or 1.5 in, or 2 in to 2.5 in, or 3 in, or 3.5 in, or 4 in. In further embodiments, the total thickness T may be specifically selected or designed based on the size of the opening12and/or the capacity, performance or other metric of the compressor. The 3D-printed oil separation assembly100′ further includes at least one securing structure44′ composed of first support44a′, second support44b′ and locking structure which secures the coalescing structure, or, in the embodiment shown inFIG.2, the demisting structure40′, to the crankcase chamber side of the opening12and adjacent the opening12. More particularly, in the embodiment shown, the first support44a′ is a channel-forming support which extends from the opening12into the crankcase chamber30. The first support44a′ is a tube-like structure which creates a channel into the crankcase chamber30around which the coalescing structure, e.g., demisting structure40′, may be positioned. The first support44a′also serves as a structure with which the locking structure44c′can engage. To facilitate adequate flow through the suction chamber20and crankcase chamber30, and facilitate pressure equalization between the chambers20,30, the embodiment shown inFIG.2the first support44a′also includes cross holes46′ to allow gasses to pass through the opening12and demisting structure42. In the embodiment shown inFIG.2, the second support44b′is a structure which provides a first barrier for larger oil droplets from passing through the opening12, such as, for example, a plate or a cup. The locking structure44c′is a structure which engages the first and second supports44a′,44b′to secure the demisting structure40′ in position relative to the opening12. In an embodiment shown, the locking structure44c′is a screw. In an embodiment, one advantage of the 3D-printed oil separation assembly described herein is that the assembly or components thereof, i.e., the coalescing structure, or one or more components thereof, may be at least partially, or preferably substantially or wholly, manufactured by 3D printing. By utilizing 3D printing technology, coalescing structures, and, in particular, baffled structure or demisting structures, can be custom made to fit a particular opening. In a particular embodiment, a coalescing structure is as shown inFIGS.1A-1Bcomprising at least one baffled structure. Such a baffled structure can be formed to have exact external dimensions which fit the specific compressor cavity, and such forming is more readily completed using 3D printing. Moreover, the discontinuous channels of a demisting structure can be more complex and precise when the demisting structure is made using 3D printing. In an embodiment, one advantage of the 3D-printed oil separation assembly described herein is that the assembly may be installed into existing reciprocating compressors. That is, existing reciprocating compressors may be retrofit with the 3D-printed oil separation assembly of the present disclosure. Existing reciprocating compressors may therefore exhibit the improvements in operation provided by the oil separation assembly. To install the 3D-printed oil separation assembly in a reciprocating compressor, whether a new compressor or an existing compressor, a coalescing structure is provided at an opening of the partition member of the compressor. At least one securing structure is then assembled in operable relation to the coalescing structure to secure the coalescing structure in place relative to the opening. The coalescing structure may be any embodiment or combination of embodiments described herein. In an embodiment, the coalescing structure comprises at least one baffled structure. In a further embodiment, the coalescing structure comprises at least one demisting structure. In a still further embodiment, the coalescing structure comprises a baffled structure and a demisting structure. In an embodiment, the at least one of a baffled structure or demisting structure is provided at an opening at the partition member of the compressor on the crankcase chamber-side of the opening. If the coalescing structure includes a second component (i.e., a further baffled structure or demisting structure), in an embodiment, the second component is provided at the opening of the suction chamber-side of the opening. The at least one securing structure is then assembled in operable relation to the first (and, if utilized, second) components of the coalescing structure to secure the baffled structure(s) and/or demisting structure(s) in place. In an embodiment, the method of installing the 3D-printed oil separation assembly in a reciprocating compressor further includes 3D-printing at least a portion of the at least one of a baffled structure, demisting structure, or combinations thereof. In an embodiment, the coalescing structure (or, at least one of the baffled structure, demisting structure, or combinations thereof) is substantially or wholly 3D-printed. In embodiments, the step of 3D-printing includes at least one of identifying and/or calculating internal dimensions of a reciprocating compressor at the location the oil separation assembly will be installed, designing or identifying a pattern to be printed (e.g., a series of baffles), selecting a suitable material for 3D printing, programming a 3D printer to perform the printing, and printing the at least one baffled structure, demisting structure, or combinations thereof. In an embodiment, the at least one securing structure includes a first support, a second support and a locking structure. In such embodiment, the step of assembling the at least one securing structure in operable relation to the coalescing structure includes positioning a first support in relation to the coalescing structure, positioning a second support in relation to the coalescing structure, and securing the first and second supports in position using a locking structure. In an embodiment, only a crankcase chamber-side coalescing structure (i.e., baffled structure or demisting structure) is provided. In such an embodiment, the step of assembling the at least one securing structure in operable relation to the coalescing structure may include, for example, positioning a first support in relation to the opening at the partition member to extend into the crankcase chamber and into the coalescing structure, positioning a second support in relation to the coalescing structure in the crankcase chamber, and securing the first and second supports together in relation to the demisting structure using a locking structure. In an embodiment in which the coalescing structure is composed of two or more structures (i.e., two or more of a baffled structure, a demisting structure, and combinations thereof) that are used on opposite sides of an opening (i.e., a suction chamber-side structure and a crankcase chamber-side structure are both used), the step of assembling the at least one securing structure in operable relation to the coalescing structure may include, for example, positioning a first support in relation to the suction chamber-side component of the coalescing structure, positioning a second support in relation to the crankcase chamber-side component of the coalescing structure, and securing the first and second supports together in relation to the coalescing structure using a locking structure. The 3D-printed oil separation assembly described herein addresses at least three issues. First, the oil separation assembly limits the amount of oil passing through the vent holes12from the crankcase chamber to the suction chamber when the rotating crankshaft splashes or sprays oil that comes in contact with it. Second, the 3D-printed oil separation assembly helps to maintain a pressure equilibrium between the suction chamber and the crankcase chamber. Third, the 3D-printed oil separation assembly assists in returning oil collected in the suction chamber back to the crankcase chamber. By (1) limiting the amount of oil passing from the crankcase chamber to the suction chamber, the oil separation assembly decreases oil loss and therefore costs associated with operating and maintaining a reciprocating compressor, (2) helping to maintain a pressure equilibrium between the suction chamber and crankcase chamber, and (3) assisting in returning oil collected in the suction chamber back to the crankcase chamber. The disclosed 3D-printed oil separation assembly is also easily installed in existing reciprocating compressors at existing vent holes. Additional advantages of the 3D-printed oil separation assembly will be readily identified and understood by those of skill in the art. One of skill in the art will understand that the specific measurements (e.g., height, width, diameter, etc.) of the oil separation assembly may vary based on compressor design and the dimensions of the 3D-printed oil separation assembly may be altered accordingly to correspond to the measurements of the compressor. The 3D-printed oil separation assemblies contemplated and disclosed within above are now exemplified in the following embodiments: E1. An oil separation assembly for use in a reciprocating compressor, the compressor comprising a suction chamber, a crankcase chamber, and at least one partition member at least partially separating the suction chamber and the crankcase chamber, the at least one partition member including at least one opening, the oil separation assembly comprising: a coalescing structure having at least a portion of which is positioned within the crankcase chamber adjacent the at least one partition member at the at least one opening; and at least one securing structure secured in operable relation with the at least one coalescing structure so as to secure the at least one coalescing structure relative to the opening. E2. The oil separation assembly of E1, wherein the coalescing structure comprises at least one structure selected from the group consisting of a baffled structure, a demisting structure, and combinations thereof. E3. The oil separation assembly of E2, wherein the coalescing structure comprises a baffled structure. E4. The oil separation assembly of E2, wherein the coalescing structure comprises a demisting structure. E5. The oil separation assembly of E2, wherein the coalescing structure comprises a baffled structure and a demisting structure. E6. The oil separation assembly of E5, wherein the baffled structure is positioned with in the crankcase chamber adjacent the at least one partition member at the at least one opening and the demisting structure is positioned within the suction chamber adjacent the at least one partition member at the at least one opening. E7. The oil separation assembly of E2, wherein the coalescing structure comprises a first demisting structure. E8. The oil separation assembly of E7, wherein the coalescing structure comprises a second demisting structure. E9. The oil separation assembly of E7-E8, wherein one of the first and second demisting structures is selected from the group consisting of wire mesh, steel wool, stainless mesh, steel mesh and combinations thereof. E10. The oil separation assembly of E1-E9, wherein the at least one securing structure comprises a first support, a second support and a locking structure. E11. The oil separation assembly of E1-E10, wherein at least a portion of the coalescing structure is 3D-printed. E12. The oil separation assembly of E1-E11, wherein the coalescing structure is substantially or wholly 3D-printed. E13. An oil separation assembly for use in a reciprocating compressor, the compressor comprising a suction chamber, a crankcase chamber, and at least one partition member at least partially separating the suction chamber and the crankcase chamber, the at least one partition member including at least one opening, the oil separation assembly comprising: a coalescing structure, wherein at least a portion of the coalescing structure is positioned within the crankcase chamber adjacent the at least one partition member at the at least one opening; and at least one securing structure secured in operable relation with the coalescing structure so as to secure the at least one coalescing structure relative to the opening, wherein at least a portion of the coalescing structure is 3D printed. E14. The oil separation assembly of E13, wherein the coalescing structure comprises at least one structure selected from the group consisting of a baffled structure, a demisting structure, and combinations thereof. E15. The oil separation assembly of E14, wherein the coalescing structure comprises at least one baffled structure. E16. The oil separation assembly of E15, wherein the at least one baffled structure comprises an outer wall and a plurality of sloped baffles. E17. The oil separation assembly of E16, wherein the plurality of sloped baffles comprises at least a first sloped baffle having a free end and a secured end and a subsequent sloped baffle having a free end and a secured end, wherein the secured ends are secured to the outer wall such that the free ends are oppositely disposed and the free end of the first baffle is closer to the secured end of the subsequent baffle than the secured end of the first baffle to the free end of the subsequent baffle. E18. The oil separation assembly of E17, wherein the first and subsequent sloped baffles are each secured to the outer wall at an angle from 5° to 30°. E19. The oil separation assembly of any of E17-18, wherein the distance between the free end of the first baffle and the secured end of the subsequent baffle is greater than or equal to a cross-sectional area of the opening. E20. The oil separation assembly of any of E15-19, wherein the at least one baffled structure is 3D printed. E21. The oil separation assembly of any of E15-E20, wherein the at least one baffled structure is wholly 3D printed. E22. The oil separation assembly of any of E15-12, wherein the coalescing structure further includes at least one demisting structure. E23. The oil separation assembly of E14, wherein the coalescing structure comprises at least one demisting structure. E24. The oil separation assembly of E23, wherein the coalescing structure further includes a second demisting structure positioned within the suction chamber adjacent the at least one partition member at the at least one opening. E25. The oil separation assembly of any of E13-E24, wherein the at least one securing structure comprises a first support, a second support, and a locking structure. E26. A reciprocating compressor comprising: a suction chamber; a crankcase chamber; a partition member at least partially separating the suction chamber and the crankcase chamber and comprising at least one opening; and at least one oil separation assembly comprising a coalescing structure, wherein at least a portion of the coalescing structure is positioned within the crankcase chamber adjacent the at least one partition member at the at least one opening; and at least one securing structure secured in operable relation with the coalescing structure so as to secure the at least one coalescing structure relative to the opening, wherein at least a portion of the coalescing structure is 3D printed. E27. The reciprocating compressor of E26, wherein the coalescing structure is substantially or wholly 3D-printed. E28. The reciprocating compressor of any of E26-27, wherein the coalescing structure comprises at least one structure selected from the group consisting of a baffled structure, a demisting structure, and combinations thereof. E29. The reciprocating compressor of any of E26-28, wherein the coalescing structure comprises at least one baffled structure. E30. The reciprocating compressor of E29, wherein the at least one baffled structure comprises an outer wall and a plurality of sloped baffles. E31. The reciprocating compressor of E30, wherein the plurality of sloped baffles comprises at least a first sloped baffle having a free end and a secured end and a subsequent sloped baffle having a free end and a secured end, wherein the secured ends are secured to the outer wall such that the free ends are oppositely disposed and the free end of the first baffle is closer to the secured end of the subsequent baffle than the secured end of the first baffle to the free end of the subsequent baffle. E32. A method of retrofitting a reciprocating compressor with an oil separation assembly, the compressor comprising a suction chamber, a crankcase chamber, and at least one partition member at least partially separating the suction chamber and the crankcase chamber, the at least one partition member including at least one opening, the method comprising: identifying the internal dimensions of the compressor at the at least one opening; designing a coalescing structure configuration; programming a 3D printer based on the internal dimensions identified and coalescing structure configuration; 3D printing at least a portion of the coalescing structure; and securing the coalescing structure at the opening on the crankcase chamber-side of the partition member. E33. The method of E32, where 3D printing at least a portion of the coalescing structure includes 3D printing the entirety of the coalescing structure. The terms “comprising,” “including,” “having,” and their derivatives, are not intended to exclude the presence of any additional component, step or procedure, whether or not the same is specifically disclosed. Unless stated to the contrary, implicit from the context, or customary in the art, all parts and percentages are based on weight and all test methods are current as of the filing date of this disclosure. It is specifically intended that the crankcase 3D-printed oil separation assembly and related methods not be limited to the embodiments and illustrations contained herein, but include modified forms of those embodiments including portion so the embodiments and combinations of elements of different embodiments as come with the scope of the following claims. In addition, the order of various steps of operation described herein can be varied. Further, numerical ranges provided herein are understood to be exemplary and shall include all possible numerical ranges situated there between. | 32,880 |
11859604 | DETAILED DESCRIPTION Hereinafter, exemplary embodiments of the present disclosure will be described in detail with reference to accompanying drawings, such that those skilled in the art can more apparently understand the present disclosure. It should be understood that the exemplary embodiments herein are provided only for the illustrative purpose, and various modifications of the embodiments are reproduced. In addition, the shapes and the sizes of elements in accompanying drawings will be exaggerated for more apparent description. FIG.1is a perspective view illustrating an example of a reciprocating compressor, andFIG.2is a cross sectional view taken along line2-2′ ofFIG.1. Referring toFIGS.1and2, a reciprocating compressor1can include a shell10forming an outer appearance of the reciprocating compressor1. An enclosed space can be formed inside the shell10, and various components constituting the reciprocating compressor1can be received in the enclosed space. The shell10can be formed a metallic material. A cavity can be formed in an inner space of the shell10to define the resonance frequency of the refrigerant. In some implementations, a structure of reducing noise caused in a cavity resonance frequency band of the refrigerant can be provided. The shell10includes a lower shell11and an upper shell16provided at an upper side of the lower shell11. In detail, the lower shell11has a substantially hemispherical shape and forms a receiving space to receive various components, for example, a driving device20, a compressing device30, and a suction and discharge device100, together with the upper shell16. The lower shell11can be referred to as a “compressor body” and the upper shell16can be referred to as a “compressor cover.” The lower shell11includes a suction pipe12, a discharge pipe13, a process pipe14, and a power supply. The suction pipe12is used to introduce a refrigerant into the shell10, and is mounted through the lower shell11. The suction pipe12can be mounted separately from the lower shell11or can be integrally formed with the lower shell11. The discharge pipe13is used to discharge the refrigerant, which is compressed in the shell10, and is mounted through the lower shell11. The discharge pipe13can be separately mounted separately from the lower shell11or can be integrally formed with the lower shell11. A discharge hose60(seeFIG.3) is connected with the discharge pipe13. The refrigerant, which is introduced into the suction pipe12and compressed by the compressing device30, can be discharged to the discharge pipe13through the suction and discharge device100and the discharge hose60. The process pipe14, which is a device provided to fill the refrigerant into the shell10after the inner portion of the shell10is sealed, can be mounted through the lower shell11. The driving device20is provided in the inner space of the shell10to provide driving force. The driving device20can include a stator21, a rotor24, and a rotating shaft22. The stator21includes a stator core and a coil coupled to the stator core. When power is applied to the coil, the coil generates electromagnetic force to perform electromagnetic interaction with the stator core and the rotor. Accordingly, the driving device20can generate driving force for a reciprocating motion of the compressing device30. The rotor24has a magnet, and is rotatably provided inside the coil. The rotational force resulting from the rotation of the rotor24acts as driving force for driving the compressing device20. The rotating shaft22can rotate together with the rotor24, and can be mounted through an inner portion of the rotor24in a vertical direction. In addition, the rotating shaft22is connected to a connecting rod34to transmit the rotational force generated by the rotor24to the compressing device30 In detail, the rotating shaft22can include a base shaft22a, a rotational plate22b, and an eccentric shaft22c. The base shaft22ais mounted inside the rotor24in the vertical direction. When the rotor24rotates, the base shaft22acan be rotated together with the rotor24. The rotational plate22bcan be installed on one side of the base shaft22a, and can be rotatably mounted to a cylinder block31to be described later. The eccentric shaft22cprotrudes upward from a position eccentric from the axial center of the base shaft22ato eccentrically rotate when the rotational plate22brotates. A connecting rod34is mounted on the eccentric shaft22c. As the eccentric shaft22ceccentrically rotates, the connecting rod34can linearly reciprocate (a linear reciprocation motion) in a front-rear direction. The compressing device30receives the driving force from the driving device20to compress the refrigerant through linear reciprocation motion. The compressing device30can include a cylinder block31, a connecting rod34, a piston35, and a piston pin37. The cylinder block31is provided above the rotor24. In addition, the cylinder block31has a shaft opening such that the rotating shaft22passes through the shaft opening. A lower portion of the cylinder block31can rotatably support the rotational plate22b. The cylinder33is provided at a front portion of the cylinder block31and arranged to receive the piston35. The piston35reciprocates in the front-rear direction, and a compressing space “C” for compressing the refrigerant is formed inside the cylinder33. The connecting rod34is a device for transmitting the driving force, which is provided from the driving device20, to the piston35, and converts the rotational motion of the rotating shaft22into the linear reciprocation motion. In detail, the connecting rod34linearly reciprocates in the front-rear direction when the rotating shaft22rotates. The piston35is a device for compressing the refrigerant, and is provided in the cylinder33. The piston35is connected with the connecting rod34and linearly reciprocates in the cylinder33, as the connecting rod34moves. The refrigerant introduced from the suction pipe12can be compressed in the cylinder33, as the piston35linearly reciprocates. The piston pin37couples the piston35and the connecting rod34. In detail, the piston pin37can connect the piston35with the connecting rod34by passing through the piston35and the connecting rod34in the vertical direction. The suction and discharge device100is configured to suction the refrigerant to be supplied to the compressing device30and to discharge the compressed refrigerant from the compressing device30. The suction and discharge device100can include a muffler assembly110and a discharge hose60. The muffler assembly110transfers the suctioned refrigerant, which is received from the suction pipe12, into the cylinder33, and transfers the refrigerant, which is compressed in the compressing space “C’ of the cylinder33, to the discharge pipe13. To this end, the muffler assembly110has a suction space “S” for receiving the suctioned refrigerant from the suction pipe12and a discharge space “D” for receiving the refrigerant compressed in the compressing space C of the cylinder33. In detail, the suctioned refrigerant from the suction pipe12can be introduced into the suction space “S” of a suction and discharge tank (or a tank)120through suction mufflers130and140. The refrigerant compressed in the cylinder33passes through discharge mufflers150and160through the discharge space “D” of the suction and discharge tank120, and is discharged of the compressor1through the discharge hose60and the discharge pipe13. For example, the suction mufflers130and140and the discharge mufflers150and160can be cases, containers, or reservoirs that define inner spaces configured to accommodate and guide the refrigerant. The discharge hose60is a device to transfer the compressed refrigerant, which is contained in the discharge space “D,” to the discharge pipe13, and is integrally formed with a second discharge muffler part160of the discharge mufflers150and160. In detail, one portion of the discharge hose60can be coupled to the second discharge muffler part160to communicate with the discharge space “D,” or can be formed integrally with the second discharge muffler part160. An opposite portion of the discharge hose60is coupled to the discharge pipe13through a connector65. The discharge hose60and the connector65can be jointed to each other or can be formed integrally with each other. The connector65has a plurality of grooves, and ring members66aand66bcan be installed in the plurality of grooves, respectively. The ring members66aand66bcan be formed of rubber or synthetic resin material. FIG.3is a perspective view illustrating an example configuration of the muffler assembly,FIG.4is a front exploded perspective view illustrating an example configuration of the muffler assembly, andFIG.5is a perspective view illustrating an example configuration of the muffler assembly. Referring toFIGS.3to5, the muffler assembly110can include a first suction muffler part130and a second suction muffler part140constituting the suction muffler. The first suction muffler part130and the second suction muffler part140can be assembled, and a refrigerant suction space (or a suction fluid passage) can be defined inside the first and second suction mufflers130and140through the assembling between the first suction muffler part130and the second suction muffler part140. When viewed based onFIG.3, the first suction muffler part130can be coupled to an upper side of the second suction muffler part140. For example, the first suction muffler part130can include a hook135, and the second suction muffler part140can include a hook protrusion145coupled to the hook135. Unlike the drawings, the hook protrusion can be provided on the first suction muffler part130, and the hook coupled to the hook protrusion can be provided on the second suction muffler part140. The first suction muffler part130can include a first muffler body131including a suction guide hole136. An end portion of the first muffler body131can be open. A first muffler flange132coupled to the second suction muffler part140can be provided on the first muffler body131. The first muffler flange132can be formed to be stepped from the first muffler body131such that an outer diameter of the first muffler flange132is greater than an outer diameter of the first muffler body131. The first muffler flange132can be coupled to an open end portion of the second discharge muffler part160. For example, the first muffler flange132can be coupled to an outer portion of the second discharge muffler part160. The second suction muffler part140can include a second muffler body141having a suction hole142communicating with the suction pipe12. The combination of the first muffler body131of the first suction muffler part130and the second muffler body141of the second suction muffler part140can be collectively referred to as a “suction muffler body.” The suction hole142can be formed through a portion of an outer circumferential surface of the second muffler body141. In addition, the suction hole142is positioned adjacent to the inside of one point of the lower shell11to which the suction pipe12is coupled. The second suction muffler part140can include an oil drain part148such that oil separated from the refrigerant in the inner space of the suction mufflers130and140is discharged into the inner space of the shell10. The oil drain part148can protrude downward from a bottom surface of the second muffler body141. The second suction muffler part140can further include a skirt149protruding downward from the bottom surface of the second muffler body141to prevent the oil discharged from the oil drain part148from scattering. The skirt149can be provided adjacent to the oil drain part148. The suction and discharge tank120is connected to one side of the first suction muffler part130. For example, the first suction muffler part130and the suction and discharge tank120can be integrally formed. The discharge mufflers150and160can be provided in opposition to each other based on the suction and discharge tank120. In detail, the first discharge muffler part150of the discharge muffler can be spaced apart from one side of the first suction muffler part130. The suction and discharge tank120having the suction space “S” and the discharge space “D” are mounted between the first suction muffler part130and the first discharge muffler part150. The first suction muffler part130, the suction and discharge tank120, and the first discharge muffler part150can be integrally configured. The first suction muffler part130, the suction and discharge tank120, and the first discharge muffler part150can be collectively named a “tank assembly.” The first suction muffler part130, the suction and discharge tank120, and the first discharge muffler part150can be formed of the same material, for example, of a nylon material having higher pressure resistance. The suction and discharge tank120can include a tank body121having a suction and discharge space. For example, the tank body121can have a cylindrical shape. A suction chamber123aand a discharge chamber123bcan be formed inside the tank body121. The suction chamber123acan have the suction space “S,” and the discharge chamber123bcan have the discharge space “D” The suction chamber123aand the discharge chamber123bcan be formed to be recessed in a surface facing the valve assembly. The suction chamber123acan be configured to communicate with the suction guide hole136of the first suction muffler part130. The suction guide hole136can be formed in the connection part between the suction and discharge tank120and the first suction muffler part130. For example, the suction guide hole136can be formed in one side of an outer circumferential surface of the suction and discharge tank120. The discharge chamber123bcan be configured to communicate with the discharge guide hole156of the first discharge muffler part150. The discharge guide hole156can be formed in the connection part between the suction and discharge tank120and the first discharge muffler part150. For example, the discharge guide hole156can be formed in an opposite side of an outer circumferential surface of the suction and discharge tank120. The suction and discharge tank120can include a partition part122to partition the inner space of the suction and discharge tank120into the suction chamber123aand the discharge chamber123b. The valve assembly can be installed at one side of the suction and discharge tank120. The valve assembly can include a suction valve to open and close the suction chamber123aand a discharge valve to open and close the discharge chamber123b. A retainer124can be provided in the discharge chamber133bto limit the opening amount of the discharge valve. The retainer124can protrude from the bottom surface of the discharge chamber133band be disposed adjacent to the discharge guide hole156. The suction and discharge tank120can further include a sealing protrusion125to which a sealing member is coupled. The second discharge muffler part160of the discharge muffler can be assembled with the first discharge muffler part150, and a discharge space (or a discharge fluid passage) for the refrigerant can be defined inside the first and second discharge mufflers150and160through the assembling. When viewed based onFIG.3, the first discharge muffler part150can be coupled to an upper side of the second discharge muffler part160. The first discharge muffler part150can include a first muffler body151including a discharge guide hole156. An end portion of the first muffler body151can be open. A first muffler flange152coupled to the second discharge muffler part160can be provided on the first muffler body151. The first muffler flange152can be formed to be stepped from the first muffler body151such that an outer diameter of the first muffler flange132is greater than an outer diameter of the first muffler body151. The first muffler flange152can be inserted into an open end portion of the second discharge muffler part160. The second discharge muffler part160can include a second muffler body161having a discharge part165coupled to the discharge hose60. The first muffler body151of the first discharge muffler part150and the second muffler body161of the second discharge muffler part160can be collectively named a “discharge muffler body.” A second muffler flange162, which is coupled to the first discharge muffler part150, can be provided on an end portion of the second muffler body161. The second muffler flange162can be formed to be stepped from the second muffler body161such that an outer diameter of the second muffler flange162is greater than an outer diameter of the second muffler body161. The second muffler flange162can be coupled to an outer portion of the first muffler flange152. A discharge guide device or discharge guide300for reducing pressure pulsation of the discharged refrigerant can be provided inside the discharge mufflers150and160. The discharge guide device300can form the discharge fluid passage of the refrigerant, and can be supported by inner surfaces of the discharge mufflers150and160. The discharge guide300can include one or more pipes, tubes, or the like. The discharge hose60can extend from the second discharge muffler part160and be coupled to the discharge pipe13. The discharge hose60can be coupled to the discharge part165 FIG.6is a view illustrating an example of a suction and discharge tank that is integrated with first and third mufflers. Referring toFIG.6, the muffler assembly110can include a tank assembly. For example, the tank assembly can include the suction and discharge tank120, the first suction muffler part130provided at one side of the suction and discharge tank120, and the first discharge muffler part150provided at an opposite side of the suction and discharge tank120. The first suction muffler part130and the first discharge muffler part150can be disposed in opposition to each other based on the suction and discharge tank120. The first suction muffler part130can include a first muffler body131to form a flowing space (that is, the suction fluid passage) for the refrigerant which is suctioned into the muffler assembly110. The suction guide hole136, which is to suction the refrigerant into the suction and discharge tank120, can be formed in the first muffler body131. The suction guide hole136can be formed in a part at which the first suction muffler part130is connected with the suction and discharge tank120. The first suction muffler part130can further include an inner wall133provided inside the first muffler body131. The inner wall133can extend along an inner circumferential surface of the first muffler body131in parallel to the first muffler body131. The inner wall133can be spaced apart from the inner circumferential surface of the first muffler body131. An insertion space134can be provided between the first muffler body131and the inner wall133. An end portion of the second suction muffler part140can be inserted into the insertion space134, such that the first and second suction mufflers130and140can be assembled. The first discharge muffler part150can include a first muffler body151that forms a flowing space (that is, a discharge fluid passage150a) for the refrigerant discharged from the suction and discharge tank120. The discharge guide hole156, which is to discharge the refrigerant from the suction and discharge tank120, can be formed in the first muffler body151. The discharge guide hole156can be formed in a part at which the first discharge muffler part150is connected with the suction and discharge tank120. The first discharge muffler part150can include at least one wall (see reference numerals153,154, and155) provided in the discharge fluid passage150ato divide the discharge fluid passage150ainto a plurality of discharge rooms. In detail, the discharge muffler bodies151and161, the walls153,154and155, and the discharge guide device300can define an inner space of the discharge muffler, which is to be divided into a plurality of discharge rooms. The walls153,154, and155can be provided to protrude from the inner circumferential surface of the first discharge muffler part150. For example, the walls153,154, and155can extend in the vertical direction when viewed based onFIG.11. The at least one wall can include a plurality of walls153,154, and155 The plurality of walls153,154, and155can function as “reinforcing walls” that prevent the discharge mufflers150and160from being damaged by the high pressure applied when the discharged refrigerant flows. The plurality of walls153,154, and155can include a first wall153, a second wall154spaced apart from one side of the first wall153, and a third wall155spaced apart from an opposite side of the first wall153. The second and third walls154and155can be provided on opposite sides of the first wall153. The first to third walls153,154, and155can function as reinforcing walls to prevent the discharge mufflers150and160from being damaged under a higher-pressure environment of the discharge mufflers150and160. The discharge chamber123bof the suction and discharge tank120can form a primary discharge room “DR1” for the refrigerant (seeFIG.11). A space between the first wall153and the first muffler body151can form a secondary discharge room “DR2” for the refrigerant (seeFIG.11). A space between the second wall154and the first muffler body151can form a tertiary discharge room for the refrigerant. In detail, the space formed by the second wall154and the discharge muffler bodies151and161can be defined as the tertiary discharge room “DR3” for the refrigerant (seeFIG.11). A space between the first wall153and the second wall154can form a quaternary discharge room for the refrigerant. In detail, the space formed by the first and second walls153and154, the discharge muffler bodies151and161, and the discharge guide device300can define the quaternary discharge room “DR4” (seeFIG.11) for the refrigerant. The discharge guide device300can be arranged to be positioned in the spaces among the plurality of walls153,154, and155. A main stream of the refrigerant discharged to the first discharge muffler part150through the discharge guide hole156passes through an inner fluid passage of the discharge guide device300and is discharged to the outside through the discharge part165of the second discharge muffler part160. In some implementations, a sub-stream of the refrigerant discharged to the first discharge muffler part150through the discharge guide hole156can be diffused into the secondary discharge room to the quaternary discharge room. The discharge pulsation of the refrigerant can be reduced by the main stream and the sub-stream of the refrigerant. A second suction muffler part140can be assembled to the first suction muffler part130. The second suction muffler part140can include a second muffler body141that forms a suction space for the refrigerant. An assembly end portion147inserted into the insertion space134of the first suction muffler part130can be formed in the second muffler body141. The assembly end portion147can be formed at an upper end portion of the second muffler body141. In some implementations, the end portion of the first suction muffler part130is placed on protrusion parts215aand215bof a suction guide device200. Accordingly, when the first and second suction mufflers130and140are assembled, the first suction muffler parts130can press the upper end portion of the protrusion parts215aand215b. Accordingly, the suction guide device200can be stably supported by inner parts of the first and second suction mufflers130and140 The suction guide device200can include a partition wall210to partition the inner space of the suction mufflers130and140into two spaces, and a guide pipe220forming a resonance hole225while extending in a direction of crossing the partition wall210. The suction fluid passage for the refrigerant can be formed inside the guide pipe220. Hereinafter, the configuration and the mounting structure of the discharge guide device will be described with reference to accompanying drawings. FIG.7is a perspective view illustrating an example of a second discharge muffler part coupled to a discharge guide device, andFIG.8is an exploded perspective view illustrating the second discharge muffler part and the discharge guide device.FIG.9is a perspective view illustrating an example configuration of the discharge guide device, andFIG.10is a perspective view illustrating an example configuration of the discharge guide device.FIG.11is a cross sectional view taken along line11-11′ ofFIG.3. Referring toFIGS.7to11, the second discharge muffler part160can be assembled to the first discharge muffler part150. The first discharge muffler part150and the second discharge muffler part160can be coupled to each other through laser fusion. Accordingly, the coupling status of the discharge mufflers150and160forming the high-pressure environment can be firmly maintained. The second discharge muffler part160can include a second muffler body161and a second muffler flange162that form a discharge fluid passage160afor the refrigerant. The second muffler flange162can be coupled to an outer portion of the first muffler flange152. The second discharge muffler part160can further include an inner wall163provided inside the second muffler body161. The inner wall163can extend along an inner circumferential surface of the second muffler body161in parallel to the second muffler body161. The inner wall163can be spaced apart from the inner circumferential surface of the second muffler body161. An insertion space164can be provided between the second muffler body161and the inner wall163. An end portion of the first discharge muffler part150is inserted into the insertion space164, such that the first and second discharge mufflers150and160can be assembled. A portion of the discharge guide device300can be supported by the upper end portion of the inner wall163. The second discharge muffler part160can further include an inner wall163provided to be stepped at an inside of the second muffler body161. Another portion of the discharge guide device300can be supported by the upper end portion of the wall protrusion part167. The upper end portion of the wall protrusion part167can be formed at a lower position than that of the upper end portion of the inner wall163. The inner wall163and the wall protrusion part167can be understood as components including a “first jaw” and a “second jaw,” respectively, in that the inner wall163and the wall protrusion part167support the discharge guide device300. The discharge guide device300can be supported by the second discharge muffler part160. The discharge guide device300can be seated on a bottom surface of the second discharge muffler part160. The discharge guide device300can include a pipe310in which a fluid passage312(seeFIG.11; the inner fluid passage) for the refrigerant discharged to the discharge mufflers150and160is formed. The pipe310can have a bending shape to guide the refrigerant, which is positioned at the upper side of the discharge mufflers150and160, to the discharge part165positioned at the lower side of the discharge mufflers150and160. The pipe310can include a first pipe part311extending toward the discharge part165from the discharge guide hole156of the discharge mufflers150and160. For example, the first pipe part311can extend in the vertical direction when viewed based onFIG.7. The first pipe part311can include a pipe inflow hole311ato introduce the refrigerant, which is introduced into the discharge mufflers150and160through the discharge guide hole156, into the pipe310. The pipe inflow hole311acan be formed in an end portion of the first pipe part311, and can be disposed toward the discharge guide hole156. The pipe inflow hole311acan be formed at a position closest to the discharge guide hole156of components of the discharge guide device300. The pipe310can include a second pipe part315bent from the first pipe part311to extend toward the discharge part165. For example, the second pipe part315can extend in the horizontal direction when viewed based onFIG.7. The second pipe part315can include a pipe outflow hole315ato discharge the refrigerant from the pipe310. The pipe outflow hole315acan be formed in an end portion of the second pipe part315, and can be disposed toward the discharge part165. The pipe outflow hole315acan be formed at a position closest to the discharge part165of components of the discharge guide device300. The refrigerant can be introduced into the first pipe part311through the pipe inflow hole311a, can flow through the second pipe part315, and can be discharged from the second pipe part315through the pipe outflow hole315a. The discharge guide device300can further include a fixing bracket330to support the pipe310with respect to the discharge mufflers150and160. For example, the fixing bracket330can be provided at an outer portion the second pipe part315. In other words, the fixing bracket330can surround a portion of the outer circumferential surface of the second pipe part315. The discharge guide device300can further include a first pipe connection part340to connect the first pipe part311to the fixing bracket330. The first pipe part311, the fixing bracket330, and the first pipe connection part340can be integrally formed with each other. The first pipe connection part340can be interposed between the first pipe part311and the fixing bracket330. The supporting status of the first pipe part311with respect to the discharge mufflers150and160can be firmly maintained through the first pipe connection part340. The discharge guide device300can further include a second pipe connection part350to connect the second pipe part315to the fixing bracket330. The second pipe part315, the fixing bracket330, and the second pipe connection part350can be integrally formed with each other. The second pipe connection part350can be provided on a side surface of the second pipe part315. In other words, the second pipe connection part350can be provided on an outer circumferential surface of the second pipe part315. The supporting status of the second pipe part315with respect to the discharge mufflers150and160can be firmly maintained through the second pipe connection part350. The fixing bracket330can include a bracket body331having an insertion groove338into which the walls153,154, and155are inserted. The first and second pipe connection parts340and350can be provided at opposite sides of the bracket body331. The insertion groove338can be formed to be recessed downward from the top surface of the fixing bracket330. For example, the first wall153can be inserted into the insertion groove338. As the first wall153is inserted into the insertion groove338, the inner space of the discharge mufflers150and160can be partitioned by the first wall153and the discharge guide device300. For example, the first wall153and the discharge guide device300can act to separate the secondary discharge room “DR2” and the quaternary discharge room “DR4” from each other. The second wall154can be disposed adjacent to an upper portion of the second pipe part315or disposed in contact with the second pipe part315 The second pipe part315and the second wall154do not completely separate the tertiary discharge room “DR3” from the quaternary discharge room “DR4,” and the tertiary discharge room “DR3” and the quaternary discharge room “DR4” can communicate with each other through the surrounding space of the second pipe part315. The bracket body331can be supported by the second discharge muffler part160. In detail, the bracket body331can include stepwise sections333and335supported by the second discharge muffler part160. The stepwise sections333and335can include a first stepwise section333supported by the inner wall163of the second discharge muffler part160. The first stepwise section333can be stepped in a direction, in which the width of the bracket body331is reduced, from the outer surface of the bracket body331. The stepwise sections333and335can include a second stepwise section335supported by the wall protrusion part167of the second discharge muffler part160. The second stepwise section335can be stepped in a direction, in which the width of the bracket body331is reduced, from the outer surface of the first stepwise section333. Accordingly, the width of the second stepwise section335can be narrower than the width of the first stepwise section333. The first stepwise section333can be positioned above the second stepwise section335, corresponding to that the inner wall163is positioned above the wall protrusion part167. Hereinafter, the procedure of assembling the discharge guide device300with the discharge mufflers150and160will be described in brief. The first wall153is inserted into the insertion groove338of the discharge guide device300, thereby assembling the discharge guide device300with the first discharge muffler part150. Then, the second discharge muffler part160is assembled with the first discharge muffler part150such that the discharge guide device300is seated on the second discharge muffler part160. The first and second discharge mufflers150and160are firmly coupled to each other by laser fusion. FIG.12is a view illustrating an example of a refrigerant flow in the discharge muffler. Hereinafter, a refrigerant discharging action in the discharging mufflers150and160will be described in brief with reference toFIGS.11and12together. When the reciprocating compressor1starts to drive, the refrigerant is introduced into the shell10through the suction pipe12, and introduced into the suction mufflers130and140through the suction hole142. The refrigerant can be introduced into the second suction muffler part140, and can flow through the guide pipe220. In this case, a portion of the refrigerant is diffused into the inner space of the suction mufflers130and140through the resonance hole225, and noise of the suctioned refrigerant can be reduced. The refrigerant suctioned into the suction mufflers130and140is compressed in the cylinder33via the suction chamber123aof the suction and discharge tank120, and the compressed higher-pressure gas refrigerant can be discharged to the discharge mufflers150and160through the discharge chamber123bof the suction and discharge tank120and the discharge guide hole156. The discharge chamber123bcan have the primary discharge room “DR1” for the refrigerant. The main stream (marked with a solid arrow) of the refrigerant introduced into the discharge mufflers150and160can be introduced into the pipe310through the pipe inflow hole311a. The refrigerant can be discharged through the pipe outflow hole315avia the first pipe part311and the second pipe part315. The pressure pulsation can be reduced in the procedure in which the refrigerant flows through the first and second pipe parts311and315. The refrigerant can be discharged through the discharge part165of the discharge mufflers150and160, and can flow through the discharge hose60. The secondary discharge room “DR2” can be formed inside the discharge mufflers150and160. The secondary discharge chamber “DR2” can be defined as an external space of the discharge guide device300, of spaces formed by the first wall153and the discharge muffler bodies151and161. The secondary discharge chamber “DR2” can be separated from the quaternary discharge room “DR4” by the first wall153and the discharge guide device300 A sub-stream (marked with a dotted arrow) of the discharge refrigerant other than the main stream can be diffused into the secondary discharge room “DR2.” The tertiary discharge room “DR3” can be formed inside the discharge mufflers150and160. The tertiary discharge room “DR3” can include a space defined by the second wall154and the discharge muffler bodies151and161. The sub-stream of the refrigerant other than the main stream, which is discharged through the pipe outflow hole315aof the pipe310, can be spread into the tertiary discharge room “DR3.” The quaternary discharge room “DR4” can be formed inside the discharge mufflers150and160. The quaternary discharge room “DR4” can include a space defined by the first and second walls153and154, the discharge muffler bodies151and161, and the discharge guide device300. The quaternary discharge room “DR4” can communicate with the tertiary discharge room “DR3.” The communicating space can be a surrounding space (a front-rear space when viewed from the drawing) of the second pipe part315. The sub-stream of the refrigerant other than the main stream, which is discharged through the pipe outflow hole315aof the pipe310, can be spread into the quaternary discharge room “DR4” through the tertiary discharge room “DR3.” As described above, the refrigerant introduced into the discharge mufflers150and160has the main stream into the pipe310and sub-streams into the secondary discharge room “DR2” to the quaternary discharge room “DR4.” In this procedure, the pressure pulsation can be reduced. FIG.13is a graph illustrating an example of an experimental result showing an effect of reducing a pulsation with the discharge muffler having the discharge guide device. Specifically,FIG.13illustrates the comparison between a related art and the present disclosure in terms of the intensity of sound pressure generated in a frequency range having a specific band. The frequency range having the specific band shows 2,000 Hz or less. The related art relates to a technology of using a discharge muffler without a discharge guide device, and the present disclosure relates to a technology in which the discharge guide device300described above is provided inside the discharge mufflers150and160. The intensity of the sound pressure generated from the discharge muffler according to the present disclosure can be lower than the intensity of the sound pressure generated from the discharge muffler according to the related art, throughout the whole frequency range. According to the experimental result, as the discharge guide device is provided in the discharge muffler according to the preset disclosure, the pressure pulsation of the discharged refrigerant can be reduced. | 38,222 |
11859605 | MODE FOR CARRYING OUT THE INVENTION Hereinafter, specific embodiments of a compressor system of the present invention will be described based on the drawings. First Embodiment FIG.1is a system diagram of a compressor system in the present embodiment. In the present embodiment, an example will be described in which the present invention is applied to a water-cooled oil-free screw compressor as a compressor unit. In addition, an oil-free screw compressor illustrated inFIG.1is configured as a water-cooled gas compressor that suctions, compresses, and discharges gas (air in the present embodiment). InFIG.1, a compressor unit1includes a single-stage compressor100that suctions air through an air pathway401, compresses the air to a predetermined pressure, and discharges the compressed air, and a water-cooled aftercooler202that cools discharged high-temperature compressed air. A discharge air temperature sensor501that measures the temperature of the discharged high-temperature compressed air is installed on the air pathway401downstream of the compressor100. In addition, a water-cooled oil cooler203is provided that cools a lubricant which lubricates the compressor100and a drive mechanism not illustrated, and the lubricant is supplied to each part, namely, a necessary place inside the compressor unit1through a lubricant pathway408and is circulated. The compressor100and the oil cooler203are usually cooled by cooling water flowing through a first cooling liquid pathway402and an oil cooler cooling pathway branching from the first cooling liquid pathway402. The cooling water in the first cooling liquid pathway402is circulated by a cooling pump103, and releases heat in a cooling heat exchanger204represented by a cooling tower or the like. In the first cooling liquid pathway402, a supply water valve303is disposed on a discharge side of the cooling pump103, and a supply water valve304is disposed on a pathway on a suction side of the cooling pump103, the pathway allowing the cooling water to return to the cooling heat exchanger204. Generally, the cooling pump103and the cooling heat exchanger204are shared with existing equipment separate from the compressor unit1in the present embodiment and a heat recovery unit2to be described later. For this reason, unless requested as requirement specifications by a user, the compressor unit1or the heat recovery unit2does not directly control the operation of a circulation pump104or the cooling heat exchanger204. In the compressor system of the present embodiment, the heat recovery unit2is installed side by side with the compressor unit1. The heat recovery unit2includes a heat recovery heat exchanger205and the circulation pump104, and a suction side of the circulation pump104is connected to a high-temperature fluid side outlet side of the heat recovery heat exchanger205. In addition, a discharge side of the circulation pump104is connected to a cooling water inlet side of the aftercooler202in the compressor unit1, and a cooling water outlet side of the aftercooler202is connected to a high-temperature fluid side inlet side of the heat recovery heat exchanger205, so that a second cooling liquid pathway403is formed. A supply water valve306is disposed on the discharge side of the circulation pump104in the second cooling liquid pathway403. The supply water valve306operates in connection with the circulation pump104, and is opened during operation of the circulation pump104. A low-temperature side fluid pathway407of the heat recovery heat exchanger205is a pathway through which a liquid such as relatively low-temperature water is supplied from the outside, and is a pathway through which the liquid exchanges heat with high-temperature circulating water, which has increased in temperature after having cooled high-temperature compressed air in the aftercooler202, in the second cooling liquid pathway403to be heated and returns to the outside again. The water circulating in the low-temperature side fluid pathway407is not particularly limited in use, and can be widely used for, for example, the preheating of boiler supply water, hot water heating, showering, and the like. In addition, a first bypass pathway405is formed that branches from a downstream side of a cooling water outlet of the compressor100on the first cooling liquid pathway402, and that is connected to a portion downstream of a cooling water outlet of the aftercooler202on the second cooling liquid pathway403. In addition, a second bypass pathway406is formed that branches from an upstream side of a cooling water inlet of the aftercooler202on the second cooling liquid pathway403, and that is connected to a portion downstream of and close to the supply water valve303on the first cooling liquid pathway402. In addition, the first cooling liquid pathway402and the second cooling liquid pathway403communicate with the first bypass pathway405and the second bypass pathway406, respectively. An electromagnetic valve301is provided on the first bypass pathway405, and an electromagnetic valve302is provided on the second bypass pathway406. FIG.2is a simple wiring and pipe connection diagram of the compressor system in the present embodiment. InFIG.2, a control device505is provided in the compressor unit1. The control device505performs the operation and stop of an electric motor not illustrated that drives mainly the compressor100, discharge air pressure control by rotation speed control or switching between a load operation and an unload operation, and the like. A control device507is provided in the heat recovery unit2. The control device507is mainly responsible for the operation, stop, rotation speed control, and the like of the circulation pump104, and controls the opening and closing of the electromagnetic valves301and302and the supply water valves303,304, and306on the respective water pathways of the parts via control wirings506and508. FIG.3is a flowchart of control performed by the control device507of the heat recovery unit2in the present embodiment. InFIG.3, when a power supply is turned on, control is started in step S101. In step S102, a heat recovery mode A is defined in which the electromagnetic valve301and the electromagnetic valve302are closed and the supply water valves303and304are opened, and at this time, a flag inside the control device507is initialized to OFF. Next, in step S103, a signal, which indicates that the compressor unit1has started operation, from the control device505in the compressor unit1is detected, and a signal indicating that the circulation pump104in the heat recovery unit2is detected. Then, in step S104, after a time variable t counted by a timer510inside the control device507is reset, the counting is started again. Next, in step S105, it is determined whether or not a load operation signal from the compressor unit1is detected. If detected, the process proceeds to step S106, and if not detected, the process branches to step S109. In a case where the load operation signal is detected, in step S106, when a discharge air temperature Td1detected by the discharge air temperature sensor501is smaller than a predetermined temperature threshold value Tdx, the process proceeds to step S107, and when the discharge air temperature Td1is the predetermined temperature threshold value Tdx or more, the process branches to step S110. Here, it is desirable that the temperature threshold value Tdx is set to a temperature slightly lower than Tda representing a discharge air alarm temperature (for example, 395° C. or the like with respect to Tda=400° C.) In step S107, it is determined whether or not the time variable t counted by the timer510is larger than a predetermined set time tc, and if larger, the process proceeds to step S108, and if smaller, the process branches to step S111. Here, the set time tc is the time set to limit the frequency of switching between the heat recovery modes A and B, and is set to, for example, three minutes or the like. Since the set time tc is set, the frequency of opening and closing of the electromagnetic valves or the supply water valves can be suppressed, and the component life can be suppressed from becoming extremely short. In step S108, the heat recovery mode B is started which defines a state where the electromagnetic valve301and the electromagnetic valve302are opened and the supply water valves303and304are closed, and the flag at this time is set to ON. After the execution of step S108, the process returns to step S105. In step S109, if the time variable t is larger than the predetermined set time tc, the process proceeds to step S108, and if smaller, the process returns to step S105. In step S110, the time variable t is reset once, and the counting is restarted from 0 again. In step S111, the flag is set to OFF, namely, the heat recovery mode A is executed. When the heat recovery mode A is executed, as for the flow of the cooling water, the first cooling liquid pathway402and the second cooling liquid pathway403are independent of each other. The cooling of the compressor100and the oil cooler203are performed in the cooling heat exchanger204, which is disposed outside, via the first cooling liquid pathway402. The cooling of the aftercooler202can be performed in the second cooling liquid pathway only by the water circulated by the circulation pump104, heat exchange between the water of the second cooling liquid pathway which is a high-temperature side fluid and the water of the low-temperature side fluid pathway407can be performed in the heat recovery heat exchanger205, and the heat extracted from the high-temperature compressed air can be supplied to the outside as hot water. Next, an effect of executing the heat recovery mode A will be described below. For example, ambient temperature increases due to the influence of the installation environment of the compressor unit1, and accordingly, the temperature of the compressed air to be discharged increases, and reaches the discharge air alarm temperature Tda in some cases, which is a problem. In that case, in order to prevent a failure caused by the overheating of the compressor100, generally, while safely cooling the compressor100and the oil cooler203with the cooling heat exchanger204having a cooling capacity sufficiently larger than the heat quantity released by the compressor unit1, heat can be recovered from the cooling water in the second cooling liquid pathway, which has flowed through the aftercooler202and increased in temperature, to a low-temperature side fluid in the low-temperature side fluid pathway407via the heat recovery heat exchanger205. Next, an effect of executing the heat recovery mode B will be described below. For example, in an operation state where the amount of air to be used at a demand destination is small and the load factor of the compressor100is low, and accordingly, the rotation speed of the compressor100is lowered to reduce the amount of discharged air or the operation mode is switched to the unload operation to generate almost no amount of discharged air, the heat quantity that can be recovered from the compressed air is greatly reduced. In that case, since the compressor100requires cooling regardless of the load operation or the unload operation, the heat recovery mode B is executed, so that a first cooling liquid circuit and a second cooling liquid circuit communicate with the first bypass pathway405and the second bypass pathway406, respectively. In addition, meanwhile, the cooling heat exchanger204is functionally disconnected to close the supply water valves303and304, so that the cooling water can be circulated inside the compressor unit1and the heat recovery unit2only by the circulation pump104, and the compressor100, the aftercooler202, and the oil cooler203each are cooled, and heat can be recovered from all the cooling water, which has increased in temperature, to the low-temperature side fluid pathway407via the heat recovery heat exchanger205. Therefore, even in a state where the load factor of the compressor100is low, a reduction in recovered heat quantity is suppressed, and energy is saved. In addition, even in an operation state where the load factor during load operation is close to 100%, when a condition is satisfied in which the discharge air temperature Td1is less than the temperature threshold value Tdx, and a condition is satisfied in which the time variable t is larger than the set time tc, the heat recovery mode B is executed. Therefore, there is no influence such as the overheating of the compressor100on reliability, a large heat quantity can be recovered, and the effect of large energy saving can be obtained. As described above, according to the present embodiment, it is possible to provide the compressor system and a control method for the same which, in the water-cooled gas compressor in which the compressor, compressed gas, or the lubricant is cooled by water, while effectively cooling the compressor, the compressed gas, and the lubricant such that the temperature of the compressed gas can be maintained less than the alarm temperature as far as possible at which the compressed gas becomes hotter than usual, can continue heat recovery from these high-temperature heat sources. Second Embodiment FIG.4is a system diagram of a compressor system in the present embodiment. InFIG.4, parts denoted by the same reference signs as those inFIGS.1to3of the first embodiment indicate the same or corresponding parts, and a description of the parts will be omitted. In the present embodiment, a bypass pathway410communicating with an inlet and an outlet of the heat recovery heat exchanger205is provided on the second cooling liquid pathway403, and a temperature regulation valve308is provided on the bypass pathway410. The temperature regulation valve308has a function of automatically regulating the valve opening degree such that a low-temperature side fluid outlet temperature Tu of a temperature sensor504which measures the temperature of an outlet side of the heat recovery heat exchanger205on the low-temperature side fluid pathway407is a predetermined target temperature Tux. The purpose of providing the temperature regulation valve308is to obtain an effect of enabling the low-temperature side fluid outlet temperature Tu to reach the target temperature Tux more quickly. In the present embodiment, it is assumed that the temperature regulation valve308is a two-way automatic valve which is completely closed when as the low-temperature side fluid outlet temperature Tu measured by the temperature sensor504approaches the target temperature Tux, the volume of a liquid with which the inside of the temperature regulation valve308is filled expands to apply force to an opening and closing mechanism inside a valve body, the valve opening degree is gradually reduced, and the target temperature Tux is reached. When the low-temperature side fluid outlet temperature Tu is still sufficiently lower than the target temperature Tux, the temperature regulation valve308is at the maximum opening degree. In this case, the cooling water of a corresponding flow rate according to a ratio between the diameter of a pipe forming the bypass pathway410and the diameter of a pipe forming the second cooling liquid pathway403returns to the suction side of the circulation pump104without flowing through the heat recovery heat exchanger205, and is discharged again. Then, since a part of the cooling water does not flow through the heat recovery heat exchanger205, the hot water that has not been subjected to heat exchange receives heat from the high-temperature compressed air in the aftercooler202again. Since this circulation is continued, the temperature in the second cooling liquid circuit increases more quickly, and accordingly, the low-temperature side fluid outlet temperature Tu also increases more quickly. Since the opening degree of the temperature regulation valve308is reduced as the low-temperature side fluid outlet temperature Tu approaches the target temperature Tux, the amount of the cooling water flowing through the heat recovery heat exchanger205increases. Therefore, the temperature of the cooling water in the second cooling liquid circuit increases gently, and accordingly, the low-temperature side fluid outlet temperature Tu also increases gently. Therefore, an effect of enabling the low-temperature side fluid outlet temperature Tu to reach the target temperature Tux more quickly is obtained by providing the temperature regulation valve308. Third Embodiment FIG.5is a system diagram of a compressor system in the present embodiment. InFIG.5, parts denoted by the same reference signs as those inFIGS.1to4indicate the same or corresponding parts, and a description of the parts will be omitted. In the present embodiment, the compressor unit1includes a multi-stage oil-free screw compressor in which air is compressed to a predetermined pressure by a plurality of stages of compressors. As illustrated inFIG.5, the compressor system includes a low-pressure stage compressor101; a high-pressure stage compressor102; an intercooler201that cools compressed air discharged from the low-pressure stage compressor101; and the aftercooler202that cools compressed air discharged from the high-pressure stage compressor102. In addition, on the air pathway401, the low-pressure stage discharge air temperature sensor501is provided that measures the temperature of the discharged air from the low-pressure stage compressor101, a high-pressure stage suction air temperature sensor502is provided that measures the temperature of the air which has been cooled in the intercooler201but has not yet been suctioned into the high-pressure stage compressor102, and a high-pressure stage discharge air temperature sensor503is provided that measures the temperature of the discharged air from the high-pressure stage compressor102. Similar to the first embodiment or the second embodiment, also in the present embodiment, the first cooling liquid pathway402and the second cooling liquid pathway403are provided. In addition, the first bypass pathway405is formed that branches from a downstream side of a cooling water outlet of the high-pressure stage compressor102on the first cooling liquid pathway402, and that is connected to a place downstream of the cooling water outlet of the aftercooler202on the second cooling liquid pathway403. In addition, the second bypass pathway406is formed that branches from an upstream side of a cooling water inlet of the intercooler201on the second cooling liquid pathway403, and that is connected to a portion downstream of and close to the supply water valve303on the first cooling liquid pathway402. Then, the first cooling liquid pathway402and the second cooling liquid pathway403communicate with the first bypass pathway405and the second bypass pathway406, respectively. The electromagnetic valve301is provided on the first bypass pathway405, and the electromagnetic valve302is provided on the second bypass pathway406. In the case of the heat recovery mode A, namely, in a case where the electromagnetic valve301and the electromagnetic valve302are closed and the supply water valve303and the supply water valve304are opened, the cooling water in the first cooling liquid pathway402is fed to the low-pressure stage compressor101, the high-pressure stage compressor102, and the oil cooler203by the cooling pump103. Meanwhile, a pathway is established in which the cooling water that has flowed through the low-pressure stage compressor101flows through the high-pressure stage compressor102, and then merges with the cooling water that has flowed through the oil cooler203, and is fed to the cooling heat exchanger204. In this case, a pathway is established in which the cooling water in the second cooling liquid pathway403is fed to the intercooler201by the circulation pump104, and thereafter, flows through the aftercooler202, flows through the heat recovery heat exchanger205, exchanges heat with the low-temperature side fluid, and then is discharged again by the circulation pump104. Namely, a configuration is implemented in which in the first cooling liquid pathway, the low-pressure stage compressor101and the high-pressure stage compressor102are connected in series to each other and in the second cooling liquid pathway, the intercooler201and the aftercooler202are connected in series to each other. In the case of the heat recovery mode B, namely, when the electromagnetic valve301and the electromagnetic valve302are opened and the supply water valve303and the supply water valve304are closed, all the cooling water that has been heated in the low-pressure stage compressor101, the high-pressure stage compressor102, the intercooler201, the aftercooler202, and the oil cooler203can exchange heat with the low-temperature side fluid pathway407via the heat recovery heat exchanger205, and the low-temperature side fluid can be heated and supplied. As described above, in a method in which the plurality of compressors or the coolers are connected in series to each other and the cooling water flows therethrough, a higher cooling water temperature can be obtained than in a method in which these elements are connected in parallel to each other and the cooling water of the same flow rate flows therethrough. Namely, since the low-temperature side fluid temperature after heat exchange in the heat recovery heat exchanger205can be a high temperature, the temperature range of the low-temperature side fluid that can be supplied can be widened. Incidentally, control of each valve in the present embodiment can be performed in the same procedure as the flowchart ofFIG.3. Meanwhile, it is desirable that the predetermined temperature threshold value Tdx of the compressed air is set to a temperature lower than a low-pressure stage discharge air alarm temperature Td1aand a high-pressure stage discharge air alarm temperature Td2a, for example, with respect to Td1a=215° C. and Td2a=220° C., Tdx is set to 210° C. which is slightly lower than both the alarm temperatures. In this case, it is desirable that the determination condition in step S106ofFIG.3is set to “Td1<Tdx and Td2<Tdx” using the low-pressure stage discharge air temperature Td1by the low-pressure stage discharge air temperature sensor501and the high-pressure stage suction air temperature Td2by the high-pressure stage suction air temperature sensor502, and this setting can contribute to protecting both the low-pressure stage compressor101and the high-pressure stage compressor102from an overheating state. Fourth Embodiment FIG.6is a system diagram of a compressor system in the present embodiment. InFIG.6, parts denoted by the same reference signs as those inFIGS.1to5indicate the same or corresponding parts, and a description of the parts will be omitted. In the present embodiment, a bypass pathway411is provided that branches from between the cooling water outlet of the aftercooler202on the second cooling liquid pathway403and the inlet of the heat recovery heat exchanger205, and that merges with a portion between a downstream side of the supply water valve304on the first cooling liquid pathway402and the cooling heat exchanger204. A supply water valve307is provided on the bypass pathway411. In addition, in order to detect a pressure difference between the inlet and the outlet of the heat recovery heat exchanger205on the second cooling liquid pathway403, a differential pressure switch509is provided that opens and closes an internal electric circuit according to the pressure difference, and a detection pipe412is provided that introduces the pressures of the inlet and the outlet of the heat recovery heat exchanger205to the differential pressure switch509. By any chance, when the circulation pump104fails or clogging occurs inside the heat recovery heat exchanger205, the intercooler201and the aftercooler202cannot be cooled during execution of the heat recovery mode A. In addition, during execution of the heat recovery mode B, in addition to the coolers, the low-pressure stage compressor101, the high-pressure stage compressor102, and the oil cooler203cannot be cooled. For this reason, the compressor unit1has to be stopped automatically to prevent a serious failure, so that the supply of the compressed air which is relatively important than the supply of the hot water by heat recovery is stopped. The present embodiment is configured for the purpose of preventing the above-described event, and securing the cooling of each element inside the compressor unit1and continuing to supply the compressed air even when a defect such as a failure of the circulation pump104occurs. In the control performed by the control device507of the heat recovery unit in the present embodiment, a case where the circulation pump104fails to cause the stop of the operation or clogging occurs inside the heat recovery heat exchanger205to cause the water not to flow is determined as a failure. Namely, usually, the differential pressure switch509determines a failure in such a manner that when the water flows, a pressure difference is generated and the differential pressure switch509does not operate, and when the water does not flow, the pressure difference is 0 and the differential pressure switch509operates. In that case, a backup cooling mode is performed to open the electromagnetic valve301, the electromagnetic valve302, the supply water valve303and the supply water valve307and close the supply water valve304and the supply water valve306. Accordingly, the first cooling liquid pathway402and the second cooling liquid pathway403communicate with each other, but all the cooling water is cooled in the cooling heat exchanger204, so that all the elements requiring cooling inside the compressor unit1are cooled. Therefore, the stop of the compressor unit1caused by a defect on a heat recovery unit2side can be prevented. Incidentally, it is desirable that unless the defect on the heat recovery unit2side is resolved and a failure signal or the like is reset, the backup cooling mode is continued. In addition, a failure may be determined by a water cutoff detection device as another configuration instead of the differential pressure switch as long as a case is detected in which the water does not flow. In addition, in the present embodiment, the configuration has been described that is obtained by adding a configuration to the configuration ofFIG.5in the third embodiment, but is not limited thereto, and the same configuration may be added to the configuration of the first or second embodiment. As described above, according to the present embodiment, even when a water supply pump that supplies water to the heat recovery heat exchanger has failed or the like, the cooling of the compressors, compressed gas, and the lubricant can be continued. Fifth Embodiment FIG.7is a system diagram of a compressor system in the present embodiment. InFIG.7, parts denoted by the same reference signs as those inFIGS.1to5indicate the same or corresponding parts, and a description of the parts will be omitted. InFIG.7, the first bypass pathway405branches from a cooling water outlet of the low-pressure stage compressor101on the first cooling liquid pathway402, and merges with an outlet of the intercooler201on the second cooling liquid pathway. The electromagnetic valve301and an orifice309immediately after the electromagnetic valve301are provided on the first bypass pathway405. In addition, a third bypass pathway409branches from a cooling water outlet of the high-pressure stage compressor102on the first cooling liquid pathway402, and merges with a portion upstream of the cooling water inlet of the aftercooler on the second cooling liquid pathway403. An electromagnetic valve305is provided on the third bypass pathway409. In the present embodiment, in the heat recovery mode A, control is performed to close the electromagnetic valve301, the electromagnetic valve302, and the electromagnetic valve305and open the supply water valve303and the supply water valve304. In addition, in the heat recovery mode B, control is performed to open the electromagnetic valve301, the electromagnetic valve302, and the electromagnetic valve305and close the supply water valve303and the supply water valve304. According to the present embodiment, an optimum distribution between a cooling water flow rate flowing into the high-pressure stage compressor102and a cooling water flow rate flowing into the aftercooler202can be obtained by designing and incorporating the inner diameter of the orifice309in advance according to specifications such as the heat exchange performance of the compressors or the coolers and the pressure loss of the cooling water pathway which are known in advance. Incidentally, in the present embodiment, the bypass pathway411, the supply water valve307, the detection pipe412, and the differential pressure switch509that are the configurations of the fourth embodiment may be added. Sixth Embodiment FIG.8is a system diagram of a compressor system in the present embodiment. InFIG.8, parts denoted by the same reference signs as those inFIGS.1to5andFIG.7indicate the same or corresponding parts, and a description of the parts will be omitted. In the present embodiment, in addition to the configuration ofFIG.7in the fifth embodiment, the temperature regulation valve308and the temperature sensor504that is attached to the outlet of the heat recovery heat exchanger205on the low-temperature side fluid pathway407, which are the same as those in the second embodiment, are provided. Therefore, according to the present embodiment, similar to the second embodiment in the fifth embodiment, an effect of enabling the low-temperature side fluid outlet temperature Tu to reach the target temperature Tux more quickly is obtained by providing the temperature regulation valve308. Incidentally, in the present embodiment, the bypass pathway411, the supply water valve307, the detection pipe412, and the differential pressure switch509that are the configurations of the fourth embodiment may be added. The embodiments have been described above; however, the present invention is not limited to the above-described embodiments and includes various modification examples. For example, in the embodiments, the example has been described in which the present invention is applied to the oil-free screw compressor; however, the present invention is not limited thereto, and can also be applied to oil-cooled screw compressors or water-injection type screw compressors in the same manner, and can be applied to any fluid machine such as scroll compressors, roots blowers, and turbochargers in the same manner. In addition, in the above-described embodiments, an example of the screw compressor including a pair of male and female screw rotors in a rotor chamber has been described; however, the present invention can also be applied to a single screw compressor including one screw rotor in the same manner. In addition, in the embodiments, the case has been illustrated in which water is used as the cooling liquid circulating through the first cooling liquid pathway and the second cooling liquid pathway; however, it can be assumed that a coolant containing an antifreeze component such as alcohols, or oil is used, and the cooling liquid is not limited to only water. Further, the low-temperature side fluid to be supplied to the outside after heat recovery is also not limited to water, and is assumed to be various fluids. In addition, the branch positions of the bypass pathways are not limited to only the embodiments, and the bypass pathways may be provided such that the cooling liquid thereinside flows toward the cooling heat exchanger or the heat recovery heat exchanger, and two cooling liquid pathways may be communicatable with each other. In addition, the above-described embodiments have been described in detail to facilitate the understanding of the present invention, and the present invention is not necessarily limited to including all the configurations that have been described. In addition, a part of a configuration of an embodiment can be replaced with a configuration of another embodiment, and a configuration of another embodiment can be added to a configuration of an embodiment. In addition, other configurations can be added to, removed from, or replaced with a part of the configuration of each of the embodiments. In addition, the control device may be realized by software by causing a processor to interpret and execute a program for realizing each function, or may be realized by hardware by being designed with, for example, an integrated circuit. REFERENCE SIGNS LIST 1Compressor unit2Heat recovery unit100Compressor (single-stage type)101Low-pressure stage compressor102High-pressure stage compressor103Cooling pump104Circulation pump201Intercooler202Aftercooler203Oil cooler204Cooling heat exchanger205Heat recovery heat exchanger301,302,305Electromagnetic valve303,304,306,307Supply water valve308Temperature regulation valve309Orifice401Air pathway402First cooling liquid pathway403Second cooling liquid pathway404Oil cooler cooling pathway405First bypass pathway406Second bypass pathway407Low-temperature side fluid pathway408Lubricant pathway409Third bypass pathway410,411Bypass pathway412Detection pipe501Discharge air temperature sensor or Low-pressure stage discharge air temperature sensor502High-pressure stage suction air temperature sensor503High-pressure stage discharge air temperature sensor504Temperature sensor505,507Control device506,508Control wiring509Differential pressure switch510TimerTd1Discharge air temperature or Low-pressure stage discharge air temperatureTd2High-pressure stage discharge air temperatureTdx Temperature threshold valueTda Discharge air alarm temperatureTd1aLow-pressure stage discharge air alarm temperatureTd2aHigh-pressure stage discharge air alarm temperatureTu Low-temperature side fluid temperatureTux Target temperaturetc Set time | 34,069 |
11859606 | IV. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring generally toFIGS.1through25, particular embodiments of a magnetically driven pressure generator (1) can include one or more of: a housing (2) having an open end (3) and a closed end (4), a flexible member (5) having a peripheral margin (6) sealably coupled to the open end (3) of said housing (2), a first magnetic force generator (7) disposed on the flexible member (5), and a second magnetic force generator (8) disposed proximally adjacent the flexible member (5), where either the first magnetic force generator (7) or second magnetic force generator (8) comprises an electromagnetic force generator (9). Now referring primarily toFIGS.1and21, the housing (2) can have a housing depth (10) disposed between an open end (3) and a closed end (4). In particular embodiments, the housing (2) can be configured as a right cylinder (as shown in the illustrative example ofFIGS.1through5); however, this is not intended to preclude embodiments which otherwise include the housing (2) having a configuration in cross section, such as a rectangle, square, triangle, elliptical cylinder, or combinations thereof, or where the sides are arcuate or have an amount of curvature and are not linear. The housing (2) can be composed of a substantially non-electrically conducting, rigid material, such as plastic, rubber, elastomer, glass, ceramics, or the like. The housing (2) can be fabricated, molded, or formed from a plurality of pieces or as one-piece. As illustrative examples: sintering of metal powders, plastic injection molding, waterjet machining, or combinations thereof. Now referring primarily toFIGS.1through13, a flexible member (5) can be sealably engaged along the peripheral margin (6) proximate the open end (3) of the housing (2). The term “sealably engaged” means engagement of the peripheral margin (6) of the flexible member (5) at or proximate to the open end (3) of the housing (2) to effect a substantially fluid tight seal, and without limitation to the breadth of the foregoing, includes as illustrative examples, a substantially fluid tight seal effected by compression between surfaces of the peripheral margin (6) of the flexible member (5) at or proximate to the open end (3) of the housing (2), adhesive applied between the surfaces of the peripheral margin (6) of the flexible member (5) and the open end (3) of the housing (2), laser welding of the peripheral margin (6) of the flexible member (5) to the open end (3) of the housing (2), or combinations thereof. The flexible member (5) can comprise one or more of a substantially non-electrically conductive elastomer, thermoplastic, or other material that can flex or deform from a first position to a second position, resiliently or non-resiliently, to correspondingly increase or decrease the volume of the enclosed space (11) in the housing (2). Additionally, the flexible member (5) can be substantially fluid impermeable or partially fluid impermeable during the normal operating cycle of the magnetically driven pressure generator (1). The flexible member (5) can be disposed at or proximate the open end (3) of the housing (2) to define an enclosed space (11) inside the housing (2), the enclosed space (11) bound by the internal surface (12) of the housing (2) and a first side (13) of the flexible member (5). Again, referring primarily toFIGS.1through13, a first magnetic force generator (7) can be disposed on or in the flexible member (5), and a second magnetic force generator (8) can be disposed axially adjacent to the first magnetic force generator (7) and proximate to the closed end (4) or proximate the open end (3) of the housing (2), whether disposed in the enclosed space (11) or disposed external to the housing (2) (as shown in the illustrative example ofFIGS.1-5). As to particular embodiments, the first magnetic force generator (7) can be an electromagnetic force generator (9) and the second magnetic force generator (8) can be a magnet (15)(as shown in the illustrative example ofFIG.13), or the first magnetic force generator (7) can be a magnet (15) and the second magnetic force generator (8) can be an electromagnetic force generator (9)(as shown in the illustrative examples ofFIGS.1through11). The term “magnet” means a material that retains its magnetic properties in the absence of an inducing field or current and, without limitation to the breadth of the foregoing, can be a piece of metal surrounded by a magnetic field which can be aligned with, attracted to, or repelled by an external magnetic field, and as illustrative examples: neodynium iron boron, samarium cobalt, alnico, ceramic or ferrite, or the like. The term “electromagnetic force generator” means an electrically conductive winding of a conductive material which upon passage of an electrical current generates a magnetic field (59) and, without limitation to the breadth of the foregoing, can as illustrative examples be one or more electrically conductive windings of: copper, silver, brass, or other like conductive materials or combinations thereof. Again, referring primarily toFIGS.1through5, particular embodiments can, but need not necessarily, include a first ferromagnetic core (16). The term “ferromagnetic core” means a body susceptible to magnetization in an applied electromagnetic field and, without limitation to the breadth of the foregoing, can be a one-piece body or a body comprising a plurality of layers of material susceptible to magnetization, such as: nickel, iron, cobalt, or other like material, or combinations thereof. In particular embodiments, the first magnetic force generator (7) coupled to the flexible member (5) can be a magnet (15) and the second magnetic force generator (8) can be an electromagnetic force generator (9) with the first ferromagnetic core (16) having a location responsive to the second magnetic force generator (8). In particular embodiments, the first ferromagnetic core (16) can be generally axially aligned with the first magnetic force generator (7). As to particular embodiments, the electromagnetic force generator (9) can engage the first ferromagnetic core (16) or be disposed a spaced distance about the first ferromagnetic core (16). As to particular embodiments, the second magnetic force generator (8) can comprise a plurality of metal windings wound about the external surface (17) of the housing (2) proximate to the closed end (4), and the first ferromagnetic core (16) can be disposed a spaced distance apart within the electromagnetic force generator (9) axially aligned with the first magnetic force generator (7)(as shown in the illustrative example ofFIG.5). In particular embodiments, the second magnetic force generator (8) can comprise a plurality of windings wound about the ferromagnetic core external surface (18) with the first ferromagnetic core (16) substantially axially aligned with the first magnetic force generator (7). Now referring primarily toFIGS.1through5, particular embodiments can, but need not necessarily, include a third magnetic force generator (19), which can be disposed at or proximate to the open end (3) or the closed end (4) of the housing (2). The third magnetic force generator (19) can be a magnet (15) or electromagnetic force generator (9), as described above. As to embodiments that include a third magnetic force generator (19) in the form of an electromagnetic force generator (9), a second ferromagnetic core (20) can, but need not necessarily, be disposed proximate to the open end (3) of the housing (2) at a location to which the second ferromagnetic core (20) can be responsive to the electromagnetic field applied by the electromagnetic force generator (9). The second ferromagnetic core (20) can be disposed to generally axially align with the first magnetic force generator (7) disposed on the flexible member (5). Now referring primarily toFIGS.14through23, in particular embodiments, the housing (2) can, but need not necessarily, be partitioned into a first fluid chamber (21) and a second fluid chamber (22) by a partition wall (23). The partition wall (23) can be sealably engaged with the closed end (4) of the housing (2) and extend to the open end (3) of the housing (2). The flexible member (5) can be sealably engaged along the peripheral margin (6) at or proximate to the open end (3) of the first fluid chamber (21). A cover (24) can be sealably engaged to or proximate the open end (3) of the second fluid chamber (22). The cover (24) can be comprised of one or more substantially non-electrically conductive elastomers, thermoplastics, or the like. Additionally, the cover (24) can be substantially fluid impermeable during the normal operating cycle of the magnetically driven pressure generator (1). The partition wall (23) can further include an aperture (25) communicating between the first fluid chamber (21) and second fluid chamber (22). A first unidirectional valve (26) can be disposed in the partition wall (23) to permit a fluid flow (27) to move in only one direction between the first and second chambers (21)(22). The first unidirectional valve (26) disposed in the partition wall (23) can be responsive to negative or positive fluid pressure (28) within the first or second fluid chambers (21)(22) (as shown in the illustrative example ofFIGS.21and23, the first unidirectional valve (26) can comprise a flap valve) or the first unidirectional valve (26) can be an electrically operable between an open condition and a closed condition in response to a signal from a controller (29), as further described below. Again, referring primarily toFIGS.1through23, particular embodiments can, but need not necessarily, further include one or more ports (30) disposed in the housing (2) which communicate between the internal surface (12) and external surface (17) of the housing (2). Particular embodiments can, but need not necessarily, further include conduits (31) engaged to the one or more ports (30) to extend the enclosed space (11) of the housing (2) to the distal end (32) of the conduits (31) allowing an increase or decrease of fluid pressure (28) or fluid flow (27) within the conduits (31) at the distal end (23). As to particular embodiments, the housing (2) can include one or more of a fluid outlet port (33), a fluid bleed port (34), a fluid inlet port (35), and a pressure sensor port (36). The fluid outlet port (33) can communicate between the external surface (17) and the internal surface (12) of the housing (2) to provide a fluid flow (27) from the enclosed space (11)(as to the illustrative embodiments ofFIGS.1-13) or from the first fluid chamber (21) (as shown in the illustrative embodiments ofFIGS.14-23). A fluid delivery conduit (40) can be sealably engaged to the fluid outlet port (33) for delivery of an amount of fluid (41) to the distal end (32) of the fluid delivery conduit (40), which can, but need not necessarily, be disposed to deliver an amount of fluid (41) from the enclosed space (11) of the housing (2) or the first chamber (21). Now referring primarily toFIGS.14-23, a fluid inlet port (35) can communicate between the external surface (17) and the internal surface (12) of the housing (2) of the second chamber (22). The fluid inlet port (35) can sealably engage a fluid inlet conduit (44) open to atmosphere in the ambient environment (65) or coupled to a fluid source (45) which can contain an amount of fluid (41). The amount of fluid (41) contained by the fluid source (45) can be, as illustrative examples: a liquid, a gel, a viscous polymer, or other material, or combinations thereof, which deforms continuously for delivery from the fluid source (45) into the second fluid chamber (22). The amount of fluid (41) contained in the fluid source (45) can be delivered as a fluid flow (27) from the fluid source (45) under force of one or more of: gravity, pressurized head space, a fluid pump, or combinations thereof. As to particular embodiments, a fluid inlet valve (46) can be disposed between the fluid inlet port (35) and the fluid source (45) to intermittently or continuously interrupt flow of an amount of fluid (41) to or from the second fluid chamber (22) toward the fluid source (45). Again, referring primarily toFIGS.14through23, the fluid bleed port (34) can communicate between the external surface (17) and internal surface (12) of the housing (2) of the second chamber (22). The fluid bleed port (34) can sealably engage a fluid bleed conduit (47) and the distal end (32) of the fluid bleed conduit (47) can be disposed in the ambient environment (65). The fluid bleed conduit (43) can conduct an amount of fluid (41) from the second chamber (22) to the ambient environment (65). If the amount of fluid (41) delivered from the fluid source (45) exceeds the volume of the second fluid chamber (22), the excess amount of fluid (38) can egress from the second fluid chamber (22) through the fluid bleed port (34) and the fluid bleed conduit (47) to the ambient environment (65). Again, referring primarily toFIGS.14through23, as to particular embodiments, a fluid flow generator (49) can be coupled between the fluid bleed port (35) and the distal end (32) of the fluid bleed conduit (46). The fluid flow generator (49) can operate in the first instance to provide the bleed valve (48) in the open condition, which allows egress of an excess amount of fluid (41) from the second fluid chamber (22). The fluid flow generator (49) in the second instance can operate to generate a flow of air (66) from the ambient environment (65) into the second fluid chamber (22) to move the amount of fluid (41) contained in the second fluid chamber (22) through the aperture (25) disposed in the partition wall (23) into the first fluid chamber (21). Now referring primarily toFIGS.1through23, embodiments can, but need not necessarily, further include a fluid pressure relief valve (38). As to particular embodiments, the fluid pressure relief valve (38) can be coupled to a pressure relief port (37) which communicates between the external surface (17) and the internal surface (12) of the housing (2) of the enclosed space (11)(as shown in the illustrative example ofFIGS.1through5). As to other embodiments, a fluid return conduit (50) can, but need not necessarily, be fluidicly coupled to the fluid delivery conduit (40) to return the amount of fluid (41) to the fluid source (45), a fluid collection vessel (51), or discharge the amount of fluid to the ambient environment (65) (as shown in the illustrative examples ofFIGS.14through23). As to these embodiments the pressure relief valve (38) can operate between a closed condition to generate an amount of fluid pressure (28) in the first fluid chamber (21), the fluid delivery conduit (40), or the fluid return conduit (50), and an open condition to relieve an amount of fluid pressure (28) in the first fluid chamber (21), the fluid delivery conduit (40), or the fluid return conduit (50). As illustrative examples, the pressure release valve (38) can be configured to relieve an amount of pressure (28) in the enclosed space (11) or first fluid chamber (21) when the amount of pressure (28) exceeds a pre-selected pressure (28) to actuate the pressure release valve (38). In one illustrative embodiment, the pressure release valve (38) can be disposed in the open condition when the amount of pressure (28) exceeds 5.0 psi (pounds per square inch; about 34 kPa; 1 psi=about 6.8 kPa). As to particular embodiments, the pressure release valve (38) can be disposed in the open condition in response to lesser or greater amounts of pressure (28) in a range of about 0 psi to 20 psi (about 0 kPa to about 137.8 kPa). The amount of pressure (28) can be selected from the group including or consisting of: about 0.0 psi to about 1.0 psi, about 0.5 psi to about 1.5 psi, about 1.0 psi to about 2.0 psi, about 1.5 psi to about 2.5 psi, about 2.0 psi to about 3.0 psi, about 2.5 psi to about 3.5 psi, about 3.0 psi to about 4.0 psi, about 3.5 psi to about 4.5 psi, about 4.0 psi to about 5.0 psi, about 4.5 psi to about 5.5 psi, about 5.0 psi to about 6.0 psi, about 5.5 psi to about 6.5 psi, about 6.0 psi to about 7.0 psi, about 6.5 psi to about 7.5 psi, about 7.0 psi to about 8.0 psi, about 7.5 psi to about 8.5 psi, about 8.0 psi to about 9.0 psi, about 8.5 psi to about 9.5 psi, about 9.0 psi to about 10.0 psi, about 9.5 psi to about 10.5 psi, about 10.0 psi to about 11.0 psi, about 10.5 psi to about 11.5 psi, about 11.0 psi to about 12.0 psi, about 11.5 psi to about 12.5 psi, about 12.0 psi to about 13.0 psi, about 12.5 psi to about 13.5 psi, about 13.0 psi to about 14.0 psi, about 13.5 psi to about 14.5 psi, about 14.0 psi to about 15.0 psi, about 14.5 psi to about 15.5 psi, about 15.0 psi to about 16.0 psi, about 15.5 psi to about 16.5 psi, about 16.0 psi to about 17.0 psi, about 16.5 psi to about 17.5 psi, about 17.0 psi to about 18.0 psi, about 17.5 psi to about 18.5 psi, about 18.0 psi to about 19.0 psi, about 18.5 psi to about 19.5 psi, and about 19.0 psi to about 20.0 psi. The foregoing embodiments are not intended to preclude embodiments which dispose the pressure release valve (24) in the open condition at a fluid pressure (28) of greater than 20 psi, depending on the application. Now referring primarily toFIGS.1through23, particular embodiments can, but need not necessarily, further include a pressure sensor (39). The pressure sensor (39) can be fluidicly coupled to the enclosed space (11) of the housing (2) or first fluid chamber (21) to sense the amount of pressure (28) inside the enclosed space (11) or first fluid chamber (21). The pressure sensor (39) can generate a signal (53) which varies based on the increase or decrease of pressure (28) within the enclosed space (11) or first fluid chamber (21) within the housing (2). Now referring generally toFIGS.1through24, with particular reference toFIGS.21through24, particular embodiments can, but need not necessarily, further include a controller (29) including a controller processor (54) communicatively coupled to a controller non-transitory computer readable media (55) containing a computer program (56) executable by the controller processor (54) to control the direction and magnitude of current (57) in the one or more electromagnetic force generators (9). The controller (29) can be contained inside of the magnetically driven pressure generator (1) or within a casing (71) enclosing the magnetically driven pressure generator (1) or can be electronically coupled (whether wired or wirelessly) through intermediary hardware to an external controller (29A) in which the processor (54A) the non-transitory computer readable medium (55A) containing the computer program (56A) resides in a mobile device (68), such as: a cellular telephone, tablet computer, laptop computer, or other computer implemented device in which the computer program (56A) can reside. As to particular embodiments, the computer program (56)(56A) can operate a current controller (58) electrically coupled to one or more electromagnetic force generators (9)(19). The current controller (58) can function to control the magnitude of the current (57) conducted through the one or more electromagnetic force generators (9)(19). The current controller (58) can be adapted for use with alternating current, direct current, or both. The magnetic field (59) generated by the electromagnetic force generator (9) can be proportional to the magnitude of the current (57). Accordingly, the current controller (58), by varying the amplitude of the current (57), can correspondingly continuously or intermittently vary the strength of the magnetic field (59) to correspondingly continuously control flexure of the flexible member (5) to intermittently or continuously precisely form pressure waves (67) having pre-selected amplitude and frequency values (63)(64) over time. As to particular embodiments, the computer program (56) can further operate a polarity controller (60) electrically coupled to the one or more electromagnetic force generators (9). The polarity controller (60) operates to control the direction of the current (57) being conducted through the one or more electromagnetic force generators (9)(19). The direction of magnetic polarity generated by the electromagnetic force generator (9) can be changed by correspondingly changing the direction of current (57) flowing in the electromagnetic force generator (9)(19). Accordingly, the polarity controller (60) can, by changing the direction of the current (57) in the electromagnetic force generator, (9)(19) correspondingly change the direction of the magnetic polarity generated by the electromagnetic force generator (9)(19). Particular embodiments can further include a power source (61). The power source (61) can be electrically coupled to the one or more electromagnetic force generators (9) directly, through intermediary hardware (the microprocessor, a current controller, a polarity controller), or both. Further, the power source (61) can provide power convertible to alternating current, direct current, or both. Now referring primarily toFIGS.1through23, particular embodiments of the magnetically driven pressure generator (1) can be used to generate either an increase or decrease in pressure (28) of a fluid flow (27) of an amount of fluid (41) in or from the enclosed space (11) or the first fluid chamber (21) depending on the embodiment. As an illustrative example, referring toFIGS.1through13, the magnetically induced pressure generator (1) can be configured to operate the second magnetic force generator (8) to induce an amount of flexure in the flexible member (5) to correspondingly alter the volume of the enclosed space (11) to correspondingly increase or decrease pressure of an amount of fluid (41) contained therein. A gas contained in a closed system, exhibits an inverse relationship between pressure and volume. Accordingly, if the flexible member (5) flexes toward the closed end (4) of the housing (2), the volume of the enclosed space (11) correspondingly decreases, and the fluid pressure (28) of the gas within the enclosed space (11) can correspondingly increase. Conversely, if the flexible member (5) flexes away from the closed end (4) of the housing (2), the volume of the enclosed space (11) correspondingly increases, and the pressure of the gas within the enclosed space (11) correspondingly decreases. In the aforementioned particular embodiments, the amplitude of change in pressure (28) of the gas in the enclosed space (11) can be proportionate to the amount of flexure of the flexible member (5) induced by attracting or repulsing forces generated between the first magnetic force generator (7) and the second magnetic force generator (8). Additionally, alternating the attracting and repulsing forces generated between the first magnetic force generator (7) and the second magnetic force generator (8) can correspondingly generate oscillation in the flexible member (5) in an oscillation period independent of the oscillation amplitude. Accordingly, pressure waves can be precisely generated in the enclosed space (11) of the housing (2) having a pre-selected amplitude or frequency values (63)(64) over a period of time by operation of the current controller (58) and the polarity controller (60). Referring primarily toFIGS.14through23, particular embodiments of the magnetically driven pressure generator (1) can operate to alter fluid pressure (28) or generate a fluid flow (27) in an amount of fluid (41), whether the fluid is a liquid or a gas. As an illustrative example, the enclosed space (11) can, as above described, include a first fluid chamber (21), a second chamber (22), a fluid delivery conduit (40), a fluid return conduit (50), and an earpiece (43) coupled to the fluid delivery conduit (40) and the fluid return conduit (50) which can be disposed in or sealably engaged to the external ear canal (42). The fluid inlet valve (46) can be disposed in the open condition to allow an amount of fluid (41) to be delivered from the fluid source (45) through the fluid inlet conduit (44) to the second fluid chamber (22). As an amount of fluid (41) flows into the second fluid chamber (22), the bleed valve (48) within the fluid flow generator (49) can be disposed in the open condition to permit air inside the second fluid chamber (22) to flow through the fluid bleed conduit (47) and to the ambient environment (65). Once the second fluid chamber (22) contains an amount of fluid (22), the fluid flow generator (49) can be further operated to generate a flow of air (67) into the second fluid chamber (22) to force the amount of fluid (41) within the second fluid chamber (22) through the aperture (25) disposed in the partition wall (23) into the first fluid chamber (21). The first unidirectional valve (26) operates to prohibit fluid flow (27) from the first fluid chamber (21) back into the second fluid chamber (22). By operation of the flexible member (5) the amount of fluid (41) can then be delivered from the first fluid chamber (21) through the fluid delivery conduit (40) and through the fluid return conduit (50). As one illustrative example, the fluid delivery conduit (40) and the fluid return conduit (50) can be disposed in the external ear canal (42) of an ear (70), and as to certain embodiments, the fluid delivery conduit (40) and the fluid return conduit (50) can pass through or be surrounded by an earpiece (43) which can be disposed in or sealably engaged with the external ear canal (42) of the ear (70). The amount of fluid (41) can be delivered into the external ear canal (42) from the fluid delivery conduit (40), circulate in the external ear canal (42), pass into the fluid return conduit (50), and through the pressure release valve (38) in the open condition. The pressure relief valve (38) can then be disposed in the closed condition to allow the pre-selected fluid pressure (28) to be generated in the fluid delivery conduit (40), the fluid return conduit (50), and in the external ear canal (42) of the ear (70) when the earpiece (43) engages or sealably engages the external ear canal (42). As above described, operation of the first magnetic force generator (7) and the second magnetic force generator (8) can effect an amount of flexure in the flexible member (5) to correspondingly alter the volume of the first fluid chamber (21) to correspondingly increase or decrease fluid pressure of the fluid (41) therein. The flexure of the flexible member (5) toward the closed end (4) of the housing (2) can decrease the volume of the first fluid chamber (21), without substantially increasing or decreasing the surface area of the first fluid chamber (21) or volume of amount of fluid (38) within the first fluid chamber (21), thereby increasing the fluid pressure (28) within the first fluid chamber (21). The flexure of the flexible member (5) can also occur away from the closed end (4) of the housing (2), which increases the volume of the first fluid chamber (21) without substantially increasing or decreasing the surface area of the first fluid chamber (21) or volume of amount of fluid (41) within the first fluid chamber (21), thereby decreasing the fluid pressure (28) within the first fluid chamber (21). In the aforementioned particular embodiments, the amplitude of change in fluid pressure (28) of the amount of fluid (41) in the first fluid chamber (21) can be proportionate to the amount of flexure of the flexible member (5) induced by attracting or repulsing forces generated between the first magnetic force generator (7) and the second magnetic force generator (8). Additionally, alternating the attracting and repulsing forces generated between the first magnetic force generator (7) and the second magnetic force generator (8) can correspondingly generate oscillation in the flexible member (5) in an oscillation period independent of the oscillation amplitude. Accordingly, pressure waves (67) can be generated in the first fluid chamber (21) having a pre-selected amplitude (63) and frequency values (64) by operation of the current controller (58) and the polarity controller (60). Again, referring toFIG.5, in particular embodiments, a third magnetic force generator (19) can be included comprising either a magnet (15) or electromagnetic force generator (9) to further interact with the attracting forces or repulsing forces of the first magnetic force generator (7) and second magnetic force generator (8), flexing the flexible member (5) accordingly, as described above. In a particular embodiment, the operation of the program (56) can be executed to oscillate the flexible member (5) as described above, at a pre-selected oscillation frequency (64). The oscillation frequency (64) can be in a range of about 0 to about 100 kiloHertz (kHz). The oscillation frequency can be selected from the group including or consisting of: about 0 kHz to about 5.0 kHz, about 2.5 kHz to about 7.5 kHz, about 5.0 kHz to about 10.0 kHz, about 7.5 kHz to about 12.5 kHz, about 10.0 kHz to about 15.0 kHz, about 12.5 kHz to about 17.5 kHz, about 15.0 kHz to about 20.0 kHz, about 17.5 kHz to about 22.5 kHz, about 20.0 kHz to about 25.0 kHz, about 22.5 kHz to about 27.5 kHz, about 25.0 kHz to about 30.0 kHz, about 27.5 kHz to about 32.5 kHz, about 30.0 kHz to about 35.0 kHz, about 32.5 kHz to about 37.5 kHz, about 35.0 kHz to about 40.0 kHz, about 37.5 kHz to about 42.5 kHz, about 40.0 kHz to about 45.0 kHz, about 42.5 kHz to about 47.5 kHz, about 45.0 kHz to about 50.0 kHz, about 47.5 kHz to about 52.2 kHz, about 50.0 kHz to about 55.0 kHz, about 52.5 kHz to about 57.5 kHz, about 55.0 kHz to about 60.0 kHz, about 57.5 kHz to about 62.5 kHz, about 60.0 kHz to about 65.0 kHz, about 62.5 kHz to about 67.5 kHz, about 65.0 kHz to about 70.0 kHz, about 67.5 kHz to about 72.5 kHz, about 70.0 kHz to about 75.0 kHz, about 72.5 kHz to about 77.5 kHz, about 75.0 kHz to about 80.0 kHz, about 77.5 kHz to about 82.5 kHz, about 80.0 kHz to about 85.0 kHz, about 82.5 kHz to about 87.5 kHz, about 85.0 kHz to about 90.0 kHz, about 87.5 kHz to about 92.5 kHz, about 90.0 kHz to about 95.0 kHz, about 92.5 kHz to about 97.5 kHz, about 95.0 kHz to about 100 kHz, and combinations thereof. In yet another particular embodiment, the computer program (56) can be executed to generate a pre-selected pressure amplitude (63), whether a positive pressure or negative pressure as compared to the ambient pressure (52) in the enclosed space (11) or first fluid chamber (21), depending upon the embodiment and application. In one illustrative embodiment, the range of pre-selected pressure amplitude (63) can be about 0 psi to about 5 psi (about 0 kPa to about 34.4 kPa; 1 psi=6.8 kPa). In another illustrative embodiment, the pre-selected pressure amplitude (63) can be a range of pressures of about 0 psi to about 20 psi (about 0 kPa to about 137.8 kPa; 1 psi=6.8 kPa). The pre-selected pressure amplitude (63) in the closed space (11) or the first fluid pressure chamber (21) can be selected from the group including or consisting of: about 0.0 psi to about 1.0 psi, about 0.5 psi to about 1.5 psi, about 1.0 psi to about 2.0 psi, about 1.5 psi to about 2.5 psi, about 2.0 psi to about 3.0 psi, about 2.5 psi to about 3.5 psi, about 3.0 psi to about 4.0 psi, about 3.5 psi to about 4.5 psi, about 4.0 psi to about 5.0 psi, about 4.5 psi to about 5.5 psi, about 5.0 psi to about 6.0 psi, about 5.5 psi to about 6.5 psi, about 6.0 psi to about 7.0 psi, about 6.5 psi to about 7.5 psi, about 7.0 psi to about 8.0 psi, about 7.5 psi to about 8.5 psi, about 8.0 psi to about 9.0 psi, about 8.5 psi to about 9.5 psi, about 9.0 psi to about 10.0 psi, about 9.5 psi to about 10.5 psi, about 10.0 psi to about 11.0 psi, about 10.5 psi to about 11.5 psi, about 11.0 psi to about 12.0 psi, about 11.5 psi to about 12.5 psi, about 12.0 psi to about 13.0 psi, about 12.5 psi to about 13.5 psi, about 13.0 psi to about 14.0 psi, about 13.5 psi to about 14.5 psi, about 14.0 psi to about 15.0 psi, about 14.5 psi to about 15.5 psi, about 15.0 psi to about 16.0 psi, about 15.5 psi to about 16.5 psi, about 16.0 psi to about 17.0 psi, about 16.5 psi to about 17.5 psi, about 17.0 psi to about 18.0 psi, about 17.5 psi to about 18.5 psi, about 18.0 psi to about 19.0 psi, about 18.5 psi to about 19.5 psi, about 19.0 psi to about 20.0 psi, and combinations thereof. The above embodiments are illustrative only, as the pre-selected pressure amplitude can be selected from the range of about 0 psi to about any pre-selected pressure amplitude, depending on the application. By combining pre-selected pressure amplitudes (63) in various combinations and permutations with pre-selected oscillation frequencies (64) over a period of time, stable pressure amplitudes (63)(whether positive or negative relative to the ambient pressure (52)) or pressure waves (67) having preselected amplitude values (63) or frequency values (64), or combinations thereof, can be generated in the enclosed space (11) or the first fluid pressure chamber (21) to track pre-selected pressure profiles (62) of the program (56). To ensure that the pre-selected amplitude and frequency values (63)(64) or pre-selected pressure profiles (62) are achieved, the pressure sensor signal (53) generated by the pressure sensor (39) coupled to the pressure sensor port (36) can be analyzed by a feedback module (72) of the computer program (56) to correspondingly alter operation of the flexible member (5). Now referring primarily toFIGS.21through25, as to particular embodiments, the distal ends (32) of the fluid delivery conduit (40) or the fluid return conduit (50) can be disposed in the external ear canal (42) of an ear (70). An amount of fluid (41) can be delivered from the first fluid chamber (21) of the housing (2) to the distal end (32) of the fluid delivery conduit (40) into the external ear canal (42) of an ear (70) and egress the external ear canal (42) of the ear (70) through the fluid return conduit (50). The pressure relief valve (38) can be disposed in the open condition or closed condition depending on the amount of fluid pressure (28) to be generated in the external ear canal (42) of the ear (70). As to particular embodiments, the pressure relief valve (38) can be maintained in the open condition to allow an amount of fluid (41) to circulate in the external ear canal (42) of the ear (70) at a relatively low fluid pressure (28). As to other embodiments, the pressure relief valve (38) can be maintained in the closed condition or intermittently closed condition to generate a continuous or substantially continuous fluid pressure (28)(whether negative or positive compared to ambient pressure (52)) or a variable fluid pressure (28), or a fluid pressure adjusted over a period time to track a pre-selected pressure profile (62)(a set of pre-selected pressure values over a period of time). Again referring primarily toFIGS.14through25, embodiments can further include a casing (71) which encloses or operably supports one or more of: the housing (2), the magnetic force generators (8)(9)(19), ferromagnetic cores (16)(20), fluid flow generator (49), controller (29), conduits (31), and associated circuitry. The casing (71), as to particular embodiments, can be configured to couple, connect, attach, or bring embodiments of the magnetically driven pressure generator (1) into proximity with an object or person for use. As shown in the illustrative example ofFIG.25, the casing (71) can be configured to provide an external ear canal pressure regulation device (74) which can be disposed behind and about the auricle (73) of the ear (70). As can be easily understood from the foregoing, the basic concepts of the present invention may be embodied in a variety of ways. The invention involves numerous and varied embodiments of a magnetically driven pressure generator and methods for making and using such a magnetically driven pressure generator including the best mode. As such, the particular embodiments or elements of the invention disclosed by the description or shown in the figures or tables accompanying this application are not intended to be limiting, but rather exemplary of the numerous and varied embodiments generically encompassed by the invention or equivalents encompassed with respect to any particular element thereof. In addition, the specific description of a single embodiment or element of the invention may not explicitly describe all embodiments or elements possible; many alternatives are implicitly disclosed by the description and figures. It should be understood that each element of an apparatus or each step of a method may be described by an apparatus term or method term. Such terms can be substituted where desired to make explicit the implicitly broad coverage to which this invention is entitled. As but one example, it should be understood that all steps of a method may be disclosed as an action, a means for taking that action, or as an element which causes that action. Similarly, each element of an apparatus may be disclosed as the physical element or the action which that physical element facilitates. As but one example, the disclosure of an “electromagnetic force generator” should be understood to encompass disclosure of the act of “generating an electromagnetic force”—whether explicitly discussed or not—and, conversely, were there effectively disclosure of the act of “generating an electromagnetic force”, such a disclosure should be understood to encompass disclosure of an “electromagnetic force generator” and even a “means for generating an electromagnetic force.” Such alternative terms for each element or step are to be understood to be explicitly included in the description. In addition, as to each term used it should be understood that unless its utilization in this application is inconsistent with such interpretation, common dictionary definitions should be understood to be included in the description for each term as contained in the Random House Webster's Unabridged Dictionary, second edition, each definition hereby incorporated by reference. All numeric values herein are assumed to be modified by the term “about”, whether or not explicitly indicated. For the purposes of the present invention, ranges may be expressed as from “about” one particular value to “about” another particular value. When such a range is expressed, another embodiment includes from the one particular value to the other particular value. The recitation of numerical ranges by endpoints includes all the numeric values subsumed within that range. A numerical range of one to five includes for example the numeric values 1, 1.5, 2, 2.75, 3, 3.80, 4, 5, and so forth. It will be further understood that the endpoints of each of the ranges are significant both in relation to the other endpoint, and independently of the other endpoint. When a value is expressed as an approximation by use of the antecedent “about,” it will be understood that the particular value forms another embodiment. The term “about” generally refers to a range of numeric values that one of skill in the art would consider equivalent to the recited numeric value or having the same function or result. Similarly, the antecedent “substantially” means largely, but not wholly, the same form, manner or degree and the particular element will have a range of configurations as a person of ordinary skill in the art would consider as having the same function or result. When a particular element is expressed as an approximation by use of the antecedent “substantially,” it will be understood that the particular element forms another embodiment. Moreover, for the purposes of the present invention, the term “a” or “an” entity refers to one or more of that entity unless otherwise limited. As such, the terms “a” or “an”, “one or more” and “at least one” can be used interchangeably herein. Thus, the applicant(s) should be understood to claim at least: i) each of the magnetically driven pressure generator herein disclosed and described, ii) the related methods disclosed and described, iii) similar, equivalent, and even implicit variations of each of these devices and methods, iv) those alternative embodiments which accomplish each of the functions shown, disclosed, or described, v) those alternative designs and methods which accomplish each of the functions shown as are implicit to accomplish that which is disclosed and described, vi) each feature, component, and step shown as separate and independent inventions, vii) the applications enhanced by the various systems or components disclosed, viii) the resulting products produced by such systems or components, ix) methods and apparatuses substantially as described hereinbefore and with reference to any of the accompanying examples, x) the various combinations and permutations of each of the previous elements disclosed. The background section of this patent application provides a statement of the field of endeavor to which the invention pertains. This section may also incorporate or contain paraphrasing of certain United States patents, patent applications, publications, or subject matter of the claimed invention useful in relating information, problems, or concerns about the state of technology to which the invention is drawn toward. It is not intended that any United States patent, patent application, publication, statement or other information cited or incorporated herein be interpreted, construed or deemed to be admitted as prior art with respect to the invention. The claims set forth in this specification, if any, are hereby incorporated by reference as part of this description of the invention, and the applicant expressly reserves the right to use all of or a portion of such incorporated content of such claims as additional description to support any of or all of the claims or any element or component thereof, and the applicant further expressly reserves the right to move any portion of or all of the incorporated content of such claims or any element or component thereof from the description into the claims or vice-versa as necessary to define the matter for which protection is sought by this application or by any subsequent application or continuation, division, or continuation-in-part application thereof, or to obtain any benefit of, reduction in fees pursuant to, or to comply with the patent laws, rules, or regulations of any country or treaty, and such content incorporated by reference shall survive during the entire pendency of this application including any subsequent continuation, division, or continuation-in-part application thereof or any reissue or extension thereon. Additionally, the claims set forth in this specification, if any, are further intended to describe the metes and bounds of a limited number of the preferred embodiments of the invention and are not to be construed as the broadest embodiment of the invention or a complete listing of embodiments of the invention that may be claimed. The applicant does not waive any right to develop further claims based upon the description set forth above as a part of any continuation, division, or continuation-in-part, or similar application. | 43,387 |
11859607 | DETAILED DESCRIPTION A new and useful actuated valve for reciprocating machines has been developed and is disclosed herein. The novel valve is particularly useful as a suction valve and can be useful as a discharge valve in reciprocating compressors. The valve includes a cage and a valve closing member, i.e. a shutter. The valve closing member is adapted to be drivingly coupled to a control actuator. The valve closing member has an actuation stem, which is guided in a guide integrally formed with the cage of the valve. Effective guidance of the valve closing member is thus obtained. Several additional features of exemplary embodiments and relevant advantages thereof will be described in more detail here below, reference being made to the accompanying drawings. In the following description embodiments of reciprocating compressor valves will be described. Those skilled in the art will however understand that the actuated valves disclosed herein can be used with advantage also in other reciprocating machines. FIG.1schematically shows a double-acting reciprocating compressor1. The reciprocating compressor1comprises a cylinder3and a piston5arranged in the cylinder3and adapted to reciprocatingly move therein when the compressor is in use. The piston5and the cylinder3form two compressor chambers7A,7B where a gaseous fluid to be compressed is cyclically sucked and compressed. A crank shaft9, drivingly coupled to a driver, not shown, transmits motion to the piston5. The rotary motion of the crank shaft9is converted into reciprocating translation motion by a connecting rod11ad a crosshead13, which is connected to the piston5by a piston rod15. Each compression chamber7A,7B is provided with at least one suction valve21and one delivery or discharge valve23, respectively. The suction valves21can be fluidly coupled to a suction plenum25, from which a gaseous fluid at a first, lower pressure P1is sucked alternatively in the first and second compression chambers7A,7B. The discharge valves23can be fluidly coupled to a discharge plenum27, into which the gaseous fluid is discharged at a second, higher pressure P2. A respective actuator, for example an electro-magnetic actuator29, controls each suction valve21. A respective actuator, for instance an electro-magnetic actuator31, controls each discharge valve23. Suitable electro-magnetic actuators are disclosed in US2007/0272890, which is incorporated herein by reference. In operation, the piston5moves reciprocatingly according to double arrow f5inside the cylinder3such that gas is cyclically sucked through suction valves21at suction pressure P1and discharged at discharge pressure P2through discharge valves23. Opening and closing of the suction valves21and discharge valve23is controlled by actuators29and31. A more precise control of the compression cycle and of the compressor flowrate can be achieved. While inFIG.1both the suction valves21and the discharge valves23are fully actuated by actuators29and31, in other embodiments, one, some of all the suction valves21, or one, some or all discharge valves23can be automatic valves. For instance, the suction valves21can be fully actuated valves, while the discharge valves23can be automatic valves. Actuators on one, some or all suction valves21may be used to better control the compressor flowrate. With continuing reference toFIG.1,FIGS.2,3,4and5illustrate an exemplary embodiment of a suction valve21, and the way it can be mounted on the compressor cylinder3. In the embodiment ofFIGS.2,3and4the suction valve21includes a casing or cage33, which has a set of posts35extending between a cover37and a seat39. The posts define flow passages, such that when the valve21is arranged in fluid communication with the suction duct or plenum25, gas can enter the valve and flow therethrough. The seat39can include a plurality of suction apertures or ports41. The apertures41can be in the form of elongated and curved ports arranged according to circumferential concentric lines, coaxial with the valve axis A-A. The seat39can include a replaceable seat plate43, which is provided with ports or apertures46, having the same shape and position as the ports41. A pin44can be used to mount the replaceable seat plate43in the correct angular position, such that the apertures46and41are mutually aligned. A ferrule42can be provided to mount the replaceable seat plate43on the seat39. The cover37can be provided with an annular groove37A adapted to receive an O-ring or any other gasket or sealing member, which provides a seal between the suction valve21and the compressor cylinder3when the valve21is mounted, seeFIG.5. The suction valve21further comprises a valve closing member45also referred to as shutter. The valve closing member45is illustrated in detail inFIG.4, separated from the suction valve21. The valve closing member45comprises a plate47and a stem49. The plate47includes a plurality of apertures or ports51, which are shifted with respect to the suction apertures41, such that the solid (non-perforated) portions of the plate47close the suction apertures41when the valve closing member45is in the closed position, in abutment against the replaceable seat plate43. In order to mount the valve closing member45in the correct angular position with respect to the seat39, a transverse pin53can be provided along the stem49, said pin slidingly engaging a slot57machined in the seat49. The valve closing member45can be manufactured as a single component, for instance by additive manufacturing. This may reduce manufacturing costs. In other embodiments, however, the plate47and the stem49can be manufactured separately and then coupled together, e.g. by welding, gluing, soldering, or else by way of screws or bolts. The valve closing member45can be manufactured in metal material. In other embodiments, use of polymeric material is not excluded. The stem49can be hollow (see hole49A) in order to reduce the mass and therefore the inertia thereof. The axial hole49A can be closed at the end facing the interior of the compression chamber, to reduce the clearance volume of the compressor. In some embodiments, a honeycomb or other stiffening structure can be provided inside the axial hole49A. Such structure can easily be manufactured e.g. by additive manufacturing. In the embodiment ofFIG.3the plate47has a convex lower surface. This can be useful for stiffening the plate47, since the thickness thereof increases moving radially from the periphery towards the center. However, other embodiments are possible. For example, the plate47can be flat (FIG.4). The stem49extends through the cover37such that an end49B of the stem49, opposite the plate47, is accessible from the exterior of the suction valve21for coupling to the actuator29. In use, the valve closing member45is controlled in a reciprocating motion according to double arrow f45by the actuator29. For better guidance of the valve closing member45during operation, the stem49can be slidingly movable in a guide59. In the embodiment ofFIG.3the guide59is in the form of a tubular guide, which can extend from the seat39to the cover37. The stem49may include one or more annular projections49C,49D, forming respective sliding surfaces, in sliding contact with the inner surface of the tubular guide59. Preferably, the annular projections49C,49D are distanced from one another along the axial extension of the stem49, such that better guidance is achieved. A smooth and efficient guiding action on the stem49is thus obtained and buckling of the stem during movement thereof is prevented. In some embodiments, along the tubular guide59and/or in the cover37a sealing arrangement61is provided. The sealing arrangement61can be mounted in an axial seat formed in the cover37and/or in the tubular guide59by means of a lock nut or any other suitable lock member63. The lock member63has an axial hole, through which the stem49extends, such that the distal end49B thereof projects outside the suction valve21for connection to the actuator29(seeFIG.5). By providing a sealing arrangement61within the tubular guide59and/or the cover37a compact valve is obtained, with a reduced axial length. The reduction of the axial extension of the valve members also reduces the total weight of the valve and the weight of the reciprocatingly moving part thereof, namely the valve closing member45. A gas recovery duct65can be integrated in the valve cage or casing. The gas recovery duct65is adapted to recover any gas leakage along the tubular guide59. By arranging the gas recovery duct65inside the structure of the valve cage a compact structure is obtained. The gas recovery duct65can end with a connection65A arranged outside the compressor cylinder and that can be fluidly coupled to a gas recovery circuit, not shown. In some embodiments, the cage33and the cover37of the suction valve21can be manufactured as a single monolithic block. In other embodiments, the cage33and the seat39, excluding the replaceable seat plate43, if provided, can be manufactured as a single monolithic body. In yet further embodiments, the cage33and the tubular guide59can be manufactured as a single monolithic body. In the exemplary embodiment shown herein, the cage33, including the posts35, the seat39, the tubular guide59and the cover37are formed as a single monolithic body, preferably in one and the same material, for instance metal. The replaceable seat plate43can be manufactured in a polymeric material or metallic material. The polymeric material being softer, impact forces generated by the valve closing member45are absorbed and a higher reliability is achieved. Wear is concentrated on the replaceable seat plate, which is less expensive than the valve closing member45. If a metallic material is used for manufacturing the replaceable seat plate43, the valve closing member45can be advantageously made of a polymeric material, for shock absorption and wear concentration purposes. Polymeric, rather than metallic material for manufacturing the valve closing member45is also beneficial in terms of reduced mass of such reciprocatingly movable member. In particularly advantageous embodiments, the above mentioned components of the suction valve21can be manufactured by additive manufacturing. Any additive manufacturing process suitable for the metal material used for this kind of component and adapted to achieve the desired final properties of the component can be used. In some embodiment, additive layer deposition, or powder bed fusion (PBF) can be used, such as by direct metal laser melting (DMLM), electron beam melting (EBM), directed metal laser sintering (DMLS), selective laser melting (SLM), selective laser sintering (SLS) or selective heat sintering (SHS). Other additive manufacturing processes are not ruled out. In other, presently less preferred embodiments, two or more sections or parts of the stationary components of the valve can be manufactured separately and then assembled to one another, e.g. by soldering or welding to obtain a final component. By integrating several components of the suction valve21in a single body, handling of the valve and assembling thereof in the compressor1become simpler and faster and require less technical expertise. The entire valve assembly, including the valve closing member45and the replaceable seat plate can be pre-assembled outside the cylinder, and subsequently mounted and fixed to the compressor cylinder by simply screwing bolts through holes37A of cover37(seeFIG.5). The above described exemplary suction valve is termed sometimes of the “open type”, since the valve closing member45faces directly the interior of the compression chamber. In other embodiments, the suction valve21can be of the so-called “closed type”. Suction valves of the closed type are provided with a guard, which is arranged in front of the valve closing member45, opposite the seat39. The plate47of the valve closing member45is thus reciprocatingly movable between the seat and the guard. With continuing reference toFIGS.1,2,3,4and5, a suction valve of the closed type is shown inFIG.6. The same reference numbers indicate the same parts as already described above in connection withFIGS.2,3,4and5; these parts will not be described again. The main difference between the valve of the open type shown inFIGS.1,2,3,4and5and the closed type valve ofFIG.6is that this latter includes a guard71provided with ports or apertures72, which are aligned with the ports or apertures51of the plate47of the valve closing member45. The plate47of the valve closing member45is adapted to move axially between the surface of the guard71facing the plate47and the replaceable seat plate43of the seat39, i.e. between an open position (plate47resting on guard71) and a closed position (plate47resting on the replaceable seat plate43). The guard71can be integral with the ferrule42which retains the replaceable seat plate43on the valve seat39. With continuing reference toFIG.1, an exemplary embodiment of a discharge valve23is shown, inFIG.7. The discharge valve23comprises a cage81with posts83which extend between a cover85and a seat87. The seat87is provided with a plurality of discharge apertures or ports89. The posts83can be connected to the seat87. The ports89of the seat87can be selectively opened and closed by a valve closing member91, also referred to as shutter, which is adapted to reciprocatingly move according to double arrow f91between an open position and a closed position. The valve closing member91comprises a plate93and a stem95. The plate93is provided with ports or apertures97which are offset with respect to the apertures or ports89, such that when the plate93is urged against the seat87the apertures89are closed by the plate93; when the plate93is distanced from the seat87compressed gas can flow through the apertures89and97towards the discharge plenum27of the compressor1. Similarly to what has been described in connection withFIGS.2,3,4and5, also in the discharge valve23pins (not shown) can be provided in order to mount the seat87and the valve closing member91in the correct mutual angular position, such that elongated and curved apertures or ports97and89will be in the correct mutual position. The stem95is slidingly housed in a tubular guide99and can project beyond the cover85, such that the end95A of the stem95can be coupled to the actuator31(FIG.1; not shown inFIG.7). Similarly to the stem49, also stem95can be provided with annular portions95A forming surfaces in sliding and guiding contact with the inner surface of the tubular guide99. A sealing arrangement100, similar to the sealing arrangement66, can be arranged in the tubular guide99. In some embodiments the cage21, the tubular guide99and possibly the cover85can be formed as a single monolithic body, for instance by additive manufacturing, or else by soldering or welding separate components (cover and cage) together. With continuing reference toFIG.1, a further embodiment of a suction valve is shown inFIG.8. The suction valve ofFIG.8is again labeled21as a whole. Also in the embodiment ofFIG.8the suction valve21includes a casing or cage133which has a set of posts135extending between a cover137and a seat139. The posts133can have portions which are perpendicular to the seat139and portions which are inclined and converge towards each other near the cover137. The seat139can include a plurality of suction apertures or ports141. The apertures141can be in the form of elongated and curved ports arranged according to circumferential concentric lines, coaxial with the valve axis A-A. The seat139can include a replaceable seat plate143, which is provided with ports or apertures146, having the same shape and position as the ports141. A ferrule142can be provided to mount the replaceable seat plate143on the seat139. The cover137can be provided with an annular groove137A adapted to receive an O-ring or any other gasket or sealing member, not shown, which provides a seal between the suction valve21and the compressor cylinder3when the valve is mounted. The suction valve21ofFIG.8further comprises a valve closing member, i.e. a shutter145. The valve closing member145comprises a plate147and a stem149. The plate147includes a plurality of apertures or ports151which are shifted with respect to the suction apertures141, such that the solid (non-perforated) portions of the plate147will close the suction apertures141when the valve closing member145is in the closed position, in abutment against the replaceable seat plate143. The valve closing member145can be manufactured as a single component, for instance by additive manufacturing. This may reduce manufacturing costs. In other embodiments, however, the plate147and the stem149can be manufactured separately and then bonded together, e.g. by welding, gluing, soldering, or else by way of screws or bolts. The stem149can be hollow (see hole149A), in order to reduce the mass and therefore the inertia thereof. As described above in connection with stem49, also stem149can include a honeycomb structure or other stiffening structure in the axial hole149A. Such structure can easily be manufactured e.g. by additive manufacturing. The stem149extends through the cover137such that an end149B of the stem149, opposite the plate147, is accessible from the exterior of the suction valve21for coupling to the actuator129. The stem149is slidingly movable in a tubular guide159, which can extend from the seat139to the cover137. The stem149may include one or more annular projections forming respective sliding surfaces, in sliding contact with the inner surface of the tubular guide159. In some embodiments, along the tubular guide149and/or in the cover137a sealing arrangement161is provided, similarly to other embodiments disclosed above. While the invention has been described in terms of various specific embodiments, it will be apparent to those of ordinary skill in the art that many modifications, changes, and omissions are possible without departing form the spirit and scope of the claims. In addition, unless specified otherwise herein, the order or sequence of any process or method steps may be varied or re-sequenced according to alternative embodiments. | 18,244 |
11859608 | DETAILED DESCRIPTION The detailed description set forth below in connection with the appended drawings is intended as a description of various configurations and is not intended to represent the only configurations in which the concepts described herein may be practiced. The detailed description includes specific details for the purpose of providing a thorough understanding of various concepts. However, it will be apparent to those skilled in the art that these concepts may be practiced without these specific details. In some instances, well known components are shown in block diagram form in order to avoid obscuring such concepts. In an aspect, the disclosure may provide for an enclosure assembly having a case cover that is usable with a pump, such as a positive displacement pump. The case cover may include one or more drainage channels that divert fluid away from the display of the case cover. The drainage channels may be disposed on an underside surface of the case cover, for example. In one example implementation, as fluid accumulates on or near the display, the fluid may enter the one or more drainage channels to be diverted away from the display. FIG.1illustrates a perspective view of an example of the case100(which may also encompass a pump drive, for example). In some implementations, the case100may include an enclosure assembly102and a base104. The enclosure assembly102and the base104may enclose mechanical, electrical, hydraulic, and/or other components. The case100may include a case cover106and a case body107. The case body107may include an opening that is covered by the case cover106. The case cover106may include a display108for displaying information related to the operation and/or status of the case100. The display108may be a touch sensitive display, such as a capacitive touch sensitive display, a resistive touch sensitive display, etc. The display108may be optionally framed by a bezel109of the case cover106. The case cover106and/or the display108may be configured to prevent fluid from interfering with the operation of the display108as described in more detail below. The case100may include a pump cover110configured to couple to a pump head (not shown inFIG.1). In an example implementation, the case cover106may include a diffuser114and one or more light emitting diode (LED) and/or other indicators112. The one or more indicators112may be disposed underneath the diffuser114. The diffuser114may diffuse, scatter, and/or distribute the light from the one or more indicators112. The one or more indicators112may be controlled by a LED array (not shown, discussed below). The one or more indicators112may be optionally covered by a light diffuser configured to diffuse the light from the one or more indicators112. The one or more indicators112may include organic LED, III-V LED, quantum dot LED, etc. The LED array may adjust (individually or together) the luminance intensities of the one or more indicators112, the illumination pattern (e.g., pulsing, blinking, flashing, continuous illumination, etc.) of the one or more indicators112, and/or the colors of the one or more indicators112. The one or more indicators112may be configured indicate the operation and/or status of the case100and/or one or more components of the case100. In one example, the one or more indicators112may be in an “off” (non-illuminating) state when the case100is in the off state, and on when the case100is in the on state. In another example, the one or more indicators112may flash to indicate to an operator that maintenance and/or inspection of the case100is necessary. In a third example, the one or more indicators112may illuminate light at a first color (e.g., blue) to indicate proper operation of the case100and a second color (e.g., red) to indicate improper operation of the case100. Other illuminations may be implemented. In certain implementations, the case cover106may be configured to include various features to divert fluid on or near (within 1 centimeter (cm), 2 cm, 3 cm, etc.) the case cover106and/or the display108away from the display108. The case cover106may include one or more drainage channels at an underside surface of the case cover106(discussed below). The one or more drainage channels may be configured to divert the fluid on or near the case cover106and/or the display108away from the display108. FIG.2illustrates a bottom view of an example of the case cover106without the display108illustrated (FIG.1). In certain implementations, the case cover106may include an underside surface202. One or more bosses204may be disposed on the underside surface202. The one or more bosses204may prevent the display108from being over-compressed (i.e., causing the display108to function improperly, such as delamination or discoloration) as discussed further below. The case cover106may include one or more drainage channels206a-206cconfigured to divert fluid on or near the case cover106and/or the display108, the diffuser114, and/or on the underside surface202of the case cover106, away from the display108. For example, the first drainage channel206amay diver fluid collecting near the diffuser114away from the diffuser114and/or the one or more indicators112(not shown). The second drainage channel206band the third drainage channel206cmay diver fluid collecting on or near the display108away from the display108. FIG.3illustrates a side view of the case cover106with the display108. In some implementations and referencingFIG.2, the display108may abut the underside surface202of the case cover106. In optional implementations, one or more gaskets may be emplaced for substantially sealing any gap between the underside surface202of the case cover106and the display108. Fluid accumulating, for example, on the surface of the display108, near the display108, near the diffuser114, and/or the on the case cover106may be diverted away via the drainage channels206a-206c. For example, fluid pooling near the display108may enter one or more of the drainage channels206a-206c. The fluid may travel in a direction302via one or more of the drainage channels206a-206c, so as to be drawn away from the display108(due to gravitational force, capillary effect, etc.). FIG.4illustrates an underside or bottom view of the case cover106with the display108and a frame plate402shown. In one example implementation, the frame plate402may encapsulate at least a portion of the display108. At least a portion of the display108may thereby be disposed between the case cover106and the frame plate402. One or more fasteners404may fasten the frame plate402to the case cover106. The one or more fasteners404may be or include screws, nails, bolts, battens, buckles, clamps, clips, pegs, pins, etc. In one example, the one or more fasteners404may be mateably inserted (e.g., screwed) into the one or more bosses204(FIG.2). The one or more bosses204may prevent the frame plate402from over-compressing the display108, thus avoiding the display108being distorted, delaminated, and/or discolored. The frame plate402, when encapsulating the display108, may reduce and/or prevent fluid, moisture, debris, and/or other contaminants from contacting or remaining contact with the display108. In an implementation, the frame plate402may include electrical connections for the display108. The electrical connections may transfer data from an external device to the display108or data from the display108to the external device. In certain example implementations, fluid accumulating on or near the display108, on or near the one or more indicators112, on or near the diffuser114, and/or on or near the frame plate402may enter the one or more drainage channels206a-206c. The one or more drainage channels206may thereby divert the fluid away from the display108, the one or more indicators112, the diffuser114, and/or the frame plate402. FIG.5illustrates a side view of the case cover106with the display108and the frame plate402shown emplaced relative thereto. In some implementations and referencingFIG.8, the display108may abut the underside surface202of the case cover106. In optional implementations, one or more gaskets for substantially sealing any gap between the underside surface202of the case cover106and the display108. Fluid accumulating on and/or near the display108, near the diffuser114, on and/or near the frame plate402, and/or the on the case cover106may be diverted away via the drainage channels206a-206c. For example, fluid pooling near the display108may enter one or more of the drainage channels206a-206c. The fluid may travel in a direction302away from the display108(due to gravitational force, capillary effect, etc.). FIG.6illustrates a perspective view of the enclosure assembly102and the case cover106of the case100, along with a close-up cross-sectional view of a portion of the assembly102. In some implementations and referencingFIG.8, the case cover106or the enclosure assembly102may include a gasket602. The gasket602may prevent fluid from entering the case100where the gasket602is present. In one example implantation, a subjection delineated by arrows604of the case cover106may not contact the enclosure assembly102directly or via any gasket. As such, a gap606may exist between the case cover106and the case body107the enclosure assembly102. During operation, for example, fluid accumulating on and/or near the display108, on and/or near the diffuser114, on and/or near the frame plate402, and/or the on the case cover106may be diverted away via the drainage channels206a-206c. The accumulated fluid may enter one or more of the drainage channels206a-206c. The fluid may travel in a direction302away from the display108, the diffuser114, the frame plate402, and/or the case cover106(due to gravitational force, capillary effect, etc.). The fluid may exit the drainage channels206a-206cand trickle onto the pump cover110of the case100. In optional implementations, the pump cover110may include tubes, other drainage channels, pipes, or other devices configured to divert the fluid exiting the drainage channels206a-206caway from the case100. FIG.7illustrates a rear view of the case100ofFIG.1. In certain implementations, the case100may include an interface panel700. The interface panel700may be mounted onto the base104. The interface panel700may include one or more electrical ports, connectors, and/or switches. In one illustrative implementation, the interface panel700may include a Universal Serial Bus (USB) port702, an Ethernet port704, and a Profibus port706(e.g., a DB9 Profibus port). The interface panel700may include a power switch708to turn the case100“on” or “off” The interface panel700may include an electrical power receptacle710. The interface panel700may include one or more sensor connectors712configured to electrical connect to one or more sensors (e.g., temperature sensors, etc.). In other implementations, the interface panel700may include one or more serial ports, parallel ports, phone jack ports, Interbus ports, Controller Area Network (CAN) ports, Firewire ports, and/or other ports. FIG.8illustrates a perspective view of an example of drive components800disposed on the base104. Some or all of the drive components800may be mounted to the base104. In some implementations, the enclosure assembly102(FIGS.1and4) may incorporate the pump cover110, rather than the pump cover110being separate, as shown inFIG.8. The pump cover110may include one or more bosses814configured to physically mate and/or couple to a pump head (not shown). The pump cover110may include a flange member812configured to connect to a fluid channel of the pump head (not shown inFIG.8). In some implementations, the drive components800may include a gear case assembly820. The gear case assembly may be coupled to the pump cover110. The drive components800may include a motor822configured to drive the pump head (not shown). The drive components800may optionally include a power supply (not shown) configured to convert the line voltage (e.g., 120 volt or 240 volt) to a direct current (DC) or alternative current (AC) voltage utilized by the drive components800for operation. In an implementation, and also referencing various features shown inFIG.1, an edge830of the base104may optionally include a lip832as shown in the cross-sectional view of the edge830. The lip832may be configured to mateably coupled to an edge of the enclosure assembly102(FIG.1). The lip832may prevent fluid from leaking into the inside of the case100(FIG.1), for example. The lip832may be disposed toward the outside surface of the base104, toward the inside surface of the base104, or in between the outside surface and the inside surface of the base104(as shown). FIG.9is a representative schematic diagram of an example network environment900in which a positive displacement pump910having a housing and other features, in accordance with aspects of the present disclosure, may be utilized. The network environment900may include a user device920(examples of which may also interchangeably be referred to herein as “terminals”) for providing a user interface to a user, a communication network930for transmitting various communications among devices as described herein, a command server940for publishing commands to one or more positive displacement pumps910, an application server950for providing an application to the user device920, and a database server960for storing data reported by one or more positive displacement pumps910and user devices920. The positive displacement pump910may be a positive displacement pump including communications hardware (e.g., network interface) and software described herein for providing remote control of the positive displacement pump910. In an aspect, the positive displacement pump910may operate in either a local mode, in which a local user interface is used to control operation of the positive displacement pump910, or a remote mode, in which commands received via a network interface are used to control operation of the positive displacement pump910. The term “positive displacement pump” as used herein describes a category of fluid pumps that may contain or “trap” a fixed amount of fluid, such as within a portion of flexible tubing (e.g., a peristaltic pump), and force the contained or trapped fluid to a discharge pipe. Positive displacement pumps are conventionally used in processes that require precise measurement or dosing of fluid. Positive displacement pumps may be driven by an electric motor under the control of a controller (e.g., electronic control unit (ECU) and/or other processor) that moves fluid at a desired rate. In an aspect, a positive displacement pump may include a detachable pumphead that includes a casing and fluid contacting components of the positive displacement pump. The pumphead may be driven by the motor via a magnetic coupling, for example. The positive displacement pump may be fitted with variable pumpheads, depending on the desired operation. For example, in an aspect, a positive displacement pump may include a housing including the drive motor, controller, and user interfaces, and a detachable pumphead may be fitted in or on the housing. The selection of different pumpheads may configure the positive displacement pump910as, for example, one of a peristaltic pump, gear pump, or diaphragm pump. Examples of a positive displacement pump and/or a pumphead may be found in U.S. Pat. No. 10,578,096, the contents of which are hereby incorporated by reference in their entireties. The user device920may include various computing devices that may be used to access an application via a web interface. For example, the user device920may be or include any mobile or fixed computer device, including but not limited to a desktop or laptop or tablet computer, a cellular telephone, a gaming device, a mixed reality or virtual reality device, a music device, a television, a navigation system, a camera, a personal digital assistant (PDA), a handheld device, or any other suitable computer device having wired and/or wireless connection capability with one or more other devices. The user device920may include a processor that executes an operating system and one or more applications. In an aspect, the user device920may execute a dedicated application for providing a user interface to the pump control application server950. In another aspect, the user device920may execute a web browser application to access a webpage providing a user interface to the pump control application server950. In an aspect, the user device920may be configured for secure communication with the application server950. For example, the user device920may install a certificate of the application server950allowing device verification and encrypted communications. The communication network930may be or include a computer network that allows communication among various devices. For example, the communication network930may include the Internet and may transmit data packets according to the Internet protocol. As illustrated, the communication network930may include the command server940, application server950, and database server960. In an aspect, the command server940, application server950, and database server960may be implemented using a cloud architecture. For example, the command server940, application server950, and database server960may each be implemented as a virtual server to be provided by a cloud services provider. The cloud service provider may generate instances of the virtual servers using geographically dispersed computing hardware. A cloud architecture may provide scalability, load balancing, stability against network interruptions, and redundancy of stored data, among other features. It should be appreciated that the command server940, application server950, and database server960may also be implemented using conventional computer servers configured to execute the programs described herein. The command server940may include one or more computer servers configured to publish commands to one or more positive displacement pumps910, for example. In an aspect, the command server940may use a publish-subscribe based messaging protocol. For example, the command server940may use Message Queuing Telemetry Transport (MQTT) protocol. In an aspect, the use of a publish-subscribe based messaging protocol may provide security by having the positive displacement pumps910establish a connection to a known server, rather than accepting a connection from potentially different sources. The command server940may publish commands to control the positive displacement pumps910. The control may include commands for the positive displacement pump910to provide information. The commands may be associated with a command string or topic, which may include an identifier (i.d.) of the positive displacement pump910that should execute the command. The i.d. may be, for example, a media access control (MAC) address of the positive displacement pump910. The commands may also include one or more parameters for executing the command. Table9, below, includes a listing of example commands that may be used with a positive displacement pump910. TABLE 1TOPICDESCRIPTIONmflx/id/sts/onlinePowerup and Last Will Topic,message = “true” or “false”mflx/id/sts/UptimeTime since power up and Date/Time. JSONmflx/id/sts/InfoRPM, Model, Adapter andConnection. JSONmflx/id/sts/RunStatusJSONtrue = pump motor on,false = pump motor offtrue = dispense on,false = dispense offtrue = sensor open,false = sensor closederror code (0 = status OK)mflx/id/sts/FlowDirFlow direction, “CW” or “CCW”mflx/id/sts/RemCont“1” = Remote, “0” = Localmflx/id/sts/DispMode“Continuous”, “Time” or “Volume”mflx/id/sts/TubeSize and calibration status in JSON“1”, “2”, . . . , “N” where N = lasttube size selection false = tube notcalibrated, true = calibratedmflx/id/sts/FlowUnits“1”, “2”, . . . , “N” where N = lastflow units selectionmflx/id/sts/CumVolCumulative volume (Text string offloat number)mflx/id/sts/RemDispRemaining dispense volume andtime in JSONmflx/id/sts/BatchCountBatch Count current and total inJSONmflx/id/sts/FlowRateCurrent, Min and Max flow ratesin JSONmflx/id/sts/Request to server to send UnixNeedTimestampTimestamp (no message) The command server940may implement a program for a positive displacement pump910by publishing commands. For example, the command server940may receive a selection of a program from the application server950. The selected program may include a series of commands and parameters. The command server940may publish the commands at the appropriate time to control the positive displacement pump910to operate according to the program. Additionally, the command server940may receive feedback from the positive displacement pump910(e.g., in response to a Get command). The command server940may evaluate conditions based on the feedback for executing the program. In an aspect, the command server940may be implemented as a remote server that provides commands for multiple positive displacement pumps910, which may be owned by different organizations, for example. In another aspect, a local command server may be implemented (e.g., by an organization) to allow control of local positive displacement pumps910. For example, a command server940may be implemented on a user device920and communicate via a local area network (LAN) or other short-range communication protocol. Application server950may include one or more computer servers configured to provide a user interface accessible via a user device920. The application server950may communicate with dedicated applications executing on user devices920or may provide a web-based interface accessible via a web browser, for example. As described in further detail below, in one or more example implementations, the user interface provided by the application server may allow a user to configure one or more positive displacement pumps for operation. The application server950may also perform monitoring of the positive displacement pumps910and provide alerts to the user devices920. The user interface may allow the user device920to configure which alerts to receive and how the alerts are received (e.g., via application notification, text, or email). Database server960may store information collected from one or more positive displacement pumps910via the command server940. The database server960may provide data security and integrity protection, for example. In an aspect, the database server960may collect and store data that may be reported to regulatory agencies, for example, as evidence of laboratory processes. The database server960may provide data security using secure socket layer (SSL) certificates to encrypt data between the pumps910and the database server960. Additionally, access to the database server960, as well as the application server950and command server940, may be controlled using authenticated user names and passwords, for example. Actions on any of the servers may be attributed to a specific user. The database server960may generate an audit trail indicating which users performed actions at which time. Further, because the pumps910may be operated in either local mode or remote mode, the database server960may track actions taken in local mode even if a registered user is not identified. For example, the actions performed in local mode may therefore be attributed to a local user. The database server960may segregate data of multiple customers. For example, a customer (e.g., a laboratory, corporation, or other entity), may have access only to data associated with devices belonging to the customer. A customer may designate multiple registered users (e.g., employees), who may access data based on user role. For example, the database server960may allow access to users based on a security level. For instance, an administrator may be able to configure database storage, export data, annotate data, and generate audit reports, while a regular user may only be able to read or export data. Additionally, a system administrator may not be associated with any customer and may at least read any data. FIG.10is a representative schematic diagram of an example positive displacement pump910usable in accordance with aspects of the present disclosure. The positive displacement pump910may include a wet end1020and a case100. The wet end1020may include fluid handling components including a pumphead1022, a liquid supply1024, an inlet tube1026, and an outlet tube1028. The wet end1020may be detachable from the case100to allow replacement or substitution of the wet end1020. For example, different pumpheads1022may be selected for use in pumping different fluids. The pumphead1022may include a mechanism for pumping fluid. In an aspect, the positive displacement pump910may use a pumphead that allows precise monitoring of the fluid being pumped (e.g., volume pumped). Example pumpheads may include a peristaltic pumphead, a quaternary diaphragm pumphead, and/or a gear pumphead. The pumphead1022may be connected to a liquid supply1024via an inlet tube1026. The pumphead1022may pump the fluid to the outlet tube1028. In an aspect, for example, using a peristaltic pump, the inlet tube1026and the outlet tube1028may be or include a continuous tube extending through the pumphead1022. The case100may include electronic components of the positive displacement pump910. For example, the case100may include a network interface1032, a local user interface1034, a drive motor1040, a processor1050, a memory1052, and a leak sensor1054. Further, the memory1052may store instructions executable by the processor1050for implementing a pump controller1060, which may include a motor controller1062, a command module1064, and a reporting module1066. The network interface1032may include a wired or wireless network interface for transmitting and receiving data packets. In an aspect, the network interface1032, for example, may utilize transmission control protocol/Internet protocol (TCP/IP) packets that may carry commands, parameters, or data. For example, the network interface1032may receive MQTT messages including the commands listed in Table1above. The network interface1032may forward commands to the processor1050for processing by the pump controller1060. Conversely, the network interface1032may receive data generated by the pump controller1060from the processor1050and transmit the data to the command server940. The local user interface1034may include any suitable controls provided on the positive displacement pump910for controlling the positive displacement pump910. In an aspect, the local user interface1034may include a display screen that presents menus for selecting commands similar to the commands transmitted by the command server940. In another aspect, the local user interface1034may include dedicated buttons and/or other selection features that perform specific commands. For example, the local user interface1034may include a button for selection to start/stop pumping. The local user interface1034may generate commands to the processor1050for processing by the pump controller1060. As noted above, the positive displacement pump910may operate in a remote mode in which the local user interface1034is at least partially disabled to prevent local input. The drive motor1040may be or include an electric motor that provides a force for pumping the fluid. In an aspect, the drive motor1040may be magnetically coupled to the pumphead1022to drive the pumphead1022. The drive motor1040may be controlled by the pump controller1060. For example, the pump controller1060may generate a control signal indicating a speed and direction of the drive motor1040based on received commands. The processor1050may include one or more processors for executing instructions. An example of processor1050may include, but is not limited to, any suitable processor specially programmed as described herein, including a controller, microcontroller, application specific integrated circuit (ASIC), field programmable gate array (FPGA), system on chip (SoC), or other programmable logic or state machine. The processor1050may include other processing components, such as an arithmetic logic unit (ALU), registers, and a control unit. The processor1050may include multiple cores and may be able to process different sets of instructions and/or data concurrently using the multiple cores to execute multiple threads, for example. Memory1052may be configured for storing data and/or computer-executable instructions defining and/or associated with the pump controller1060, and processor1050may execute such instructions with regard to operation of the pump controller1060. Memory1052may represent one or more hardware memory devices accessible to processor1050. An example of memory1052can include, but is not limited to, a type of memory usable by a computer, such as random access memory (RAM), read only memory (ROM), tapes, magnetic discs, optical discs, volatile memory, non-volatile memory, and any combination thereof. Memory1052may store local versions of a pump controller application being executed by processor1050, for example. Leak sensor1054may be or include a hardware leak sensor that detects whether liquid is leaking within or from the positive displacement pump910. For example, a leak may occur when a component of the wet end1020fails or becomes detached. In such a situation, the inlet tube1026or the outlet tube1028may rupture or become detached from the pumphead1022. In an aspect, the leak sensor1054may include an electronic mesh that forms a circuit when liquid is present. The leak sensor1054may be coupled to the processor1050, which may generate a stop command to stop operation of the positive displacement pump910in response to the leak sensor1054detecting a leak. Stopping the positive displacement pump910may prevent damage to the pump and waste of a fluid, for example. Further, a notification of the leak may be used to abort or modify a process using the positive displacement pump910. The pump controller1060may control operation of the positive displacement pump910based on commands received from either the network interface1032or the local user interface1034, for example. The pump controller1060may include a motor controller1062for controlling operation of the drive motor1040, a command module1064for interpreting and executing received commands, and/or a reporting module1066for monitoring pump operation and reporting data regarding the positive displacement pump910. Aspects of the present disclosure may be implemented using hardware, software, or a combination thereof and may be implemented in one or more computer systems or other processing systems. In one aspect, the disclosure is directed toward one or more computer systems capable of carrying out the functionality described herein.FIG.11presents an example system diagram of various hardware components and other features that may be used in accordance with aspects of the present disclosure. Aspects of the present disclosure may be implemented using hardware, software, or a combination thereof and may be implemented in one or more computer systems or other processing systems. In one example variation, aspects of the disclosure are directed toward one or more computer systems capable of carrying out the functionality described herein. An example of such a computer system1100is shown inFIG.11. Computer system1100includes one or more processors, such as processor1104. The processor1104is connected to a communication infrastructure1106(e.g., a communications bus, cross-over bar, or network). Various software aspects are described in terms of this example computer system. After reading this description, it will become apparent to a person skilled in the relevant art(s) how to implement aspects of the disclosure using other computer systems and/or architectures. Computer system1100may include a display interface1102that forwards graphics, text, and other data from the communication infrastructure1106(or from a frame buffer not shown) for display on a display unit1130. Computer system1100also includes a main memory1108, preferably random access memory (RAM), and may also include a secondary memory1110. The secondary memory1110may include, for example, a hard disk drive1112and/or a removable storage drive1114, representing a floppy disk drive, a magnetic tape drive, an optical disk drive, etc. The removable storage drive1114reads from and/or writes to a removable storage unit1118in a well-known manner. Removable storage unit1118, represents a floppy disk, magnetic tape, optical disk, etc., which is read by and written to removable storage drive1114. As will be appreciated, the removable storage unit1118includes a computer usable storage medium having stored therein computer software and/or data. In alternative aspects, secondary memory1110may include other similar devices for allowing computer programs or other instructions to be loaded into computer system1100. Such devices may include, for example, a removable storage unit1122and an interface1120. Examples of such may include a program cartridge and cartridge interface (such as that found in video game devices), a removable memory chip (such as an erasable programmable read only memory (EPROM), or programmable read only memory (PROM)) and associated socket, and other removable storage units1122and interfaces1120, which allow software and data to be transferred from the removable storage unit1122to computer system1100. Computer system1100may also include a communications interface1124. Communications interface1124allows software and data to be transferred between computer system1100and external devices. Examples of communications interface1124may include a modem, a network interface (such as an Ethernet card), a communications port, a Personal Computer Memory Card International Association (PCMCIA) slot and card, etc. Software and data transferred via communications interface1124are in the form of signals1128, which may be electronic, electromagnetic, optical or other signals capable of being received by communications interface1124. These signals1128are provided to communications interface1124via a communications path (e.g., channel)1126. This path1126carries signals1128and may be implemented using wire or cable, fiber optics, a telephone line, a cellular link, a radio frequency (RF) link and/or other communications channels. In this document, the terms “computer program medium” and “computer usable medium” are used to refer generally to media such as a removable storage drive1114, a hard disk installed in hard disk drive1112, and signals1128. These computer program products provide software to the computer system1100. Aspects of the disclosure are directed to such computer program products. Computer programs (also referred to as computer control logic) are stored in main memory1108and/or secondary memory1110. Computer programs may also be received via communications interface1124. Such computer programs, when executed, enable the computer system1100to perform various features in accordance with aspects of the present disclosure, as discussed herein. In particular, the computer programs, when executed, enable the processor1104to perform such features. Accordingly, such computer programs represent controllers of the computer system1100. In variations where aspects of the disclosure are implemented using software, the software may be stored in a computer program product and loaded into computer system1100using removable storage drive1114, hard disk drive1112, or communications interface1120. The control logic (software), when executed by the processor1104, causes the processor1104to perform the functions in accordance with aspects of the disclosure as described herein. In another variation, aspects are implemented primarily in hardware using, for example, hardware components, such as application specific integrated circuits (ASICs). Implementation of the hardware state machine so as to perform the functions described herein will be apparent to persons skilled in the relevant art(s). In yet another example variation, aspects of the disclosure are implemented using a combination of both hardware and software. FIG.12is a block diagram of various example system components (e.g., on a network) that may be used in accordance with aspects of the present disclosure. The system1200may include one or more accessor1260(also referred to interchangeably herein as one or more “users”) and one or more terminals1242,1266(which may be the case100in an example). The accessor1260may correspond to user devices920(FIG.9). In one aspect, data for use in accordance with aspects of the present disclosure may, for example, be input and/or accessed by accessor1260via terminals1242,1266, such as personal computers (PCs), minicomputers, mainframe computers, microcomputers, telephonic devices, or wireless devices, such as personal digital assistants (“PDAs”) or a hand-held wireless devices coupled to a server1243, such as a PC, minicomputer, mainframe computer, microcomputer, or other device having a processor and a repository for data and/or connection to a repository for data, via, for example, a network1244, such as the Internet or an intranet, and couplings1245,1246,1264. The couplings1245,1246,1264include, for example, wired, wireless, or fiber optic links. In another example variation, the method and system in accordance with aspects of the present disclosure operate in a stand-alone environment, such as on a single terminal. The aspects of the disclosure discussed herein may also be described and implemented in the context of computer-readable storage medium storing computer-executable instructions. Computer-readable storage media includes computer storage media and communication media. For example, flash memory drives, digital versatile discs (DVDs), compact discs (CDs), floppy disks, and tape cassettes. Computer-readable storage media may include volatile and nonvolatile, removable and non-removable media implemented in any method or technology for storage of information such as computer readable instructions, data structures, modules or other data. In some aspects, an enclosure assembly of a pump may include a case cover coupled to the enclosure assembly via a gasket, wherein the case cover and the enclosure assembly form a gap between the case cover and the enclosure assembly in a portion of the case cover without the gasket, a display, a plurality of bosses, a frame plate removable fastened to the plurality of bosses, wherein the display is fixedly attached to the case cover when the frame plate is fastened to the plurality of bosses, and one or more drainage channels disposed at an underside surface of the case cover, the one or more drainage channels being configured to divert fluid away from the display via the gap. Any of the enclosure assembly above, wherein the plurality of bosses prevent the display from being over-compressed by the frame plate. Any of the enclosure assembly above, wherein first ends of the one or more drainage channels are closer to the display than second ends of the one or more drainage channels and the first ends are higher than the second ends. Any of the enclosure assembly above, further comprising a base including a pump cover configured to fluidically couple to the pump. Any of the enclosure assembly above, wherein the one or more drainage channels are further configured to divert the fluid toward the pump cover. Any of the enclosure assembly above, further comprising one or more light emitting diode (LED) indicators and a diffuser configured to diffuse lights from the one or more indicators. Any of the enclosure assembly above, wherein the display is a touch-sensitive display. Some aspects of the present disclosure includes a case for a pump assembly including a base, an enclosure assembly having a case cover coupled to the enclosure assembly via a gasket, wherein the case cover and the enclosure assembly form a gap between the case cover and the enclosure assembly in a portion of the case cover without the gasket, a display, a plurality of bosses, a frame plate removable fastened to the plurality of bosses, wherein the display is fixedly attached to the case cover when the frame plate is fastened to the plurality of bosses, and one or more drainage channels disposed at an underside surface of the case cover, the one or more drainage channels being configured to divert fluid away from the display via the gap. Any of the case above, further comprising a pump head, wherein the base comprises a pump cover configured to fluidically couple to the pump head. Any of the case above, wherein the one or more drainage channels are further configured to divert the fluid toward the pump cover. Any of the case above, wherein the base comprises a motor configured to drive the pump head. Any of the case above, wherein the base comprises a lip configured to mateably couple to an edge of the enclosure assembly to prevent fluid from entering the case. Any of the case above, wherein the base comprises an interface panel including one or more electrical ports. Any of the case above, wherein the one or more electrical ports include at least a Universal Serial Bus port, an Ethernet port, a Profibus port, a serial port, a parallel port, a phone jack port, an Interbus port, a Controller Area Network (CAN) port, or a Firewire port. Any of the case above, wherein the plurality of bosses prevent the display from being over-compressed by the frame plate. Any of the case above, wherein first ends of the one or more drainage channels are closer to the display than second ends of the one or more drainage channels and the first ends are higher than the second ends. Any of the case above, wherein the enclosure assembly further comprises one or more light emitting diode (LED) indicators and a diffuser configured to diffuse lights from the one or more indicators. Any of the case above, wherein the display is a touch-sensitive display. This written description uses examples to disclose aspects of the present disclosure, including the preferred embodiments, and also to enable any person skilled in the art to practice the aspects thereof, including making and using any devices or systems and performing any incorporated methods. The patentable scope of these aspects is defined by the claims, and may include other examples that occur to those skilled in the art. Such other examples are intended to be within the scope of the claims if they have structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal language of the claims. Aspects from the various embodiments described, as well as other known equivalents for each such aspect, can be mixed and matched by one of ordinary skill in the art to construct additional embodiments and techniques in accordance with principles of this application. | 43,118 |
11859609 | Where applicable, like reference characters designate identical or corresponding components and units throughout the several views, which are not to scale unless otherwise indicated. The embodiments disclosed herein may include elements that appear in one or more of the several views or in combinations of the several views. Moreover, methods are exemplary only and may be modified by, for example, reordering, adding, removing, and/or altering the individual stages. DETAILED DESCRIPTION The discussion that follows describes embodiments of a device that connects a pump head with a pump. This arrangement is typical of construction found at an additive pump or pump station. But it's possible that the concepts could translate to other types of devices that are in need of similar features as well. In this regard, the device uses a two-piece design. A first piece connects the pump head with the pump. A second piece inserts into the first piece. This second piece is configured to extend into the pump head, for example, outside of the first piece so as to position an o-ring (or like sealing member) in contact with the pump head. Other embodiments are within the scope of this disclosure. FIG.1depicts, schematically, an exemplary embodiment of a sealed connection device100. The embodiment is shown as part of a pump, identified generally by the numeral10. Examples of the pump10may have a pump head12that couples with a conduit14that carries material16. The pump head12may also couple with a supply18that provides an additive20. The pump10may include a motive unit22, possibly an electric motor or a pneumatic cylinder. A shaft24may couple with the motive unit22. The shaft24may extend through the sealed connection device100to locate its end proximate the pump head12. In operation, the motive unit22moves the shaft24to operate the pump head12to disperse the additive20into the conduit14. The sealed connection device100may form a sealed interface102with the pump head12. On its inside, the sealed connection device100may form a sealed region103to contain leaks of additive20that may migrate down the shaft24(toward the motive unit22). Broadly, the sealed connection device100may simplify construction of the pump10. To date, practice in the field prescribes devices with multiple pieces to support and seal reciprocating shafts in additive pumps. The sealed interface102and sealed region103are constructed to offer a unique solution that replaces these pieces with a single, robust member. This feature may effectively reduce manufacturing costs and, at the same time, prolong operating life of the seals. FIG.2depicts a schematic diagram of an example of structure for the sealed connection device100ofFIG.1to facilitate the sealed interface102. This structure includes a sealed collar104that resides in an adapter106that is useful to couple the pump head12to the motive unit22. The sealed collar104can receive and support the shaft24as it reciprocates under load from the motive unit22. At the sealed interface102, the sealed collar104extends into the pump head12. The adapter106may also receive part of the pump head12to form an overlapping region110, where structure of these components mesh or mate with one another. This configuration forms a direct seal108between sealed collar104and the pump head12. FIG.3depicts a perspective view of exemplary structure for the sealed connection device100in exploded form. Starting on the left-hand side of the digram, the sealing collar104may have a collar body112, shown here as an elongate cylinder or with cylindrical form factor that can be fashioned as a single piece of material or, otherwise, of unitary or monolithic design. The collar body112may have a through-bore114that forms a longitudinal axis116and a pair of open ends (e.g., a first open end118and a second open end120). The collar body112may also have an outer surface122with a stepped profile124defined by a dimension D1(for example, a diameter for cylinders or annular pieces,) as measured from the longitudinal axis116. In one implementation, the stepped profile124may form at least one shoulder126that separates the outer surface122into two regions (e.g., a first region128and a second region130). The diameter D1in the regions128,130is smaller than the diameter D1at the shoulder126. Grooves132that circumscribe the longitudinal axis116may populate the outer surface122of the collar body116, including at the shoulder126and in the regions128,130. In addition, the collar body116may include an annular detent134, shown here in the second region130and adjacent the shoulder126. One or more apertures136may reside in the annular detent134. The apertures136may be spaced annularly apart from one another about the longitudinal axis116. The sealing collar104may be configured with one or more components so that fluid cannot migrate out of the device. These components may include annular seals138like elastomeric o-rings (e.g., a first o-ring140, a second o-ring142, and a third o-ring144). On either end118,120, the collar body112may accommodate radial seals (e.g., a first radial seal146and a second radial seal148). The o-rings140,142,144may assemble into the grooves132so as to circumscribe the collar body112. Examples of the radials seals146,148may engage with the shaft24but allow for moveable contact so that the shaft24can reciprocate (or rotate) along the longitudinal axis116as noted herein. The adapter106may be configured to receive the sealing collar104. This configuration may have an adapter body150. This piece may also be fashioned unitarily with a cylindrical form factor. The adapter body150may have a through-bore152that forms a longitudinal axis154and open ends (e.g., a first open end156and a second open end158). Its outer surface160has a stepped profile162featuring two sections (e.g., a distal section164and a proximal section166) defined by a dimension D2(also a diameter for purposes of the cylindrical form factor) as measured from the longitudinal axis154. In one implementation, the diameter D2of the distal section164is larger than the diameter D2of the proximal section166. Apertures168and grooves170may populate the distal section164. FIG.4depicts an elevation view of the cross-section of the side of the adapter body150ofFIG.3. The through-bore152may have a stepped inner surface172typical of variations in diameter along the longitudinal axis154. These variations may define a pair of distal counterbores (e.g., a first counterbore174and a second counterbore176) that terminate at a first landing surface178. An interior thread relief180may interpose between the counterbores174,176. The inner surface172may also include a third or medial counterbore182of smaller diameter (than the counterbores174,176). The third counterbore182may extend from the landing surface178to a second landing surface184. The stepped inner surface172may terminate at a fourth or proximal counterbore186at the end of the adapter body156in the proximal section166. As also shown, the apertures168may be configured to extend through the material of the adapter body150to the through-bore152. These configurations may have a multi-diameter profile that reduces in size from the outer surface160toward the through-bore152. FIG.5depicts an elevation view of the cross-section from the side of the collar body112ofFIG.3. The through-bore114may have a stepped inner surface188of varying diameter along the longitudinal axis116. This variable diameter may define a pair of counterbores (e.g., a first counterbore190and a second counterbore192) at the ends132,134. As also shown, the apertures136may penetrate the material of the collar body112to allow access to the through-bore114. FIG.6shows an elevation view of the side, cross-section of the sealed connection device ofFIG.3in assembled form. The sealing collar104inserts into the through-bore152of the adapter body150. Contact between the end120and the second landing surface184may set the appropriate position of the collar body112in the adapter body150. When assembled, part of the first region128of the collar body112may reside outside of the distal section164of the adapter body150. This configuration may locate the first o-ring140outside of the adapter body150. The second region130of the collar body112resides extensibly in the distal section164of the adapter body150. This location orients the annular detent134in longitudinal alignment with the apertures168. The collar body112may orient so that the apertures136align with the apertures168as well, but this is not necessary for operation of the device. The location also places o-rings142,144in contact with the adapter body150in the counterbores176,182. This feature creates the sealed region103with fluid barriers (e.g., the o-rings142,144) on either side of the annular detent134. In use, additive that migrates into the through-bore114(for example, because the radial seal146fails) can exit through the aperture136to the annular detent134. The additive can flow from there to the apertures168in the annular body150, which may couple with conduit to direct the additive back into the pump10(FIG.1). The sealed region103prevents further migration from the adapter body150. FIG.7depicts a perspective view of exemplary structure for the pump10that includes the sealed connection device100ofFIG.3. The pump structure may utilize piece parts with appropriate fit and function. The concepts herein, however, may accommodate different variations of this structure because the pump10may operate across a wide range of applications that might nominally require changes, updates, and revisions in the design. In this regard, the pump head12may have pump body26with a valve stem28and a pair of connectors (e.g., a first connector30and a second connector32) disposed thereon. The connectors30,32may connect with the conduit14and the supply18, respectively. The motive unit22may include a housing34that terminates at a mounting plate36. As shown, the sealed connection device100may be configured to interpose between the pump body26and the housing34. This configuration may operate as an option on these types of devices, for example, for use with additives that might be caustic or hazardous materials. The option may outfit the pump10to address environmental regulations or specifications that require “extra” containment measures to prevent leaks of these materials. To accommodate, the sealed connection device100may releasably engage with the body26and housing34. Threaded connections may benefit the device for this purpose so as to allow the pump body26and the housing34to thread onto or into the adapter body150. FIG.8depicts an elevation view of the side, cross-section of the pump10ofFIG.7to discuss such configurations. The proximal section166of the adapter body150may insert into the housing34. Corresponding threads on outer surface160may engage a threaded bore of the housing34may be useful for this purpose. A nut194may thread onto the proximal section166of the adapter body150. When tightened against the housing34, the nut196may operate to lock and prevent annular rotation of the adapter body150relative to the housing34. At the pump head12, the sealed interface102may receive a part38of the pump body26that inserts into the first counter bore174of the adapter body150. The part38may have an outer surface40that is threaded to mate with complimentary threads of the first counter bore174. On the inside, the part38may include a bore42that ends at a terminable face44. Assembly of the device may require the part38to screw into the adapter body150so as to cause the end118of the collar body112to contact the terminable face44. The threaded connection may cause a slight compressive loading to “squeeze” the collar body112between the terminable face44(on the first end118) and the second landing surface184(on the second end120). When assembled, the exposed portion of the collar body112resides inside of the part38of the pump body10. This configuration places the first o-ring140in contact with the bore42of the part38. In light of the foregoing, the embodiments are useful to re-circulate additive from around the shaft in the elongate cylindrical body. This feature can contain the additive within the device (or, generally, the additive pump) to avoid leaks or spills so that the device aligns with environmental regulations or standards. Unlike conventional designs, though, the improvements herein simply construction. The elongate cylindrical body employs unitary construction to eliminate unnecessary additional parts. This construction also operates to seal directly with the pump head, which is nominally not found in prior designs. This written description uses examples to disclose the invention, including the best mode, and also to enable any person skilled in the art to practice the invention, including making and using any devices or systems and performing any incorporated methods. An element or function recited in the singular and proceeded with the word “a” or “an” should be understood as not excluding plural said elements or functions, unless such exclusion is explicitly recited. References to “one embodiment” of the claimed invention should not be interpreted as excluding the existence of additional embodiments that also incorporate the recited features. Furthermore, the claims are but some examples that define the patentable scope of the invention. This scope may include and contemplate other examples that occur to those skilled in the art. Such other examples are intended to be within the scope of the claims if they have structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal language of the claims. Examples appear below that include certain elements or clauses one or more of which may be combined with other elements and clauses describe embodiments contemplated within the scope and spirit of this disclosure. | 14,039 |
11859610 | While the disclosure will be described in connection with the preferred embodiments, it will be understood that it is not intended to limit the disclosure to that embodiment. On the contrary, it is intended to cover all alternatives, modifications, and equivalents, as may be included within the spirit and scope of the disclosure as defined by the appended claims. DETAILED DESCRIPTION The method and system of the present disclosure will now be described more fully hereinafter with reference to the accompanying drawings in which embodiments are shown. The method and system of the present disclosure may be in many different forms and should not be construed as limited to the illustrated embodiments set forth herein; rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey its scope to those skilled in the art. Like numbers refer to like elements throughout. In an embodiment, usage of the term “about” includes +/−5% of the cited magnitude. In an embodiment, usage of the term “substantially” includes +/−5% of the cited magnitude. It is to be further understood that the scope of the present disclosure is not limited to the exact details of construction, operation, exact materials, or embodiments shown and described, as modifications and equivalents will be apparent to one skilled in the art. In the drawings and specification, there have been disclosed illustrative embodiments and, although specific terms are employed, they are used in a generic and descriptive sense only and not for the purpose of limitation. When introducing elements of various embodiments of the present disclosure, the articles “a”, “an”, “the”, and “said” are intended to mean that there are one or more of the elements. The terms “comprising”, “including”, and “having” are intended to be inclusive and mean that there may be additional elements other than the listed elements. Any examples of operating parameters and/or environmental conditions are not exclusive of other parameters/conditions of the disclosed embodiments. Additionally, it should be understood that references to “one embodiment”, “an embodiment”, “certain embodiments”, or “other embodiments” of the present disclosure are not intended to be interpreted as excluding the existence of additional embodiments that also incorporate the recited features. Furthermore, reference to terms such as “above”, “below”, “upper”, “lower”, “side”, “front”, “back”, or other terms regarding orientation or direction are made with reference to the illustrated embodiments and are not intended to be limiting or exclude other orientations or directions. Additionally, recitations of steps of a method should be understood as being capable of being performed in any order unless specifically stated otherwise. Furthermore, the steps may be performed in series or in parallel unless specifically stated otherwise. Embodiments of the present disclosure relate to combining smaller FE blocks into a single large FE. In hydraulic fracturing, fluid pumps are typically built as either triplex pumps with 3 plungers or quintuplex pumps with 5 plungers. Since the FEs are typically made from a single block of steel or alloy steel, most manufactures do not have the tooling to build larger pumps with more than 5 plungers, and most maintenance equipment used by service companies cannot lift FE blocks any larger or heavier than a quintuplex for replacement on a frac pump. While the present Applicant has identified the advantages of a larger pump for electric frac equipment, the supply chain of manufacturers willing and able to create such pumps is very small. However, these problems can be overcome by connecting 3 triplex FE blocks together with sealing systems between the discharge passages to generate a novemplex (nine plunger) pump. Using a series of triplex FEs enables any manufacturer to create the smaller components with minor modifications to their existing triplex designs. The same triplex block segments may also be usable as stand-alone triplex pumps for use in legacy equipment. This would increase vendor pools for purchasing FEs while also keeping inventory simple as triplex and novemplex pumps can share the same FEs. Embodiments of the present disclosure may also reduce repair and maintenance costs. By way of example, a single triplex FE might cost around $30,000 while a novemplex might cost around $90,000. If a single bore in a single block novemplex FE washes out, the entire FE will need to be replaced. If a novemplex pump is composed of 3 triplex blocks bolted or otherwise coupled together, a single section can be replaced at a third of the cost. This will allow the useful remaining life of the other triplex sections to be utilized until failure. A single triplex section is also much lighter and can be lifted into place on a wellsite using a forklift, light crane, or small service truck crane. A large single block novemplex FE may require an overhead crane in a local shop or the use of a larger mobile crane which cannot always be parked close enough to equipment in the field for servicing. Replacement triplex sections can also be more easily transported between districts and out to well sites without needing large trailers and tractors. For example, if during hydraulic fracturing operations, the fluid supply to the suction ports of the FE might be hampered to the rear most plungers (7, 8, and 9) on a novemplex FE causing cavitation in those cavities of the FE, damage could be mitigated by swapping that triplex portion earlier than the other portions. For example, a section may be damaged by the cavitation, which could lead to an early failure of 1,000 hours or less while other sections may last 2,000 hours or more. The most common hydraulic fracturing plunger type pump in the industry is a quintuplex pump with a 2,500 horsepower rating. Currently in the industry, there is a push by some pump manufacturers to create hydraulic fracturing pumps with power ends and fluid ends capable of operating at higher power levels, such as 5,000 horsepower. This effort is typically focused on electric fracturing units, since electric motors can be packaged in a much smaller footprint than diesel engine/transmission prime mover systems. These higher powered pump designs are centered around staying with a quintuplex style power ends and fluid ends with the overall footprint of the pumps remaining very similar to the 2,500 horsepower legacy pumps. While it is possible to redesign and strengthen the PE of a legacy style quintuplex pump to operate at 5,000 horsepower, the FE is still limited to 5 plungers. Essentially, at the 5,000 horsepower level, each plunger will now have double the amount of power pumping through them, thereby likely lessening the life of the FE by 50%. However, by utilizing features of the present disclosure, full utilization of a higher powered prime mover by both the PE and FE with no decrease in life expectancy is enabled. Embodiments of the present disclosure provide pumps formed from segments of FEs rather than a large novemplex pump (9-plungers) made out of a single block of metal. For example, a novemplex pump may be formed from 3 triplex fluid ends connected together with a sealing system between the common discharge ports of the segments. This pump will act as a single FE block and can achieve far higher fluid rates and HHP. Additionally, using embodiments of the present disclosure enables scaling up to larger FEs, such as 12 or 15 plunger pumps. Further advantages are found by simplifying supply chains and warehousing by having common FEs that can be used in a variety of different applications. FIG.1is a plan schematic view of an embodiment of a hydraulic fracturing system10positioned at a well site12. In the illustrated embodiment, pumping units14(e.g., pump trucks), which make up a pumping system16, are used to pressurize a slurry solution for injection into a wellhead18. An optional hydration unit20receives fluid from a fluid source22via a line, such as a tubular, and also receives additives from an additive source24. In an embodiment, the fluid is water and the additives are mixed together and transferred to a blender unit26where proppant from a proppant source28may be added to form the slurry solution (e.g., fracturing slurry) which is transferred to the pumping system16. The pumping units14may receive the slurry solution at a first pressure (e.g., 80 psi to 160 psi) and boost the pressure to around 15,000 psi for injection into the wellhead18. In certain embodiments, the pumping units14are powered by electric motors. After being discharged from the pump system16, a distribution system30, such as a missile, receives the slurry solution for injection into the wellhead18. The distribution system30consolidates the slurry solution from each of the pump trucks14and includes discharge piping32coupled to the wellhead18. In this manner, pressurized solution for hydraulic fracturing may be injected into the wellhead18. In the illustrated embodiment, one or more sensors34,36are arranged throughout the hydraulic fracturing system10to measure various properties related to fluid flow, vibration, and the like. In embodiments, the sensors34,36transmit flow data to a data van38for collection and analysis, among other things. Furthermore, while not pictured inFIG.1, there may be various valves distributed across the system. For examples, a manifold (not pictured) may be utilized to supply fluid to the pumping units14and/or to receive the pressurized fluid from the pumping units14. Valves may be distributed to enable isolation of one or more components. As an example, there may be valves arranged to enable isolation of individual pumping units14. Furthermore, various support units may also include valves to enable isolation. As noted above, it may be desirable to isolate singular pumping units14or the like if operation upsets are detected. This would enable operations to continue, although at a lower rate, and may potential environmental or personnel hazards, as well as prevent increased damage to the components. However, during operations, personnel may be evacuated or otherwise restricted from entering a pressure zone. Embodiments of the present disclosure may enable remote operation of the valves and, in various embodiments, may enable electrical control using electric energy provided on site, such as through a generator or the like. A power generation system40is shown, which may include turbines, generators, switchgears, transformers, and the like. In various embodiments, the power generation system40provides energy for one or more operations at the well site. It should be appreciated that while various embodiments of the present disclosure may describe electric motors powering the pumping units14, in embodiments, electrical generation can be supplied by various different options, as well as hybrid options. Hybrid options may include two or more of the following electric generation options: Gas turbine generators with fuel supplied by field gas, CNG, and/or LNG, diesel turbine generators, diesel engine generators, natural gas engine generators, batteries, electrical grids, and the like. Moreover, these electric sources may include a single source type unit or multiple units. For example, there may be one gas turbine generator, two gas turbines generators, two gas turbine generators coupled with one diesel engine generator, and various other configurations. In various embodiments, equipment at the well site may utilize 3 phase, 60 Hz, 690V electrical power. However, it should be appreciated that in other embodiments different power specifications may be utilized, such as 4160V or at different frequencies, such as 50 Hz. Accordingly, discussions herein with a particular type of power specification should not be interpreted as limited only to the particularly discussed specification unless otherwise explicitly stated. Furthermore, systems described herein are designed for use in outdoor, oilfield conditions with fluctuations in temperature and weather, such as intense sunlight, wind, rain, snow, dust, and the like. In embodiments, the components are designed in accordance with various industry standards, such as NEMA, ANSI, and NFPA. In an embodiment, a small VFD paired with a dedicated electric motor rated for not more than 100 HP can be used to rotate the chemical additive pump, this motor and VFD can operate at voltages of 240V, 480V, 600V, 690V, or 720V. It should be appreciated that while embodiments may be described with reference to electric motors, in other embodiments, diesel prime movers and hydraulic pumps may also be utilized at the fracturing site, for example, to drive chemical additive pumps. For example, a large diesel engine can power an open or closed hydraulic system containing at least one hydraulic pump and one hydraulic motor to rotate a chemical additive pump. Both of these embodiments will be controlled by a software control system utilizing a user programmed P&ID loop and calibration factor used to help tune the accuracy of chemical flow rates and reactions to flow rate changes, as will be described below. As described above, the pumps utilized in these operations may be pumps with three or five plungers. However, larger pumps may be desirable with larger PEs or where larger capacity may be desirable. Accordingly, embodiments of the present disclosure are directed toward systems and methods for modular or segmented FEs that may be used in fracturing operations, among other industrial applications.FIG.2is a perspective view of an embodiment of a novemplex FE200that includes a cutaway section to illustrate various features of the present disclose. It should be appreciated that various features have been removed for clarity with the present disclosure. The illustrated FE200consists of three different triplex FEs202,204,206that have been coupled together along a discharge axis208(e.g., perpendicular to the suction ends). In the illustrated embodiment, a notch210has been machined into each triplex section202,204,206to allow for one or more fasteners (not pictured), such as bolts, studs, clamps, etc., to couple adjacent fluid end blocks together. It should be appreciated that a set of fasteners may be utilized for only two sections or may extend to couple more than two sections together. The illustrated notch210is arranged above (e.g., axially higher) suction caps212, but it should be appreciated that the notch may be arranged below (e.g., axially lower) the suction caps212or there may be notches at both above and below locations. Further illustrated within the cutout section is a second notch214in the rear216of the fluid end section, opposite the suction caps212, where additional and/or alternative connectors may be used to couple the fluid end sections together. The rear section216of the FE faces the power end and is where the plungers penetrate each pressure bore. A discharge port218is illustrated that runs the length of each fluid end section202,204,206. Discharge piping is connected to one or both ends to allow pressurized fluid to be connected to a manifold or wellhead (not pictured). Sealing this connection between each fluid end section may be accomplished using sealing systems or the like. For example, various seals (e.g., elastomer, metallic, etc.) and the like may be utilized within various grooves formed between interfaces between the sections202,204,26. It should be appreciated that the sealing design may be particularly selected depending on where along the assembly the fluid end section is arranged. A coupling aperture220is illustrated at an end222, which may receive the one or more fasteners to couple the fluid ends together. In the illustrated embodiment, the coupling aperture220is a threaded hole that receives a threaded bolt, but it should be appreciated that other apertures or receivers may be utilized to enable coupling of the various segments. As noted above, while a single aperture is illustrated in this embodiment, there may be multiple apertures that receive multiple fasteners to couple the sections together. Furthermore, as stated, a threaded fitting is only utilized as an example and various other features may also be used to couple the sections together. By way of example only, clamps may be utilized, or tongue and groove segments may be used to secure the sections together. Suction caps are installed along the bores212. As will be appreciated, there is one suction cap per pressure bore and plunger. It should be appreciated that certain bores/caps have been removed, but that embodiments of the present disclosure may be directed to a novemplex FE with 9 bores/suction caps. In other words, embodiments are directed toward coupling three triplex FEs together. As noted above, various components have been removed fromFIG.2for clarity. By way of example, discharge caps (normally on the top face of the fluid end sections) have been removed. These caps would be removed to allow operators access to the discharge valves and discharge port. Additionally, a suction manifold has been removed. In operation, the suction manifold is on the bottom of the fluid end and allows low pressure fluid to be supplied evenly to each pressure bore. This manifold can be placed on either the top or bottom of a fluid end and is opposite the discharge caps. Discharge irons have also been removed. Discharge irons are a pressure rated iron pipe that is normally bolted to one or both sides of the discharge port. The inside diameter and pressure rating of the iron are determined by the required flow rate and expected wellhead pressure. Sensor locations are also not noted inFIG.2. Embodiments may include several sensors such as pressure transducers and vibration monitors. Additional components that have been removed include discharge port gaskets, bolt holes, other clamping bolts, and stay rods. Stay rods may hold the fluid end to the power end. They are similar to a sleeved bolt design where there is a gap between them to allow a “pony rod” from the power end to be attached to a plunger. The gap also allows maintenance of packing to prevent fluid leaks where the plungers enter the fluid end. Another example of a component that has been removed are packing lube ports for the plungers. FIG.3illustrates a perspective view of the back side216of the FE200. As described above, a cutaway section has been included to illustrate a section notch214that includes a fastener location300where a bolt, stud, or other fastener may be utilized to couple the fluid end sections204,206together. As noted, there may also be sealing systems positioned between the fluid end sections. Furthermore, there may be more than one fastener used, along with alternative fastening arrangements. The illustrated embodiment also includes plunger penetration locations302. As shown, triplex blocks are used, but it should be appreciated that other blocks, such as quintuplex blocks, may be used. The plunger penetration locations302illustrate the penetrations for the plungers in each fluid end section204,206. Accordingly, in various embodiments, the sections202,204,206are coupled together at both a suction side and a power side, but it should be appreciated that more or fewer areas may be coupled together based on anticipated operating conditions and the like. FIG.4is a schematic illustration of a stroking order400that may be utilized with embodiments of the present disclosure. For example, the illustrated embodiment describes a novemplex pump having nine plungers402. The preferred stroking order, or the order in which plungers within the fluid end make their respective discharge stroke, is an order which will result in the optimum balancing of the loading on the crankshaft. Referring toFIG.4, the circles represent the number of plunger bores within the FE, and for simplicity are numbered1through9from right to left, wherein the plungers402would reciprocate within the bores. The preferred stroking order would be as shown in the middle row. This order results in the following number of plungers that have gone through their respective discharge strokes adjacent to the plunger that is stroking next according the shown stroking order. So, after plunger #1 strokes, plungers #4 and #7 go through their respective strokes before plunger #2 which is adjacent to plunger #1. Therefore, there were two plunger strokes relatively far away from plunger #1 (#4 and #7) that completed their respective strokes before the adjacent plunger to #1 stroked. Accordingly, after plunger #2 strokes, plunger #5 and #8 complete their stroke resulting in 2 strokes occurring relatively far away from plunger #2. As shown in the figure, the number of strokes that occur between plunger #3 and #4 is 3. The number of strokes that occur between plunger #4 and #5 is 2, and so on as the figure shows. Therefore, the loading on the crankshaft from this stroking order is balanced. It should be appreciated that the illustrated stroking order is for illustrative purposes only and that other embodiments may have different stroking orders. Furthermore, different arrangements may be established based on the number of plungers used. FIG.5is a flow chart of an embodiment of a method500for assembling a segmented FE. It should be appreciated that this method, and all methods described herein, may have more or fewer steps. Moreover, the steps may be performed in a different order, or in parallel, unless otherwise specifically stated. In this example, at least two FE segments are provided502. As noted above, the FE segments may be configured to be coupled together, and as a result, at two FE segments may be aligned along a discharge axis504. The alignment may correspond to aligning respective apertures formed in the segments. One or more sealing systems may be positioned at an interface between the segments506. The sealing systems may include various seals and/or machined components that are utilized to block fluid leakage. The segments may then be coupled together508. In this manner, a segmented FE may be formed by joining together a selected number of FE segments. Embodiments of the present disclosure present a number of advantages over existing systems and methods. As an example, systems and methods of the present disclosure may reduce costs by using multiple smaller blocks for pump manufacturing. As a result, production of a single larger block may be cheaper and easier. Furthermore, repairs and/or replacements may be performed on specific sections, rather than on the entire block. Moreover, inventory control with manufacturers and operations may be improved. For example, legacy equipment can continue to use triplex and quintuplex blocks while newer equipment can use novemplex (9) or quindenplex (15) pumps composed of the same blocks. In various embodiments, operators may keep supplies of the sections that may be then swapped out to replace either the legacy triplex blocks or to make repairs to the newly formed blocks. Moreover, a vendor pool may be increased as more companies may be capable of manufacturing smaller blocks. Embodiments may provider further advantages in the field. For example, the systems described herein may enable easier field swaps because a single block section (triplex or quintuplex) may be easier to transport and swap out on a frac pump trailer in the field versus a single large novemplex block. Moreover, utilizing these systems may result in fewer pump trailers on location. For example, a triplex pump can pump at an optimal fluid rate of around 5 bpm (barrels per minute) whereas a single novemplex can discharge up to 12 bpm for an optimal rate. It should be appreciated that these rates are for illustrative purposes only and may be rounded off and depend of plunger size, discharge pressure, and plunger velocity. A normal frac site needs 90-120 bpm with an additional 12-18 bpm as spare or standby pumping capability. Accordingly, the number of trailers may be reduced through the incorporation of larger pumps. Moreover, fewer trailers may also lead to fewer power cables, thereby decreasing congestion at the site. Additionally, with fewer trailers and power cables required to have the same amount of HHP (hydraulic horsepower) on a frac fleet, operations may be able to reduce the amount of switch gear on electric frac sites. Switch gear is composed of the breakers, relays, and bus bars that safely distribute electricity to connected equipment. As an example, replacing 15 quintuplex pumps with 10 novemplex pumps would reduce switch gear by one third. This reduction in switch gear leads to reduced costs and shrinks the size of the switch gear trailers. Systems and methods of the present disclosure may also incorporate larger power ends to maintain compact and mechanically simple designs. As an example, a single large PE may be utilized with embodiments of the present disclosure. However, it should be appreciated that PEs may also be similarly segmented, as noted about with respect to the FEs. By way of example, a PE normally lasts 3-5 times longer than a standard FE and field swaps are normally not performed. Once assembled, a frac pump may only need a PE swap every 6,000-8,000 hours versus an expected life span of 1,500-2,000 hours for a FE. As a result, larger PEs will still enable longer overall useful lives when utilized with embodiments of the present disclosure. Additionally, embodiments may also incorporate larger motors or prime movers. That is, embodiments may include a physically larger and higher HP motor or prime mover to take advantage of the large fluid pumps. While this may take up space and add weight and/or cost to each frac pump trailer, due to quantities of scale and the advantages obtained by using a larger pump, the cost per horsepower of an entire fleet will be reduced. Moreover, such a configuration simplifies equipment rig up by reducing the number of individual trailers and power cables on a wellsite. Horsepower ranges of 3500-5500 BHP may be desirable to take advantage of the larger fluid pumps, as compared to present ratings of 1750-2500 HHP for triplex and quintuplex designs. Various embodiments may also incorporate stronger couplers to withstand the torque of the large motors. Additionally, leak points between segments (e.g., at segment interfaces) may be addressed using a variety of methods. The discharge bore through the fluid ends is typically machined horizontally through all of the plunger vertical cross bores such that the horizontal discharge bore terminates with a machined flange connection on each side onto which the discharge manifold connects. One methodology of sealing between FE segments includes machining the sealing geometry into the side of each FE instead of machining the flange connection geometry such that the sealing interface on one side of the fluid end could be termed the “male” sealing interface and the opposite side of the fluid end could be termed the “female” sealing interface. Clamping this interface together could be performed as shown above. A number of sealing methods are possible, but one embodiment of the sealing elements could be to utilize a common D-ring seal in the horizontal sealing pocket of the “female” sealing interface in addition to a common o-ring seal machined into the vertical face of the “female” sealing interface. The “male” sealing interface on each FE would then be particularly sized to obtain the desired amount of compression on the seals when the clamping bolts or studs are tightened to connect the FE segments together. The same methodology would apply to connecting the third FE segment into the first pair. Adapters could then be machined to connect to the two exposed sealing interfaces on the unconnected sides of group of 3 fluid ends. These adapters may be designed to connect to the common legacy discharge manifold components. Embodiments of the present disclosure may also be utilized with larger trailers. A larger fluid end, power end, motor, variable frequency drive (VFD), and cooling package may use a larger trailer than traditional systems. For electric equipment, trailer sizes have been reduced significantly as the technology advanced and became more compact. Applicant has recognized capability to lengthening the trailers by 10 or more feet to increase the HHP. It should be appreciated that various configurations shown herein are for illustrative purposes to convey concepts discussed herein, but are not intended to be limiting. For example, the segmented FE pump that was used as an example throughout this disclosure is the “Triple-Triplex”-Novemplex, which is a frac pump composed to three triplex blocks sealed together to prevent fluid leaks to act as a large novemplex pump powered by a single power end. However, there are several other usable combinations that could be created while using current styles of fluid end blocks, including but not limited to a “Quintuple-Triplex” Quindenplex fluid end. This configuration is composed of 5 triplex blocks to create a large 15-plunger pump. Additionally, a “Triple-Quintuplex” Quindenplex fluid end is another possible 15-plunger pump composed of 3 quintuplex blocks. As another example, a “Double-Quintuplex” Decemplex fluid end is a 10-plunger pump composed of 2 quintuplex blocks. It should be appreciated that even numbers of plungers may be undesirable due to their flow ripple (approximately double odd number plunger pumps). However, embodiments of the present disclosure enable a resulting flow ripple better than that of the industry accepted triplex and comparable to that of the industry accepted quintuplex due to the number of plungers. In another example, a “Quadruple-Triplex” Duodecaplex fluid end is a 12-plunger pump formed by using 4 triplex blocks. This is another even numbered plunger pump, but the flow ripple would be acceptable due to the quantity of plungers. It should be appreciated various other configurations may also be enabled by embodiments of the present disclosure. Various embodiments of the present disclosure may include a plunger and valve size of 4″ for the novemplex pump. Many current triplex and quintuplex pumps are 4.5″. Some pump down pumps (frac pumps modified for higher fluid rate and a lower pressure rating) use 5″ components. All three of these sizes are industry standards and can be used for the Segmented FE Pump design of the present disclosure. Other nonstandard component sizes of 3.5″, 3.75″, and 4.25″ may also be used. The advantages of some of these smaller and intermediate sizes include providing a better balance of fluid rate and maximum pressure rating. It should be appreciated that various components may be selected, at least in part, by rod load on the PE and horsepower capability of the prime mover. For example, a novemplex PE and FE may be rated for 4500 HHP with a 5000 BHP motor attached; this could allow the pump to achieve fluid rates of 12 BPM at a max pressure of 15,000 psi. Alternatively, the same FE/PE/Motor combination with a larger plunger and valve size could achieve fluid rates of 15 BPM at a max pressure of 12,000 psi. Certain shale basins have higher or lower expected frac pressures and frac pumps can be tailored to meet this requirement with the highest possible fluid rate per pump. This same frac pump could be converted to a pump-down pump with an even larger component size and achieve 18 BPM with a pressure rating of 10,000 psi, this would allow use of a single frac pump trailer for pump down whereas normally 2-4 pump trailers are required. Fluid end blocks can be made out of stainless steel or carbon steel, among other materials. The present disclosure described herein, therefore, is well adapted to carry out the objects and attain the ends and advantages mentioned, as well as others inherent therein. While a presently preferred embodiment of the disclosure has been given for purposes of disclosure, numerous changes exist in the details of procedures for accomplishing the desired results. These and other similar modifications will readily suggest themselves to those skilled in the art, and are intended to be encompassed within the spirit of the present disclosure disclosed herein and the scope of the appended claims. | 32,447 |
11859611 | DETAILED DESCRIPTION Turning now to the non-prior art figures,FIGS.6and7show a fluid end100. The fluid end100may be attached to the traditional power end34, shown inFIG.3. Alternatively, the fluid end100may be attached to various embodiments of power ends, such as the modular power end described in U.S. Provisional Patent Application Ser. No. 63/053,797, authored by Thomas et al. and filed on Jul. 20, 2020. Unlike the traditional fluid end46, shown inFIG.3, the fluid end100comprises a plurality of fluid end sections102rather than a single housing48. The fluid end sections102are positioned in a side-by-side relationship. Preferably, the fluid end100comprises five fluid end sections102. However, more or less fluid end sections102may be used. Forming the fluid end100out of multiple fluid end sections102allows a single fluid end section102to be replaced, if needed. In contrast, the entire housing48in traditional fluid ends46may need to be replaced if only a portion of the housing48fails. Turning toFIGS.8and9, each fluid end section102comprises a horizontally positioned housing104having a generally cylindrical cross-sectional shape, as shown inFIG.8. In alternative embodiments, each fluid end section may have a generally rectangular cross-sectional shape. Unlike the traditional fluid end46shown inFIGS.3and5, each housing104does not include a vertical bore intersecting a horizontal bore to form an internal chamber. Rather, each housing104only has a single horizontally positioned bore106, as shown inFIG.9. Removing the internal chamber found in traditional fluid ends from the housing104removes common stress points from the housing104. Eliminating the intersecting bore also reduces the cost of manufacturing the fluid end100as compared to traditional fluid ends. The time required to manufacture the fluid end100is greatly reduced without the need for machining an intersecting bore, and the fluid end100may be manufactured on a lathe instead of a machining center. The fluid end100may also be manufactured out of lower strength and less costly materials since it does not include the high stress areas found in traditional fluid ends. Each housing104may be manufactured out of high strength alloy steel, such as carbon steel. In alternative embodiments, each housing104may be manufactured out of stainless steel. Continuing withFIGS.8and9, each housing104comprises a first outer surface108joined to an opposed second outer surface110by an intermediate outer surface112. The horizontal bore106extends through the housing104along a central longitudinal axis114and interconnects the opposed first and second outer surfaces108and110, as shown inFIG.9. Each housing104is of single piece construction. Since each housing104only has a single horizontal bore106, fluid must be routed throughout the housing104differently from how fluid is routed throughout a traditional fluid end housing48. As will be described in more detail herein, a fluid routing plug116, shown inFIGS.52-64, is installed within each housing104and is configured to route fluid throughout the housing104. With reference toFIGS.6,7, and10-16, each housing104is supported on a single connect plate118in a one-to-one relationship. A plurality of sets of stay rods120, shown inFIG.6, are used to attach each connect plate118to a power end. The connect plates118may each be attached to the corresponding stay rods120prior to attaching a housing104to a corresponding connect plate118. Because the housings104are each attached to a connect plate118, the fluid end100does not include a flange like the flange50formed in the fluid end46shown inFIG.3. In an alternative embodiment, multiple housings may be attached to a single, larger connect plate. In such embodiment, the stay rods are likewise attached to the single, larger connect plate. The stay rods120shown inFIG.6are configured for use with a modular power end, like that shown in in U.S. Provisional Patent Application Ser. No. 63/053,797, authored by Thomas et al. and filed on Jul. 20, 2020. A spacer122is installed on each stay rod120and is configured to engage with a front surface of the power end. In alternative embodiments, the stay rods may be configured like the stay rods42shown inFIG.3. With reference toFIGS.10-13, each connect plate118has a generally rectangular shape and has opposed first and second surfaces124and126. A plurality of first passages128are formed around the outer periphery of each connect plate118. Each first passage128interconnects the first and second surfaces124and126of the connect plate118and is configured for receiving a stay rod120. Each stay rod120extends through a corresponding passage128in a one-to-one relationship. The connect plate118shown inFIGS.10-13has four first passages128. Likewise, four stay rods120are shown attached to each connect plate118inFIG.6. In alternative embodiments, the connect plate may have more than four or less than four first passages, as long as the amount of first passages corresponds with the number of stay rods being used with each connect plate. Once each stay rod120is installed in a connect plate118, a first end130of each stay rod120projects from the first surface124of the connect plate118, as shown inFIG.16. A nut132and a washer134are installed on the projecting first end130of each stay rod120in a one-to-one relationship. The nut132is turned until it tightly engages a corresponding washer134and the first surface124of the connect plate118, thereby securing the connect plate118to the stay rods120. With reference toFIGS.6, and14-16, a plurality of notches136are formed around the periphery of the housing104at its second surface110, as shown inFIGS.14and15. When the housing104is attached to the connect plate118, each notch136partially surrounds one of the first passages128in a one-to-one relationship. The notches136provide space to access the washer134and nut132during operation. Continuing withFIGS.10-13, a central bore138is formed in each connect plate118and interconnects the first and second surfaces124and126. The central bore138is configured for receiving a stuffing box140, as described in more detail later herein. A plurality of second passages142are formed in the connect plate118and surround the central bore138. Each second passage142interconnects the first and second surfaces124and126of the connect plate118. The second passages142are configured to align in a one-to-one relationship with a plurality of first threaded openings144formed in the second surface110of each housing104, as shown inFIGS.14and15. Each housing104is attached to the first surface124of a corresponding connect plate118using a fastening system146. The fastening system146comprises a plurality of studs148, a plurality of washers150, and a plurality of nuts152, as shown inFIGS.7and17. A first end154of each stud148is configured to mate with a corresponding one of the first openings144formed in the housing104. The second passages142formed in the connect plate118subsequently receive the plural studs148projecting from the housing104. When the housing104and the connect plate118are brought together, a second end156of each stud148projects from the second surface126of the connect plate118. A washer150and a nut152are subsequently installed on the second end156of each stud148, in a one-to-one relationship. The nut152is turned until it tightly engages the washer150and the second surface126of the connect plate118, thereby securing the housing104and the connect plate118together. InFIGS.10-15, the housing104and connect plate118each have eight corresponding first openings144and second passages142. In alternative embodiments, more than eight or less than eight corresponding openings and second passages may be formed in the housing and connect plate. In such embodiments, the fastening system may comprise the same number of studs, washers, and nuts as there are openings and passages. In further alternative embodiments, the fastening system may comprise different types of fasteners, such as socket-headed screws. Continuing withFIGS.10-15, a pair of third passages158are formed in the connect plate118on opposite sides of the central bore138. The third passages158are alignable with a pair of pin holes160formed in the second surface110of the housing104. Each third passage158and each corresponding pin hole160is configured to receive a dowel pin in a one-to-one relationship. The dowel pins are used to help align the housing104on the connect plate118during assembly. A threaded hole162may also be formed in a top surface164of each connect plate118, as shown inFIGS.10and11. The threaded hole162is configured for receiving a lifting eye (now shown) used to lift and support the connect plate118during assembly. In alternative embodiments, the connect plate may have various shapes and sizes other than those shown inFIGS.10-13. For example, the connect plate may be shaped like the various embodiments disclosed in U.S. Provisional Patent Ser. No. 63/053,797, authored by Thomas et al. and filed on Jul. 20, 2020. Turning back toFIGS.6and7, in contrast to the traditional fluid end46, shown inFIG.3, the fluid end100is configured to receive fluid from two manifolds, rather than just one. The fluid end100comprises an upper intake manifold166and a lower intake manifold168. Each manifold166and168is in fluid communication with each fluid end section102. Using two different manifolds166and168allows different types of fluid to be delivered to each fluid end section102. For example, fluid having a higher level of proppant may be delivered via the upper intake manifold166, while fluid having a zero to minimal level of proppant may be delivered via the lower intake manifold168. Continuing withFIGS.6and7, the upper and lower intake manifolds166and168are joined to the fluid end sections102via a plurality of conduits159. Each conduit159is positioned directly below the corresponding manifold166and168and extends along a straight line between the fluid end section102and the corresponding manifold166and168. Thus, each conduit159and corresponding manifold166and168have a “T” shape. Turning toFIGS.7A and7B, an alternative embodiment of an upper and lower intake manifold161and163is shown. The upper and lower intake manifolds161and163are joined to the fluid end sections102via a plurality of conduits165. The conduits165have an elbow shape. The elbow shape of the conduits165causes the corresponding manifolds161and163to be spaced farther away from a discharge manifold167, than the manifolds166and168. Providing more space between the intake manifolds161and163and the discharge manifold167provides more space for maintenance to different areas of the fluid end100, when needed. Turning back toFIG.9, an upper and lower intake bore170and172are formed within the housing104. Each bore170and172interconnects the intermediate outer surface112and the horizontal bore106. The upper and lower intake bores170and172shown inFIG.9are collinear. In alternative embodiments, the upper and lower intake bores may not be collinear. With reference toFIGS.6-9, the upper intake bore170is in fluid communication with the upper intake manifold166, and the lower intake bore172is in fluid communication with the lower intake manifold168. In operation, fluid may be delivered into the housing104through both the upper and lower intake bores170and172. In alternative embodiments, only one intake bore may be formed in the housing and only one intake manifold may be attached to the housing. Continuing withFIGS.6-9, the fluid end100further comprises a plurality of discharge conduits174. Each discharge conduit174is attached to one of the fluid end sections102in a one-to-one relationship. A discharge manifold176interconnects each of the discharge conduits174, as shown inFIGS.6and7. In alternative embodiments, the discharge conduits and discharge manifold may be formed as a single unit, like the discharge manifold167, shown inFIGS.7A and7B. Continuing withFIG.9, a discharge bore178is formed in the housing104and interconnects the intermediate surface112and the horizontal bore106. The discharge bore178is positioned between the first surface108of the housing104and the intake bores170and172. The discharge bore178is in fluid communication with the discharge conduit174. In operation, fluid to be pressurized enters the housing104through the upper and lower intake bores170and172. Pressurized fluid exits the housing104through the discharge bore178. With reference toFIG.18, the discharge bore178has an oval cross-sectional shape, as shown by a discharge bore opening180. The opening180has a length A and a width B. The discharge bore178is formed within the housing104such that the width B extends along an axis that is parallel to the longitudinal axis114of the housing104. During operation, high fluid pressure within the discharge bore178may cause the walls along the length A to compress, causing the discharge bore178to have a more circular cross-sectional shape. Providing room for the walls surrounding the discharge bore178to compress, helps reduce stress in the housing104and increase fluid flow. In alternative embodiments, the discharge bore may have a circular cross-sectional shape. Continuing withFIG.19, a counterbore173is formed within the housing104immediately above the opening180of the discharge bore178. The discharge bore178opens into the counterbore173. The counterbore173has a circular cross-sectional shape, as shown by the opening175inFIG.18. A portion of the discharge conduit174is installed within the counterbore173through its opening175. A seal182is interposed between the walls of the housing104surrounding the discharge bore178and an outer surface of the discharge conduit174. The seal182is installed within a groove184formed in the walls of the housing104. The seal182may be identical to the second seal376, described with reference toFIGS.65and70. In alternative embodiments, the seal may be identical to the first seal374, described with reference toFIGS.65and71. The groove184is characterized by two sidewalls185joined to a base183. The sidewalls185may join the base183via radius corners or at a 90 degree angle. No grooves are formed in the outer surface of the discharge conduit174for housing a seal. In operation, the seal182wears against the outer surface of the discharge conduit174. If the outer surface of the discharge conduit174begins to erode, allowing fluid to leak around the seal182, the discharge conduit174may be replaced with a new discharge conduit174. The discharge bore178shown inFIG.9interconnects a top surface113of the intermediate surface112of the housing104and the horizontal bore106. Likewise, the discharge conduits174shown inFIGS.6,7, and9are attached to the top surface113of the intermediate surface112of each housing104. In operation, any gas trapped within the housing104rises towards the top of the housing104. Placing the discharge bore178and conduit174at the top of the housing104allows the gases to naturally escape. Additionally, any wear caused to the components by the rising gas will primarily be imposed on the discharge conduit174, rather than the housing104. The discharge conduit174and corresponding discharge piping176are easily replaced, if needed. In alternative embodiments, the discharge bore may interconnect a bottom or side surface of the intermediate surface and the horizontal bore, and the discharge conduit may be attached to the corresponding surface of the housing. In further alternative embodiments, the discharge bore may interconnect the first outer surface of the housing and the horizontal bore, and the discharge conduit may be attached to the first outer surface of the housing. With reference toFIGS.6,18and19, a rectangular flange171is formed around each discharge conduit174. Each rectangular flange171is attached to the housing104using a plurality of threaded studs186and nuts187, as shown inFIGS.6and19. A plurality of threaded openings188are formed in the housing104for receiving the studs186, as shown inFIG.18. The openings188are positioned in a rectangular pattern around the discharge bore opening180. Such pattern helps maximize the surface area of the intermediate surface112of the housing104, helping to reduce the size and weight of the housing104. With reference toFIGS.7and18, the intake manifolds166and168each comprise a plurality of rectangular flanges189joined to a plurality of conduits191in a one-to-one relationship, as shown inFIG.7. Each rectangular flange189is attached to the housing104using a plurality of threaded studs190and nuts193, as shown inFIG.7. A plurality of threaded openings192are formed in the housing104for receiving the studs190, as shown inFIG.18. The openings192are positioned in a rectangular pattern around the intake bores170and172to maximize surface area of the housing104. In alternative embodiments, the discharge conduits and intake manifolds may be attached to the housing using different types of fasteners, such as socket-headed screws. Continuing withFIG.18, the intermediate surface112of the housing104includes a first portion194joined to a second portion196by a first tapered portion198. The second portion196is joined to a third portion200by a second tapered portion202. The first portion194is joined to the first surface108and the third portion200is joined to the second surface110. The second portion196has a smaller diameter than both the first and third portions194and200. Providing the second portion196with a smaller diameter helps remove unnecessary weight from the housing104. The third portion200may have a slightly larger diameter than the first portion194. The first, second, and third portions194,196, and200are generally cylindrical. Thus, the housing104may be characterized as being primarily cylindrical. In alternative embodiments, the housing may be uniform in diameter throughout its intermediate surface. In further alternative embodiments, the housing may have various diameters throughout its intermediate surface other than those shown inFIG.18. Continuing withFIG.18, a threaded hole204is formed in the top surface113of the intermediate surface112. The threaded hole204is positioned at the center of gravity of the housing104when the housing104is fully loaded with the components described herein. The threaded hole204is configured to receive a lifting eye (not shown) used to lift and support the housing104during assembly and maintenance, as shown inFIG.9. With reference toFIGS.20-29, each fluid end section102further comprises a stuffing box140attached to the second outer surface110of the housing104. The stuffing box140has a generally cylindrical shape and comprises a first outer surface206joined to an opposed second outer surface208by an intermediate outer surface210. The intermediate surface210includes a cylindrical first portion212joined directly to a cylindrical second portion214. The first portion212is positioned adjacent the first surface206and has a reduced diameter from that of the second portion214. A threaded hole215is formed in a top surface of the second portion214. The threaded hole215is configured to receive a lifting eye (not shown) used to lift and support the stuffing box140during assembly and maintenance. A central passage216interconnects the stuffing box's first and second outer surfaces206and208. The walls surrounding the central passage216include a first section218joined to a second section220by a tapered shoulder222, as shown inFIGS.25,26, and29. The second section220has a larger diameter than that of the first section218. As described in more detail herein, the second section220and the tapered shoulder222are configured for receiving a plunger packing224, as shown inFIGS.20and21. Continuing withFIGS.23-29, a plurality of passages226are formed around the periphery of the second portion214of the stuffing box140. Each passage226interconnects the second surface208of the stuffing box140and a base228of the second portion214. The passages226are formed parallel to the central passage216. Turning back toFIGS.14and15, a plurality of second threaded openings230are formed in the second surface110of the housing104. The openings230surround the opening of the horizontal bore106. The second openings230are surrounded by the first openings144used with the connect plate118. Continuing withFIGS.20and21, the walls surrounding the horizontal bore106adjacent the second surface110of the housing104are sized to receive the first portion212of the stuffing box140. The first portion212is installed within the horizontal bore106such that the base228of the second portion214abuts the second surface no of the housing104. A portion of the second portion214is disposed within the central bore138formed in the connect plate118. The stuffing box140is aligned on the housing104such that the passages226align with the second openings230in a one-to-one relationship. With reference toFIGS.20,21, and30-37, the stuffing box140is attached to the housing104using a retainer232and a fastening system234. The retainer232has a generally cylindrical shape and comprises opposed first and second outer surfaces236and238joined by an intermediate surface240. A central passage242interconnects the first and second outer surfaces236and238. At least a portion of the central passage242has internal threads244. A plurality of side passages246are formed in the retainer232. Each passage246interconnects the central passage242and the intermediate surface240. The passages246provide a pathway for lubricating oil to be introduced to the horizontal bore106during operation. The oil lubricates the moving parts within the housing104during operation. Continuing withFIGS.30-37, a plurality of passages248are formed in the retainer232and surround the central passage242. Each passage248interconnects the first and second outer surfaces236and238. The first surface236of the retainer232is positioned on the second surface208of the stuffing box140such that the passages248align with the passages226formed in the stuffing box140, in a one-to-one relationship. A pair of dowel pin holes241are formed in the second surface208of the stuffing box140, as shown inFIGS.27and28. A corresponding pair of dowel pin holes243are formed in the first surface236of the retainer232, as shown inFIGS.31and32. The holes241and243are configured for receiving a dowel pin. The dowel pin aligns the retainer232on the stuffing box140during assembly. Turning back toFIGS.20and21, the fastening system234secures both the retainer232and the stuffing box140to the housing104. The fastening system234comprises a plurality of studs250, nuts252, and washers254. A first end256of each stud250mates with one of the second openings230in the housing104in a one-to-one relationship. The passages226in the stuffing box140and the passages248in the retainer232subsequently receive the plural studs250projecting from the housing104. A second end258of each stud250projects from the second surface238of the retainer232. The projecting second end258of each stud250receives a washer254and a nut252. The nut252is turned until it tightly engages the washer254and the second surface238of the retainer232, thereby securing the retainer232and the stuffing box140together. The retainer232, in turn, holds the stuffing box140against the housing104. The stuffing box140and the retainer232may be attached to and removed from the housing104without removing the connect plate118. When the first portion212of the stuffing box140is installed within the housing104, a seal260is interposed between the walls of the housing104and outer surface of the first portion212. The seal260is installed within a groove262formed in the walls of the housing104. The seal260may be identical to the first seal374, described with reference toFIGS.65and71. In alternative embodiments, the seal may be identical to the second seal376, described with reference toFIGS.65and70. The groove262is characterized by two sidewalls264joined by a base266, as shown inFIG.21. The sidewalls264may join the base266via radius corners or at a 90 degree angle. No grooves are formed in the first portion212of the stuffing box140for housing a seal. The seal260wears against the outer surface of the first portion212during operation. If the outer surface of the first portion212begins to erode, allowing fluid to leak around the seal260, the stuffing box140may be replaced with a new stuffing box140. When the stuffing box140is attached to the housing104using the fastening system234, a first end256of the studs250may be installed within the housing104such that they extend past the seal260, as shown inFIG.20. An edge of the studs250may not be purposely aligned with an edge of the seal260in order to prevent areas of high stress from being aligned with one another in the housing104, potentially causing a stress riser. Continuing withFIGS.20,21, and38-42, a plunger packing224is installed within the central passage216of the stuffing box140. The plunger packing224engages the tapered shoulder222and is positioned within the second section220of the central passage216, as shown inFIGS.20and21. A portion of the plunger packing224may extend into the central passage242of the retainer232. The plunger packing224has a central passage268that aligns with the central passages216and242when the plunger packing224is installed within the stuffing box140and the retainer232. In alternative embodiments, the plunger packing may be sized to not extend into the retainer. The plunger packing224comprises a pair of outer ring seals270and271and at least one inner ring seal272. The outer ring seals270and271may be made of metal while the inner ring seals272may be made of an elastomer material. The outer ring270has a tapered outer surface274that is sized to engage the tapered shoulder222formed in the central passage216. The tapered engagement helps reduce stress in the stuffing box140during operation. In alternative embodiments, the walls surrounding the central passage of the stuffing box may include an annular shoulder rather than a tapered shoulder. In such embodiment, the plunger packing may have a flat outer ring configured to mate with the annular shoulder. A plurality of holes275are formed in the outer ring271. The holes275are in fluid communication with the side passages246formed in the retainer232in order to deliver lubricating oil to the housing104. With reference toFIGS.20,21, and43-46, a packing nut276is installed within the retainer232and engages the plunger packing224. The packing nut276comprises a first surface278joined to an opposed second surface280by an intermediate surface282. A central passage284extends through the packing nut276and interconnects the opposed first and second surfaces278and280. A plurality of side holes286are formed in the packing nut276and interconnect the central passage284and the intermediate surface282. The holes286are configured for engaging a tool used to grip the packing nut276. Continuing withFIGS.43-46, external threads288are formed in a portion of the intermediate surface282of the packing nut276. The external threads288are configured to mate with the internal threads244formed within the retainer232, as shown inFIGS.20and21. The mating threads288and244are buttress threads. The buttress threads are configured to handle a large amount of load using a low amount of threads. Using a low amount of threads allows the packing nut276to be quickly removed or installed within the retainer232. In alternative embodiments, the packing nut and retainer may mate using traditional threads. When the packing nut276is installed within the retainers232, the first surface278of the packing nut276engages an outer ring seal270of the plunger packing224. Such engagement compresses the plunger packing224, creating a tight seal. After the packing nut276has been installed within a retainer232, the central passage284within the packing nut276is aligned with the central passage268in the plunger packing224. Continuing withFIGS.20and21, when the stuffing box140and the retainer232are attached to the housing104, the central passages216and242align with the horizontal bore106. Likewise, the central passages268and284in the installed plunger packing224and packing nut276align with the horizontal bore106. Thus, the central passages216,242,268, and284may be considered an extension of the horizontal bore106. A plunger290is disposed with the installed plunger packing224and the packing nut276, as shown inFIG.20. In operation, the plunger290reciprocates within the horizontal bore106in order to pressurize fluid contained with the housing104. With reference toFIGS.20,21, and47-49, the horizontal bore106is sealed at the first surface108of the housing104by a retainer300. The retainer300has a first surface302joined to an opposed second surface304by an outer intermediate surface306. A cutout308is formed in the second surface304for receiving a portion of a discharge valve guide298. A central passage310is formed in the retainer300and interconnects the first surface302and the cutout308. The walls surrounding the central passage310have a polygonal shape. The polygonal shape is configured to mate with a tool used to grip the retainer300. The intermediate surface306of the retainer300has external threads312that mate within internal threads314formed in the walls surrounding the horizontal bore106adjacent the first surface108of the housing104, as shown inFIGS.20and21. The mating threads312and314are buttress threads. The buttress threads are configured to handle a large amount of load using a low amount of threads. Using a low amount of threads allows the retainer300to be quickly removed from or installed within the housing104. In alternative embodiments, the retainer may mate with the housing using traditional threads. In further alternative embodiments, the retainer may be secured to the housing using a fastening system, like the fastening system234. Turning now toFIGS.50and51, the fluid routing plug116is installed within a medial section of the horizontal bore106. The fluid routing plug116is configured to engage with a suction valve292on one side and a discharge valve294on the opposite side. In operation, the suction and discharge valves292and294move axially along an axis that is parallel to or aligned within the central longitudinal axis114of the housing104, shown inFIG.9, as the valves292and294move at alternating times between an open and closed position. In the closed position, the valves292and294are pressed against the fluid routing plug116, preventing fluid from exiting the plug116. In the open position, the valves292and294are spaced from the fluid routing plug116, allowing fluid to flow from the plug116. As will be described in more detail herein, axial movement of the suction valve292is limited by a suction valve guide296installed within the housing104. Likewise, axial movement of the discharge valve294is limited by the discharge valve guide298installed within the housing104. Turning now toFIGS.52-64, the fluid routing plug116comprises a body316having opposed first and second outer surfaces318and320joined by an intermediate outer surface322. The first outer surface318may also be referred to as the suction side of the fluid routing plug116. The second outer surface320may also be referred to as the discharge side of the fluid routing plug116. A central longitudinal axis324extends through the body316and both surfaces318and320, as shown inFIG.55. A plurality of first fluid passages326are formed within the body316and interconnect the intermediate surface322and the first surface318. The first fluid passages326interconnect the intermediate surface322and the first surface318by way of an axial-blind bore328, as shown inFIG.55. The blind bore328extends along the central longitudinal axis324of the body316. The first fluid passages326each open into the blind bore328via a plurality of openings330. A longitudinal axis332of each first fluid passage326intersects the central longitudinal axis324of the body316, as shown inFIG.58. The fluid routing plug116shown inFIGS.52-64has four first fluid passages326formed in its body316. The first fluid passages326are equally spaced around the body316. In alternative embodiments, more than four or less than four first fluid passages may be formed in the body and may be equally or unequally spaced apart from one another. Continuing withFIG.55, the first fluid passages326extend between the intermediate surface322and the blind bore328at a non-right angle relative to the central longitudinal axis324—the acute angle facing the second surface320of the body316. Forming the first fluid passages326at such an angle reduces the amount of stress in the fluid routing plug116as fluid flows through the first fluid passages326. Forming the first fluid passages326at such angle also helps direct fluid flow towards the blind bore328and the first surface318. With reference toFIGS.57and59, the first fluid passages326have an oval cross-sectional shape, as shown by an opening334of each first fluid passage326on the intermediate surface322. Each opening334has a length C and a width D, as shown inFIG.59. The first fluid passages326are formed in the body316such that the length C extends along an axis that is parallel to the central longitudinal axis324of the body316. Orienting the first fluid passages326as such helps reduce the amount of stress in the body316as fluid flows through the first fluid passages326and helps maximize the rate of fluid flow through the passages326. In alternative embodiments, the first fluid passages may have a different cross-sectional shape, such as a circular or oblong shape. In further alternative embodiments, the first fluid passages may be shaped like the first fluid passages910, shown inFIGS.121and124. With reference toFIGS.60-63, the fluid routing plug116further comprises a plurality of second fluid passages336formed in the body316. The second fluid passages336each have a circular cross-sectional shape and interconnect the first and second surfaces318and320of the body316. In alternative embodiments, the second fluid passages may have a different cross-sectional shape, such as an oval or oblong shape. Unlike the first fluid passages326, the second fluid passages336do not intersect an axially blind bore. Rather, each second fluid passage336extends between the first and second surface318and320along a straight-line path. The second fluid passages336and the first fluid passages326do not intersect and are positioned offset from one another, as shown inFIG.58. Positioning the first and second passages326and336offset from one another helps minimize the stress in the fluid routing plug116during operation. The fluid routing plug116shown inFIGS.52-64has twelve second fluid passages336formed in its body316. In alternative embodiments, more or less than twelve second fluid passages may be formed in the body. Each second fluid passage336extends between the first and second surfaces318and320along a different axis, as shown inFIGS.60-63. Each axis is positioned at a non-zero angle relative to the central longitudinal axis324of the body316. Forming each second passage336along a different axis helps alleviate stress in the fluid routing plug116during operation and helps maximize the rate of fluid flow through the second passages336. Turning back toFIGS.53,55, and56, the first surface318of the body316includes an outer rim338joined to a tapered wall340. The outer rim338may taper slightly between the intermediate surface322and the tapered wall340, as shown inFIG.55. Such taper provides more surface area for the tapered wall340without increasing the length of the intermediate surface322. The tapered wall340extends between an entrance342of the blind bore328and the outer rim338at an angle of at least 30 degrees relative to the central longitudinal axis324of the body316. Preferably, the tapered wall340is formed at an angle of 45 degrees relative to the central longitudinal axis324of the body316, as is shown inFIG.55. As will be described in more detail later herein, the tapered wall340forms a cavity344within the first surface318of the body316that is sized to receive a sealing element346of the suction valve292, as shown inFIGS.72-76. Continuing withFIGS.53and56, the second fluid passages336open on the outer rim338of the first surface318, as shown by the openings348. The second fluid passages336are formed within the body316such that the openings348are positioned in groups350around the outer rim338. The first surface318shown inFIG.59comprises four groups350of openings348, each group350comprising three openings348. Adjacent openings348within each group350are equally spaced. The spacing between the nearest openings348of adjacent groups350exceeds the spacing between adjacent openings348within a single group350. Spacing the openings348in groups350helps achieve the ideal velocity of fluid flow through the fluid routing plug116and allows the second fluid passages336to be offset from the first fluid passages326, as shown inFIG.58. In alternative embodiments, the openings may be spaced in differently sized groups or different patterns than that shown inFIG.56. With reference toFIGS.52,54, and55, the second surface320of the body316comprises an outer rim352joined to a central base354by a tapered wall356. The tapered wall356extends between the central base354and the outer rim352at an angle of at least 30 degrees relative to the central longitudinal axis324of the body316. Preferably, the tapered wall356is formed at an angle of 45 degrees relative to the central longitudinal axis324of the body316, as is shown inFIG.55. As will be described in more detail later herein, the tapered wall356forms a cavity358within the second surface320of the body316that is sized to receive a sealing element360of the discharge valve294, as shown inFIGS.85-89. Continuing withFIGS.52,54, and55, a blind bore362is formed in the center of the central base354. The walls surrounding the blind bore362may be configured to mate with a tool used to grip the fluid routing plug116. For example, the walls surrounding the blind bore362may be threaded. The second fluid passages336open on the central base354of the second surface320, as shown by the openings364inFIGS.52and54. The second fluid passages336are formed within the body316such that the openings364surround the opening of the blind bore362. The openings364shown inFIG.54are all equally spaced from one another around the opening of the blind bore362. In alternative embodiments, the openings of the second fluid passages on the central base may not all be equally spaced apart from one another. Continuing withFIG.55, in order to provide space for the openings364on the second surface320, the tapered wall356has a greater diameter than the tapered wall340formed in the first surface318. Thus, as will be described in more detail herein, the sealing element360of the discharge valve294is larger in size than the sealing element346of the suction valve292, as shown inFIGS.72-76and85-89. Turning back toFIGS.50and51, the fluid routing plug116is installed within the horizontal bore106such that the first fluid passages326are in fluid communication with the upper and lower intake bores170and172. The upper and lower intake bores170and172direct fluid into the first fluid passages326of the fluid routing plug116. The first fluid passages326direct the fluid into the blind bore328and towards the first surface318of the fluid routing plug116. When the plunger290is retracted from the housing104, the fluid flowing through the first fluid passages326forces the suction valve292to move axially away from the first surface318. Such position is considered an open position of the suction valve292. When the suction valve292is spaced from the first surface318, fluid flows out of the blind bore328, through the gap between the first surface318and the suction valve292. From there, the fluid flows around the suction valve292and the suction valve guide296and into the horizontal bore106. A first fluid flow path for the fluid to be pressurized is shown by the arrows366inFIG.50. With reference toFIG.51, as the plunger290extends into the horizontal bore106, the plunger290forces fluid in the horizontal bore106back towards the fluid routing plug116. Pressurized fluid forced back towards the fluid routing plug116by the plunger290forces the suction valve292to seal against the first surface318, sealing the entrance342of the blind bore328. Such position is considered a closed position of the suction valve292. Once the entrance342of the blind bore328is sealed, the only place for fluid to flow is through the openings348of the second fluid passages336on the outer rim338of the first surface318. Fluid flows into the openings348on the first surface318and through the second passages336towards the second surface320of the fluid routing plug116. The pressurized fluid at the second surface320forces the discharge valve294to move axially away from the second surface320, unsealing the openings364of the second fluid passages336. Such position is considered an open position of the discharge valve294. Pressurized fluid is then allowed to flow around the discharge valve294and into the discharge bore178. A second fluid flow path for the pressurized fluid is shown by the arrows368inFIG.51. When the plunger290retracts from the housing104, the fluid pressure on the back side of the discharge valve294is greater than the fluid pressure within the fluid routing plug116. Such pressure differential causes the discharge valve294to seal against the second surface320, sealing the openings364of the second fluid passages336. Such position is considered the closed position of the discharge valve294. Turning toFIG.64, the intermediate surface322of the fluid routing plug116varies in diameter throughout its length and generally decreases in size from its second surface320to its first surface318. The intermediate surface322comprises a first sealing surface370positioned adjacent the first surface318and a second sealing surface372positioned adjacent the second surface320. The first and second sealing surfaces370and372each extend around the entire intermediate surface322in an endless manner and surround the longitudinal axis324of the body316. The first and second sealing surfaces370and372shown inFIG.64are annular. In alternative embodiments, the first and second sealing surfaces may have non-annular shape, such as an oval shape. The first sealing surface370has a smaller diameter than the second sealing surface372. As will be described in more detail herein, the first and second sealing surfaces370and372are configured to engage a first and second seal374and376installed within the housing104, as shown inFIGS.70and71. Continuing withFIG.64, the intermediate surface322of the fluid routing plug116further comprises a first bevel378positioned between the opening334of the first fluid passages326and the first sealing surface370. The first bevel378extends around the entire intermediate surface322in an endless manner and surrounds the longitudinal axis324of the body316. The first bevel378shown inFIG.64is annular. In alternative embodiments, the first bevel may have a non-annular shape, such as an oval shape. A maximum diameter of the first bevel378is greater than the diameter of the first sealing surface370. The maximum diameter of the first bevel378is positioned adjacent the openings334of the first fluid passages326and a minimum diameter of the first bevel378is positioned adjacent the first sealing surface370. As will be described in more detail later herein, the first bevel378corresponds with a first beveled surface380formed in the housing104, as shown inFIGS.65and69. The intermediate surface322also comprises a second bevel382positioned between the second sealing surface372and the openings334of the first fluid passages326. The second bevel382extends around the entire intermediate surface322in an endless manner and surrounds the longitudinal axis324of the body316. The second bevel382shown inFIG.64is annular. In alternative embodiments, the first bevel may have non-annular shape, such as an oval shape. A maximum diameter of the second bevel382is positioned adjacent the second sealing surface372and a minimum diameter of the second bevel382is positioned adjacent the openings334of the first fluid passages326. The second sealing surface372and the maximum diameter of the second bevel382both have a greater diameter than the maximum diameter of the first bevel378and the diameter of the first sealing surface370. As will be described in more detail later herein, the second bevel382corresponds with a second beveled surface384formed in the housing104, as shown inFIGS.65and68. A small transition bevel386may extend between the second sealing surface372and the second bevel382. However, the transition bevel386does not engage the second beveled surface384, as shown inFIG.68. The transition bevel386helps reduce friction between the fluid routing plug116and the housing104during installation. As described above, the first and second bevels378and382are positioned between the first and second sealing surfaces370and372. The first and second bevels378and382help alleviate stress in the fluid routing plug116during operation. In alternative embodiments, the intermediate surface may only include a single bevel positioned between the first and second sealing surfaces. Continuing withFIG.64, the various diameters of the intermediate surface322are shown in more detail. The first sealing surface370has a diameter D1. The maximum diameter of the first bevel378has a diameter D2. The maximum diameter of the second bevel382has a diameter D3, and the second sealing surface372has a diameter D4. As described above in detail, D4is greater than D3, D3is greater than D2, and D2is greater than D1. With reference toFIG.65, in addition to being shaped to alleviate stress, the intermediate surface322is shaped to allow for easy installation of the fluid routing plug116within the horizontal bore106. The fluid routing plug116is installed into the horizontal bore106at the first outer surface108of the housing104. The fluid routing plug116is installed with the first surface318entering the horizontal bore106before the second surface320. The fluid routing plug116is pushed into the horizontal bore106until the first sealing surface370engages the first seal374and the second sealing surface372engages the second seal376. The first sealing surface370and first bevel378have smaller diameters than the second seal376and the second beveled surface384. Thus, clearance exists between these features as the fluid routing plug116is installed into the horizontal bore106. Providing such clearance during installation avoids unnecessary wear to both the housing104and fluid routing plug116during installation. With reference toFIGS.65and67, once the fluid routing plug116is installed within the housing104, an annular chamber388is formed between the walls of the housing104and the intermediate surface322. The intake bores170and172open into the chamber388. Only a couple of the openings334of the first fluid passages326may align with the intake bores170and172. Alternatively, the fluid routing plug116may be installed within the housing104such that none of the openings334directly align with the intake bores170and172. The chamber388provides a pathway for fluid from the intake bores170and172to flow around the fluid routing plug116and into the openings334of the first fluid passages326. The chamber388also provides space for proppant or other debris to collect during operation. Continuing withFIG.67, the walls of the housing104surrounding the horizontal bore106immediately adjacent the intake bores170and172are beveled, as shown by bevels390and392. The bevels390and392help reduce stress in the housing104during operation and increase the size of the annular chamber388. In alternative embodiments, the bevels390and392may be larger than those shown inFIG.67in order to increase the size of the chamber388, as shown for example inFIG.100F. Similarly, the walls of the housing104surrounding the horizontal bore106immediately adjacent the discharge bore178are also beveled, as shown by the bevel394inFIG.66. The bevel394reduces stress in the housing104during operation and helps direct fluid into the discharge bore178. Continuing withFIGS.65and68, the second bevel382and the second beveled surface384are shown in more detail. The second beveled surface382is positioned between the second seal376and the intake bores170and172. The second beveled surface384has an annular shape and surrounds the horizontal bore106in an endless manner. In alternative embodiments, the second beveled surface may have a shape that conforms to the shape of the second bevel formed in the fluid routing plug. When the fluid routing plug116is installed within the horizontal bore106, the second bevel382seats against the second beveled surface384, as shown inFIG.68. The bevels382and384meet at a non-right angle. Such angle reduces stress in the fluid routing plug116and the housing104during operation. The bevels382and384remain engaged during the forward and backwards stroke of the plunger290. Turning toFIGS.65and69, the first bevel378and the first beveled surface380are shown in more detail. The first beveled surface380is positioned between the intake bores170and172and the first seal374. The first beveled surface380has an annular shape and surrounds the horizontal bore106in an endless manner. In alternative embodiments, the first beveled surface may have a shape that conforms to the shape of the first bevel formed in the fluid routing plug. In contrast to the second bevel382, the first bevel378is sized to be spaced from the first beveled surface380when the fluid routing plug116is initially installed within the housing104, as shown by a gap398. The gap398provides space for the fluid routing plug116to expand during operation. As the plunger290retracts backwards away from the housing104, a significant amount of load is applied to the second bevel382. The applied load causes the fluid routing plug116to slightly compress, forcing the intermediate surface322at the first bevel378to expand outwards. As the first bevel378expands, it eventually engages with the first beveled surface380. Upon engaging the first beveled surface380, the load being applied to the second bevel382is shared with the first bevel378, thereby decreasing the load applied to the second bevel382. Without the gap398, the fluid routing plug116would not have room to expand, potentially causing damage to the fluid routing plug116and the housing104over time. As the plunger290extends forward into the housing104, the first bevel378will return to its un-expanded state, re-creating the gap398. The gap398will repeatedly be created and closed during operation as the plunger290reciprocates. In addition to providing space for the fluid routing plug116to expand, the gap398also provides a gas and fluid relief area during the forward stroke of the plunger290. Continuing withFIGS.68and69, because the second bevel382carries the majority of the load experienced by the fluid routing plug116during operation, the second bevel382is longer than the first bevel378. In alternative embodiments, the first bevel may be longer than that shown inFIG.69or be equal in length to the second bevel. In such embodiments, the first beveled surface formed in the housing may correspond with the chosen size of the first bevel. In further alternative embodiments, the first bevel may be sized to mate with the first beveled surface when the fluid routing plug is first installed within the housing. With reference toFIGS.65,70, and71, in order to prevent fluid from leaking around the fluid routing plug116during operation, the first and second seals374and376are positioned between the sealing surfaces370and372and the walls of the housing104surrounding the horizontal bore106. The first seal374is positioned within a first annular groove400formed in housing104and surrounding the horizontal bore106in an endless manner. The first groove400is positioned between the intake bores170and172and the second outer surface110of the housing104, as shown inFIG.65. The first groove400is characterized by two sidewalls402joined by a base404, as shown inFIG.71. The sidewalls402may join the base404via radius corners or at a 90 degree angle. In alternative embodiments, the first groove may have a non-concentric shape that corresponds with the shape of the first sealing surface. The second seal376is positioned within a second annular groove406formed in the housing104and surrounding the horizontal bore106in an endless manner. The second groove406is positioned between the discharge bore178and the intake bores170and172, as shown inFIG.65. The second groove406is characterized by two sidewalls408joined by a base410. The sidewalls408may join the base410via radius corners or at a 90 degree angle. In alternative embodiments, the second groove may have a non-concentric shape that corresponds with the shape of the second sealing surface. The second groove406has a larger diameter than that of the first groove400due to the diameter of the horizontal bore106at each groove, as shown inFIG.65. Likewise, the second seal376has a larger diameter than that of the first seal374. Because the first and second grooves400and406are formed in the housing104, no grooves are formed in the intermediate surface322of the fluid routing plug116for receiving a seal. When the fluid routing plug116is installed within the horizontal bore106, the first and second seal374and376tightly engage the corresponding first and second sealing surfaces370and372, as shown inFIGS.70and71. During operation, the first and second seals374and376wear against the first and second sealing surfaces370and372. If the first or second sealing surface370or372begins to erode, allowing fluid to leak around the fluid routing plug116, the plug116may be removed and replaced with a new plug116. The first or second seal374or376may also be replaced with a new seal, if needed. The first groove400shown inFIG.71is wider than the second groove406shown inFIG.70. As described below, each groove400and406is sized to correspond with the size of the seal installed within the groove. In alternative embodiments, the first and second grooves may be wider or narrower than those shown in the figures in order to accommodate the size of the seal installed within the groove. As discussed above, the fluid routing plug116may repeatedly stretch and contract in response to the changing fluid pressure. For example, when the plunger290is retracted out of the housing104, the fluid pressure at the first surface318is equal or approximately equal to the pressure of fluid delivered to the housing104from the intake manifolds166and168. Such fluid pressure may be around 100-200 psi, for example. When the plunger290extends into the housing104, the fluid at the first surface318may be pressurized to around 10,000 psi, for example. The first seal374, being positioned adjacent the first surface318of the fluid routing plug116experiences the constant change in fluid pressure. In contrast, the second seal376, being positioned adjacent the second surface320, experiences more static fluid pressure. The fluid pressure at the second surface320of the fluid routing plug116may remain at or close to 10,000 psi, for example. Continuing withFIGS.70and71, because the first seal374experiences more pressure fluctuations during operation than the second seal376, the first seal374may be more robust than the second seal376. For example, the first seal374is larger than the second seal376and has a generally square cross-sectional shape, while the second seal376has a circular cross-sectional shape. The first seal374may also have a higher durometer value than the second seal376. As described below, both seals374and376are bi-directional seals. In alternative embodiments, the second seal may be of the same construction as the first seal. Continuing withFIG.71, the first seal374is shown engaged with both side walls402of the first groove400. In operation, as the plunger290extends into the housing104, pressurized fluid pushes against the right side of the first seal374, helping to activate the first seal374and create a tight seal between the first seal374and the first sealing surface370. As the plunger290retracts from the housing104and the fluid pressure drops, the fluid pressure is greater on the left side of the first seal374. Thus, the fluid pressure may push against the left side of the first seal374, helping to activate the first seal374. Therefore, in operation, the first seal374may move slightly between its left and right side. Continuing withFIG.70, the second seal376is shown engaged with both side walls408of the second groove406. In operation, pressurized fluid within the housing104helps to activate the second seal376, thereby creating a tight seal between the second seal376and the second sealing surface372. Because the second seal376experiences primarily static fluid pressure, the second seal376may not move within the second groove406, as much as the first seal374moves within the first groove400. Continuing withFIGS.70and71, the first seal374also takes up approximately 97% of the open volume within the first groove400. Likewise the second seal376takes up almost 97% of the open volume within the second groove406. Normally, seals are configured to take up around 70% of the open volume within the groove the seal is installed within. The remaining open volume provides space for the seal to expand and move. However, in operation, fluid and proppants can fill the open volume and wear against the groove, eventually causing the walls of the groove to erode. If the walls of the groove are damaged, the housing104may need to be replaced. By sizing the grooves400and406so that the seals374and376take up almost all of the open volume within the corresponding grooves400and406, there is less room for fluid or proppants to fill any open space within the grooves. Specifically, fluid and proppants are prevented from entering any open volume on the back side of the seals374and376, thereby protecting the first and second grooves400and406from erosion. In alternative embodiments, the first seal may take less volume of the first groove than is shown inFIG.70. Likewise, in alternative embodiments, the second seal may take up less volume of the second groove than is shown inFIG.71. The other grooves formed in the housing and described herein may also be configured so that the corresponding seals take up approximately 97% of the open volume within the groove. Continuing withFIG.71, the first sealing surface370may extend up to immediately adjacent the first surface318of the body316. A first portion412of the intermediate surface322between the first bevel378and the first sealing surface370faces the housing104walls. A very small gap exists between the first portion412and the housing104. The gap may be as small as 0.001 inches in width. Such gap provides clearance to reduce friction between the fluid routing plug116and the housing104during installation and operation. Such gap also provides space for excess proppant to collect during operation. Continuing withFIG.70, a second portion416of the intermediate surface322between the second sealing surface372and the second surface320may face the walls of the housing104. A third portion418of the intermediate surface322between the second sealing surface372and the transition bevel386may also face the walls of the housing104. Like the first portion412, a very small gap exists between the second and third portions416and418and the housing104. The gaps may be as small as 0.001 inches in width. Such gaps provide clearance to reduce friction between the fluid routing plug116and the housing104during installation and operation. Such gaps also provide space for excess proppant to collect during operation. Turning back toFIG.65, as discussed above, the walls of the housing104surrounding the horizontal bore106are sized to allow for easy installation of the fluid routing plug116. The second groove406has a diameter D5. A maximum diameter of the second beveled surface384has a diameter D6. A maximum diameter of the first beveled surface380has a diameter D7, and the first groove400has a diameter D8. The diameter D8is greater than the diameter D7. The diameter D7is greater than the diameter D6, and the diameter D6is greater than the diameter D5. With reference toFIGS.72-76and85-89, the suction and discharge valves292and294are generally identical, with the exception that the discharge valve294may be larger in size than the suction valve292. As discussed above, the suction and discharge valves292and294each have a sealing element346and360. The sealing elements346and360each include a sealing surface420and422that tapers at an angle that matches the angle of the tapered wall340and356of the fluid routing plug116. Thus, the sealing surfaces420and422each taper at an angle of 30 or 45 degrees. Preferably, the tapered walls340and356and the sealing surfaces420and422both taper at an angle of 45 degrees. Forming the mating tapered walls340and356and sealing surfaces420and422at 45 degrees provides more surface area for the valves292and294to seal against the fluid routing plug116. Providing more sealing surface area or a larger “strike face” helps distribute the forces applied to the valves292and294and the fluid routing plug116, thereby providing more evenly distributed sealing. Providing more evenly distributed sealing prevents certain areas from wearing faster than others, helping to increase the life of the parts. Each valve292and294also has an outer sealing diameter E and an inner sealing diameter F, as shown inFIGS.72and85. The ratio of the outer sealing diameter E to the inner sealing diameter F is preferably 1.55 or greater. This ratio helps increase the life of the valves292and294and reduce any turbulent fluid flow during operation. The valves292and294and the fluid routing plug116are configured so that no portion of the valves292and294enters the first or second fluid passages326and336during operation. Additionally, no portion of the valve292enters the blind bore328during operation. Rather, the suction valve292is configured only to cover the entrance342of the blind bore330on the first surface318, and the discharge valve294is configured only to cover the openings364of the second fluid passages336on the second surface320. Continuing withFIGS.72-76, the suction valve292is shown in more detail. The suction valve292comprises the sealing element346joined to a stem424. When the suction valve292is installed within the horizontal bore106, the stem424extends along an axis that is parallel to or aligned with central the longitudinal axis114of the housing104. The sealing element346comprises opposed first and second surfaces426and428joined by the sealing surface420. A groove430is formed in the sealing surface420adjacent the first surface426, as shown inFIG.76. A seal432is installed within the groove430. The groove430is characterized by a first sidewall434joined to a second sidewall436. The sidewalls434and436may be joined by an inner groove438. The groove430is sized to correspond with the inward facing surface of the seal432. An outward facing surface of the seal432comprises a convex surface440joined to a concave surface442. The seal432is preferably made of a polyurethane compound. In alternative embodiments, the seal may be made of a different elastomer material. When the suction valve292seals against the first surface318of the fluid routing plug116, the seal432and a portion of the sealing surface420mate with the tapered wall340, as shown inFIG.51. The seal432is shaped so that the convex surface440displaces into, or toward, the concave surface442as the seal432engages the tapered wall340. This relative movement allows the shear forces to be dissipated, increasing the life of the seal432and the suction valve292. If the seal432becomes worn and no longer seals properly, the seal432may be removed and replaced with a new seal432. In alternative embodiments, the seal and groove may have various shapes and sizes, as desired. In further alternative embodiments, the sealing surface may not include a groove and corresponding seal. Continuing withFIG.76, the second surface428of the sealing element346is sized to cover the entrance342of the blind bore328, as shown inFIG.51. A cutout444is formed within the second surface428. The cutout444creates a small cavity within the second surface428. The cavity provides space for fluid to collect and apply pressure to the suction valve292. Such pressure helps force the suction valve292to move axially to an open position. Continuing withFIGS.75and76, the stem424projects from the first surface426of the sealing element346. An annular void446is formed in the first surface426and surrounds the stem424. The first surface426further includes a ring-shaped outer rim448that surrounds the annular void446and the stem424. The outer rim448joins the sealing surface420. The annular void446reduces weight within the suction valve292and helps orient the valve's center of gravity during operation. An annular groove450is formed in the outer rim448. The groove450is configured for receiving a bottom portion of a spring452, as shown inFIG.83. As described below, a top portion of the spring452engages with the suction valve guide296, as shown inFIGS.83and84. The spring452biases the suction valve292in the closed position. Positioning the spring452on the outer rim448helps to stabilize the suction valve292during operation. With reference toFIGS.77-82, the stem424is configured to move axially within the suction valve guide296. The suction valve guide296may also be referred to as a cage for the suction valve292. The suction valve guide296comprises a body454having opposed first and second surfaces456and458. A central passage460is formed within the body454and interconnects the first and second surfaces456and458. A plurality of legs462extend out from the body454adjacent its first surface456and project downward towards its second surface458. The suction valve guide296shown inFIGS.77-82has six evenly spaced legs462formed around its body454. In alternative embodiments, more or less than six legs may be formed on the body and may be non-uniformly spaced. The legs462gradually decrease in thickness from the body454to a bottom surface464of each leg462. The bottom surface464of each leg462is extremely thin so that the legs462do not block or interfere with the openings348of the second fluid passages336on the first surface318, as shown inFIG.50. Continuing withFIGS.77-82, an outer surface of each leg462includes a bevel466. The bevels466are configured to engage a corresponding bevel468formed in the walls of the housing104, as shown inFIGS.50and51. The suction valve guide296is inserted into the horizontal bore106until the bevels466and468engage, allowing the guide296to bottom out on the walls of the housing104. Once the bevels466and468are engaged, the suction valve guide296is held against the walls of the housing104by the spring452and fluid pressure. When the suction valve guide296is in its installed position, the bottom surface464of each of the legs462hovers just above the first surface318of the fluid routing plug116, leaving a gap between the legs462and the plug116. The bottom surfaces464do not directly contact the fluid routing plug116in order to prevent the suction valve guide296from applying load to the plug116during operation. Continuing withFIG.80, a tubular insert470is installed within the central passage460of the body454. The insert470may be press-fit within the passage460. The insert470extends the length of the central passage460and is formed from a more wear resistant material than the suction valve guide296. For example, the insert470may be made of tungsten carbide, while the suction valve guide296may be made of high strength alloy steel. The stem424is installed within the insert470and reciprocates within the insert470during operation, as shown inFIGS.50and51. Any fluid contained within the insert470drains from the opening of the central passage460on the first surface456of the body454. During operation, the stem424may wear against the insert470as it reciprocates. The insert470helps decrease the rate of wear and helps the stem to wear evenly against the insert. Forming only the insert470out of a wear resistant material helps reduce the cost of the other parts, that do not experience as much wear during operation. Turning toFIGS.83and84, the spring452is interposed between the suction valve292and the suction valve guide296. The spring452is held between the outer rim448of the suction valve292and an inner surface472of the legs462. At least a portion of the spring452surrounds the body454of the suction valve guide296. As the suction valve292moves to an open position, the spring452compresses between the suction valve292and the suction valve guide296. With reference toFIGS.85-89, the discharge valve294is shown in more detail. As discussed above, the discharge valve294is constructed identically to the suction valve292, with the exception that the discharge valve294may be larger in size. The discharge valve294shown inFIGS.85-89, for example, has a larger sealing surface422and a longer stem474than the suction valve292. When the discharge valve294is installed within the horizontal bore106, the stem424extends along an axis that is parallel to or aligned with the central longitudinal axis114of the housing104. A seal475is installed within a groove477formed in the sealing surface422and is configured to engage with the tapered wall356formed in the second surface320of the fluid routing plug116. A bottom surface476of the discharge valve294is sized to cover the central base354, as shown inFIG.50. With reference toFIGS.90-95, the stem474formed on the discharge valve294is configured to move axially within the discharge valve guide298. The discharge valve guide298may also be referred to as a cage for the discharge valve294. The discharge valve guide298comprises a body478having opposed first and second surfaces480and482joined by an intermediate surface484. The intermediate surface484includes a front portion486, a medial portion488, and a rear portion490. The medial portion488has a larger diameter than both the front and rear portions486and490. The front portion486has a slightly larger diameter than the rear portion490. Continuing withFIGS.90-95, a blind bore492is formed in the first surface480and extends into the front portion486of the body478. The blind bore492is configured to receive a tool used to grip the discharge valve guide298. The front portion486is sized to be received within the cutout308formed in the retainer300, as shown inFIGS.50and51. When the discharge valve guide298and the retainer300are engaged, the blind bore492opens into the central passage310formed in the retainer300. A central passage494is formed in the body478and opens on the second surface482, as shown inFIGS.93and94. The central passage494opens in the body478into an axially blind counterbore496. A plurality of relief ports498are formed in the body478. Each relief port498interconnects the counterbore496and a base500of the medial portion488, as shown inFIG.94. Continuing withFIGS.93and94, a tubular insert502is installed within the central passage494. The insert502is identical to the insert470, with the exception that the insert502may be larger than the insert470. During operation, the stem474moves axially within the insert502installed within the central passage494. Any fluid within the insert502drains from the body478through the counterbore496and the relief ports498. Continuing withFIGS.90-92, a plurality of legs504project from the medial portion488and extend towards the second surface482of the body478. The discharge valve guide298shown inFIGS.90-95comprises five legs504. The legs504are positioned on the body478so as to leave a large space506between at least two adjacent legs504. Other than the space506, the legs504are equally spaced from one another. The space506is intended to align with the discharge bore178, thereby preventing any legs504from blocking the discharge bore178during operation. Providing the space506therefore allows fluid to flow freely between the discharge valve294and the discharge bore178without significant obstructions. The space506also helps minimize wear applied to the legs504by the flowing fluid over time. In alternative embodiments, the body may have more or less than five legs as be spaced, as desired, as long as the legs are positioned on the body so as to leave a large space between at least two of the legs. With reference toFIG.90, each of the legs504has a thicker upper portion508and thinner lower portion510. The thicker upper portion508provides strength to the legs504while the lower portion510is thinned in order to provide more room for fluid flow around the legs504. The upper portion508also includes a tapered inner surface512. Tapering the inner surface512of the legs504provides strength and alleviates stress in the legs504during operation. Continuing withFIGS.90-95, when the discharge valve guide298is installed within the horizontal bore106, a bottom surface514of each leg504engages the outer rim352of the second surface320of the fluid routing plug116, as shown inFIGS.50and51. The discharge valve guide298is held against the fluid routing plug116by the retainer300. Such engagement helps keep the second bevel382of the fluid routing plug116seated against the second beveled surface384, as shown inFIGS.65and68. Continuing withFIGS.93and95, a dowel pin516is installed within a blind bore517formed in the medial portion488of the body478. The dowel pin516is configured to be received within a dowel pin hole or groove518formed in the walls of the housing104surrounding the horizontal bore106, as shown inFIGS.96and97. The discharge valve guide298is installed within the horizontal bore106such that the dowel pin516is positioned within the dowel pin hole518. Such positioning ensures that the space506between the pair of legs504aligns with the discharge bore178, thus preventing any legs504from blocking the discharge bore178during operation. Continuing withFIGS.96and97, a seal520is interposed between the intermediate surface484of the body478and the walls of the housing104. The seal520may be identical to the second seal376shown inFIGS.65and70. In alternative embodiments, the seal may be identical to the first seal374shown inFIGS.65and71. The seal520is installed within a groove522formed in the housing104. The groove522is characterized by two sidewalls524joined to a base526. The sidewalls524may join the base526via radius corner or at a 90 degree angle. During operation, the seal520wears against the outer intermediate surface484of the discharge valve guide298. If the intermediate surface484begins to erode, allowing fluid to leak around the seal520, the discharge valve guide298may be removed and replaced with a new discharge valve guide298. With reference toFIGS.98and99, a spring528is installed between the discharge valve294and the discharge valve guide298. A bottom portion of the spring528sits in a groove530, shown inFIG.89, formed in an outer rim532of the discharge valve294. A top portion of the spring528engages a ledge534formed in the base500of the medial portion488of the discharge valve guide298. During operation, the spring528compresses against the ledge534of the medial portion488. Turning toFIG.100, the components installed within the housing104are installed through the first surface108, starting with the suction valve guide296. The diameter of the installed components slightly increases from the second surface320to the first surface318. For example, the suction valve guide296has smaller outer diameters than the fluid routing plug116, and the fluid routing plug116has smaller outer diameters than the discharge valve guide298. The discharge valve guide298has smaller outer diameters than the retainer300. Likewise, the diameters of the walls surrounding the horizontal bore106generally increase from the second surface110to the first surface108. As shown inFIG.100, a diameter D12of the horizontal bore106is greater than a diameter D11of the horizontal bore106. The diameter D11of the horizontal bore106is greater than a diameter D10of the horizontal bore106. The diameter D10of the horizontal bore106is greater than a diameter D9of the horizontal bore106. Such construction allows the components to be installed without engaging the walls of the housing104until the component is at its intended installed position. The seals374,376, and520may be installed within the housing104prior to installing the other components described above. Turning toFIGS.100A-100E, another embodiment of a fluid routing plug550is shown. The fluid routing plug550may be installed within the housing104in place of the fluid routing plug116. The fluid routing plug550is identical to the fluid routing plug116, with a few exceptions. The fluid routing plug550comprises a body552having a first outer surface554joined to a second outer surface556by an intermediate outer surface558. The second surface556of the fluid routing plug550generally identical to the second surface320of the fluid routing plug116, but a central base560formed in the second surface556is spaced from an edge562of a tapered wall564formed in the second surface556. The central base560is spaced from the tapered wall564such that a throat566is formed between the central base560and the tapered wall564. Continuing withFIGS.100A-100D, a blind hole568is formed in the central base560and a plurality of openings570corresponding to a plurality of second fluid passages572open on the central base560and surround the blind hole568. In operation, fluid exiting the openings570flows into the throat566before pushing against the discharge valve294engaged with the second surface556. Allowing fluid to gather in the throat566before contacting the discharge valve294helps the fluid to contact more surface area of the discharge valve294, instead of having a plurality of single points of contact from each second fluid passage opening. Allowing the fluid to contact more surface area of the discharge valve294helps reduce wear to the valve over time. Continuing withFIGS.100E and100F, the intermediate surface558of the fluid routing plug550is identical to the intermediate surface322formed on the fluid routing plug116. However, the intermediate surface558may include a cutout576adjacent the second surface556. The cutout576provides space for fluid or proppant to collect during operation, as shown inFIG.100G. The cutout576also helps reduce friction during installation of the fluid routing plug550within the housing104. A small gap578may also exist between the walls of the housing104and the intermediate surface558between a second sealing surface580and the cutout576, as shown inFIG.100G. The gap578helps the seal376breath during operation. Continuing withFIG.100B, the first surface554of the fluid routing plug550is identical of the first surface318of the fluid routing plug116, with the exception of its outer rim582. The outer rim582is flat and wider than the outer rim338, shown inFIG.55. Because the outer rim582is wider, a plurality of openings584for the second fluid passages572may have a slightly larger diameter than the openings348, shown inFIG.56. Likewise, the openings570may also have a slightly larger diameter than the openings364shown inFIG.54. Providing a slightly larger diameter for the second fluid passages572helps reduce fluid velocity through the fluid routing plug550during operation. Reducing fluid velocity within the fluid routing plug550helps reduce wear to the fluid routing plug550over time. Turning toFIGS.101-109, another embodiment of a fluid routing plug600is shown. The fluid routing plug600may be installed within the housing104in place of the fluid routing plug116. The fluid routing plug600is identical to the fluid routing plug116, with a few exceptions. The fluid routing plug600comprises a body602having a first outer surface604joined to a second outer surface606by an intermediate outer surface608. In contrast to the fluid routing plug116, the first and second surfaces604and606of the fluid routing plug600are configured so that each surface604and606has identically sized tapered walls610and612, as shown inFIG.103. Because the tapered walls610and612are the same size, a suction valve614and a discharge valve616used with the fluid routing plug600may be identical in size, as shown inFIGS.108and109. Using the same size suction and discharge valves614and616helps equalize the forces applied to the fluid routing plug600and the valves614and616during operation, helping to reduce any wear to the parts over time. Making the suction and discharge valves614and616identical also makes replacing the valves614and616during operation easier. Continuing withFIGS.103,105, and106, the tapered wall612formed in the second surface606extends between an outer rim618and an annular groove620formed in the center of the second surface606. The annular groove620may be considered a central base formed in the second surface606. The groove620surrounds a blind bore622formed in the center of the second surface606. The blind bore622is identical to the blind bore362formed in the fluid routing plug116, as shown inFIG.55. The groove620is characterized by two parallel sidewalls624joined by a base626. The sidewalls624each extend at a non-zero angle relative to a central longitudinal axis628of the body602. Because the sidewalls624of the groove620extend at an angle, the base626of the groove620extends at a non-zero angle relative to the central longitudinal axis628of the body602. Preferably, the base626extends at approximately the same angle as the tapered wall612so that the base626and the tapered wall612are in a generally parallel relationship. The tapered wall612shown inFIG.103extends at a 45 degree angle relative to the central longitudinal axis628. An annular inner edge638of the tapered wall612is joined to the outer sidewall624of the groove620at a right angle. The diameter of the inner edge638of the tapered wall612is the same size as a diameter of an entrance630of an axially blind bore632formed in the first surface604, as shown inFIG.103. In alternative embodiments, the groove formed in the second surface and the inner edge of the tapered wall may not have an annular shape. Continuing withFIGS.103,105, and106, a plurality of second fluid passages634are formed in the body602. The second fluid passages634are identical to the second fluid passages336formed in the fluid routing plug116, shown inFIGS.52-64, with the exception of the positioning of their openings636on the second surface606. Each second fluid passage634opens on the base626of the groove620formed in the second surface606. Thus, the openings636are axially spaced from the inner edge638of the tapered wall612. Because the sidewalls624of the groove620are formed at an angle, the inner edge638of the tapered wall612slightly overlaps the openings636, as shown inFIG.106. By positioning the openings636in an axially spaced relationship with the inner edge638of the tapered wall612, the size of the tapered wall612can be decreased without decreasing the size of the openings636. The annular groove620also functions as a throat, similar to the throat566formed in the fluid routing plug550. Because the tapered wall612is decreased in size from the tapered wall356shown inFIG.55, the outer rim618on the second surface606is wider than the outer rim352. The outer rim618also tapers between the intermediate surface608and the tapered wall612, as shown inFIGS.103and104. Such taper increases the length of the tapered wall612without increasing the length of the intermediate surface608. Continuing withFIGS.101-107, the first surface604is identical to the first surface318shown inFIGS.53,55, and56, with the exception of its outer rim640. Instead of tapering like the outer rim338, shown inFIG.55, the outer rim640is flat. The outer rim640is flat in order to slightly decrease the size of the tapered wall610to match the size of the tapered wall612. The intermediate surface608of the fluid routing plug600is identical to that of the fluid routing plug116, shown inFIG.64. A plurality of first fluid passages642formed in the body602are identical to the first fluid passages326, shown inFIGS.55,57, and59. The second fluid passages634open on the outer rim640of the first surface604, as shown by the openings644. The openings644are positioned in groups645, in the same manner as the second fluid passages336formed in the fluid routing plug116, as shown inFIG.56. The openings636on the second surface606may remain spaced in groups645, as shown inFIG.106. With reference toFIGS.108and109, the fluid routing plug600routes fluid throughout the housing104in the same manner as the fluid routing plug116. The suction valve guide296is shown engaged with suction valve614. Another embodiment of a discharge valve guide647is shown engaged with the discharge valve616. The discharge valve guide647is identical to the discharge valve guide298, shown inFIGS.90-95, with a few exceptions. A counterbore649formed in the guide647is larger than the counterbore496. The counterbore649is larger in order to accommodate the shorter stem646of the discharge valve616. An insert651installed within the discharge valve guide647is the same size as the insert470installed within the suction valve guide296. With reference toFIGS.110-114, as discussed above, in contrast to the valves292and294, the valves614and616are identical in size and shape. The valves614and616are generally identical to the valves292and294, with a few exceptions. Each valve614and616comprises a sealing element652joined to a stem646. The stem646projects from a first surface650of the sealing element652. An annular cutout648is formed within a medial portion of the stem646. The cutout648provides space for fluid or proppants to collect during operation. Providing such space prevents the fluid and proppants from rubbing against the inserts470and502. The suction and discharge valves292and294may be configured to include an annular cutout within their stems424and474. Continuing withFIGS.110-114, the sealing element652further includes a second surface668joined to the first surface650by a sealing surface658. A groove656is formed in the sealing surface658for housing a seal654. The groove656is identical to the groove430, shown inFIG.76. An outward facing surface of the seal654comprises a sidewall660joined to a tapered base662. In operation, the tapered base662engages the tapered walls610and612of the fluid routing plug600. The sidewall660may compress creating a tight seal. The first surface650of the sealing element652includes an outer rim664. An outer ledge666surrounds the outer rim664. A bottom portion of a spring engages the outer rim664and is held in place by the outer ledge666. While not shown, a cutout may be formed in the second surface668of the sealing element652, like the cutout444, shown inFIG.76. One or more kits may be useful in assembling the fluid end section102. A kit may comprise a plurality of housings104and a plurality of the corresponding fluid routing plugs116or600. The kit may also comprise a plurality of suction valves292or614, discharge valves294or616, suction valve guides296, discharge valve guides298or657, springs452and528, retainer300, stuffing box140, retainer232, plunger packing224, packing nut276, fastening system234, discharge conduit174, and the various seals described herein. The kit may also comprise the intake manifolds166and168, pipe system176, connect plate118, fastening system146and stay rods120. The kit may also comprise other various features described herein for use with the fluid end100. Unless specifically described herein, the various components of the fluid end100may be made of high strength alloy steel, such as carbon steel or stainless steel. With reference toFIGS.115-117, an alternative embodiment of a fluid routing plug700is shown. The fluid routing plug700may be installed within the housing104in place of the fluid routing plug116. The fluid routing plug700is identical to the fluid routing plug116, with the exception of the shape of its first and second bevels702and704. When the fluid routing plug700is first installed within the horizontal bore106, the second bevel704only partially engages a second beveled surface706, as shown inFIG.116. The bevels704and706mate at a second bevel mating surface708and a second beveled surface mating surface710. Below the mating surfaces708and710, the second bevel704and the second beveled surface706have mating angles that are not equal, causing a gap712to exist between the bevels704and706. Specifically, the second bevel704may have a slightly convex shape so that portions of the second bevel704do not match the flat shape of the second beveled surface706. The width of the gap712gradually increases between the mating surfaces708and710and a bottom portion714of the second bevel704and a bottom portion716of the second beveled surface706. Thus, the width H of the gap712is wider than the width G of the gap712. Because the second bevel704has a slightly convex shape, the angle between the mating surfaces708and710is different from the angle between the bottom portions714and716. Turning toFIG.117, the first bevel702and the first beveled surface718are shown in more detail. Like the second bevel704, the first bevel702may only partially engage a first beveled surface718. The bevels702and718mate at a first bevel mating surface720and a first beveled surface mating surface722. Below the mating surfaces720and722, the first bevel702and the first beveled surface718have mating angles that are not equal, causing a gap724to exist between the bevels702and718. Specifically, the first bevel702may have a slightly convex shape so that portions of the first bevel702do not match the flat shape of the first beveled surface718. The width of the gap724gradually increases between the mating surfaces720and722and a bottom portion726of the first bevel702and a bottom portion728of the first beveled surface718. Thus, the width J of the gap724is wider than the width I of the gap724. Because the first bevel702has a slightly convex shape, the angle between the mating surfaces720and722is different from the angle between the bottom portions726and728. The width of the gaps712and724has been exaggerated inFIGS.116and117for illustration purposes. In reality, portions of the gaps712and724may be approximately 0.002 inches in width, for example. However, the gaps712and724may be wider or smaller depending on the materials and forces used. As discussed above, in operation, the fluid pressure applied to the fluid routing plug700will cause the plug700to compress and expand as the plunger290retracts from the housing104. As the fluid routing plug700starts to expand, the bottom portion714of the second bevel704will move to engage the bottom portion714of the second beveled surface706, causing the bottom portions714and716to mate. Likewise, the bottom portion726of the first bevel702will move to engage the bottom portion728of the first beveled surface718. Such movement of the fluid routing plug700distributes the load applied to the fluid routing plug700through the length of the first and second bevels702and704. With reference toFIGS.118-120, an alternative embodiment of a fluid routing plug Boo is shown. The fluid routing plug Boo may be installed within the housing104in place of the fluid routing plug116. The fluid routing plug Boo is identical to the fluid routing plug700, with the exception of the shape of its first and second bevels802and804. Like the fluid routing plug700, the second bevel804is sized to leave a gap806between the second bevel804and a second beveled surface808when the fluid routing plug Boo is first installed within the housing104. In contrast to the gap712, an angle formed between the mating surfaces810and812and bottom portions814and816of the second bevel804and second beveled surface808remains the same. Thus, an area K of the gap806has the same angle as an area L of the gap806. Likewise, the first bevel802is shaped so that an angle formed between the first bevel802and a first beveled surface820stays relatively the same between mating surfaces822and824and bottom portions826and828. Thus, the width M of the gap818has approximately the same angle as the width N of the gap818. The width of the gaps806and818has been exaggerated inFIGS.119and120for illustration purposes. In reality, portions of the gaps806and818, for example, may be approximately 0.002 inches in width. However, the gaps806and818may be wider or smaller depending on the materials and forces used. As discussed above, the first and second bevels802and804expand during operation. Such movement of the fluid routing plug800distributes the load applied to the fluid routing plug800through the length of the first and second bevels802and804. In alternative embodiments, the first bevel may be configured to have a gap that increases in size, as shown inFIG.117, while the second bevel may be configured to have a gap that increases by a different amount, as shown inFIG.119, and vice versa. In further alternative embodiments, the width of the gap may be of various shapes and sizes depending on the materials used and forces involved. In even further alternative embodiments, the intermediate surface of the fluid routing plug may include any combination of the different bevel constructions described herein. Turning toFIGS.121-128, another embodiment of a fluid routing plug900is shown. The fluid routing plug900may be installed within the housing104in place of the fluid routing plug116. The fluid routing plug900is identical to the fluid routing plug116, with a few exceptions. The fluid routing plug900comprises a body902having a first outer surface904joined to a second outer surface906by an intermediate outer surface908. A plurality of first fluid passages910are formed in the body902and interconnect the intermediate surface908and the first surface904by way of an axially blind bore912, as shown inFIG.124. In contrast to the first fluid passages326, shown inFIGS.55and58, a longitudinal axis914of each first fluid passage910does not intersect a central longitudinal axis916of the body902, as shown inFIG.125. Rather, the first fluid passages910are formed such that the longitudinal axis914of each passage910is offset from the central longitudinal axis916of body902. The offset configuration of the first fluid passages910encourages a vortex type flow of fluid about the central longitudinal axis916, thereby reducing fluid turbulence during operation. In alternative embodiments, the longitudinal axis914of each first fluid passage910may intersect the longitudinal axis916of the body902. A plurality of openings918formed on the intermediate surface908for the first fluid passages910are similar to the openings334, shown inFIGS.57and59, but have a more oblong shape, as shown inFIG.121. The oblong shape shown inFIG.121has opposed first and second ends920and922. The second end922, which is closer to the second surface906, is slightly wider than the first end920. The unequal size of the ends920and922helps direct fluid along the offset longitudinal axis914of the first fluid passages910. The unequal size of the ends920and922also helps increase the wall thickness in certain areas of the body902between the first fluid passages910and a plurality of second fluid passages924. In alternative embodiments, the opposed ends of the openings may be identical in size or may be shaped identical to the openings334, shown inFIGS.57and59. The opening918of the first fluid passage910shown inFIG.121extends along an axis that is parallel to the longitudinal axis916of the body902. In alternative embodiments, the openings of the first fluid passages may extend at a non-zero angle relative to the longitudinal axis916of the body902, as shown for example by the openings972shown inFIG.128D. The angle at which the first fluid passages910are formed in the body902may vary, as desired, in order to increase the wall thickness within the body902and reduce stress in the body902during operation. Continuing withFIGS.122and126, each of the second fluid passages924formed in the body902interconnects the first and second surfaces904and906. The second fluid passages924are identical to the second fluid passages336, shown inFIGS.60-63, but the second fluid passages924are slightly pivoted from the position of the second fluid passages336. Each second fluid passage924is pivoted so that it has a compound angle with respect to the central longitudinal axis916, as shown inFIGS.122,123126, and127. Meaning, each second fluid passage924extends such that it has two different angles relative to the central longitudinal axis916—up-and-down, and side-to-side. Like the first fluid passages910, forming the second fluid passages924at such angles encourages a vortex type flow of fluid about the central longitudinal axis916, thereby reducing fluid turbulence during operation. Continuing withFIGS.124,127, and128, the first surface904of the fluid routing plug900may be identical to the first surface318, shown inFIGS.53,55, and56. However, an outer rim926of the first surface904may be flat rather than tapered. The second surface906of the fluid routing plug900is identical to the fluid routing plug116, but a central base928formed in the second surface906may be slightly set back within the body902, as compared to the central base354, shown inFIGS.54and55. An outer rim930on the second surface906may be slightly wider than the outer rim352, shown inFIGS.54and55. The intermediate surface908of the fluid routing plug900may be identical to the intermediate surface322of the fluid routing plug116. Alternatively the intermediate surface may be identical to those formed on the fluid routing plug700or800. In alternative embodiments, the first and second surfaces904and906of the fluid routing plug900may be configured so that its tapered walls932and934are the same size, like the fluid routing plug600. In further alternative embodiments, the first and second surfaces of the fluid routing plug900may be identical to the first and second surfaces of the fluid routing plug116. Turning toFIGS.128A-128G, another embodiment of a fluid routing plug950is shown. The fluid routing plug950may be installed within the housing104in place of the fluid routing plug116. The fluid routing plug950is identical to the fluid routing plug900, with a few exceptions. The fluid routing plug950comprises a body962having a first outer surface964joined to a second outer surface952by an intermediate outer surface966. In contrast to the fluid routing plug900, the second surface952of the fluid routing plug950is formed identically to the second surface556of the fluid routing plug55o, shown inFIGS.100A-100E. A central base954formed in the second surface952is spaced from an edge956of a tapered wall958such that a throat960is formed within the second surface952. The throat960serves the same purpose as the throat566formed in the fluid routing plug550. Continuing withFIG.128A-128G, a plurality of first fluid passages968, shown inFIG.128G, and a plurality of second fluid passages970, shown inFIG.128A, are formed in the body962. The first and second fluid passages968and970are identical to the first and second passages910and924formed in the fluid routing plug900. However, as discussed above, an opening972of the first fluid passages968may extend along a non-zero angle relative to a central longitudinal axis974of the body962, as shown inFIG.128D. In alternative embodiments, the openings972may be identical to the openings918, shown inFIG.121. Like the fluid routing plug900, the angle at which the first fluid passages968are formed in the body962may vary, as desired, in order to increase the wall thickness within the body962and reduce stress in the body962during operation. In alternative embodiments, the first and second surfaces964and952of the fluid routing plug950may be configured like the fluid routing plug600. In further alternative embodiments, the first and second surfaces of the fluid routing plug950may be identical to the first and second surfaces of the fluid routing plug116. Turning toFIGS.129-131, another embodiment of a fluid routing plug1000is shown. The fluid routing plug1000may be installed within the housing104in place of the fluid routing plug116. The fluid routing plug1000is identical to the fluid routing plug116, but includes a first and second annular recess1002and1004formed in its intermediate surface1001. The first annular recess1002is positioned between a first bevel1006and a first sealing surface1008. The second annular recess1004is positioned between a second sealing surface1010and a second bevel1012. When the fluid routing plug1000is installed within the horizontal bore106, a small annular space exists between the wall of the housing104and each recess1002and1004. The space provides relief areas for excess fluid or proppant to collect during operation. The first and second recesses1002and1004may also be formed in the intermediate surfaces of the fluid routing plugs550,600,700,800,900, and950. In alternative embodiments, the first and second surfaces of each of the fluid routing plugs550,600,700,800,900, and950may each be sized so as to engage with identically sized suction and discharge valves292,294,614or616, as discussed with regard to fluid routing plug600. In further alternative embodiments, the first and second surfaces of each of the fluid routing plugs550,600,700,800,900, and950may be sized so as to engage with differently sized suction and discharge valves292,294,614or616. In such embodiment, the valves292,294,614or616may be sized as desired, as long as the ratio of the outer sealing diameter A to the inner sealing diameter B of each valve is preferably 1.55 or greater, as discussed with regard toFIGS.72and85. The desired size of the valve may vary depending on the desired fluid velocity within the corresponding fluid routing plug. With reference toFIGS.132-138, another embodiment of a fluid routing plug1100is shown. The fluid routing plug1100is identical to the fluid routing plug116, with the exception of its outer intermediate surface1102. The intermediate surface1102includes a first sealing surface1104, a second sealing surface1106, and a first bevel1108. In contrast to the fluid routing plug116, the intermediate surface1102does not include a second bevel. The first bevel1108is positioned between the first sealing surface1104and a first surface1110of the fluid routing plug1100. In contrast, the first bevel378is positioned between the first fluid passage326and the first sealing surface370in the fluid routing plug116, as shown inFIG.64. A plurality of first and second fluid passages1112and1114are formed in the fluid routing plug1100. The first and second fluid passages1112and1114are formed identically to the first and second fluid passages326and336formed in the fluid routing plug116. Likewise, the first surface1110and a second surface1109of the fluid routing plug1100are generally identical to the first and second surfaces318and320of the fluid routing plug116. The intermediate surface1102also includes a taper1116between the second sealing surface1104and a plurality of openings1118of the first fluid passages1112. Fluid is routed throughout the fluid routing plug1100and the housing1120in the same manner as the fluid routing plug116and housing104shown inFIGS.50and51. Continuing withFIGS.136-138, another embodiment of a housing1120is shown. The housing1120is identical to the housing104with the exception of the shape of the walls surrounding its horizontal bore1122. The walls surrounding the horizontal bore1122are shaped to mate with the fluid routing plug1100. The walls include a first beveled surface1124that mates with the first bevel1108, as shown inFIG.138. Unlike the housing104, the walls do not include a second beveled surface, as shown inFIG.137. When the fluid routing plug1100is installed within the housing1120, an annular chamber1126is formed between the walls of the housing1120and the taper1116on the intermediate surface1102. The chamber1126provides a pathway for fluid to flow from a pair of intake bores1128and1130and the openings1118. A first and second seal1132and1134installed within the housing1120are identical to the first and second seals374and376, shown inFIGS.70and71. With reference toFIGS.139-142, another embodiment of a fluid routing plug1200is shown. The fluid routing plug1200is identical to the fluid routing plug1100, with the exception of its first and second surfaces1202and1204. The first surface1202does not include an outer rim. Rather, the first surface1202has a tapered wall1206that tapers between an entrance1208of an axially blind bore1210and an outer edge1212of the first surface1202. A plurality of openings1214for a plurality of second fluid passages1216are formed in the tapered wall1206adjacent the outer edge1212. Removing the outer rim provides more surface area for the tapered wall1206and allows the tapered wall1206to taper at an angle of up to 60 degrees. Providing more surface area for the tapered wall1206provides more sealing area for a suction valve. Similarly, the second surface1204does not include an outer rim. Rather, the second surface1204has a tapered wall1218that tapers between a central base1220and an outer edge1222of the second surface1204. Removing the outer rim provides more surface area for the tapered wall1218and allows the tapered wall1218to taper at an angle of up to 60 degrees. Providing more surface area for the tapered wall1218provides more sealing area for a discharge valve. The fluid routing plug1200may be installed within the housing1120, shown inFIG.136. Fluid is routed throughout the fluid routing plug1200and the housing1120in the same manner as the fluid routing plug116and housing104, shown inFIGS.50and51. With reference toFIGS.143-150, another embodiment of a fluid routing plug1300is shown. The fluid routing plug1300comprises a body1302having opposed first and second outer surfaces1304and1306joined by an intermediate outer surface1308. A central longitudinal axis1310extends through the body1302and both surfaces1304and1306. A plurality of first fluid passages1312are formed within the body1302and interconnect the intermediate surface1308and the first surface1304, as shown inFIG.146. The first fluid passages1312interconnect the intermediate surface1308and the first surface1304by way of an axially blind bore1314, as shown inFIG.146. The first fluid passages1312have an oval cross-sectional shape similar to the first fluid passages326, shown inFIG.59. In contrast to the first fluid passages326, the first fluid passages1312extend orthogonally to the central longitudinal axis1310of the body1302. Continuing withFIG.147, a plurality of second fluid passages1316are formed in the body1302that interconnect the first surface1304and the second surface1306. Like the second fluid passages336, shown inFIGS.60-63, the second fluid passages1316extend along a straight-line path between the first and second surfaces1304and1306. The second fluid passages1316are offset from and do not intersect the first fluid passages1312. Continuing withFIGS.147and149, a first recessed cavity1318is formed in the first surface1304. The first cavity1318is characterized by a base1320surrounded by a side wall1322. The base1320extends between the side wall1322and an entrance1324of the blind bore1314. The side wall1322extends between the base1320and an outer rim1326of the first surface1304. A plurality of openings1328for the second fluid passages1316are formed in the outer rim1326. The openings1328are positioned in groups1330, similar to the openings348, shown inFIG.56. An annular first insert1332is installed within the first cavity1318such that it is fittingly received within the first cavity1318. The first insert1332has a base1334joined to a sidewall1336and a central opening1338. The base1334and sidewall1336are sized to correspond with the base1320and sidewall1322of the first recessed cavity1318. The first insert1332has a tapered surface1340that extends between the sidewall1336and the base1334. The tapered surface1340is sized to engage a suction valve1342, as shown inFIG.150. The first insert1332is made of a harder and more wear-resistant material than the body1302. For example, if the body1302is made of metal, the first insert1332may be made of tungsten carbide. Making the first insert1332out of a harder and more wear-resistant material than the body1302helps extend the life of the body1302. Further, the first insert1332may be removed and replaced with a new insert, if needed. Continuing withFIGS.145,147, and148, a central base1344is formed in the second surface1306of the body1302. A blind bore1348is formed in the central base1344, similar to the blind bore362shown inFIG.55. A plurality of openings1350for the second fluid passages1316are formed in the central base1344and surround the blind bore1348. In contrast, to the openings364, shown inFIG.54, the openings1350are spaced around in the blind bore1348in groups1352, similar to the openings1328on the first surface1304. A second recessed cavity1354is formed in the second surface1306of the body1302and surrounds the openings1350. The second recessed cavity1354is characterized by a base1356surrounded by a sidewall1358. The base1356of the second cavity1354serves as an extension of the central base1344. The sidewall1358joins the base1356and an outer rim1360. An annular second insert1362is installed within the second cavity1354such that the second insert is fittingly received within the second cavity1354. The second insert1362is identical to the first insert1332, but has an outer diameter that is greater than an outer diameter of the first insert1332. Likewise, a central passage1331formed in the second insert1362has a greater diameter than the central passage1338. A tapered surface1364of the second insert1362is configured to engage a discharge valve1366, as shown inFIG.150. Continuing withFIGS.143,144, and146, the intermediate surface1308of the fluid routing plug1300has a generally cylindrical shape. The intermediate surface1308includes a first sealing surface1368and a second sealing surface1370. The sealing surfaces1368and1370are configured to engage respective first and second seals1372and1374installed within another embodiment of a housing1376, as shown inFIG.150. The seals1372and1374may be identical to the first and seconds seals374and376installed within the housing104. The first sealing surface1368has a smaller diameter than the second sealing surface1370. The intermediate surface1308also includes a first bevel1378positioned between the first sealing surface1368and the first surface1304, and a second bevel1380positioned between the second sealing surface1374and the first fluid passages1312. With reference toFIG.150, the housing1376is similar to the housing104, with the exception of the shape of its horizontal bore1382. The walls surrounding the horizontal bore1382are shaped to engage the fluid routing plug1300. The walls engage the outer rims1326and1360on the first and second surfaces1304and1306and the first and second bevels1378and1380. Fluid is routed throughout the fluid routing plug1300and the housing1376in the same manner as the fluid routing plug116and housing104, shown inFIGS.50and51. With reference toFIGS.151-160, another embodiment of a fluid routing plug1400is shown. The fluid routing plug1400comprises a body1402having opposed first and second outer surfaces1404and1406joined by an intermediate outer surface1408. A central longitudinal axis1410extends through the body1402and both surfaces1404and1406, as shown inFIG.155. A plurality of first fluid passages1412are formed within the body1402and interconnect the intermediate surface1408and the first surface1404, as shown inFIG.156. The first fluid passages1412interconnect the intermediate surface1408and the first surface1404by way of a first axially blind bore1414, as shown inFIG.156. The first blind bore1414opens on the first surface1404of the body1402. Rather than having a plurality of wide first fluid passages, like those shown inFIG.55, the first fluid passages1412comprise a plurality of groups1416of smaller first fluid passages1412. The first fluid passages1412within each group1416are positioned in a side-by-side relationship, as shown by openings1417for the first fluid passages1412on the intermediate surface1408inFIG.164. Three first fluid passages1412are shown in each group1416inFIGS.151-154. In alternative embodiments, more or less than three first fluid passages may be included in each group. The first fluid passages1412each have a circular cross-sectional shape and extend orthogonally to the central longitudinal axis1410of the body1402, as shown inFIG.156. The fluid routing plug1400further comprises a plurality of second fluid passages1418formed within the body1402, as shown inFIG.155. The second fluid passages1418interconnect the first surface1404and the second surface1406of the body1402. The second fluid passages1418interconnect the first surface1404and the second surface1406by way of a second axially blind bore1420. The second blind bore1420opens on the second surface1406of the body1402. Each second fluid passage1418extends between the first surface1404and the second blind bore1420along a straight line path. Continuing withFIG.158, a first recessed cavity1422is formed in the first surface1404of the body1402. The first cavity1422is identical to the first cavity1318shown inFIG.149. An annular first insert1424is installed within the first cavity1422. The first insert1424is identical to the first insert1332, shown inFIG.149. The first insert1424is configured to engage a suction valve1426, as shown inFIGS.159and160. The first cavity1422is surrounded by an outer rim1428. A plurality of openings1430for the second fluid passages1418are formed on the outer rim1428. The openings1430are equally spaced around the outer rim1428. Continuing withFIG.157, a second recessed cavity1438is formed in the second surface1406and surrounds an entrance1440to the second blind bore1420. The second cavity1438is identical to the second cavity1354, shown inFIG.148. An annular second insert1442is installed within the second cavity1438. The second insert1442is identical to the second insert1362, shown inFIG.148. The second insert1442is configured to engage a discharge valve1444, as shown inFIGS.159and160. Continuing withFIG.155, a third blind bore1434is formed in a base1436of the second blind bore1420. The third blind bore1434is configured to engage with a tool to help remove the fluid routing plug1400from the horizontal bore with which it is installed. Turning back toFIGS.151,152, and154, the intermediate surface1408of the body1402varies in diameter throughout its length and has a generally cylindrical shape. The intermediate surface1408includes a first sealing surface1446and a second sealing surface1448. The first and second sealing surfaces1446and1448are configured to engage with a first and second seal1450and1452installed within another embodiment of a housing1454, as shown inFIGS.159and160. The first and second seal1450and1452may be identical to the first and second seals374and376installed within the housing104, as shown inFIGS.70and71. The first sealing surface1446is positioned between the first surface1404of the body1402and the first fluid passages1412. The second sealing surface1448is positioned between the second surface1406of the body1402and the first fluid passages1412. The intermediate surface1408has a first reduced diameter portion1456around the first fluid passages1412, as shown inFIG.154. When the fluid routing plug1400is installed within the housing1454, an annular chamber1458is formed between the first reduced diameter portion1456and the housing1454, as shown inFIG.159. An intake bore1460opens into the chamber1458. The chamber1458provides a pathway for fluid to flow from the intake bore1460to the openings1417of the first fluid passages1412. The intermediate surface1408also has a second reduced diameter portion1464, as shown inFIG.154. The second reduced diameter portion1464surrounds the second cavity1438, as shown inFIG.156. The second reduced diameter portion1464provides space for a plurality of legs1466of a discharge valve guide1468to engage the fluid routing plug1400, as shown inFIG.159. The legs1466help hold the components installed within the housing1454in place during operation. With reference toFIGS.159and160, the housing1454is generally similar to the housing104with the exception of the shape of its horizontal bore1470. While not shown, a stuffing box and related components may be attached to the housing1454. The walls surrounding the horizontal bore1470are shaped to engage the fluid routing plug1400. The first surface1404of the fluid routing plug1400seats against an annular shoulder1472formed in the housing1454. Fluid is routed throughout the fluid routing plug1400and the housing1454in the same manner as the fluid routing plug116and housing104shown inFIGS.50and51. A discharge bore1474is shown opening on a bottom surface1476of the housing1454inFIGS.159and160. In alternative embodiments, the discharge bore may open on a top surface of the housing, like the discharge bore178shown inFIGS.50and51. The housing1454shown inFIGS.159and160also includes a single intake bore1460. In alternative embodiments, a second intake bore may also be formed in the housing, like the housing104. With reference toFIGS.161-164, another embodiment of a fluid routing plug1500is shown. The fluid routing plug1500is identical to the fluid routing plug1400, but does not include a first and second sealing surface. Instead, a first and second annular groove1502and1504are formed in an intermediate surface1506. The grooves1502and1504are formed at the same position as the first and second sealing surface1446and1448formed in the fluid routing plug1400, as shown inFIG.159. A first and second seal1508and1510are installed within each respective first and second groove1502and1504. The fluid routing plug1500is installed within another embodiment of a housing1512, as shown inFIG.164. The housing1512is identical to the housing1454, but does not include any grooves for housing the first and second seals1508and1510. Rather, the first and second seals1508and1510engage the walls of the housing1512when the fluid routing plug1500is installed. Thus, the seals1508and1510are installed within the fluid routing plug1500, rather than the walls of the housing1512. Continuing withFIGS.161-163, the fluid routing plug1500also does not include the second reduced diameter portion formed in the fluid routing plug1400, as shown inFIG.154. Instead, the fluid routing plug1500has a uniform diameter between the second seal1510and its second surface1514. A discharge valve guide1516may engage the second surface1514of the fluid routing plug1500, as shown inFIG.164. With reference toFIGS.165-170, another embodiment of a fluid routing plug1600is shown. The fluid routing plug1600comprises a body1602having opposed first and second outer surfaces1604and1606joined by an intermediate outer surface1608. A central longitudinal axis1610extends through the body1602and both surfaces1604and1606, as shown inFIG.168. A plurality of first fluid passages1612are formed within the body1602and interconnect the intermediate surface1608and the first surface1604. The first fluid passages1612extend at a non-zero angle relative to the central longitudinal axis1610of the body1602. Continuing withFIGS.168and169, a first recessed cavity1614is formed in the first surface1604. The first cavity1614is identical to the first cavity1318, shown inFIG.149, but includes a plurality of openings1616for the first fluid passages1612, as shown inFIG.169. An annular first insert1618is installed within the first cavity1614. The first insert1618is identical to the first insert1332, but includes a plurality of insert passages1620. When the first insert1618is installed within the first cavity1614, the plurality of insert passages1620align with the plurality of first fluid passages1612in a one-to-one relationship, as shown inFIG.168. Thus, the insert passages1620become an extension of the first fluid passages1612. An opening1622of each first fluid passage1612on the intermediate surface1608has an oval shape, while an opening1624of each first fluid passage1612on the first surface1604has a circular shape, as shown inFIGS.165and166. The openings1624are equally spaced around the periphery of the first insert1618, as shown inFIG.167. The fluid routing plug1600includes more first fluid passages1612than the fluid routing plug116shown inFIG.52. However, the first fluid passages1612have a smaller diameter than a diameter of the first fluid passages326formed in the fluid routing plug116. Continuing withFIG.168, the fluid routing plug1600further comprise a single second fluid passage1626formed in the body1602. The second fluid passage1626interconnects the first surface1604and the second surface1606along a straight-line path. The second fluid passage1626has a circular cross-sectional shape and extends along the central longitudinal axis1610of the body1602. Because the body1602only includes a signal second fluid passage1626, the second fluid passage1626has a much larger diameter than the other second fluid passages described herein. The second surface1606of the body1602includes a second recessed cavity1628having an annular second insert1630installed therein. The second cavity1628and second insert1630are identical to the second cavity1354and second insert1362, shown inFIG.148. The first cavity1614and the first insert1618surround an opening1632of the second fluid passage1626on the first surface1604of the body1603. Likewise, the second cavity1628and the second insert1630surround an opening1634on the second surface1606of the body1602. The intermediate surface1608of the fluid routing plug1600is identical to the intermediate surface1506of the fluid routing plug1500, but does not have seals installed within grooves formed in the intermediate surface1608. Rather, the intermediate surface1608has a first and second sealing surface1636and1638, like the fluid routing plug1400. In alternative embodiments, a first and second seal may be installed within the intermediate surface1608of the fluid routing plug1600. With reference toFIG.170, fluid is routed through the fluid routing plug1600differently from the previously described fluid routing plugs. The fluid routing plug1600is shown installed within the housing1454. Fluid passes from the intake bore1460, through the first fluid passages1612and into an opening in the horizontal bore1470. A suction valve1640used with the fluid routing plug1600includes a central passage1642. Thus, the suction valve1642can seal the first fluid passages1612while leaving the second fluid passage1626open to the horizontal bore1470. As a plunger extends, the plunger forces fluid in the horizontal bore1470into the second fluid passage1626. The pressurized fluid flows through the second fluid passage1626and exits the second surface1606of the body1602. From there, the pressurized fluid flows around a discharge valve1644and towards the discharge bore1474formed in the housing1454. Various features of the fluid routing plugs116,600,700,800,900,1000,1100,1200,1400,1500, and1600described above may be modified, varied, or included in each of the plugs, as desired. Turning toFIGS.171-187, another embodiment of a fluid routing plug1700is shown. Instead of having a single body, like the fluid routing plugs described above, the fluid routing plug1700is separated into two different sections—a first section1702and a second section1704. A suction valve1706seals against the first section1702and a discharge valve1708seals against the second section1704, as shown inFIGS.185and187. The first section1702may be characterized as a suction seat, and the second section1704may be characterized as a discharge seat. In operation, fluid is primarily routed throughout the first section1702. Continuing withFIGS.171-180, the first section1702comprises a body1710having opposed first and second surfaces1712and1714joined by an intermediate surface1716. A plurality of first fluid passages1718are formed in the body1710and interconnect the intermediate surface1716and the first surface1712, as shown inFIG.173. The first fluid passages1718interconnect the intermediate surface1716and the first surface1712by way of an axially blind bore1720. The first fluid passages1718have the same shape and orientation as the first fluid passages1312, shown inFIG.146. Continuing withFIG.174, a plurality of second fluid passages1722are formed in the body1710and interconnect the first and second surfaces1712and1714along a straight-line path. The first fluid passages1718and the second fluid passages1722are formed offset from one another in the body1710and do not intersect. The second fluid passages1722each have a circular cross-sectional shape, like the second fluid passages336, shown inFIGS.60-63. The second fluid passages1722may each extend at a non-zero angle relative to a central longitudinal axis1724of the body1710. Continuing withFIGS.179and180, a first recessed cavity1726is formed in the first surface1712of the first section1702. The first cavity1726is characterized by a base1728surrounded by a sidewall1730. The sidewall1730is joined to an outer rim1732. A first annular insert1734is installed with the first cavity1726, as shown inFIG.179. The first insert1734is identical to the first insert1332, shown inFIG.149. The first insert1734is configured to engage the suction valve1706, as shown inFIGS.185and187. Continuing withFIGS.175and177, each second fluid passage1722opens on the outer rim1732of the first surface1712, as shown by a plurality of openings1736. The openings1736may be spaced in groups1738on the first surface1712, similar to the openings1328, shown inFIG.144. Each group1738shown inFIG.177includes three openings1736. A plurality of blind bores1740of varying shapes and sizes are formed in the outer rim1732between each of the openings1736. The blind bores1740function to remove excess weight from the first section1702. Continuing withFIGS.171and172, the second surface1714of the first section1702has an outer rim1742and a central blind bore1744. The blind bore1744may be threaded and is configured to engage with a tool used to grip the first section1702. A plurality of countersinks1746are formed in the second surface1714surrounding the blind bore1744. The countersinks1746form a plurality of raised surfaces1748surrounding the blind bore1744. Each raised surface1748may have a generally triangular shape. The countersinks1746help remove excess weight from the first section1702. In alternative embodiments, the countersinks and raised areas may have various shapes and sizes as desired. The second fluid passages1722open on the raised surfaces1748, as shown by a plurality of openings1750. A plurality of blind bores1752of various shapes and sizes may be formed in the raised surfaces1748around the openings1750. The blind bores1752help remove excess weight from the first section1702. The openings1750may remain spaced in groups1738on the second surface1714. In alternative embodiments, the openings of the second fluid passages may have different spacing or grouping, as desired. Continuing withFIGS.176and178, the intermediate surface1716of the first section1702has a generally cylindrical shape. The intermediate surface1716includes a first sealing surface1754positioned between the first surface1712and the first fluid passages1718, and a second sealing surface1756positioned between the second surface1714and the first fluid passages1718. The first and second sealing surfaces1754and1756are configured to engage a first and second seal1758and1760installed within another embodiment of a housing1762, as shown inFIGS.185and187. The first and second seals1758and1760may be identical to the first and second seals374and376installed within the housing104, as shown inFIGS.70and71. The first sealing surface1754has a smaller diameter than the second sealing surface1756in order to reduce friction during installation of the first section1702within the housing1762. The intermediate surface1716further includes a first bevel1764positioned between the first sealing surface1754and the first surface1712. The intermediate surface1716further includes a taper1766positioned between the second sealing surface1756and the first fluid passages1718. The first bevel1764is configured to engage a first beveled surface1768formed in the housing1762, as shown inFIG.187. When the first section1702is installed within the housing1762, an annular chamber1770is formed between the taper1766and the housing1762, as shown inFIG.187. The chamber1770provides a pathway for fluid from an upper and lower intake bore1772and1774and the first fluid passages1718. Continuing withFIGS.185and187, fluid is routed throughout the first section1702in the same manner as the fluid routing plug116. However, when fluid exits the second surface1714of the first section1702, the fluid is directed into the second section1704, instead of being directed towards a discharge bore. Turning toFIGS.181-184, the second section1704comprises a body1776having opposed first and second surfaces1778and1780joined by an intermediate surface1782. A central passage1784interconnects the first and second surfaces1778and1780of the body1776. The first surface1778has an outer rim1786joined to a tapered wall1788. The tapered wall1788extends between the central passage1784and the outer rim1786. A second recessed cavity1790is formed in the second surface1780. The second cavity1790is characterized by a base1792surrounded by a sidewall1794. The sidewall1794is joined to an outer rim1796. The outer rim1796is thicker than the outer rim1786. The base1792of the second cavity1790surrounds an opening1798of the central passage1784. A second annular insert1800is installed within the second cavity1790and surrounds the opening1798of the central passage1784, as shown inFIGS.185and187. The second insert1800is identical to the second insert1362, shown inFIG.148. The second insert1800is configured to engage the discharge valve1708, as shown inFIGS.185and187. Continuing withFIGS.181-184, the intermediate surface1782of the second section1704has a generally cylindrical shape. The intermediate surface1782includes a third sealing surface1802positioned between the first and second surfaces1778and1780, as shown inFIG.184. The third sealing surface1802is configured to engage with a third seal1804installed within the housing1762, as shown inFIG.187. The third seal1804may be identical to the first or second seal1758or1760. The intermediate surface1782also includes a second bevel1806positioned between the third sealing surface1802and the second surface1780. The second bevel1806is configured to engage with a second beveled surface1808formed in the housing1762, as shown inFIG.187. Continuing withFIGS.185-187, the second section1704is installed within the housing1762such that the outer rim1786of its first surface1778engages the outer rim1742of the second surface1714of the first section1702. A seal1810may be positioned between the outer rims1786and1742, as shown inFIG.186. The seal1810may be installed within a groove1812formed in the outer rim1786of the second section1704. The first section1702may have smaller outer diameters than the second section1704in order to reduce friction as the first and second sections1702and1704are installed within the housing1762, as shown inFIG.187. In operation, fluid exiting the second surface1714of the first section1702is funneled into the central passage1784of the second section1704by way of the tapered wall1788. Fluid exits the second surface1780of the second section1704and flows around the discharge valve1708and a discharge valve guide1814towards a discharge bore1816. With reference toFIGS.188-195, another embodiment of a first section1900is shown. The first section1900is identical to the first section1702with a few exceptions. A plurality of first fluid passages1902formed in a body1904of the first section1900have an oblong cross-sectional shape, rather than an oval cross-sectional shape, as shown by the opening1903inFIG.194. An end of the oblong shape may be wider than its opposed end, as shown inFIG.194. A first surface1906of the first section1900is identical to the first surface1712of the first section1702shown inFIG.177, with the exception of its blind bores1908. The blind bores1908have different spacing than the blind bores1740formed in the first surface1712. A second surface1910of the first section1900includes a central base1912surrounded by an outer rim1914. A blind bore1916is formed in the central base1912, similar to the blind bore1744. Instead of including a plurality of countersinks and raised surfaces like the first section1702, the second surface1910of the first section1900includes a cut-out area1918between the blind bore1916and the outer rim1914. The cut-out area1918helps remove excess weight from the first section1900. A plurality of second passages1920formed in the first section1900open on the outer rim1914of the second surface1910, as shown by the openings1922. A plurality of blind bores1924are positioned adjacent the openings1922to help remove excess weight. The spacing of the openings1922may be identical to the spacing of the openings1750, shown inFIG.172. An intermediate surface1926of the first section1900is identical to the intermediate surface1716of the first section1702with a minor exception. The intermediate surface1926includes two tapers1928and1930positioned on opposite sides of the first fluid passages1902. When the first section1900is installed in the housing1762, an annular chamber1932is formed between the housing1762and the tapers1928and1930, as shown inFIG.195. The annular chamber1932provides a pathway for fluid from the intake bores1772and1774to the first fluid passages1902. Continuing withFIG.195, the second section1704is shown engaging the first section1900within another embodiment of a housing1934. The housing1934is generally identical to the housing1762shown inFIG.187. A discharge conduit1936is shown attached to a bottom surface1938of the housing1934. In alternative embodiments, the discharge conduit may attach to a top surface of the housing. Likewise, the discharge bore may interconnect the top surface of the housing and the horizontal bore. While not shown, a stuffing box and corresponding components may be attached to the housing1934. Fluid is routed through the first and second sections1900and1704in the same manner as the fluid routing plug1700. With reference toFIGS.196-203, another embodiment of a fluid routing plug2000is shown. The fluid routing plug2000comprises a first section2002and a second section2004. The first section2002is generally identical to the first section1900, with a few exceptions. In contrast to the first surface1900, no blind bores are formed in an outer rim2006of a first surface2008of the first section2002. An opening2010of each of the plurality of second fluid passages2012formed in the first section2002are equally spaced around the outer rim2006, rather than being spaced in groups. A second surface2014of the first section2002is flat with the exception of a plurality of openings2016of the second fluid passages2012and a central blind bore2018. The openings2016are equally spaced around the blind bore2018. The central blind bore2018may be threaded and configured to engage a tool used to grip the first section2002. A plurality of first fluid passages2020formed in the first section2002are identical to the first fluid passages1902, shown inFIG.190. However, an oblong shaped opening2021of each first fluid passage2020may have the same sized ends, as shown inFIG.199. Turning toFIGS.202and203, the second section2004is shown engaging the first section2002within another embodiment of a housing2022. The second section2004is generally identical to the second section1704, shown inFIGS.181-184, but its first surface2024may have a thicker outer rim2026than the second section1704. While not shown inFIGS.202and203, a seal may be placed between the first and second sections2002and2004, like that shown inFIG.186. The housing2022is sized to receive the first and second sections2002and2004. The housing2022shown inFIGS.202and203has a single intake bore2028and a discharge bore2030positioned on a bottom surface2032of the housing2022. In alternative embodiments, the housing may include a second intake bore and the discharge bore may be formed on a top surface of the housing. While not shown, a stuffing box and corresponding components may be attached to the housing2022. Fluid is routed throughout the first and second sections2002and2004in the same manner as the fluid routing plug1700, shown inFIGS.185and187. With reference toFIGS.204-211, another embodiment of a first section2100is shown. The first section2100is identical with the first section2002, with a few minor exceptions. An intermediate surface2102of the first section2100has a uniform diameter throughout its length. The intermediate surface2102includes a first sealing surface2104positioned adjacent its first surface2106and a second sealing surface2108positioned adjacent its second surface2110. The first and second sealing surfaces2104and2108are configured to engage a first and second seal2112and2114installed within another embodiment of a housing2116, shown inFIGS.210and211. The first and second seal2112and2114may be identical to the first and second seals374and376, shown inFIGS.70and71. A plurality of first fluid passages2118formed in the first section2100may be generally identical to the first fluid passages1902, shown inFIG.190. The second surface2110of the first section2100shown inFIG.205does not include a central blind bore. In alternative embodiments, a central blind more may be formed in the second surface. A plurality of second fluid passages2120formed in the first section2100may extend parallel to a central longitudinal axis2122of the first section2100, as shown inFIG.208. Turning toFIGS.210and211, the second section2004is shown engaging the first section2100within the housing2116. While not shown, a seal may be placed between the first and second sections2100and2004, like that shown inFIG.186. The housing2116is sized to receive the first and second sections2100and2004. The housing2116shown inFIGS.210and211has a single intake bore2124and a discharge bore2126positioned on a bottom surface2128of the housing2116. In alternative embodiments, the housing may include a second intake bore and the discharge bore may be formed on a top surface of the housing. While not shown, a stuffing box and corresponding components may be attached to the housing2116. Fluid is routed throughout the first and second sections2100and2004in the same manner as the fluid routing plug1700, shown inFIGS.185and187. The housings described herein have various embodiments of suction valves, discharge valves, suction valve guides, and discharge valve guides. One of skill in the art will appreciate that these components may have various shapes and sizes depending on the construction of the housing and various components. While not shown herein, one of skill in the art will appreciate that the fluid end100described herein may be formed as a single housing having a plurality of horizontal bores formed therein and positioned in a side-by-side relationship. The housing may be attached to a single, large connect plate. In further alternative embodiments, the single housing described above may be broken up into one or more sections have two or more horizontal bores formed therein. Such housings may be attached to one or more connect plates. One of skill in the art will further appreciate that various features of the fluid routing plugs, housings, and other components described herein may be modified or changed, as desired. While not specifically shown in a figure herein, various features from one or more of the fluid routing plugs described herein may be included in another one of the plugs. Likewise, various features from one or more of the different housings described herein may be included in another one of the housings. One or more kits may be useful in assembling the fluid end sections102. A kit may comprise a plurality of housings described herein and a plurality of the corresponding fluid routing plugs described herein. The kit may also comprise a plurality of suction valves, discharge valves, suction valve guides, discharge valve guides, and various seals described herein. The concept of a “kit” is described herein due to the fact that fluid ends are often shipped or provided unassembled by a manufacturer, with the expectation that a customer will use components of the kit to assemble a functional fluid end. Alternatively, some components are replaced during operation. Accordingly, certain embodiments within the present disclosure are described as “kits,” which are unassembled collections of components. The present disclosure also describes and claims assembled apparatuses and systems by way of reference to specified kits, along with a description of how the various kit components are actually coupled to one another to form the apparatus or system. The term “means for routing fluid” refers to the various fluid routing plugs described herein and structural equivalents thereof. The term “means for regulating fluid flow” refers to the various suction and discharge valves and suction and discharge valve guides described herein and structural equivalents thereof. A “means for pressurizing fluid” refers to the fluid end and the various embodiments of housings and components installed within or attached to the various housings described herein and structural equivalents thereof. The various features and alternative details of construction of the apparatuses described herein for the practice of the present technology will readily occur to the skilled artisan in view of the foregoing discussion, and it is to be understood that even though numerous characteristics and advantages of various embodiments of the present technology have been set forth in the foregoing description, together with details of the structure and function of various embodiments of the technology, this detailed description is illustrative only, and changes may be made in detail, especially in matters of structure and arrangements of parts within the principles of the present technology to the full extent indicated by the broad general meaning of the terms in which the appended claims are expressed. Changes may be made in the construction, operation and arrangement of the various parts, elements, steps and procedures described herein without departing from the spirit and scope of the invention as described in the following claims. | 143,585 |
11859612 | DETAILED DESCRIPTION Referring now to the drawings submitted herewith, wherein various elements depicted therein are not necessarily drawn to scale and wherein through the views and figures like elements are referenced with identical reference numerals, there is illustrated a fluid transfer and depressurization system100constructed according to the principles of the present invention. An embodiment of the present invention is discussed herein with reference to the figures submitted herewith. Those skilled in the art will understand that the detailed description herein with respect to these figures is for explanatory purposes and that it is contemplated within the scope of the present invention that alternative embodiments are plausible. By way of example but not by way of limitation, those having skill in the art in light of the present teachings of the present invention will recognize a plurality of alternate and suitable approaches dependent upon the needs of the particular application to implement the functionality of any given detail described herein, beyond that of the particular implementation choices in the embodiment described herein. Various modifications and embodiments are within the scope of the present invention. It is to be further understood that the present invention is not limited to the particular methodology, materials, uses and applications described herein, as these may vary. Furthermore, it is also to be understood that the terminology used herein is used for the purpose of describing particular embodiments only, and is not intended to limit the scope of the present invention. It must be noted that as used herein and in the claims, the singular forms “a”, “an” and “the” include the plural reference unless the context clearly dictates otherwise. Thus, for example, a reference to “an element” is a reference to one or more elements and includes equivalents thereof known to those skilled in the art. All conjunctions used are to be understood in the most inclusive sense possible. Thus, the word “or” should be understood as having the definition of a logical “or” rather than that of a logical “exclusive or” unless the context clearly necessitates otherwise. Structures described herein are to be understood also to refer to functional equivalents of such structures. Language that may be construed to express approximation should be so understood unless the context clearly dictates otherwise. References to “one embodiment”, “an embodiment”, “exemplary embodiments”, and the like may indicate that the embodiment(s) of the invention so described may include a particular feature, structure or characteristic, but not every embodiment necessarily includes the particular feature, structure or characteristic. Referring in particular toFIG.1herein, a pipeline schematic1is illustrated therein so as to demonstrate an exemplary installation of the fluid transfer and depressurization system100. The fluid transfer and depressurization system100is fluidly coupled to a pipeline portion2that requires to have the contents therein removed. The pipeline portion2is a conventional pipeline portion such as but not limited to a pigging station. The pipeline portion2is configured to be isolated utilizing the appropriate valves3. The fluid transfer and depressurization system100is coupled to the pipeline portion2at the gas inlet10of the fluid transfer and depressurization system100utilizing a suitable hose or similar element. The fluid transfer and depressurization system100is operably coupled to an adjacent pipeline portion4via the gas discharge port11utilizing suitable hosing or tubing. As the fluid transfer and depressurization system100commences operation the pressurized gas stored in pipeline portion2is transferred to the adjacent pipeline portion4that is also at a pressure that is greater than that of atmospheric pressure. During operation of the fluid transfer and depressurization system100the contents disposed within the pipeline portion2are completely evacuated and transferred to adjacent pipeline portion4. At the termination of the operating cycle of the fluid transfer and depressurization system100the pipeline portion2has been substantially evacuated of its contents and the pressure therein is at or below atmospheric pressure. Ensuing completion of the evacuation of the contents disposed in the pipeline portion2, the pipeline portion2can be accessed for maintenance or other purposes. The fluid transfer and depressurization system100is disposed within a suitable durable housing (not illustrated herein) and as illustrated herein inFIG.7includes a drive chamber20having a first cylinder22operably coupled thereto and a second cylinder24operably coupled thereto on the opposing side thereof. The fluid transfer and depressurization system100in its preferred embodiment is powered utilizing compressed air which is introduced via the air inlet26. Air inlet26is operably coupled to a conventional compressed air source such as but not limited to a compressor or air tank utilizing conventional elements. The air is directed via tubing28to the controller30. Operably coupled to tubing28are conventional elements such as but not limited to a filter21, regulator23and lubricator25. The immediately aforementioned elements are well known in the art and provide required functionality when utilizing compressed air. The controller30is constructed similarly to an air-switching valve and functions to direct air into the interior volume19of the drive chamber20. Controller30functions to alternate the flow of air into the drive chamber20so as to facilitate the reciprocal movement of the drive assembly35. The controller30is operably coupled to the drive chamber20utilizing tubing39. Tubing39is conventional metal tubing and is configured to direct air into the drive chamber so as to facilitate the reciprocal movement of the drive assembly35. Drive assembly35includes a drive member38and rod40. Drive member38is manufactured from a suitable durable material as is movably secured within the interior volume19of the drive chamber20. The drive member38is sealably engaged with the inner wall27utilizing suitable durable techniques so as to inhibit air from leaking across the drive member38. Rod40includes first portion41and second portion42. First portion41extends outward from the first side48of the drive member38and is perpendicular thereto. First portion41extends inward into first cylinder22. Integrally formed on the end44of the first portion41is piston45. Piston45is sealably engaged with the first cylinder22utilizing suitable durable techniques. As will be further discussed herein, reciprocal movement of the piston45will facilitate transfer of gas from the gas inlet10to the gas discharge port11. The first cylinder22is constructed of suitable durable material and is manufactured to a desired length and diameter so as to accommodate a preferred amount of fluid therein. Operably intermediate the first cylinder22and the drive chamber20is the first coupling block50. First coupling block50is manufactured from a suitable durable material such as but not limited to metal. The first coupling block50provides a technique to sealably secure the first cylinder to the drive chamber20and additionally provide gas flow into the first cylinder22. First coupling block50includes sealing members51configured to provide a sealable connection intermediate first portion41of rod40. An upper passage54and a lower passage56are formed within the first coupling block50utilizing suitable techniques. The upper passage54is fluidly coupled to the gas inlet manifold60so as to facilitate introduction of gas into the first cylinder20therethrough during a movement of the piston45wherein the piston45is traveling away from the drive chamber20. The lower passage56provides an operably coupling to the gas discharge manifold65. During a movement of the piston45inwards towards the drive chamber20gas disposed intermediate the piston45and the drive chamber20is transferred to gas discharge manifold65via lower passage56. The fluid transfer and depressurization system100includes second cylinder24opposedly coupled to the drive chamber20relative to the first cylinder22. The second cylinder24is constructed similarly to the first cylinder22and is configured to receive and discharge a fluid being transferred by the fluid transfer and depressurization system100. The second portion42of the rod40extends into the second cylinder24and is sealably engaged therewith. Second portion42of the rod40has a piston57integrally formed on the end thereof distal to the drive member38. Piston57is sealably coupled with second cylinder24utilizing suitable durable techniques. Piston57is reciprocally movable within the interior volume of second cylinder24. As drive member38alternates direction of travel, piston57moves in conjunction therewith and as further discussed herein facilitates fluid transfer from the gas inlet10to the gas discharge port11. Intermediate the drive chamber20and the second cylinder24is the second coupling block70. The second coupling block70provides a sealable operable coupling of the drive chamber20and the second cylinder24. The second coupling block70includes sealing elements72surroundably mounted to second portion42of the rod40. Sealing elements72provide the necessary hermetic seal and it is contemplated within the scope of the present invention that the sealing elements72could be formed from various suitable materials such as but not limited to rubber. The second coupling block70further has formed therein an upper passage75and a lower passage76. The upper passage75is operably coupled to gas inlet manifold60and is configured to facilitate flow of fluid therebetween. The lower passage76is operably coupled to the gas discharge manifold65and allows the flow of fluid therebetween during a piston57movement that is traversing towards the drive chamber20. Operably coupled to first cylinder22distal to the drive chamber20is first gas block80. The first gas block80is hermetically coupled to the first cylinder22and is manufactured from a suitable durable material. The first gas block80is fluidly coupled to the first cylinder22and provides additional passages for transfer of fluid from the gas inlet manifold60to the gas discharge manifold65. First gas block80includes first passage81and second passage82fluidly coupled to the gas inlet manifold60and gas discharge manifold65respectively. As is further discussed herein, dependent of the direction of movement of the piston45fluid is transferred into and/or out of the first cylinder22via the first passage81and/or second passage82. Operably coupled to second cylinder24distal to the drive chamber20is second gas block90. The second gas block90is hermetically coupled to the second cylinder24and is manufactured from a suitable durable material. The second gas block90is fluidly coupled to the second cylinder24and provides additional passages for transfer of fluid from the gas inlet manifold60to the gas discharge manifold65. Second gas block90includes first passage91and second passage92fluidly coupled to the gas inlet manifold60and gas discharge manifold65respectively. As is further discussed herein, dependent of the direction of movement of the piston57fluid is transferred into and/or out of the second cylinder24via the first passage91and/or second passage92. The reciprocal movement of the drive member38is provided by the compressed air and its distribution thereof by the controller30. The controller30will alternate the flow of air through tubes39so as to facilitate the reciprocal movement of the drive member38. By way of example but not limitation, an exemplary movement of the drive member38is as follows. The controller30will direct air into tube139so as to drive air into the drive chamber area120. The compressed air is introduced at a sufficient pressure into the drive chamber area120so as to move the drive member38in the direction towards the second cylinder24. As the drive member38traverses towards the second cylinder24and becomes proximate thereto, the drive member38will engage first switch110. First switch110is operably coupled to controller30and upon engagement therewith, the controller30will terminate supply of air into tube139and alternate supply of compressed air into tube137. Subsequent the air supply alteration, the drive member38will commence traversing through the drive chamber20in the alternate direction towards the first cylinder22. The drive member38continues travel towards the first cylinder22until engagement of the second switch111which will return the airflow to the first step discussed above. The gas transfer from the first cylinder22and second cylinder24as a result of the drive member38movement will be further discussed herein. The gas inlet10is operably coupled to the gas inlet manifold60. The gas inlet manifold60is constructed of suitable durable material and has an interior volume that is configured to receive/stage a gas being introduced thereinto from the gas inlet10. As is illustrated herein inFIG.2throughFIG.4, it is contemplated within the scope of the present invention that the fluid transfer and depressurization system100could have alternate configurations/quantities of the gas inlet manifold60. The gas inlet manifold60functions to provide a sufficient volume of gas to first cylinder22and/or second cylinder24during operation of the fluid transfer and depressurization system100. Exemplary configurations of the present invention include having a single gas inlet manifold60fluidly coupled to the first cylinder22and second cylinder24. Alternatively, as illustrated herein inFIGS.3and4herein, a contemplated configuration of the fluid transfer and depressurization system100would utilize a gas inlet manifold60that is fluidly coupled to the first cylinder22. Additionally, as shown inFIG.4herein, an inter-stage manifold115is further contemplated. The various configurations discussed and illustrated herein for the gas inlet manifold60do not serve as limitations but provide exemplary configurations which are a part of the contemplated present invention. It is contemplated within the scope of the present invention that at least one gas inlet manifold60is provided so as to receive and store gas from the gas inlet10. The gas discharge manifold65is operably coupled to the gas discharge port11and is manufactured from a suitable durable material. The gas discharge manifold65is constructed to have an interior volume being of sufficient size to accommodate gas from either the first cylinder22and/or the second cylinder24as the gas is discharged therefrom. The gas discharge manifold65provides a technique to direct the outflow of gas to the gas discharge port11. As illustrated herein throughFIG.2andFIG.4it is contemplated within the scope of the present invention that the fluid transfer and depressurization system100could have alternate configurations and/or quantities of gas discharge manifolds65. In one contemplated configuration as illustrated herein inFIG.2, the gas discharge manifold65is fluidly coupled to the first cylinder22and the second cylinder24. An alternate configuration contemplated within the scope of the present invention as illustrated inFIG.3submitted as a part hereof wherein the gas discharge manifold65is operably coupled to the second cylinder24. An additional configuration includes utilization of an inter-stage manifold115as illustrated herein inFIG.4. It should be understood within the scope of the present invention that the fluid transfer and depressurization system100could deploy as few as one gas discharge manifold65or more than one. Referring again to the controller30, the controller30has operably coupled thereto tubing120. Tubing120is manufactured from conventional material such as but not limited to metal tubing. As the drive assembly35is reciprocally moved by the compressed air as described herein, release of the compressed air is intrinsic to the operational cycle of the drive assembly35. The controller30directs the release of air to atmosphere utilizing tubing120. Tubing120is configured so as to have a portion thereof end adjacent the first cylinder22and another portion end proximate the second cylinder24. The air discharged from the tubing187functions to provide cooling of the first cylinder22and second cylinder24. It is contemplated within the scope of the present invention that the tubing187could be configured in alternate manners and further be configured to provide an atmospheric vent for the compressed air and not be directed so as to provide the cooling discussed herein. Illustrated herein as being a part of the fluid transfer and depressurization system100are a plurality of conventional components that are known in the art of pressurized gas systems. By way of example but not by way of limitation, the fluid transfer and depressurization system100employs exemplary cutoff switches160, exemplary valves162and exemplary gauges164that are deployed and utilized in a conventional manner so as to control flow, direct flow and measure flow as is known in the art. It is contemplated within the scope of the present invention that the fluid transfer and depressurization system100could employ various quantities of exemplary cutoff switches160, exemplary valves162and exemplary gauges164as needed to provide the desired aforementioned functionality. Now referring toFIG.3herein, a discussion of an exemplary flow path of gas within the fluid transfer and depressurization system100is as follows. Controller30is configured such that compressed air is being introduced into the drive chamber20via tube139and air disposed in the drive chamber20intermediate the drive member38and the second cylinder24is being expelled via tube137. As compressed air flows through tube139the drive member38traverses towards the second cylinder24. As the drive member38traverses towards the second cylinder24gas from the gas inlet10travels through tube170into gas inlet manifold60. The gas flow continues through tube172into the interior volume of the first cylinder22in particular the portion intermediate the first gas block80and piston45. Gas disposed on the opposing side of the piston45in the first cylinder22egresses therefrom as the piston45is traveling in conjunction with the drive member38. Gas intermediate the piston45and the first coupling block50is directed through lower passage56into tubing175. The gas flows from tubing175to the second passage76of the second coupling block70and is introduced into the second cylinder24wherein the gas will be disposed intermediate the piston57and the second coupling block70. Simultaneously, gas disposed intermediate piston57and second gas block90propagates passage91outward towards the gas discharge manifold65. The gas continues outward from the gas discharge manifold65via tube176where the gas exits the fluid transfer and depressurization system100via the gas discharge port11. The immediately aforementioned flow path description for the fluid transfer and depressurization system100serves to demonstrate a flow path for a single movement of the drive member38. During the reciprocal movement of the drive member38it should be understood by those skilled in the art that a similar but opposing flow path occurs. It is contemplated within the scope of the present invention that the flow path of the fluid transfer and depressurization system100will vary based upon the configurations illustrated herein and contemplated as a part of the present invention. Irrespective of the particular configuration, as the drive member38is reciprocally moved within the drive chamber20the introduction of gas into either the first cylinder22or the second cylinder24occurs and simultaneous expulsion of gas from the opposing cylinder occurs and is discharged outward from the fluid transfer and depressurization system100via the gas discharge port11. The fluid transfer and depressurization system100is configured so as to operably couple to a first location having a pressurized gas disposed therein and transfer the gas to a second location wherein during operation the fluid transfer and depressurization system100depressurizes the first location without the loss of gas to the atmosphere. It is further contemplated within the scope of the present invention that the fluid transfer and depressurization system100could move a fluid at atmospheric pressure from a first location to a second location wherein the second location is also at atmospheric pressure. While the fluid transfer and depressurization system100has been discussed herein for movement of a pressurized gas from a first location to a second location, it is contemplated within the scope of the present invention that the fluid transfer and depressurization system100could be utilized to move various types of fluids such as but not limited to liquids. Additionally, while the fluid transfer and depressurization system100has been illustrated and discussed herein as having a first cylinder22and a second cylinder24opposedly located with respect to the drive chamber20, it is further contemplated within the scope of the present invention that more than two cylinders could be utilized. By way of example but not limitation, four or more cylinders increasing by paired numbers could be utilized in the fluid transfer and depressurization system100and achieve the desired functionality as described herein. While not suitable for all operational environments of the fluid transfer and depressurization system100, it is further contemplated within the scope of the present invention that the operational technique of utilizing compressed air could be replaced with alternate suitable techniques such as but not limited to electric motors, wherein an electric motor would reciprocally move the drive assembly35as described herein. It should be further understood by those skilled in the art that the fluid transfer and depressurization system100while illustrated and discussed herein as being utilized in a standalone configuration could further be deployed in parallel or series configurations. In the preceding detailed description, reference has been made to the accompanying drawings that form a part hereof, and in which are shown by way of illustration specific embodiments in which the invention may be practiced. These embodiments, and certain variants thereof, have been described in sufficient detail to enable those skilled in the art to practice the invention. It is to be understood that other suitable embodiments may be utilized and that logical changes may be made without departing from the spirit or scope of the invention. The description may omit certain information known to those skilled in the art. The preceding detailed description is, therefore, not intended to be limited to the specific forms set forth herein, but on the contrary, it is intended to cover such alternatives, modifications, and equivalents, as can be reasonably included within the spirit and scope of the appended claims. | 23,119 |
11859613 | DETAILED DESCRIPTION OF THE EMBODIMENTS Exemplary embodiments will now be described more comprehensively with reference to the accompanying drawings. Exemplary embodiments are provided so that the present application will be thorough and will more fully convey the scope to those skilled in the art. Many specific details such as examples of specific components, devices, and methods are described to provide a thorough understanding of various embodiments of the present application. It will be clear to those skilled in the art that the exemplary embodiments may be implemented in many different forms without using specific details, none of which should be construed as limiting the scope of the present application. In some exemplary embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail. The overall structure of a scroll compressor100will be described below with reference toFIG.1. As shown, the compressor100includes a housing11, a compression mechanism CM, a motor16, a rotating shaft (also referred to as a drive shaft or a crankshaft)14, and a main bearing housing15. The housing11may include a cylindrical body11a, a top cover11blocated at the top end of the cylindrical body11a, and a bottom cover11clocated at the bottom end of the cylindrical body11a. The housing11forms a closed space in which the compression mechanism CM, the motor16, the rotating shaft14and the main bearing housing15are accommodated. A partition plate11dmay further be provided between the top cover11band the cylindrical body11a. The partition plate11ddivides the closed space of the housing11into a high-pressure side and a low-pressure side. The high-pressure side is defined by the partition plate11dand the top cover11b, and the low-pressure side is defined by the partition plate11d, the cylindrical body11a, and the bottom cover11c. The cylindrical body11ais provided with an inlet port (not shown) for introducing the working fluid with a suction pressure into the housing11. The top cover11bis provided with an outlet port11efor discharging the working fluid with discharge pressure compressed by the compression mechanism CM out of the housing11. During the operation of the scroll compressor100, the low-pressure working fluid is introduced into the compressor100via the inlet port (introduced to the low-pressure side in the example shown inFIG.1), sucked into the compression mechanism CM, discharged to the high-pressure side after being compressed, and finally discharged out of the scroll compressor100via the outlet port11e. The compression mechanism CM includes a non-orbiting scroll12fixed to the housing11(specifically, the cylindrical body11a) and an orbiting scroll13. The motor16is configured to drive the rotating shaft14to rotate, which in turn drives the orbiting scroll13to orbit relative to the non-orbiting scroll12(i.e., a center axis of the orbiting scroll moves around a central axis of the non-orbiting scroll, but the orbiting scroll does not rotate around its own center axis) to compress the working fluid. The orbiting movement is realized via an Oldham coupling17(referring toFIG.2). The non-orbiting scroll12may be fixed relative to the housing11in any suitable manner. As shown, the non-orbiting scroll12is fixedly mounted to the main bearing housing15by bolts, which will be described in detail later. The non-orbiting scroll12may include a non-orbiting scroll end plate122, a non-orbiting scroll vane124extending from one side of the non-orbiting scroll end plate122, and an outlet121located approximately at a central portion of the non-orbiting scroll end plate122. For ease of description, the radially outermost portion of the non-orbiting scroll vane124is referred to as a peripheral wall portion126herein. As shown inFIG.2, the non-orbiting scroll12further has a flange128extending radially outward from an outer peripheral surface of the peripheral wall portion126. The flange128is provided therein with a mounting hole127for receiving an axial compliance mounting mechanism, so as to be connected to the main bearing housing15. The orbiting scroll13may include an orbiting scroll end plate132, an orbiting scroll vane134formed on one side of the orbiting scroll end plate132, and a hub131formed on the other side of the orbiting scroll end plate132. The non-orbiting scroll vane124and the orbiting scroll vane134can be engaged with each other, so that a series of moving compression chambers with volume gradually decreasing from a radial outer side to a radial inner side are formed between the non-orbiting scroll vane124and the orbiting scroll vane134during operation of the scroll compressor, so as to compress the working fluid. The hub131is engaged with an eccentric crank pin of the rotating shaft14and is driven by the eccentric crank pin. The main bearing housing15is adapted to support the orbiting scroll end plate132of the orbiting scroll13. The orbiting scroll end plate132orbits on a bearing surface155of the main bearing housing15(referring toFIG.2). The main bearing housing15may be fixed with respect to the housing11of the scroll compressor100by any suitable means. In order to achieve fluid compression, an effective sealing is required between the non-orbiting scroll12and the orbiting scroll component13. On the one hand, during the normal operation of the scroll compressor, a radial sealing is also required between a side surface of the spiral vane124of the non-orbiting scroll12and a side surface of the spiral vane134of the orbiting scroll13. The radial sealing between the two is generally achieved by a centrifugal force of the orbiting scroll13during orbiting movement and a driving force provided by the rotating shaft14. In a case that incompressible foreign matter (e.g., solid impurities and liquid refrigerant) enters the compression chamber and gets stuck between the spiral vanes124and134, the spiral vanes124and134can be temporarily separated from each other in the radial direction to allow the foreign matter to pass through, thereby preventing the spiral vanes124and134from being damaged, so as to provide the scroll compressor100with radial compliance. On the other hand, during the normal operation of the scroll compressor, an axial sealing is further required between a tip of the spiral vane124of the non-orbiting scroll12and the end plate132of the orbiting scroll13, and between a tip of the spiral vane134of the orbiting scroll13and the end plate122of the non-orbiting scroll12. In a case of excessive pressure in the compression chamber of the scroll compressor, the fluid in the compression chamber leaks to the low-pressure side through a gap between the tip of the spiral vane124of the non-orbiting scroll12and the end plate132of the orbiting scroll13and a gap between the tip of the spiral vane134of the orbiting scroll13and the end plate122of the non-orbiting scroll12to achieve unloading, thereby providing the scroll compressor100with axial compliance. In order to provide axial compliance, the non-orbiting scroll12is mounted to the main bearing housing15via the axial compliance mounting mechanism18. Referring toFIG.2, the axial compliance mounting mechanism18includes a bolt181and a sleeve182located radially outside the bolt181. The bolt181has a stem portion1813, a head portion1811located at one end of the stem portion1813, and a threaded portion1817located at the other end of the stem portion1813. The head portion1811has an abutting surface1812for abutting against an upper end surface1821(referring toFIG.3) of the sleeve182and an upper surface (first surface)1281of the flange128. The threaded portion1817is configured to be able to be screwed into a threaded hole151of the main bearing housing15. The sleeve182is further received in a mounting hole127of the flange128of the non-orbiting scroll12and is located between the head portion1811and the upper surface153of the main bearing housing15, thereby positioning the head portion1811such that the non-orbiting scroll12is capable of moving a predetermined distance in the axial direction. The inventor found that the bolts of the existing axial compliance mounting mechanism are liable to be loose or fractured. The reason why the bolts are liable to be loose or fractured is analyzed below with reference toFIG.13. Forces borne by the bolts are very complicated, and thus are simplified for ease of understanding the cause of the fracture. The bolt is liable to be broken or failed at the position P indicated by the dashed line, at an upper threaded joint between the bolt3and the main bearing housing2. With respect to the distance from the flange128, the “upper threaded joint” is referred to herein as a proximal joint. As described above, when the orbiting scroll (not shown inFIG.13) orbits relative to the non-orbiting scroll1, a vane side contact force (acting force) is generated due to the centripetal acceleration, and is transmitted to the bolt3via the sleeve4. It is generally considered that an equivalent acting point of the force F applied to the bolt3by the non-orbiting scroll1corresponds to an axial geometric center point of the flange of the non-orbiting scroll1. A distance between the position P and the force F is D, so that a moment M (product of the force F and the distance D) is generated with the position P as the fulcrum. The moment M causes the bolt to be easily broken at the position P. The present application aims to alleviate or prevent the bolt from being broken by reducing the distance D. For the ease of description herein, it is assumed that a distance between the position P and an upper surface2aof the main bearing housing2(i.e., an axial height of a counterbore2b) is unchanged in various embodiments. In this way, by reducing the distance h from the upper surface2aof the main bearing housing2to the equivalent acting point of the force F, it is possible to alleviate or prevent fracture of the bolt. When the compressor is operating normally, the orbiting scroll exerts force on the sleeve through the flange (lug) of the non-orbiting scroll. Generally, the flange of the non-orbiting scroll is fitted in the sleeve with face-to-face contact, so the force applied to the sleeve can be regarded as forces distributed over a certain contact area. When the effect of these distributed forces is equivalent to a concentrated force (the force F described herein), the position of the concentrated force F is the axial position of the equivalent point of the force F described herein. In order to reduce the distance h, the flange182of the non-orbiting scroll is located at a lower half of the peripheral wall portion126close to the main bearing housing15. Preferably, the flange extends radially outward from an end of the peripheral wall portion126(the lower surface1283of the flange182is substantially flush with the top surface of the vane124). FIGS.1to3show an example of reducing the distance h by modifying an outer contour of a sleeve182. As shown, the outer contour (outer peripheral surface) of the sleeve182is not of a cylindrical shape with a constant diameter, but has a convex section1828. A dashed line C1inFIG.2represents the axial geometric center position of the flange128, and a dashed line C2corresponds to a maximum diameter portion1829of the convex section1828and therefore represents a position (i.e., the axial position of the equivalent acting point of the force F) where the sleeve contacts with the mounting hole127of the flange182. The convex section1828tapers from the maximum diameter portion1829toward the upper surface (first surface)1281and the lower surface (second surface)1283of the flange128. In examples shown, the sleeve182may further have a straight section1827with a constant diameter located adjacent to the main bearing housing15. InFIG.2, a distance from the position P to the axial position C2of the equivalent acting point is obviously shorter than a distance from the position P to the axial geometric center position C1. It will be appreciated that the present application is not limited to the specific embodiments illustrated. For example, the convex section1828may only taper from the maximum diameter portion1829toward the first surface1281of the flange128, and there is a constant diameter from the maximum diameter portion1829to an end adjacent to the main bearing housing15. In this case, the axial position of the equivalent acting point can be further offset downward, that is, the distance from the position P to the equivalent acting point of force can be further reduced. In the examples shown, the convex section1828is in the form of a curved surface. However, it should be understood that the convex section1828may also be in the form of a shoulder forming a step or the like. In the shown examples, the sleeve182and the bolt181are separate components. However, it should be understood that the sleeve182and the bolt181may be integrated as one piece, that is, a shouldered bolt. It can be seen from the above content that it is possible to alleviate or prevent fracture of the bolt181by providing the outer contour of the axial compliance mounting mechanism18with a convex section, which causes the axial position C2of the equivalent acting point to be lower than the axial geometric center position C1. FIGS.4and5show an example of reducing the distance h by modifying an inner contour (shape of an inner wall) of a mounting hole227of a flange228. As shown, the inner contour (shape of the inner wall) of the mounting hole227is not of a cylindrical shape with a constant diameter, but has a convex section2272. Therefore, a sleeve282may have a cylindrical shape with a constant diameter. Similar to the examples shown inFIGS.1to3, a dashed line C2corresponds to a maximum diameter portion2279of the convex section2272and therefore represents a position (i.e., the axial position of the equivalent acting point of the force F) where the mounting hole contacts with the sleeve282. The convex section2272tapers from the maximum diameter portion2279toward the upper surface (first surface)2281and the lower surface (second surface)2283of the flange228. In examples shown, the mounting hole227may further have a straight section2271with a constant diameter located adjacent to the upper surface (first surface)2281. InFIG.4, a distance from the position P to the axial position C2of the equivalent acting point is obviously shorter than a distance from the position P to the axial geometric center position C1. It will be appreciated that the present application is not limited to the specific embodiments illustrated. For example, the convex section2272may have any other suitable form, as long as the axial position C2of the equivalent acting point is below the axial geometric center position C1. FIGS.6and7show another example of reducing the distance h by modifying the structure of a flange328. As shown, the flange328further has an extension portion3285extending downward in the axial direction from a lower surface (second surface)3283, so that a lower end surface (third surface)3284of the extension portion3285is below a top surface of the non-orbiting scroll vane124. In this example, a mounting hole327of the flange328may have a constant inner diameter, and a sleeve382may also have a constant outer diameter substantially equal to the inner diameter of the mounting hole327. In the example shown inFIGS.6and7, the dashed line C1still represents an axial geometric center position between an upper surface (first surface)3281and the lower surface (second surface)3283, and the dashed line C2corresponds to an axial geometric center position between the upper surface (first surface)3281and the lower end surface (third surface)3284and therefore represents an axial position of the equivalent acting point of the force F applied to the bolt. In this example, by extending the length of the mounting hole327toward the main bearing housing15, the axial position of the equivalent acting point is offset toward the main bearing housing15, thereby reducing a distance from the position P to the axial position of the equivalent acting point, i.e., reducing the distance h. FIGS.8and9show another example of reducing the distance h by modifying the structure of the main bearing housing15. As shown, the main bearing housing15has a connecting portion452for threaded engagement with a bolt481. The connecting portion452may extend toward the flange such that an upper end surface453of the connecting portion452is higher than a bearing surface455for supporting an end plate432of the orbiting scroll13, and more preferably, the connecting portion452is close to a lower surface4283of a flange428. As described above, for the ease of description herein, it is assumed that a distance between the position P and an upper surface of the main bearing housing (i.e., an axial height of a counterbore) is unchanged in each embodiment. Therefore, in the examples shown inFIGS.8and9, by extending the connecting portion452toward the flange428, the position P is offset toward the flange428, thereby reducing the distance h. The inventor has further made a finite element analysis on some parameters related to the axial compliance mounting mechanism18. By optimizing the design of some parameters, the bolt fracture can also be alleviated or prevented. Reference is made toFIG.10below to understand the parameters related to alleviating or preventing bolt fracture. The components inFIG.10that are the same as those inFIG.8are denoted by the same reference numerals as inFIG.8. As shown inFIG.10, the height of the flange428between the first surface4281and the second surface4283is indicated by H1. A distance between an axial position C2of the equivalent acting point of the force applied by the flange428to the axial compliance mounting mechanism and the second surface4283is indicated by h1. A distance between the first surface4281and the end surface453of the connecting portion452is indicated by H2. A distance between the second surface4283and the end surface453is indicated by h2. A distance between the axial position C2of the equivalent acting point and the end face453is indicated by h, and h=h1+h2. Through finite element analysis, the inventor found that bolt fracture can be significantly alleviated or prevented in a case that the following conditions are met: 0<h2/H1<0.3; 0<h2/H2<0.3; 0<h/H1<0.6; or 0<h/H2<0.6. The inventor has further performed tests within these parameter ranges with respect to various embodiments described above.FIG.11acorresponds to the embodiment shown inFIGS.1to3, andFIG.11bcorresponds to the embodiment shown inFIGS.4and5. In the examples shown inFIG.11aandFIG.11b, h1/H1=0.25, and h=14.5. The tests show that this parameter can significantly alleviate or prevent bolt fracture. FIG.11ccorresponds to the embodiment shown inFIGS.8and9. In the example shown inFIG.11c, h2/H2=0.06, h/H2=0.36, and h=9.3. Tests show that this parameter can significantly alleviate or prevent bolt fracture.FIG.11dcorresponds to the embodiment shown inFIGS.6and7. In the example shown inFIG.11d, h2/H2=0.10, h/H2=0.55, and h=14.3. Tests show that this parameter can significantly alleviate or prevent bolt fracture. The inventor has further tested moments generated at the position P at different distances h under the same force. In these tests, structures of the flange, the main bearing housing and the axial compliance mounting mechanism are the same, and only value of the distance h is varied. The test results are shown in Table 1 below. TABLE 1ForceDistanceMoment at positionF (N)h (mm)P (N * mm)30008.22803300010.23229300012.23665300014.24105300016.24546300018.24975300020.25418300022.25851300024.26289 A graph is drawn according to Table 1, referring toFIG.12.FIG.12more intuitively shows that the smaller the distance h is, the smaller the moment at the position P is. Therefore, by reducing the distance h, bolt fracture can be significantly alleviated or prevented. While the present application has been described with reference to the exemplary embodiments, it will be appreciated that the present application is not limited to the specific embodiments described and illustrated in detail herein. The person skilled in the art can make various variants to the exemplary embodiments without departing from the scope defined by the claims. It should further be understood that, provided that there is no contradiction in technical solutions, the features in the various embodiments can be combined with each other, or can be omitted. | 20,616 |
11859614 | Reference numerals used in the figures correspond to the following structures:10—reversible gerotor pump;11—slot;11a—first end of slot;11b—second end of slot;12—locking pin;13—eccentric ring;14—housing;15—shaft;16—inner rotor;17—outer rotor;18—inlet direction;18′—direction from inlet to the pump;19—outlet direction;20—outer plate;21a,21b,21c—axle center for shaft at different positions;22a,22b,22c—axle center for outer rotor at different positions;C1—radial clearance between shaft and inner rotor; C2—radial clearance between outer rotor and interior of the eccentric ring; C3—radial clearance between interior of the housing and exterior of the eccentric ring; D1, D2—arrows showing direction of movement and clearance through slot;30—suction port;30a—upstream side;30b—downstream side;31,31′—prolongation;32—discharge port;40—cavity for discharge;50,50′—cavity for suction;60—external tooth of inner rotor;71—inner tooth of outer rotor;72—recess area between inner teeth of outer rotor;100—positive contact mechanism;101,101′—spring;102—plunger;103—cavity;104—piston;105—pads;111—linear line;112—2% drop line;113—computational fluid dynamic (CFD) line;121—fill speed curve for the gerotor pump of the present disclosure;122—fill speed curve for the conventional gerotor pump;123—volumetric efficiency curve for the gerotor pump of the present disclosure;124—volumetric efficiency curve for the conventional gerotor pump;131,132—convex outer surfaces of the eccentric ring. DETAILED DESCRIPTION Existing truck transmission has only unidirectional lubrication pump. However, in some applications, it is desired to remove the reverse gear. Now, when the heavy duty electric vehicle has no reverse gear mechanism, the transmission for the electric vehicle must have a lubrication pump with the ability to work in both clockwise and counterclockwise rotation directions while using the same ports for suction and discharge of the hydraulic fluid unidirectionally. Reversible gerotor pumps are designed for supplying hydraulic fluid for the vehicle transmission. The lubrication pump is expected to support a maximum operating speed of 5000 rpm and 95% volumetric efficiency in a heavy duty electric vehicle automatic 4-speed transmission. The conventional design of a gerotor pump provides two symmetric bean shaped ports at the suction and discharge sides, which are symmetric about the x-axis, as inFIG.7. Research (as shown inFIG.11) reveals that the conventional gerotor pump has the fill speed (maximum operating speed) at 3300 rpm and volumetric efficiency at 68%, both of which are less than the critical to quality (CTQ) requirements. It is happening because of insufficient filling of the pump cavity volume through the suction port at higher speed due to cavitation and thus, reduction in pump discharge flow. Therefore, there is a constant need for improving the design of the reversible gerotor pump to improve volume efficiency of the cavities and the filling and operating speed. As shown inFIGS.1A to1C, the reversible gerotor pump10of the present invention comprises a cylindrical housing14with a slot11of 180 degree along a periphery of the housing. Slot11is defined by a first end11aat the top and a second end11bat the bottom. An eccentric ring13for adjusting eccentricity is positioned within housing14, and radial clearance C3is defined between eccentric ring13and housing14. As shown inFIG.1A, a locking pin12is fixed to the outer periphery of eccentric ring13at the thickest portion (along A-A′ line inFIG.2A) and movably engaged in slot11between the first end11aand the second end11bin housing14. An outer rotor17is positioned within eccentric ring13, and radial clearance C2is defined between eccentric ring13and outer rotor17. Outer rotor17has a plurality of internal teeth71with recesses72defined between adjacent teeth71. Outer rotor17and eccentric ring13are located eccentrically. An inner rotor16is positioned within outer rotor17. Inner rotor16comprises a plurality of external teeth60, where at least a portion of the external teeth60of inner rotor16are engaged with at least a portion of internal teeth71of outer rotor17at the recesses72. Inner rotor16and outer rotor17are eccentric relative to one another. An inner rotor tip clearance Ci is defined as a radial clearance between the tip of the external tooth and the moveable portion of the outer rotor corresponding to the external tooth. A shaft15is coupled with inner rotor16for rotatably driving inner rotor16. A radial clearance C1is defined between shaft15and inner rotor16. When shaft15rotates and drives inner rotor16to rotate in the same direction, the plurality of meshed teeth60of inner rotor16and internal teeth71of outer rotor17form a plurality of cavities50and50that expand and contract as they rotate. While rotating, cavity50is being expanded and forms a basis for a sucking port and inlet (direction18and18′ as shown inFIG.6), and cavity40is being contracted and forms a basis for a discharge port and outlet (direction19as shown inFIG.6). As shown inFIG.1A, reversible gerotor pump10rotates clockwise and is in the first position. Locking pin12stops at the top, i.e., the first end11a, and clockwise rotation of eccentric ring13is stopped, while inner rotor16and outer rotor17rotate clockwise with shaft15with the inlet and outlet function for suction and discharge, respectively. As reversible gerotor pump10is in clockwise rotation, each cavity formed between the external tooth60of inner rotor16and corresponding recess72of outer rotor17, as illustrated by shaded area50on the right side inFIG.1A, increases in volume, thus creating a vacuum and suction force to draw hydraulic liquid into the cavity through the inlet; at the same time, each cavity formed between the external tooth60of inner rotor16and corresponding recess72of outer rotor17, as illustrated by shaded area40on the left side inFIG.1A, decreases in volume, thus creating a pressure to discharge hydraulic fluid in the cavity through outlet. In the first position, reversible gerotor pump10of the present invention has contact at C1, C2, and C3shown inFIG.1A, and axel center21aof shaft15is directly above axel center22aof outer rotor17. If shaft15rotates at speed +n, then, inner rotor16rotates at speed +n as well, outer rotor rotates at speed +n×(number of external teeth of inner rotor/number of interior teeth of outer rotor), and eccentric ring13is not rotating; contact force F (F1at C1and F3at C3) is represented by formula (1): F=T/r(1), where T is torque required to rotate reversible gerotor pump10and r is the radius at the contact. When reversible gerotor pump10starts to rotate in the reversal direction, i.e., counterclockwise, it comes to the third position as shown inFIG.1Cthrough a second position shown inFIG.1B. As shown inFIG.1B, reversible gerotor pump10is in an intermediate (second) position where there are contact at C1and C2and eccentric ring13, outer rotor17, and inner rotor16rotate as one part with shaft15. Reversible gerotor pump10will pass through the second position when shaft15changes rotation direction, such as from clockwise to counterclockwise or from counterclockwise to clockwise. When the rotation direction changes, eccentric ring13is driven to rotate in the reversed rotating direction by contact force between eccentric ring13and outer rotor17while locking pin12moves along slot11until it stops at the second end11b, the bottom, to stop rotation of eccentric ring13. In the second position, reversible gerotor pump10has contact at C1and C2as shown inFIG.1B(axel center21bof shaft15is at the same horizontal line as axel center22bof outer rotor17). If shaft15now rotates at speed −n, then, all inner rotor16, outer rotor17, and eccentric ring13rotate at speed −n; contact force F2at C2in the second position is represented by formula (2): F2=mrω2(2), where m is the mass of eccentric ring13, r is the radius at the contact C2, and ω is the angular speed of eccentric ring13. The condition to avoid sticking and achieving interior diameter contact on eccentric ring at C2during the rotation direction change of shaft15is as in formula (3): C3>ΣC1,C2,C1 (3), where C1is the radial clearance between shaft15and inner rotor16at that position; C2is the radial clearance between outer rotor17and eccentric ring13at that position, C3is the radial clearance between eccentric ring13and housing14at that position, and Ci is inner rotor tip clearance between the tip of external tooth60and corresponding part of the outer rotor. As shown inFIG.1C, reversible gerotor pump10comes to the third position in the reversed rotation, i.e., counterclockwise, where eccentric ring13comes at the bottom, and shaft15, along with inner rotor16and outer rotor17, rotates counterclockwise. At the third position, locking pin12stops at the bottom, i.e., the second end11b, and counterclockwise rotation of eccentric ring13is stopped, while inner rotor16and outer rotor17rotate counterclockwise with shaft15, and directions of inlet18and18′, and direction of outlet19for suction and discharge are shown, respectively. As reversible gerotor pump10is in counterclockwise rotation, each cavity formed between the external tooth60of inner rotor16and corresponding recess72of outer rotor17, as illustrated by shaded area50on the right side inFIG.1C, increases in volume, thus creating a vacuum and suction force to draw hydraulic liquid into the cavity through the inlet; at the same time, each cavity formed between the external tooth60of inner rotor16and corresponding recess72of outer rotor17, as illustrated by shaded area40on the left side inFIG.1C, decreases in volume, thus creating a pressure to discharge hydraulic fluid in the cavity through the outlet. In the third position, reversible gerotor pump10has contact at C1, C2, and C3shown inFIG.1C, and axel center21cof shaft15is directly below axel center22cof outer rotor17. If shaft15rotates at speed −n, then inner rotor16rotates at speed −n, outer rotor rotates at speed −n×(number of external teeth of inner rotor/number of interior teeth of outer rotor), and eccentric ring13is not rotating; contact force Fat contact points C1and C3is again represented by formula (1) as in the first position, where T is torque required to rotate reversible gerotor pump10and r is the radius at the contact point. As shown inFIG.2A, the outer periphery and internal shape of eccentric ring13are both cylindrical, however, they are not concentric while the thickness of eccentric ring13is distributed symmetrically along A-A′ center line. The eccentric ring comprises an annulus of material, an inner circumference, and an outer circumference of the annulus, where the two circumferences are not concentric, thereby creating an eccentricity in the thickness of the eccentric ring. The thickness of the eccentric ring is uneven but distributed along the periphery of the circumference while symmetrically along the A-A′ line. Locking pin12is fixed to the thickest part of eccentric ring13. As shown inFIG.2B, eccentric ring13has convex profile (131,132) on the outer diameters and both sides, which helps to maintain lubrication file on the surface and keep line contact, instead of surface contact, in the second position as shown inFIG.1B. The convex profile of eccentric ring13reduces tendency of sticking at the second position. When reversible gerotor pump10is in the first position as shown inFIG.1Aand third position as shown inFIG.1C, the profile becomes flat on the outer diameter of eccentric ring13due to torque load. During the reversal of rotation direction, it may occur that the inertia and convex profile of the eccentric ring are not able to overcome sticking. A positive contact mechanism can be provided to increase the frictional drag between the eccentric ring and rotating rotors and overcome sticking. In the first embodiment of the positive contact system as shown inFIGS.3A and3B, positive contact mechanism100is provided at a higher thickness side of eccentric ring13. As shown in the partially enlarged view inFIG.3C, spring101and plunger102are arranged in cavity103such that spring101remains in compressed state. Due to the compression of spring101, a load (N) is acting on outer rotor through plunger102according to the friction force formula (4): F′=μ*Nequation (4), wherein F′ is the friction force, N is the load, and μ is the coefficient that depends on the friction surface and working condition. Thus, an increase in the load (N) results in more friction force F which is capable of rotating eccentric ring13. If required, plunger102can have Ferritic Nitro-Carburizing (FNC) friction coating which results in higher coefficient μ of the friction. FNC coating helps increase static coefficient of friction and reduce tendency of wear. Moreover, if cavity103is difficult to manufacture in eccentric ring13, a drill through hole with a cap added at the outer diameter of eccentric ring13can be used. In the second embodiment of the positive contact system as shown inFIGS.4A to4C, a frictional disc brake type positive contact mechanism is provided. The positive contact system comprises spring, piston, and pads that are arranged on the pump system as in the frictional disc brake system. The working mechanism and components of the conventional frictional disc brake system is well known where, based on the Pascal Law, the force applied to the pad is proportional to the area of the pad in the system. The frictional disc brake type positive contact system in the present invention further provides added auto release function in addition to the frictional force. As shown inFIGS.4A to4C, a frictional disc brake type positive contact mechanism comprises spring101′, piston104, and pad105. As shown inFIG.4B, spring101′ hold eccentric ring13and outer rotor17together with help of pads105and spring force at the second position. As shown inFIG.4C, as the pump rotates, outlet pressure releases pads105and allow eccentric ring13and outer rotor17to rotate freely at the first and third positions. In application, when shaft15is rotating at slow speed during switching of rotation direction (from clockwise to counterclockwise or vice versa) or contact force F2in accordance with formula (2) in the second position is not sufficient to rotate eccentric ring13, positive contact mechanism with friction disc brake pads105is especially useful. In one embodiment of the frictional disc brake positive contact system, the spring may be a Bellvile or wave spring that can be crushed by the fluid pressure and then expand to push the piston to the left and compress the friction discs. Friction discs would have a natural “compliance” whereby they expand when rotating to release grip. Furthermore, in the reversible gerotor pump of the present invention, the locking pin moves within the slot in both directions with clearance. As shown inFIG.5, clearance in both moving directions D1and D2provide self damping effect to avoid impact loading, locking pin12moves within the confinement of slot11. As shown inFIG.6, reversible gerotor pump10of the present invention is assembled for use in vehicle transmission. Under outer plate20, hydraulic fluid is sucked into reversible gerotor pump10through direction of inlet18and following direction18′ into the cavity between meshing teeth of inner rotor16and outer rotor17, while outer rotor17is in eccentric ring13which is confined by locking pin12fixed thereto within housing14. As shaft15rotates, inner and outer rotors rotate, and hydraulic fluid is discharged through direction of outlet19. The reversible gerotor pump can further comprise a novel design for the suction port with elongations at sides. As shown inFIGS.1A to1C, meshed teeth60of inner rotor16and teeth71of outer rotor17form regions called cavities40and50, and some cavity expands in one side50and contracts in other side40of housing14as rotation of both rotors advances. Rotation of rotor forms multiple cavities between the rotor teeth. The suction port of the reversible gerotor pump decides the filling capability of cavity and helps to prevent cavitation. Further, at any angular position of rotation, the cavity should not connect discharge and suction ports at the same time, and inter-porting losses from the higher pressure region of the discharge port to the lower pressure region of the suction port should be avoided. As shown inFIG.7, the conventional design of the gerotor pump includes the region in which expansion of cavity takes place and gives the basis to form a suction port30, and similarly, a discharge port32is formed in the following contraction region. Suction port30and discharge port32are symmetric bean shaped ports at the suction and discharge side, respectively. The bean shaped suction port30includes upstream side30aand downstream side30b. As the pump is reversible (bi-directional), the suction port30and the discharge port32are symmetric about x-axis. As shown inFIG.8A, suction port30of the present invention is provided with prolongations31and31′ at both upstream side30aand downstream side30b, respectively. As shown inFIG.8B, prolongation31at upstream side30aof suction port30is provided to increase cavity filling time when rotor rotates in reverse direction, and prolongation31′ at downstream side30bof suction port30is provided to increase cavity filling time when rotor rotates in clockwise direction. Cavity50′ inFIG.8Bshows that the cavity is about to connect to discharge port32and leave suction port30, though the cavity should never connect discharge and suction ports at the same time to avoid inter-porting losses from the higher pressure region of the discharge port to the lower pressure region of the suction port. As further illustrated inFIGS.9A and9B, suction port30is terminating in the rotation direction of the rotor sets with two prolongations31and31′. The shape and dimensions of prolongations31and31′ are designed such that suction and discharge ports do not connect to the same captured volume and inter-porting losses from high to low pressure side do not take place. Prolongation31′ at downstream side30bdirect more fluid into cavity to fill it substantially. Prolongation31at upstream side30aof rotor are given for the same purpose when rotor is in reverse direction. FIGS.10A to10Fshow analysis results for the vapor volume fraction for the conventional gerotor pump and the reversible gerotor pump with the prolongation at the suction port at 0 degree, 30 degree, and 60 degree of rotor rotation at 5000 rpm and 0.5 bar back pressure. As shown inFIGS.10A and10D, suction starts at 0 degree and advances in direction of rotation which is captured at 30 degree (FIGS.10B and10E) and 60 degree (FIGS.10C and10F). In conventional gerotor pump at 5000 rpm, at 0 degree as shown inFIG.10A, the low pressure regions form at the upstream side on the right due to expansion of the cavity before suction port, and vapor fraction is carried from suction port as shown by the 3 large areas on the left; at 30 degree as shown inFIG.10B, vapor intensity in the cavity at upstream side inFIG.10Ais getting reduced as it exposes to higher pressure fluid at suction port, while at the downstream side, vapor fraction is carried from suction port as seen at the upper portion ofFIG.10B; at 60 degree as shown inFIG.10C, vapor formation can be seen at the downstream side of the suction port (right side) due to insufficient cavity filling, while on left side, a large vapor fraction is carried from the suction port to the discharge port. In summary, in the conventional design, as the cavity volume increases, the vapor fraction also increases because of insufficient filling, i.e., vapor at the discharge side is carried from the suction port (but it is not generated at the discharge port). In comparison, in the reversible gerotor pump at 5000 rpm, at 0 degree as shown inFIG.10D, the low pressure regions form at the upstream side on the right due to expansion of the cavity before suction port, while there is no vapor fraction carried from suction port on the left; at 30 degree as shown inFIG.10E, as the prolongation on the suction port improves the cavity filling time which results in sufficient filling and prevents cavitation, the vapor intensity in the cavity moving towards the upstream side is getting further reduced as it exposes to higher pressure fluid at suction port, and there is no vapor fraction at the downstream side, and no vapor fraction is carried from suction port; at 60 degree as shown inFIG.10F, no significant vapor formation is shown at the downstream side of the suction port (right side), while on inter-porting cavity on the top and at the left side, there is no vapor fraction. In summary, the reversible gerotor pump having the prolongations increases the cavity filling time which results in sufficient filling and prevent cavitation. As shown inFIG.12, the fill speed of the pump improves to above 5000 rpm, and up to 5370 rpm in comparison to the conventional pump at 3330 rpm—an increase in the fill speed by 2040 rpm. As shown inFIG.13, an increase in the volumetric efficiency of 29% is achieved, i.e., from 68% to 97%, at 5000 rpm speed, which exceeds the CTQ requirement.FIG.13shows that there is significant increase in the volumetric efficiency in the cavitation zone, that is, after 3330 rpm, and the volumetric efficiency increases even at lower pump speeds where cavitation is not taking place due to improved filling through the prolongations. The prolongations on the suction port of the reversible gerotor pump system may be manufactured in all sizes of reversible gerotor pumps to improve the volumetric efficiency and maximum operating speed. The suction port of the reversible gerotor pump system can be implemented on any lubrication pump. It is beneficial in the transmission system for vehicles and is particularly useful for medium and heavy-duty electric vehicle transmissions, as an example. The reversible gerotor pump can be used in other applications than vehicle transmissions. It is easily manufacturable since High Pressure Die Casting (HPDC) is used to manufacture the pump housing. There is no addition in the weight of pump, and it is cost effective and helps to reduce the overall size of the port by reducing other dimensions, such as the depth and width of the port, while maintaining the required volumetric efficiency. The suction port meets all technology feasibility, manufacturability, and cost aspects. The reversible gerotor lubrication pump provides a compact design due to the radial position of the eccentricity adjusting reversing ring. Self actuation based on the inertia of the eccentricity adjusting ring and the rotational friction during reversal operation eliminate the need for external actuation. The transmission gear gets lubrication from same port in either clockwise or counterclockwise direction of rotation with high pump volume and utilization rates, whether at slow or high speed. A transmission system for vehicles can comprise the reversible gerotor pump system of the present disclosure. The reversible gerotor pump system can be used for supplying hydraulic fluid in the transmission system of any vehicles and is particularly useful in the transmission system for medium and heavy-duty electric vehicles. An electric vehicle can comprising the transmission system disclosed herein. The electric vehicle can be a heavy duty truck. The description is exemplary in nature and one of skill would understand that variations are intended to be within the scope of the present invention. | 23,647 |
11859615 | DETAILED DESCRIPTION OF THE EMBODIMENTS The following description is essentially only illustrative, rather than intending to limit the present disclosure and the application or usage thereof. It should be appreciated that, throughout all drawings, similar reference numerals indicate the same or similar parts or features. Each drawing only illustratively shows the concept and principle of the embodiments of the present disclosure, and does not necessarily show the specific dimensions and scales of various embodiments of the present disclosure. Specific parts in specific drawings may be exaggerated to illustrate related details or structures of various embodiments of the present disclosure. In the description of the embodiments of the present disclosure, the orientation terms related to “upper”, “lower”, “left”, and “right” used herein are described according to the upper, lower, left and right position relationships of the views shown in the accompanying drawings. In practical applications of the scroll compressor, the positional relationships of “upper”, “lower”, “left”, and “right” used herein may be defined according to actual conditions. These relationships may be reversed. FIG.1shows a cross-sectional view of a scroll compressor1of a comparative example. As shown inFIG.1, the scroll compressor1includes a housing assembly10, a compression mechanism20and a partition30(for example, a muffler plate) accommodated in the housing assembly10. The housing assembly10includes a top cover11, a housing12and a base13. The top cover11, the housing12and the base13are hermetically coupled to each other to define a sealed space within the housing assembly10. The partition30divides the space inside the housing assembly10of the scroll compressor1into a high pressure space VH and a low pressure space VL. Specifically, the top cover11is sealingly mounted to an upper end of the housing12, the partition30is mounted above the compression mechanism20and is sealingly mounted to the inner wall of the housing assembly10(either the inner peripheral wall of the top cover11or the inner peripheral wall of the housing12or both), thereby defining a high pressure space VH between the top cover11and the partition30in the housing assembly10of the scroll compressor1and defining a low pressure space VL below the partition30in the housing assembly10. The compression mechanism20includes a fixed scroll21and a movable scroll23. The fixed scroll21includes blades212extending from the end plate211toward the first side (lower side inFIG.1) and cylindrical portions213extending from the end plate211toward the opposite second side (upper side inFIG.1). A radial dimension of the upper end of the cylindrical portion213is set to be smaller than a radial dimension of the rest of the cylindrical portion213, so that an outer shoulder portion2131is formed at the upper end of the cylindrical portion23(seeFIG.2andFIG.3). An exhaust port214is provided in the center of the fixed scroll21, and the exhaust port214penetrates through the end plate211and the cylindrical portion213. The exhaust port214is provided to have a smaller diameter in the end plate211and a larger diameter in the cylindrical portion213. The movable scroll23includes blades232extending toward one side (upper side inFIG.1) from an end plate231thereof. The movable scroll23is adapted to translate relative to the fixed scroll21, so that the blades232of the movable scroll23cooperate with the blades212of the fixed scroll21to define a series of compression chambers between the movable scroll23and the fixed scroll21. During the operation of the scroll compressor1, with the compression movement of the compression mechanism20, the working fluid (for example, refrigerant gas) enters the housing assembly10from the air inlet port14of the scroll compressor1, and enters the compression chamber in the compression mechanism20. The compressed working fluid (for example, high pressure refrigerant gas) exits the compression mechanism20from the exhaust port214of the fixed scroll21and enters the high pressure space VH in the housing assembly10of the scroll compressor1, and leaves the scroll compressor1through the exhaust port15. The scroll compressor1is further provided with a capacity adjustment device M. The capacity adjustment device M includes a bypass passage41, an annular adjusting member42and a mounting piece43. The bypass passage41is formed in the fixed scroll21and penetrates through the end plate211of the fixed scroll21. The first end (lower end inFIG.1) of the bypass passage41is opened at the second side (lower side) of the end plate211of the fixed scroll21, so as to communicate with the first compression chamber (for example, the first medium pressure chamber) C1of a series of compression chambers of the compression mechanism20that has a pressure P1. The second end (the upper end inFIG.1) of the bypass passage41is open to the first side of the end plate211of the fixed scroll21and selectively communicates with the low pressure space VL. The mounting piece43is mounted to the fixed scroll21. The adjusting member42is hermetically installed with the fixed scroll21and the mounting piece43and is provided to be movable in the axial direction O of the compression mechanism20relative to the fixed scroll21and the mounting piece43, so as to selectively open or cover the second end of the bypass passage41, and to establish or interrupt the communication between the first compression chamber C1and the low pressure space VL, thereby realizing the capacity adjustment of the scroll compressor1. FIG.2andFIG.3show partial sectional views of the scroll compressor1inFIG.1, showing the capacity adjustment device and the sealing assembly S of the scroll compressor1under different load conditions. The annular adjusting member42includes a first portion421and a second portion422surrounding the first portion421. The first portion421has a flat bottom surface. The first portion421is located directly above the bypass passage41, and the sealing ring44is mounted on the first portion421via the fixing member45. The sealing ring44is sandwiched between the fixing member45and the first portion421. The radially inner edge of the sealing ring44is sealingly engaged with the outer peripheral wall of the cylindrical portion213of the fixed scroll21, so as to provide a seal between the space above and below the first portion421. The adjusting member42is movable in the axial direction O relative to the cylindrical portion213, so that the first portion421selectively opens or covers the second end of the bypass passage41. The second portion422extends upward in the axial direction O and radially outward from the outer periphery of the first portion421, thereby forming a first annular recessed portion between the outer peripheral wall of the cylindrical portion213and the second portion422, the opening of which faces the partition30and forming a second annular recessed portion in the second portion422, the opening of which faces the end plate211of the fixed scroll21. The lower end of the first annular recessed portion is sealed by the sealing engagement of the sealing ring44with the outer peripheral wall of the cylindrical portion213of the fixed scroll21. The sealing assembly S is installed in the first annular recessed portion whose lower end is sealed, and provides a seal between the partition30, the fixed scroll21and the adjusting member42, thereby forming a back pressure chamber B in the first annular recessed portion. The sealing assembly S includes a first sealing piece51, a second sealing piece52, a third sealing piece53and a first mounting piece54. The first sealing piece51and the first mounting piece54are engaged (e.g., riveted) to each other, and sandwich the second sealing piece52and the third sealing piece53therebetween. The upper end of the first sealing piece51abuts against the partition30to form a first sealing portion, thereby separating the high pressure space VH and the low pressure space VL in the scroll compressor1. The inner periphery of the second sealing piece52abuts against the cylindrical portion213of the fixed scroll21to form a second sealing portion, and the outer periphery of the third sealing piece53abuts against the second portion422of the adjusting member42to form a third sealing portion, thereby forming a back pressure chamber B in the first annular recessed portion between the outer peripheral wall of the cylindrical portion21and the second portion422, the back pressure chamber B communicates with a back pressure passage (not shown) formed in the fixed scroll21. The first end (lower end)216of the back pressure passage (only shown inFIG.4) communicates with the second compression chamber (for example, the second medium pressure chamber) of a series of compression chambers of the compression mechanism20that has a pressure P2, thereby providing back pressure (i.e., pressure P2) to the back pressure chamber B.FIG.4shows a plan view of the fixed scroll21of the scroll compressor1as viewed from the blade212side of the fixed scroll21, showing the first end216of the back pressure passage and the first end411of the bypass passage41. To prevent the back pressure passage from being covered by the first portion421of the adjusting member42, the back pressure passage is at least partially formed in the cylindrical portion213of the fixed scroll21, so that the second end (upper end, not shown) of the back pressure passage is exposed from the outer shoulder portion2131of the cylindrical portion213. The mounting piece43is sealingly mounted within a second annular recessed portion in the second portion422of the adjusting member42, and is mounted on the end plate211of the fixed scroll21, the annular sealing piece46is mounted on the mounting piece43. The annular sealing piece46abuts against the side wall of the second annular recessed portion, thereby forming an annular variable pressure chamber D within the second annular recessed portion. The annular variable pressure chamber D may selectively communicate with the low pressure space VL or the back pressure chamber B in the compression mechanism20to change the pressure P3in the variable pressure chamber D. When the variable pressure chamber D communicates with the low pressure space VL, the pressure P3in the variable pressure chamber D is a relatively low intake pressure, so that the resultant force of the upward force acting on the adjusting member42is insufficient to overcome the resultant force of the downward force acting on the adjusting member42. The adjusting member42moves downward so that the first portion421of the adjusting member42rests on the surface of the end plate211of the fixed scroll21, thereby blocking the bypass passage41, as shown inFIG.2. At this time, the communication between the first compression chamber C1and the low pressure space VL is interrupted, and the scroll compressor1operates in a full load condition. The upward resultant force acting on the adjusting member42includes the upward force acting on the adjusting member42by the bypass passage41, the upward force acting on the adjusting member42by the low pressure space VL and the upward force acting on the adjusting member42by the variable pressure chamber D. The downward resultant force acting on the adjusting member42includes the gravity of the adjusting member42itself, the downward force acting on the adjusting member42by the low pressure space VL and the downward force acting on the adjusting member42by the back pressure chamber B. When the variable pressure chamber D communicates with the back pressure chamber B, the pressure P3in the variable pressure chamber D is the back pressure (pressure P2) in the back pressure chamber B. The resultant upward force acting on the adjusting member42can overcome the resultant downward force acting on the adjusting member42. The adjusting member42moves upward away from the end plate211of the fixed scroll21in the axial direction O relative to the fixed scroll21, the mounting piece43and the annular sealing piece46to open the bypass passage41, as shown inFIG.3. The first compression chamber C1communicates with the low pressure space VL, and the scroll compressor1operates at a partial load. In the scroll compressor1, the sealing assembly S is designed as a floating sealing ring, and the first sealing portion between the sealing assembly S and the partition30is a metal contact surface. During the operation of the scroll compressor1, in order to reliably separate the high pressure space VH and the low pressure space VL, the contact force of the first sealing portion needs to be set larger. Under partial load condition, in order to provide reliable sealing at the first sealing portion between the first sealing piece51and the partition30to separate the high pressure space VH from the low pressure space VL, it is often necessary to set the back pressure (pressure P2) in the back pressure chamber B to be relatively high, and it is necessary to set the first end216of the back pressure passage communicating with the back pressure chamber B to be closer to the central area of the blade212of the fixed scroll21, as shown inFIG.4. However, when the scroll compressor1operates at full load, it is often desired that the back pressure (pressure P2) in the back pressure chamber B be relatively low to reduce the axial force of the compression mechanism20, thereby reducing the power consumption of the scroll compressor1and ensuring the system performance. Therefore, the requirements for the pressure in the back pressure chamber B of the scroll compressor1are significantly different under partial load conditions and under full load conditions. In addition, since the first sealing portion between the first sealing piece51and the partition30separates the high pressure space VH and the low pressure space VL, the pressure difference between the two sides of the sealing portion is large, and it is further required to set the back pressure (pressure P2) in the back pressure chamber B to be relatively high, so that the difference in the requirements for the back pressure (pressure P2) in the back pressure chamber B under different load conditions are further enlarged. In addition, the manufacturing and processing requirements of each component of the above-mentioned sealing assembly S are also strict, and the cost is relatively high. In addition, the metal sealing surface is prone to rust which is also a problem. Therefore, it is necessary to improve the sealing assembly and capacity adjustment device of the scroll compressor to balance the requirements for the pressure in the back pressure chamber under different working conditions. Under the condition of ensuring sealing, it is desirable to reduce the axial force of scroll compressor, reduce the power consumption of compressor, improve the system performance and reduce the manufacturing cost as much as possible. In view of the above problems, the present inventor proposes an improved scroll compressor, and the difference between the requirements for the pressure of the back pressure chamber under different load conditions is favorably alleviated by reasonably designing the capacity adjustment device and the sealing assembly arranged between the capacity adjustment device, the fixed scroll and the partition. It is possible to reduce the axial force of the scroll compressor under full load condition, reduce the power consumption of the compressor, improve the system performance and reduce the manufacturing cost while ensuring reliable sealing. The scroll compressor according to the present disclosure is described below with reference to the accompanying drawings. FIG.5toFIG.7illustrates partial cross-sectional views of the scroll compressor100according to the first embodiment of the present disclosure.FIG.6andFIG.7show the compression mechanism20, the partition30, the capacity adjustment device M1and the sealing assembly S1mounted between these components of the scroll compressor100under different load conditions, respectively. The scroll compressor100according to the first embodiment of the present disclosure is different from the scroll compressor1of the comparative example in the design of the capacity adjustment device and the sealing assembly, and the other aspects are generally the same. In the drawings, the same elements as those of the scroll compressor1of the comparative example are denoted by the same reference numerals, and the description are not repeated. Only the differences between the scroll compressor100according to the first embodiment of the present disclosure and the scroll compressor1of the comparative example are described below. As shown inFIG.5toFIG.7, the capacity adjustment device M1of the scroll compressor100includes a bypass passage71, an annular adjusting member72and a mounting piece73. The bypass passage71is formed in the fixed scroll21and penetrates through the end plate211of the fixed scroll21. The first end711(lower end inFIG.5toFIG.7) of the bypass passage71is opened at the first side (lower side in the figure) of the end plate211of the fixed scroll21, so as to communicate with the first compression chamber (for example, the first medium pressure chamber) C1of a series of compression chambers of the compression mechanism20that has a pressure P1. The second end (the upper end inFIG.5toFIG.7) of the bypass passage71is open at the second side (the upper side in the figure) of the end plate211of the fixed scroll21and selectively communicates with the low pressure space VL in the scroll compressor100. The first portion721of the adjusting member72is located directly above the second end of the bypass passage71, and the sealing ring74is mounted on the first portion721via the fixing member75. The sealing ring74is sandwiched between the fixing member75and the first portion721. The radially inner edge of the sealing ring74is sealingly engaged with the outer peripheral wall of the cylindrical portion213of the fixed scroll21, so as to provide a seal between the space above and below the first portion721. The adjusting member72is movable in the axial direction relative to the cylindrical portion213of the fixed scroll21, so that the first portion721selectively opens or covers the second end of the bypass passage71. The second portion722of the adjusting member72extends radially outward and axially upward from the outer periphery of the first portion721, and a first annular recessed portion whose opening faces the partition30is formed between the outer peripheral wall of the cylindrical portion213of the fixed scroll21and the second portion722of the adjusting member72. A second annular recessed portion whose opening faces the end plate211of the fixed scroll21is formed in the second portion722. The lower end of the first annular recessed portion is sealed by the sealing engagement of the sealing ring74with the outer peripheral wall of the cylindrical portion213of the fixed scroll21. However, the present disclosure is not limited thereto. In other examples of the present disclosure, in the case where the first portion721of the adjusting member72has a sufficient thickness, a sealing piece may be provided between the radially inner end face of the first portion721of the adjusting member72and the outer peripheral wall of the cylindrical portion213of the fixed scroll21. For example, an annular groove is provided in the radially inner end face of the first portion721of the adjusting member72and an annular sealing piece is provided in the annular groove, so that the radially inner end face of the first portion721of the adjusting member72is sealingly engaged with the outer peripheral wall of the cylindrical portion213of the fixed scroll21. The sealing assembly S1is installed in the first annular recessed portion whose lower end is sealed, and provides a seal between the partition30, the fixed scroll21and the adjusting member72, thereby forming a back pressure chamber B1in the first annular recessed portion. The sealing assembly S1adopts a flat-top sealing ring design, and includes a first sealing piece61, a second sealing piece62, a first mounting piece63and a second mounting piece64. Both the first sealing piece61and the second sealing piece62are flexible sealing pieces, and both the first mounting piece62and the second mounting piece64are compression springs. The first sealing piece61is mounted between the cylindrical portion213of the fixed scroll21and the partition30. The first mounting piece63abuts the first sealing piece61against the partition30to form a first sealing portion, and at least a part of the first sealing piece61abuts against the inner wall of the cylindrical portion213. The upper end of the cylindrical portion213of the fixed scroll21is further formed with an inner shoulder portion2132. The first mounting piece63is mounted on the inner shoulder portion2132, so that the first sealing portion between the first sealing piece61and the partition30is located radially inside the cylindrical portion213. The second sealing piece62is installed between the partition30and the adjusting member72, and the second mounting piece64presses the second sealing piece62against the partition30to form a second sealing portion. The second sealing portion is located radially outside the first sealing portion, and at least a part of the second sealing piece62abuts against the second portion722of the adjusting member72, thereby forming a back pressure chamber B1in the first annular recessed portion between the outer peripheral wall of the cylindrical portion213of the fixed scroll21and the second portion722of the adjusting member72. The back pressure chamber B1communicates with the second compression chamber (for example, the second medium pressure chamber) C2of a series of compression chambers of the compression mechanism20that has a pressure P2via a back pressure passage215formed in the fixed scroll21. The first end (lower end)2152of the back pressure passage215is exposed from the lower surface of the end plate211of the fixed scroll21and communicates with the second compression chamber C2, and the second end (upper end)2151of the back pressure passage215is exposed from the outer shoulder portion2131of the cylindrical portion213of the fixed scroll21.FIG.8shows a plan view of the fixed scroll21of the scroll compressor100as viewed from the blade212side of the fixed scroll21, showing the first end2152of the back pressure passage215and the first end711of the bypass passage71. The mounting piece73is sealingly mounted in a second annular recessed portion in the second portion722of the adjusting member72, and is mounted on the end plate211of the fixed scroll21, the annular sealing piece76is mounted on the mounting piece73. The annular sealing piece76abuts against the side wall of the second annular recessed portion, thereby defining an annular variable pressure chamber D1within the second annular recessed portion. The variable pressure chamber D1selectively communicates with the low pressure space VL in the compression mechanism20or communicates with the back pressure chamber B1to change the pressure P3in the variable pressure chamber D1. When the variable pressure chamber D1communicates with the low pressure space VL, the pressure P3in the variable pressure chamber D1is the relatively low intake pressure, the resultant upward force acting on the adjusting member72may not overcome the resultant downward force acting on the adjusting member72. The adjusting member72moves downward in the axial direction with respect to the fixed scroll21, the mounting piece73and the annular sealing piece76so that the first portion721of the adjusting member72rests on the surface of the end plate211of the fixed scroll21, thereby blocking the bypass passage71, as shown inFIG.6. At this time, the communication between the first compression chamber C1and the low pressure space VL is interrupted, and the scroll compressor100operates in a full load condition. The upward resultant force acting on the adjusting member72includes the upward force acting on the adjusting member72by the bypass passage71, the upward force acting on the adjusting member72by the low pressure space VL and the upward force acting on the adjusting member72by the variable pressure chamber D1. The downward resultant force acting on the adjusting member72includes the gravity of the adjusting member72itself, the downward force acting on the adjusting member72by the low pressure space VL and the downward force acting on the adjusting member72by the back pressure chamber B1. When the variable pressure chamber D1communicates with the back pressure chamber B1, the pressure P3in the variable pressure chamber D1is the back pressure (pressure P2) in the back pressure chamber B1. The resultant upward force acting on the adjusting member72can overcome the resultant downward force acting on the adjusting member72. The adjusting member72moves upward away from the end plate211of the fixed scroll21in the axial direction relative to the fixed scroll21and the mounting piece73to open the bypass passage71, as shown inFIG.7. At this time, the first compression chamber C1communicates with the low pressure space VL, and the scroll compressor1operates at a partial load. FIG.9shows a partial enlarged view ofFIG.7showing the installation between the second sealing piece62of the sealing assembly S1and the partition30and the adjusting member72. As shown inFIG.9, the second mounting piece64abuts the second sealing piece62against the partition30and the second portion722of the adjusting member72. The second sealing piece62is compressed between the top of the second mounting piece64and the partition30, and at least a portion of the second sealing piece62is in sealing contact with the second portion of the adjusting member72. The axial spacing between the top of the second mounting piece64and the partition30(i.e., the thickness of the second sealing piece62in the compressed state) is d1, and the axial spacing between the top of the second portion722of the adjusting member72and the partition30is d2. In order to prevent the second sealing piece62from being blown out of the back pressure chamber B1, d1 and d2 are designed to satisfy the following relationship: d1>0.7d2. In addition, the thickness of the second sealing piece62in the uncompressed state is set to be greater than the axial distance d1 between the top of the second mounting piece64and the partition30, so that the second sealing piece62is in a compressed state when mounted between the second mounting piece64and the partition30, thereby ensuring sealing. The second mounting piece64is mounted on the outer shoulder portion2131and the second end2151of the back pressure passage215is always communicated with the back pressure chamber B1. In this example, in order to prevent the second mounting piece64from covering the second end2151of the back pressure passage215when mounted on the outer shoulder portion2131of the cylindrical portion213of the fixed scroll21, the second mounting piece64is mounted to the outer shoulder portion21of the fixed scroll21via the annular retainer65(seeFIG.6,FIG.7andFIG.9).FIG.10shows a plan view of the annular retainer65, the annular retainer65is provided with a notch651extending radially inward from the outer periphery of the annular retainer65. When the annular retainer65is mounted on the outer shoulder portion21of the fixed scroll21, the notch651is located directly above the second end2151of the back pressure passage215and faces the second end2151of the back pressure passage215, so that the back pressure chamber B1is always kept in communication with the back pressure passage215. The notch651may penetrate the entire thickness of the annular retainer65, or may extend from one side surface of the annular retainer65in the thickness direction of the annular retainer65without penetrating the annular retainer65. However, the present disclosure is not limited to this. In the case that the annular lower end of the second mounting piece64has sufficient radial size and sufficient rigidity can be ensured, the annular retainer65may not be provided. Instead, a through hole or groove directly facing the upper end2151of the back pressure passage215is provided at the annular lower end of the second mounting piece64, so that the back pressure chamber B1is always in communication with the back pressure passage215. In the scroll compressor100, the variable pressure chamber D1is selectively communicated with the low pressure space VL or the back pressure chamber B1via the electromagnetic switching valve80, so that the pressure P3in the variable pressure chamber D1is the intake pressure or the relatively high back pressure (pressure P2).FIG.11shows a perspective view of the electromagnetic switching valve80and the compression mechanism20being mounted together,FIG.12shows a cross-sectional view taken along the section line I-I inFIG.11. As shown inFIG.11andFIG.12, the electromagnetic switching valve80is mounted to the outer peripheral wall of the adjusting member72via the first set of screws T1. FIG.13andFIG.14show schematic diagrams of the electromagnetic switching valve80. The electromagnetic switching valve80is a two-position three-way electromagnetic valve, and includes a first valve body part81, a second valve body part82, and a control line83which are coupled to each other. The first valve body part81has a first surface81A, a second surface81B, and a third surface81C. The first surface81A is provided with a first set of mounting holes H1, the first set of screws T1pass through the first set of mounting holes H1on the first surface81A respectively to mount the first valve body part81to the outer peripheral wall of the second portion722of the adjusting member72. The second surface81B is provided with a second set of mounting holes H2, a second set of screws (not shown) pass through the second valve body part82and is screwed into the second set of mounting holes H2on the second surface81B of the first valve body part81, so as to couple the first valve body part81and the second valve body part82of the electromagnetic switching valve80to each other. A first inlet passage811, a second inlet passage814and an outlet passage817are provided in the first valve body part81. The first port812of the first inlet passage811is opened at the third surface81C and communicates with the low pressure space VL, the second port813of the first inlet passage811is opened at the second surface81B. The first port815of the second inlet passage814is opened at the first surface81A, and communicates with the back pressure chamber B1via a first through hole (not shown) on the adjusting member72, and thus communicates with the second compression chamber C2of the compression mechanism20. The second port816of the second inlet passage814is opened at the second surface81B. The first port818of the outlet passage817is opened at the second surface81B, the second port819of the outlet passage817is opened at the first surface81A, and communicates with the variable pressure chamber D1via a second through hole (not shown) on the adjusting member72. A valve core (not shown) of the electromagnetic switching valve80is controlled to selectively communicate the outlet passage817with the first inlet passage811or with the second inlet passage814. When the outlet passage817communicates with the first inlet passage811, the pressure P3in the variable pressure chamber D1is the intake pressure. When the outlet passage817communicates with the second inlet passage814, the pressure P3in the variable pressure chamber D1is equal to the back pressure (pressure P2) in the back pressure chamber B1. However, the present disclosure is not limited to this, and the pressure P3in the variable pressure chamber D1does not have to be equal to the back pressure (pressure P2) in the back pressure chamber B1. In other embodiments according to the present disclosure, the second inlet passage814of the electromagnetic switching valve80may be arranged to communicate with other medium pressure chambers in the series of compression chambers of the compression mechanism20instead of communicating with the back pressure chamber B1. The scroll compressor100according to the first embodiment of the present disclosure has been described above with reference toFIG.5toFIG.14. In the scroll compressor100according to the first embodiment of the present disclosure, the sealing assembly S1adopts the design of a flat-top sealing ring, and a first sealing portion and a second sealing portion are formed between the sealing assembly51and the partition30. The sealing surfaces of the first sealing portion and the second sealing portion are both flexible sealing surfaces, so that the requirements for the contact force of each sealing surface can be reduced, and the pressure in the back pressure chamber B1can be designed to be relatively small. Therefore, compared with the scroll compressor1of the comparative example, as can be seen from the comparison ofFIG.4andFIG.8, the second end2152of the back pressure passage215can be arranged closer to the outer periphery of the blades212of the fixed scroll21, so that the back pressure (pressure P2) is relatively small. With this arrangement, the axial force in the compression mechanism20can be reduced when the scroll compressor100operates under full load conditions, the difference between the requirements for the pressure in the back pressure chamber B1under different load conditions can be alleviated, the power consumption can be reduced and the system performance can be improved. Furthermore, compared with the sealing assembly S in the scroll compressor1of the comparative example, the sealing assembly S1itself of the scroll compressor100according to the first embodiment of the present disclosure is less difficult to manufacture and process, and the manufacturing cost can be reduced. The first sealing portion between the first sealing piece61and the partition30separates the high pressure space VH and the back pressure chamber B1(medium pressure space) in the scroll compressor100the second sealing portion between the second sealing piece62and the partition30separates the back pressure chamber B1(medium pressure space) and the low pressure space VL in the scroll compressor100. There is no direct leakage passage between the high pressure space VH and the low pressure space VL in the scroll compressor100. Therefore, this design itself may also reduce the contact force requirement of each sealing portion, thereby helping to set the back pressure (pressure P2) in the back pressure chamber B1to be relatively small, which is beneficial to alleviate the difference between the requirements for the back pressure (pressure P2) in the back pressure chamber B1under different load conditions. In addition, in the scroll compressor100according to the first embodiment of the present disclosure, the first sealing piece61is provided on the radially inner side of the cylindrical portion213of the fixed scroll21, so the cross-sectional area of the back pressure chamber B1that is perpendicular to the axial direction of the compression mechanism20can be set to be relatively small. Due to the reduced cross-sectional area, the axial force on the compression mechanism20can be reduced even when the back pressure (pressure P2) in the back pressure chamber B1is constant. Therefore, this arrangement optimizes the design of the back pressure chamber B1, which further facilitates reducing the axial force on the compression mechanism20. In addition, by adopting the arrangement that the first mounting piece63abuts the first sealing piece61against the partition30and the cylindrical portion213of the fixed scroll21and the second mounting piece64abuts the second sealing piece62against the partition30and the adjusting member72, it is helpful to seal the back pressure chamber B1. In addition, by mounting the second mounting piece64on the outer shoulder portion2131of the fixed scroll21through the annular retainer65with the notch651, it is helpful to maintain the communication between the back pressure chamber B1and the back pressure passage215, so as to establish the back pressure in the back pressure chamber B1, and thus facilitates the pressure adjustment of the variable pressure chamber D1. The scroll compressor200according to the second embodiment of the present disclosure is described below with reference toFIG.15andFIG.16. The scroll compressor200according to the second embodiment of the present disclosure is different from the scroll compressor1shown inFIG.1toFIG.4and the scroll compressor100shown inFIG.5toFIG.14in the design of the capacity adjustment device and the sealing assembly, and the other aspects are basically the same. Therefore, only the differences are shown in the drawings, and the same elements as scroll compressor1and scroll compressor100are denoted by the same reference numerals, and the differences are mainly described in the following, and the description of the same parts are not repeated. FIG.15shows a sectional view of the scroll compressor200. As shown inFIG.15, the capacity adjustment device M2of the scroll compressor200has a structure similar to the structure of the capacity adjustment device M of the scroll compressor1of the comparative example, and includes a bypass passage41, an adjusting member42and a mounting piece43.FIG.16shows the sealing assembly S2of the scroll compressor200. As shown inFIG.16, the sealing assembly S2includes a first sealing piece91, a second sealing piece92, a third sealing piece93, a first mounting piece94, a second mounting piece95and a third mounting piece96. The second sealing piece92, the third sealing piece93and the third mounting piece96have the same configurations as the second sealing piece52, the third sealing piece53and the first mounting piece54of the sealing assembly S of the scroll compressor1of the comparative example, respectively. The second mounting piece95is substantially the same as the first sealing piece51of the sealing assembly S of the scroll compressor1of the comparative example and the difference is that the second mounting piece95is provided with an annular flange951extending radially inward from the inner wall of the second mounting piece95, and the upper end of the second mounting piece95does not provide a seal with the partition30. The first sealing piece91is a flexible sealing piece, the first mounting piece94is a compression spring, the lower end of the first mounting piece is mounted on the annular flange951of the second mounting piece95, and the upper end of the first mounting piece abuts the first sealing piece91against the partition30to form a first sealing portion. The first sealing piece91is sandwiched between the partition30and the upper end of the cylindrical portion213of the fixed scroll21. The first sealing portion provides a seal between the high pressure space VH and the low pressure space VL in the scroll compressor200. The second mounting piece95and the third mounting piece96are coupled to each other and sandwich the second sealing piece92and the third sealing piece93therebetween. The inner peripheral edge of the second sealing piece92and the outer peripheral wall of the cylindrical portion213of the fixed scroll21form a second sealing portion. The second sealing portion separates the high pressure space VH and the back pressure chamber B2. The outer peripheral edge of the third sealing piece93and the second portion422of the adjusting member42form a third sealing portion. The third sealing portion separates the back pressure chamber B2from the low pressure space VL. The sealing surface of the first sealing portion is a flexible sealing surface, which can reduce the contact force required by the sealing portion compared with the scroll compressor1of the comparative example, and can set the back pressure (pressure P2) in the back pressure chamber B2to be relatively small, thereby reducing the axial force on the compression mechanism20under the full load condition and reducing the power consumption. It is possible to balance the requirements for the back pressure (pressure P2) in the back pressure chamber B2under different load operating conditions, improve the system performance, and realize the technical effects similar to those of the scroll compressor100according to the first embodiment of the present disclosure. Furthermore, compared with the scroll compressor100according to the first embodiment of the present disclosure, the scroll compressor200according to the second embodiment of the present disclosure makes fewer modifications on the basis of the scroll compressor1of the comparative example. The exemplary embodiments of the present disclosure have been described in detail here. It should be understood that the present disclosure is not limited to the specific embodiments described and shown in detail herein. Those skilled in the art can make various modifications and variations to the present disclosure without departing from the spirit and scope of the present disclosure. All these modifications and variations fall within the scope of the present disclosure. Moreover, all the members described herein can be replaced by other technically equivalent members. | 41,408 |
11859616 | FIG.1illustrates a compressor1consisting of a compressor element2with a gas inlet3and a compressed gas outlet4. The compressor1is usually driven by a fixed or variable-speed motor5. The compressor element2must be interpreted as the housing in which the compressor process takes place by means of a rotor or via a piston compressor movement. The compressor1comprises a pressure vessel6with an inlet7connected to the compressed gas outlet4and an outlet8connected to a user network9. This pressure vessel6is also known as a liquid separator, because it is inside this vessel that the air is separated from most of the liquid. The separated liquid is then returned to the compressor element via the return pipe16. The compressor1also comprises a (coalescence) filter which is either mounted in the liquid separator6, or in a separate pressure vessel13after the liquid separator6. A minimum pressure valve10is provided at the outlet8, on the liquid pipe provided between the pressure vessel6and the user network9. The minimum pressure valve10has a valve inlet11connected to the outlet8of the pressure vessel6and a valve outlet12adapted to be connected to a user network9. A pipe14connects the outlet8of the pressure vessel6with the pressure control entry of the minimum pressure valve10; in this pipe a control unit15is provided which regulates the pressure supply via the supply pipe14. FIGS.2and3show a cross-section of a minimum pressure valve10according to the invention. The minimum pressure valve10comprises a housing17with a housing inlet18, a housing outlet19, a chamber22afor receiving a removable subassembly22and a connecting space22bbetween the chamber22aand the housing outlet19. The housing inlet18is brought in fluid connection with the valve inlet11and the housing outlet19is brought in fluid connection with the valve outlet12when the minimum pressure valve is mounted within the compressor1. The minimum pressure valve10comprises a valve body21that is moveable in a chamber20between a closed position in which the valve inlet11is closed and an open position in which the valve inlet11is opened. When the valve inlet11is closed, no or practically no liquid is allowed to flow through the minimum pressure valve10, thus from the housing inlet18to the housing outlet19and further towards the user network9. Considering that, when the valve inlet11is open, liquid is allowed to flow through the minimum pressure valve10, from the housing inlet18to the housing outlet19and further reaching the user network9. The pressure which determines whether the valve body21moves to an open position, is determined by a control unit15. In commonly used minimum pressure valves10, a spring is used to set the pressure value whereby the minimum pressure valve is opened and such a spring is selected to suit the capacity and the pressure range of the compressor1. In the embodiment of the figures a control unit15replaces said spring, hereby avoiding the need for components which would be difficult to fit or replace as described in BE 2018/5011. The control unit15comprises a pipe14which forms a connection between the outlet8of the pressure vessel6and a space contained between the valve body21and the chamber20. The channel40will be used to transport air to a first end21aof the valve body21. The chamber20comprises a groove27or recess above a first end21aof the valve body21. Such a groove27creates a hollow space between the inside of the chamber20and the valve body21at the level of the first end21a. In the context of the present invention it should be understood that minimum pressure valves containing on the one hand a spring or on the other a control unit15, are within the scope of the invention. The valve body21comprises a seal24that is adapted to be mounted on the outer contour24aof the valve body21, thus between the valve body21and the internal side of the chamber20. The seal24is mounted between the first end21aand the second end21bof the valve body21. Such a seal24is therefore positioned so that there is a separation between on the one hand the space contained between the seal24, the groove27and the first end21a, whereby the pressure value is defined by the pressure of the liquid flowing through the channel40, and on the other hand the space contained between the seal24, the second end21band the connecting space in the housing17between the housing inlet18and the housing outlet19, whereby the pressure value is defined by the pressure supplied to the housing inlet18in the case that the valve body is in the open position or by the relevant pressure in the valve outlet19in the case that the valve body is in the closed position. Depending on the requirements for the minimum pressure valve10, more than one seal24may be fitted, such as for example 2, 3 or more seals. Preferably, a bi-directional seal is used. Such a seal will work in both directions.FIGS.4and5show a cross-section of such a seal. Alternatively, two single-action seals can be used, placed back-to-back or front-to-front in series. Although the figures show the seal placed around the valve body21, it is also possible to place this in the housing17of the minimum pressure valve10by providing a groove in the chamber20. Preferably, but without limiting nature, these seals can be characterised by very low friction and little stick-slip. The valve body21comprises a conductive element26, adapted to be fitted on the outer contour26aof the valve body21, between the valve body21and the inside of the chamber20. Such a conductive element26reduces the wear on the valve body21and on the inside of the chamber20. This wear is caused by the movement of the valve body21within the chamber20and the friction caused upon this. One or more conductive elements can be provided. In addition the conductive elements26absorb the transverse forces that occur during the movement of the valve body21within the chamber20. Consequently, these conductive elements26prevent the valve body21from tipping within the chamber20and subsequently becoming stuck in the chamber20. The seal24is fitted between two conductive elements26. The conductive element26can be executed in the form of a seal, a slide ring or a conductive tape. Although in the figures the conductive element26is placed around the valve body21, it would also be possible to place this in the housing17of the minimum pressure valve10by providing a groove in the chamber20. The valve body21comprises a bore28in which the piston23of the non-return valve36is mounted. This non-return valve is moveable between a closed position in which the housing inlet18is closed and an open position in which the housing inlet18is opened. In the piston23a channel25is provided to ensure that no air mounts up between the end of the piston23and the end of the internal bore28in the valve body21in which the piston23moves. For a stable and balanced operation of the non-return valve the axis of the bore28is aligned or almost aligned with the axis of the valve body21. The step section29of the non-return valve36ensures a seal between the outlet12of the minimum pressure valve10and the outlet of the pressure vessel6. For a flowing movement between the piston23and the valve body21and for the protection of the piston23and the valve body21from the harmful effects of the friction that is caused upon it, the piston23also comprises a second conductive element30which is adapted so that this can be mounted in position30abetween the piston23and the valve body21. Although in the figures the second conductive element30is placed around the piston23, it would also be possible to place this in the valve body21of the minimum pressure valve10by providing a groove in the central bore28of the valve body21. Depending on the design the minimal pressure valve10can consist of some or even all technical characteristics and functions mentioned herein and in any desired combination thereof. ‘Technical characteristics and functions’ refers here to: all components of the compressor1and the control unit15(can also be replaced with a spring), the pipe14, the valve body21, the channel25, the piston23, the seal24, the conductive unit26, the groove27, the step section29and the second conductive unit30. These functions do not all need to be present. As indicated in theFIGS.2,3,6and7, part of the minimum pressure valve10is removable (the subassembly22) through an opening31in the housing17; we call this removable part the subassembly. Subassembly refers here to: the lid32, the valve body21, the seal24, the conductive unit26, the piston23, the step section29and the second conductive unit30. These components do not all need to be present. The subassembly has an integrated cover plate or lid32which covers the opening31in the housing17of the minimum pressure valve10, preferably in the side wall of the housing17. An optional handle33used to easily remove the subassembly is fixed to the outside of the lid32. The subassembly is attached to the outside of the housing17of the minimum pressure valve10with the help of four bolts34. In addition, the subassembly, which can be taken out of the minimum pressure valve10, is provided with a connection40so that a particular air pressure can be applied to the components. Servicing of the minimum pressure valve10, according to the invention, is carried out as follows: First the four bolts34on the subassembly and the connection of the pressure supply pipe coming from the control unit15on the connection40in the housing17are detached. Next the subassembly is taken out of the housing17using the handle33. Then the valve body21is taken out of the chamber20. The seal24and the two slide rings26are now easily accessed for replacement. The non-return valve36(including the piston23) is taken out of the valve body21whereby the two slide rings30can be replaced. The piston23and the non-return valve36are mounted in the valve body21using self-alignment; the same occurs with the valve body21in the chamber20. Finally the four bolts34on the subassembly are tightened on the housing17of the minimum pressure valve10, and the pressure supply pipe coming from the control unit15is reattached to the connection40in the housing17. In the example shown a seal38is provided between the lid32and the housing17of the minimum pressure valve10in order to guarantee air tightness. This seal38will also be easily accessed for replacement when the subassembly is removed from the housing17using the handle33. The present invention is by no means limited to the embodiment described as an example and shown in the drawings, but a minimum pressure valve, compressor and method according to the invention as defined by the claims, can be realised in all kinds of variants without departing from the scope of the invention. | 10,811 |
11859617 | DETAILED DESCRIPTION OF EMBODIMENT(S) Embodiment An embodiment will be described below. As shown inFIG.1, a scroll compressor (10) is placed in a refrigerant circuit of a vapor compression refrigeration cycle. In this refrigerant circuit, a refrigerant compressed in the scroll compressor (10) condenses in a condenser, has its pressure decreased in a decompression mechanism, evaporates in an evaporator, and is then sucked into the scroll compressor (10). The scroll compressor (10) includes a casing (20), and an electric motor (30) and a compression mechanism (40) housed in the casing (20). The casing (20) has a vertically oriented cylindrical shape, and is configured as a closed dome. The electric motor (30) includes a stator (31) fixed to the casing (20) and a rotor (32) inside the stator (31). The rotor (32) is fixed to a drive shaft (11). The casing (20) has, at its bottom, an oil reservoir (21) for storing oil. A suction pipe (12) is connected to an upper portion of the casing (20). A discharge pipe (13) is connected to a barrel of the casing (20). A housing (50) is fixed to the casing (20). The housing (50) is located above the electric motor (30). The compression mechanism (40) is located above the housing (50). The discharge pipe (13) has an inflow end between the electric motor (30) and the housing (50). The drive shaft (11) extends vertically along the center axis of the casing (20). The drive shaft (11) includes a main shaft portion (14) and an eccentric portion (15) provided at the upper end of the main shaft portion (14). The main shaft portion (14) has a lower portion rotatably supported by a lower bearing (22). The lower bearing (22) is fixed to the inner circumferential surface of the casing (20). The main shaft portion (14) has an upper portion extending so as to pass through the housing (50) and rotatably supported by an upper bearing (51) of the housing (50). The compression mechanism (40) includes a fixed scroll (60) and a movable scroll (70). The fixed scroll (60) is fixed to the upper surface of the housing (50). The movable scroll (70) is interposed between the fixed scroll (60) and the housing (50). The housing (50) includes an annular portion (52) and a recess (53). The annular portion (52) forms the outer circumference of the housing (50). The recess (53) is provided in a central upper portion of the housing (50). The upper bearing (51) is located below the recess (53). The housing (50) is fixed to the inside of the casing (20). The inner circumferential surface of the casing (20) and the outer circumferential surface of the annular portion (52) of the housing (50) are in airtight contact with each other throughout the entire circumference. The housing (50) partitions the interior of the casing (20) into an upper space (23) in which the compression mechanism (40) is housed and a lower space (24) in which the electric motor (30) is housed. The fixed scroll (60) includes a fixed-side end plate (61), an outer circumferential wall (63) in a substantially cylindrical shape which stands on the outer edge of the lower surface of the fixed-side end plate (61), and a spiral fixed-side wrap (62) which stands inside the outer circumferential wall (63) of the fixed-side end plate (61) (seeFIG.2). The fixed-side end plate (61) is located on the outer circumference and continuous with the fixed-side wrap (62). The end surface of the fixed-side wrap (62) and the end surface of the outer circumferential wall (63) are substantially flush with each other. The fixed scroll (60) is fixed to the housing (50). The movable scroll (70) includes a movable-side end plate (71), a spiral movable-side wrap (72) located on the upper surface of the movable-side end plate (71), and a boss (73) located at a central portion of the lower surface of the movable-side end plate (71) (seeFIG.3). The eccentric portion (15) of the drive shaft (11) is inserted into the boss (73), whereby the boss (73) is connected to the drive shaft (11). An annular recess is formed in a portion of the upper portion of the housing (50) radially outside the recess (53). A back pressure chamber (54) is defined by the annular recess in the upper portion of the housing (50), the fixed scroll (60), and the movable scroll (70). An intermediate-pressure refrigerant is supplied from a compression chamber (S) in the course of compression to the back pressure chamber (54). The back pressure chamber (54) has an atmosphere with an intermediate pressure between the suction pressure and discharge pressure of the compression chamber (S). The intermediate pressure of the back pressure chamber (54) acts on the back surface of the movable scroll (70). An Oldham coupling (46) is provided in the back pressure chamber (54). The Oldham coupling (46) blocks the rotation of the movable scroll (70) on its axis. The compression mechanism (40) includes, between the fixed scroll (60) and the movable scroll (70), the compression chamber (S) into which a refrigerant flows. The movable scroll (70) is placed so that the movable-side wrap (72) meshes with the fixed-side wrap (62) of the fixed scroll (60). Here, the lower surface of the outer circumferential wall (63) of the fixed scroll (60) serves as a sliding surface that faces the movable scroll (70). On the other hand, the upper surface of the movable-side end plate (71) of the movable scroll (70) serves as a sliding surface that faces the fixed scroll (60). A suction port (64) that communicates with the compression chamber (S) is formed in the outer circumferential wall (63) of the fixed scroll (60). The suction pipe (12) is connected to the upstream side of the suction port (64). The compression chamber (S) is partitioned into an outer chamber (S1) located radially outward of the movable scroll (70) and inner chambers (S2) located radially inward of the movable scroll (70). Specifically, when the inner circumferential surface of the outer circumferential wall (63) of the fixed scroll (60) and the outer circumferential surface of the movable-side wrap (72) of the movable scroll (70) substantially come into contact with each other, the outer chamber (S1) and the inner chambers (S2) become separate sections with the contact portion serving as a boundary (see, e.g.,FIG.5). The fixed-side end plate (61) of the fixed scroll (60) has, at its center, an outlet (65). The high-pressure refrigerant compressed by the compression mechanism (40) flows out of the compression mechanism (40) to the lower space (24) via a path (not shown) formed through the fixed-side end plate (61) of the fixed scroll (60) and the housing (50). An oil supply hole (16) is provided inside the drive shaft (11) so as to extend vertically from the lower end to the upper end of the drive shaft (11). A lower end portion of the drive shaft (11) is immersed in the oil reservoir (21). The oil supply hole (16) supplies the oil in the oil reservoir (21) to the lower bearing (22) and the upper bearing (51), and to the gap between the boss (73) and the drive shaft (11). The oil supply hole (16) is open to the upper end surface of the drive shaft (11) and supplies oil to above the drive shaft (11). The recess (53) of the housing (50) communicates with the oil supply hole (16) of the drive shaft (11) via the inside of the boss (73) of the movable scroll (70). The high-pressure oil is supplied to the recess (53), so that a high pressure equivalent to the discharge pressure of the compression mechanism (40) acts on the recess (53). The movable scroll (70) is pressed onto the fixed scroll (60) by the high pressure that acts on the recess (53). An oil path (55) is provided in the housing (50) and the fixed scroll (60). The oil path (55) has an inflow end that communicates with the recess (53) of the housing (50) (not shown). The oil path (55) has an outflow end open to the sliding surface of the fixed scroll (60). Through the oil path (55), the high-pressure oil in the recess (53) is supplied to the sliding surfaces of the movable-side end plate (71) of the movable scroll (70) and the outer circumferential wall (63) of the fixed scroll (60). Configurations of Outer Oil Supply Mechanism, Inner Oil Supply Mechanism, and Intermediate-Pressure Groove As illustrated inFIG.2, the sliding surface of the outer circumferential wall (63) of the fixed scroll (60) has a fixed-side oil groove (81) serving as an outer oil supply mechanism (80), an oil supply groove (86)(an oil supply portion) serving as an inner oil supply mechanism (85), and an intermediate-pressure groove (83) (an intermediate-pressure portion). The fixed-side oil groove (81) is formed in the sliding surface, of the outer circumferential wall (63) of the fixed scroll (60), which faces the movable-side end plate (71) of the movable scroll (70). The fixed-side oil groove (81) extends substantially in an arc shape along the inner circumferential surface of the outer circumferential wall (63) of the fixed scroll (60). The oil path (55) communicates with the fixed-side oil groove (81), and oil is supplied to the fixed-side oil groove (81) from the oil path (55). The oil supply groove (86) extends along the circumferential direction of the fixed scroll (60). The oil supply groove (86) has one end that communicates with the suction port (64). Note that the oil supply groove (86) merely needs to communicate with a suction region of the compression chamber (S) upstream of the suction-side end of the movable-side wrap (72). The intermediate-pressure groove (83) is formed between the fixed-side oil groove (81) and the oil supply groove (86). The intermediate-pressure groove (83) has one end that communicates with the compression chamber (S) in the course of compression (under intermediate pressure). As illustrated inFIG.3, the sliding surface of the movable-side end plate (71) of the movable scroll (70) has a movable-side oil groove (82) serving as the outer oil supply mechanism (80), and a communication port (87) serving as the inner oil supply mechanism (85). The movable-side oil groove (82) is formed near an end portion of the fixed-side oil groove (81) of the fixed scroll (60). The movable-side oil groove (82) is substantially arc-shaped. An end portion of the movable-side oil groove (82) closer to the fixed-side oil groove (81) is bent and extends toward the center of the movable scroll (70). The movable-side oil groove (82) communicates with the fixed-side oil groove (81) and the outer chamber (S1) of the compression chamber (S) during one rotation of the movable scroll (70). The communication port (87) passes through an outer peripheral portion of the movable-side end plate (71) in the thickness direction thereof. The communication port (87) allows the sliding surface of the movable scroll (70) and the back pressure chamber (54) to communicate with each other. The communication port (87) of the movable scroll (70) communicating with the oil supply groove (86) of the fixed scroll (60) as indicated by the arrow inFIG.4allows oil in the back pressure chamber (54) to be supplied to the suction port (64). The compression mechanism (40) performs an inner oil supply operation for supplying oil to the inner chambers (S2), an outer oil supply operation for supplying oil to the outer chambers (S1), and a back pressure adjusting operation for supplying the intermediate-pressure refrigerant to the back pressure chamber (54). Specifically, the compression mechanism (40) sequentially repeats the inner oil supply operation, the outer oil supply operation, and the back pressure adjusting operation during one rotation of the movable scroll (70). Operation A basic operation of the scroll compressor (10) will be described. When activated, the electric motor (30) rotatably drives the movable scroll (70) of the compression mechanism (40). Since the rotation of the movable scroll (70) is blocked by the Oldham coupling (46), the movable scroll (70) performs only the eccentric rotation about the axis of the drive shaft (11). As illustrated inFIGS.5to8, the eccentric rotation of the movable scroll (70) partitions the compression chamber (S) into the outer chamber (S1) and the inner chambers (S2). The plurality of inner chambers (S2) are formed between the fixed-side wrap (62) of the fixed scroll (60) and the movable-side wrap (72) of the movable scroll (70). As the movable scroll (70) rotates eccentrically, these inner chambers (S2) gradually come closer to the center (i.e., the outlet (65)) and the volumes of these inner chambers (S2) gradually decrease. The refrigerant is gradually compressed in the inner chambers (S2) in this manner. When the inner chamber (S2) with the minimum volume communicates with the outlet (65), the high-pressure gas refrigerant in the inner chamber (S2) is discharged from the outlet (65). The high-pressure gas refrigerant flows out to the lower space (24) via the path formed in the fixed scroll (60) and the path formed in the housing (50). The high-pressure gas refrigerant in the lower space (24) is discharged outside the casing (20) via the discharge pipe (13). Oil Supply Operation Next, an oil supply operation of the scroll compressor (10) will be described in detail with reference toFIGS.4to8. Once the high-pressure gas refrigerant flows out to the lower space (24) of the scroll compressor (10), the lower space (24) becomes a high-pressure atmosphere, and the pressure of the oil in the oil reservoir (21) increases. The high-pressure oil in the oil reservoir (21) flows upward through the oil supply hole (16) of the drive shaft (11) and flows out from the opening at the upper end of the eccentric portion (15) of the drive shaft (11) to the inside of the boss (73) of the movable scroll (70). The oil supplied to the boss (73) is supplied to the gap between the eccentric portion (15) of the drive shaft (11) and the boss (73). Accordingly, the recess (53) of the housing (50) becomes a high-pressure atmosphere equivalent to the discharge pressure of the compression mechanism (40). The high pressure of the recess (53) presses the movable scroll (70) onto the fixed scroll (60). The high-pressure oil accumulated in the recess (53) flows out through the oil path (55) to the fixed-side oil groove (81) (not shown). Accordingly, the oil with the high pressure equivalent to the discharge pressure of the compression mechanism (40) is supplied to the fixed-side oil groove (81). An intermediate-pressure refrigerant is intermittently supplied from the compression chamber (S) under intermediate pressure to the back pressure chamber (54). As a result, the back pressure chamber (54) has an atmosphere with a predetermined intermediate pressure. The inner oil supply operation, the outer oil supply operation, and the back pressure adjusting operation are sequentially performed as the movable scroll (70) rotates eccentrically in this state. In all of these operations, the oil in the fixed-side oil groove (81) is used to lubricate the sliding surfaces around the fixed-side oil groove (81). Inner Oil Supply Operation The inner oil supply operation is performed when the movable scroll (70) reaches the eccentric angular position illustrated in, for example,FIG.5. In the inner oil supply operation, the communication port (87) and the oil supply groove (86) communicate with each other, and the oil in the back pressure chamber (54) is supplied to the oil supply groove (86). The oil supplied to the oil supply groove (86) is supplied to the suction port (64) of the compression chamber (S). Here, in this embodiment, to facilitate supplying oil toward the inner chambers (S2), the period during which the communication port (87) and the oil supply groove (86) communicate with each other is set as appropriate. Specifically, the communication port (87) and the oil supply groove (86) are determined to communicate with each other within a predetermined period in which the center position (C2) of a suction-side end of the movable-side wrap (72) in the thickness direction is located radially outward of the center position (C1) of the space between adjacent turns of the fixed-side wrap (62). In the example illustrated inFIG.5, the communication port (87) and the oil supply groove (86) start communicating with each other when the suction of the refrigerant is completely blocked by the movable scroll (70). The period in which the communication port (87) and the oil supply groove (86) communicate with each other is determined by setting the position of the communication port (87) and the width of the oil supply groove (86) as appropriate. Thus, the oil in the back pressure chamber (54) flows through the communication port (87), the oil supply groove (86), and the suction port (64) toward the inner chambers (S2) as indicated by the arrows inFIG.5. This can improve the oil sealing performances of the inner chambers (S2). When the movable scroll (70) in the eccentric angular position illustrated inFIG.5further rotates eccentrically, for example, to the eccentric angular position illustrated inFIG.6, the entire communication port (87) is located within the oil supply groove (86). At this timing, as well, the center position (C2) of the movable-side wrap (72) is located radially outward of the center position (C1) of the space between adjacent turns of the fixed-side wrap (62). This facilitates supplying oil to the inner chambers (S2) (see the arrows inFIG.6). When the movable scroll (70) in the eccentric angular position illustrated inFIG.6further rotates eccentrically, for example, to the eccentric angular position illustrated inFIG.7, the communication port (87) and the oil supply groove (86) are immediately before ending communication with each other. At this timing, the center position (C2) of the movable-side wrap (72) and the center position (C1) of the space between adjacent turns of the fixed-side wrap (62) substantially coincide with each other. This allows oil to be distributed to the inner chambers (S2) and the outer chamber (S1) (see the arrows inFIG.7). Outer Oil Supply Operation The outer oil supply operation is performed when the movable scroll (70) in the eccentric angular position illustrated inFIG.7further rotates eccentrically, for example, to the eccentric angular position illustrated inFIG.8. In the outer oil supply operation, the fixed-side oil groove (81) and the movable-side oil groove (82) communicate with each other, and the oil in the fixed-side oil groove (81) is delivered to the movable-side oil groove (82). Since a portion of the movable-side oil groove (82) bent radially inward communicates with the outer chamber (S1) at this moment, the oil in the movable-side oil groove (82) is supplied to the outer chamber (S1). This can improve the oil sealing performances of the outer chamber (S1). Back Pressure Adjusting Operation When the movable scroll (70) is in the eccentric angular position illustrated inFIG.8, the back pressure adjusting operation is also performed. In the back pressure adjusting operation, the communication port (87) and the intermediate-pressure groove (83) communicate with each other. Thus, the refrigerant in the outer chamber (S1) under intermediate pressure is supplied through the intermediate-pressure groove (83) and the communication port (87) to the back pressure chamber (54). As a result, the back pressure chamber (54) has an atmosphere with a predetermined intermediate pressure. As shown also inFIG.9, after the back pressure adjusting operation, the inner oil supply operation is performed again. Thereafter, the outer oil supply operation and the back pressure adjusting operation are sequentially repeated. In this embodiment, the period in which the communication port (87) and the oil supply groove (86) communicate with each other is set with reference to an angle at which the suction of the refrigerant into the outer chamber (S1) is completely blocked. Specifically, the communication port (87) communicates with the oil supply groove (86) within a predetermined period in which the movable scroll (70) rotates in a range of from 0° to 100°, where 0° is the angle at which the suction into the outer chamber (S1) is completely blocked. The predetermined period as used herein is represented by the rotational angle θ of the movable scroll (70), and is determined by the position of the communication port (87) and the width of the oil supply groove (86). Thus, oil can be supplied to the inner chamber (S2) of the compression chamber (S) at predetermined timing. Advantages of Embodiment The scroll compressor (10) of this embodiment includes the fixed scroll (60), and the movable scroll (70) that forms the compression chamber (S) with the fixed scroll (60). This scroll compressor (10) includes: a back pressure chamber (54) allowing an intermediate pressure between a suction pressure and a discharge pressure of the compression chamber (S) to act on a surface of the movable scroll (70) opposite to a sliding surface of the movable scroll (70); an outer oil supply mechanism (80) configured to supply oil to an outer chamber (S1) of the compression chamber (S) located radially outward of a movable-side wrap (72) of the movable scroll (70); and an inner oil supply mechanism (85) configured to supply oil to an inner chamber (S2) of the compression chamber (S) located radially inward of the movable-side wrap (72) of the movable scroll (70), wherein the inner oil supply mechanism (85) includes an oil supply groove (86) (oil supply portion) and a communication port (87), the oil supply portion (86) being formed in a sliding surface of the fixed scroll (60) to communicate with a suction region of the compression chamber (S), the communication port (87) passing through the sliding surface of the movable scroll (70) to communicate with the back pressure chamber (54), and the communication port (87) communicates with the oil supply groove (86) within a predetermined period in which a center position (C2) of a suction-side end of the wrap (72) of the movable scroll (70) in a thickness direction is located radially outward of a center position (C1) of a space between adjacent turns of a wrap of the fixed scroll (60), during one rotation of the movable scroll (70). In this embodiment, the outer oil supply mechanism (80) configured to supply oil to the outer chamber (S1) of the compression chamber (S) and the inner oil supply mechanism (85) configured to supply oil to the inner chambers (S2) are provided. The inner oil supply mechanism (85) has the oil supply groove (86) and the communication port (87). The communication port (87) and the oil supply groove (86) communicate with each other within the predetermined period in which the center position (C2) of the suction-side end of the wrap (72) of the movable scroll (70) in the thickness direction is located radially outward of the center position (C1) of the space between adjacent turns of the wrap of the fixed scroll (60). Accordingly, oil can be supplied to the spaces in the compression chamber (S) which are located radially inward and outward of the movable scroll (70). The scroll compressor (10) of this embodiment has the intermediate-pressure groove (83) (intermediate-pressure portion) formed in the sliding surface of the movable scroll (70) to communicate with the compression chamber (S) in the course of compression. The communication port (87) communicates alternately with the oil supply groove (86) and the intermediate-pressure groove (83) during one rotation of the movable scroll (70). In this embodiment, the communication port (87) communicates with the oil supply groove (86) and the intermediate-pressure groove (83) alternately during one rotation of the movable scroll (70). Thus, an intermediate-pressure refrigerant is intermittently supplied from the compression chamber (S) under intermediate pressure to the back pressure chamber (54). This allows the back pressure chamber (54) to have an atmosphere with a predetermined intermediate pressure. The scroll compressor (10) of this embodiment is configured such that the communication port (87) communicates with the oil supply groove (86) within the predetermined period in which the movable scroll (70) rotates in the range of from 0° to 100°, where 0° is the angle at which the suction into the outer chamber (S1) is completely blocked. In this embodiment, the period in which the communication port (87) and the oil supply groove (86) communicate with each other is set with reference to the angle at which the suction into the outer chamber (S1) is completely blocked. Thus, oil can be supplied to the inner chamber (S2) of the compression chamber (S) at predetermined timing. While the embodiment and variations have been described above, it will be understood that various changes in form and details can be made without departing from the spirit and scope of the claims. The above embodiment and variations may be appropriately combined or replaced as long as the functions of the target of the present disclosure are not impaired. As described above, the present disclosure is useful for a scroll compressor. | 25,226 |
11859618 | DETAILED DESCRIPTION OF EXEMPLARY EMBODIMENT(S) AND EXEMPLARY METHOD(S) Reference will now be made in detail to exemplary embodiments and methods of the invention as illustrated in the accompanying drawings, in which like reference characters designate like or corresponding parts throughout the drawings. It should be noted, however, that the invention in its broader aspects is not limited to the specific details, representative devices and methods, and illustrative examples shown and described in connection with the exemplary embodiments and methods. As best shown inFIG.1, a fluid pump assembly comprises a dry-side assembly10containing at least one magnet12and a wet-side assembly14containing at least one magnet16. The wet-side magnet16is operatively associated with a blade20for imparting movement to a fluid. The dry-side magnet12is connected to a shaft24which is driven by a motor18to rotate about an axis. In an exemplary embodiment, the dry-side magnet12is a circular disc having at least one pair of magnetic poles N and S. The poles may be arranged in an equal and opposite fashion, and can be arrayed in a radial pattern around the disc. The dry-side magnet12may be made from a variety of magnetic materials. In an exemplary embodiment, the dry-side magnet12is made from neodymium or other high performance magnetic material. The drive motor18may be of any appropriate type, such as electric, hydraulic, pneumatic, etc. In an exemplary embodiment, the drive motor18is an electric motor operating on either AC or DC. The motor18is connected to a power source (not shown) which may be a battery or outlet power. The drive shaft24rotates the dry-side magnet12about an axis. Because the movement of the dry-side magnet12creates a magnetic field, it may be useful to shield the motor18with a cover made out of a material, such as steel, that will prevent the magnetic field generated by the magnet from affecting the motor18. The dry-side assembly10may be permanently or releasable secured to the wall of a container26. Alternatively, the dry-side assembly10and the wet-side assembly14are placed on opposite sides of the container26and hold each other in place through the magnetic interaction between the magnets12,16. When the pump is activated, the drive motor18will rotate the dry-side magnet12. Rotation of the dry-side magnet12causes rotation of the wet-side magnet16, which causes the blade20to rotate and imparts movement to the fluid in the container26. The magnetic attraction between the magnets12,16should be sufficiently high so that the wet-side assembly14is held in place in the container26with enough force to prevent it from being dislodged due to liquid circulation or slight contact. For example, the net magnetic attraction between the dry-side assembly10and the wet-side assembly14may be at least 1.0 pound, though the net magnetic attraction may be varied depending on the size of the pump and the operating environment. Additionally, a variety of friction elements or cooperating projections and depressions between the assemblies10,14and the container26may be included. Though not necessary, additional brackets or other mechanical holding means can be included to attach the assemblies10,14to the container26. An exemplary embodiment of the dry-side assembly10will now be explained in more detail. As best shown inFIGS.2and3, the dry side assembly10comprises a housing30. The housing30includes a top portion32, a plurality of side ribs33, and an open bottom for receiving a bottom cover34. The housing30may be made from a material having a low thermal conductivity, such as a polymer material, and may be formed via a molding or extruding process. The side ribs33may vary in number and spacing. The side ribs33add strength to the housing30and assist in handling and placement of the housing30on a container26. In an exemplary embodiment, the bottom cover34is releasably secured to the remainder of the housing30. As best shown inFIG.3, the bottom cover34has a channel36which receives a projection38formed in the bottom of the housing30. The projection38may interlock with the channel36, or an adhesive may be applied to connect the two more permanently. Additional tabs or protrusion may be used in connection with or in place of the projection38to attach the bottom cover34to the housing30. A pad39made from a resilient material such foam, rubber, or silicone may be attached to the bottom of the cover34. The pad39separates the bottom cover34from a wall of the container26, acting as a cushion to prevent damage to both the dry-side assembly10and the container26. The pad39may also act as a friction device which assists in preventing the dry-side assembly10from rotating relative to the container26and to the wet-side assembly14during operation of the pump. An adhesive layer, for example a releasable adhesive, may be attached to the outer side of the pad39to increase the security of the connection between the housing30and the container26. In an exemplary embodiment, the housing30has a slot40which can receive a grommet42. The grommet42is made from a flexible material, for example rubber, to provide a flexible connection for a power cable (not shown) that connects to the motor18through the housing30. The grommet42prevents the cable from becoming worn due to contact with the housing30. The grommet42may attach to the housing through a mechanical connection, an adhesive connection, or a combination of both. As shown inFIG.3, an exemplary embodiment of the grommet42has a first tab44and a second tab46for connecting with the housing30and the bottom cover34respectively. The housing30may also be provided with a slot to retain the grommet42. If a power source is used for the motor18that does not require a direct cable connection, such as battery power, the grommet42and thus the slot40may not be incorporated into the housing30. The top portion32of the housing30may have a plurality of holes48for receiving screws, bolts, or other mechanical fasteners to connect the housing30to the motor18. Holes48may be chamfered to provide countersinking, allowing the mechanical fasteners to be either flush with or below the outer surface of the top portion32. The top portion32may also have a plurality of upper vents50. The upper vents50assist in providing air flow through the housing. For example, the upper vents50may act as air inlet vents. The housing30may also include a set of lower vents52spaced from the upper vents50. The lower vents52may act as air outlet vents in conjunction with air received from the upper vents50. The number of vents50,52, as well as their size and shape, may vary to allow for optimized air flow through the housing30and around the motor18. For example, areas of the housing30,32around the vents50,52may have transition portions, such as the rounded edges shown around the upper vents50or the tapered portions shown around the lower vents52. The transition portions reduce turbulence which can lessen noise and increase heat transfer efficiency. In an exemplary embodiment, the motor18is surrounded by an exterior casing19. As best shown inFIG.4, the casing19may include a top endcap54and a bottom endcap56. The endcaps54,56may be formed from a variety of materials. In an exemplary embodiment, the endcaps54,56are formed from a material having a high thermal conductivity such as aluminum. While the endcaps54,56are shown and described herein as separate pieces, it is possible that the endcaps54,56are formed as a unitary structure. The top endcap54may have a plurality of holes55to accommodate screws, bolts, or other mechanical fasteners to connect the top endcap54to the housing30. As shown inFIG.4, these holes55may be chamfered to provide countersinking, similar to holes48in the housing30. In an exemplary embodiment, the motor casing19has at least one fin58. Preferably, a plurality of fins58are arrayed circumferentially around the endcaps54,56as shown inFIG.4. The fins58extend longitudinally along the exterior surface of the motor casing19. These fins58may be connected to, or formed integrally with, either the top endcap54or to the bottom endcap56. The fins58may be formed from the same material as the endcaps54,56or from a separate material. Because the fins58act as heat exchangers, they may be formed from a material having a higher thermal conductivity than the endcaps54,56. In an exemplary embodiment, the fins58will be connected to the top endcap54and extend down below the top endcap54so that they are at least partially covering the bottom endcap56. The diameter of the endcaps54,56or the fins58may be dimensioned so that the fins58extending from the top endcap54contact the bottom endcap56. The fins58may be substantially frusto-pyramidal in shape, so that the bottom portion of the fin58connected to the casing19is longer than the top portion and the sides taper upwards towards each other. As best shown inFIG.4, the side of the fins58may have a rounded surface58a. This rounded side surface58awill face the air inlet vents50of the motor housing30. As air is drawn in through the inlet vents50, it flows over these rounded surfaces58abefore encountering the rest of the fin58. This helps maintain a smoother, more laminar flow, increasing the heat transfer along the fins58and resulting in quieter operation of the pump. Additionally, the top of the fins58may have chamfered, beveled, or rounded edges along the length of the fin to reduce turbulence. In an exemplary embodiment, the fins58are as thin as allowed by the associated material to increase the rate of heat transfer. The fins58may have an equal length or they may vary in length. As best shown inFIGS.4and5, this may be necessary when a slot57is placed in the bottom endcap56to allow a portion of the grommet42to pass through the endcap54. In an exemplary embodiment, the casing19is attached to the top portion32of the housing30, for example with mechanical fasteners connected through holes55. The upper vents50are sized to create an opening from approximately the outer surface of the casing19to approximately just beyond the fins58extended from the outer surface of the casing19. This allows for air to pass along the fins58and the outer surface of the casing19, increasing the amount of heat transfer. In the exemplary embodiment shown inFIG.5, the motor casing19bhas a top endcap54b, a bottom endcap56b, and a center casing59b. The top and bottom endcaps54b,56bmay have a plurality of holes55bfor connecting the housing30. The holes55bin at least one of the endcaps54b,56bmay also be used to connect the endcap to the stator64of the motor. The center casing59bincludes the slot57band the fins58bwhich may be attached to the center casing59bor formed integrally therewith. The fins58bmay be evenly distributed and extend along the length of the center casing59b. The endcaps54b,56band center casing59bmay be connected by screws, other mechanical fasteners, or an adhesive. Additionally, a sealing member such as an o-ring may be used to seal the connection between the endcaps54b,56band the center casing59b. The motor casing19houses the internal components of the motor18. In an exemplary embodiment, the motor18is a brushless dc motor, though a variety of motors may be used.FIG.6depicts portions of an exemplary motor18for reference, while other components have been omitted for clarity as the typical components and operation of a motor18will be understood by one of ordinary skill in the art. The motor18includes a rotor60having a shaft62, and a stator64. The bottom of the shaft62connects to the dry-side magnet assembly12. This connection may be achieved in a variety of different ways including bonding and press fit. In an exemplary embodiment, the shaft62is connected to the magnet66via a threaded connection. The threads on the shaft62may be either male or female. When the shaft has a male thread, female threads may be present on the magnet66and other components that may be connected therewith, such as plate68and a fan70. In various exemplary embodiments, the magnet66has a thread connection while the plate68and/or fan70are connected to the magnet66or one another via and adhesive. Additionally, both the shaft62and the magnet66may have a female thread, and a threaded fastener may be used to connect the components. As shown inFIG.9, the top of the shaft62may have a slot63so that a tool, such as a screwdriver, can be used to drive the shaft63, screwing it into the magnet assembly12. Though a flat-head screwdriver slot63is shown, a variety of other typical heads may be used such as a phillips heads or a hexagon or allen head. The threaded connection allows for easy assembly and changing of parts. As best shown inFIGS.7,9, and10the magnet assembly12comprises a magnet66, a plate68, and a fan70. The magnet66may be made from any magnet material, for example neodymium. In an exemplary embodiment, the intermediate plate68separates the fan70from the magnet66. The plate68may be made of a material, such as steel, that will block magnetic flux from the motor18. As the dry-side magnet12rotates and drives the wet-side magnet16, a magnetic field is created. Flux from the magnetic field can disturb the operation of the motor18. The intermediate plate68prevents or minimizes this disturbance. The magnet66, plate68, and fan70may be connected through a variety of different ways, such as mechanical fasteners or adhesives. As discussed above, these components may also be connected to each other through their connection to the shaft62. As best shown inFIGS.7-9, the fan70comprises a plurality of blades72. In an exemplary embodiment, the fan70will be designed as an impeller which draws air through the motor casing30. The fan70can be a radial fan or an axial fan. In a radial fan, the air will flow in a radial direction to the shaft, while in an axial fan the air will flow parallel to the shaft. Mixed flow fans, which result in both radial and axial type flow, and cross-flow fans may also be utilized. The fan70may be designed so that the airflow through the housing30has a near or completely laminar flow. Where laminar flow of the air through the housing is desired, an axial type fan may be used. In the exemplary embodiment shown inFIG.8A, the blades72aare equally spaced about the fan70a. The blades72ahave a flat end74a, a curved body76a, and a tapered end78a. Additionally the fan blades72aare spaced so that they do not overlap one another. Another exemplary embodiment of a fan70bis shown inFIG.8B. The blades72bhave a rounded end74b, a curved body76b, and a tapered end78b. The blades72bare positioned so they overlap one another and extend from the outer edge of the fan70bto the inner edge. The fan70bshown inFIG.8Balso includes a raised inner edge80b. The number, size, shape, and spacing of the blades72a,72bcan be varied from the exemplary embodiments shown to optimize airflow through a housing30, based on the design and internal components thereof. FIGS.10and11show an exemplary dry-side assembly10. The housing30is connected to the bottom cover34and surrounds the motor18and motor casing19. The pad39is connected to the bottom cover34. The top portion32of the housing30connects to the top endcap54of the motor casing19. The shaft62of the rotor60is connected to the magnet66. As the motor is operated, the shaft62will turn, rotating the magnet66and the fan70. The rotating blades72of the fan70will draw air in through the upper vents50. The air passes over the motor casing and along the fins58(if present). The air then exits the lower vents52. In this way, air can be drawn through the housing30to cool the motor18. The vents50,52should be designed to allow the most airflow while minimizing noise and turbulence. In an exemplary embodiment, the airflow through the housing30is completely laminar. The fins58increase the surface area, and hence the amount of heat transfer between the circulating air and the motor18, allowing the pump to operate at a higher rate of performance with less of a chance of overheating. Additionally, air cooling the motor18can reduce the amount of heat transferred to the container26. As discussed above, the housing30may be made from a material with a low thermal conductivity. Thus, as the air passes through the housing30, it forms a thermal boundary, minimizing the heat transferred to the housing30. This may keep the housing30cool to the touch, so that it may be safely handled by a user, even after prolonged periods of use. The foregoing description of the exemplary embodiments of the present invention has been presented for the purpose of illustration. It is not intended to be exhaustive or to limit the invention to the precise forms disclosed. Obvious modifications or variations are possible in light of the above teachings. The embodiments disclosed hereinabove were chosen in order to best illustrate the principles of the present invention and its practical application to thereby enable those of ordinary skill in the art to best utilize the invention in various embodiments and with various modifications as are suited to the particular use contemplated, as long as the principles described herein are followed. Thus, changes can be made in the above-described invention without departing from the intent and scope thereof. Moreover, features or components of one embodiment may be provided in another embodiment. Thus, the present invention is intended to cover all such modification and variations. | 17,484 |
11859619 | DETAILED DESCRIPTION The following describes various principles related to liquid cooling systems by way of reference to specific examples of heat exchangers and liquid cooling pumping units, including specific arrangements and examples of main bodies and multiple pumps embodying innovative concepts. More particularly, but not exclusively, such innovative principles are described in relation to selected examples of liquid cooling pumping units. Well-known functions or constructions are not described in detail for purposes of succinctness and clarity. Nonetheless, one or more of the disclosed principles can be incorporated in various other embodiments of liquid cooling pumping units to achieve any of a variety of desired outcomes, characteristics, and/or performance criteria. Thus, liquid cooling pumping units having attributes that are different from those specific examples discussed herein can embody one or more of the innovative principles, and can be used in applications not described herein in detail. Accordingly, embodiments of liquid cooling pumping units not described herein in detail also fall within the scope of this disclosure, as will be appreciated by those of ordinary skill in the relevant art following a review of this disclosure. Exemplary embodiments as disclosed herein are directed to liquid cooling systems and liquid cooling multi-pumping units, wherein a heat exchanger is in thermal contact with electric and/or electronic elements, devices and/or systems, transporting heat away therefrom, and then cooling fluid, circulating inside of a cooling loop system incorporating the heat exchanger via fluid conduits, flows over the heat exchanger by a multi-pumping unit, removing heat therefrom. The heated cooling fluid is output from the multi-pumping unit and input to a radiator. Next, the heated cooling fluid flows to and through the radiator, whereby, the radiator may have a plurality of heat fins thereon for increased heat dissipation. Then the cooling fluid flows from the radiator to the multi-pumping unit to once again begin the cooling loop. Although the cooling loop includes a multi-pumping unit, more than one multi-pumping unit may be coupled to the radiator. In this manner, multiple heat generating devices and/or a larger heat generating area may be cooled. Each of the multi-pumping units may be adjacently configured in rows or differently, allowing for design flexibility enabling application-specific configurations. The liquid cooling system may be configured within a chassis or as part of an electric or electronics system that includes heat generating devices to be cooled. The liquid cooling system includes at least one liquid-based cooling loop, and may further comprise one or more fans. The one or more fans may be coupled to the back end of the radiator via a fastener (for example, bolts, screws, an adhesive material, and the like) at structural portions of the radiator, transporting air through the radiator to an air plenum or to an outside of the chassis or electric or electronics system. Those of ordinary skill in the relevant art may readily appreciate that the type and size of fans may be varied, as long as cooling fluid may be circulated through the radiator and air may be transferred through the radiator to an air plenum or to an outside of the chassis or electric or electronics system. In some embodiments, the one or more fans may be high pressure (that is, high airflow) fans. In some embodiments, the one or more fans may have reinforced fan blades. In some embodiments, the design of the fan blades and/or other components (such as bearings, and so on) may be such that noise generated during operation may be minimized. In some embodiments, the fans may be constructed using fasteners (that is, anti-vibration rivets, gaskets, and the like) that may be used to minimized vibration during operation. In an exemplary embodiment, a liquid cooling multi-pumping unit comprising a main body and first and second pumps arranged in series is provided. During operation, cooling fluid is sucked via a cooling fluid inlet into a first fluid chamber and then into a first central chamber opening to a plurality of curved blades of a first impeller assembled in a first pump chamber. From there, the cooling fluid travels and is sucked through a fluid distribution channel into a second fluid chamber and then into a second central chamber opening to a plurality of curved blades of a second impeller assembled in a second pump chamber, before exiting through a fluid outlet. The series arrangement of the first and second pumps increases head pressure, and provides sufficient liquid flow in the case where one liquid cooling pump fails. Additionally, lower energy consumption is achieved due to the lower operating speeds required. FIG.1Ais a schematic perspective first interior view of a liquid cooling multi-pumping unit, according to an exemplary embodiment.FIG.1Bis a schematic perspective second interior view of the liquid cooling multi-pumping unit ofFIG.1A, according to an exemplary embodiment.FIG.2is a schematic exploded view of the liquid cooling multi-pumping unit ofFIG.1A, according to an exemplary embodiment. The liquid cooling system having the liquid cooling multi-pumping unit may be employed to cool at least one of an electric and/or electronic element, device and/or system. Referring toFIGS.1A to2, a liquid cooling multi-pumping unit100comprising a main body150and a plurality of pumps is provided. In some embodiments, the amount of the plurality of pumps is two, comprising a first pump260A having a first motor assembly569A and a second pump260B having a second motor assembly569B. As illustrated inFIGS.3B to7, the main body150comprises a first pump chamber424A and a first fluid chamber426A, in communication therewith via a first central chamber opening422A and opposite therefrom, and a second pump chamber424B and a second fluid chamber426B, in communication therewith via a second central chamber opening422B and opposite therefrom. The first fluid chamber426B is positioned on a parallel plane to the first pump chamber424A and the second fluid chamber426B is positioned on a parallel plane to the second pump chamber424B. The first pump chamber424A is in communication with the second fluid chamber426B. The openings of the first and second pump chambers424A,424B, respectively, are in a same direction, and the openings of the first and second fluid chambers426A,426B, respectively, are in a same direction. The first pump260A is assembled within the first pump chamber424A and corresponds, in dimensions and depth, thereto and the second pump260B is assembled within the second pump chamber424B and corresponds, in dimensions and depth, thereto. The first pump260A having the first motor assembly569A, further comprises a first stator casing566A having a first stator and a first impeller564A having a plurality of curved blades, and the second pump260B having the second motor assembly569B, further comprises a second stator casing566B having a second stator and a second impeller564B also having a plurality of curved blades. A side of the first impeller564A opposite the plurality of curved blades, corresponds, in dimensions and depth, to a side of the first stator casing566A opposite the first motor assembly569A, and is moveably positioned there upon. A side of the second impeller564B opposite the plurality of curved blades, corresponds, in dimensions and depth, to a side of the second stator casing566B opposite the second motor assembly569B, and is moveably positioned there upon. The first and second motor assemblies569A,569B, first and second stator casings566A,566B, and first and second impellers564A,564B are assembled together to form the first and second pumps260A,260B. The main body150, first and second motor assemblies569A,569B, first and second stator casings566A,566B, and first and second impellers564A,564B are parallel assembled, respectively, and integrated on planes which are parallel. In some embodiments, the first and second impellers564A,564B have a shape and a design intended only for one way rotation, a clock-wise rotation. Thereby, the efficiency of the first and second impellers564A,564B is increased when compared to impellers capable of and intended for both clock-wise and counter clock-wise rotation. The liquid cooling multi-pumping unit100further comprises a first pump cover359A and a first pump plate351A, a second pump cover359B and a second pump plate351B, and a plurality of gasket sealants GS. The first and second pump plates351A,351B are secured to the first and second pumps260A,260B, respectively, the first and second pumps260A,260B are sealingly assembled to the main body150, respectively, and the first and second pump covers359A,359B are sealingly assembled to the first and second fluid chambers426A,426B, respectively. The first and second pump plates351A,351B, first and second pumps260A,260B, the main body150, and first and second pump covers359A,359B are secured together and may be sealingly assembled, respectively, by the plurality of gasket sealants GS and bolts (not always shown). However, the embodiments are not limited thereto. Those of ordinary skill in the relevant art may readily appreciate that other convenient sealants and fastening means may also be used, so long as a secure or liquid tight connection can be achieved where required. In some embodiments, the plurality of gasket sealants GS are circular-shaped and tightly fit into indented rimmed step portions of the main body150, respectively. The main body150, first and second motor assemblies569A,569B, first and second stator casings566A,566B, and stators, first and second impellers564A,564B, first and second pump covers359A,359B, and first and second pump plates351A,351B as an example, and not to be limiting, may be made of metal, plastic and/or any combination thereof. Metal minimizes fluid diffusion or evaporation of the fluid. The metal may be provided as a thin layer of metal coating provided on either or on both of the internal or the external sides of plastic parts. Generally, the same metal material is used throughout the cooling loop (the radiator, and so on), such as, copper. The fluid conduits may be flexible and/or rigid. Referring toFIGS.3A to7, and referring toFIGS.1A to2, the main body150of the liquid cooling multi-pumping unit100further comprises a fluid inlet420, a fluid distribution channel120, and a fluid outlet320. The fluid inlet420is in communication with the first fluid chamber426A and positioned on a fourth side of the main body150, the fluid outlet320is in communication with the second pump chamber424B and positioned on a fifth side of the main body150, opposite the fourth side, and the fluid distribution channel120is positioned between the first pump chamber424A and second fluid chamber426A. In some embodiments, the amount of the fluid distribution channel120is one, and the fluid distribution channel120is generally straight and positioned on a plane that is parallel to the first pump chamber424A and second fluid chamber426A; however, the embodiments are not limited thereto. Those of ordinary skill in the relevant art may readily appreciate that there may be more than one fluid distribution channel120and the fluid distribution channel120may not be generally straight and/or positioned on a plane that is parallel to the first pump chamber424A and second fluid chamber426A. As long as the fluid distribution channel120is in communication with both the first pump chamber424A and second fluid chamber426A and cooling fluid is able to freely flow therethrough. In some embodiments, the liquid cooling multi-pumping unit100further comprises a secondary opening324. The secondary opening324is in communication with the first pump chamber424A and positioned on the fourth side of the main body150, diagonal to the fluid inlet420. Those of ordinary skill in the relevant art may readily appreciate that the secondary opening324provides an additional feature for fluid distribution of the first pump chamber424A, and may be incorporated in various other embodiments of liquid cooling pumping units to achieve any of a variety of desired outcomes, characteristics, and/or performance criteria. During operation of the liquid cooling multi-pumping unit100, the first and second motor assemblies569A,569B of the first and second pumps260A,260B, respectively, rotate the first and second impellers564A,564B in series. Cooling fluid is sucked via the cooling fluid inlet420into the first fluid chamber426A and then into the first central chamber opening422A to the plurality of curved blades of the first impeller564A assembled in the first pump chamber424A. From there, the cooling fluid travels and is sucked through the fluid distribution channel120into the second fluid chamber426B and then into the second central chamber opening422B to the plurality of curved blades of the second impeller564B assembled in the second pump chamber424B, before exiting outward through the fluid outlet320. The first and second fluid chambers426A,426B communicate directly with the first and second pump chambers424A,424B, respectively, ensuring lubrication of the liquid cooling multi-pumping unit100and heat transfer, avoiding damage and failure thereof. In some embodiments, the amount of the plurality of pumps is two, comprising the first and second pumps260A,260B, and the first and second pumps260A,260B are staggeredly positioned to allow for gravity to assist in increasing cooling fluid flow from the first and second fluid chambers426A,426B to the first and second pump chambers424A,424B; however, the embodiments are not limited thereto. In alternative embodiments, the amount of the plurality of pumps is more than two, and the plurality of pumps may not be staggeredly positioned. As long as cooling fluid may be sucked via a cooling fluid inlet into a fluid chamber and then into a central chamber opening to a plurality of curved blades of an impeller, and then travel and be sucked through a fluid distribution channel into another fluid chamber and then into another central chamber opening to another plurality of curved blades of an another impeller, and so on, before eventually exiting outward through a fluid outlet and the fluid chambers communicate directly with the pump chambers, respectively, ensuring lubrication and heat transfer of the liquid cooling multi-pumping unit, avoiding damage and failure thereof. FIG.8Ais a schematic perspective first interior view of an alternative liquid cooling multi-pumping unit, according to an exemplary embodiment.FIG.8Bis a schematic perspective second interior view of the alternative liquid cooling multi-pumping unit ofFIG.8A, according to an exemplary embodiment.FIG.9is a schematic exploded view of the alternative liquid cooling multi-pumping unit ofFIG.8A, according to an exemplary embodiment. Referring toFIGS.8A to9, a liquid cooling multi-pumping unit800comprising a main body850and a plurality of pumps is provided. In some embodiments, the amount of the plurality of pumps is three, comprising a first pump860A having a first motor assembly569A, a third pump860C having a third motor assembly569C, and a second pump260B having a second motor assembly569B. The main body850comprises a first pump chamber424A and a first fluid chamber826A, in communication therewith via a first central chamber opening422A and opposite therefrom, a third pump chamber424C and a third fluid chamber826C, in communication therewith via a third central chamber opening422C and opposite therefrom, and a second pump chamber424B and a second fluid chamber826B, in communication therewith via a second central chamber opening422B and opposite therefrom. The first fluid chamber826B is positioned on a parallel plane to the first pump chamber424A, the third fluid chamber826C is positioned on a parallel plane to the third pump chamber424C, and the second fluid chamber826B is positioned on a parallel plane to the second pump chamber424B. The first pump chamber424A is in communication with the third fluid chamber826C, and the third pump chamber424C is in communication with the second fluid chamber826B. The openings of the first and second pump chambers424A,424B, respectively, are in a same direction, and opposite the opening of the third pump chamber424C, and the openings of the first and second fluid chambers826A,826B, respectively, are in a same direction, opposite the opening of the third fluid chamber826C. The first pump260A is assembled within the first pump chamber424A and corresponds, in dimensions and depth, thereto, the third pump260C is assembled within the third pump chamber424C and corresponds, in dimensions and depth, thereto, and the second pump260B is assembled within the second pump chamber424B and corresponds, in dimensions and depth, thereto. The first pump260A having the first motor assembly569A, further comprises a first stator casing566A having a first stator and a first impeller564A having a plurality of curved blades. The third pump260C having the third motor assembly569C, further comprises a third stator casing566C having a third stator and a third impeller564C having a plurality of curved blades. The second pump260B having the second motor assembly569B, further comprises a second stator casing566B having a second stator and a second impeller564B also having a plurality of curved blades. A side of the first impeller564A opposite the plurality of curved blades, corresponds, in dimensions and depth, to a side of the first stator casing566A opposite the first motor assembly569A, and is moveably positioned there upon. A side of the third impeller564C opposite the plurality of curved blades, corresponds, in dimensions and depth, to a side of the third stator casing566C opposite the third motor assembly569C, and is moveably positioned there upon. A side of the second impeller564B opposite the plurality of curved blades, corresponds, in dimensions and depth, to a side of the second stator casing566B opposite the second motor assembly569B, and is moveably positioned there upon. The first, third and second motor assemblies569A,569C,569B, first, third and second stator casings566A,566C,566B, and first, third and second impellers564A,564C,564B are assembled together to form the first, third and second pumps260A,260C,260B. The main body850, first, third and second motor assemblies569A,569C,569B, first, third and second stator casings566A,566C,566B, and first, third and second impellers564A,564C,564B are parallel assembled, respectively, and integrated on planes which are parallel. In some embodiments, the first, third and second impellers564A,564C,564B have a shape and a design intended only for one way rotation, a clock-wise rotation. Thereby, the efficiency of the first, second and third impellers564A,564C,564B is increased when compared to impellers capable of and intended for both clock-wise and counter clock-wise rotation. The liquid cooling multi-pumping unit800further comprises a first pump plate351A, a third pump cover359C and a third pump plate351C, and a second pump cover359B and a second pump plate351B, and a plurality of gasket sealants GS (not shown). The first, third and second pump plates351A,351C,351B are secured to the first, third and second pumps260A,260C,260B, respectively, the first, third and second pumps260A,260C,260B are sealingly assembled to the main body850, respectively, and the third and second pump covers359C,359B are sealingly assembled to the third and second fluid chambers826C,826B, respectively. The first, third and second pump plates351A,351C,351B, first, third and second pumps260A,260C,260B the main body850, and third and second pump covers359C,359B are secured together and may be sealingly assembled, respectively, by the plurality of gasket sealants GS and bolts (not always shown). However, the embodiments are not limited thereto. Those of ordinary skill in the relevant art may readily appreciate that other convenient sealants and fastening means may also be used, so long as a secure or liquid tight connection can be achieved where required. In some embodiments, the plurality of gasket sealants GS are circular-shaped and tightly fit into indented rimmed step portions of the main body150, respectively. The main body850, first, third and second motor assemblies569A,569C,569B, first, third and second stator casings566A,566C,566B, and stators, first, third and second impellers564A,564C,564B, third and second pump covers359C,359B, and first, third and second pump plates351A,351C,351B as an example, and not to be limiting, may be made of metal, plastic and/or any combination thereof. FIG.10Ais a schematic exploded view of the alternative liquid cooling multi-pumping unit ofFIG.9with line E-E, according to an exemplary embodiment.FIG.10Bis a schematic cross-sectional view of the alternative liquid cooling multi-pumping unit along line E-E ofFIG.10A, according to an exemplary embodiment.FIG.11Ais schematic perspective first view of the main body of the alternative liquid cooling multi-pumping unit ofFIG.8Awith line F-F, according to an exemplary embodiment.FIG.11Bis schematic cross-sectional view of the main body along line F-F ofFIG.11A, according to an exemplary embodiment.FIG.12Ais schematic perspective first view of the main body of the alternative liquid cooling multi-pumping unit ofFIG.8Awith line G-G, according to an exemplary embodiment.FIG.12Bis schematic cross-sectional view of the main body along line G-G ofFIG.12A, according to an exemplary embodiment.FIG.13Ais schematic perspective first view of the alternative liquid cooling multi-pumping unit ofFIG.8Awith line H-H and line I-I, according to an exemplary embodiment.FIG.13Bis schematic cross-sectional view of the alternative liquid cooling multi-pumping unit ofFIG.8Aalong line H-H ofFIG.13A, according to an exemplary embodiment.FIG.13Cis schematic cross-sectional view of the alternative liquid cooling multi-pumping unit ofFIG.8Aalong line I-I ofFIG.13A, according to an exemplary embodiment.FIG.14Ais schematic perspective first view of the alternative liquid cooling multi-pumping unit ofFIG.8Awith line J-J and line K-K, according to an exemplary embodiment.FIG.14Bis schematic cross-sectional view of the alternative liquid cooling multi-pumping unit ofFIG.8Aalong line J-J ofFIG.14A, according to an exemplary embodiment.FIG.14Cis schematic cross-sectional view of the alternative liquid cooling multi-pumping unit ofFIG.8Aalong line K-K ofFIG.14A, according to an exemplary embodiment.FIG.15is a schematic perspective third interior view of the main body of the alternative liquid cooling multi-pumping unit ofFIG.8A, according to an exemplary embodiment. Referring toFIGS.10A to15, and referring toFIGS.8A to9, the main body850of the liquid cooling multi-pumping unit800further comprises a first fluid distribution channel120A, a second fluid distribution channel120C, and a fluid outlet320. In some embodiments, a fluid tank may be added to the liquid cooling multi-pumping unit800, whereby cooling fluid may be stored. The fluid tank (not shown) is sealingly assembled to the first fluid chamber826A and positioned thereupon. The fluid tank feeds directly into the liquid cooling multi-pumping unit800for even greater flow, ensuring lubrication and heat transfer and avoiding damage and failure thereof. A volume of cooling fluid may be retained in the fluid tank during operation of the liquid cooling system. In some embodiments, a visible portion of the cooling fluid in the fluid tank via a transparent material may allow users to visually observe an amount of cooling fluid in the cooling loop, and determine when additional cooling fluid may need to be added. Via the fluid tank, fluid loss over time due to permeation may be mitigated, and air bubbles may gradually be replaced during fluid circulation, increasing cooling loop efficiency of the liquid cooling system. The fluid tank (not shown) is in communication with the first fluid chamber826A and positioned thereupon, the fluid outlet320is in communication with the second pump chamber424B and positioned on a fifth side of the main body850, opposite the fourth side, the first fluid distribution channel120A is positioned between the first pump chamber424A and third fluid chamber826C, and the second fluid distribution channel120C is positioned between the third pump chamber424C and second fluid chamber826B. In some embodiments, the amount of the first and second fluid distribution channels120A,120B, is one each, and the first and second fluid distribution channels120A,120B are generally straight and positioned on a plane that is parallel to the first pump chamber424A and third fluid chamber826C and third pump chamber424C and second fluid chamber826B, respectively; however, the embodiments are not limited thereto. In some embodiments, the liquid cooling multi-pumping unit800further comprises a secondary opening520. The secondary opening520is in communication with the first pump chamber424A and positioned on a fourth side of the main body150. Those of ordinary skill in the relevant art may readily appreciate that the secondary opening520provides an additional feature for fluid distribution of the first pump chamber424A, and may be incorporated in various other embodiments of liquid cooling pumping units to achieve any of a variety of desired outcomes, characteristics, and/or performance criteria. During operation of the liquid cooling multi-pumping unit800, the first, third and second motor assemblies569A,569C,569B of the first, third and second pumps260A,260C,260B, respectively, rotate the first, third and second impellers564A,564C,564B in series. Cooling fluid is sucked from the first fluid chamber826A, sealingly assembled to the fluid tank, and then into the first central chamber opening422A to the plurality of curved blades of the first impeller564A assembled in the first pump chamber424A. From there, the cooling fluid travels and is sucked through the first fluid distribution channel120A into the third fluid chamber826C and then into the third central chamber opening422C to the plurality of curved blades of the third impeller564C assembled in the third pump chamber424C. Next, the cooling fluid travels and is sucked through the second fluid distribution channel120B into the second fluid chamber826B and then into the second central chamber opening422B to the plurality of curved blades of the second impeller564B assembled in the second pump chamber424B, before exiting outward through the fluid outlet320. The first, third and second fluid chambers826A,826C,826B communicate directly with the first, third and second pump chambers424A,424C,424B, respectively, ensuring lubrication of the liquid cooling multi-pumping unit800and heat transfer, avoiding damage and failure thereof. In some embodiments, the main body of the liquid cooling multi-pumping unit further comprises a fluid inlet (not shown) and a first pump cover (not shown), and not a fluid tank. The fluid inlet is in communication with a first fluid chamber (not shown) and positioned on a fourth side of the main body (not shown), diagonal to the secondary opening520. The first pump cover is sealingly assembled to the first fluid chamber. During operation of the liquid cooling multi-pumping unit, the first, third and second motor assemblies569A,569C,569B of the first, third and second pumps260A,260C,260B, respectively, rotate the first, third and second impellers564A,564C,564B. Cooling fluid is sucked via the cooling fluid inlet into the first fluid chamber and then into the first central chamber opening422A to the plurality of curved blades of the first impeller564A assembled in the first pump chamber424A. From there, the cooling fluid travels and is sucked through the first fluid distribution channel120A into the third fluid chamber826C and then into the third central chamber opening422C to the plurality of curved blades of the third impeller564C assembled in the third pump chamber424C. Next, the cooling fluid travels and is sucked through the second fluid distribution channel120B into the second fluid chamber826B and then into the second central chamber opening422B to the plurality of curved blades of the second impeller564B assembled in the second pump chamber424B, before exiting outward through the fluid outlet320. The first, third and second fluid chambers (not shown),826A,826C,826B communicate directly with the first, third and second pump chambers424A,424C,424B, respectively, ensuring lubrication of the liquid cooling multi-pumping unit800and heat transfer, avoiding damage and failure thereof. In some embodiments, the liquid cooling system is configured to cool each heat generating device included within a chassis or electric or electronics system. In alternative embodiments, the liquid cooling system is configured to cool only selective heat generating devices, or only a single heat generating device, while other heat generating devices are left to be cooled by other or complimentary means. The cooling fluid of the liquid cooling system may be any type of cooling fluid such as water, water with additives such as anti-fungicide, water with additives for improving heat conducting or other special compositions of cooling fluids such as electrically non-conductive liquids or liquids with lubricant additives or anti-corrosive additives. Control of the liquid cooling multi-pumping units, driven by an AC or DC electrical motor, preferably takes place by means of an operative system or like means or the electric and/or electronics system itself, wherein the electric and/or electronics system comprises a means for measuring load and/or temperature of one or more processors. Using the measurement performed by the operative system or a like system eliminates the need for special means for operating the liquid cooling multi-pumping units. Communication between the operative system or a like system and a processor for operating the liquid cooling multi-pumping units may take place along already established communication links in the system such as a USB-link. Thereby, a real-time communication between the liquid cooling system and liquid cooling multi-pumping units may be provided without any special means for establishing the communication. Further control strategies utilizing the operative system or a like system may involve balancing the rotational speed of each of the liquid cooling multi-pumping units as a function of the cooling capacity needed. If a lower cooling capacity is needed, the rotational speed of each of the liquid cooling multi-pumping units may be individually adjusted or limited, thereby limiting the noise generated by the motor driving the liquid cooling multi-pumping units and wear and tear thereof. In the embodiments, liquid cooling systems and liquid cooling multi-pumping units, wherein a heat exchanger is in thermal contact with electric and/or electronic elements, devices and/or systems, transporting heat away therefrom, and then cooling fluid, circulating inside of a cooling loop system incorporating the heat exchanger via fluid conduits, flows over the heat exchanger by a multi-pumping unit, removing heat therefrom. In the embodiments, a liquid cooling multi-pumping unit100comprises a main body150and first and second pumps260A,260B. During operation of the liquid cooling multi-pumping unit100, first and second motor assemblies569A,569B of the first and second pumps260A,260B, respectively, rotate first and second impellers564A,564B. Cooling fluid is sucked via a cooling fluid inlet420into a first fluid chamber426A and then into a first central chamber opening422A to the plurality of curved blades of the first impeller564A assembled in the first pump chamber424A. From there, the cooling fluid travels and is sucked through a fluid distribution channel120into a second fluid chamber426B and then into a second central chamber opening422B to a plurality of curved blades of the second impeller564B, before exiting outward through a fluid outlet320. The first and second fluid chambers426A,426B communicate directly with the first and second pump chambers424A,424B, respectively, ensuring lubrication of the liquid cooling multi-pumping unit100and heat transfer, avoiding damage and failure thereof. Also, air bubbles are decreased as they are gradually replaced during fluid circulation, leading to greater efficiency of the liquid cooling system. The series arrangement of the plurality of pumps assembled in one main body150, increases head pressure, overcoming long conduit lengths with high friction losses, and provides sufficient liquid flow in the case where one of the plurality of pumps fails, mitigating damage to the electric and/or electronic elements, devices and/or systems due to overheating, while minimizing costs, total installation time, risks for leakage, loss of parts, and total area requirements when compared to separate pump assemblies. Additionally, lower energy consumption is achieved due to the lower operating speeds required, thereby reducing wear and tear, increasing reliability and operating lifespan. The presently disclosed inventive concepts are not intended to be limited to the embodiments shown herein, but are to be accorded their full scope consistent with the principles underlying the disclosed concepts herein. Directions and references to an element, such as “up,” “down,”, “upper,” “lower,” “horizontal,” “vertical,” “left,” “right,” and the like, do not imply absolute relationships, positions, and/or orientations. Terms of an element, such as “first” and “second” are not literal, but, distinguishing terms. As used herein, terms “comprises” or “comprising” encompass the notions of “including” and “having” and specify the presence of elements, operations, and/or groups or combinations thereof and do not imply preclusion of the presence or addition of one or more other elements, operations and/or groups or combinations thereof. Sequence of operations do not imply absoluteness unless specifically so stated. Reference to an element in the singular, such as by use of the article “a” or “an”, is not intended to mean “one and only one” unless specifically so stated, but rather “one or more”. As used herein, “and/or” means “and” or “or”, as well as “and” and “or.” As used herein, ranges and subranges mean all ranges including whole and/or fractional values therein and language which defines or modifies ranges and subranges, such as “at least,” “greater than,” “less than,” “no more than,” and the like, mean subranges and/or an upper or lower limit. All structural and functional equivalents to the elements of the various embodiments described throughout the disclosure that are known or later come to be known to those of ordinary skill in the relevant art are intended to be encompassed by the features described and claimed herein. Moreover, nothing disclosed herein is intended to be dedicated to the public regardless of whether such disclosure may ultimately explicitly be recited in the claims. No element or concept disclosed herein or hereafter presented shall be construed under the provisions of 35 USC 112f unless the element or concept is expressly recited using the phrase “means for” or “step for”. In view of the many possible embodiments to which the disclosed principles can be applied, we reserve the right to claim any and all combinations of features and acts described herein, including the right to claim all that comes within the scope and spirit of the foregoing description, as well as the combinations recited, literally and equivalently, in the following claims and any claims presented anytime throughout prosecution of this application or any application claiming benefit of or priority from this application. | 36,008 |
11859620 | DETAILED DESCRIPTION The described techniques enable a sump pump system to detect and utilize motion of water in sump basins when implementing control of sump pumps. A sump pump system may detect a malfunctioning level sensor that is used by the pump to detect high-water and low-water marks at which the sump pump activates and deactivates, respectively. By contrast, most sump pump systems do not utilize sensors capable of detecting a malfunction of a typical float sensor in a sump pump. As a result, float sensors represent a single point of failure in many sump pump systems. If the float sensor gets “stuck” while disengaged or deactivated, for example, the sump pump may fail to detect a high-water mark in the sump basin, resulting in the sump pump failing to activate or engage when one would typically expect, resulting in the sump basin overflowing (and potentially resulting in flooding a basement in which the sump pump is installed, potentially leading to costly water damage to walls, floors, furniture, electronics, etc.). Alternatively, if the float sensor becomes “stuck” after activating or engaging, the sump pump may continuously run. While this may prevent an overflow of the sump basin in the short-term, the sump pump motor may quickly burn out if this condition is not corrected. And at that point, the sump basin is obviously at risk of overflowing. At a high level, a system implementing the described techniques relies on sensor(s) configured to detect motion (e.g., acceleration), which can be analyzed to calculate water rise rates. These sensors may be accelerometers, gyroscopes, inertial measurement units (IMUs), or force acceleration sensors. Generally speaking, the sensor(s) may be disposed on or within the water, and may be responsive to the water such that, when the water level rises or drops, the sensor(s) responsively and proportionally drop. Accordingly, one may use a technique akin to dead-reckoning, in which relative changes in the water level are detected for the purpose of approximating the water level in the sump basin. Alternatively or additionally, the data from these sensors that detect motion or acceleration may be analyzed, for example, to identify acceleration or vibration patterns that correspond to certain water levels. Generally speaking, sump pumps are used in areas where lower level (e.g., ground level or below ground level) flooding may be a problem and/or is a recurring problem. A typical sump pump system comprises a submersible impeller type pump disposed in a sump basin. The sump basin is a holding cavity formed by digging a recess into the floor of a lower level of a property, such as a ground level or below ground level (e.g., a basement) of a property (e.g., a home, an office, or any other building or structure). The sump basin acts both to house the sump pump and to collect accumulated water. Water may accumulate in the sump basin when excessive amounts of rain, snow melt or ground water saturate the soil adjacent to the property and/or property lower level floor. Water may also enter the sump basin via drainage or inlet pipes that have been placed into the ground to divert any excess water into the sump basin before the water can begin to permeate foundation walls, floors, etc., or water may enter the sump basin through porous or cracked walls, floors, etc. Generally speaking, the sump basin is installed in a basement such that the top of the sump basin is lower than the lowest floor level in the basement. Accordingly, when the water table underneath and around the property rises, water flows into the sump basin to then be pumped away from the area, thereby avoiding the water table rising above the basement floor (which can result in leaks and flooding due to the typically porous nature of basement walls). In any event, after the sump pump basin fills and the water reaches a high-water mark, the sump pumping action of a sump pump removes the accumulated water in the sump basin via one or more outlet or discharge pipes that carries the pumped water to an area away from the property (such as into a municipal storm drain, a dry well, a water retention area, etc.), thereby avoiding potential flooding inside the building. Ideally, the sump basin fills and empties at a rate fast enough to prevent the water table from rising above the basement floor. Turning to the figures,FIG.1illustrates an example sump pump system100that can be used to remove water accumulated in a lower level of a property150(e.g., a home, an office, or any other building or structure). As shown inFIG.1, the sump pump system100may be part of an example sump pump network system160. The example sump pump system100includes a sump pump102located in a sump basin104. The sump pump102and a sump pump motor103are enclosed in a housing105. The sump pump motor103may also be referred to herein as the motor103, and the sump pump102may also be referred to herein as the pump102. While the sump pump102inFIG.1is shown as a submersible type sump pump (e.g., where the motor103and the sump pump102are mounted inside the basin104), the sump pump102, in general, may be any type of sump pump, such as a pedestal type sump pump that is mounted above or outside of the basin104. As shown inFIG.1, the sump basin104is a well-like cavity or hole formed through a floor106of the property150. The example sump pump system100also includes a water inlet pipe108terminating at the sump basin104, and a discharge pipe112(also referred to herein as an outlet pipe) connected to the sump pump102to carry water out of the sump basin104. An impeller117of the sump pump102draws in water through an inlet118, and pumps the water up the discharge pipe112to an outlet110. In the illustrated example, the discharge pipe112extends upward from the sump pump102and then out of the building. However, other arrangements may be used. The discharge pipe112is outfitted with a check valve114. The check valve114allows water to flow up through the discharge pipe112, but does not allow the water in the discharge pipe112to flow back into the sump basin104when the sump pump102is off. A weep hole116in the discharge pipe112allows excess air to escape from the pipe, preventing air binding, also known as air locking. The opening of the sump basin104may be protected by a cover to prevent objects from falling into the basin, and to keep noxious gases (e.g., radon) from entering the property150. In the case of a sealed sump pump basin104, an air vent120may be needed to relieve excess air pressure in the basin. Generally, the sump pump102may be electrically powered and hardwired into the electrical system of the property150. Additionally and/or alternatively, the sump pump102may be powered by a battery or other independent power source (not shown for clarity of illustration). The operation of the sump pump102is controlled by a pump activation switch122in response to a water level in the basin104. For example, the sump activation switch122may activate the sump pump102when a water level in the sump basin104reaches a preset level. The preset level is determined by the placement of the sump pump activation switch122. In illustrated example ofFIG.1, the sump pump activation switch122is shown in the form of a float switch, although other technologies such as liquid level sensors may also be used. As shown inFIG.1, the sump pump activation switch122is connected to the motor103of the sump pump102. In some embodiments, the sump pump activation switch122is a level sensor, such as a float switch. When the rising water in the basin104lifts a float of the sump pump activation switch122to a high water level or mark142, the float rises a rod, which activates and/or energizes the motor103to begin pumping water. In other embodiments, the sump pump activation switch122may be a mercury tilt switch. The rising water in the basin104lifts and tilts a float of the sump pump activation switch122and, when the float reaches the high water level or mark142, a sufficient tilt causes a small amount of liquid mercury to slide towards open electrodes to close an electrical circuit, which activates and/or energizes the motor103. As water is pumped out of the sump basin104, the water level drops to a low or initial water level or mark140. The falling water level carries the sump pump activation switch122back to an initial or low water level or mark140, at which the sump pump activation switch122is deactivated. Thus, the motor103de-energizes or shuts off at the initial or low water level or mark140. When the sump pump102and/or the motor103fails, flooding may ensue as water fills up the sump basin104and overflows above the floor level106of the property150. The amount of water that overflows can vary from a few inches to several feet, which may result in substantial water damage to the structures of property150, as well as personal belongings. Accordingly, the ability to maintain sump pumps, and to detect and resolve impending sump pump failures before they occur is of great importance to the property owners and the building and property insuring parties. The sump pump102may fail because of a failure in the motor103, which renders the entire sump pump102inoperable. The failure in the motor103may be caused by various factors such as age, fatigue, overheating, poor maintenance, etc. Aside from the failure of the motor103, the sump pump102may fail because of other soft mechanical failures of the components of the sump pump system100. For example, sediment or debris build-up may cause the motor impeller117and/or another sump pump component to stall, thus, rendering the sump pump102unable to pump water even though the motor103is operational. Additionally or alternatively, the sump pump activation switch122may fail to engage in response to the rising water level and subsequently fail to actuate the motor103. Additionally or alternatively, the check valve114may malfunction, and back flow of the discharged water into the sump pump basin104may equal or exceed the amount of water being pumped out by the sump pump102. Additionally or alternatively, there might be a blockage in the discharge pipe112, preventing water flow to the outlet110. Additionally and/or alternatively, an air pocket may cause the sump pump102to run dry. As such, mechanisms to maintain the sump pump and/or detect impending sump pump failures may include monitoring for the occurrence of such failures. Generally, soft mechanical failures may be identified or detected indirectly. In an embodiment, soft mechanical failures may be detected by using properly placed sensors, such as sensors124,126,128,130,132, and134ofFIG.1, able to detect issues associated with failures of the sump pump system100. The sensors124,126,128,130,132, and134may be configured to communicate with a sump pump controller138, which may be configured to communicate with other components of the sump pump system100, or components of a sump pump network system160, described below. The sump pump controller138may also be referred to in this specification as the controller138. The controller138is configured to receive and analyze data from the sensors124,126,128,130,132, and134using built-in computing capabilities or in cooperation with other computing devices of the sump pump network system160to identify specific failures of the sump pump system100, and in some instances remediate the issues, and/or generate an alert regarding the detected failures. Interactions between the sensors124,126,128,130,132, and134, the controller138, and the components of the system160are discussed below in more detail. Example remedies to soft mechanical failures (such as a blockage or stuck impeller) may include activating a shaker, altering a speed of a pump impeller, reversing a direction of spin of the pump impeller, gradually accelerating the impeller, or alternating gradual accelerations of the impeller with gradual decelerations. If desired, the sump pump system100may include a variable speed motor or controller for the sump pump102. In an embodiment, the sump pump motor103is a variable speed motor; in an embodiment, it is not. Similarly, in an embodiment, the sump pump controller138is a variable speed controller; in an embodiment, it is not. For example, in embodiments in which the pump impeller is reversed or adjusted in speed, a variable speed motor or controller may be included for controlling the pump and/or pump impeller in such a manner. In some embodiments, a variable speed motor or controller may detect a blocked impeller by sensing that the position of the rotor or impeller is not changing even though power is applied. To dislodge the mechanical blockage, the controller may spin the motor in reverse direction or alternate gradual acceleration with gradual deceleration in opposite directions. Gradual acceleration upon motor activation and gradual deceleration upon motor disengagement may reduce initial step level force impact of the pump turning on or off, which may benefit the system by lengthening the serviceable life of the motor and the marginal pipe infrastructure. As shown inFIG.1, the sump pump system100may include a variety of mechanical, electrical, optical, or any other suitable sensors124,126,128,130,132, and134disposed within, at, throughout, embedded within, or in mechanical connection to the sump basin104, the sump pump housing105, the inlet pipe108, or the discharge pipe112. Additionally, the sensors124,126,128,130,132, and134may be disposed on, at, or within the motor103, the sump pump102, or any other components of the sump pump system100. The one or more sensors124,126,128,130,132, and134may transduce one or more of: light, sound, acceleration, translational or rotational movement, strain, pressure, presence of liquid, or other suitable signals into electrical signals. The sensors124,126,128,130,132, and134may be acoustic, photonic, micro-electro-mechanical systems (MEMS) sensors, or any other suitable type of sensor. The sensor124may be a water level sensor, placed a short distance (e.g., 10, 20, 30, or 50 mm above) above the high water level or mark142in the sump basin104. In operation, if the water level sensor124does not detect water, then the water level in the basin104is deemed adequate. In other words, the sump pump102is either working properly to constantly pump water out of the basin104, or the water level is not yet high enough to activate the sump pump102. In any event, it can be assumed that the sump pump102is not experiencing any soft mechanical failure. On the other hand, if the water level sensor124detects water, then water may be on the rise in the basin104, and may overflow the sump basin104. In other words, a dangerous level of water is present in the sump basin104, which may be due to either a failure of the sump pump102, a failure to activate the sump pump102, and/or a soft mechanical failure that has rendered the sump pump102unable to pump out adequate amount of water. The sensor124may include magnetic or mechanical floats, pressure sensors, optical, ultrasonic, radar, capacitance, electroconductive and/or electrostatic sensors. The sensor124may be a continuous or a point level switch. A continuous liquid level switch or sensor provides a continuous feedback showing liquid level within a specified range. A point level switch detects whether a liquid level is above or below a certain sensing point. In embodiments, the sensor124may be a reed switch, or a mercury switch, a conductive level sensor, and/or any type of a suitable switch that changes a state from inactive to active as liquid level reaches a certain level relative to the switch position. In some embodiments, the sensor124may be a continuous liquid level switch providing a measurement of the height of the water level inside the sump basin104. The controller138can use these measurements, taken at time intervals (e.g., at 1, 5, or 10 second intervals), to estimate the volume of water being pumped, deposited, or backflowing in the sump basin104. For example, knowing the sump pump basin104dimensions, such as a diameter (if the basin is a cylinder), or the bottom diameter, a top diameter, and a height (if the basin is a graduated cylinder) or width and length measurements (if the basin is a rectangular prism), and water level height over time will yield a measurement of water volume increase or decrease over time. The controller138may utilize any suitable volume formula to calculate changes in volume (e.g., volume=πr2h for a cylinder). For example, if the basin104is a cylinder basin, the controller138may be programmed to assume a known radius (e.g., 8 inches). The controller138may identify the distance from the bottom of the basin104to the water level (e.g., based on a water level sensor). This distance may be used for the “h” variable in the volume formula, enabling the controller138to calculate volume at any given time it can detect the “height” of the water level. In some instances, the controller138may be configured to account for displacement that occurs due to the pump itself being submerged within water. For example, a known volume of the pump (which is generally static) may be subtracted from a formula that assumes a perfect cylinder. Additionally, knowing the sump basin104capacity (e.g., in gallons) and water volume increase over time, the controller138may calculate an estimate of when the sump pump basin may overflow. For example, in a sump basin with a capacity of 26 gallons and an initial water volume of 0 gallons, the controller138may calculate that a water volume increase at 0.1 gallons per second would result in a sump basin overflow in 260 seconds or 4 minutes and 20 seconds. The sump pump controller138may generate an alert, communicating an approximated time of the critical event of the sump basin104overflowing, or communicating the time (e.g., in minutes or seconds) remaining until the estimated overflow. Additionally, functions of the sump pump controller138ofFIG.1may be used together with the water level sensor124to detect certain soft mechanical failures, such as when the sump motor103becomes stuck and runs indefinitely. This may be due to a mechanical malfunction of the sump pump activation switch122or another activation element. In this scenario, when the water level sensor124does not detect water, the sump pump controller138may analyze the electrical load waveform of the motor103to determine how long the motor103is running. In general, if the sump pump102is working properly, then the motor103will automatically shut off when the falling water carries the sump pump activation switch122back to the initial or low level or mark140. However, if the sump pump activation switch122jams or otherwise fails, then the sump motor103may become stuck and continue to run for a long time. Thus, if the water level sensor124is not detecting water but the sump pump controller138is detecting a long period of run time on the part of the sump motor103(e.g., if the run time of the sump motor103exceeds a certain length of time), then the sump pump102may be deemed to be experiencing a soft mechanical failure. The sensor126may be a force sensor or transducer, configured to detect a water rise or fall rate in the sump basin104, or water disturbance (e.g., splashing) in the sump basin104. The sensor126may be, for example a piezoelectric crystal, a pneumatic, a hydraulic, an inductive, a capacitive, a magnetostrictive, or a strain gage load cell, or an accelerometer, or any other suitable sensor capable of transducing a force into an electrical signal. In an embodiment, an accelerometer of the sensor126measures inertial acceleration, from which water rise rate in the sump basin104can be determined. The sensor126may be placed above the initial or low water level or mark140and, for example, below the high water level or mark142in the sump basin104. Alternatively, the sensor126may be placed above the high water level or mark142in the sump basin104. In operation, a rising water level in the sump basin104would exert a load on the sensor126, from which a rise or fall rate of the water level in the sump basin104can be determined. If the sensor126does not detect any force exerted on it, there may be no water at the level of the sensor126. Alternatively, the water level at the sensor126in the sump basin104may be constant. In other words, water rise rate, or inflow rate may equal the rate of water pumped out through the discharge pipe112by the sump pump102. In an alternative scenario, the sensor126may sense an upward force of the rising water level when the sump pump102is operational, and an inlet sensor130(described later in more detail) detects water entering the sump basin104from the inlet108, indicating that the inflow rate is greater than the rate of water pumped out through the discharge pipe112by the sump pump102. In yet another scenario, the sensor126may sense rising water, the inlet sensor130may not detect any water inflow into the sump basin104, and at the same time the sump pump102may be engaged, the scenario indicating that the water level is rising due to additional inflow (e.g., back flow from the discharge pipe, or the vent120, or through the floor106opening of an uncovered sump basin). The sump pump system100may include a vibration sensor128, placed in direct or indirect contact with the sump pump102or pump motor103.FIG.1shows the vibration sensor128located on the sump pump housing105. In some embodiments, the vibration sensor128may be placed on the motor103, the sump pump102, the discharge pipe112, or on any component within the sump basin104. The vibration sensor128may be a ceramic piezoelectric sensor, or any suitable sensor capable of detecting vibration or acceleration of motion of a structure. In operation, by measuring the inertial vibration, the vibration sensor128monitors the condition, predicts or monitors wear, fatigue, and failure of the sump pump system100components, for example sump pump102, the motor103, the housing105, or the discharge pipe112and their respective constituents by measuring their vibrational signatures and, thus, determining the kinetic energy and forces acting upon the components. The inertial vibration signatures, when compared to a standard or when monitored for changes over time, may predict wear, impending failures, and immediate failures, such as a loose bearing, a stuck motor103, an overloaded motor103, a dry motor103, a damaged discharge pipe112, a faulty check valve114, a broken hermetic seal of the housing105, a stuck impeller117, debris on the impeller117or inside the sump pump102, etc. The inlet sensor130and the outlet sensor132of the sump pump system100may be water level sensors, analogous to the water level sensor124. In operation, the sensor130detects presence of water in the inlet pipe108, or inflow. If the sensor130does not detect water in the inlet pipe108, there is no water flowing into the sump basin104via the inlet pipe108.FIG.1shows the sensor130placed on the surface of the inlet pipe108. In some embodiments, the sensor130may be embedded within the water inlet pipe108, or placed at the junction of the inlet pipe108and the wall of the sump basin104. In some embodiments, the sensor130may include a hinged flap or a hinged lid (not shown) covering the opening of the inlet pipe108. When the pressure of the inflowing water lifts the flap, the displacement of the flap triggers a signal that water is flowing into the sump basin104via the inlet pipe108. The flap displacement may be registered, for example, in the hinge mechanism (e.g., by breaking or establishing an electrical connection by the movement of the hinge parts), or as a disconnected electrical or a magnetic connection between the flap and the inlet pipe108or the wall of the sump basin104. Alternatively, the sensor130may be a sensor configured to detect deflection of the flap (e.g., with a laser-based or an acoustic technology). The outlet sensor132detects presence of water in the discharge pipe112before the check valve114, monitoring whether the check valve114is working properly, i.e., preventing the back flow of water into the sump basin104when the motor103is disengaged and the sump pump102is not operating.FIG.1shows the sensor132placed inside the discharge pipe112before, or closer to the sump pump102than the check valve114. In operation, if the sensor132does not detect water when the sump pump102is deactivated, then the check valve114may be assumed to be functioning properly. The sensor134may be a water level sensor, placed at a level or mark136in the sump basin104corresponding to the bottom137of the impeller117and/or another sump pump component of the sump pump102, which is below the low or initial water level or mark140. In operation, if the sensor134does not detect water, then the current water level in the basin104may be deemed adequately low to avoid, prevent, reduce, etc. corrosion of the impeller117and/or another sump pump component due to standing water in the sump basin104. On the other hand, if the water level sensor134detects water, then at least a portion of the impeller117and/or another sump pump component may be currently exposed to water and a condition for potential corrosion may exist. Alternatively, the sensor134may be a force sensor or transducer and configured to detect a water rise or fall rate, water movement (e.g., a disturbance, splashing, sloshing, ripples, etc.) in the sump basin104due to the sump pump102running, etc. at the level or mark136. The sensor134may include magnetic or mechanical floats, pressure sensors, optical, ultrasonic, radar, capacitance, electroconductive or electrostatic sensors. The sensor134may be a continuous or a point level switch. A continuous liquid level switch or sensor provides a continuous feedback showing liquid level within a specified range. A point level switch detects whether a liquid level is above or below a certain sensing point. In some embodiments, the sensor134may be a reed switch, or a mercury switch, a conductive level sensor, or any type of a suitable switch that changes a state from inactive to active as liquid level reaches a certain level relative to the switch position. Each of the sensors124,126,128,130,132, and134may include one or more associated circuits, as well as packaging elements. The sensors124,126,128,130,132, and134may be electrically or communicatively connected with each other (e.g., via one or more busses or links, power lines, etc.), and may cooperate to enable “smart” functionality described within this disclosure. The sump pump system100may include a mechanical shaker101that is physically attached to the sump pump102and/or the discharge pipe112. When engaged, the shaker101vibrates at a given frequency for the purpose of transferring motion to the sump pump102or the discharge pipe112in order to cause the pump102or the discharge pipe112to vibrate in a manner sufficient to “break loose” a blockage that is blocking the impeller117or the pipe112. The mechanical shaker101may be in the form of an electromechanical vibration device (e.g. a linear motor) that physically agitates or shakes the sump pump. The intensity and duration of the vibration produced by the mechanical shaker101may be set or adjusted as desired. For example, the mechanical shaker101may be set to vibrate intensely and continuously for a short burst of time. As another example, the mechanical shaker101may be set to vibrate in multiple operating cycles (e.g., 3 or 5 cycles), with each cycle producing a different level of vibration intensity (e.g., an increase in the level of intensity going from the first cycle to the last cycle). Further, different types of vibration profiles may be specified such as a sine sweep, random vibration, synthesized shock, etc. The mechanical shaker101may be a standalone unit that may be retrofitted or added to the sump pump102. In some embodiments, the mechanical shaker101may be integrated with or be part of the sump pump102. Further, both the mechanical shaker101and the water level sensor(s) in the system100may be connected to the controller138so that the controller138can control the operation of the mechanical shaker101and the water level sensor(s). The mechanical shaker101may be automatically activated in response to detected soft mechanical failures, such as when water overflow is detected by water level sensor or when the motor103runs too long in the absence of any water overflow detection. The mechanical shaker101may also be automatically activated in response to the controller138detecting potential problems with the motor103. For example, the controller138may detect a vibration or acceleration pattern (e.g., of the water or of the sump pump or sump pipe) indicative of a problem (e.g., a blockage), and may respond by activating the shaker101. In some examples, the sump pump controller138maintains, tests, etc. the sump pump system100by periodically (e.g., every 14 days) running the motor103for at least a short duration (e.g., 30 seconds), regardless of the amount of water in the sump basin104. To reduce, avoid, prevent, etc. corrosion of the impeller117due to extended exposure of the impeller117to standing, potentially dirty water, in some examples, the sump pump controller138periodically activates the motor103(e.g., every 14 days) until the level of water in the sump basin104as detected by, for example, the sensor134is below the bottom137of the impeller117. When the sensor134is a level sensor, the level of water in the sump basin104may be detected as being below the impeller117when the sensor134fails to sense any water. When the sensor134is a force sensor, the level of water in the sump basin104may be detected as above the bottom137of the impeller117when the sensor134senses a falling water level, water movement (e.g., sloshing, splashing, ripples, etc.) due to pump vibrations, etc. Additionally and/or alternatively, following a water event, the sump pump controller138runs the motor103until a current level of the water in the sump basin104as detected by, for example, the sensor134is below the bottom137of the impeller117and/or another sump pump component. Example water events include, but are not limited to, a storm, a flood, a plumbing failure, etc. that initially causes an initial inrush of incoming water, followed by a slower flow of incoming water. An example method of detecting a water event includes: (i) during a first time period, detecting that a rate at which water is rising in the sump basin exceeds a first threshold; (ii) during a second, later time period, detecting that a rate at which water is rising in the sump basin104is less than a second, lower threshold; and (iii) optionally detecting that water has stopped rising in the sump basin. In some examples, the force sensor126is configured to determine the water rise rate in the sump basin104. The rate at which water is rising in the sump basin104may, additionally and/or alternatively, be determined by counting the number of activations of the motor103in a period of time to, for example, maintain a current level of water in the sump basin104below the water level or mark142. As shown in the illustrated example ofFIG.1, the sump pump controller138and/or, more generally, the sump pump system100, may be a smart device that is part of the sump pump network system160. However, the sump pump controller138and/or, more generally, the sump pump system100may, additionally and/or alternatively, operate as a standalone system. The sump pump controller138may convey data, updates, alerts, etc. related to the sump pump system100to a smart home hub152at the property150via any number and/or type(s) of local network(s)154. The smart home hub152may connect to smart home devices (e.g., the sump pump controller138, the sump pump system100, doorbells, lights, locks, security cameras, thermostats, etc.) to enable a user156(e.g., a homeowner) to install, configure, control, monitor, etc. such devices via an electronic device158, such as a smartphone, a tablet, a personal computer, or any other computing device. In some embodiments, the smart home hub152may send alerts, updates, notifications, etc. when certain conditions occur (e.g., when the sump pump controller138detects potential failure conditions) to the user156via their electronic device158. Additionally and/or alternatively, alerts, status updates, notifications, etc. may be provided remotely via any number and/or type(s) of remote network(s)162, such as the Internet. Thus, the user156may receive alerts, status updates, notifications, etc. via their electronic device158both when they are at the property150and when they are away. Moreover, alerts, status updates, notifications, etc. may be sent to a remote processing server164(e.g., a server or servers associated with insurance provider or providers) via the remote network(s)162for remote monitoring, control, etc. While examples disclosed herein are described with reference to the sump pump controller138receiving and processing data from the sensors124,126,128,130,132and134to maintain and/or detect failures of the sump pump system100, additionally and/or alternatively, data from the sensors124,126,128,130,132and134may be sent to the remote processing server164for processing to control, maintain and/or detect failures of the sump pump system100, etc. In some examples, the remote processing server164may be part of security system monitoring server. In some examples, data from the sensors124,126,128,130,132and134, and/or alerts, status updates, notifications, trends, etc. determined by the sump pump controller138are stored in a cache, datastore, memory, etc.144for subsequent recall. While the example sump pump controller138and/or, more generally, the example sump pump system100for monitoring sump pumps for failures and/or maintaining sump pumps are illustrated inFIG.1, one or more of the elements, processes, devices and/or systems illustrated inFIG.1may be combined, divided, re-arranged, omitted, eliminated or implemented in any other way. Further, the sump pump controller138and/or, more generally, the sump pump system100may include one or more elements, processes, devices and/or systems in addition to, or instead of, those illustrated inFIG.1, and/or may include more than one of any or all of the illustrated elements, processes, devices and/or systems. FIG.2is a block diagram of an example computing system200configured in accordance with described embodiments. The example computing system200may be used to, for example, implement all or part of the sump pump controller138and/or, more generally, the sump pump system100. The computing system200may be, for example, a computer, an embedded controller, an Internet appliance, and/or any other type of computing device. Any one or more of the server164, the hub152, the device158, or the controller138may be similar to the system200, and may have components identical to or similar to those of the system200. The computing system200includes, among other things, a processor202, memory204, input/output (I/O) interface(s)206and network interface(s)208, all of which are interconnected via an address/data bus210. The program memory204may store software and/or machine-readable instructions that may be executed by the processor202. It should be appreciated that althoughFIG.2depicts only one processor202, the computing system200may include multiple processors202. The processor202of the illustrated example is hardware, and may be a semiconductor based (e.g., silicon based) device. Example processors202include a programmable processor, a programmable controller, a graphics processing unit (GPU), a digital signal processor (DSP), an application specific integrated circuit (ASIC), a programmable logic device (PLD), a field programmable gate array (FPGA), a field programmable logic device (FPLD), etc. In this example, the processor implements sump pump controller138. The memory204may include volatile and/or non-volatile memory(-ies) or disk(s) storing software and/or machine-readable instructions. For example, the program memory204may store software and/or machine-readable instructions that may be executed by the processor202to implement the sump pump controller138and/or, more generally, the sump pump system100. In some examples, the memory204is used to store the datastore140. Example memories204include any number or type(s) of volatile or non-volatile tangible, non-transitory, machine-readable storage medium or disks, such as semiconductor memory, magnetically readable memory, optically readable memory, a hard disk drive (HDD), an optical storage drive, a solid-state storage device, a solid-state drive (SSD), a read-only memory (ROM), a random-access memory (RAM), a compact disc (CD), a CD-ROM, a DVD, a Blu-ray disk, a redundant array of independent disks (RAID) system, a cache, a flash memory, or any other storage medium or storage disk in which information may be stored for any duration (e.g., permanently, for an extended time period, for a brief instance, for temporarily buffering, for caching of the information, etc.). As used herein, the term non-transitory, machine-readable medium is expressly defined to include any type of machine-readable storage device and/or storage disk, to exclude propagating signals, and to exclude transmission media. The processing platform200ofFIG.2includes one or more communication interfaces such as, for example, one or more of the input/output (I/O) interface(s)206and/or the network interface(s)208. The communication interface(s) enable the processing platform200ofFIG.2to communicate with, for example, another device, system, host system, or any other machine such as the smart home hub152and/or the remote processing server164. The I/O interface(s)206ofFIG.2enable receipt of user input and communication of output data to, for example, the user156. The I/O interfaces206may include any number and/or type(s) of different types of I/O circuits or components that enable the processor202to communicate with peripheral I/O devices (e.g., the example sensors124,126,128,130,132and134ofFIG.1) or another system. Example I/O interfaces206include a universal serial bus (USB) interface, a Bluetooth® interface, a near field communication (NFC) interface, a serial interface, and/or an infrared transceiver. The peripheral I/O devices may be any desired type of I/O device such as a keyboard, a display (a liquid crystal display (LCD), a cathode ray tube (CRT) display, a light emitting diode (LED) display, an organic light emitting diode (OLED) display, an in-place switching (IPS) display, a touch screen, etc.), a navigation device (e.g., a mouse, a trackball, a capacitive touch pad, a joystick, etc.), a speaker, a microphone, a printer, a button, etc. AlthoughFIG.2depicts the I/O interface(s)206as a single block, the I/O interface(s)206may include any number and/or type(s) of I/O circuits or components that enable the processor202to communicate with peripheral I/O devices and/or other systems. The network interface(s)208enable communication with other systems (e.g., the smart home hub152ofFIG.1) via, for example, one or more networks (e.g., the networks154and162). The example network interface(s)208include any suitable type of wired and/or wireless network interface(s) configured to operate in accordance with any suitable protocol(s) like, for example, a TCP/IP interface, a Wi-Fi™ transceiver (according to the IEEE 802.11 family of standards), an Ethernet transceiver, a cellular network radio, a satellite network radio, a coaxial cable modem, a digital subscriber line (DSL) modem, a dialup modem, or any other suitable communication protocols or standards. AlthoughFIG.2depicts the network interface(s)208as a single block, the network interface(s)208may include any number and/or type(s) of network interfaces that enable the processor202to communicate with other systems and/or networks. To provide, for example, backup power for the example sump pump controller138and/or, more generally, the example sump pump system100, the example computing system200may include any number and/or type(s) of battery(-ies)212. To determine the time between events, the example computing system200includes any number and/or type(s) of timer(s)214. For example, a timer214may be used to periodically trigger (e.g., every 14 days) the activation of the motor103for maintenance purposes. A timer214may, additionally and/or alternatively, be used to determine the rate at which water is rising in the sump basin (e.g., number of activations of the motor103required) during a period of time. FIG.3depicts an example method300for detecting and utilizing motion of water in sump basins when implementing control of sump pumps. A sump pump system may implement the method300to detect a malfunctioning level sensor that is used by the pump to detect high-water and low-water marks at which the sump pump activates and deactivates, respectively. By contrast, most sump pump systems on the market do not utilize sensors capable of detecting a malfunction of a typical float sensor in a sump pump, much less capable of detecting such a malfunction in the manner described with respect to the method300. As a result, float sensors represent a single point of failure in many sump pump systems. If the float sensor gets “stuck” while disengage or deactivated, for example, the sump pump may fail to detect a high-water mark in the sump basin, resulting in the sump pump failing to activate or engage when one would typically expect, resulting in the sump basin overflowing (and potentially resulting in a basement in which the sump pump is installed flooding, potentially leading to costly water damage to walls, floors, furniture, electronics, etc.). Alternatively, if the float sensor becomes “stuck” after activating or engaging, the sump pump may continuously run. While this may prevent an overflow of the sump basin in the short-term, the sump pump motor may quickly burn out if this condition is corrected. And at that point, the sump basin is obviously at risk of overflowing. At a high level, a system implementing the method300relies on sensor(s) configured to detect motion (e.g., acceleration), which can be analyzed to calculate water rise rates. These sensors may be accelerometers, gyroscopes, inertial measurement units (IMUs), or force acceleration sensors. Generally speaking, the sensor(s) may be disposed on or within the water, and may be responsive to the water such that, when the water level rises or drops, the sensor(s) responsively and proportionally drop. Accordingly, one may use a technique akin to dead-reckoning, in which relative changes in the water level are detected for the purpose of approximating the water level in the sump basin. Alternatively or additionally, the data from these sensors that detect motion or acceleration may be analyzed, for example, to identify acceleration or vibration patterns that correspond to certain water levels. For example, inlet pipes into the sump basin are generally set at a fixed position above the bottom of the sump basin. As a result, when the water level is low, the water will fall further from the pipe before hitting the water in the basin than it will when the basin is nearly full. As a result, the water will be disturbed in different manners when the sump basin is 0% full, 25% full, 50% full, 75% full, 100% full, etc. The acceleration data from the sensors can be analyzed to detect these different disturbance patterns in the water (sometimes call acceleration patterns or vibration patterns), and can thus be used as proxies for water level. Note, the patterns and corresponding levels may be updated over time, rather than static. For example, the rate of in-flow into the basin may also impact the disturbance pattern of water in the basin. As a result, the sump pump control system may continuously adapt and update known relationships between water vibration patterns and estimated water levels. For example, in a given cycle, the system may identify a water disturbance pattern when the pump engages (because this is a known level, such as 10% full) and another water disturbance pattern when the pump disengages (again, because this is a known level, such as 90% full). If desired, the system may interpolate between these points and analyze the difference between disturbance patterns to “guess” disturbance patterns at other points based on time between activation and deactivation. For example, if two minutes pass between engagement and disengagement, the system may “guess” that a water disturbance pattern at a water level of 50% is an average of the 90% and 10% marks. This may be performed for any desired number of water levels. Likewise, this observation and calculation may be performed at any desired rate (e.g., every cycle, every other cycle, every fifth cycle, etc.). Further, the system may use a rolling average if desired (e.g., wherein patterns from a number of past cycles are considered). If desired, a machine-learning algorithm may be utilized to learn correlations between patterns and water levels, and may be implemented to estimate level based on observed vibration or acceleration patterns. In some instances, the vibration or acceleration sensors may be installed in one or more inlet pipes and may be used to monitor in-flow (which can be used to help determine level). For example, the inlet pipes may themselves move slightly when water is flowing through them. In some instances, sensors may be tether to the inner wall of a pipe, resulting in the sensor moving when water flows through the inlet pipes. In any event, returning toFIG.3, the method300may be implemented, in whole or in part, by any suitable controller or system such as the sump pump controller138shown inFIG.1or the sump pump processor202shown inFIG.2. In an embodiment, the method300may be embodied by a set of instructions or routines that are stored to memory and executable by a processor (e.g., of the controller138) to implement the functionality of the method300. If desired, the smart home hub152or the remote processing server164shown inFIG.1, for example, may implement the method300, depending on the embodiment. Understand that while the description below references structural or software components of a sump pump system shown inFIG.1, the method300may be implemented with respect to any suitable sump pump and sump pump system to perform the described functions below. At a step305, a sump pump (e.g., the sump pump102) is implemented. The sump pump may be configured to operate based on water levels detected via a first sensor, such as the float switch122shown inFIG.1. If desired, the first sensor may be a float level sensor, which is a sensor designed for point level detection (i.e., detecting a binary condition; water is either detected at a particular point or it is not detected) rather than a “continuous” level of detection. So for example, a float switch that detects only two “points” such as a high-water mark and a low-water mark, is a point level sensor. For the most part, a float level sensor works as a switch to engage a function when the tank level either rises or falls to a certain level. This could be to sound an alarm or to engage a piece of equipment. Essentially, the sensor detects when the liquid has reached the desired point and it acts as a switch to activate the necessary response. At a step310, a sump pump controller (e.g.,134) for the sump pump detects acceleration of a second sensor (e.g., the sensor126) that is caused by movement of water in the sump basin (e.g., the basin104). At a step315, the sump pump controller analyzes acceleration data, representing the detected acceleration, to estimate a water level that is indicative of a fault in the first sensor. For example, the controller may detect and quantify a change in position of the second sensor based on the analysis, and may track this change in position relative to a previously known position in order to estimate a current water level. As another example, the controller may identify an acceleration pattern (sometimes called water vibration pattern or ripple pattern) indicative of a current water level. The controller may do this by comparing a detected ripple pattern to known ripple patterns that are stored to memory as being associated with various levels. In an embodiment, the controller detects a transition in ripple patterns that indicates a water inlet pipe has become at least partially submerged by water. Due to at least some of the in-flow being under water, this may result in a detectable change in water movement in the sump basin. Further, because the height of the inlet pipe(s) within the sump basin are constant, the controller may be programmed to estimate the water level is at this known level when the transition is detected. In some embodiments, the controller may implement machine learning techniques to detect these transitions and estimate a water level (e.g., based on training procedures involving analyzing various water signature patterns and known sump basin levels). In any event, the controller may determine that the estimated water level is at a level indicative of a potential fault in the first sensor. For example, the controller may determine that either a high-water mark or a low-water mark has been crossed but not detected by the first sensor. In embodiments in which the first sensor is configured to detect other water levels (e.g., 50% full), the controller may likewise determine that the 50% mark has been crossed but not detected by the first sensor. As another example, the controller may determine that one or more water vibration patterns detected via the second sensor indicate a particular in-flow or range of in-flow. The controller may calculate an expected duration to the high-water mark based on this estimated in-flow, and may trigger activation of a timer. When the timer indicates the duration of time has been exceeded (e.g., potentially including a buffer of time), the controller may conclude that the high-water mark has potentially or likely been exceeded. In some instances, the controller may determine that the estimated water level confirms that the first sensor is functional and accurate. For example, the controller may determine that the first sensor detected a high-water mark and that the second sensor detected a vibration pattern of water consistent with known water vibration patterns typically present at a high-water mark. In some embodiments, the controller138may assess the sump pump system condition by analyzing motor control characteristics such as current draw and pump motor103rotation speed. Based on the analysis, the controller138may determine whether the pump102is pumping water or air. The controller138can utilize the dry/submerged status of the pump102to calculate a fill rate and/or a level of water (e.g., without directly sensing a water level via a level sensor). For example, the controller138may calculate (or be configured to store) a high-water volume (i.e., the volume of water in the basin when the water reaches the high-water mark). Similarly, the controller138may calculate (or be configured to store) a dry-pump volume (i.e., the volume of water in the basin when the water drops low enough to result in the pump102pumping air rather than water). The difference between the high-water volume and the dry-pump volume may be referred to as the delta volume (the controller138may be configured to store the delta volume, or it may be configured to calculate the delta volume). For example, the delta volume may be 2.5 gallons. The controller138may detect when the high-water volume exists (because the time at which the pump102is activated is likely the same time at which the high-water volume is achieved). Further, using the described techniques, the controller138may detect a moment at which an active pump or impeller starts pumping air instead of water. The controller138may calculate the time (e.g., 30 seconds or ½ minute) between these two moments and may divide the known delta volume (e.g., 2.5 gallons) by the calculated time (½ minute) to arrive at a fill rate (e.g., 5 gallons per minute). Further, the controller138may utilize the calculated fill rate to estimate the level in the basin. For example, the controller138may start a timer when the water level reaches a known sensed level. For example, the low-water mark may be a known height. After a level sensor detects the low-water mark (e.g., the mark at which the pump102typically stops pumping), it may start the timer to track a time and may multiply the time by the fill rate to estimate the level at the time. This may be done multiple times if desired (e.g., continuously). Likewise, the controller138may be configured to store a known height just below the pump or impeller (i.e., the “dry-pump mark”). The controller138may utilize the disclosed techniques to detect (e.g. via motor control characteristics or power/current draw) a moment at which the pump starts to dry pump. The controller138may then assume the water level is at the dry-pump mark, and may utilize a timer and the fill rate to calculate or track an estimated water level (e.g., continuously if desired). The estimated water level may be used as a secondary or back-up level tracking (e.g., in case the primary level sensor faults). In other words, if an estimated water level indicates the water is above the high-water mark and a primary level sensor has not detected water at the high-water mark, the controller138may nevertheless activate the pump102to prevent flooding. If desired, the controller138may generate an alarm to notify someone (e.g., a user156or a home insuring party) that the level sensor may be faulty. Using motor characteristics change over time to determine water rise rate in the sump basin104can be used in addition to or instead of detecting a correlation between the identified one or more acceleration patterns detected from a sensor mounted on a sump pump or a sump pipe (e.g., the sensor128) and one or more sump pump conditions corresponding to the identified patterns. In any event, at a step320, the controller responds to estimating that the water level is indicative of the first sensor experiencing a fault by activating or engaging the sump pump. That is, to address a likelihood that a high-water mark has been crossed (or is at risk of being crossed), the controller may activate the sump pump. In some instances, the response may include activating a back-up level sensor to the first sensor and/or a back-up sump pump. In some instances, the controller may continue estimating water levels in the sump basin in accordance with the techniques described above. In some instances, the controller may institute a time-based schedule for cycling activation and deactivation of the sump pump based, for example, on an estimated in-flow rate that is estimated based on water signatures and/or based on rates calculated between deactivation and activation times when the first sensor was known (because the high-water and low-water marks are constant and known, the controller can calculate a time between 10% full and 90% full, for example). In some instances, the controller may switch to a mode in which it cycles (i.e., activates and deactivates) based on water patterns corresponding estimated to correspond to low-water and high-water marks. In an embodiment, the controller's response to detecting the fault may include generating an alarm. In some embodiments, the alarm may be a trigger to order replacement sump pump system components and their necessary fixtures. The trigger may be, for example, a push notification to the user device linked to the user's (e.g., the user156) account with an online retailer of the user's choice. The notification may be an alert requiring the user's approval to complete the order. In some embodiments, the controller138, based on the rise rate measurement, may respond by adjusting the pumping rate of the sump pump102, where the sump pump motor103may be a variable speed motor. A known parameter of the dimensions of the sump basin104(e.g., diameter or width and length) and the detected water level rise rate would yield a volume of water rise level per unit of time (e.g., gallons per second, or gallons per minute). The controller138may adjust the pumping rate of the sump pump102to the match or overcome the water rise rate for a specific size of the sump basin104. The controller138may implement this control in addition to or instead of generating an alert to, for example, the user156. When implemented in software, any of the applications, services, and engines described herein may be stored in any tangible, non-transitory computer readable memory such as on a magnetic disk, a laser disk, solid state memory device, molecular memory storage device, or other storage medium, in a RAM or ROM of a computer or processor, etc. Although the example systems disclosed herein are disclosed as including, among other components, software or firmware executed on hardware, it should be noted that such systems are merely illustrative and should not be considered as limiting. For example, it is contemplated that any or all of these hardware, software, and firmware components could be embodied exclusively in hardware, exclusively in software, or in any combination of hardware and software. Accordingly, while the example systems described herein are described as being implemented in software executed on a processor of one or more computer devices, persons of ordinary skill in the art will readily appreciate that the examples provided are not the only way to implement such systems. Referencing the method300specifically, the described functions may be implemented, in whole or in part, by the devices, circuits, or routines of the system100shown inFIG.1. The method300may be embodied by a set of circuits that are permanently or semi-permanently configured (e.g., an ASIC or FPGA) to perform logical functions of the respective method or that are at least temporarily configured (e.g., one or more processors and a set instructions or routines, representing the logical functions, saved to a memory) to perform the logical functions of the respective method. Throughout this specification, plural instances may implement components, operations, or structures described as a single instance. Although individual operations of one or more methods are illustrated and described as separate operations, one or more of the individual operations may be performed concurrently in certain embodiments. As used herein, any reference to “one embodiment” or “an embodiment” means that a particular element, feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment. The appearances of the phrase “in one embodiment” in various places in the specification are not necessarily all referring to the same embodiment. As used herein, the terms “comprises,” “comprising,” “includes,” “including,” “has,” “having” or any other variation thereof, are intended to cover a non-exclusive inclusion. For example, a process, method, article, or apparatus that comprises a list of elements is not necessarily limited to only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Further, unless expressly stated to the contrary, “or” refers to an inclusive or and not to an exclusive or. For example, a condition A or B is satisfied by any one of the following: A is true (or present) and B is false (or not present), A is false (or not present) and B is true (or present), and both A and B are true (or present). Further, the phrase “wherein the system includes at least one of X, Y, or Z” means the system includes an X, a Y, a Z, or some combination thereof. Similarly, the phrase “wherein the component is configured for X, Y, or Z” means that the component is configured for X, configured for Y, configured for Z, or configured for some combination of X, Y, and Z. In addition, use of the “a” or “an” are employed to describe elements and components of the embodiments herein. This description, and the claims that follow, should be read to include one or at least one. The singular also includes the plural unless it is obvious that it is meant otherwise. Further, the patent claims at the end of this document are not intended to be construed under 35 U.S.C. § 112(f) unless traditional means-plus-function language is expressly recited, such as “means for” or “step for” language being explicitly recited in the claim(s). At least some aspects of the systems and methods described herein are directed to an improvement to computer functionality, and improve the functioning of conventional computers. | 61,072 |
11859621 | DETAILED DESCRIPTION This disclosure is directed to an interstage capacity control valve for a centrifugal compressor, particularly one providing side stream flow regulation or distribution. FIG.1Ashows a sectional view of a compressor100according to an embodiment when a capacity control valve is in a fully open position. Compressor100can have a cylindrical structure such that the sectional view shown inFIGS.1A-1Dbe repeated or continuous through 360° of rotation about axis A of the compressor100. Compressor100is a multi-stage centrifugal compressor according to an embodiment. Compressor100includes an inlet guide vane102where a core flow of fluid to be compressed is received. Compressor100includes a first stage impeller104driven by rotation of shaft106, a diffuser108downstream of the first stage impeller104, and a return bend110downstream of the diffuser108. Compressor100further includes one or more deswirl vanes112downstream of the return bend110. Compressor100includes a side stream injection port114and a capacity control valve116. Compressor100includes a second stage impeller118downstream of the deswirl vanes112and the side stream injection port114, with a volute scroll120and a discharge conic122downstream of the second stage impeller118. While compressor100is shown inFIGS.1A-1Das a two-stage compressor, compressors according to embodiments can include any number of stages, with the side stream injection port114and the capacity control valve116are provided in an interstage flow path between any two stages of the compressor. For example, compressor100can be a three-stage compressor, with the side stream injection port114and capacity control valve116disposed between the exhaust of the second stage and the intake of the third stage, or the like. Flow of working fluid into compressor100may be controlled using one or more inlet guide vanes102. The one or more inlet guide vanes102can be configured to obstruct or permit flow of working fluid into the compressor100. In an embodiment, each of the inlet guide vanes102can be a rotating vane, for example, each rotating vane forming a section of a circle such that when all rotating vanes are in a closed position, the inlet guide vanes102obstruct an inlet of the compressor100. The one or more inlet guide vanes102can be movable between a fully open position and the closed position. In the fully open position the effect of the inlet guide vanes102on flow into compressor100can be minimized, for example by positioning the inlet guide vanes102such that the plane of each vane is substantially parallel to the direction of flow of working fluid into the inlet of compressor100. In an embodiment, each or all of the one or more inlet guide vanes102can be varied continuously from the fully open position to the closed position, through one or more partially open positions. Compressor100includes a first stage impeller104. The first stage impeller104includes a plurality of blades. The first stage impeller104is configured to draw in the working fluid that passes the one or more inlet guide vanes102when rotated, and to expel the working fluid towards diffuser108. The first stage impeller104is joined to shaft106. Shaft106is rotated by, for example, a prime mover such as a motor. Diffuser108receives the fluid discharged from first stage impellers104and directs the flow of the fluid towards return bend110. Return bend110changes the direction of the flow of the fluid such that it travels through the deswirl vanes112towards the second stage impeller118. One or more deswirl vanes112are vanes extending from the return bend110towards the second stage impeller118. The deswirl vanes112are shaped to straighten the flow of the fluid as the flow passes towards the second stage impeller118. The deswirl vanes112can include notches configured to receive at least a portion of the capacity control valve116. Side stream injection port114is a port configured to allow a side stream to be introduced into the interstage flow of fluid through compressor100. The side stream injection port114includes a leading end124and a trailing end126, with the leading end124towards the return bend110and the trailing end126towards the second stage impeller118. Side stream injection port114fluidly connects a side stream flow channel128with the interstage flow. The side stream flow channel128can receive a side stream of fluid from within a fluid circuit including the compressor100. The source of the side stream of fluid received by side stream flow channel can be from one or more of a condenser, an economizer, an intercooler, a heat exchanger, or any other suitable source of fluid that is at an intermediate pressure, between the suction pressure and the discharge pressure of the compressor100. The side stream injection port114can be a ring shape surrounding an intake of the second stage impeller118. The side stream injection port114can be provided between the return bend110and the second stage impeller118. Capacity control valve116is a valve configured regulate the flow through the side stream injection port114. Capacity control valve116is configured to be extended axially through the side stream injection port114such that it extends substantially perpendicular to a direction of flow of the interstage flow from deswirl vane110towards the second stage impeller118. Capacity control valve116is configured to be able to prohibit flow through side stream injection port114in a closed position, for example by including a portion having a thickness corresponding to the width of the side stream injection port114from leading end124to trailing end126. In an embodiment, capacity control valve116is controlled in conjunction with inlet guide vanes102. In an embodiment, capacity control valve116is controlled independently of inlet guide vanes102. Capacity control valve116includes a leading side130facing towards the return bend110and a trailing side132facing towards an inlet into second stage impeller118. Leading side130includes curved surface134extending towards a tip136of the capacity control valve116. The curved surface134can reduce the cross-sectional thickness of the capacity control valve116from a thickness corresponding to the width of the side stream injection port114at the base of the curved surface134to a smaller thickness at the tip136. The change in the cross-sectional thickness of capacity control valve116over the length of curved surface134towards tip136is configured to vary the amount of flow through the side stream injection port based on the extension of the capacity control valve116. In the embodiment shown inFIGS.1A-1D, trailing side132can be, for example, a linear profile in the longitudinal direction of the capacity control valve116configured to always be in contact with trailing end126of the side stream injection port114, such that all flow of the side stream into the interstage flow is over the leading side130. Where side stream injection port114has a ring shape, the capacity control valve116can have a corresponding ring shape. In an embodiment, the capacity control valve is a single ring. In an embodiment, the capacity control valve includes a plurality of ring segments. In an embodiment, the capacity control valve116includes one or more notches configured to avoid contact between the capacity control valve116and one or more deswirl vanes112as the capacity control valve116is extended. In an embodiment, the capacity control valve can be moved from a fully open position where the tip136is located within the side stream injection port116or the side stream channel128, and a fully closed position, where the capacity control valve116obstructs the side stream injection port114from leading end124to trailing end126. In the fully open position of the capacity control valve116, the tip136of the capacity control valve116does not extend through the side stream injection port114. Accordingly, the interstage flow through the deswirl vane112is not obstructed, and obstruction of the side stream injection port114by the capacity control valve is at a minimum. The side stream fluid passes over the curved surface134to join the interstage flow between return bend110and second stage impeller118. The fully open position can be used when the compressor100is operating at or near a full-load capacity. Second stage impeller118is used to achieve the second stage of compression. Second stage impeller118draws in the combined interstage and side stream flows and expels the fluid towards volute scroll120. Second stage impeller118can be rotated by shaft106, which is also used to rotate first stage impeller104. Fluid at the volute scroll120can then be discharged from compressor100at discharge conic122. In an embodiment, the side stream provided through side stream injection port114can be received from an economizer, such as the economizer314shown inFIG.3Band described below. The economizer can be a flash-tank economizer, where flash or bypass gas rises and can be directed to the side stream flow channel128. The gas from the economizer being directed to the side stream flow channel128can reduce or eliminate the presence of gas in the liquid being passed to an evaporator of the HVACR system including compressor100. This can in turn improve the absorption of energy at the evaporator without further subcooling by providing more saturated liquid working fluid. In the full load cycle corresponding to the fully open position of capacity control valve116, the pressure at the side stream injection port114can allow the entrained vapor to be substantially removed from the working fluid in the economizer. FIG.1Bshows a sectional view of the compressor shown inFIG.1Awhen the capacity control valve116is in a high flow position. The high flow position shown inFIG.1Bcan be used in a partial load condition where the load is relatively close to full load for the compressor100. In the high flow position shown inFIG.1B, the capacity control valve116is extended axially such that it partially extends through side stream injection port114. The leading side130of the capacity control valve116partially deflects the interstage flow in compressor100due to the projection of the capacity control valve reducing the size of the passage for interstage flow. The capacity control valve116restricts flow through the side stream injection port to a greater extent than when in the fully-open position shown inFIG.1Aand described above, with curved surface134reducing the orifice size by being closer to the leading end124of the side stream injection port114. The trailing side132of the capacity control valve116continues to be in contact with the trailing end126of the side stream injection port114, and all flow through side stream injection port114passes between the leading end124of side stream injection port114and the leading side130of capacity control valve116. Optionally, inlet guide vane102can be rotated to partially obstruct flow to the first stage impeller104of compressor100. FIG.1Cshows a sectional view of the compressor shown inFIG.1Awhen the capacity control valve is in a low flow position. The low flow position shown inFIG.1Ccan be used in a partial load condition where the load is below the full load for the compressor100, and less than the load where the capacity control valve is in a high flow position such as inFIG.1B. In the low flow position shown inFIG.1C, the capacity control valve116is extended axially such that it extends through side stream injection port114, extending further than the high flow position shown inFIG.1B. The leading side130of the capacity control valve116deflects the interstage flow in compressor100due to the greater projection of the capacity control valve116, further reducing the size of the passage for interstage flow. The capacity control valve116restricts flow through the side stream injection port to a greater extent than when in the high flow position shown inFIG.1Band described above, with curved surface134further reducing the orifice size by being even closer to the leading end124of the side stream injection port114. The trailing side132of the capacity control valve116continues to be in contact with the trailing end126of the side stream injection port114, and all flow through side stream injection port114passes between the leading end124of side stream injection port114and the leading side130of capacity control valve116. Optionally, inlet guide vane102can be rotated to further obstruct flow to the first stage impeller104of compressor100compared to its position in the high flow position shown inFIG.1B. FIG.1Dshows a sectional view of the compressor shown inFIG.1Awhen the capacity control valve is in a closed position. The closed position shown inFIG.1Dcan be used when the compressor100is in a partial-load condition at or near a minimum load for the compressor. In the closed position, capacity control valve116partially or completely obstructs side stream injection port114, from leading end124to trailing end126. It is appreciated that due to manufacturing tolerances, wear, etc. that there may be some leakage even when the capacity control valve116is configured to completely obstruct the side stream and is in the closed position. In an embodiment, capacity control valve116is sized such that it does not contact side stream injection port114and allows some flow to continue through side stream injection port114even in the fully extended closed position. The extension of the capacity control valve116into the interstage flow through compressor100is at a maximum, reducing the size of the orifice through which the interstage flow passes from return bend110towards second stage impeller118. Accordingly, this position imparts the greatest additional velocity to the interstage flow, while prohibiting the side stream flow from joining the interstage flow. Optionally, inlet guide vane102can be rotated to further obstruct flow to the first stage impeller104of compressor100, for example by pacing the inlet guide vane102in a minimum-flow position. FIG.2Ashows a sectional view of a compressor200according to an embodiment when a capacity control valve is in a fully open position. Compressor200can have a cylindrical structure such that the sectional view shown inFIGS.2A-2Dbe repeated or continuous through 360° of rotation about axis A of the compressor200. Compressor200is a multi-stage centrifugal compressor. Compressor200includes an inlet guide vane202where a core flow of fluid to be compressed is received. Compressor200includes a first stage impeller204driven by rotation of shaft206, a diffuser208downstream of the first stage impeller204, and a return bend210downstream of the diffuser208. Compressor200further includes one or more deswirl vanes212downstream of the return bend210. Compressor200includes a side stream injection port214and a capacity control valve216. Compressor200includes a second stage impeller218downstream of the deswirl vanes212and the side stream injection port214, with a volute scroll220and a discharge conic222downstream of the second stage impeller218. While compressor200is shown inFIGS.2A-2Das a two-stage compressor, compressors according to embodiments can include any number of stages, with the side stream injection port214and the capacity control valve216are provided in an interstage flow path between any two stages of the compressor. For example, compressor200can be a three-stage compressor, with the side stream injection port214and capacity control valve216disposed between the exhaust of the second stage and the intake of the third stage, or the like. Compressor200can include one or more inlet guide vane202to control flow of working fluid into the compressor200. The inlet guide vanes202can be substantially similar to the inlet guide vanes102described above and shown inFIGS.1A-1D. The one or more inlet guide vanes202can be configured to obstruct or permit flow of working fluid into the compressor200. In an embodiment, each of the inlet guide vanes202can be a rotating vane, for example, each rotating vane forming a section of a circle such that when all rotating vanes are in a closed position, the inlet guide vanes202obstruct an inlet of the compressor200. The one or more inlet guide vanes202can be movable between a fully open position and the closed position. In the fully open position the effect of the inlet guide vanes202on flow into compressor200can be minimized, for example by positioning the inlet guide vanes202such that the plane of each vane is substantially parallel to the direction of flow of working fluid into the inlet of compressor200. In an embodiment, each or all of the one or more inlet guide vanes202can be varied continuously from the fully open position to the closed position. Compressor200includes a first stage impeller204. The first stage impeller204is driven by shaft206. Shaft206is rotated by, for example, a prime mover such as a motor. The first stage impellers204are configured to draw in the working fluid that passes the one or more inlet guide vanes202when rotated, and to expel the working fluid towards diffuser208. Diffuser208receives the fluid discharged from first stage impellers204and directs the flow of the fluid towards return bend210. Return bend210changes the direction of the flow of the fluid such that it travels through the deswirl vanes212towards the second stage impeller218. One or more deswirl vanes212are vanes extending from the return bend210towards the second stage impeller218. The deswirl vanes212are shaped to straighten the flow of the fluid as the flow passes towards the second stage impeller218. The deswirl vanes212can include notches configured to receive at least a portion of the capacity control valve216. Side stream injection port214is a port configured to allow a side stream to be introduced into the interstage flow of fluid through compressor200. The side stream injection port214includes a leading end224and a trailing end226, with the leading end224towards the return bend210and the trailing end226towards the second stage impeller218. Side stream injection port214fluidly connects a side stream flow channel228with the interstage flow. The side stream flow channel228can receive a side stream of fluid from within a fluid circuit including the compressor200. The source of the side stream of fluid received by side stream flow channel228can be from one or more of a condenser, an economizer, an intercooler, a heat exchanger, or any other suitable source of fluid that is at an intermediate pressure, between the suction pressure and the discharge pressure of the compressor200. The side stream injection port214can be a ring shape surrounding an intake of the second stage impeller218. The side stream injection port214can be provided between the return bend210and the second stage impeller218. Capacity control valve216is a valve that configured regulate the flow through the side stream injection port214. Capacity control valve216is configured to be extended axially through the side stream injection port214such that it extends substantially perpendicular to a direction of flow of the interstage flow from deswirl vane212towards the second stage impeller218. Capacity control valve216is configured to be able to prohibit flow through side stream injection port214in a closed position, for example by including a portion having a thickness corresponding to the width of the side stream injection port214from leading end224to trailing end226. In an embodiment, capacity control valve216is controlled in conjunction with inlet guide vanes202. In an embodiment, capacity control valve216is controlled independently of inlet guide vanes202. Capacity control valve216includes a leading side230facing towards the return bend210and a trailing side232facing towards an inlet into second stage impeller218. Leading side230includes curved surface234extending towards a tip236of the capacity control valve116. The curved surface234can cause the distance between capacity control valve216and leading end224of side stream injection port214to be varied as capacity control valve216is axially extended or retracted. Trailing side232includes one or more passages238configured to allow the side stream flow from side stream flow channel228to pass through the side stream injection port214and be introduced into the interstage flow on the trailing side232of the capacity control valve216. In an embodiment, passage238includes one or more channels having openings on the trailing side232of the capacity control valve216. In an embodiment, passage238is a cutout or scalloping formed in the trailing side232, such that in some positions of capacity control valve216, a gap exists between the trailing side232and the trailing end224of the side stream injection port214. In the fully open position of the capacity control valve216, side stream flow passes from the side stream flow channel228through side stream injection port214, between the leading end224of the side stream injection port214and the leading side230of the capacity control valve216. Tip236of the capacity control valve216is located within the side stream injection port214or retracted into the side stream flow channel228, and capacity control valve216does not substantially affect the interstage flow passing from return bend210to second stage impeller218. Optionally, in the fully open position shown inFIG.2A, inlet guide vane202can be in an open position where it provides little to no resistance to flow into the first stage impeller204. The fully open position shown inFIG.2Acan be used, for example, when compressor200is being operated at or near full load capacity. In the embodiment shown inFIG.2, when in the fully open position shown inFIG.2A, some or all of the side stream flow passing through side stream injection port214can pass over the leading side230of capacity control valve216. Second stage impeller218is used to achieve the second stage of compression. Second stage impeller218draws in the combined interstage and side stream flows and expels the fluid towards volute scroll220. Second stage impeller218can be rotated by shaft206, which is also used to rotate first stage impeller204. Fluid at the volute scroll220can then be discharged from compressor200at discharge conic222. In an embodiment, the side stream provided through side stream injection port214can be received from an economizer, such as the economizer314shown inFIG.3Band described below. The economizer can be a flash-tank economizer, where flash or bypass gas rises and can be directed to the side stream flow channel228. The gas from the economizer being directed to the side stream flow channel228can reduce or eliminate the presence of gas in the liquid being passed to an evaporator of the HVACR system including compressor200. This can in turn improve the absorption of energy at the evaporator without further subcooling by providing more saturated liquid working fluid. In the full load cycle corresponding to the fully open position of capacity control valve216, the pressure at the side stream injection port214can allow the entrained vapor to be substantially removed from the working fluid in the economizer. FIG.2Bshows a sectional view of the compressor shown inFIG.2Awhen the capacity control valve216is in a high flow position. The high flow position shown inFIG.2Bcan be used in a partial load condition where the load is relatively close to full load for the compressor200. In the high flow position shown inFIG.2B, capacity control valve216is extended such that tip236projects into the path for interstage flow from return bend210to the second impeller218, partially obstructing the path for the interstage flow. In the high flow position of the embodiment shown inFIG.2B, a first gap exists between the leading end224of the side stream injection port and the leading side230of the capacity control valve216, and a second gap exists at passage238between the trailing side232of the capacity control valve216and the trailing end226of the side stream injection port214. Each of the first and second gaps allow some of the side stream flow to join the interstage flow. The portion passing through the second gap experiences less of the pressure exerted by the interstage flow due to its introduction on the trailing side232of the capacity control valve216. Optionally, in the high flow position shown inFIG.2B, inlet guide vane202can be in a high flow position where the inlet guide vane202provides increased resistance to flow into the first stage impeller204compared to the fully open position shown inFIG.2A, but less resistance to flow than the low flow or closed positions shown inFIGS.2C and2D, respectively. In the high-flow position shown inFIG.2B, flow through side stream injection port214can include both flow over the leading side230and past the trailing side232of the capacity control valve. FIG.2Cshows a sectional view of the compressor shown inFIG.2Awhen the capacity control valve216is in a low flow position. The low flow position shown inFIG.2Ccan be used in a partial load condition where the load is below the full load for the compressor200, and less than the load where the capacity control valve is in a high flow position such as inFIG.2B. In the low flow position shown inFIG.2C, capacity control valve216is extended further into the interstage flow from return bend210to second impeller218. The capacity control valve216thus provides even greater resistance to the interstage flow when compared to the high flow position shown inFIG.2B. In the low flow position of the embodiment shown inFIG.2C, a first gap exists between the leading end224of the side stream injection port and the leading side230of the capacity control valve216, and a second gap exists at passage238between the trailing side232of the capacity control valve216and the trailing end226of the side stream injection port214. Compared to the first and second gaps shown of the high flow position shown inFIG.2B, in the low flow position ofFIG.2C, the second gap is relatively larger compared to the first, and a greater proportion of the side stream flow passes through the second gap to join the interstage flow relative to the amount of the side stream flow passing through the first gap. Optionally, in the low flow position shown inFIG.2C, inlet guide vane202can be in a low flow position where the inlet guide vane202provides increased resistance to flow into the first stage impeller204compared to the high flow position shown inFIG.2B, but less resistance to flow than the closed positions shown inFIG.2D. In the low-flow position shown inFIG.2B, flow through side stream injection port214can primarily or entirely be past the trailing side232of the capacity control valve. The shape of the leading side230and of passage238can each or both be selected to control the relative amount of flow being introduced on either the leading side230or trailing side232of the capacity control valve216, and how those relative amounts vary with the position of capacity control valve216from the fully open position through the closed position as shown inFIGS.2A-2D. In an embodiment, side stream flow channel228can receive the side stream flow from an economizer, such as economizer314shown inFIG.3Band described below. Providing passage238in capacity control valve216can allow capacity control valve216to not only control the quantity of flow being introduced, but the particular point at which the side stream is introduced in side stream injection port214, and the pressure at the point of introduction. Controlling the position of the point of introduction of side stream flow can provide control over the relationship between core flow and side stream flow in the compressor. Control of the point of introduction can improve economizer effectiveness across different load conditions. The low flow position shown inFIG.2Ccan be used when compressor200is operated at part load. When the compressor200is operated at part load, the static pressure at the side stream injection port214, particularly between leading end222of the side stream injection port214and the leading side232of the capacity control valve216, can be relatively elevated. The pressure within the economizer is a function of the static pressure at the injection location in compressor200, in addition to pipe losses and fixed orifice pressure drops for the system. The elevated pressure at side stream injection port214can therefore lead to an elevated pressure at the economizer, reducing effectiveness in removing flash or bypass gas from the fluid contained within. Passage238, by being on an opposite side of the capacity control valve216from leading side232that is facing the interstage flow within compressor200, is subject to a reduced pressure in comparison to the pressure on the leading side232, or the static pressure at the side stream injection port114in the embodiment shown inFIG.1C. The reduced pressure at such an injection point can correspondingly lower the pressure within the economizer as described above, improving the release of flash or bypass gas from liquid in the economizer and its removal from the stream of working fluid passing to the evaporator. This improves the heat transfer at the evaporator and can also reduce recompression losses in the system including compressor200having capacity control valve216including passages238. FIG.2Dshows a sectional view of the compressor shown inFIG.2Awhen the capacity control valve216is in a closed position. The closed position shown inFIG.2Dcan be used when the compressor200is in a partial-load condition at or near a minimum load for the compressor. In the closed position, capacity control valve216partially or completely obstructs side stream injection port214, from leading end224to trailing end226. It is appreciated that due to manufacturing tolerances, etc., there may be some possible leakage even when capacity control valve216is in the closed position. In an embodiment, capacity control valve216may be sized such that it does not contact side stream injection port214, and allows some flow through the gap between the side stream injection port214and the capacity control valve216. Any features of capacity control valve216configured to allow the introduction of the side stream flow on the trailing side232of the capacity control valve216such as passage238can be configured such that they do not permit such flow when capacity control valve216in the closed position. For example, as shown inFIG.2D, a scalloped portion on the trailing side232forming passage238in this embodiment is sized and positioned such the trailing side232contacts the trailing end226of side stream injection port214when the capacity control valve216is extended into the closed position. The extension of the capacity control valve216into the interstage flow through compressor200is at a maximum, reducing the size of the orifice through which the interstage flow passes from return bend210towards second stage impeller218. Accordingly, this position imparts the greatest additional velocity to the interstage flow, while prohibiting the side stream flow from joining the interstage flow. Optionally, inlet guide vane202can be rotated to further obstruct flow to the first stage impeller204of compressor200, for example by pacing the inlet guide vane202in a minimum-flow position. FIG.3Ashows a heating, ventilation, air conditioning and refrigeration (HVACR) circuit according to an embodiment. HVACR circuit300includes compressor302, condenser304, expander306, and evaporator308. Compressor302is a centrifugal compressor, for example compressor100shown inFIGS.1A-1Dor compressor200shown inFIGS.2A-2Dand described above. Condenser304receives working fluid from compressor302and allows the working fluid to reject heat, for example to air or another heat exchange medium. In an embodiment, a fluid line from the condenser304can convey some of the working fluid of HVACR circuit300back to compressor302, as the side stream flow provided to the side stream flow injection port of the compressor302, such as side stream injection ports114or214described above and shown inFIGS.1A-2D. Condensed working fluid from condenser304can then pass to expander306. Expander306expands the working fluid passing through as the fluid passes through HVACR circuit300. Expander306can be any suitable expander for the working fluid within the HVACR circuit300, such as, for example, an expansion valve, one or more expansion orifices, or any other suitable expansion device for use in an HVACR circuit. Evaporator308is a heat exchanger where the working fluid of HVACR circuit300absorbs heat, for example from an ambient environment or a fluid to be cooled such as water in a water chiller HVACR system. The evaporator308can be, for example, an indoor coil of an air conditioner or a heat exchanger configured to cool water used in an HVACR system including the HVACR circuit300. HVACR circuit300can further include an intercooler310. Intercooler310is a heat exchanger where working fluid from the HVACR circuit exchanges heat with the interstage flow within compressor302. The working fluid that exchanges heat with the interstage flow in intercooler310can be sourced from, for example, evaporator308, between expander306and evaporator308, or between the evaporator308and the compressor302. Some or all of the working fluid that exchanges heat with the interstage flow can then be reintroduced into HVACR circuit300downstream of where the working fluid is sourced. In an embodiment, at least some of the working fluid from intercooler310can be directed to a side stream flow channel of compressor302instead of returning to the ordinary flow path through HVACR circuit300. The side stream flow channel can be, for example, side stream flow channel128or side stream flow channel228of the compressors100and200described above and shown inFIGS.1A-1D and2A-2D. FIG.3Bshows an economized HVACR circuit320according to an embodiment. InFIG.3B, compressor302, condenser304and evaporator308are included as in HVACR circuit300described above and shown inFIG.3A, with compressor302being a multi-stage compressor in this embodiment. HVACR circuit320includes a first expander312and a second expander314. Each of first expander312and second expander314can be any suitable expander for the working fluid within the HVACR circuit320such as, for example, an expansion valve, one or more expansion orifices, or any other suitable expansion device for use in an HVACR circuit. Economizer314can be disposed between first and second expanders312,314, such that working fluid of HVACR circuit320is at an intermediate pressure at the economizer314. The economizer314can be used as a source for the side stream introduced into compressor302, for example through a side stream flow channel such as side stream flow channel128or side stream flow channel228as described above and shown inFIGS.1A-1D and2A-2D. FIG.4shows a sectional view of a centrifugal compressor according to an embodiment along an interstage flow path. Centrifugal compressor400includes compressor housing402. Compressor housing402in part defines an interstage flow path404. The interstage flow path includes deswirl vanes406radially distributed around the interstage flow path404. Capacity control valve ring408extends into interstage flow path404, upstream of following stage inlet410. Capacity control valve ring can408be, for example, capacity control valve116or capacity control valve216as described above and shown inFIGS.1A-1D and2A-2D. Capacity control valve ring408can be a single continuous ring or composed of a plurality of ring segments that combine to provide the ring shape. Following stage inlet410receives flow passing the capacity control valve ring408and allows the flow to enter into the following stage impeller412. FIG.5shows a sectional view of a portion of a centrifugal compressor according to an embodiment. In the view of centrifugal compressor500, the interaction between the deswirl vanes502and the capacity control valve ring504. Deswirl vanes502can be any of the deswirl vanes shown inFIG.1A-1D,2A-2D, or4. Capacity control valve ring504can be any of the capacity control valves shown inFIG.1A-1D,2A-2D, or4. Capacity control valve ring includes notches506, each of notches506configured to accommodate one of the deswirl vanes502such that the capacity control valve ring504can be extended into a flow path including the deswirl vanes502without mechanically interfering with the deswirl vanes502. In an embodiment, notches corresponding to notches506can instead be included on each of the deswirl vanes502such that the deswirl vanes502do not contact the capacity control valve ring504as it is extended. In an embodiment, notches506are provided along with corresponding notches on the deswirl vanes502. In this embodiment, the notches506can have a depth that is less than an entire height of the area where capacity control valve ring504could contact deswirl vanes502, and the notches in the deswirl vanes have a depth such that they accommodate any portion of capacity control valve ring504that would otherwise contact the deswirl vanes502in the absence of said notches. FIG.6is a side perspective view of an embodiment of a centrifugal compressor600.FIG.7is a front view of the centrifugal compressor600. In an embodiment, the centrifugal compressor600is the compressor302in the HVACR circuit302inFIG.3AorFIG.3B. The compressor600includes a housing602having a suction inlet604, a discharge outlet606, and an intermediate injection inlet608. Working fluid enters the housing600through the suction inlet604, is compressed by the compressor600, and is discharged as compressed working fluid from the discharge outlet606. The compressor600includes a first stage S1, a second stage S2, and an interstage throttle630. The working fluid is compressed in the first stage S1(e.g., to a first pressure P1), flows from the first stage to the second stage S2, and is then further compressed to a higher pressure (e.g., second pressure P2) in the second stage S1. The intermediate injection inlet608is configured to receive a side stream of intermediate pressure working fluid (e.g., at an intermediate pressure that is between the first pressure P1and the second pressure P2). The intermediate injection inlet608can be, for example, the side stream flow channel128or the side stream flow channel228as described above and shown inFIGS.1A-1D and2A-2D. The compressed working fluid discharged from the first stage S1flows from the first stage S1to the second stage S2through the interstage throttle630. For example, the intermediate injection inlet608connects to a side stream injection port (e.g., side stream injection port114, side stream injection port214, or the like) disposed between the first stage S1and the second stage S2. The intermediate pressure working fluid mixes with the stream of compressed interstage fluid flowing from the first stage S1to the second stage S2, and the mixed flow of compressed interstage fluid and intermediate pressure fluid flow into the second stage S2. The interstage throttle630is configured to control a flowrate of the interstage fluid from the first stage S1to the second stage S2and a flowrate of the intermediate pressure fluid through the intermediate injection inlet608and into the second stage S2. FIGS.8-10show an embodiment of a capacity control valve and an actuation mechanism699for the capacity control valve of the interstage throttle630. The capacity control valve as described herein can have a ring shape and be referred to as a throttle ring660. Throttle ring660can be, for example, the capacity control valve116or the capacity control valve216as described above and shown inFIGS.1A-1D and2A-2D. FIG.8is front view section view of the throttle ring660, the actuation mechanism699, and a housing632of the interstage throttle630. The interstage throttle630includes the housing632. Housing632shown inFIG.8is the portion of the compressor housing602inFIG.6. For example, the housing632remains stationary within the compressor600during operation (e.g., remains stationary during rotation of the shaft that drives the first stage impeller and the second stage impeller).FIG.9is a side perspective view of the throttle ring660and the actuation mechanism actuation mechanism699when the throttle ring660is in its extended position.FIG.10is a side perspective view of the throttle ring660and the actuation mechanism actuation mechanism699when the throttle ring660is in its retracted position. The centrifugal compressor600can generally include features similar to the centrifugal compressors100,200,302,400,500inFIGS.1A-5. For example, the centrifugal compressor600includes a first stage impeller, a second stage impeller, deswirl vanes and a side stream injection port located between the first stage impeller and the second stage impeller as similarly described above and shown inFIGS.1A-2D. In an embodiment, one or more of the centrifugal compressors100,200,302,400,500inFIGS.1A-5may include the actuation mechanism699for operating/moving its capacity control valve116,216,416,516. The actuation mechanism699is configured to axially move the throttle ring660as similarly described above and shown inFIGS.1A-1D and2A-2Dfor the capacity control valve116or capacity control valve216. For example, the throttle ring660is moveable in the axial direction (e.g., positive axial direction D1, negative axial direction D2inFIG.9) between an extended position (shown inFIG.9) and a retracted position (shown inFIG.10). For example, the capacity control valve216in its fully open position inFIG.2Ais an example of the throttle ring660in the retracted position, and the capacity control valve216in its fully closed position inFIG.2Dis an example of the throttle ring660in the extended position. The throttle ring660may also include intermediate position(s) between its retracted position and its extended position as similarly shown and described for the capacity control valve216inFIGS.2B and2C. The actuation mechanism699for the throttle ring630includes the actuation linkage assembly672, a drive ring680, drive linkages682, and support linkages684. The compressor600also includes an actuator670that operates/drives the actuation mechanism699to axially move the throttle ring630within the housing632. The actuation linkage assembly672connects to the actuator670and extends through the housing632. For example, the actuation linkage assembly672includes a shaft674that extends through the housing632and the actuation of the actuator670(e.g., extending, retracting) rotates the shaft674. As shown inFIG.8, the actuator670can be mounted external to the housing632. In the illustrated embodiment, the actuation linkage assembly672is configured utilize the motion of the actuator670(e.g., linear motion, extension, retraction, etc.) to rotate the drive ring680. For example, the linear motion (e.g., extension, retraction, or the like) of actuator670rotates a shaft672of the actuation linkage assembly670and the rotation of the shaft672in turn rotates the drive ring680. As shown inFIGS.9and10, the drive ring680may have at or about the same circumference as the throttle ring660. The drive ring680is obscured by the throttle ring660inFIG.8. In an embodiment, the circumferences of the drive ring680and the throttle ring660are less than 10% different. In another embodiment, the circumferences of the drive ring680and the throttle ring660may be less than 5% different. FIG.9shows the actuator670when retracted such that the throttle ring630is in its extended position.FIG.10shows the throttle ring630when the actuator670is extended and has moved the throttle ring630to its retracted position. For example, a controller (not shown) of the centrifugal compressor600and/or the HVACR controller may be configured to control the capacity of the compressor600by controlling the position/actuation of the actuator670. The linkages682,684are configured to move the throttle ring660in the axial direction (e.g., positive axial direction D1, negative axial direction D2) using the rotation of the drive ring680. The drive linkages682connect the drive ring680to the throttle ring660. Each of the drive linkages682separately extends from the drive ring680to the throttle ring660. As shown inFIGS.8-10, the throttle ring660and the drive ring680each include radial shafts664,681(e.g., pins, bolts, integral shafts, or the like) that extend radially outward from the throttle ring660and the drive ring680, respectively. It should be appreciated that one or more of the radial shafts664,681may extend radially inward in another embodiment. The linkages682,684are rotatably connected to the radial shafts664,681on the rings660,680. As shown in theFIGS.8-10, the linkages682,684can each be an arm that connects their respective structures. The linkages682,684are configured to use the rotation of the drive ring680to move the throttle ring660in the axial direction with little to no rotation of the throttle ring660. As shown inFIG.8, each support linkage684has a first end685A that is rotatably connected to the throttle ring660and a second end685B that is rotatably connected to the housing632. For example, each support linkage684has a through-hole on its first end685A that is inserted onto a respective radial shaft664on the throttle ring660. For example, each support linkage684has a through-hole on its second end685B that is inserted onto a respective shaft634on the housing632. For example, the shaft634on the housing632extends in the axial direction (e.g., in axial direction D1inFIG.7). As shown inFIG.9, each drive linkage682has a first end683B that is rotatably connected to the throttle ring660and a second end683A that is rotatably attached to the drive ring680. For example, each drive linkage682has a through-hole on its first end683B that is inserted onto a respective radial shaft664on the throttle ring660. For example, each drive linkage682has a through-hole on its second end683A that is inserted onto a respective radial shaft681on the drive ring680. As shown inFIGS.8-10, the drive linkages682and support linkages684are provided in pairs. In each drive linkage682and support linkage684pair, the drive linkage682and the support linkage684connect to the throttle ring660at the same location. For example, the drive linkage682and the support linkage684in each pair is rotatably connect to the same radial shaft664of the throttle ring660. The drive linkage682is configured to transfer the movement from the drive ring680(e.g., rotation of the drive ring680) to the radial shaft664of the throttle ring664while the support linkage684is configured to limit/prevent rotation of the throttle ring660. In the illustrated embodiment, the interstage throttle630includes 4 pairs of the drive and supports linkages682,684. However, it should be appreciated that the interstage throttle630in an embodiment may include a different number of the linkages682,684. For example, the interstage throttle630in an embodiment may include three or more pairs of the linkages682,684. As shown inFIGS.9and10, the linkages682,684are configured so that the rotation of the drive ring680moves the throttle ring664in the axial direction with limited rotational movement. For example, the throttle ring664is configured to rotate less than 5 degrees between its fully retracted position to fully extend position. In an embodiment, the throttle ring664may be configured to rotate less than 3 degrees between its from its fully retracted position to its fully extend position. For example, the throttle ring664moves from its fully retracted position to its fully extended position when the actuator670is actuated moves from 0% extended to 100% extended, or from 100% extended to 0% extended. As shown inFIG.9, the throttle ring660includes teeth662that extend towards in the axial direction D1. For example, the teeth662can be the portion of the capacity control valve116that is moved into the interstage flow inFIGS.1B-1Cor the portion of the capacity control valve216that is moved into the interstage flow inFIGS.2B-2C. The compressor600also includes deswirl vanes (e.g., deswirl vanes112, deswirl vanes212, deswirl vanes406, deswirl vanes502, or the like) located between the first stage impeller (e.g., first stage impeller104, first stage impeller204, or the like) and the second stage impeller (e.g., second stage impeller118,218, or the like). The deswirl vanes may alternatively be referred to as guide vanes. The teeth662configured to intermesh with the guide vanes when in the extended position. In an embodiment, the teeth662can include one or more of the shape feature(s) described for the capacity control valve116inFIGS.1A-1D(e.g., leading end124, trailing end126, leading side130, trailing side132, curved surface134, tip136, and the like), and/or one of the more of the shape feature(s) of the capacity control valve216inFIGS.2A-2D(e.g., leading end224, trailing end226, leading side230, trailing side232, curved surface234, tip236, and the like). As shown inFIG.9, the teeth662of the throttle ring660are spaced apart from each other in the circumferential direction D3. A respective gap663is formed between each circumferentially adjacent pair of teeth662. Each gap is configured to accept a respective one of the guide vanes644(omitted inFIG.9) when the throttle ring660is in its extended position (e.g., seeFIG.12). FIGS.11and12are schematics diagrams illustrating the intermeshing of the throttle ring660and the guide vanes644. For example, the view inFIGS.11and12is a partial cross section extending in the circumferential direction along the teeth662of the throttle ring660and the guide vanes664. For example,FIG.11shows the throttle ring660in the retracted position (e.g., as shown inFIG.10).FIG.12shows the throttle ring660in the extended position (e.g., shown inFIG.9) As shown inFIG.11, channels646are formed by the guide vanes644. The channels646spiral extend radially inward (e.g., see the channels formed between each adjacent pair of deswirl vanes502inFIG.5). More specifically, the channels extend radially inward by spiraling radially inward. The compressed interstage fluid flows from the first stage impeller to the second stage impeller by flowing through the channels646. For example,FIGS.1B-1Dshow the tip136of the capacity control valve116disposed in one of the channels formed between the deswirl vanes112. The flow direction of interstage flow of the fluid from the first impeller stage to the second impeller stage would be into the page inFIGS.11and12. For example, radially inward is into the page inFIGS.11and12. The teeth662of the throttle ring660are spaced apart from each other in the circumferential direction D3. The guide vanes644are space apart from each other in the circumferential direction D3such that the channels646are spaced apart from each other in the circumferential direction D3. Each of the teeth662has a width W1in the circumferential direction that is smaller than the width W2of its respective channel646such that the teeth662fit into their respective channels646. The teeth662intermesh with the channels646when the throttle ring is in its extended position (e.g., as shown inFIG.12). Referring toFIG.11, the compressor600may include the guide vanes644as part of a guide flow plate640. The guide flow plate640can include a baseplate642and the guide vanes644being provided on the baseplate642. The guide vanes644provided on the baseplate642extend/swirl radially inward along the baseplate642(e.g., the deswirl vanes502provided on a baseplate inFIG.5in which the sectional view ofFIG.5removes a portion of the baseplate). Each of the channels646has a cross sectional area A1when the throttle ring660is in in its retracted position. The fluid flows through the channels646by passing through the cross-sectional area A1between the flow guide plate640and the tips664of the teeth662. In the illustrated embodiment, the teeth662of the throttle ring660are not disposed in the channels646when the throttle ring660is in its retracted position. However, it should be appreciated that the throttle ring660in an embodiment may be configured such that the ends of the teeth662remain in the channels646when in the retracted position. When actuated into the extended position as shown inFIG.12, the throttle ring660moves closer to the flow guide plate640in the axial direction D1and the teeth662are disposed in the channels646. The movement of the throttle ring660disposes a greater length L1of the teeth662in the channels646and moves the teeth662closer to the baseplate142of the flow guide plate640. The teeth662and channels646intermesh together in the extended position. Each tooth662is disposed in its respective channel646and between a respective adjacent pair (e.g., adjacent in the circumferential direction D3) of the guide vanes644. When moved to the extended position, the teeth662partially block the channels646and reduce the open height H of the channels. The blocking of the channels646reduces their open cross sectional area A2at the teeth662. This creates reduces a pressure drop for the fluid to flow through the smaller cross sectional area A2which reduces the flow rate of the fluid through the channels646(e.g., reduces the flowrate of fluid in the interstage flow). FIG.13is a cross-sectional view of the centrifugal compressor600as indicated inFIG.7. As shown inFIG.13, the compressor600includes the first stage S1, the second stage S2, and the interstage throttle630that connects the first stage S1to the second stage S2. The first stage S1includes the first stage impeller610A and the second stage S2includes the second stage impeller610A which rotate to compress the fluid in their respective stage S1, S2. The compressor600also includes a driveshaft612, a rotor614, and a stator616. The impellers610A,610B are each affixed to the driveshaft612. For example, the first stage impeller610A is affixed to an end of the driveshaft612while the second stage impeller610B is affixed closer to a middle of the shaft612. The rotor614is attached to the driveshaft612and is rotated by the stator616, which rotates driveshaft612and the impellers610A,610B. The rotor614and stator616form an electric motor of the compressor610. The electric motor (e.g., the stator616and the rotor614) operates according to generally known principles. In another embodiment, the driveshaft612may be connected to and rotated by an external electric motor, an internal combustion engine (e.g., a diesel engine or a gasoline engine), or the like. It is appreciated that in such embodiments that the rotor614and the stator616would not be present within the housing602of the compressor600. The driveshaft612extends through the first and second stages S1and S2as well as the interstage throttle630as shown inFIG.13. It should be appreciated that the terms “axial”, “radial”, and “circumferential” as used herein are generally with respect to the axis of the compressor600(e.g., the axis of the driveshaft612), unless specified otherwise. The flow path F1of working fluid through the compressor600is indicated in dashed arrows inFIG.13. The flow path F1extends from the suction inlet604to the discharge outlet606of the compressor600. The working fluid enters the compressor600through the suction inlet604, is compressed within the first stage S1by the first impeller610A, flows through the interstage throttle630to the second stage S2, is further compressed in the second stage S2by the second stage impeller610B, and is then discharged from the compressor600through the discharge outlet606. The first stage impeller610A in the first stage S1is configured to compress the working fluid from an inlet pressure (e.g., pressure P1) to a first pressure P1, and the second stage impeller610B in the second stage S2is configured to further compress the working fluid to a second pressure P2that is greater than the first pressure P1. As similarly discussed above, the side stream of intermediate pressure working fluid can flow (depending on the position of the throttle ring630) into the flow path F1between the first stage impeller610A and the second stage impeller610A. The pressure of the working fluid flowing into the inlet620of the second stage impeller610A may be different from the first pressure P1(e.g., can be a pressure between the pressure of the intermediate working fluid and the first pressure P1). In flow path F1, the interstage throttle630is disposed between the first stage impeller610A of the first stage S1and the second stage impeller610B of the second stage S2. The interstage throttle630is disposed between the outlet618of the first impeller S1and the inlet620of the second impeller610B. The driveshaft612extends through the interstage throttle630. The interstage throttle630fluidly connects the outlet618of the first stage impeller610A to the inlet620of the second stage impeller610B. The interstage throttle630directs the working fluid discharged from the first stage S1(e.g., the compressed working fluid at the first pressure P1) to the second stage impeller610B of the second stage S2. For example, the interstage throttle630directs the compressed working fluid (after being discharged radially outward from the first stage impeller610A) radially inward to the inlet620of the second stage impeller610B. The interstage throttle630also directs the intermediate pressure working fluid to the second stage impeller610B. For example, the interstage throttle630directs the intermediate pressure working fluid into the stream of compressed working fluid flowing from the first stage impeller610A to the second stage impeller610B, and then directs the mixture of intermediate pressure working fluid and compressed working fluid radially inward to the inlet620for the second stage impeller610A. The intermediate working fluid can mix with the compressed working fluid from the first stage impeller610A as the within the channels646. The interstage throttle630is adjustable to control the flowrate of the compressed working fluid flowing from the first stage S1to the second stage S2and the flowrate of the intermediate working fluid into the second stage S2(e.g., the flowrate of the intermediate working fluid into the compressor600). The interstage throttle630includes the actuator670for operating the interstage throttle630. The actuator670is operable/actuates to adjust the flowrate of the compressed working fluid flowing through the interstage throttle630. For example, a controller (not shown) of the compressor600and/or the HVACR controller may be configured to control the capacity of the compressor600by controlling the position/actuation of the actuator670. The interstage throttle630includes the flow guide plate640with the guide vanes644and the channels646formed by the guide vanes644. The channels646spiral radially inward as discussed above. As shown inFIG.13, the working fluid flows through interstage throttle630by flowing through the channels646. The channels646direct the working fluid discharged from the first stage S1radially inward to the inlet620of the second stage impeller610B. The interstage throttle630includes the throttle ring660configured to be actuated to adjust a size of the channels646(e.g., the cross-sectional area of the channels646). The throttle ring660includes the teeth662that extend towards the flow guide plate640. The throttle ring660is configured to be actuated in the axial direction (e.g., in the positive axial direction D1, in the negative axial direction D2) relative to the channels646. The axial movement of the throttle ring660changes the length of the teeth662disposed in the channels646to adjust the cross-sectional area of the channels646. For example, when the throttle ring660is actuated towards the channels646(e.g., in a positive axial direction D1), the teeth662extend further into the channels646and reduce the cross-sectional area of the channels646. As each tooth662is disposed further into its respective channel646, the tooth662partially blocks more of the channel646and decreases the cross-sectional area of the channel646(e.g., decreases the open cross-sectional area in each channel646). The decreased cross-sectional area of the channels646decreases the flowrate of the working fluid through the channels646and the interstage throttle630. When the throttle ring660is actuated away from the channels646(e.g., in the negative axial direction D2), the teeth662extend less into the channels646and the cross-sectional area of the channels646is increased, which increases the flow of the working fluid through the interstage throttle630. For example, the throttle ring660in an embodiment may have the retracted position in which the teeth662are disposed entirely outside of the channels646. FIG.14is a side view of another embodiment of a drive linkage782for connecting a drive ring780to a throttle ring760in an interstage throttle730. For example, the interstage throttle730may have features similar to the interstage throttle inFIGS.6and8except as described below. The throttle ring760is actuated by rotating the drive ring780. For example, the rotational axis of the drive ring780would extend vertically inFIG.14such that rotation of the drive ring780in the circumferential direction D3would cause the left side of the drive ring780to move into the page and the right side of the drive ring780to move out of the page. For example, an actuator and actuation linkage assembly similar to the actuator670and actuation linkage assembly672as described above can be used to drive the drive ring780to rotate. The rotation of the drive ring780causes the throttle ring760to move in the axial direction (e.g., positive axial direction D1).FIG.14shows the throttle ring760in its extended position. The throttle ring760is moved in the axial direction (e.g., opposite to the positive axial direction D1) by rotating the drive ring780in the opposite direction (e.g., opposite to the circumferential direction D3). In the illustrated embodiment, the drive linkage782is a slot in the drive ring780. A radial shaft764of the throttle ring760extends through the slot. The slot is angled between the axial direction D1and circumferential direction D3such that the rotation of drive ring780forces the radial shaft764to move axially within the slot which moves the throttle ring760in the axial direction D1. InFIG.14, the drive ring780has been rotated in a first direction (e.g., circumferential direction D3) to move the radial shaft764to the end of the slot closest to the throttle ring760(e.g., to move the throttle ring760to its extended position). The drive ring780is then rotated in the opposite direction (e.g., opposite to the circumferential direction D3inFIG.14) moving the radial shaft764in the opposite direction until reaching the end of the slot farthest from the throttle ring760(e.g., moving the throttle ring760to its retracted position). A respective drive linkage782(e.g., a respective slot in the drive ring780) can be provided for each radial shaft764of the throttle ring760as similarly discussed for the drive linkages inFIGS.8-10. In an embodiment, support linkages (e.g., support linkages184) can be provided for the radial shafts764on throttle ring760similar to the throttle ring660inFIGS.8-10such that the rotation of the throttle ring760when actuated in the axial direction is limited. For example, a support linkage is provided for the radial shaft764that limits/prevents the radial shaft764in the circumferential direction D3while allowing the radial shaft764to move axially within the slot when the drive ring780is rotated. FIG.15is a block diagram of an embodiment of a method1000of operating a centrifugal compressor. In an embodiment, the method1000may be applied to the centrifugal compressor600ofFIGS.6-13. The method starts at1010. At1010, fluid (e.g., working fluid) is compressed by and discharged from a first stage impeller of the compressor (e.g., first stage impeller104, first stage impeller204, first stage impeller610A). Compressing the fluid in the first stage1010can include rotating the first stage impeller. The rotating of the first impeller at1012compresses the fluid from an inlet pressure (e.g., inlet pressure PI) to a higher pressure (e.g., first pressure P1) and radially discharges the compressed fluid from the first stage impeller1012. The method1010then proceeds from1010to1020. At1020, the compressed fluid is directed from the outlet of the first stage impeller to the inlet of the second stage impeller of the compressor (e.g., second stage impeller118, second stage impeller218, second stage impeller610B) via channels (e.g., channels646) formed by guide vanes (e.g., deswirl vanes112, deswirl vanes212, deswirl vanes406, deswirl vanes502, guide vanes644). The compressed fluid flows from the first stage impeller to the second stage impeller by passing through the channels. The method1000then proceeds from1020to1030. At1030, a throttle ring is actuated to adjust a flow of the fluid in the interstage flow into the second stage impeller. Actuating the throttle ring at1030includes moving the throttle ring in an axial direction between a retracted position and an extended position by rotating a drive ring (e.g., drive ring680, drive ring780)1032. The rotation of the drive ring is configured to cause the throttle ring to move in the axial direction. The actuation of the throttle ring at1030also adjusts the flow of intermediate pressure working fluid into the inlet of the second stage impeller. For example, the actuation of the throttle ring at1030adjusts how much the of a side stream injection port from which the intermediate pressure working fluid flows (e.g., side stream injection port114, side stream injection port214) is blocked/obstructed by the throttle ring (e.g., seeFIGS.1A-2D). The moving of the throttle ring in the axial direction between a retracted position and an extended position at1032can include moving the throttle ring from the retracted position to the extend position1034and/or moving the throttle ring from the extended position to the retracted position1036. Moving the throttle ring from the retracted position to the extended position at1034moves teeth of the throttle ring (e.g., teeth662) in the axial direction into the channels (e.g., from outside of the channels into the channels, further into the channels, or the like). Moving the throttle ring from the extended position to the retracted position at1036withdraws the teeth of the throttle ring from the channels in the axial direction (e.g., partially withdraws the teeth from the channels, fully withdraws the teeth form the teeth, etc.). In an embodiment, moving the throttle ring from the extended position to the retracted position at1036includes moving the teeth along the axial direction into the side stream injection port. In an embodiment, moving the throttle ring between the retracted position and the extended position by rotating the drive ring at1032includes extending an actuator (e.g., actuator670) to rotate the drive ring in a first direction and retracting the actuator to rotate the drive in an opposite direction. It should be appreciated that the method1000in an embodiment may be modified to have features as discussed above for the centrifugal compressor100inFIGS.1A-1D, the centrifugal compressor inFIGS.2A-2D, the centrifugal compressor300inFIG.3, the centrifugal compressor400inFIG.4, the centrifugal compressor400inFIG.5, the centrifugal compressor600inFIGS.6-11, and/or the centrifugal compressor730inFIG.11. Aspects: It is understood that any of aspects 1-12 can be combined with any of aspects 13-34, any of aspects 13-19 can be combined with any of aspects 20-34, and any of aspects 20-30 can be combined with any of aspects 31-34. Aspect 1. A centrifugal compressor, comprising:a first stage impeller;a second stage impeller;a side stream injection port located between the first stage impeller and the second stage impeller, the side stream injection port configured to receive a side stream of a fluid; anda capacity control valve, the capacity control valve configured to extend and retract through the side stream injection port, wherein:the capacity control valve has a curved surface facing a direction of flow from the first stage impeller to the second stage impeller; andthe capacity control valve is configured to be extended through the side stream injection port between an open position where the side stream of the fluid can flow through the side stream injection port and a closed position where the capacity control valve obstructs flow of the side stream of the fluid through the side stream injection port. Aspect 2. The centrifugal compressor according to aspect 1, wherein the capacity control valve has a ring shape. Aspect 3. The centrifugal compressor according to any of aspects 1-2, comprising a plurality of the side stream injection ports and a plurality of the capacity control valves. Aspect 4. The centrifugal compressor according to any of aspects 1-3, wherein in the open position, a tip of the capacity control valve at an end of the curved surface is within the side stream injection port. Aspect 5. The centrifugal compressor according to any of aspects 1-4, wherein the capacity control valve extends and retracts in a direction substantially perpendicular to the direction of flow from the first stage impeller to the second stage impeller. Aspect 6. The centrifugal compressor according to any of aspects 1-5, further comprising one or more deswirl vanes between the first stage impeller and the second stage impeller. Aspect 7. The centrifugal compressor according to aspect 6, wherein the capacity control valve includes one or more notches, the one or more notches each configured to accommodate at least a portion of one of the one or more deswirl vanes. Aspect 8. The centrifugal compressor according to any of aspects 6-7, wherein the one or more deswirl vanes each include one or more notches, the one or more notches each configured to accommodate at least a portion of the capacity control valve. Aspect 9. The centrifugal compressor of any of aspects 1-8, wherein the capacity control valve has a linear meridional profile on a side opposite the curved surface, the linear meridional profile contacting an edge of the side stream injection port. Aspect 10. The centrifugal compressor of any of aspects 1-9, wherein a side of the capacity control valve opposite the curved surface is configured such that when the capacity control valve is between the open position and the closed position, the fluid can flow past the capacity control valve on the side of the capacity control valve opposite the curved surface. Aspect 11. The centrifugal compressor according to aspect 10, wherein the side of the capacity control valve opposite the curved surface includes a second curved surface. Aspect 12. The centrifugal compressor according to any of aspects 10-11, wherein the side of the capacity control valve opposite the curved surface includes one or more channels configured to allow flow of the side stream of the fluid. Aspect 13. A heating, ventilation, air conditioning, and refrigeration (HVACR) circuit, comprising:a centrifugal compressor;a condenser;an expander; andan evaporator,wherein the centrifugal compressor includes:a first stage impeller;a second stage impeller;a side stream injection port located between the first stage impeller and the second stage impeller, the side stream injection port configured to receive a side stream of a fluid; anda capacity control valve, the capacity control valve configured to extend and retract through the side stream injection port,the capacity control valve has a curved surface facing a direction of flow from the first stage impeller to the second stage impeller; andthe capacity control valve is configured to be extended through the side stream injection port between an open position where the side stream of the fluid can flow through the side stream injection port and a closed position where the capacity control valve obstructs flow of the side stream of the fluid through the side stream injection port. Aspect 14. The HVACR circuit according to aspect 13, wherein the side stream of the fluid is from the condenser to the side stream injection port. Aspect 15. The HVACR circuit according to aspect 13, further comprising an economizer and wherein the side stream of the fluid is from the economizer to the side stream injection port. Aspect 16. The HVACR circuit according to aspect 13, further comprising an intercooler and wherein the side stream of the fluid is from the intercooler to the side stream injection port. Aspect 17. The HVACR circuit according to any of aspects 13-16, wherein the capacity control valve has a ring shape. Aspect 18. The HVACR circuit according to any of aspects 13-17, wherein the capacity control valve has a linear meridional profile on a side opposite the curved surface, the linear meridional surface contacting an edge of the side stream injection port. Aspect 19. The HVACR circuit according to any of aspects 13-17, wherein a side of the capacity control valve opposite the curved surface is configured such that when the capacity control valve is between the open position and the closed position, the fluid can flow past the capacity control valve on the side of the capacity control valve opposite the curved surface. Aspect 20. A centrifugal compressor for compressing a fluid, comprising:a first stage impeller;a second stage impeller;a plurality of guide vanes forming channels located between the first stage impeller and the second stage impeller, the channels configured to direct an interstage flow of the fluid from the first stage impeller to the second stage impeller;a side stream injection port located between the first stage impeller and the second stage impeller, the side stream injection port configured to receive a side stream of the fluid; anda throttle ring configured to move through the side stream injection port between an extended position and a retracted position,a drive ring; andlinkage assemblies connecting the drive ring to the throttle ring such that rotation of drive ring moves the throttling ring in the axial direction between the retracted position and the extended position, whereinin the extended position, the throttle ring obstructs flow of the side stream of the fluid through the side stream injection port and partially obstructs the interstage flow of the fluid through the channels, andin the retracted position, the throttle ring allows the side stream of the fluid to flow through the side stream injection port. Aspect 21. The centrifugal compressor of Aspect 20, whereinthe throttle ring includes teeth, andin the extended position, the teeth of the throttle ring are disposed in and obstruct the channels. Aspect 22. The centrifugal compressor of Aspect 21, wherein the teeth extend in the axial direction and include tips that curve radially inward. Aspect 23. The centrifugal compressor of any one of Aspects 21 and 22, whereinin the retracted position, the teeth of the throttle ring are disposed in the side stream injection port. Aspect 24. The centrifugal compressor of any one of aspects 21-23, whereinthe teeth of the throttle ring obstruct less of the channels in the retracted position than in the extended position, andthe throttle ring obstructs more of the side stream injection port in the retracted position than in the extended position. Aspect 25. The centrifugal compressor of any one of aspects 21-24, whereinin the retracted position, the fluid in the side stream flows over the throttle ring into the side stream injection port, andin the extended position, the fluid in the interstage flow passing through the channels by flowing across the tips of the teeth. Aspect 26. The centrifugal compressor of any one of aspects 21-25, whereinin the retracted position, the throttle ring blocks the side stream injection port Aspect 27. The centrifugal compressor of claim1, wherein in the retracted position:the interstage flow of the fluid from the first stage impeller has a higher flowrate in the extended position, andthe side stream has a higher flowrate through the side stream injection port than in the extended position Aspect 28. The centrifugal compressor of any one of aspects 21-27, wherein the throttle ring includes radial shafts, each of the linkage assemblies include pairs of a drive linkage and a support linkage connected to the radial shafts of the throttle ring, the drive linkage and the support linkage in each of the pairs connected to the same respective one of the radial shafts on the throttle ring. Aspect 29. The centrifugal compressor of aspect 28, further comprising:a housing, the throttle ring, the drive ring, and the guide vanes disposed within the housing, whereinthe drive linkages connect the drive ring to the throttle ring, the drive linkages configured to transfer rotation of the drive ring into axial movement of the throttle ring, andthe support linkages connect the throttle ring to the housing, the support linkages configured to prevent rotation of the throttle ring. Aspect 30. The centrifugal compressor of any one of aspects 21-29, further comprising:an actuator and an actuation linkage assembly connecting the actuator to the drive ring, the actuator configured to extending causing the rotation of the drive ring and configured to retract causing an opposite rotation of the drive ring. Aspect 31. A method of operating a centrifugal compressor, the centrifugal compressor including a first stage impeller, a second stage impeller, and a plurality of guide vanes and a side stream injection port each respectively located between the first stage impeller and the second stage impeller, and the method comprising:compressing a fluid with the first stage impeller;directing, via channels formed by the plurality of guide vanes, an interstage flow of the fluid discharged from the first stage impeller to an inlet of the second stage impeller; andactuating a throttle ring to adjust a flow of the fluid in the interstage flow into the second stage impeller, the centrifugal compressor including the throttle ring, a drive ring, and linkage assemblies connecting the drive ring to the throttle ring, and the actuating of the throttle ring including:moving the throttle ring in an axial direction between a retracted position and an extended position by rotating the drive ring, the rotation of the drive ring causing the throttle ring to move in the axial direction, whereinin the extended position, flow of the side stream of the fluid through the side stream injection port is obstructed by the throttle ring and flow of the interstage fluid through the channels is obstructed by the throttle ring, andin the retracted position, the side stream of the fluid flows through the side stream injection port and into the inlet of the second stage impeller. Aspect 32. The method of aspect 31, whereinthe moving of the throttle ring in an axial direction between the retracted position and the extended position includes:moving the throttle ring from the retracted position to the extended position, which includes moving the teeth into the channels, andmoving the throttle ring from the extended position to the retracted position, which includes withdrawing the teeth from the channels. Aspect 33. The method of any one of aspects 31 and 32, whereinmoving the throttle ring from the extended position to the retracted position includes moving the teeth along the axial direction into the side stream injection port. Aspect 34. The method of any one of aspects 31-33, whereinthe centrifugal compressor includes an actuator and an actuation linkage assembly connecting the actuator to the drive ring, andthe moving of the throttle ring in the axial direction between the retracted position and the extended position by rotating the drive ring includes:extending the actuator to rotate the drive ring in a first direction, andretracting the actuator to rotate the drive ring in an opposite direction. The terminology used herein is intended to describe particular embodiments and is not intended to be limiting. The terms “a,” “an,” and “the” include the plural forms as well, unless clearly indicated otherwise. The terms “comprises” and/or “comprising,” when used in this Specification, specify the presence of the stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, and/or components. In an embodiment, “connected” and “connecting” as described herein can refer to being “directly connected” and “directly connecting”. With regard to the preceding description, it is to be understood that changes may be made in detail, especially in matters of the construction materials employed and the shape, size, and arrangement of parts without departing from the scope of the present disclosure. This Specification and the embodiments described are exemplary only, with the true scope and spirit of the disclosure being indicated by the claims that follow. | 81,437 |
11859622 | DETAILED DESCRIPTION OF ILLUSTRATED EXAMPLES The following description is provided in relation to several examples (most of which are illustrated, some of which may not) which may share common characteristics and features. It is to be understood that one or more features of any one example may be combinable with one or more features of the other examples. In addition, any single feature or combination of features in any example or examples may constitute patentable subject matter. In this specification, the word “comprising” is to be understood in its “open” sense, that is, in the sense of “including”, and thus not limited to its “closed” sense, that is the sense of “consisting only of”. A corresponding meaning is to be attributed to the corresponding words “comprise”, “comprised” and “comprises” where they appear. The term “air” will be taken to include breathable gases, for example air with supplemental oxygen. The subject headings used in the detailed description are included only for the ease of reference of the reader and should not be used to limit the subject matter found throughout the disclosure or the claims. The subject headings should not be used in construing the scope of the claims or the claim limitations. PAP System A PAP system (e.g., CPAP system) typically includes a PAP device (including a blower for generating air at positive pressure), an air delivery conduit (also referred to as a tube or tubing), and a patient interface. In use, the PAP device generates a supply of pressurized air (e.g., 2-30 cm H2O) that is delivered to the patient interface via the air delivery conduit. The patient interface or mask may have suitable configurations as is known in the art, e.g., full-face mask, nasal mask, oro-nasal mask, mouth mask, nasal prongs, nasal cannula, etc. Also, headgear may be utilized to comfortably support the patient interface in a desired position on the patient's face. Certain examples relate to PAP systems in which the PAP device or blower is adapted to be worn on the patient's head, is built into or incorporated into the patient interface or mask, is wearable or carried by the patient, is portable, is reduced in size or combinations thereof. In certain examples, the blower may be of the types described in International Application PCT/AU2010/001031, filed Aug. 11, 2010, entitled “Single Stage, Axial Symmetric Blower and Portable Ventilator,” and/or International Application PCT/AU2010/001106, filed Aug. 27, 2010, entitled “PAP system,” each of which is incorporated herein by reference in its entirety. For example,FIG.1illustrates a headworn PAP system10including PAP device or blower20, a patient interface or mask30(e.g., nasal mask), and an outlet tube40that interconnects the patient interface and the blower. Headgear50secures the blower and patient interface in position on the patient's head in use. However, the PAP system may be configured in other arrangements such as in or beside a pillow, in a scarf-like arrangement, incorporated into clothing, attached to a bed or bed head, etc., or in a more conventional PAP device configured to be located on a surface near a bedside similar to the ResMed™ S9™ CPAP system. In certain examples, the PAP system may be used as a hygiene device to purify the incoming air. A filter may be present at the air inlet of the device to filter out particulate matter or impurities in the incoming air to deliver purified or filtered air to the user. Blower FIGS.2to16illustrate a single-stage blower100according to an example of the present technology (e.g., blower100may be provided as blower20in the PAP system ofFIG.1). The blower provides an arrangement that is very small in size, low cost, compact, lightweight, and provides ease of assembly, e.g., for use in a small wearable PAP system. In an example, the blower may be structured to provide pressurized air up to about 8 cmH2O (e.g., a maximum of up to about 4-8 cmH2O, e.g., 4 cmH2O, 5 cmH2O, 6 cmH2O, 7 cmH2O, or 8 cmH2O), which may be suitable for mild forms of sleep apnea or for treatment of snoring) and be run at a speed of approximately 15,000 rpm and flow approximately 60-70 L/min. In another example, the blower may be structured to provide pressurized air at higher pressures such as about 1-25 cmH2O and higher flows above 70 L/min such as up to approximately 90-120 L/min. In another example, the blower may include a multiple stage design, e.g., two or more impellers. In such a multiple stage design, the blower may be capable of providing higher levels of pressurized air of about 1-30 cmH2O and higher flow rates of up to approximately 140 L/min. However, a skilled addressee would understand that other motor speeds, pressures and flows may be used. As illustrated, the blower100includes a housing or cover120with a top housing part or top cover122and a bottom housing part or bottom cover124, a bearing-housing structure130(also referred to as a central bearing structure), a motor140(including a stator assembly or stator component145, a magnet150, and a rotor cup or cap160) provided to the bearing-housing structure and adapted to drive a rotatable shaft or rotor170, and an impeller180coupled to the rotor cap160. The rotor cap160is coupled to an end portion of the rotor170and together with the magnet150may be referred to as the rotor assembly. In this arrangement, the motor has an outer rotor configuration to rotate the impeller180. This arrangement also allows the motor components to at least be partially nested within the impeller providing a lower profile blower. In an alternative arrangement, not shown, the motor may include an inner rotor configuration wherein the magnet150may be coupled to the rotor170and impeller180is coupled to an end portion of the shaft or rotor170. In such an arrangement, the impeller may be located above or around the motor components.FIG.99illustrates an internal rotor configuration in which the rotor cap160includes an inner wall160-1to support the magnet150within the stator component145supported by the bearing-housing structure130. The impeller180is coupled to the rotor cap160so it extends above or around the motor components. In a further alternative arrangement, as shown inFIG.100, the motor may include an axial gap motor wherein the stator component145(including stator and windings), magnet150and rotor cap160have a stacked or pancake configuration. However, it is to be understood that the motor may have any arrangement suitable to drive rotation using an electromagnetic interaction. Motor Assembly FIGS.3-5illustrate the assembled motor140within the blower100. The motor is structured such that the bearing-housing structure130provides a support for the other components of the motor as well as providing the bearing function to facilitate rotation of the rotor assembly. In the illustrated example, one end portion170(1) of the rotor170(e.g., metal or plastic) is rotatably supported within the bearing shaft136of the bearing-housing structure130and the other end portion170(2) of the rotor170is inserted freely into the rotor cap160, i.e., rotor not fastened to motor. The rotor cap160includes an opening162to receive the rotor170(e.g., seeFIGS.12and13). However, rotor retention designs may be incorporated into certain examples to retain the rotor and/or rotor assembly within the motor especially when the motor is not in use as described in more detail below. The hub185of the impeller180is provided along the exterior surface163of the rotor cap160, and the magnet150is provided along the interior surface165of the rotor cap160, for example by frictional engagement or by the use of an adhesive. The interior surface165may provide a recess or groove165(1) to receive the magnet150(e.g., seeFIG.13). In an alternative example, as shown inFIG.108, the rotor cap and the impeller may be integrally formed as a one-piece structure, e.g., rotor cap and impeller molded in one piece from a plastic material, e.g., Lexan®, polycarbonate (e.g., glass reinforced polycarbonate), Polyether ether ketone (PEEK) or other suitable materials. As illustrated, the one-piece structure includes a rotor cap portion360and an impeller portion380. A metal sleeve351and a magnet350are provided along the interior surface of the rotor cap portion360. The sleeve351provides a magnetic return or flux path between the poles of the magnet350. Another example of a one-piece rotor cap and impeller is described in U.S. Pat. No. 7,804,213, which is incorporated herein by reference in its entirety. In a further alternative example (not shown), the impeller may be overmolded onto the rotor cap. A diamond neural or other surface finish may be provided on the surface of the rotor cap to facilitate the fixturing or attachment of the overmolded impeller. The magnet150is coupled to the interior surface of the rotor cap160and is located to facilitate magnetic interaction with the stator assembly to drive the motor. The magnet may be made from any permanent magnet material such as a bonded NdFeB ring, a ferrite material, samarium cobalt or other such magnetic material. In certain examples, the magnet may be centered on the stator assembly. In another example, the magnet150may be off-set from the stator assembly to magnetically preload a thrust bearing portion of the bearing-housing structure130. In this arrangement, a pre-load spring may be not required for the bearing. Off-setting the magnet150may also assist with retaining the rotor assembly within the motor. The stator assembly145is coupled to the bearing-housing structure130to retain the stator assembly145in position. The stator assembly145may be coupled to the bearing-housing structure130by a snap-fit, over-molding, adhesively bonded, or other fastening means. The stator assembly or stator component145is provided along the exterior surface136(3) of the bearing shaft136of the bearing-housing structure130. In use, the stator assembly145acts on the magnet150which causes spinning movement of the rotor cap160and hence the impeller180. This arrangement at least partially “nests” the motor (stator assembly, fixed magnet and rotor cap) within the impeller to reduce the size of the blower. In an example, components of the motor are at least partially within a common (horizontal) plane. As shown inFIGS.17and18, the stator assembly145includes a stator core146having a plurality of stator teeth147, e.g., six stator teeth, on which stator coils or windings are wound. In the illustrated example, the stator core146includes a plurality of laminations, e.g. 2-100 laminations or more, that are stacked on top of one another. The laminations may be affixed to one another using adhesives or other techniques. The number of laminations may depend upon the power requirements of the motor. Alternatively, the stator core may have a different arrangement such as a solid member rather than a stack of laminations. The stator assembly145may also include a pair of slotliners, e.g., first and second slotliners148-1and148-2as shown inFIGS.17and18, structured to insulate the stator core146from the stator coils or windings. First and second slotliners148-1and148-2may be provided to opposite sides of the stator core146prior to winding the stator coils onto the stator core. The thickness of the slotliners may be controlled to facilitate the packing of more stator coil or winding into the stator. However, in an alternative arrangement, the stator core may be coated with a material, for example, by powder coating the stator core. In certain examples, the slotliners may include those described in the applicants pending U.S. patent application publication number US-2009-0324435, published Dec. 31, 2009, and entitled “Insulator for Stator Assembly of Brushless DC Motor,” which is incorporated herein by reference in its entirety. The stator coils or winding comprise magnet wire or motor wire such as copper wire, for example. In an example, the stator assembly may comprise three motor wires for a 3 phase motor, e.g., 2 coils per phase, 45 turns per coil, however other coil arrangements are possible. The different wires for each phase may each be identified by using a different color for each of the motor wires. The motor wires may be directly interfaced to a PCB coupled to the blower for ease of assembly. Further, the center tap and lead wires may be bonded to the housing to minimize loose motor wire entering into the air path. In an example arrangement, the motor wires may be routed through the stator vanes to a PCB assembly or driver as described below. The motor wires may be routed together and twisted for ease of wire egress. However, the motor wires may be routed out separately. The motor wire is wound onto the stator core. Rotor Retention In certain examples, one or more rotor retention designs or structures may be included to assist in retaining the rotor and/or rotor assembly within the motor especially when the motor is not in use. For example, one or more over-top rotor retention arms may be attached to the top cover and over the rotor assembly to prevent vertical movement of the rotor assembly.FIG.19shows an example an over-top retention arm202having one end202(1) attached to the top cover120, e.g., by a fastener, and the opposite end202(2) positioned over the rotor assembly (i.e., rotor cap160, magnet150, and rotor170). In another rotor retention example, the bearing-housing structure130may be coupled or interlocked to a mating feature in the rotor cap160. For example, as shown inFIGS.20and21, the bearing-housing structure130may comprise a slot or groove131on the thrust bearing surface136(2) configured to receive a lip or ridge161present on the mating feature of the rotor cap160. The lip or ridge161on the rotor cap160may snap-fit into the slot or groove131on the thrust bearing surface136(2). The mating feature may be incorporated at the lower surface surrounding the aperture162of the rotor cap160. The snap-fit design may also include radii, fillet and/or chamfers to assist with the connection. The ridge or lip may be provided around the entire circumference of the mating feature of the rotor cap160or may be limited to a plurality of discrete snaps, beads, or protrusions at locations around the mating surface, such as 2-10 snaps or protrusions or more. FIGS.22-27show alternative examples of mating features to couple the rotor cap to the bearing housing structure.FIG.22is similar to the arrangement ofFIGS.20and21in which the rotor cap160includes a lip or ridge161to engage within a slot or groove131provided to the bearing-housing structure130. InFIG.23, the rotor cap includes a bead161-1adapted to engage within a groove131-1provided to the bearing-housing structure130. InFIGS.22and23, the mating features engage along an inwardly facing surface of the bearing-housing structure, i.e., surface facing the rotor.FIGS.24and25show arrangements in which the mating features engage along an outwardly facing surface of the bearing-housing structure, i.e., surface facing away from the rotor. For example,FIG.24shows a rotor cap including a bead161-2adapted to engage within a groove131-2provided to the bearing-housing structure130, andFIG.25shows a rotor cap including a recess161-3adapted to engage with a bead131-3provided to the bearing-housing structure130.FIGS.26and27show an arrangement in which the rotor cap160includes a plurality of discrete beads161-4(e.g., 4 beads) adapted to engage within a groove131-4provided to the bearing-housing structure130. FIG.28shows another rotor retention example in which a lower flange, ridge or projection171is coupled to the bottom of the rotor or shaft170(e.g., constructed of stainless steel and press-fit to rotor) that is positioned underneath the bearing-housing structure130. The lower flange171prevents the rotor170from lifting vertically out of the motor assembly140. The lower flange may also provide an additional or alternative rotating surface for the rotor170. In certain examples including a pre-swirl cover as shown inFIG.29, as described in more detail below, the pre-swirl cover205may further include an axial shock bumper or stop205-1to prevent the rotor assembly (i.e., rotor cap160, magnet150, and rotor170) or rotor170from separating from the motor assembly in the case of a shock. For example, the bumper or stop205-1may prevent the rotor assembly from lifting off the bearing-housing structure's thrust bearing surface if the blower is dropped or bumped, especially when not in use. The bumper or stop is arranged above the rotor170in a manner that prevents the rotor and/or rotor assembly from lifting up and out of the motor assembly. The bumper or stop may include a ball, such as a steel ball, a flat surface or any other means that would maintain the rotor and rotor assembly in the correct position within the motor. In another rotor retention example, as shown inFIGS.30to32, complimentary screw threads161-5,131-5may be incorporated on the rotor cap160and the bearing thrust surface136(2) of the bearing-housing structure130, respectively. In such a design, the rotor assembly (i.e., rotor cap160, magnet150, and rotor170) must be screwed over the screw thread and fully engaged with the bearing thrust surface136(2) of the bearing-housing structure130before the rotor assembly may freely rotate. The screw threads would be configured in the same direction in which the rotor rotated to prevent the release or uncoupling of the rotor assembly in use. The rotor assembly may be removed by rotating or unscrewing the rotor assembly in the opposite direction to normal rotation.FIG.30shows the rotor assembly and bearing-housing structure before engagement,FIG.31shows the rotor assembly and bearing-housing structure partially engaged, andFIG.32shows the rotor assembly and bearing-housing structure fully engaged. Blower Housing The top cover122provides an inlet123at one end of the blower and the bottom cover124provides an outlet125at the other end of the blower. The blower is operable to draw a supply of gas into the housing through the inlet and provide a pressurized flow of gas at the outlet. The blower has axial symmetry with both the inlet and outlet aligned with an axis of the blower. In use, gas enters the blower axially at one end and leaves the blower axially at the other end. In another example, the blower may include an axial aligned inlet and an outlet that is tangential to the inlet. The top and bottom covers (e.g., constructed of a plastic material) may be attached to one another by fasteners, e.g., plurality of openings126provided along flange-like perimeter of covers122,124to allow fasteners to extend therethrough. In addition, the top and bottom covers may provide a joint128(e.g., tongue and groove arrangement as shown inFIGS.3and4) along its perimeter to facilitate alignment and connection. However, it should be appreciated that the covers may be attached to one another in other suitable manners, e.g., ultrasonic weld. As shown inFIGS.8and9, the bottom cover124includes a plurality of stator vanes or de-swirling vanes129, e.g., between about 2 and 50 stator vanes or about 15-30 or about 5-15, to direct airflow towards the outlet125, e.g., also referred to as flow straighteners. In the illustrated example, the bottom cover has 6 stator vanes. Each vane is substantially identical and has a generally spiral shape. In the illustrated example, the leading edge of each vane extends generally tangential to flow so as to collect air exiting the impeller and direct it from a generally tangential direction to a generally radial direction. In the illustrated example, the stator vanes support the bearing-housing structure130within the cover. In certain examples, one or more of the de-swirling vanes129may be structured as dual vanes that provide a passage to allow for the motor wires to be routed through the vanes and out to the PCB or driver. For example,FIGS.33to35show exemplary deswirling vanes129each including spaced apart side walls or dual vanes129-1,129-2that provide a space129-3therebetween. A cylindrical guide129-4is provided within the space that allows motor wires203(e.g., seeFIG.35) to be routed through the vane.FIG.33shows an example of a dual vane arrangement in relation to a single vane arrangement.FIG.8shows an example in which three of the deswirling vanes129include a dual vane configuration that provide passage for motor wires. In another example, only one or two of the deswirling vanes may include a dual vane structure for routing all motor wires. FIGS.101and102illustrate another example of a de-swirling vane arrangement for the bottom cover. In this example, the vanes include different thicknesses. For example, one of the vanes129.1is relatively thick while the remaining vanes129.2(e.g., remaining 5 vanes) are relatively thin with respect to the vane129.1. However, it should be appreciated that the thickness arrangement may have other suitable arrangements, e.g., same number of thick/thin vanes, more thin than thick vanes, more thick than thin vanes, all vanes have different thicknesses, etc. In certain examples, as shown inFIGS.28,29and36to38, the blower may also include a plurality of pre-swirl inlet vanes206located above the inlet123and above or on the top cover120. The plurality of inlet vanes206, e.g., between about 2 and 50 inlet vanes or about 15-30 or about 5-15, such as 5, 6, 7, 8, 9, 10, or 11 vanes, are structured to direct airflow towards the inlet123. Each inlet vane206is substantially identical and has a curved profile (e.g., seeFIG.37) to direct the airflow towards the inlet123. The inlet vanes are structured to pre-swirl the incoming air to facilitate a reduction in shock losses at the leading edge of the impeller blades. The inlet vanes may also assist in reducing the radiated noise from the inlet123. The inlet vanes may further assist in increasing the efficiency of the blower. In certain examples, the pre-swirl vanes are coupled to the outer surface of the top cover120. The pre-swirl vanes may be integrally molded into the top cover120or attached via gluing, ultrasonic welding, snap fit, adhesive or some other fastening means.FIGS.103and104show an example of pre-swirl vanes206integrally molded or otherwise attached to the top cover120. As shown inFIGS.28,29, and36to38, the pre-swirl vanes206are covered by a pre-swirl cover205structured to cover the pre-swirl vanes and form a plurality channels to direct the air flow towards the inlet123. The pre-swirl cover is coupled to the top edge of the pre-swirl vanes on the top cover120, e.g., by heat staking, ultrasonic welding, gluing, adhesive or other such fastening means.FIGS.105to107show the top cover120and vanes206ofFIGS.103and104with a pre-swirl cover205coupled to the vanes. The pre-swirl cover may be made from a plastic material, metal, aluminum or other suitable materials, for example the pre-swirl cover may be molded from a plastic material or formed by metal injection molding. The pre-swirl cover may be molded from or over-molded with a low durometer material such as a silicone or urethane, to provide a dampening function. In an alternative example, the pre-swirl vanes206may be integrally molded with the pre-swirl cover205and the top cover120is coupled to the bottom edge of the pre-swirl vanes206.FIG.38also shows a bumper or stop205-1on the pre-swirl cover205, as described above in relation toFIG.29. Inlet Cap In an example, an inlet cap may be provided to the inlet, e.g., to reduce noise. The inlet cap may be integrally formed in one-piece with the top cover. Alternatively, the inlet cap may be formed separately from the top cover and attached or otherwise provided to the inlet of the top cover. In an example, the inlet cap may be structured to support or otherwise retain a filter to filter the incoming air. For example,FIGS.116to119show a blower300including an inlet cap310provided to the inlet323of the top cover322according to an example of the present technology. The remaining components of the blower are similar to that shown inFIGS.109-110, which is described in greater detail below, e.g., blower includes a bearing-housing structure330structured to support a bearing cartridge390adapted to rotatably support the rotor370. As illustrated, the inlet cap310includes a generally disk-shaped inner portion312, a generally ring-shaped outer portion314, and radially extending spokes or connectors316that interconnect the inner and outer portions312,314. The outer portion314of the inlet cap310engages the annular side wall322(1) of the top cover322defining the inlet323to support the inlet cap310at the inlet323. The outer portion314overhangs the side wall322(1) to secure the inlet cap in position and align the inlet cap with the axis of the inlet. In an example, the inlet cap may engage the side wall with a press or friction fit, however, it should be appreciated that the inlet cap may be secured to the side wall in other suitable manners, e.g., adhesive, mechanical interlock (e.g., snap-fit), ultrasonic welding, etc. In use, the inner portion312is positioned to occlude or block a central portion of the inlet323and a supply of gas is drawn into the housing through the annular gaps315defined between the outer edge of the inner portion312and the inner edge of the outer portion314. In an example, the cross-sectional area provided by the gaps315(i.e., inlet area) is greater than about 150 mm2, e.g., about 150-300 mm2, 175-225 mm2, 200-250 mm2, 250-300 mm2. Such arrangement reduces noise, e.g., by reducing radiated noise from the inlet by reducing the effective inlet area, by reducing the Helmholtz resonance frequency. In the illustrated example, the inner portion312includes a diameter that is less than a diameter of the rotor cap360, e.g., diameter of inner portion312less than about 20 mm, e.g., 18 mm. However, it should be appreciated that in other examples the inner portion may include a diameter that is similar to or greater than a diameter of the rotor cap. In an example, as shown inFIG.124, the clearance A between the rotor cap360and inner portion312of the inlet cap310is substantially similar to the clearance A between the impeller380and top cover322, e.g., clearance A greater than 0.1 mm, e.g., greater than about 0.1 mm to 1.0 mm, such as between 0.3 mm and 0.5 mm, or between 0.35 mm to 0.4 mm, or greater than 0.381 mm, such as greater than about 0.381 mm to 1.0 mm. Also, in an example, as shown inFIG.124, the thickness B of the inner portion312of the inlet cap310is substantially similar to the thickness B of the top cover322. In the illustrated example, the inlet cap includes three spokes or connectors316, however it should be appreciated that more or less spokes may be provided, e.g., 2, 4, 5, 6 or more spokes. Also, it should be appreciated that the spokes or connectors may include other configurations and may be arranged in other suitable manners to interconnect the inner and outer portions312,314. For example,FIGS.120to123show inlet caps according to alternative examples of the present technology. InFIG.120, the inlet cap410includes a larger number of radially extending connectors416, e.g.,17connectors, than the inlet cap310described above interconnecting the inner and outer portions412,414. However, it should be appreciated that more or less connectors are possible. InFIG.121, the inlet cap510includes a plurality of connectors516, e.g.,10connectors, that extend tangentially from the inner portion512to interconnect the inner portion512with the outer portion514. Also, the connectors may be skewed or angled towards horizontal, e.g., to enhance noise reduction. InFIG.122, the connectors616, e.g.,7connectors, between the inner and outer portions612,614of the inlet cap610include a generally curved configuration. InFIG.123, the connectors716, e.g.,15connectors, between the inner and outer portions712,714of the inlet cap710are in the form of cylinders. It should be appreciated that the number of connectors416,516,616,716may be varied and the above numbers are only exemplary, thus more or less connectors416,516,616,716may be utilized, such as 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 16, 17, 18 or more connectors. Bearing-Housing Structure In an example, the blower does not require or use ball bearings to rotatably support the rotor. Rather, the bearing-housing structure130(rotatably supports the rotor170along with the rotor cap160and retains the stator assembly145of the motor140. The bearing-housing structure130may also comprise a shielding disk between the impeller blades and the stator vanes. The bearing-housing structure130is constructed of a lubricous material such as sintered bronze, an engineered plastic material, e.g., a polyamide-imide resin such as a Torlon™, and/or other very low friction materials or a combination of materials including a lubricous material or a material having a very low coefficient of friction. For example, a first material such as an aluminum, steel, brass, bronze or other metal or plastic may be coated with a lubricous material or material having a very low coefficient of friction such as a ceramic based or a nickel based coating material. In certain examples, the coating may be applied only to the critical wear surfaces of the bearing-housing such as the shaft receiving surface. Alternatively or additionally, the shaft may be coated with such materials to reduce friction. As shown inFIGS.10and11, the bearing-housing structure130includes a base132, an annular flange or disk134extending from the base, and a rotor or bearing shaft136that rotatably supports the rotor170. The bearing shaft136includes a radial or sleeve bearing portion136(1) and a thrust bearing portion136(2). The thrust bearing portion136(2) is at the top surface of the bearing-housing structure130surrounding the rotor170and adjacent the rotor cap160. The thrust bearing portion136(2) provides a thrust surface to allow the rotor cap to rotate. The radial bearing portion136(1) is configured as a sleeve bearing along the surface of the rotor and provides a radial surface along the rotor to facilitate rotation of the rotor170. The rotor may be polished to provide a desired surface finish at the rotor cap thrust surface. The surface finish may be attained using one or more techniques including grinding, diamond burnishing, lapping and polishing and/or chemical tumbling or any other surface generation techniques. The surface finish may be provided with a micro finish of between 3 micro-inches root mean square (RMS) to 40 micro-inches RMS, such as 3 micro-inches RMS to 32 micro-inches RMS, such as 8 micro-inches RMS to 16 micro-inches RMS. In certain examples, the surface finish may not be super highly polished as this may create some friction. Alternatively, the surfaces may be coated with a lubricous or very low coefficient of friction material as described above rather than being polished. The bearing shaft provides a single bearing incorporating both radial and thrust bearing properties which assists in reducing the height of the blower. A thrust load may be provided to the thrust bearing portion136(2) of the bearing-housing structure130. The thrust load is provided by the rotor cap160on a top surface or thrust surface136(2) of the bearing shaft in use. As there is only a single bearing, the motor only requires balancing in one plane and not two planes. The disk134of the bearing-housing structure provides support to the rotor. The outer edge134(1) of the disk134substantially aligns with or extends radially beyond the outer edge of the impeller180to prevent a line of sight between the tips of the impeller blades and the de-swirling vanes129. The outer edge134(1) of the disk134provides a shielding function to prevent blade pass tonal noise from being generated from the de-swirling vanes of the bottom cover124when the impeller spins in use. The disk134provides a narrow annular gap135, e.g., about 0.75 mm, between its outer edge and the side wall of the cover120, which is sufficient to allow enough gas to flow towards the outlet without significant loss in pressure and motor efficiency. In certain examples, the gap may be between 0.4 mm and 100 mm, e.g., between 0.4 mm and 2 mm, such as 0.5 mm, 0.75 mm, 1 mm or 1.5 mm. Also, the disk may include one or more openings for guiding the motor wire to outside of the air path, e.g., seeFIGS.28,29, and35showing motor wire203routed through opening144in disk134. In certain examples, the bearing-housing structure130may have a split configuration that is assembled from a separate disk component134and a separate bearing component136, e.g., also including the base132. In this split configuration, the disk component134and the bearing component132,136may be constructed of different materials. For example, the bearing component132,136may be constructed of a lubricous material as described above and the disk component134may be constructed of a plastic, polycarbonate or similar materials. The separate disk component134may be coupled to the bearing component132,136using a range of different coupling systems. The coupling system between the disk component134and the bearing component132,136may include one or more of the following systems: over molding one component onto the other component, e.g., over molding the disk component134onto the base132or vice versa; using a snap-fit or clip arrangement; using an interference fit; using a screw or bayonet connection; using an elastomeric component coupled between the disk component134and the base132such that no direct fastening of the disk component to the base132is required, the elastomeric component, e.g., TPE, may be over molded onto the end of the disk component, or the base32or both; or any other coupling system. One or more elastomeric or complaint components, such as TPE over molds or o-rings, may be included in any of the above coupling systems between the disk component134and the base132to reduce the transmission of vibration. For example,FIG.39shows an example of a separate disk component134coupled to a separate, cylindrical bearing component136, e.g., overmolded with one another. InFIG.40, the base132of the separate bearing component136is interlocked within a groove provided to the separate disk component134, e.g., to enhance connection between components. InFIGS.41and42, an o-ring138is provided between the separate disk component134and the separate bearing component132,136, e.g., to minimize vibration transmission. Also, one or more o-rings139may be provided between the bearing component132,136and the bottom cover124to minimize vibration transmission.FIG.45shows a separate bearing component132,136with an elastomer137overmolded along the edge of the base132. The separate disk component134(e.g., constructed of plastic) may be ultrasonically welded or heat staked to vanes129of the bottom cover124. In such split configuration examples, the plurality of stator vanes or de-swirling vanes129positioned below the disk component134may be either located on the disk component or on the bottom cover124as described above or both, such that some of the stator vanes129are located on the disk component134and some of the stator vanes129are located on the bottom cover124to provide the complete set of stator vanes129. The stator vanes129may be integrally formed or molded with the disk component134and/or the bottom cover124. For example,FIG.43shows a separate bearing component132,136overmolded with a separate disk component134, the disk component134including stator vanes129integrally formed or molded therewith. The bottom cover124supports the end portion of the vanes, e.g., end portion of vanes molded into the bottom cover. Such split configurations allow motor wires or stator wires to be routed out of the blower assembly between the disk134and base132, e.g., seeFIG.43showing motor wires203routed between disk component134and bearing component132,136and through an exit in the bottom cover124. The motor wires may be routed to an exit within the bottom cover and attached to a PCB Assembly or driver, e.g., seeFIG.44showing motor wires203routed through bottom cover124and to the PCB assembly or driver207. The motor wires may also be routed through at least some of the stator vanes129as described above. In certain examples, the PCB assembly or driver may be mounted to the bottom cover outside the air path, e.g., seeFIG.44in which PCB assembly or driver207mounted to exterior portion of the bottom cover124outside the air path. In other certain examples, the disk134may be a separate component that acts as a shield as described in U.S. Pat. No. 7,866,944 entitled “Compact low noise efficient blower for CPAP devices,” which is incorporated herein by reference in its entirety. The bearing-housing structure may be coupled to the bottom cover124to facilitate assembly of the blower. The bearing-housing structure130may be coupled to the bottom cover124at 2 or more positions, such as 3-6 positions or more. At least some of the stator vanes129on the bottom cover may be coupled to the disk134of the bearing-housing structure130. However, if the stator vanes are located on the disk134, at least some of the stator vanes129may be coupled to the bottom cover. The stator vanes129may be coupled to the disk134and/or the bottom cover by any means including one or more of the methods described below or combinations thereof or any other coupling method. In certain examples, at least some of the stator vanes129may be adhesively coupled to the disk134and/or bottom cover124, such as using a glue or double side tape. For example,FIG.46shows the disk134coupled to stator vanes129by double side tape208.FIG.47shows an example, in which the stator vanes129of the bottom cover124are overmolded TPE or hard plastic which may be adhesively bonded to the disk134. In other examples, the stator vanes129may be coupled to the disk134and/or bottom cover124by heat staking or ultrasonic welding. For example,FIG.29shows the bearing-housing structure130heat-staked onto the bottom cover124. In such example, the vanes129are overmolded with an elastomer129-5, e.g., to minimize vibrations. In other examples, the stator vanes129may be coupled to the disk134and/or bottom cover124using a press-fit arrangement wherein protrusions on an edge of the stator vanes are received within complementary apertures in the disk134or bottom cover124or vice versa in that the protrusions are on the disk134and/or bottom cover124and the complementary apertures are on the stator vanes129. Further examples may utilize a snap-fit, interference fit, clip or boss arrangement to couple the stator vanes129to the disk134and/or bottom cover124. The top or bottom edges of the stator vanes129may include an elastomeric material to minimize vibration transmission from the bearing housing structure134to the bottom cover124. The elastomeric material may be over-molded, adhesively attached, or inserted on to the edges of the stator vanes129. The elastomeric material, such as an o-ring, may be retained between the coupled stator vanes129and the disk134and/or bottom cover due to coupling means. For example,FIG.48illustrates an o-ring or TPE overmold139placed between the bearing housing structure130and the bottom cover124for vibration isolation. The bearing housing structure may be heat staked onto the bottom cover to retain the o-ring in position. In certain examples, the bearing-housing structure130may be coupled additionally or alternatively directly to the bottom cover124, i.e., not via the stator vanes129. In an example as shown inFIGS.49and50, the bearing-housing structure130may comprise a boss130-1that is engaged with a fastener209at the bottom cover124. As best shown inFIGS.50to52, the fastener209may include a plurality of teeth-like protrusions209-1that grip or bite into and retain the boss130-1. The teeth-like protrusions may be angled to allow ease of insertion of the boss in one direction but prevent or hinder release of the boss in the opposing direction. The fastener may be a separate component that is inserted through the bottom cover to couple the bottom cover124and housing-bearing structure130. Alternatively, the boss may be located on the bottom cover124and the fastener on the bearing-housing structure130. In another arrangement, as shown inFIG.53, the boss130-1may be integrated with the bearing housing structure130and configured to press-fit into the bottom cover124until at least a portion of some of the stator vanes129contact the disk134of the bearing housing structure130. A fastener210, such as a Tinnerman clip, pal nut, speed nut, push nut or other fastener, may secure the bearing housing structure to the bottom cover.FIG.54shows another example of the bearing housing structure130secured to the bottom cover124by a fastener210, e.g., Tinnerman clip. In this example, the bearing bore or through hole133in the bearing housing structure in the area of the bottom cover (i.e., lower portion of bore133) may be slightly larger in diameter as compared to area of the bearing sleeve or rotor support (i.e., upper portion of bore133that supports rotor170) to minimize compressive shrink due to press fit of fastener, e.g., Tinnerman clip. In other certain examples, the boss of the bearing-housing structure130may comprise a protrusion including one or more lips that are configured to engage with a fastener at the bottom cover124. The fastener may have one or more mating grooves adapted to receive the lip(s) in a snap fit arrangement. Alternatively, the protrusion may be located on the bottom cover124and the fastener on the bearing-housing structure130. Other fasteners that may be used include Tinnerman clips, pal nuts, speed nuts, push nuts and other such fasteners. In other examples, the base132of the bearing-housing structure130may be directly coupled to the bottom cover124via a snap feature that snaps into a groove. The snap feature may be located on the bottom cover124and the groove on the bearing-housing structure130or vice versa. For example,FIG.55shows a bottom cover124including a snap feature211structured to snap into a groove provided on the bearing housing structure130to attach the bottom cover the bearing housing structure.FIGS.56to65show alternative examples of snap features211for attaching the bottom cover124to the bearing housing structure130. In certain examples, as shown inFIG.66, the bottom cover124may be coupled to the bearing-housing structure130using a screw arrangement. A central screw212may be inserted via the outlet125through a portion of the bottom cover124and into a threaded anchor213provided to the bearing-housing structure130(e.g., anchor integrally molded or bored). The screw212may be inserted into an anchor portion124-1of the bottom cover124which further comprises at least one arm124-2that extends upwards towards the disk134of the bearing-housing structure130to provide support. The at least one arm124-2may be configured to couple with the disk134, e.g., interlocking engagement. This may facilitate dampening the bottom cover by clamping. Optionally, the screw may be sealed over after assembly to prevent the screw from falling out or being removed or tampered with. The screw may seal the bottom of the bearing spindle and assist in preventing air flow therethrough and any bearing grease or lubricant from drying out. Bearing grease or lubricant may be added to the bearing spindle prior to installing the screw.FIG.67shows another example of the bottom cover124coupled to the bearing-housing structure130by a central screw212. In certain examples, the screw arrangement may be integrated into the bottom cover124and/or the bearing-housing structure130. For example, as shown inFIG.68, the bearing-housing structure130may be configured to comprise a threaded screw portion212-1(e.g., male screw portion) at the end of the bearing shaft136that is received within a corresponding threaded screw receiving portion212-2(e.g., female screw portion) in the bottom cover124. Alternatively, the male screw portion may be located on the bottom cover124and the female screw portion on the bearing-housing structure130. The screw portions allow the bearing-housing structure and the bottom cover to be screwed together. Bearing grease or lubricant is used to assist in stabilizing the rotor assembly in the bearing-housing structure. Thus, means of retaining the lubricant may be incorporated within the motor assembly. As shown inFIG.69, a lubricant reservoir215may be built into the bearing shaft136of the bearing-housing structure130that is designed to supply the lubricant to the bearing thrust surface136(2). A supply of lubricant may be fed to the reservoir215via an aperture216through the bearing-housing structure. The bearing shaft136may include one or more recessed channels217(e.g., seeFIG.70), e.g., 3-10 channels, 4-8 channels, 4-6 channels, 4, 5, or 6 channels, etc., along the bearing thrust surface136(2) to focus pressure points at the top and/or bottom of the bearing shaft136. The recessed channel(s) assist in retaining the lubricant at the rotating surface. FIGS.71to74illustrate an example of a bearing-housing structure130including a lubricant reservoir215within the bearing shaft136. In an example, as shown inFIG.73, the lubricant reservoir215may be substantially centrally located within the bearing shaft136, e.g., d1and d2about 1.5 to 3.0 mm, e.g., about 2.25 mm. In an example, as shown inFIG.73, the depth d3of the reservoir is about 0.05 to 0.1 mm, e.g., about 0.08 mm or about 0.003 inches. FIGS.75to79illustrate an example of a bearing-housing structure130including one or more recessed channels217(also referred to as lands) along the bearing thrust surface136(2) of the bearing shaft136to assist in retaining lubricant at the rotating surface. In an example, as shown inFIGS.77and78, the length d1of each channel is about 0.5 to 1.0 mm, e.g., 0.8 mm, the width d2of each channel is about 0.2 to 0.6 mm, e.g., 0.4 mm, the radius of curvature d3is about 0.2 mm, the depth d4is about 0.01 to 0.05 mm, e.g., 0.025 mm (about 0.001 inches), and the radius of curvature d5is about 0.0155 inches. However, it should be appreciated that other suitable dimensions for the channels are possible. For example, the dimensions may be selected to adjust the hydrodynamic pressure provided by the channels, e.g.,FIG.80shows channels217each having a width of about 0.016 inches andFIG.81shows channels217each having a smaller width of about 0.011 inches. FIGS.82and83schematically illustrate the hydrodynamic pressure concentration (outlined in dashed lines) created by the channels217between the bearing shaft136and the rotor cap160in use. FIGS.84to89illustrate an example of a bearing-housing structure130including an annular recessed channel217along the bearing thrust surface136(2) of the bearing shaft136to assist in retaining lubricant at the rotating surface. In an example, as shown inFIG.88, the depth d1of the channel is about 0.01 to 0.04 mm, e.g., 0.025 mm, the radius of curvature d2is about 0.3 to 0.5 mm, e.g., about 0.4 mm, d3is about 1.5 to 2 mm, e.g., about 1.9 mm, and d4is about 0.25 to 0.5 mm, e.g., about 0.4 mm. Preferably, the bearing shaft or sleeve has a trilobe configuration rather than a circular configuration. For example,FIG.90shows an example of a bearing shaft with a trilobe configuration with respect to the rotor170in use. Each “lobe” increases the fluid dynamic or hydrodynamic pressure. In an example, the depth d1of each lobe is about 0.0001 to 0.0005 inches. In certain examples, as shown inFIG.91, a retaining ring218, such as an acorn shaped grooveless retaining ring, may be coupled to the bottom of the bearing shaft136to assist in retaining the lubricant around the bearing-housing structure130. In certain examples, as shown inFIG.92, the bearing-housing structure130may be closed at one end, such as the lower end130.1, of the radial bearing portion136(1) to retain the lubricant within the bearing shaft. The grease or lubricant may include a Kyoto Ushi Multem or other such lubricants. Alternatively, the bearing may be a dry bearing, i.e., the bearing-housing and/or rotating components are formed at least in part or coated with a low friction material such as a low coefficient of friction material, e.g., a ceramic based coating, a nickel based coating, Teflon™ or graphite, that provides lubricity and eliminates the requirement for a grease or lubricant. Bearing Cartridge In an alternative example, as shown inFIGS.109-110and125-127, the bearing shaft of the bearing-housing structure may be replaced with a bearing cartridge390including bearings394,395adapted to rotatably support the rotor370. As illustrated, the bearing cartridge390includes a tubular sleeve or cartridge392, two spaced-apart bearings394,395supported within the sleeve392, and a spacer396(which may be optional) between the bearings to provide a preload (e.g., direction of preload shown by arrows a1and a2inFIG.112). Each bearing394,395includes an outer race engaged with the interior surface of the sleeve392and an inner race engaged with the rotor370, e.g., bonded using an adhesive.FIG.112is an isolated view of the bearing cartridge390. In this example, the bearing-housing structure330(e.g., injection molded of plastic material) includes a housing part providing a base332and an annular flange or disk334extending from the base332. The base332provides a tube portion333that supports an end of the bearing cartridge390, e.g., an exterior surface of the sleeve392of the bearing cartridge390is bonded in the tube portion333, e.g., using adhesive. Also, the stator component345is provided (e.g., bonded using an adhesive) along the exterior surface of the sleeve392. InFIGS.109and110, the tube portion333is open ended and provides a flange333(1) along the opening to provide a stop surface for supporting the bearing cartridge390within the tube portion333. In an example, such opening at the bottom of the tube portion may be capped or sealed off. In an alternative example, as shown inFIG.111, the bottom of the tube portion333may be closed by an integral lower wall333(2) to provide the stop surface for supporting the bearing cartridge390within the tube portion333. In this example, as shown in109,126, and127, stator vanes329of the bearing-housing structure330provide tabs329(1) that are adapted to engage within respective openings324(1) in the bottom cover324(e.g., with a snap-fit, heatstake) to retain and align the bearing-housing structure330with respect to the bottom cover324. The top cover322may be secured to the bottom cover324, e.g., by adhesive or ultrasonic welding or using other known methods. As described above, the rotor cap160(supporting the magnet150and impeller180) is provided to the end portion370(2) of the rotor370. In an example, the magnet may be centered on the stator assembly to remove magnetic preload or thrust from the rotor cap to the bearing cartridge. In an example, the rotor cap160may be provided to the rotor370(e.g., press-fit) in a first assembly operation, and then the rotor370(with the rotor cap attached thereto) may be provided to the bearing cartridge390in a second assembly operation. Such assembly may impart less damage to the bearings of the bearing cartridge. In an alternative example, the bearing cartridge may include a single bearing adapted to cooperate with another bearing supported in the housing for rotatably supporting the rotor. In another alternative example, an air bearing arrangement may be provided to support the rotor. Tangential Outlet In an example, the blower may include an axial aligned inlet and an outlet that is tangential to the inlet or tangential to the direction of rotation of the impeller. For example,FIGS.128to131show a blower800including a top cover822providing an inlet823and a bottom cover824providing an outlet825that is tangential to the inlet823. Similar to examples described above, the blower includes a bearing-housing structure830structured to support a bearing cartridge890adapted to rotatably support the rotor870. The rotor cap860(supporting the magnet850and impeller880) is provided to an end portion of the rotor870. In this example, the bearing-housing structure830includes an annular side wall835that extends downwardly from an end portion of the disk834. The free end of the side wall835provides tabs835(1) that are adapted to engage within respective openings in the bottom cover824(e.g., with a snap-fit, heat stake, ultrasonic weld) to retain and align the bearing-housing structure830with respect to the bottom cover824. The side wall835along with the covers822,824define a volute837for directing air towards the outlet825. In this example, the volute837expands in cross-sectional area towards the outlet to generate pressure via static regain. The side wall835and bottom cover824also provide an open space839out of the air flow path, e.g., for electronic components such as a PCB or driver. FIGS.132-138show another example of a blower including an outlet that is tangential to the inlet. In this example, the blower900includes a bearing-housing structure that is incorporated into or otherwise provided by the blower housing920. As illustrated, the blower housing920includes a top cover922providing an inlet923and a bottom cover924that cooperates with the top cover922to provide an outlet925that is tangential to the inlet923. The bottom cover924is also structured to support the bearing cartridge990and define the volute937for directing air towards the outlet925. Specifically, the bottom cover924includes a base932providing a tube portion933that supports the bearing cartridge990and an annular flange or disk934that curves upwardly and then extends radially outwardly from the base932. An annular side wall935extends downwardly from an edge of the disk934to define the volute937. The rotor cap960(supporting the magnet950and impeller980) is provided to an end portion of the rotor970rotatably supported by the bearing cartridge990. In this example, the volute937expands in cross-sectional area towards the outlet to generate pressure via static regain, e.g., seeFIG.136. In the illustrated example, the volute includes a generally semi-circular cross-section configuration, e.g., seeFIGS.137and138, however other suitable volute shapes are possible. FIGS.139to142show another example of a blower including an outlet that is tangential to the inlet. The blower1000includes housing1020having a top cover1022and a bottom cover1024. The top cover1022provides the inlet1023and also provides the outlet1025that is tangential to the inlet1023. In this example, a chimney or inlet tube portion1027is provided to the inlet1023. A bearing-housing structure or stationary component1030is provided to the housing1020and is structured to support a bearing cartridge1090and define a volute1039for directing air towards the outlet1025. The bearing-housing structure1030includes a tube portion1033that supports the bearing cartridge1090, outwardly and upwardly extending wall portions1035,1036that defines a recess to receive motor components, an annular flange or disk1034, and a downwardly and outwardly extending end portion1037extending from the disk. The tube portion1033supports an end of the bearing cartridge1090, e.g., an exterior surface of the sleeve1092of the bearing cartridge1090is bonded in the tube portion1033, e.g., using adhesive. Also, the stator component1045is provided (e.g., bonded using an adhesive) along the exterior surface of the sleeve1092. A rotor cap1060(supporting the magnet1050and impeller1080) is provided to the rotor1070rotatably supported by bearings1094,1095within the bearing cartridge1090. In this example, the magnet1050is provided along an interior surface of the rotor cap1060and a peg or pin1061is provided to the upper wall of the rotor cap to retain the impeller1080. In the illustrated example, the peg1061provides a diameter (e.g., 3-5 mm, e.g., 4 mm) that is larger than a diameter of the rotor1070(e.g., 1-3 mm, e.g., 2 mm). The recess provided by the outwardly and upwardly extending wall portions1035,1036of the bearing-housing structure1030allow the rotor cap, magnet and stator component to at least be partially nested within the bearing housing structure to provide a lower profile blower. The top cover1022cooperates with the bearing-housing structure1030to define the volute1039that directs air towards the outlet1025. As illustrated, the top cover1022includes a cylindrical, separating wall or baffle1022(1) and together with the stepped configuration of the end portion1037separate the volute1039into two regions, i.e., a high speed airpath region1070(1) and a low speed airpath region1070(2), e.g., to minimize pressure pulsations and/or acoustic noise. A seal1095(e.g., constructed of silicone rubber or other suitable material) may be provided between the bearing-housing structure1030and the top and bottom covers1022,1024, e.g., to provide a seal along the volute, support a PCB, and/or provide wire grommet for guiding PCB wires. Further details and examples of aspects of the blower1000, e.g., high speed and low speed airpath regions, are disclosed in PCT Publication No. WO 2011/062633, which is incorporated herein by reference in its entirety. FIG.148shows another blower example similar to that shown inFIGS.139to142. In contrast, the bottom cover1024of the blower1000provides a tube portion1024(1) supports an end of the bearing cartridge1090. In this example, the bearing-housing structure1030includes a central opening that allows the rotor cap1060, magnet1050and stator component1045to at least be partially nested within the bearing housing structure.FIGS.149and150show such blower1000mounted within the casing1012of a PAP device1015according to an example of the present technology. As illustrated, the inlet1013and outlet1014are provided on opposite ends of the casing, FIGS.143-147and151show alternative examples of blowers including an outlet that is tangential to the inlet. InFIG.143, the impeller1180is supported along the upper wall of the rotor cap1160. The rotor cap1160(also supporting magnet1150) is provided to the rotor1170rotatably supported by the bearing cartridge1190. In this example, the housing1120includes a tube portion1133that supports the bearing cartridge1190. The stator component1145is provided along the exterior surface of the bearing cartridge1190. A stationary component1130is provided within the housing1120to provide a disk1134(e.g., to prevent blade pass tonal noise) and define the volute for directing air towards the outlet1125. InFIG.144, the bearing-housing structure1230is integrated with the stator component1245of the motor, e.g., by overmolding, to form a one-piece structure. The bearing-housing structure1230provides a tube portion1233that supports bearings1295that rotatably support the rotor1270. The rotor cap1260is provided to one end of the rotor1270and supports magnet1250in an operative position with respect to the stator component1245integrated with the bearing-housing structure1230. The impeller1280is provided to the opposite end of the rotor1270. InFIG.145, the bottom cover1324of the housing is structured to define the volute1339for directing air towards the outlet1325. The bottom cover1324also supports the bearing-housing structure1330including a tube portion1333that supports the bearing cartridge1390and a disk1334. The stator component1345is provided along the exterior surface of the bearing cartridge1390. The rotor cap1360(supporting magnet1350) is provided to one end of the rotor1370and the impeller1380is provided to the opposite end of the rotor1370. FIGS.146and147show alternative examples of a bearing-housing structure1430including one or more walls defining the volute1439for directing air towards the outlet1425. Similar to examples described above, the impeller1480is provided along the upper wall of the rotor cap1460, and the motor components (e.g., rotor cap, magnet and stator component) are at least partially nested within the bearing housing structure. InFIG.151, the housing1520provides a generally annular-shaped inlet1523and an outlet1525that is tangential to the inlet. The inner housing part1529supports the bearing cartridge1590adapted to rotatably support the rotor1570. The rotor cap1560(supporting the magnet1550and impeller1580) is provided to an end portion of the rotor1570. The stator component1545is provided along the exterior surface of the bearing cartridge1590. In an example, the gap A between the impeller1580and an upper part of the housing1520and the gap A between the impeller1580/rotor cap1560and a lower part of the housing1520is about 0.75 to 1.0 mm. Impeller In the illustrated example, as shown inFIGS.14and15, the impeller180(also referred to as a double-shrouded impeller or alternating-shroud impeller) includes a plurality of continuously curved or straight blades182sandwiched between a pair of disk-like shrouds184,186. As illustrated, the blades curve in towards the hub having an S-like shape. The shape is designed to reduce vortex shedding. Also, the shrouds may not fully cover the top and bottom surfaces of the blades. The lower shroud186incorporates the hub185that is adapted to receive the rotor cup160, e.g., press-fit. Also, the impeller includes a tapered configuration wherein the blades taper towards the outer edge. In an example, the impeller may be constructed of a plastic material, e.g., Lexan®. Further details of impellers are disclosed in WO 2007/048206 A1, which is incorporated herein by reference in its entirety. In certain examples, the impeller blades182may be curved in a generally clockwise direction. In an alternative example, the impeller blades182may be curved in a generally counter-clockwise direction. In an alternative example, as shown inFIGS.93and94, a bottom shrouded impeller (i.e., bottom surface of blades182covered by a lower shroud186) may be used, e.g., to help prevent impeller lifting off the shaft or rotor in use.FIG.93illustrates an example of the S-like shape of the blades182. The slight S-shape at the beginning of each blade is a result of having the blades attach to the hub and not block the inflow. As shown inFIGS.95and96, the leading edges182(1) of the impeller blades182may have a sweptback configuration in that the leading edges of the impeller blades are slanted or angled back inwards in the opposite direction of the flow. This configuration provides a longer blade length providing higher pressures, reduces drag at the impeller leading edge and/or causing streamwise vortices to be formed in the flow path which can delay the flow separation, thus reducing drag and flow oscillations and increased efficiency. In an example, the blade height at the leading edge may increase at an angle of about 10-50°, e.g., 20°, along the length of the blade to a point about ¼ of the length of the vane. Alternatively, as shown inFIGS.97and98, the impeller blades182may have a leading edge182(1) that is normal to the flow direction as in conventional impellers. It should be appreciated that the blade and vane angles may be selected for different conditions and/or performance optimizations. The impeller may have a rotor portion integrated therein. The rotor portion is configured to interact with the magnet by serving as a path for the magnetic flux to cause rotation of the impeller through interaction with the stator. The rotor component of the impeller may be a single-piece construction or it may be formed as an cylindrical insert of magnetic steel within a non-ferrous structure of plastic or other non-magnetic material that could be the impeller itself; such an insert could be attached by various methods including overmolding, an interference press fit, or adhesive bonding. The insert or ring of ferrous material would retain the impeller on the stator in use. In an example, there is no fastening of the impeller to the stator—the impeller180and rotor cap160are retained by a magnetic attraction between the magnet150(coupled to the interior surface of the rotor cap) and the stator assembly145. FIGS.113to115show impellers according to alternative examples of the present technology. InFIG.113, the impeller480includes a larger number of blades482than examples disclosed above, e.g., 22 blades, to reduce noise by reducing tonal frequencies. However, it should be appreciated that more or less blades are possible. Also, each blade482includes a curved configuration and is curved in a generally clock-wise direction, e.g., to reduce broadband and tonal noise. However, as shown inFIG.114, the blades482of the impeller480may be curved in the opposite direction, i.e., curved in a generally counter-clock-wise direction.FIG.115shows another example of an impeller480including 11 blades482with each blade curved in a generally counter-clock-wise direction. InFIGS.113and114, every other blade includes a top edge482(1) along its length that tapers towards the outer edge. The remaining blades inFIGS.113and114include a top edge482(2) that gradually increases in height from the hub before tapering towards the outer edge. InFIG.115, all the blades include a top edge482(1) along its length that tapers towards the outer edge. However, it should be appreciated that other blade configurations are possible. FIG.113shows a rotor cap460along with rotor470provided to the hub485of the impeller480, e.g., with a press-fit. Exemplary Dimensions In an example, as shown inFIG.16, D1may be about 50-70 or more, about 60-65 mm, e.g., about 62.8 mm, D2may be about 8-13 mm or more, e.g., about 10.4 mm, D3may be about 15-20 mm or more, e.g., about 18.4 mm, D4may be about 15-25 mm or more, e.g., about 23.2 mm, D5may be about 20-30 mm, e.g., about 27 mm, and D6may be about 20-25 mm, e.g., about 21 mm. It is to be understood that these dimensions and ranges are merely exemplary and other dimensions and ranges are possible depending on application. For example, ranges that vary from those provided +/−10% or more may be suitable for particular applications. PAP Systems Certain examples relate to PAP systems that comprise a blower as described herein. In certain examples, the blower may be mounted on the patient's head (e.g., on the crown of the patient's head or on the front portion of a patient's head), patient's arm, chest, or other body part, in or beside a pillow, in a scarf-like arrangement, incorporated into clothing, attached to a bed or bed head, etc. However, the PAP system may utilize the blower described herein in a more conventional PAP delivery device, e.g., of the type that includes a chassis or enclosure that is intended to rest on the user's bedside table. While the present disclosure has been described in connection with certain examples, it is to be understood that the present disclosure is not to be limited to the disclosed examples, but on the contrary, is intended to cover various modifications and equivalent arrangements. For example, while the blower has been described in relation to an axial blower, the blower could also be configured as a tangential blower. Furthermore, the blower is described for use in a headworn PAP system, but it could also be used in conjunction with a more conventional PAP system that includes a separate flow generator that is not mounted on the user's head or body. Also, the various examples described herein may be implemented in conjunction with other examples, e.g., aspects of one example may be combined with aspects of another example to realize yet other examples. Further, each independent feature or component of any given assembly may constitute an additional example. In addition, while the present disclosure has particular application to patients who suffer from OSA, it is to be appreciated that patients who suffer from other illnesses (e.g., congestive heart failure, diabetes, morbid obesity, stroke, bariatric surgery, etc, or combinations thereof) may derive benefit from the teachings of this disclosure. Moreover, the teachings of this disclosure have applicability with patients and non-patients alike in non-medical applications. | 68,369 |
11859623 | DETAILED DESCRIPTION The described embodiments are by way of example only. The scope of this disclosure is limited only by the claims. Although the concepts of this disclosure can be applied to any electric motors, they will be described, by way of example, in relation to a propulsion motor for driving a propulsive element e.g. a propeller or a fan. Air cooling will be described first with respect toFIG.1. Shown inFIG.1is a typical electric motor10comprising a stator1and a rotor2, separated by an air gap3, and mounted in a housing4, for rotating a shaft5. Windings6are provided on the stator1. Rotation of the rotor2relative to the stator1generates power to rotate the shaft5. A propulsive element e.g. a propeller or fan7is mounted to the shaft for rotation with the shaft. Heat is generated by the operation of the motor and this needs to be dissipated to avoid overheating or damage to the components. As mentioned above, various cooling mechanisms are known. In the system ofFIG.1, cooling fins8are provided on the outer surface of the housing4and air9is caused to flow across the cooling fins8to cool the motor10. Different sources of air can be used to provide the cooling air. In the example shown, the propulsive air flow, i.e. the air flow through the propeller or fan is employed as cooling air9. As mentioned above, although such systems are lightweight and compact and simple, the cooling effect that can be provided by air is not sufficient to effectively cool high power density motors. The solution provided by this disclosure involves improving the performance of air cooled systems by mixing water to the cooling air. Water has a significantly higher specific heat coefficient than air for similar flow conditions thus providing an improved cooling effect. This will be described by way of example with reference toFIGS.2and3. FIG.2shows a propulsive motor100driving a propeller or fan70by means of a shaft50, caused to rotate due to the operation of the motor100. As with the system shown inFIG.1, electric motor100comprising a stator11and a rotor12, separated by an air gap13, and mounted in a housing14, for rotating a shaft15. Windings16are provided on the stator11. Rotation of the rotor12relative to the stator11generates power to rotate the shaft15. A propulsive element e.g. a propeller or fan70is mounted to the shaft for rotation with the shaft. Heat is generated by the operation of the motor and this needs to be dissipated to avoid overheating or damage to the components. As mentioned above, the concept of this disclosure that will be further described below will also be applicable to different electric motor structures including, but not limited to motors with an inner stator and an outer rotor, different permanent magnet or synchronous machines etc. The concepts are also not limited to use with propulsion machines and can be used to cool any type of motor or machine. Air30is directed towards the motor100. In the most general form of the disclosure, the air can be provided from any air supply but in the preferred example, as shown, the air30comes from the propulsive air flow of the propulsive element70and is directed towards the motor from the propulsive element70as shown. To improve the cooling, water is mixed with the air as it is provided to the motor so that motor is cooled by an air/water mix. The water is preferably provided to the air as a fine mist or spray. In a preferred example, as shown, the water is provided from a water tank31that may be provided in proximity with or more remotely from the motor. The water can be directed from the tank, e.g. via a pump32or other means for conveying the water, via a water supply pipe33and is then passed through one or more nozzles34to a location relative to the motor where it is mixed with air to cool the motor. Preferably, the nozzles are formed in the motor housing14and several nozzles can be distributed around the housing as shown best inFIG.3. The housing14may be provided with grooves or channels35to distribute the water to the nozzles34. To increase efficiency, the water may be provided from the tank31to the nozzles34via a pump32that pressurises the water supply system. In a most efficient example, the pump32can be driven by the engine shaft15and can be housed within the motor housing, thus reducing the need for external components. Using nozzles to provide the added water in the form of a mist provides a more improved cooling effect as the smaller droplets will evaporate quickly. The evaporation cooling effect means that the cooling system can perform up to five times better than known air cooling systems, depending on the size of the water droplets. It should be possible to determine an optimum droplet size. Although a water tank or reservoir31is needed, which will add some volume and weight to the overall system, the volume of water required will be relatively small especially as the water is provided in the form of a fine mist and so for the benefit provided overall, the additional structure is not significant. The volume of water required can be further reduced in a preferred embodiment where water is only added to the cooling air at specific times/flight conditions. For example, the system may be arranged to only use water/air cooling at times when the motor requires high output power e.g. during take-off. At other times of flight, air cooling alone might be sufficient. Various ways of controlling the operation of the pump32have been considered by the inventors. The pump and/or the nozzles may be controlled based on e.g. rotation of the shaft15so that water is only used at certain times. Whilst water is known to cause corrosion, this, again, should not be a major concern with this system since the water mixed with the cooling air would be evaporated quickly from the hot surfaces of the motor. The windings16could be impregnated and/or potted to protect from the water and the stator core could be provided with a protective coating if needed. The cooling system of this disclosure has the advantage that a motor can be thermally sized as an air cooled machine usually used for lower power requirements but its thermal performance can be boosted by the improved cooling effect. The disclosure provides a system which provides effective cooling and allows electric motors to have high power density without the need for a liquid cooling system including e.g. heat exchangers and other large and heavy components. The system can also be used as a means to significantly enhance the overload capability of air cooled motors. In the preferred embodiment, the propulsive air flow itself can be used to contribute to the cooling. | 6,699 |
11859624 | DETAILED DESCRIPTION OF THE INVENTION Embodiments of the present invention may comprise a combination of a fan and LED light fixture.FIGS.1and2show side sectional views of an embodiment of the present invention depicting a troffer shelf12.FIG.3shows a perspective view of an embodiment having a troffer shelf. The combination fan10may include a troffer shelf12which supports at least one LED light fixture20and a fan30. The fan30is supported by a louvered fan support18. As shown inFIG.3, the louvered fan support18has a lower solid portion19and an upper open portion17that includes several opening and louvers60which direct air from the fan chamber13along the troffer shelf12. It is not material to the present invention where the solid portion19and open portion17is located in the fan support18. What is important is that there is a solid portion19of the fan support18that braces the fan30, and an open portion17that is configured to permit air to flow from the fan chamber13to the troffer chamber16. The direction of the air flow is not necessarily important to the present invention. What is important is that the fan30causes air to flow in the vicinity of an LED light fixture20. The troffer shelf12may have the same general dimensions as a ceiling tile typically 1 ft.×2 ft., 2 ft.×2 ft. or 2 ft.×4 ft. The LED light fixture20is typically positioned along the troffer chamber16along the troffer shelf12such that light from the fixture20is not interrupted by the fan30. The LED light fixture may include an LED lamp22. The LED light fixture20is preferably in the form of a strip which runs the length of the troffer shelf12. The LED light fixture20is secured to the troffer shelf12in such a manner to permit air to flow along a substantial portion of the surface area of the LED lamp22and light fixture20. The LED light fixture20may include a magnetic attachment mechanism to secure the light fixture20to the troffer shelf12. The magnetic attachment mechanism serves multiple purposes including the ability to detach the LED light fixture20from the troffer shelf12in a relatively easy fashion. The magnetic attachment mechanism further serves to provide a space between the LED light fixture20and troffer shelf12for air to flow through which increases the surface area of the LED light fixture20that contacts the air. The greater the surface area of the LED light fixture20that comes in contact with the air flow, the faster and more efficient the temperature reduction of the LED light fixture. While LED light fixtures are discussed throughout this disclosure, it is understood that other types of lights may be utilized in the invention and benefit from the features of the invention. The fan30preferably includes at least an axial fan as shown inFIG.12. Referring back toFIGS.1,2and3, there may be more than one fan within the fan area13. The blades32of the fan30force air to move parallel to a shaft34about which the blades32rotate. Air flow40moves axially through the intake of the fan36and axially out through the outlet38of the fan30. The flow of air is generally linear trough the intake36and the outlet38. The design of the fan30is a function of the blade configuration32that creates a pressure of differential that produces airflow40across the fan blade32. The fan30may consist of anywhere from 2 to 8 blades. The fan30is connected to a motor51and typically operates at high speeds. The typical speed of the axial fan of the present invention operates between 1800 to 4000 RPM to produce airflow in the range of 85 to 150 cubic feet per minute. While an axial fan is disclosed in the figures of the invention, it is understood that other types of fans such as a bladeless fan, cross-flow fan, or impeller-type fan may be used as the fan30in the embodiments shown in the figures. Any of those types of fans can be utilized without having a detrimental effect on the function and features of the invention. The important feature of the fan30is to move and distributes air within the fan area, regardless of the type of fan that was used. As shown inFIG.2, the configuration of the troffer shelf12directs the flow of air from the outlet38of the fan30. Air flows along the troffer shelf12and the troffer baffle14, along the LED light fixture20. Air passing along the LED light fixture20acts to dissipate heat produced by the LED light fixture20which reduces the operating temperature of the LED light fixture20. In essence, the air flow reduces waste heat produced by the LED fixture20by conducting the heat away from the fixture20. It is believed that the airflow in the current invention can reduce the temperature of the LED light fixture from approximately 120° F. to approximately 80° F. in the typical environment found in offices, hospitals, retail stores, educational institutions and the like. FIGS.1,2and3depict a combination LED light fixture and fan10. The air exiting the outlet38of the fan30is propelled into the fan chamber13. The air in the fan chamber13as shown inFIG.3, is directed by a diversion mechanism50so that the air flows through openings17in the fan support18. The air flowing through the opening17is directed by louvres60into the light chamber16, along the troffer shelf12, to engage the LED light fixture20. By directing air from the fan20along the troffer shelf12causes the air to circulate around the LED light fixture20to reduce the temperature of the light fixture20. The air flow in the lighting chamber16is directed by the troffer baffle14through an exit vent84formed by the damper81. In embodiments of the present invention, there may be a vent and lens bracket80. The bracket80is affixed to the troffer shelf12in such a manner to permit air to flow from the light chamber16through an exit vent84formed by a damper81in the bracket80. The vent84permits the air heated by LED light fixture20to exit the light chamber16. The bracket80also includes a lens bracket82. The lens bracket82corresponds with a fan lens bracket83to secure a lens90in place within the combination LED light and fan10. The lens90provides a solid surface to assist with containing any air from the fan30such that it proceeds along the troffer shelf12and the troffer baffle14to the LED light fixture20and through the vent84. A lens90is not necessary to the invention. However, the lens90typically made of a somewhat flexible translucent plastic material. There is a mounting mechanism100that is used to affix the combination LED light fixture and fan to an adjacent ceiling tile or bracket. Some embodiments of the present invention may incorporate the use of color displayed by the lighting system to affect the environment in which the combination LED light and fan fixture10may be implemented. Research has shown that different colors appear to affect behavioral traits in humans. For example, the color yellow is believed to influence a person's self-confidence; the color red is believed to influence a person's physical body, the color blue is believed to influence a person's mind and the color green is believed to influence a person's emotional balance. It is believed that, for example, the combination of a yellow color with a blue color will stimulate a person's emotional balance and mind. The different color combinations may be incorporated into the present invention in numerous ways. In one embodiment of the present invention, the colors blue, red, yellow or green may be applied to the internal surface of the troffer shelf12and/or the troffer baffle14by means of paint, insert or other known technique. Alternatively, the lens90may comprise of the colors blue, red, yellow or green. The colored lens90operates to transmit light of the lens color in an indoor space. Finally, the LED light fixture20itself may be configured to generate light in the blue, red, yellow or green spectrums by means of the LED lamp22. The air exiting from the fan cavity16is directed along an airflow surface on the troffer shelf12and troffer baffles14air may alternatively be directed through a cooling chamber, which is not shown but functions to cool the fan components, as well as, the LED lighting components. The internal surface of the troffer shelf12and troffer baffles14may be coated with a Miro-Micro Matt wet paint produced by Alanod. The paint helps to maintain airflow along the surface, as well as, maintain a clean dust-free surface. The airflow40has two general components. The air that exits the fan cavity13generally has a laminar flow along the airflow surface of the troffer shelf12. As the flow of air from the fan30extends towards the exterior perimeter of the troffer shelf12and troffer baffles14through the vent84, the flow becomes more turbulent and mixes with the surrounding air. The preferred direction of the air-flow is such that the intake36of the fan30draws air from the lower portion of a space and distributes the air along the upper portion of the space. Air along the lower portion of an area tends to be cooler than air that resides at the upper portion of an area. The cooler air is pulled into the fan30and distributed from the cavity is used to cool and clean the LED light fixture20, and/or the LED light bulb22. The combination fan of the present invention may utilize the stepped-fan blade design depicted in the pending patent application Ser. No. 14/814,161, 15/043,923 and 15/346,913, each of which is hereby incorporated by reference, in the entirety. The benefits of the stepped-blade design are set-forth in detail in the pending patent applications referenced herein and need not be repeated in this provisional application and are not shown in the drawings. The stepped-fan blade design greatly improves the air flow characteristics of the fan30. As shown inFIGS.9,9(a),10and10(a), the fan intake36may include decorative perforations and/or a grill39. The grills39may be of a circular configuration as shown inFIGS.9and9(a). Alternatively, the grill may extend the length of the fan intake36as shown inFIGS.10and10(a). The air intake36may also include a filter (not shown). Alternatively, the filter may be positioned at the air outlet38or at a grill covering the combination fan39. The filter serves to clean air flowing through the fan of dust and other fine particles. The filters may be removed for cleaning or replacement on a periodic basis. The embodiments shown inFIGS.10and10(a) are more adapted to accommodate a filter. In some embodiments of the inventions, the combination fan and LED light system further includes an air diversion mechanism50. The air diversion mechanism50is positioned within the cavity of the fan chamber13. The physical configuration of the air diversion mechanism50is such that it directs air exiting the fan outlet38through the louvered openings17or diffuser in the louvered fan holder18. In some embodiments, the air diversion mechanism50is in the shape of a prism as shown inFIGS.1through7. Alternatively, the air diversion mechanism50may be in the shape of a pyramid (FIG.8), cone, pentagon, triangle or other suitable shape to divert air from the fan chamber13, through the openings17and into the troffer chamber16along the LED light fixture20. The air diversion mechanism directs air towards opening17along louvered vents60positioned along the inside fan chamber13. The vents17may include louvres60to assist in directing the air in the desired direction. Positioned within the air diversion mechanism50is a ballast housing51for LED lighting ballast, drivers and wires. The ballast housing51houses the wiring for both the LED lighting system and the fan to allow for a single hook-up to the electrical outlets or connections positioned within the ceiling. The air exiting from the fan cavity13is directed along an airflow troffer shelf12to the troffer baffle14. Air may alternatively be directed through a cooling chamber, which is not shown, but functions to cool the components located in the ballast housing51, as well as, the LED lighting components. As shown inFIG.2, air40enters the fan30and is expelled by the fan blades32into the air chamber13. Air flow in the fan chamber is generally laminar. Air is forced into the air chamber13and is directed by a louvre60through an opening in the fan chamber13into the light chamber16. The air (shown in arrows) has generally a laminar flow along the troffer shelf12and troffer baffle14. As the flow of air from the fan30extends towards the exterior perimeter of the housing in the vent84, the flow becomes more turbulent and mixes with the surrounding air such that the air exiting through the damper81is more turbulent in nature. The preferred direction of the air-flow is such that the intake36of the fan30draws air from the lower portion of a space and distributes the air along the upper portion of the space. Air along the lower portion of an area tends to be cooler than air that resides at the upper portion of an area. The cooler air is pulled into the fan30and distributed from the cavity is used to cool and clean the LED light fixture20, the LED cover24and/or the LED light bulb22. In an alternative embodiment, the direction of the airflow may be reversed. Turning toFIGS.4,5,6and7, refer to alternative embodiments to the embodiment ofFIGS.1,2and3. An alternative embodiment comprises a combination of a fan and LED light fixture.FIGS.4,5,6and7show views of different embodiments of the present invention. FIG.4depicts an alternative design of the troffer shelf and the troffer baffle14. In the alternative design, air is propelled from the fan30into the fan chamber13. The air from the fan30is deflected by a diversion mechanism50, through the opening17and directed by louvres60into the light chamber16. The louvres60are configured to direct the air from the fan along the troffer shelf12and along the troffer baffles14. By directing air from the fan30along the troffer shelf12causes the air to circulate along LED light fixtures20. The air flow helps to reduce the temperature of the LED light fixture20. The air flow is directed by the troffer baffle14through an exit vent84formed by the damper81, in the lens bracket80. InFIG.4, the troffer shelf12has more of a squared-shape. The troffer shelf12and the troffer baffle14intersect at generally right angles to each other. The fan30is positioned in generally the same position as demonstrated inFIG.3. The fan chamber13includes a diverter50to direct air exiting the fan30through the open portion17of the fan chamber13. Louvers60direct the air passing through the open portion17of the fan chamber30into the light chamber16. Air flows along the troffer shelf12and the troffer baffle14passed the LED light fixture20. Air passing along the light fixture passes along the plurality of LED light fixture20to dissipate the heat in the LED light fixture20. The air follows a path along the air baffle through the vent84out of the light chamber16. The bracket80includes a damper81and lens bracket82. The embodiment includes a lens90which acts to diffuse the light emitted from the LED lights20. There is a mounting mechanism100used to affix the combination LED light fixture and fan to an adjacent ceiling tile or bracket. The interior surface of the troffer shelf12and troffer baffle114may be coated with a Miro-Micro Matt wet paint produced by Alanod. The paint helps to maintain airflow along the surface, as well as, maintain a clean dust-free surface. The paint can be applied in any of the colors discussed above to affect the environment. As shown inFIGS.5and6, the combination fan110includes a housing112which supports at least one LED light fixture120and a fan130. The housing is the same dimensions as a ceiling tile typically 2 ft.×2 ft. or 2 ft.×4 ft. The LED light fixture120is preferably positioned along the periphery of the housing112such that light from the fixture120is not interrupted by the fan130. The LED light fixture includes an LED light bulb122. The alternative embodiments of the combination LED light fixture and fan110utilize an internal baffle114. The internal baffle114serves to direct air within the troffer cavity116and provide support for the LED lighting120. The embodiments depicted inFIGS.5and6include a fan130that directs air through a fan exit138in the fan chamber113. The fan chamber113includes an air diverter150which may take on many different shapes, such as a prism shown inFIG.5or a trapezoidal shape shown inFIG.6. Air from the fan chamber113is directed by the diverter150through the open portion117of the fan support118. The air flowing through the open portion117of the fan support118is directed by louvres160. As shown inFIG.6, the air is directed by the louvres160into the baffle chamber116along the baffle114across the LED light120. The air passing across the LED light120is directed by the baffle114through the exit vent184. InFIG.5, the baffle114guides air flowing through the openings117in the fan chamber113(which is directed by the baffles) along the LED light fixture120. The air serves to reduce the temperature of the LED light fixture120and extend the life of the fixture120. The baffle114guides the air flow from the LED light fixture120through the exit vent184. The fan130preferably includes an axial fan. The blades132of the axial fan force air to move parallel to a shaft134about which the blades132rotate. The flow of air140is axially through the intake of the fan136and axially out through the outlet138of the fan130. The flow of air is linear trough the intake136and the outlet138. The design of the fan130is a function of the blade configuration132that creates a pressure of differential that produces airflow140across the fan blade132. The axial fan130may consist of anywhere from 2 to 8 blades. The axial fan130is connected to an energy source (not shown) and typically operates at high speeds. The typical speed of the axial fan of the present invention operates between 1800 to 4000 RPM to produce airflow in the range of 85 to 150 cubic feet per minute. The combination fan of the present invention may utilize the stepped-fan blade design depicted in the pending patent applications referenced above. The fan intake136ofFIGS.5and6may include decorative perforations and/or a grill as shown inFIGS.9and10. The air intake136may also include a filter (not shown). Alternatively, the filter may be positioned at the air outlet138or at a screen covering the combination fan142. The filter serves to clean air flowing through the fan of dust and other fine particles. One embodiment of the combination fan and LED light system110further includes an air diversion mechanism150. The air diversion mechanism150is positioned within the fan chamber113of the fan130. Looking atFIG.14, the air diversion mechanism150is in the shape of a prism as shown inFIGS.5,6and13. Alternatively, the air diversion mechanism150may be in the shape of a pyramid (FIG.14), cone, pentagon, triangle or other suitable shape to divert air to the LED components and into the office space. The air diversion mechanism150directs air towards vents117positioned along the fan cavity113. The vents117may include louvres160to assist in directing the air in the desired direction. Additionally, the air diversion mechanism may have vents to permit a portion of the air circulated by the fan to enter the diversion mechanism150to provide a cooling effect on the ballast housing151. The air exiting from the fan cavity116is directed along an airflow surface on the troffer baffle114air may alternatively be directed through a cooling chamber, which is not shown but functions to cool the fan components, as well as, the LED lighting components. The internal surface of the troffer baffle114is preferably coated with a Miro-Micro Matt wet paint produced by Alanod. The paint helps to maintain airflow along the surface, as well as, maintain a clean dust-free surface. The airflow140has two general components. The air that exits the fan cavity113generally has a laminar flow along the airflow surface of the lower housing portion114. As the flow of air from the fan130extends towards the exterior perimeter of the housing112through the vent184, the flow becomes more turbulent and mixes with the surrounding air. The preferred direction of the air-flow is such that the intake136of the fan130draws air from the lower portion of a space and distributes the air along the upper portion of the space. Air along the lower portion of an area tends to be cooler than air that resides at the upper portion of an area. The cooler air is pulled into the fan130and distributed from the cavity is used to cool and clean the LED light fixture120, and/or the LED light bulb122. An embodiment of the combination LED light fixture and fan200in which the LED light fixtures220are directed toward the ceiling is depicted inFIGS.7and8. The combination LED light fixture and fan200inFIG.7includes a fan220. The fan230may include an invented axial fan, or any fan that serves the purpose of distributing air in a relatively quiet fashion. The fan230includes an air inlet236and air exit238. There is a fan chamber216. Air is drawn from the indoor environment, through the air inlet236and propelled by the fan through the fan exit238into the fan chamber213. There is a diverter250positioned within the fan chamber213to direct air from the fan through an open portion117of the fan support218. The open portion217may include louvers260to guide the air from the fan chamber213into a troffer cavity216. The combination LED light fixture and fan210has a domed shell292. While a domed-shaped shell292is shown in some embodiments, any shaped shell may be utilized and still practice the invention. The shell292serves as a troffer. The shell292is configured to direct air from the troffer cavity216along the LED light fixtures220and through the exit vent284. A lens290is positioned on top of the shell292. The LED light fixtures220may be configured to direct light upward toward the ceiling or downward toward the shell292. The shell292may be made of a solid material or alternatively a translucent material to permit light to penetrate the shell292into the room. The combination LED light fixture and fan220is supported from the ceiling by one or more mounting cables294. The mounting cables294may be configured to accommodate power cables to supply power to the fan230and LED light fixtures220. The combination LED light fixture and fan as shown in all the embodiments of the present invention may use a hard-wired control mechanism to control both the light20and fan30. The invention may use an ethernet connection and remote control to activate the fan30and LED light fixture20. Alternatively, a wi-fi (wireless) connection may be used in connection with a remote control to control the LED light20and fan30. The remote control feature is configured to adjust the intensity (or color) of the LED light fixture20and the speed of the fan30. The embodiments of the inventions shown inFIGS.1through7show a fan that is independent from the HVAC system of the building in which the combination LED lighting fixture and fan10may be installed. However, it is contemplated that the combination LED lighting fixture and fan10may be combined with the existing HVAC system in order to distribute the air from the HVAC system through fan chamber13and through the light chamber16. The combination LED lighting fixture and fan10may be the primary source of distribution of the air from the HVAC system or it could be use in a supplemental capacity. If the HVAC system is implemented in connection with the combination LED light fixture and fan20, the HVAC system could be connected to the combination LED light fixture and fan10at several locations. For example, the HVAC system could be configured to delivery air from the HVAC system into the fan chamber13or the light chamber16by connecting a duct from the HVAC system to either the fan chamber13or the troffer cavity. The fan30of combination LED light fixture and fan10provides a supplemental air delivery system to augment the HVAC system. As shown inFIGS.11and11(a), the combination fan may include two or more fans30. In the multiple fan configuration, it is beneficial that adjacent fans rotate in different directions to provide a more even distribution of air along the fan30. It is important to note that the adjacent fans rotate in opposite directions. As shown inFIG.11(a), the multiple fans may all rotate in the same direction. FIG.12depicts a fan30and130that may be used in embodiments of the inventions. Various aspects of this disclosure may include components which are implemented directly into a ceiling grid, or ceiling tile, as seen for example inFIG.15. It is contemplated that an exemplary ceiling tile1501may be sized as 1′×4′; 2′×2′; or 2′×4′, although a person of skill in the art would understand that any appropriately sized ceiling tile may be used in accordance with the present inventions. Moreover, ceiling tile1501could be acoustical, fiber, wood, metal, translucent, plastic, sheet rock, or drywall structures as are known to be used in industrial, commercial, or residential environments. In embodiments of the inventions, ceiling tile1501may have one or more fans1502and vents1503cut into the ceiling tile1501, sometimes referred to herein as a ceiling panel. Panel cuts may be made or manufactured using waterjet cutting, die cutting, laser cutting, CNC routing, CNC knife cutting, reciprocated knife cutting, or any other known techniques for cutting through tiles. Vents1503may take the form of elongated slot(s) extending near the edge of ceiling tile1501, although other shapes are also contemplated. For example,FIG.15shows two elongated vents on the ceiling tile1501's top edge, and two additional vents along the bottom edge. A person of skill in the art would understand that additional arrangements are contemplated. Optional LED strips1504may be included, and may extend between the one or more fans1502and vents1503. As seen inFIG.16A, which is a cut-away side view of embodiments of the inventions, an upper baffle1610and one or more lower baffles1620,1621, may act together to define one or more airway(s). For example, air may pass from a fan1502, along airway(s)1630,1631(e.g. a first airway to the left and a second airway to the right), to vents1503. Upper baffle1610may comprise an apex portion1615which is formed in close proximity to fan(s)1502and/or1503. Embodiments in which an apex portion1615extends into proximity with fan(s)1502and/or1503provide the advantage of improved airflow: that is because apex portion1615forces air to split evenly towards the left and right side. In the absence of apex portion1615, the direction of rotation of fan(s)1502and/or1503may lead to uneven air distribution. The apex portion1615performs a similar function to air diversion mechanism50described above. Indeed, a person of skill in the art would recognize that the air diversion mechanism50(See e.g.FIG.1) may be included in the embodiment ofFIG.16. Preferably, fan(s)1502take in air, which is released out through vents1503. In such an arrangement, fan(s)1502act as an air intake and vents1503act as an exhaust. A person of skill in the art would recognize that it is also possible for fan(s)1502and/or1503to be configured to act as an exhaust, rather than an intake. In embodiments where LED strips are included, the flow of air through airways1630and1631may act to cool the LED strips1504. Where two or more fans1502are included in an embodiment, it may be desirable, as already described above, to have them rotate in opposite directions relative to one another, e.g. one may spin clockwise while the other spins counterclockwise. Embodiments of the invention further include the functionality of irradiating germs out of the air using UV light. Such embodiments provide the advantage of not only circulating air in an environment, but also killing viral, bacterial, and fungal species which may be living in the environment's air. It is known the UV light degrades organic materials, but inorganic materials (including metals or glass) are not affected by UV light. Therefore, UV light is effective for reducing organic matter which may be airborne in the air. Reducing airborne contaminants may be important in any environment, but especially in hospitals or schools, which may be particularly susceptible to disease. Regardless of the environment, disinfecting the air of contaminants is helpful to reduce the spread of disease. It is preferable to reduce or eliminate contact with UV lighting because UV light can be harmful to humans and/or animals (particularly over prolonged durations). Embodiments of the invention therefore provide the advantage of positioning a UV light source in the ceiling tile, where the UV rays may be contained in the ceiling tiles. For example,FIG.16Billustrates exemplary UV light source(s)1640which are mounted inside the upper baffle1610and thus irradiate organic matter residing in air as air flows from the fan to the vent. A person of skill in the art would recognize that UV light sources include a power source and may optionally include a on/off controller (not shown). The UV light source may be activated by an on/off button, or it may be controlled by the remote control feature described further herein. In such an embodiment, a remote control may include the ability to activate or de-activate a UV light source. In some embodiments, light source(s)1640may emit UVC light, which has a wavelength of approximately 200 to 280 nanometers. A person of skill in the art would recognize the UVC light is optimal for irradiating airborne contaminants (such as viruses, superbugs, mold, and the like) in most environments. In embodiments of the invention, the upper baffle1610and/or the lower baffle1620/1621may be made of, or coated with, a UV-reflective material. A person of skill in the art would recognize that a UV-reflective material could include a metal, such as stainless steel, or a specialty coating. Lining the airway with a reflective material and/or reflective coating provides the advantage of creating a “kill chamber,” or “kill zone” inside the airways1630,1631, where UV rays may bounce to increase their exposure to air passing through the airways1630,1631, and by extension, increase the irradiation of organic matter contained in the air. Furthermore, some embodiments of the inventions may include a UV-screen in the form of flange1650which is attached to the end of airways1630and/or1631to shield UV rays from exiting the airways and entering an environment (such as a room or commercial space). In this way, including UV-screen(s)1650at the end of an airway AlthoughFIG.16Billustrates a UV source in an embodiment which is built into a ceiling tile, it should be understood that the disclosed UV source and “kill chamber” may be implemented in any of the embodiments disclosed herein. FIG.17shows an exploded view of components of the invention. For example, the embodiment ofFIG.17shows a ceiling tile1501in which there are cut-outs for fans1502and vents1503. Upper baffle1610is shown, sized to fit onto ceiling tile1501. Furthermore,FIG.17shows exemplary LED strips1504(including power cord) which may be mounted on the ceiling tile1501's underside. While specific combinations of elements are disclosed in specific embodiments, it should be understood that any combination of the different features may be utilized in the combined fan. The foregoing disclosure and description of the invention are illustrating and explanatory thereof, and various changes in the size, shape and materials as well as in the details of illustrated construction may be changed without departing from the spirit of the invention. It is understood that the invention is not limited to the specific embodiments disclosed and that modifications and other embodiments are intended to be included within the scope of the appended claims. Although specific terms are employed herein, they are used in a generic and descriptive sense only and not for purposes of limitation. | 32,060 |
11859625 | DETAILED DESCRIPTION It will be appreciated that for simplicity and clarity of illustration, where appropriate, reference numerals have been repeated among the different figures to indicate corresponding or analogous elements. In addition, numerous specific details are set forth in order to provide a thorough understanding of the exemplary embodiments described herein. However, it will be understood by those of ordinary skill in the art that the exemplary embodiments described herein may be practiced without these specific details. In other instances, methods, procedures, and components have not been described in detail so as not to obscure the related relevant feature being described. Also, the description is not to be considered as limiting the scope of the exemplary embodiments described herein. The drawings are not necessarily to scale and the proportions of certain parts may be exaggerated to better illustrate details and features of the present disclosure. The term “comprising” when utilized, means “including, but not necessarily limited to”; it specifically indicates open-ended inclusion or membership in the so-described combination, group, series, and the like. The disclosure is illustrated by way of example and not by way of limitation in the figures of the accompanying drawings in which like references indicate similar elements. It should be noted that references to “an” or “one” embodiment in this disclosure are not necessarily to the same embodiment, and such references can mean “at least one”. In addition, the terms “first” and “second” are used for descriptive purposes only and cannot be understood as indicating or implying relative importance or implying the number of indicated technical features. Thus, the features defined as “first” and “second” may explicitly or implicitly include one or more of the said features. In the description of embodiments of the invention, “a plurality of” means two or more, unless otherwise specifically defined. In an embodiment, as shown inFIGS.1and2, the present disclosure provides a neck fan including a body portion1and a fan assembly2. The body portion1may be worn around a neck of a user. The body portion1defines an air duct11. The body portion1defines a plurality of air outlets12communicating with the an outside of the neck fan and the air duct11. In this way, air in the air duct11may flow to the outside through the air outlets12. The fan assembly2is mounted on the body portion1and is configured to drive the air from the outside into the air duct11and blow the air to the outside through the air outlets12. The air driven into the air duct11through fan assembly2has a certain speed. Therefore, a wind pressure difference is present between an inside and the outside of air outlets12, i.e., between the air duct and the outside. In this case, while the air is being blown to the outside through the air outlets12, due to the wind pressure difference, some of the air in the air duct11may flow out of the air duct11through air outlets12to reach the neck to cool the user. In an embodiment, the plurality of air outlets12are evenly distributed and spaced apart from each other. Therefore, when being worn, the body portion1surrounds a front, a side and a back of the neck, and the air blown out from the air outlets12may be directed to the front, the side and the back of the neck. In this way, a range that the air may reach is expanded, and the user may be cooled from various directions. The neck fan is highly applicable and may be used conveniently. As shown inFIG.1, the body portion1may be bent and tubular and may be made of an elastic material that can be extended and retracted. When putting on the body portion, two ends of the body portion1may be pulled apart from each other to form a gap, and a size of the gap may be greater than a size (such as a diameter) of the neck. After the neck fan is worn to the neck, the body portion may be reset, i.e., the two ends may be reset to original positions, and the gap between the two ends of the body portion may be reduced. In some embodiments, when the two ends are at the original positions, the two ends may be spaced apart from each other, and a size of the gap therebetween may be less than the size of the neck. In some embodiments, when the two ends of the body portion are at the original positions, the two ends may be connected to each other, such that the body portion is ring-shaped (such as forming an enclosed circle). The body portion1may be made of plastic. The user may carry the body portion easily and may feel comfortable when wearing the body portion. The air outlets12are oriented towards an inside and/or a top of the bent and tubular body portion. Therefore, while being worn, the neck does not cover the air outlets12, allowing the air to be blown out the air outlets12to the neck smoothly. In detail, some of the air outlets12defined in the body portion1are oriented towards the inside of the tubular body portion, and some of the air outlets12are oriented towards the top of the tubular body portion1, increasing a range covered by the air supplied from the air outlets12. As shown inFIGS.1to3, each of two ends of the body portion1defines a mounting cavity13. The fan assembly2is received in the mounting cavity13to be mounted with the body portion1. A portion of the body portion1corresponding to the mounting cavity13defines an air inlet131. The fan assembly2is fixedly received in the mounting cavity13. When the fan assembly2is operating, the fan assembly2draws in the air in the outside through the air inlet131, and is configured to accelerate the air to drive the air to flow into the air duct11. In the present embodiment, two ends of the body portion1define two mounting cavities13, and two fan assemblies2may be received in the two mounting cavities13, respectively. Each of the two fan assemblies2may operate independently. A plate111may be arranged in a middle of the air duct11to divide the air duct11into two sections. One of the two sections of the air duct11corresponds to one of the two fan assemblies2. By arranging the plate111, a length of the air duct11may be reduced effectively, ensuring an air velocity at an air outlet12, which is further away from the fan assembly2. As shown inFIGS.2and4, the fan assembly2includes a fan blade21, a motor (not shown in the figures) which drives the fan blade21to rotate to generate an air flow, a battery22which provides power to the motor, a main control circuit board23which controls a rotation speed of the motor, and a gear switch24electrically connected to the main control circuit board23. When the neck fan needs to be initiated, the gear switch24may be pressed, and the main control circuit board23may receive a signal from the gear switch24. After receiving the signal, the main control circuit board23controls the motor to rotate to drive the fan blade21to rotate. Rotation of the fan blade21may lead the air at the outside to flow into the fan assembly2under the wind pressure, and the air may be guided by the fan assembly2to flow into the air duct11. When the wind speed of the air flowing out of the air outlets12needs to be adjusted, the gear switch24may be pressed to generate various gear signals. The main control circuit board23may receive the gear signals and control the rotation speed of the motor to further control the rotation speed of the fan blade21connected to the motor. Accordingly, a speed of the air driven by the fan assembly2to flow into the air duct11and a speed of the air flowing out through the air outlets12may change. A partition14may be arranged inside the body portion1. The partition14separates an inner space of the body portion1into a shaped cavity15and the air duct11. The battery22and the circuit board both are received in the shaped cavity15. The battery22may be disposed in a middle of the inner space of the body portion1. In this way, the fan assemblies2are arranged at the two ends of body portion1, whereas the battery2is arranged at the middle of the body portion1, the two ends of the body portion1may not be too heavy, and weights of the two ends of the body portion1may be balanced, preventing a weight center of the body portion1from being shifted towards one side. As shown inFIG.2, a cross-sectional area of the air duct11gradually decreases from the two ends to the middle of the body portion1. The air flowing from the two ends to the middle of the body portion1may generate a frictional force. At the same time, the cross-sectional area of the air duct11decreases from the two ends to the middle of the body portion1, i.e., the cross-sectional area that the air passes through while flowing in the air duct11decreases. In this way, an effect of the frictional force on slowing down the speed of the air flow in the air duct11may be partially or completely eliminated. The speed of the air flowing out of the air outlets12may be controlled within a certain range, solving a problem of a large difference between the speed of the air flowing out of an air outlet12at or near the two ends of the air duct11and the speed of the air flowing out of an air outlet12in the middle of the air duct11. As shown inFIG.2, the body portion1includes an outer shell16and an inner shell17. Compared to the body portion1configured as a one-piece structure, the body portion1of the present embodiment is assembled from the outer shell16and the inner shell17, allowing the fan assemblies to be processed and assembled more simply, and allowing later maintenance to be performed more easily. The partition14is arranged on the inner shell17and extends towards the outer shell16. The air duct11is defined cooperatively by the inner shell17, the outer shell16and the partition14. When the outer shell16is connected to the inner shell17, the partition14tightly abuts against an inner side of the outer shell16, preventing the air in the air duct11from entering the shaped cavity15. The air outlets12are defined in the inner shell17. A portion of the inner shell17that contacts the neck of the user extending upwardly to form a curved surface171. The curved surface171may be inclined at a certain angle relative to the portion that contacts the neck of the user, and the air outlets12are defined in the curved surface171, such that the air outlets12are oriented towards the inner side of the tubular body portion. As shown inFIGS.2and4, the fan assembly2includes a turbine fan25. The turbine fan25defines two inlet windows251, increasing a circulation area and an efficiency of the turbine fan25communicating with the external air. A cavity wall of the mounting cavity13defines two air inlets131corresponding to the two inlet windows251of the turbine fan25. When the turbine fan25is rotating, the external air may enter the inlet windows251through the air inlets131. A guide post132is arranged on the cavity wall of the mounting cavity13and extends towards the turbine fan25. The turbine fan25defines a guide hole251corresponding to the guide post132. When the turbine fan25is received in the mounting cavity13, the guide post132extends into the guide hole251, thereby securing the turbine fan25in the mounting cavity13. As shown inFIG.4, the turbine fan25defines an air outlet port252, which is corresponding to and communicating with the air duct11. An air flow generated by the turbine fan25enters the air duct11through the air outlet port252. A portion of a wall of the air outlet port252is received in the air duct11. The portion of the wall of the air outlet port252tightly abuts against a wall of the air duct11, reducing a loss of the air flow generated by the turbine fan25while the air is being guided into the air duct11. In an embodiment, as shown inFIGS.5and6,FIG.5is a schematic view of a neck fan according to an embodiment of the present disclosure, andFIG.6is an explosive view of the neck fan ofFIG.5. The neck fan30includes an arc-shaped shell10and at least four fan assemblies20. The at least four fan assemblies20may be arranged inside the arc-shaped shell10. It shall be understood that, for illustration purposes only, in the following embodiment, the neck fan30including the at least four fan assemblies20will be taken as an example for illustration. The arc-shaped shell10may be worn to surround the neck of the user. The arc-shaped shell10includes a first portion11and a second portion12. The first portion11and the second portion12are arranged around two sides of the neck, such as a left side and a right side. Each of the first portion11and the second portion12includes an inner wall101configured to be close to the neck, an outer wall102opposite to the inner wall101, a top wall103close to a head of the user and connecting between the inner wall101and the outer wall102, and a bottom wall104opposite to the top wall103and connecting between the inner wall101and the outer wall102. The inner wall101, the outer wall102, the top wall103, and the bottom wall104cooperatively define a receiving space105. Each of the first portion11and the second portion102defines air inlets106and air outlets107communicating with the receiving space105. In detail, in the present embodiment, the inner wall101, the bottom wall104, and the top wall103may be connected into an integrated structure (such as, a one-piece structure) to serve as a first side wall. The outer wall102may serve as a second side wall opposite to the first side wall. The first side wall and the second side wall cooperatively define the receiving space105. At least one partition13is received inside the receiving space105to divide the receiving space105into at least two receiving sub-spaces105aand150b. The at least two receiving sub-spaces105aand150bare arranged successively along an extension direction of the arc-shaped shell10. Each of the at least two receiving sub-spaces correspond to and communicate with some of the air inlets106and some of the air outlets107. Each of the fan assemblies is received in one corresponding receiving sub-space. Each of the fan assemblies is configured to guide the air, which flows into the corresponding receiving sub-space through corresponding air inlets106, to flow to air outlets107corresponding to the receiving sub-space, allowing the air to be blown out through the corresponding air outlets107. The number of the air outlets107may be more than one. The more than one air outlets may be distributed along the extension direction of the arc-shaped shell10. Sizes, shapes of the air outlets107and/or distances between every two adjacent air outlets107vary gradually along the extension direction of the arc-shaped shell10. Compared to the neck fan in the art, in the neck fan30illustrated in the above-mentioned embodiments, the arc-shaped shell10includes the first portion11and the second portion12. The first portion11and the second portion12are configured to be around two opposite sides of the neck. Each of the first portion11and the second portion12defines the receiving space105, the air inlets106, and the air outlets107. The air inlets106and the air outlets107communicate with the receiving space105. Each receiving space105is divided into at least two receiving sub-spaces by the partition13. Each of the fan assemblies20is arranged in one of the receiving sub-spaces and configured to guide the air at the air inlets106to flow to the air outlets107to be blown out. Since the fan assemblies20are received in the receiving space105, foreign matters, such as hair, may not be absorbed into the fan assemblies easily, allowing the neck fan to be used safely and conveniently. In the present embodiment, four receiving sub-spaces105aand105bare defined along the extension direction of the arc-shaped shell10, and four fan assemblies20may be arranged and received in four receiving sub-spaces respectively. Since a plurality of the receiving sub-spaces105aand105bare defined, a length of the air duct in each of the receiving sub-spaces may be relatively short. When the air is flowing in each of the receiving sub-spaces, a concentration of the air being output may be reduced, the user may be comfortable about the air output, wind noise may be reduced, and an air volume loss may be reduced. The applicant of the present disclosure finds that, the longer the air duct, the longer period of time that the air flows along the receiving sub-space, increasing the wind noise and the air volume loss. By dividing the receiving space105into the plurality of receiving sub-spaces105aand105b, the wind noise and the air volume loss may be reduced significantly. In addition, by determining an extension direction, sizes, shapes of the air outlets107and distances between two adjacent air outlets107, the user may be more comfortable about the air output from the neck fan30, the air may be output from the neck fan30more softly, improving the user's experiences. Further, each fan assembly20includes a driving shaft21and a fan blade assembly22mounted on the driving shaft21. The driving shaft21extends from the inner wall101towards the outer wall102. In this way, a thickness of the arc-shaped shell10along a direction from the inner wall101to the outer wall102may be reduced, such that the user may be comfortable when wearing the neck fan. Further, the air inlets106are defined in the outer wall102, and the air outlets107are defined in the top wall103. It shall be understood that, the air inlets106are defined in the outer wall102, and the outer wall102faces outwardly (i.e., opposite to the neck of the user), and therefore, the air may enter the shell easily and smoothly. In addition, the air outlets107are defined in the top wall103, and the driving shaft21extends from the inner wall101to the outer wall102. In this way, the fan blade assemblies20may direct the air from the air inlets106to the air outlets107to achieve a high air guiding efficiency. Moreover, the air outlets107are defined in the top wall103, such that the air may be output towards a face and the head of the user, such that the user may be cooled rapidly. Further, an end of the driving shaft21is fixedly arranged on the inner wall101. It shall be understood that, such arrangement together with the air inlets106defined in the outer wall102allows the air inlets106to be unblocked, achieving a better air inlet effect. Further, each fan assembly20corresponds to a plurality of air inlets106. It shall be understood that, air is guided into the fan assembly20through the plurality of fan inlets106, allowing the neck fan to have a better appearance, preventing foreign matters from entering the fan assembly20easily, increasing usage safety. Further, the number of the air inlets106corresponding to each fan assembly20may be the same. The air inlets106corresponding to each fan assembly20are distributed in a circular shape. It shall be understood that, such arrangement allows the neck fan to have a better appearance, and prevents foreign matters from entering the fan assembly20easily. A better air inlet effect may be achieved due to such arrangement and shapes of the fan assemblies20. Further, a plurality of air inlets108are defined in the inner wall101corresponding to each fan assembly20. The fan assembly20can guide the air from the air inlets108to the air outlets107. Each of the plurality of air inlets108is arc shaped. The plurality of air inlets108corresponding to each fan assembly20are distributed in a circular shape. It shall be understood that, such arrangement allows the neck fan to have a better appearance, and prevents foreign matters from entering the fan assembly20easily. A better air inlet effect may be achieved due to such arrangement and shapes of the fan assemblies20. Further, the fan blade assembly22is a turbine fan blade assembly. It shall be understood that the turbine fan blade assembly may reduce the wind noise and improves the usage safety. Further, the neck fan30further includes a connecting portion14connected between the first portion11and the second portion12. The connecting portion14is configured to join the first portion11and the second portion12into an integrated structure. In the present embodiment, the connecting portion14may be configured as an individual element. In some embodiments, the connecting portion14may be integrally formed with one of the first portion11and the second portion12, and then assembled with the other of the first portion11and the second portion12. A structure of the connecting portion14may be various, and shall not be limited by the present disclosure. The first portion11further includes an end plate109disposed at an end of the first portion11away from the connecting portion14. The second portion12further includes an end plate109disposed at an end of the second portion12away from the connecting portion14. Each end plate109is connected to the top wall103, the bottom wall104, the inner wall101and the outer wall102. Sizes of the air inlets106corresponding to the fan assembly20arranged near the connecting portion14are less than those of the air inlets106corresponding to the fan assembly20arranged near the end plate109. An outer diameter of the fan assembly20arranged near the connecting portion14is less that that of the fan assembly20arranged near the end plate109. In other words, an end of the first portion11at which the end plate109is disposed may serve as a free end, and an end of the second portion12at which the end plate109is disposed may serve as another free end. An end of the first portion11near the connecting portion14may serve as a connecting end, and an end of the second portion12near the connecting portion14may serve as another connecting end. In the present embodiment, the sizes of the air inlets106corresponding to the fan assembly20arranged near the connecting end are less than those of the air inlets106corresponding to the fan assembly20arranged near the free end. The outer diameter of the fan assembly20arranged near the connecting end is less than that of the fan assembly20arranged near the free end. It shall be understood that, by determining various sizes of the air inlets106and various outer diameters of the fan blade assemblies20, a size of the arc-shaped shell10may be gradually reduced along a direction from the end plate109to the connecting portion14, such that the shell10is more suitable to a curve of the neck, allowing the user to be comfortable. In the present embodiment, the end plate109may be arc shaped, providing a better appearance. The shape of the end plate109may further be suitable to shapes of the receiving sub-spaces105aand shapes of the fan assemblies20to achieve a better air inlet and outlet effect. It shall be understood that, for each of the first portion11or the second portion12, the inner wall101, the top wall103, the bottom wall104, the end plate109, and the partition13may be formed as a one-piece structure. The outer wall102may be buckled with the top wall103, the bottom wall104, and the end plate109through a buckle. There may be various types of buckles and various means to connect the above structure integrally, which will not be limited by the present disclosure. Further, the number of the air outlets107may be more than one. The more than one air outlets107are distributed along the extension direction of the arc-shaped shell10and extends to a position near the connecting portion14. Sizes of the more than one air outlets107gradually decrease along a direction from the end plate109to the connecting portion14. It shall be understood that, the more than one air outlets107may improve the usage safety. Sizes of the more than one air outlets107gradually decrease along the direction from the end plate109to the connecting portion14, allowing the air to be output in a more concentrated manner, improving air outlet intensity. In addition, sizes of the receiving sub-spaces105aand105bgradually decrease along the extension direction of the air duct. Therefore, the air output from the overall neck fan may be more uniform, and the user may feel comfortable. In detail, the extension direction of the arc-shaped shell10includes a first extension direction and a second extension direction. A direction extending from the first portion11to the second portion12may be referred to as a first extension direction D1. The sizes of the more than one air outlets107defined in the first portion11are gradually reduced along the first extension direction D1. A direction extending from the second portion12to the first portion11is referred to as a second extension direction D2. The sizes of the more than one air outlets107defined in the second portion12are gradually reduced along the second extension direction D2. Furthermore, each of the air outlets107is a strip-shaped air outlet. An extension direction of the strip-shaped air outlet may be inclined in a preset angle relative to the extension direction of the arc-shaped shell10. The preset angle may be 90 degrees. It shall be understood that, by defining the air outlets107in the above extension direction, the air outlet of the neck fan30may be softer, and the user may be more comfortable, improving the user's experience. In particular, when the preset angle is 90 degrees, the air outlet efficiency of the air outlets107is improved. In addition, a cross-sectional area of the air duct of the first portion is gradually decreased along a direction from the first portion to the second portion; and/or a cross-sectional area of the air duct of the second portion is gradually decreased along a direction from the second portion to the first portion. Further, the partition13is connected to a surface of the inner wall101facing the outer wall102and extends towards the outer wall102. The partition13includes a partition body130, a first guiding portion131, and a second guiding portion132. One end of the partition body130is connected to an end of the bottom wall104near the end plate109. The other end of the partition body130extends towards a middle of the top wall103to be close to a middle of the top wall103. The first guiding portion131includes a first sub-portion131aand a second sub-portion131b. The first sub-portion131asurrounds a periphery of the fan assembly20arranged near the end plate109. The second portion131bis connected between the first portion131aand the top wall103. The second guiding portion132is connected to the partition body130and surrounds a periphery of the fan assembly20near the connecting portion14. It shall be understood that, the partition body130is configured to divide the receiving space105into the two receiving sub-spaces105aand105b. The first guiding portion131and the second guiding portion132are configured to match shapes of the fan blade assemblies22so as to guide the air and achieve a better air outlet effect. Further, an end of the second guiding portion132away from the partition body130extends to reach the connecting portion14. Along a direction from the end plate109to the connecting portion14, a distance between the second guiding portion132and the bottom wall103is gradually reduced until the second guiding portion132is tangent to the bottom wall103, and then the distance between the second guiding portion132and the bottom wall103is gradually increased to a predetermined value and remains at the predetermined value. The predetermined value may be determined according to actual demands, for example, in some embodiments, the predetermined value may be a half of a distance between the top wall103and the bottom wall104. Such arrangement of the second guiding portion132allows the air duct to extend to reach the connecting portion14. In addition, some of the air outlets107are defined near the connecting portion14. In this way, a range of the air output from the neck fan30is larger, improving the cooling effect. Further, the neck fan30further includes an electronic control assembly15. The electronic control assembly15includes a battery and a printed circuit board151. The second guiding portion132and the partition body130cooperatively define a receiving chamber133to receive at least part of the electronic control assembly15. It shall be understood, the electronic control assembly15are received in the receiving chamber133, preventing heat generated by the electronic control assembly15from entering the receiving sub-spaces105aand150b, and therefore, the cooling effect may not be affected. In addition, such arrangement allows individual arrangement of heat dissipation and wiring of the electronic control assembly15, thereby improving the usage safety. Further, the electronic control assembly15further includes a switch button152and a data port153. The outer wall102of the second portion12defines a first opening102acorresponding to the switch button152and a second opening102bcorresponding to the data port153. The switch button152is mounted corresponding to the first opening102aand connected to the printed circuit board151. The data port153is mounted corresponding to the second opening102band connected to the printed circuit board151. Such arrangement allows the user to operate the neck fan easily, improving user's experience. Furthermore, it shall be understood, in addition to the electronic control assembly15, structures and elements of the first portion11and the second portion12are symmetrically arranged to increase wearing comfort. Further, the outer wall102includes a main plate1021and an auxiliary plate1022. A shape and a position of the auxiliary plate1022correspond to those of the partition13. The auxiliary plate1021is connected between the main plate1021and the partition13. It shall be understood that the auxiliary plate1022and the partition13cooperatively define the air duct of the fan assembly20, so as to achieve a better air guiding effect. In another embodiment, as shown inFIGS.7and8,FIG.7is a schematic view of a neck fan30according to an embodiment of the present disclosure, andFIG.8is an explosive view of the neck fan30ofFIG.7. The neck fan30includes an arc-shaped shell10and at least four fan assemblies20. The at least four fan assemblies20are arranged inside the arc-shaped shell10. It shall be understood that, in the present embodiment, a neck fan having four fan assemblies20may be taken as an example for illustration. The arc-shaped shell10may be hung around the neck of the user. The arc-shaped shell10includes a first portion11and a second portion12. The first portion11and the second portion12are arranged around two sides of the neck, such as a left side and a right side. Each of the first portion11and the second portion12includes a side wall that defines a receiving space105. Each of the first portion11and the second portion12defines air inlets106and air outlets107communicating with the receiving space105. At least one partition13is received in the receiving space105to divide the receiving space105into at least two receiving sub-spaces105aand150b. The at least two receiving sub-spaces105aand150bare arranged successively along an extension direction of the arc-shaped shell10. Each of the at least two receiving sub-spaces correspond to and communicate with some of the air inlets106and some of the air outlets107. Each of the fan assemblies20is received in one corresponding receiving sub-space. Each of the fan assemblies is configured to guide the air, which flows into the corresponding receiving sub-space through corresponding air inlets106, to flow to air outlets107corresponding to the receiving sub-space, allowing the air to be blown out through the corresponding air outlets107. The number of the air outlets107may be more than one. The more than one air outlets107may be distributed along the extension direction of the arc-shaped shell10. Sizes, shapes of the air outlets107and/or distances between every two adjacent air outlets107vary gradually along the extension direction of the arc-shaped shell10. Compared to the neck fan in the art, in the neck fan30illustrated in the above-mentioned embodiments, the arc-shaped shell10includes the first portion11and the second portion12. The first portion11and the second portion12are configured to be around two opposite sides of the neck. Each of the first portion11and the second portion12defines the receiving space105, the air inlets106, and the air outlets107. The air inlets106and the air outlets107communicate with the receiving space105. Each receiving space105is divided into at least two receiving sub-spaces105aand105bby the partition13. Each of the fan assemblies20is arranged in one of the receiving sub-spaces and configured to guide the air at the air inlets106to flow to the air outlets107to be blown out. Since the fan assemblies20are received in the receiving space105, foreign matters, such as hair, may not be absorbed into the fan assemblies easily, allowing the neck fan to be used safely and conveniently. In the present embodiment, four receiving sub-spaces105aand105bare defined along the extension direction of the arc-shaped shell10, and four fan assemblies20may be arranged and received in four receiving sub-spaces respectively. Since a plurality of the receiving sub-spaces105aand105bare defined, a length of the air duct in each of the receiving sub-spaces may be relatively short. When the air is flowing in each of the receiving sub-spaces, a concentration of the air being output may be reduced, the user may be comfortable about the air output, wind noise may be reduced, and an air volume loss may be reduced. The applicant of the present disclosure finds that, the longer the air duct, the longer period of time that the air flows along the receiving sub-space, increasing the wind noise and the air volume loss. By dividing the receiving space105into the plurality of receiving sub-spaces105aand105b, the wind noise and the air volume loss may be reduced significantly. In detail, the side wall includes a first side wall101′ configured to be close to the neck of the user and a second side wall102opposite to the first side wall101′. The air inlets106are defined in the second side wall102, and the air outlets107are defined in a region of the first side wall101′ adjacent to the second side wall102or defined in a region of the second side wall102adjacent to the first side wall101′. In the present embodiment, the air outlets107are defined in the region of the first side wall101′ adjacent to the second side wall102and are close to the user's head and face. Further, in detail, a direction extending from the first portion11to the second portion12may be referred to as a first extension direction D1. The sizes of the more than one air outlets107defined in the first portion11are gradually reduced along the first extension direction D1. A direction extending from the second portion12to the first portion11is referred to as a second extension direction D2. The sizes of the more than one air outlets107defined in the second portion12are gradually reduced along the second extension direction D2. Furthermore, each of the air outlets107is a strip-shaped air outlet. An extension direction of the strip-shaped air inlet may be inclined in a preset angle relative to the extension direction of the arc-shaped shell10. The preset angle may be 90 degrees. It shall be understood that, by defining the air outlets107in the above extension direction, the air outlet of the neck fan30may be softer, and the user may be more comfortable, improving the user's experience. In particular, when the preset angle is 90 degrees, the air outlet efficiency of the air outlets107is improved. In some embodiments, the air outlets107may be at least one of petal-shaped and heart-shaped. It shall be understood that, both the petal-shaped air outlets107and the heart-shaped air outlets107may output the air uniformly and provides better appearance for the neck fan. Further, each fan assembly20includes a driving shaft21and a fan blade assembly22mounted on the driving shaft21. The driving shaft21extends from the first side wall101′ towards the second side wall102. In this way, a thickness of the arc-shaped shell10along a direction from the first side wall101′ to the second side wall102may be reduced, such that the user may be comfortable when wearing the neck fan. It shall be understood, the air inlets106are defined in the second side wall102, and the second side wall102faces outwardly (i.e., away from the user's neck) allowing the air to flow into the air inlets106easily, allowing the air to flow in smoothly. Such arrangement together with the driving shaft21extending along the direction from the first side wall101′ to the second side wall102enables the fan blade assembly22to direct the air from the air inlets106to the air outlets107, thereby achieving a relatively high air guiding efficiency. Moreover, the air outlets107are defined at the first side wall101′ close to the user's head and face, such that the air may be directed out towards the user's head and face, thereby achieving better cooling effect. The first side wall101′ defines a plurality of air inlets108corresponding to each fan assembly20. The fan assembly20can guide the air at the air inlets108to the air outlets107. Each of the plurality of air inlets108is arc shaped. The plurality of air inlets108corresponding to each fan assembly are arranged in a circular shape. It shall be understood, such arrangement provides a better appearance of the neck fan30, and prevents the foreign matters from entering the fan assembly20. Such arrangement together with shapes of the fan assemblies20achieves a better air guiding effect. In an embodiment, the first side wall defines the plurality of air inlets108, and the second side wall defines the plurality of air inlets106. The first side wall faces the neck of the user, and the second side wall is connected to the first side wall and faces away from the neck. Further, at least one of a region of the first side wall close to the second side wall and a region of the second side wall close to the first side wall defines the plurality of air outlets107. In addition, the plurality of air outlets107are located between the plurality of air inlets108of the first side wall and the plurality of air inlets106of the second side wall along an extension direction of the driving shaft21. Further, the first portion11has a connecting end10aconnected to the second portion12and a free end10baway from the connecting end10a; and the second portion12also has a connecting end10aconnected to the first portion11and a free end10baway from the connecting end10a. Sizes of the air outlets107corresponding to the fan assembly20adjacent to the connecting end10aare less than those of the air outlets107corresponding to the fan assembly20adjacent to the free end10b. An outer diameter of the fan blade assembly22adjacent to the connecting end10ais less than that of the fan blade assembly22adjacent to the free end10b. It shall be understood, the sizes of the air inlets106and the diameter of the fan blade assembly22enables a size of the arc-shaped shell10to be reduced gradually along a direction from the free end10bto the connecting end10a, such that the shape of the neck fan may fit a curve of the neck more appropriately, increasing wearing comfort. In the present embodiment, each of the first portion11and the second portion12includes a cover16. The cover16is disposed on a side of the second side wall102away from the first side wall101′ and corresponds to (such as covers) the air inlets106. A gap161communicated with the air inlets106is defined between an edge of the cover16and the second side wall102to allow air to flow into the air inlets106. Further, the second side wall102includes a main body102cand defines a recess102d. A wall of the recess102dis connected to the main body102c. In other words, the side of the second side wall102away from the first side wall101′ is recessed inwardly towards the first side wall101′ to define the recess102d. The air inlets106are defined at the recess102d, such as defined in the bottom wall of the recess102d. The cover16covers the recess102d. The cover16is partially connected to the main body102cconnected to wall of the recess102dto define the gap161. It shall be understood, the cover16covers the air inlets106, and air enters through the gap161and the air inlets106. In this way, a better appearance is provided, and the foreign matters may be prevented from entering the fan assembly20, increasing the usage safety. Defining the recess102dfurther reduces an overall size of the neck fan30and provides the appearance aesthetics. Further, the cover16includes a cover body162and a first mounting portion163arranged at a side of the cover body162adjacent to the second side wall102. A side of the second side wall102close to the cover16is arranged with a second mounting portion102e. In detail, the second mounting portion102emay be arranged on the wall of the recess102dand is located between the plurality of air inlets106. Further, the cover16further includes the cover body162and the first mounting portion163arranged on the cover body162. The second mounting portion102eis arranged on the second side wall102and is engaged with the first mounting portion163. Engagement between the second mounting portion102eand the first mounting portion163enables the cover16to be mounted (such as detachably or movably mounted) on the side of the second side wall102away from the first side wall101′. It shall be understood, engagement between the first mounting portion163and the second mounting portion102eenables the cover16to be detachably or movably mounted onto the second side wall102, allowing the neck fan to be used or disassembled easily. Further, the first mounting portion163and the second mounting portion102emay be engaged in a first mounting state or in a second mounting state. In the first mounting state, the gap161is defined between the edge of the cover16and the second side wall102. In the second mounting state, the edge of the cover16abuts against the second side wall102so as to cover the air inlets106. It shall be understood, the first mounting portion163and the second mounting portion102emay be engaged in the first mounting state or in the second mounting state. Therefore, in the first mounting state, the air can enter the fan assembly through the gap161and the air inlets106; and in the second mounting state, the gap161and the air inlets106are covered, and dust may be prevented from entering the arc-shaped shell through the air inlets106when the neck fan30is not in use, achieving the dustproof effect. It shall be understood, the first mounting state and the second mounting state may be switched from one to the other. In some embodiments, elastic fasteners may be configured, serving as the first mounting portion and the second mounting portion. In this way, the first mounting state and the second mounting state may be switched by pressing the cover16along a direction facing the second side wall102. For example, a first press is made to switch from the first mounting state to the second mounting state, and a next press is made to switch from the second mounting state to the first mounting state. There are various structures for implementing the above-mentioned press switch control, which will not be described specifically hereinafter. In the present embodiment, the first mounting portion163may be a mounting shaft connected to the cover body162, and the second mounting portion102emay be a mounting hole corresponding to the mounting shaft. In other embodiments, the first mounting portion163may be a mounting hole defined in the cover body162, and the second mounting portion102emay be a mounting shaft corresponding to the mounting hole. It shall be understood, the mounting shaft may be received in the mounting hole to engage the cover16to the second side wall102, achieving an easy mounting operation. In the present embodiment, the partition13includes a partition body131and a guiding portion132. A shape of the partition body131at least partially fits to a shape of the fan assembly20, and the partition body131surrounds a periphery of the fan assembly20. The guiding portion132is connected to the partition body131. The guiding portion132and the side wall cooperatively define the air duct communicated to the air outlets107. It shall be understood that by adapting the partition part131to the shape of the fan assembly20and by configuring the guiding portion132and the side wall to cooperatively define the air duct17communicated to the air outlets107, a better air guiding effect may be achieved, and an air inlet and outlet efficiency may be improved. Further, for each of the first portion11and the second portion12, the guiding portion132includes a first guiding sub-portion132alocated between two fan assemblies20and a second guiding sub-portion132barranged at a side of one of the two fan assemblies20away from the other of the two fan assemblies. The second guiding sub-part132bextends from one of the first portion11and the second portion12to the other of the first portion11and the second portion12. A side of the second guiding sub-portion132band the side wall cooperatively define an accommodating space18. The neck fan30further includes an electronic control assembly15. The electronic control assembly15includes a battery and a printed circuit board. The accommodating space18is defined to receive at least one of the battery and the printed circuit board. It shall be understood, by receiving the electronic control assembly15in the accommodating space18, configuration of the neck fan30may be effectively balanced, providing wearing comfort for the user. In addition, the fan blade assembly20may be a turbine fan blade assembly. It shall be understood that the turbine fan blade assembly may achieve lower noise and higher safety. In an embodiment, as shown inFIG.4, the present disclosure provides a turbine blade assembly22for a neck fan. The turbine blade assembly22has a first side and a second side opposite to the first side. The turbine blade assembly22includes a first side blade disposed at the first side, a second side blade disposed at the second side, and a separation plate disposed between the first side and the second side. The first side defines a first inlet window, and the second side defines a second inlet window. The first inlet window and the second inlet window are defined to allow air to flow in from an outside of the neck fan. A bottom wall of the first inlet window is recessed from a plane where the first side blade is disposed. A bottom wall of the second inlet window is recessed from a plane where the second side blade is disposed. The above description only describes embodiments of the present disclosure, and is not intended to limit the present disclosure, various modifications and changes can be made to the present disclosure. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and scope of the present disclosure are intended to be included within the scope of the present disclosure. | 47,090 |
11859626 | DETAILED DESCRIPTION For the purposes of promoting an understanding of the principles of the present disclosure, reference will now be made to the embodiments illustrated in the drawings, and specific language will be used to describe the same. It will nevertheless be understood that no limitation of the scope of this disclosure is thereby intended. The following description is merely illustrative in nature and is not intended to limit the present disclosure, its application or uses. It should be understood that throughout the drawings, corresponding reference numerals indicate like or corresponding parts and features. As used herein, the term controller refers to processing circuitry that may include an application specific integrated circuit (ASIC), an electronic circuit, an electronic processor (shared, dedicated, or group) and memory that executes one or more software or firmware programs, a combinational logic circuit, and/or other suitable interfaces and components that provide the described functionality. Additionally, the term “exemplary” is used herein to mean “serving as an example, instance or illustration.” Any embodiment or design described herein as “exemplary” is not necessarily to be construed as preferred or advantageous over other embodiments or designs. The terms “at least one” and “one or more” are understood to include any integer number greater than or equal to one, i.e. one, two, three, four, etc. The terms “a plurality” are understood to include any integer number greater than or equal to two, i.e. two, three, four, five, etc. The term “connection” can include an indirect “connection” and a direct “connection.” Turning to an overview of technologies that are more specifically relevant to aspects of the present disclosure, a cabin air conditioning and temperature control system (CACTCS) provides pressurized air to certain parts of an aircraft, for example, to meet cabin and flight deck pressure demands. Aircraft may use one or more CACTCSs. CACTCSs can include a cabin air compressor (CAC) or multiple CACs. A CAC compresses the air within the CACTCS and provides the force necessary to move the air through the CACTCS. According to an example, an aircraft may use two CACTCSs, each having two CACs. CACs, which are line replaceable units (LRUs), are vulnerable to surge. Compressor surge can be damaging to the CAC and/or the entire CACTCS. Compressor surge causes unstable performance due to flow reversal, which is not acceptable to machines on which a compressor is mounted to ventilate or dense air. Another effect of compressor surge is on solid structure. For example, violent flows of compressor surge repeatedly hit blades in the compressor, which results in blade fatigue or even mechanical failure. This can also cause damage to bearings. Further, surging can also cause the compressor to overheat, potentially to the point at which a maximum allowable temperature is reached, at which point catastrophic failure of the CAC and/or CACTCS may occur. Some CACTCSs and/or CACs include built-in tests (BIT) that checks the compressor surge and issues alerts. A BIT looks for compressor surge by identifying an event indicative of compressor surge, for example, when the output pressure of the CAC cycles by more than +/−2 PSIA (absolute pressure) 6 times within a 6 second period of time. This happens when the flow reversal cycle starts, i.e., compressor surge is fully developed, and severe vibrations are already occurring. Because compressor surge events can cause damage, they may shorten the lifetime of the CAC, which may cause CAC removal, which is costly, time consuming, and reduces the usability of the aircraft (e.g., the aircraft cannot fly while the CAC and or CACTCS is being repaired/replaced). In an effort to address these and other shortcomings of the prior art, one or more embodiments described herein provide for detecting incipient compressor surge (also referred to as “incipient surge”), which occurs before flow reversal develops. By detecting incipient compressor surge, CACs can be prevented from going into full compressor surge (or at least, the likelihood of compressor surge can be reduced). This protects CACs from damage, which improves aircraft reliability and usability. Turning now to a more detailed description of the inventive teachings, one or more non-limiting embodiments of the present disclosure provide for detecting incipient compressor surge. Particularly, one or more embodiments provide for training a machine learning model that can be used to detect incipient surge in real-time (or near-real-time) and taking a corrective action when incipient surge is detected. One or more embodiments apply the trained machine learning model to vibration data collected from a vibration sensor associated with a CAC to detect incipient surge. One or more embodiments use edge-based processing technology to implement the machine learning model. Turning now to the figures,FIG.1depicts a block diagram of a system101having a processing system100for training a machine learning model108to detect incipient compressor surge within a cabin air compressor (CAC)112of a cabin air conditioning and temperature control system (CACTCS)110according to one or more embodiments described herein. The processing system100includes a processing device102(e.g., the processor521ofFIG.5), a memory104(e.g., the RAM524and/or the ROM522ofFIG.5), and a machine learning (ML) model training engine106. The ML model training engine106can be implemented as instructions stored on a computer-readable storage medium, as hardware modules, as special-purpose hardware (e.g., application specific hardware, application specific integrated circuits (ASICs), application specific special processors (ASSPs), field programmable gate arrays (FPGAs), as embedded controllers, hardwired circuitry, etc.), or as some combination or combinations of these. According to aspects of the present disclosure, the engine(s) described herein can be a combination of hardware and programming. The programming can be processor executable instructions stored on a tangible memory, and the hardware can include the processing device102for executing those instructions. Thus, a system memory (e.g., memory104) can store program instructions that when executed by the processing device102implement the engines described herein. Other engines can also be utilized to include other features and functionality described in other examples herein. The processing system100trains the machine learning model108using the ML model training engine106. According to one or more embodiments described herein, the processing system100receives data from one or more sensors of one or more CACTCSs, such as the CACTCS110. For example, the processing system100can receive speed information about a speed of the CAC112from a speed sensor114associated with the CAC112. Similarly, the processing system100can receive vibration information about a vibration of the CAC112from a vibration sensor116associated with the CAC112. It should be appreciated that the processing system110can receive the training data from multiple sources (e.g., multiple CACTCS110), from a data repository storing such data, etc. According to one or more embodiments described herein, the vibration sensor116is an industrial vibration sensor that is used to detect vibration signals from the CAC112. In an example, the vibration sensor116is mounted on the top foils of the CAC air journal bearings. The vibration sensor116may be configured to detect a wide range of frequencies. According to one or more embodiments described herein, the speed sensor114may already be implemented in the CAC112. The speed sensor114collects data about rotor speed of the CAC112. The ML model training engine106can use the speed information and/or vibration information as training data to train a machine learning model. In examples, once the data are obtained/received, the ML model training engine106preprocesses the data to generate training spectrograms, designs a model, trains the model, evaluates the model, converts/reduces the model, and deploys the model as the machine learning model108. A spectrogram is a visual represent of the spectrum of frequencies over time. For example, a spectrogram can be used to visually represent a vibration wave form over time. For example, vibration data from the vibration sensor116(e.g., mounted on top of fan foils of air journal bearings) is collected. The vibration data is captured in terms of time and amplitude. The vibration data is then converted into a spectrogram. A spectrogram works by breaking the time domain vibration data into a series of time periods and applying a fast Fourier transform (FFT) of these time periods. These series of FFTs are then overlapped on one another to visualize how both the amplitude and frequency of the vibration signal changes with time. FFTs alone may be insufficient because vibration frequency changes quickly with time in compressors and FFTs cannot capture that sufficiently. The resulting three-dimensional surface plot of FFTs can be rotated onto its side, and a color scale can be added to represent the amplitude. This results in a spectrogram, which acts as an image which can be labelled with a detected incipient surge condition. An example of a detected incipient surge condition is as follows: radial vibration signal as sub-synchronous vibration at a frequency of approximately 0.10× to 0.20× (10 to 20 percent of the rotor speed) and healthy frequency conditions. One or more additional categories can be included in other examples, but here only incipient surge and healthy used. These spectrograms are then trained using a machine learning model (e.g., a convolution neural network) and then the machine learning model is reduced/compressed to take less memory. That compressed model is then deployed on the microcontroller118, which represents an edge device that can run continuous inferences to detect incipient surge in the CAC112. For example, the machine learning model108, once trained and reduced, can be deployed to a microcontroller118associated with the CACTCS110. The machine learning model108can be used to identify incipient compressor surges in the CAC112using operating data collected during real-time operation of the CACTCS110/CAC112. The microcontroller118can be any suitable type of microcontroller. According to one or more embodiments described herein, although not shown inFIG.1, the microcontroller118can include a processor for processing instructions, a memory for storing instructions and/or data, and an input/output (I/O) interface for receiving and transmitting data/signals. The microcontroller118, in examples, supports implementing a machine learning model. Further details of the system101, including additional features and functionality of one or more components of the system101, are now described with reference toFIGS.2and3. FIG.2depicts a flow diagram of a method200for training a machine learning model (e.g., the machine learning model108) and using the machine learning model to detect incipient compressor surge within a cabin air compressor (e.g., the CAC112) of a cabin air conditioning and temperature control system (e.g., the CACTCS110) according to one or more embodiments described herein. The method200can be implemented by any suitable system or device, or combinations thereof, such as the processing system100, the microcontroller118, and/or the like. The method200includes a training portion (blocks202-206), an inference portion (blocks208-212), and an action portion (block214). Training begins at block202where the processing system100receives training data indicative of incipient compressor surge for cabin air compressors. The training data can include speed data (e.g., speed of the rotor of the CAC112determined by the speed sensor114) and vibration data (e.g., vibration signals detected by the vibration sensor116). The training data can be received from any suitable source, such as from the sensors114,116, from a training repository, etc. At block204, the processing system100generates, using the training data, a training spectrogram. According to one or more embodiments described herein, generating the training spectrogram includes applying a fast Fourier transform to the training data. At block206, the processing system100trains a machine learning model (e.g., the machine learning model108) to detect incipient compressor surge events for the cabin air compressors using the spectrogram. In one or more examples, the machine learning model can be a convolutional neural network trained to classify images (e.g., spectrograms). Once training is complete, inference begins at block208, where the microcontroller118, which is associated with the cabin air compressor112, receives operating data associated with the cabin air compressor. The operating data can include vibration data collected by the vibration sensor116. At block210, the microcontroller118generates, using the operating data, an operating spectrogram. The operating spectrogram differs from the training spectrogram(s) in that the operating spectrogram is based on real-time (or near-real-time) data used for inference while the training spectrogram(s) are generated using training data. According to one or more embodiments described herein, generating the operating spectrogram comprises applying a fast Fourier transform to the operating data. At block212, the microcontroller118detects an incipient compressor surge event by applying the machine learning model to the operating spectrogram. Once the inference detects an incipient surge event, a correction action can be implemented at block214to increase the surge margin to prevent the compressor from experiencing surge. Increasing the surge margin can be accomplished in various ways. For example, a variable diffuser can be used as a primary surge margin control; the variable diffuser position can be decreased, reducing its effective area, to increase surge margin. As another example, an anti-surge valve can be used to control surge margin by opening the valve to decrease the CAC pressure ratio while increasing CAC flow, which increases surge margin. As another example, an air cycle machine bypass valve (ABV) can be held above a minimum (or threshold) position in order to provide additional surge margin. As another example, when the variable diffuser on the CAC is failed during CAC operation, the anti-surge valve can be used to control the variable diffuser surge margin reference without an offset; in such cases, the anti-surge valve becomes the primary surge margin control. Additional processes also may be included. According to one or more embodiments described herein, the method200can include evaluating the machine learning model based at least in part on an accuracy of the machine learning model, a latency of the machine learning model, and a memory usage of the machine learning model. According to one or more embodiments described herein, the method200can include converting the machine learning model to a reduced machine learning model executable by the microcontroller. In such cases, the machine learning model is not executable by the microcontroller. In an example, converting the machine learning model to the reduced machine learning model can include reducing a size of the machine learning model by performing post-training quantization of model weights and activations. In another example, the converting the machine learning model to the reduced machine learning model includes pruning the machine learning model to remove at least one synapse from the machine learning model. It should be understood that the process depicted inFIG.2represents an illustration, and that, other processes may be added, or existing processes may be removed, modified, or rearranged without departing from the scope of the present disclosure. FIG.3depicts a flow diagram of a method300for training a machine learning model (e.g., the machine learning model108) and using the machine learning model to detect incipient compressor surge within a cabin air compressor (e.g., the CAC112) of a cabin air conditioning and temperature control system (e.g., the CACTCS110) according to one or more embodiments described herein. The method200can be implemented by any suitable system or device, or combinations thereof, such as the processing system100, the microcontroller118, and/or the like. At block302, the processing system100, using the ML model training engine106, receives data for training the machine learning model108. One way to make data set is by continuously collecting time domain vibration data for a sliding time period using the vibration sensor116. If there is a surge alert by the built-in test, the vibration data in the time period before the surge is saved along with the rotor speed, which is measured by the speed sensor114. Incipient surge occurs with sub-synchronous vibrations at a frequency of approximately 0.10× to 0.20× (10 to 20 percent of the rotor speed). The speed data is useful for confirming the occurrence of the incipient surge. At block304, the processing system100, using the ML model training engine106, preprocesses the data. Here, the time domain data is broken into small time slots and a fast Fourier transform is used to convert the time domain data into frequency domain data. By applying the FFT through a sliding window procedure, the intensity (e.g., in color) of each of frequencies over time can be analyzed to detect incipient surge events. Then, spectrograms are generated, and feature extraction can be performed on the spectrograms to identify incipient surge events, as will be described herein, using, for example, feature extraction. At block306, the processing system100, using the ML model training engine106, designs the machine learning model. According to one or more embodiments described herein, a convolutional neural network (CNN) is used to perform feature extraction on spectrograms. In other examples, other architectures, such as deep learning, can be used to achieve a balance between accuracy and memory requirements. A number of layers in the model depend on the storage available. For example, if there is no extra storage (e.g., for CNN), a minimum convolutional model with one conv2D layer and one dense layer can be used. This kind of model will provide a quick response time while accounting for memory constraints. At block308, the processing system100, using the ML model training engine106, trains the machine learning model. The machine learning model is trained and tested to achieve desired results. For example, model parameters such as accuracy, latency, and memory usage can be tuned to achieve the desired results. According to one or more embodiments described herein, training is performed on the processing system100and not the microcontroller118because the training uses highly accurate computation that the microcontroller118may not be able to provide. Further, the microcontroller118may not be able to store and/or process a dataset large enough to support training. However, in some examples, the microcontroller118can perform the training where the microcontroller118is sufficiently enabled to perform the training. At block310, the processing system100, using the ML model training engine106, evaluates the machine learning model. Evaluating the machine learning model can include considering one or more of the following properties: actual accuracy, actual latency, and/or actual memory usage. For example, these properties can be evaluated as compared to the desired properties (e.g., desired accuracy, desired latency, desired memory usage, etc. from block306). Accuracy includes balancing between false positives (i.e., alerts when there is no incipient surge) and false negatives (i.e., no alert when incipient surge occurs). This operating point can be decided manually based on the requirements (e.g., the desired accuracy). For latency, it is desirable that the machine learning model be fast enough to keep up with the vibration inputs. This is also why it is desirable to reduce the model to keep the model small. For memory usage, it is useful to be resource aware. This can include being cognizant about memory allocations in the microcontroller118such as application code (receives data from the vibration sensor116and performs the preprocessing (block304)), the inference engine deployed in the microcontroller118, various variables and parameters that define the machine learning model108and other dynamic variables, a data buffer to store the data from the vibration sensor114, and the like. At block312, the processing system100, using the ML model training engine106, converts the machine learning model to a reduced machine learning model (e.g., the ML model108). This stage provides for the trained machine learning model to function correctly when deployed on the microcontroller118. To convert a trained machine learning model to run on microcontrollers, the following steps are implemented: reduce the model size and modify it to use edge-based operations; quantize model weights and activations so they can be represented by 8-bit or fixed-point arithmetic (post-training quantization, although quantization aware training can also be implemented in some examples); prune the machine learning model by removing weights (synapses) that have relatively low impact on accuracy of the machine learning model, and convert the model to a file-type that the microcontroller118can receive. At block314, the processing system100, using the ML model training engine106, deploys the reduced machine learning model108, such as to the microcontroller118. According to one or more embodiments described herein, preprocessing code in a language executable by the microcontroller118is used to deploy the machine learning model108into the microcontroller118. At block316, the microcontroller118performs inference. The microcontroller118continues to receive new (operational) vibration time domain data from the vibration sensor116. This data is used to generate a spectrogram, which is applied to the machine learning model108by the microcontroller118. If incipient surge is detected, alert is issued and/or an action is implemented as described herein. Additional processes also may be included, and it should be understood that the process depicted inFIG.2represents an illustration, and that other processes may be added, or existing processes may be removed, modified, or rearranged without departing from the scope of the present disclosure. FIG.4Adepicts an example plot400of vibration data according to one or more embodiments described herein. In this example, the plot400plots amplitude of vibration (as a g-force) against time (in seconds). During inference, for example, the vibration sensor116collects vibration data about the CAC112, and the microcontroller118uses the vibration data generate a spectrogram.FIG.4Bdepicts an example spectrogram according to one or more embodiments described herein. In this example, the plot401represents a spectrogram, which plots frequency (in Hz) against time (in seconds). The spectrogram in the plot401is created by taking the vibration data (e.g., from plot400) and applying a fast Fourier transform to the vibration data. A sliding window procedure can be used. For example, the vibration data can be separated into overlapping windows (as shown). The results of the FFT are used to generate the spectrogram shown in the plot401. The intensity (represented, for example, in color or otherwise) of each of the frequencies over time are shown in the spectrogram. It is understood that one or more embodiments described herein is capable of being implemented in conjunction with any other type of computing environment now known or later developed. For example,FIG.5depicts a block diagram of a processing system500for implementing the techniques described herein. In accordance with one or more embodiments described herein, the processing system500is an example of a cloud computing node that can be deployed in a cloud computing environment. In examples, processing system500has one or more central processing units (“processors” or “processing resources” or “processing devices”)521a,521b,521c, etc. (collectively or generically referred to as processor(s)521and/or as processing device(s)). In aspects of the present disclosure, each processor521can include a reduced instruction set computer (RISC) microprocessor. Processors521are coupled to system memory (e.g., random access memory (RAM)524) and various other components via a system bus533. Read only memory (ROM)522is coupled to system bus533and may include a basic input/output system (BIOS), which controls certain basic functions of processing system500. Further depicted are an input/output (I/O) adapter527and a network adapter526coupled to system bus533. I/O adapter527may be a small computer system interface (SCSI) adapter that communicates with a hard disk523and/or a storage device525or any other similar component. I/O adapter527, hard disk523, and storage device525are collectively referred to herein as mass storage534. Operating system540for execution on processing system500may be stored in mass storage534. The network adapter526interconnects system bus533with an outside network536enabling processing system500to communicate with other such systems. A display (e.g., a display monitor)535is connected to system bus533by display adapter532, which may include a graphics adapter to improve the performance of graphics intensive applications and a video controller. In one aspect of the present disclosure, adapters526,527, and/or532may be connected to one or more I/O busses that are connected to system bus533via an intermediate bus bridge (not shown). Suitable I/O buses for connecting peripheral devices such as hard disk controllers, network adapters, and graphics adapters typically include common protocols, such as the Peripheral Component Interconnect (PCI). Additional input/output devices are shown as connected to system bus533via user interface adapter528and display adapter532. A keyboard529, mouse530, and speaker531may be interconnected to system bus533via user interface adapter528, which may include, for example, a Super I/O chip integrating multiple device adapters into a single integrated circuit. In some aspects of the present disclosure, processing system500includes a graphics processing unit537. Graphics processing unit537is a specialized electronic circuit designed to manipulate and alter memory to accelerate the creation of images in a frame buffer intended for output to a display. In general, graphics processing unit537is very efficient at manipulating computer graphics and image processing and has a highly parallel structure that makes it more effective than general-purpose CPUs for algorithms where processing of large blocks of data is done in parallel. Thus, as configured herein, processing system500includes processing capability in the form of processors521, storage capability including system memory (e.g., RAM524), and mass storage534, input means such as keyboard529and mouse530, and output capability including speaker531and display535. In some aspects of the present disclosure, a portion of system memory (e.g., RAM524) and mass storage534collectively store the operating system540to coordinate the functions of the various components shown in processing system500. The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting. As used herein, the singular forms “a”, “an” and “the” are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms “comprises” and/or “comprising,” when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof. The present embodiments may be a system, a method, and/or a computer program product at any possible technical detail level of integration. The computer program product may include a computer readable storage medium (or media) having computer readable program instructions thereon for causing a processor to carry out aspects of the present disclosure. The flowchart and block diagrams in the figures illustrate the architecture, functionality, and operation of possible implementations of systems, methods, and computer program products according to various embodiments. In this regard, each block in the flowchart or block diagrams may represent a module, segment, or portion of instructions, which comprises one or more executable instructions for implementing the specified logical function(s). In some alternative implementations, the functions noted in the blocks may occur out of the order noted in the Figures. For example, two blocks shown in succession may, in fact, be executed substantially concurrently, or the blocks may sometimes be executed in the reverse order, depending upon the functionality involved. It will also be noted that each block of the block diagrams and/or flowchart illustration, and combinations of blocks in the block diagrams and/or flowchart illustration, can be implemented by special purpose hardware-based systems that perform the specified functions or acts or carry out combinations of special purpose hardware and computer instructions. While the present disclosure has been described in detail in connection with only a limited number of embodiments, it should be readily understood that the present disclosure is not limited to such disclosed embodiments. Rather, the present disclosure can be modified to incorporate any number of variations, alterations, substitutions, combinations, sub-combinations, or equivalent arrangements not heretofore described, but which are commensurate with the scope of the present disclosure. Additionally, while various embodiments of the present disclosure have been described, it is to be understood that aspects of the present disclosure may include only some of the described embodiments. | 30,421 |
11859627 | DETAILED DESCRIPTION OF THE EMBODIMENTS The following makes detailed description by listing embodiments and with reference to the accompanying drawings, but the specific described embodiments are merely used to explain the embodiments of the disclosure, and are not intended to limit the embodiments of the disclosure. However, the description of structural operations is not intended to limit sequences in which the operations are performed, any structure in which elements are recombined and any device having equivalent functions shall fall within the scope covered by the content of the embodiments of the disclosure. The term “coupled” or “connected” used in the specification may mean that two or more elements are in direct physical or electrical contact with each other or indirect physical or electrical contact with each other or two or more elements are in operation or action with each other. FIG.1is a schematic diagram of a fan control system100according to some embodiments of the disclosure. In some embodiments, the fan control system100is configured to adjust the temperature of a heat generation device, so that the temperature in the system is appropriate for operations of the device. As shown inFIG.1, the fan control system100includes a fan101, a device102, a temperature sensor103, a calculating unit104, a logic controller105, a memory unit106, a processor107, an input/output interface108, and a temperature sensor109. The temperature sensor103is coupled to the calculating unit104. The calculating unit104is coupled to the logic controller105. The logic controller105is coupled to the memory unit106. The memory unit106is coupled to the fan101. The logic controller105is further separately coupled to the processor107, the input/output interface108, and the temperature sensor109. In some embodiments, the fan101is disposed near the device102to generate an air flow to adjust the temperature of the device102. In some embodiments, the device102is the heat generation device of which the temperature rises as a workload increases. When the air flow generated by the fan101flows near the device102, the temperature of the device102decreases as the air flow carries away heat. In some embodiments, the device102is a central processing unit (CPU). In some other embodiments, the device102is a graphics processing unit (GPU). In some embodiments, the temperature sensor103is disposed near the device102, and is configured to sense the temperatures of the device102. When the temperature of the device102increases as the workload increases, the temperature sensed by the temperature sensor103increases. In some embodiments, the temperature sensor103is further configured to continuously sense and continuously sample the temperatures of the device102in a time period, in order to obtain a plurality of sampled temperatures t, and transmit the sampled temperatures t to the calculating unit104. In some embodiments, the calculating unit104is configured to calculate an average value of the sampled temperatures t. The calculating unit104selects N1 latest sampled temperatures and N2 latest sampled temperatures from the sampled temperatures t, and performs calculation according to N1 and N2 separately. The calculating unit104calculates an average of the N1 latest sampled temperatures of the sampled temperatures t as a first average temperature T1avg, and calculates an average of the N2 latest sampled temperatures of the sampled temperatures t as a second average temperature T2avg. The calculating unit104is further configured to transmit the first average temperature T1avgand the second average temperature T2avgto the logic controller105. In some embodiments, N1 and N2 are positive integers. N1 is greater than 0, and N2 is greater than N1. In other words, when the calculating unit104calculates the first average temperature T1avgand the second average temperature T2avg, the N1 latest sampled temperatures of the sampled temperatures t partially overlap the N2 latest sampled temperatures of the sampled temperatures t. In an embodiment, at a moment, the temperature sensor103has sampled100temperatures t. When N1 is equal to 10 and N2 is equal to 50, the first average temperature T1avgis an average value of the 10 latest sampled temperatures t of the 100 sampled temperatures, and the second average temperature T2avgis an average value of the 50 latest sampled temperatures t of the 100 sampled temperatures. In other words, it is assumed that the temperature sensor103has sampled the 100 sampled temperatures t1to t100in a time period, and the sampled temperatures t100is the latest sampled temperature of the sampled temperatures. When N1 is equal to 10 and N2 is equal to 50, the first average temperature T1avgis an average value of sampled temperatures t91to t100, and the second average temperature T2avgis an average value of sampled temperatures t51to t100. In some embodiments, the logic controller105is configured to select one of the first average temperature T1avgand the second average temperature T2avgto output as a compensation temperature T and transmit the compensation temperature T to the memory unit106. As shown inFIG.1, the memory unit106includes an operating table106a. The operating table106ahas information about a relationship between a temperature and a rotational speed of a fan. The memory unit106outputs a rotational speed control signal Sr to the fan101corresponding to the operating table106aaccording to the compensation temperature T to adjust a rotational speed of the fan101. In some embodiments, when the compensation temperature T is higher, the rotational speed of the fan101corresponding to the rotational speed control signal Sr output by the memory unit106is faster. In some embodiments, the logic controller105has a plurality of determination modes, and selects one of the first average temperature T1avgand the second average temperature T2avgaccording to the determination modes. In some embodiments, the determination mode includes: (a) selecting the first average temperature T1avg, (b) selecting the second average temperature T2avg, (c) selecting a larger one of the first average temperature T1avgand the second average temperature T2avg, and (d) selecting a smaller one of the first average temperature T1avgand the second average temperature T2avg. In the determination mode (a), the logic controller105selects the first average temperature T1avgto output as the compensation temperature T. In the determination mode (b), the logic controller105selects the second average temperature T2avgto output as the compensation temperature T. Compared with the two modes, N1 is less than N2. Therefore, it can be learned that a quantity of sampled temperatures t is smaller, and consequently, the compensation temperature T selected by the determination mode (a) is more timely than the compensation temperature T selected by the determination mode (b). Compared with the determination mode (b), in the determination mode (a), the rotational speed control signal Sr output by the memory unit106enables the fan101to be quickly adjusted corresponding to the temperature of the device102. In some embodiments, when the rotational speed of the fan101is quickly adjusted, the temperature of the device102is also quickly adjusted, so that the temperature of the device102is maintained at an appropriate operating temperature, and consequently the efficiency is relatively high. In addition, because the rotational speed of the fan101is quickly adjusted, sound caused by the revolution of the fan101also changes quickly. In some embodiments, when the rotational speed of the fan101is adjusted at a relatively slow speed, the temperature of the device102is also adjusted at a relatively slow speed, so that the sound caused by the fan101changes at a relatively slow speed. In the determination mode (c), the logic controller105selects the larger one of the first average temperature T1avgand the second average temperature T2avgto output as the compensation temperature T. In this mode, when the temperatures of the device102quickly increase, the rotational speed of the fan101also quickly increases. Next, when the temperature of the device102decreases, the rotational speed of the fan101is still maintained at a relatively high rotational speed and does not quickly decrease in time, and eventually slows down. Therefore, in the determination mode (c), the fan101has a function of adjusting the temperature of the device102, and also has an effect of performing continuous heat dissipation for a high temperature that remains in the system after the temperature of the device102decreases. In an embodiment, when the temperature of the device102instantaneously increases, the first average temperature T1avgis higher than the second average temperature T2avg. The logic controller105selects the first average temperature T1avgto output as the compensation temperature T, so that the fan101has a relatively high rotational speed. Next, when the temperature of the device102starts to decrease, the first average temperature T1avgdecreases, but the second average temperature T2avgis kept at a high temperature. The logic controller105selects the second average temperature T2avgto output as the compensation temperature T, so that the fan101is kept at a relatively high rotational speed, and continuously enables the air flow to carry away remaining heat in the system. In the determination mode (d), the logic controller105selects the smaller one of the first average temperature T1avgand the second average temperature T2avgto output as the compensation temperature T. In this mode, when the temperature of the device102quickly increases, the rotational speed of the fan101slowly increases instead of quickly increasing. When the temperature of the device102decreases, the rotational speed of the fan101quickly decreases. Therefore, in the determination mode (d), the fan101has a time for reducing the generation of a large amount of sound change. In an embodiment, when the temperature of the device102instantaneously increases, the second average temperature T2avgis less than the first average temperature T1avg. The logic controller105selects the second average temperature T2avgto output as the compensation temperature T, so that the rotational speed of the fan101does not quickly increase. Next, when the temperature of the device102starts to decrease slowly, the first average temperature T1avgdecreases, but the second average temperature T2avgis kept at a high temperature. The logic controller105selects the first average temperature T1avgto output as the compensation temperature T, so that the rotational speed of the fan101quickly decreases to reduce the time for reducing the generation of sound change. In some embodiments, the processor107is configured to generate a control signal Sc1to the logic controller105. The logic controller105determines the determination modes according to the control signal Sc1, to select one of the first average temperature T1avgand the second average temperature T2avg. In some embodiments, the input/output interface108is configured to transmit a control signal Sc2external to the system to the logic controller105. The logic controller105determines a determination mode according to the control signal Sc2, to select one of the first average temperature T1avgand the second average temperature T2avg. In some embodiments, a user may customize a determination mode and transmit the control signal Sc2to the logic controller105through the input/output interface108. In some embodiments, the temperature sensor109is configured to sense an ambient temperature Tab, and transmit the ambient temperature Tab to the logic controller105. The logic controller105determines a determination mode according to the ambient temperature Tab, to select one of the first average temperature T1avgand the second average temperature T2avg. In some other embodiments, the logic controller105is configured to adjust N1 and N2 according to at least one of the control signal Sc1, the control signal Sc2, and the ambient temperature Tab. In an embodiment, when the ambient temperature Tab increases, the heat dissipation capability of the fan control system100decreases. Therefore, the logic controller105is configured to reduce N1 and N2, so that the rotational speed of the fan101changes in time, thereby improving the heat dissipation capability of the fan control system100. In some embodiments, the memory unit106includes a single temperature and rotational speed comparison table, that is, the operating table106a. Regardless of a determination mode in which the logic controller105selects the first average temperature T1avgor the second average temperature T2avg, the logic controller105only needs to output the rotational speed control signal Sr corresponding to the compensation temperature T output by the logic controller105. In some implementations, a heat dissipation system includes a plurality of rotational speed comparison tables, and each rotational speed comparison table corresponds to different working modes of the system. Therefore, a large amount of space is required to store the rotational speed comparison tables. Compared with the foregoing implementations, in the embodiments of the disclosure, the fan control system100only includes the single operating table106a. In different working modes, the calculating unit104and the logic controller105output the single compensation temperature T to the memory unit106after the sampled temperatures are appropriately corrected and compensated for. Therefore, even in different working modes, the fan control system100uses the single operating table106ato complete different heat dissipation functions. Therefore, space of storing a plurality of operating tables for different operating modes is saved, and the cost of the fan control system100is reduced. The arrangement of the fan control system100is only used for description. The arrangement of different fan control systems100falls within the consideration and the scope of the disclosure. In some other embodiments, the fan control system100is a system configured to dissipate heat in a computer. The calculating unit104, the logic controller105, and the memory unit106are disposed in firmware such as an embedded controller (EC) in the computer. The processor107and the input/output interface108are connected to the logic controller105by a basic input/output system (BIOS) in the computer. FIG.2is a flowchart of a fan control method200according to some embodiments of the disclosure. To better understand the content of the disclosure,FIG.2is discussed with reference to element and reference numerals inFIG.1. As shown inFIG.2, the fan control method200includes steps S201, S202, S203, S204, and S205. Step S201: The temperature sensor103continuously senses temperatures of the device102during a time period, in order to obtain a plurality of sampled temperatures t. Step S202: The calculating unit104selects N1 latest sampled temperatures and N2 latest sampled temperatures from the sampled temperatures t, and calculates a first average temperature T1avgaccording to the N1 sampled temperatures and a second average temperature T2avgaccording to the N2 sampled temperatures. The first average temperature T1avgis an average value of the N1 latest sampled temperatures t of all the sampled temperatures t, and the second average temperature T2avgis an average value of the N2 latest sampled temperatures t of all the sampled temperatures t. Step S203: The logic controller105selects one of the first average temperature T1avgand the second average temperature T2avgto output as a compensation temperature T and transmits the compensation temperature T to the memory unit106. In some embodiments, the logic controller105further determines a determination mode according to at least one of the control signal Sc1generated by the processor107, the control signal Sc2transmitted by the input/output interface108, and the ambient temperature Tab sensed by the temperature sensor109, to select one of the first average temperature T1avgand the second average temperature T2avgto output as the compensation temperature T. In some embodiments, step S203further includes adjusting, by the logic controller105, N1 and N2 according to the ambient temperature Tab. Step S204: Output the rotational speed control signal Sr to the fan101according to the operating table106ain the memory unit106and the compensation temperature T. The rotational speed control signal Sr enables the fan101to have a rotational speed corresponding to the compensation temperature T. Step S205: The fan101adjusts a rotational speed according to the rotational speed control signal Sr to adjust and control the temperature of the device102. Descriptions of the fan control method200include exemplary steps, but the step sequence of the fan control method200is adjustable. That is, the sequence of the steps of the fan control method200is able to be changed in appropriate cases, the steps are performed simultaneously or some of the steps are performed simultaneously or omitted, which shall fall within the spirit and scope of the embodiments of the disclosure. FIG.3is a schematic diagram of a fan control system300according to some other embodiments of the disclosure. Compared with the fan control system100shown inFIG.1, the fan control system300includes a plurality of fans, a plurality of devices, and a plurality of temperature sensors sensing temperatures of a device. As shown inFIG.3, the fan control system300includes fans301a,301b, devices302a,302b,302c, temperature sensors303a,303b,303c, a calculating unit304, a logic controller305, a memory unit306, a processor307, an input/output interface308, and a temperature sensor309. The temperature sensors303a,303b,303care separately coupled to the calculating unit304. The calculating unit304is coupled to the logic controller305. The logic controller305is coupled to the memory unit306. The memory unit306is coupled to the fans301a,301b. The logic controller305is further separately coupled to the processor307, the input/output interface308, and the temperature sensor309. In some embodiments, the fans301a,301bare disposed near the devices302a,302b,302cto generate air flows to adjust the temperatures of the device302a,302b,302c. In some embodiments, the temperature sensors303a,303b,303care configured to sense the temperatures of the devices302a,302b,302crespectively. When the temperatures of the devices302a,302b,302cincrease as the workload increases, the temperatures sensed by the temperature sensors303a,303b,303cincrease. In some embodiments, the temperature sensors303a,303b,303care further configured to sense and sample the temperatures of the devices302a,302b,302cand transmit the sampled temperatures t1, t2, and t3to the calculating unit304. In some embodiments, different elements include similar functions, such as the calculating unit304and the calculating unit104, the logic controller305and the logic controller105, the memory unit306and the memory unit106, the operating table306aand the operating table106a, the processor307and the processor107, the input/output interface308and the input/output interface108, and the temperature sensor309and the temperature sensor. Details are not described herein again. In some embodiments, when one of the fan301aand the fan301bfails, the heat dissipation capability of the fan control system300decreases. Therefore, the logic controller305reduces N1 and N2 to improve the heat dissipation capability of the fan control system300, so that the rotational speed of a non-failed fan changes in time for responding to the temperatures of the devices302ato302c. When an abnormal fan is recovered, the heat dissipation capability of the fan control system300improves, so that the rotational speed of the fan responses to the temperatures of the devices302ato302cin time, and the logic controller305increases N1 and N2. Quantities of the fans301aand301b, the devices302ato302c, and the temperature sensors303ato303cin the fan control system300are merely used for description. Different quantities of the fans, the devices, and the temperature sensors are all within the spirit and scope of the embodiments disclosed in the disclosure. Based on the foregoing, in the disclosure, the calculating unit and the logic controller are used to correct and compensate for the sampled temperatures, so that the fan control system adjusts the rotational speed of the fan according to the single operating table in a plurality of different operating modes. In this way, space of storing operating tables for different operating modes is saved, and costs of the fan control system is reduced. Although the embodiments of the disclosure have been disclosed above, the embodiments are not intended to limit the embodiments of the disclosure. A person skilled in the art may make variations and modifications without departing from the spirit and scope of the embodiments of the disclosure. Therefore, the protection scope of the embodiments of the disclosure should be subject to the appended claims. | 21,245 |
11859628 | DETAILED DESCRIPTION The following description may use terms such as “horizontal”, “vertical”, “lateral”, “back and forth”, “up and down”, “upper”, “lower”, “inner”, “outer”, “forward”, “rear”, etc. These terms generally refer to the views and orientations as shown in the drawings and that are associated with a normal use of the invention. The terms are used for the reader's convenience only and shall not be limiting. The use of pumps is common across various applications, ranging from the drilling of wells to the supply of water. Depending on the intended use for a pump, it may be required to have different capabilities. For example, pumps must be able to produce sufficient head to deliver a required volume of fluid per unit of time to a desired location, and may additionally be required to be used with a range of fluids, from incompressible to compressible, and even multiphase fluids. Particularly when considering pumps pumping a compressible and multiphase fluids, excessive wear or damage may be experienced. This may be due, at least in part, to operation in unfavourable pump conditions. As such, recognition of such unfavourable pump conditions may be beneficial. It can be difficult to identify unfavourable pump conditions by measuring the fluid flow and/or the composition of the fluid flow alone. This is especially true for multiphase pumps. This disclosure will provide a system for recognition of unfavourable pump operating conditions. In particular, this disclosure relates to the monitoring of pump operation to identify irregularities in fluid flow, which may be more conveniently measured and may provide a clearer indication of the pump operation condition. Examples of two unfavourable pump operation conditions of pumps are “surge” and “choke”. “Surge” is well known from rotating compressors and typically occurs at low flow rates. In this case, the pump impellers are suddenly not able to maintain the differential pressure they had established, the pressure drops and the pump flow is drastically reduced. In a short time period, e.g. a second or more, the differential pressure is re-established and then the cycle is repeated. This cycling may build up to very high levels and may prove to be detrimental to the motor and the pump. The “choke” flow condition may appear at high flow rates, wherein the flow out of the pump impellers is “choked”. This effect limits the differential pressure produced from each pump impeller and may be a source of instability of the rotor. “Choke” may be a source of increased local pressure fluctuations and rotor axial vibration, which may cause damage and/or excessive wear to the rotor, or associated pump. Typically, the range of safe pump operation is defined by performing test runs to monitor the performance of a pump under different operating conditions. The acceptable range is then implemented into a control system in order to facilitate pump operation within safe margins. In addition, such testing may be used to identify acceptable parameter limits, and ranges of values for parameters that may be used to identify the “surge” and “choke” operating conditions. Previously, control systems may have been largely or completely dependent on the measurement of the pump operation by measuring fluid flow and/or fluid composition. This disclosure provides an alternative to traditional monitoring, facilitating and/or improving the accuracy of the detection of such unfavourable pump operation conditions. FIG.1is a schematically illustrated piping system, showing a multiphase pump installation13for pumping fluid comprising an inlet1for the inflow of fluid and an outlet50for the outflow fluid, as well as a multiphase pump20. The outlet50of the pump is in fluid communication with a fluid sink, via a sink conduit, which may be considered to be the desired location to which the pump20is pumping a fluid. The pump20in this example is a multiphase pump, which is suited for pumping a multiphase fluid (i.e. a fluid comprising both a liquid and a gaseous fraction); however, other types of pumps for various fluids may be applicable for this disclosure. The pump20comprises a rotor (which may comprise a plurality of multiphase impellers) and means for tracking the axial movement of said rotor (not shown in the Figure) relative to at least one other component of the pump20, for example the housing of the pump, and/or the stator of the pump20. The means for tracking the axial movement of the rotor may be e.g. a proximity sensor arrangement which may comprise one or a plurality of proximity sensors, configured to detect movement of an indicator on the rotor and thereby track the axial movement of said rotor. For example, the proximity sensors, or a proximity sensor, may be configured to detect or measure the axial position of the rotor as the rotor rotates. The axial position of the rotor may be determined by using the proximity sensor arrangement to measure the distance between the known position of the proximity sensor arrangement and a component of the drive shaft—for example a rotating disc on the drive shaft. The rotating disc may be preferably centralised on the shaft, and may have a flat and perpendicular surface. In other examples, the proximity sensor arrangement may measure a mark, protrusion or fin on the drive shaft, or and end of the drive shaft. The means for tracking the axial movement of the rotor (e.g. the proximity sensor arrangement) may be in the form of, or comprise, an optical sensor or sensors, and/or and eddy current sensor or sensors. Additionally, the axial movement of the rotor may cause a vibration of the pump housing and/or stator. At least one accelerometer (e.g. one, two, three or more) may be coupled to any of the pump20, its housing or its stator to measure the vibration of the pump20. Measurements of the vibration of the pump and the axial movement of the rotor may be compared, analysed separately and/or any of these two may be measured and analysed solely, which may give a user an indication of the functioning of the pump. In some examples, such axial movement and/or vibration may provide an indication of the operation of the pump in unfavourable operating conditions. The pump20may also be configured to measure the dynamic motor current and the dynamic shaft torque to identify irregularities in the pump operation. Advantageously, the installation13comprises a buffer tank10for smoothing out gas slugs which may be present in a fluid as it enters the installation13at the inlet1. The tank10may be considered a fluid source for the pump20with which it may be considered to be in fluid communication via a source conduit. A multiphase fluid comprising a liquid and a gas fraction may be flowed through the inlet1and into the buffer tank10. Once in the tank10, a degree of mixing of the multiphase fluid may occur. The mixing may at least in part be as a result of the constant inflow of fluid into the buffer tank10. In this way the inflow to the pump may be a more stable mixture of liquid and gas than in a scenario without a buffer tank10. This may allow more suitable operating conditions for the pump20. In this example, there is a fluid connection via a fluid conduit from the inlet to the buffer tank10, and on to the pump20, which then extends to the outlet50. The installation13also comprises a bypass valve9, which directly connects the inlet1and outlet50to enable a fluid bypass of the pump20, for example in the case where fluid enters the installation13and does not require pumping, or if there is a requirement to pass fluid from the inlet1to the outlet50such that it may flow to a further component or piping installation (not shown) while the pump20is out of operation, for example. The installation13further comprises a recirculation valve30, advantageously in combination with a liquid extraction unit (LEU)31. The recirculation valve30is connected to a recirculation pipeline, which provides a fluid connection between the outlet of the pump20and the buffer tank10. The recirculation valve may be used to control fluid flow within the recirculation pipeline, by permitting a user to selectively permit fluid flow therethrough. The LEU31may be used to separate the liquid fraction from a multiphase fluid being pumped (e.g. a working fluid) after it has passed through the pump20and the recirculation valve30may reinject the separated liquid back into the buffer tank10. This may be useful in cases where it is anticipated that liquid with a high gas fraction will enter the buffer tank10. As such, the recirculation valve30may facilitate balancing of the liquid and gaseous fractions of a multiphase fluid entering the pump20, which may assist to reduce wear on the pump20by example providing a flow of multiphase fluid to the pump20having a preferable ratio of gas to liquid fractions. The recirculation valve may be selectively operated by a user, only when required, in cases where a fluid at the inlet experiences a large and/or many slugs of gas contained therein. Alternatively, if it is known that a fluid with a particularly high gaseous fraction is flowing through the inlet1over a period of time, then the recirculation valve may be used to continuously control the ratio of gas to liquid fractions in the multiphase fluid. Additionally or alternatively, the recirculation valve may be used in cases where the pressure at the outlet of the pump20is particularly high, which may cause an unsustainable differential pressure to act across the pump20. In these cases, the pump20may be used to reduce the pressure at the outlet of the pump20, by permitting fluid to flow from the outlet of the pump20and back into the buffer tank. The installation13comprises a discharge isolation valve40in this example. Alternatively, a choke valve may be used as discharge isolation valve40, even although an isolation valve40is used in this example. Here the discharge isolation valve40may be used to limit the flow rate of a fluid from the pump20by throttling or restricting the flow of fluid therethrough, thereby limiting the fluid outlet towards the outlet50. This may have the effect of increasing the pressure at the outlet of the pump20, which may be useful in cases where the pressure differential across the pump20is too low, or for other reasons that may cause the pressure at the outlet of the pump to be too low, or where an increase in the pressure at the outlet of the pump may be advantageous. The installation13may comprise a suction isolation valve2, advantageously with a suction isolation equalisation valve3. These may control the suction of pumping fluid from the inlet1into the buffer tank10, thereby allowing the flow of fluid into the buffer tank10to be increased or limited as required. Between the inlet1and the buffer tank10and at the recirculation path to the buffer tank10, there may be injection means8,26. The injection means8,26may be useful for injecting an additional substance into the fluid flow. The injection means8,26may for example inject methanol into the pumping fluid. The injection of methanol may be useful when a period of standstill is required, and may be used for displacing or flushing hydrocarbons from the installation13prior to a standstill period, and may additionally or alternatively be useful for repairs or retrieval of the pump20. The installation13of this example comprises pressure transmitters5,18,22,35, which are designed to measure the pressure of the pumping fluid at various locations and may transmit the measured pressures to a computational unit to analyse the measured pressures. As explained above, knowing the pressure of a fluid at the outlet of the pump20may be useful, as may knowing the pressure of a fluid at the inlet of a pump20, for example for calculating the pressure differential across the pump20. The installation13of this example also comprises temperature transmitters6,17,23, which measure the temperature of the pumping fluid and may transmit the measured temperatures to a computational unit to analyse the measured temperatures. The installation13as illustrated comprises a multiphase flow meter16, which may be used to monitor properties of the pumping fluid, for example the flow rate, density or viscosity. Here, the installation13comprises a level transmitter11, which measures the filling level of the buffer tank10and transmits the filling level to a computational unit. This may be important to ensure that the installation13is receiving a desirable volume of fluid. FIG.2shows an example of a graph illustrating an example of a measurement of the pressure difference of the measurements of pressure transmitters positioned before and after the pump (e.g. at or adjacent the inlet and the outlet of the pump20), inFIG.1the pressure transmitters are labelled with the numbers22and18. Plotted is the change in differential pressure in bar acting across the pump over time, illustrated as a sampling rate of 10 Hz. Alternatively, the output pressure of the pump20may be measured instead of the differential pressure acting across the pump, which may be plotted in a similar manner to that shown inFIG.2. A sampling rate of 10 Hz is selected in this example to ensure that measurements are taken quickly enough to gain an accurate appreciation of the change in differential, or output pressure of the pump20, thereby facilitating the identification of the condition of the pump (e.g. whether the pump is operating normally, or in the surge/choke condition). Any appropriate sampling rate that permits a sufficient frequency of measurement to provide accurate results may be used, and it should be noted that there is no absolute requirement to use 10 Hz as indicated in this example. In this example, the rate of change of differential pressure changes significantly over time, as can be seen inFIG.2. As all the measured properties of the installation13change with time as they are being measured (e.g. oscillating), some properties in this application may be analysed based on the change of that property (e.g. the analysis of pressure may focus on the change or fluctuation of pressure within a certain, relatively short, time scale). An important value may therefore be the fluctuation in pressure, rather than the pressure reading itself. The pressure fluctuation may be equal to the local peak-to-peak difference62(i.e. the difference between the peak and trough of the pressure reading), which may be equal to twice the local oscillation amplitude. The term pressure fluctuation in this disclosure is to be understood as the local peak-to-peak difference of the respectively linked physical property of the installation13. For example, the pressure fluctuation inFIG.2has a local mean value ranging from roughly sixty-five bar to eighty-five bar on the left operational range60ofFIG.2and a mean value of roughly sixty-five on the right operational range61ofFIG.2. The pressure fluctuation, however, is at most five on the right operational range61ofFIG.2and goes up to roughly forty on the left operational range60ofFIG.2. In effect, the pressure fluctuation reading on the left operational range60is much larger than the pressure fluctuation reading on the right operational range61, as illustrated. The transition between a high pressure fluctuation reading and a lower may occur very rapidly, and as such a relatively high sampling rate (such as a sampling rate of 10 Hz) may be required in order to accurately identify the transition which, as will be described, may point to a change in the operating condition of the pump20. The left operational range60ofFIG.2shows that the pump20being monitored is operating with a higher than desirable fluctuations of differential pressure, which can be contrasted against the fluctuations in differential pressure in the operational range indicated by reference numeral61. In the operational range60shown inFIG.2, the differential pressure fluctuates over time between a high pressure of 100 bar and a low pressure of approximately 43 bar (i.e. a fluctuation of between 55 and 60 bar—approximately 57 bar). In contrast, in the operational range61on the right ofFIG.2, the fluctuation in differential pressure is much smaller in comparison, approximately in the range of 5 bar. In the operational range60on the left ofFIG.2, where the fluctuation in differential pressure is much higher, in this example the fluctuations cause the differential pressure to fluctuate between a high pressure that is higher than a desirable operating pressure, and a low pressure that is lower than a desirable operating pressure. In the context of this disclosure, high pressure fluctuations may be an indication of a phenomenon known as “surge”, which may be identifiable on the illustrated graph by at least one of a heavily oscillating differential pressure as described before, and therefore a high reading of pressure fluctuation (which may be termed dynamic pressure) and a high reading of dynamic axial position of the rotor (e.g. larger than expected, or desired, changes in the axial position of the rotor). When the pump20is operating under surge conditions, damage may be caused to the rotor and/or impellors of the pump. In some examples, the highly oscillating pressure reading may indicate that there is a high differential pressure acting across the pump20, which the pump20is not able to contain. As such, this may cause pressure to be lost from the pump20, and result in rapid pressure fluctuation thereacross, which may result in damage to the pump20itself. Damage produced by this phenomenon may be mitigated by increasing the volume of fluid flow to the pump, thereby reducing the differential pressure acting across the pump20. As previously described, this may be achieved by use of the recirculation valve30, which may permit a reduction in pressure at the outlet of the pump20, thereby making operation in the surge condition less likely, and allowing a reduction in damage caused to the pump20during operation. On the right operational range61, however, the pump is operating in a stable condition and the differential pressure shows a calm operation, which may be considered to be a normal or desirable state of operation. Here, the reading of pressure fluctuation can be observed to be much lower than on the left operational range60. As illustrated, the monitoring of the difference in pressure fluctuation may be an alternative to monitoring other parameters such as the flow rate, frequency or the like, and may alleviate certain drawbacks associated with monitoring flow rate, such as having to measure and/or calculate the density or directly measure the flow rate of a multiphase fluid, or having to perform a complex frequency analysis in order to ascertain the operating condition of the pump (e.g. whether the pump is operating in a stable condition, surge condition or choke condition). One solution for transitioning from having a reading similar to that of the left operational range60, which may be a harmful operation condition for the pump, to a reading similar to that of the right operational range61may be to increase the pump flow rate by increasing pump speed. Increasing the pump speed may have the effect of increasing the fluid flow through the pump20, thereby reducing the pressure at the output of the pump20, and moving away from the surge operating condition. As can be seen, the graph ofFIG.2shows the pump operation transitioning from surge to normal operating conditions, which may be due to effective use of an increase in speed of the pump20to move away from the surge condition. FIG.3shows an example of a graph illustrating the pressure difference of the measurements of pressure transmitters positioned before and after the pump, inFIG.1these are labelled with the numbers22and18. Plotted is the pump differential pressure in bar over the pump flow rate. In this example, the left operational range70illustrates a reading that may be displayed on such a graph during a surge condition, and corresponds to the operational range60from the graph ofFIG.2. The middle operational range71shows the pump in an ordinary operation state, similar to operational range61fromFIG.2, which may correspond to a normal (e.g. a desirable) operating condition. The right operational range72illustrates a reading that may be present during the choke operating condition, wherein the differential pressure drops above a critical flow rate. To detect whether the pump20is functioning in the choke operating condition, further information in addition to the monitoring of the differential pressure fluctuation or differential pressure may be helpful to assist in the identification of the choke operating condition. Therefore, the axial position of the rotor of the pump may be measured to provide additional information to a user on the operating conditions of the pump20. The choke operating condition may result in an unstable behaviour of the rotor position, similar to the surge operating condition creating an unstable reading of the differential pressure as shown inFIG.2. As the rotor begins to operate in the choke operating condition, shown as operational range72inFIG.3, and the rotor will start to “jump”. This jumping of the rotor may result in sudden oscillations in the axial direction thereof, and therefore this information may be used to monitor whether or not the pump is operating according to the choke operating condition. The axial position (e.g. the change in axial position) of the rotor therefore is an indicator of the choke operating condition, which as described is damaging to the pump. FIG.4is a graph illustrating the axial position of the rotor in one dimension parallel to the longitudinal axis of the rotor plotted over the time in seconds from the start-up of the pump. As can be seen, the pump rotor starts to “jump” at a start-up operation range80(e.g. alternate rapidly between multiple axial locations), before reaching a stable operation range81in which axial movement of the pump rotor may still be measured, but occurs is a smoother, less erratic, and less extreme way as compared to the pump operational range80. The same effect may occur when ramping-up or ramping-down the pump. A similar reading showing oscillation of the rotor of the pump20may be shown if the pump enters the choke operating condition. Therefore, the method of preventing damage to a multiphase pump may comprise measuring the axial position of the rotor of the pump over a time period. In measuring the axial position of the rotor over time, the change in axial position may be observed, which may assist to identify whether the pump has entered a particular operating condition e.g. the choke operating condition. As illustrated inFIG.4the position of the rotor of the pump is measured relative to some reference point, and oscillates between a “minimum” value and a “maximum” value. The reference point may be, for example, the position of the rotor at the startup of operation, the position of the rotor during initial operation, or an arbitrarily designated position that is assigned for the purpose of measuring axial movement of the rotor of the pump. The “minimum” value of the axial position of the rotor may correspond to the most extreme position of the rotor in a first direction (e.g. a first direction parallel to the longitudinal axis of the rotor of the pump), while the “maximum” value of the axial position of the rotor may correspond to the most extreme position of the rotor in a second direction (e.g. a second direction parallel to the longitudinal axis of the rotor of the pump). Here, the “most extreme position” refers to the most extreme position of the rotor during a single oscillation, such that for each oscillation, a different “most extreme” position may be observed. The first direction may be directly opposite the second direction. As such, relative to the graph ofFIG.4, the “minimum” value of the axial position of the rotor of the pump may correspond to a trough (see, for example, the troughs in the operation range80inFIG.4), while the “maximum” value of the axial position of the rotor may correspond to a peak (see, for example, the peaks in the operation range80inFIG.4). In light of the above, the graphs ofFIGS.3and4may be used to identify whether the pump has entered the choke operating condition, and allow the user to take action to prevent excessive damage to the pump20. Again, this may be beneficial to the user, because it allows the user to ascertain the operating condition of a pump simply by viewing the peak-to-peak, or peak-to-trough difference on a graph. In contrast, other known techniques may involve the measurement of other parameters that require complex calculations (e.g. complex frequency calculations) in order to ascertain the operating condition of a pump. Not only may such methods be more prone to error because of their complexity, but may also be more time consuming and costly to perform. One action that a user may take to mitigate against operating in the choke operating condition is to limit the flow of a fluid through the pump20. Limiting of the fluid flow through the pump may have the effect of increasing the differential pressure across the pump20, which may bring the pump out of the choke operating condition and into the normal operating condition. In the example illustrated inFIG.1, this may be achieved by restricting flow through a valve downstream of the pump20. As illustrated, the discharge isolation valve40is located downstream of the pump20inFIG.1. Therefore closing, or partially closing, the discharge isolation valve40may have the effect of increasing the differential pressure across the pump as desired. In some examples, there may be a control system in place which may be configured to recognise the choke and surge conditions, and which may then be able to take appropriate action (e.g. by closing, or partially closing the discharge isolation valve40via an actuator, by reducing the pump speed, or the like) without direct intervention being required by a user. The monitoring of the pump conditions may feature means to circumvent raising of alarms at during normal pump operation conditions or planned events that may otherwise trigger an alarm to signal choke and/or surge operating conditions (e.g. such as during startup of the pump, intentional ramping up or ramping down of the rotor rotational speed, or periods of pump inactivity. These means may for example be the analysis of limited time windows, e.g. three to five seconds, a band-pass filter with a range of e.g. one half to five Hertz or a signal from the pump control to get a notification of planned events resulting in changes in the monitored pressure or axial rotor position, e.g. ramping up or down of the rotor speed as already described. The person skilled in the art realises that the disclosure ofFIGS.1to4is not limited to the preferred embodiments described in relation to those Figures. The person skilled in the art further realizes that modifications and variations are possible within the scope of the appended claims. Additionally, variations to the disclosed embodiments can be understood and effected by the skilled person in practicing the claimed disclosure, from a study of the drawings, the disclosure, and the appended claims. A Multiphase Pump and a Method of Pumping a Multiphase Fluid Now referring toFIGS.5to8B, there is provided an improved multiphase pump and method of pumping multiphase fluid. According to an example embodiment there is provided a multiphase pump, comprising: a housing comprising a flow inlet and a flow outlet fluidly connected by a flowpath; a rotor located in the flow path of the housing, configured to propel a fluid from the flow inlet to the flow outlet via the flow path, the rotor comprising a longitudinal axis extending the length of the rotor and a multiphase impeller; at least one leak path located in the multiphase pump, permitting reverse flow of a fluid from the flow outlet to the flow inlet; at least one channel defined within the housing, and configured to direct a liquid from a liquid source to one of the at least one leak paths in the multiphase pump. The multiphase pump may be used to transfer a multiphase fluid from one location to another. The multiphase fluid may be, for example, a hydrocarbon fluid, or may be an injection fluid, such as a surfactant. The pump may be used in a subsea location (e.g. a wellbore or subsea structure), or may be used on an offshore platform, or onshore hydrocarbon recovery plant. Having a channel defined in the housing to direct a liquid from a liquid source to a leak path may have the effect of greatly improving the efficiency of the multiphase pump. In some cases, there may be a leak path in the pump that is prone to permitting leakage of a fluid therethrough, for example leakage of a gas therethrough, from a high pressure region within the pump, to a lower pressure region in the pump. In cases where the leak path permits leakage of a gas, the flow rate of the gas leakage may be very high, which may be due to the gas having a low density. As a fluid leaks within the multiphase fluid, there will be a reduction in pressure of the leaked fluid, meaning that the multiphase pump will once again have to perform work on the fluid in order to increase its pressure for expulsion from the pump. As such fluid leakage may greatly reduce the efficiency of the pump, particularly when the leakage occurs at high flow rates, as is the case with gas leakage. One way to mitigate against this problem is to provide a supply of liquid to the leak path, thereby at least partially displacing the leaked gas, and reducing the flow rate of leakage fluid. In turn, this has the effect of improving the overall efficiency of the multiphase pump. To provide context to the described aspects and examples,FIG.5illustrates an example of a multiphase pump1010. The multiphase pump1010comprises a housing1012, which in this case comprises multiple parts. In particular, in this example, the housing comprises a first support housing1012aand a second support housing1012c, located at either axial end of the housing1012. The first and second support housings1012a,1012csupport a rotor1014, which itself comprises a drive shaft1016and a plurality of impellers1018. At least one of the first support housing1012aand the second support housing1012cmay comprise a bearing arrangement1020which supports an axial end of the drive shaft1016within the housing1012, and permits rotation of the drive shaft about its longitudinal axis1022. In some cases, both the first support housing1012aand the second support housing1012cmay comprise a bearing of the bearing arrangement1020, and may additionally comprise a drive arrangement for rotation of the drive shaft1016. The drive arrangement may be a motor, for example. The bearing arrangement1020may provide both axial and radial support to the drive shaft1016, and in this example the bearing arrangement comprises a thrust bearing. As can be seen inFIG.5, the housing1012additionally comprises an impeller housing1012b, which houses the mid-section of the drive shaft1016, as well as the plurality of impellers1018. In this example, the impeller housing1012bis modular and is comprised of a plurality of parts, although the skilled person will appreciate that having an impeller housing1012bcomprising one single part is also possible. As illustrated, several of the plurality of parts of the impeller housing1012bare substantially similar, which may facilitate manufacture of the impeller housing1012b. As will be described in more detail in the following paragraphs, the impeller housing1012bmay comprise a part or parts that are unique in their geometry. For example, here the impeller housing1012bcomprises a central support part1024that engages the drive shaft1016, and may provide support (e.g. radial support) to the drive shaft1016while facilitating rotation thereof. To permit the central support part1024to radially support the drive shaft1016, while enable rotation of the drive shaft1016, a bushing1026is located between the drive shaft1016and the central support part1024. The bushing1026may also provide a degree of sealing between the central support part1024and the drive shaft1016, to assist to prevent fluid leakage between the central support part1024and the drive shaft1016. In addition, the impeller housing1012bcomprises a connection part1028for connection of the impeller housing1012bto the second support housing1012c, which may comprise a motor, as described. As will be explained in further detail, the connection part1028may additionally assist to direct fluid flow from an inlet of the multiphase pump1030, and towards an outlet of the multiphase pump1032. In some examples, the central support part1024may be required to provide more support than in other examples. Where the drive shaft1016is thicker, then less radial support may be required than in cases where the drive shaft is thinner. In the illustrated example, the drive shaft is relatively thick, and therefore support of the rotor by the busing1026may not be strictly necessary. In addition, having a thicker drive shaft (e.g. one that requires no support from the bushing1026) may also assist the pump1010to operate in dry conditions (e.g. conditions where there is no, or very little, liquid flow in the pump), as the shaft may rely less, or not at all, on radial support provided by a liquid being pumped. The relative thickness of the drive shaft1016may be a function of the length of the drive shaft1016. In this case, having a modular impeller housing1012bcomprised of a plurality of parts may provide the user flexibility to have a varying number of impellers on the shaft, depending on the head required by the multiphase pump. Additionally, this feature may provide a multiphase pump1010that is more easily manufactured than if the housing were to be provided in a single part. As previously described, the rotor1014comprises both a drive shaft1016and a plurality of impellers1018, which may be considered to be an impeller arrangement. In this example, the impeller arrangement may comprise a combination of multiphase impellers (i.e. impellers that are suitable for use in pumping a multiphase fluid, for example one containing both a liquid and a gas fraction) and single-phase impellers may be present. As such, this multiphase pump1010may be considered to be a hybrid multiphase pump. The impellers1018may be arranged such that the multiphase impellers are positioned towards the inlet, while single-phase impellers are positioned towards the outlet, such that multiphase impellers are used to pump (e.g. increase the pressure of) a fluid initially upon entry via the inlet, while single-phase impellers are used to increase the pressure of a fluid thereafter as the fluid flows towards the outlet. In some other examples, the use of a multiphase pump1010having only multiphase impellers may be possible. Having a hybrid multiphase pump may permit a fluid to be pumped with improved differential pressure generation, and improved efficiency. A hybrid multiphase pump may be used in cases where a fluid to be pumped has a lower gas fraction (e.g. from 10 to 50 percent Gas Volume Fraction (GVF)). As the fluid is compressed by the multiphase impellers, the GVF may decrease, such that as the fluid reaches the single-phase impellers, the GVF may be in the range 5-15%. In this range of GVF, a single-phase impeller may be able to effectively pump a multiphase fluid. According to this disclosure, each of the multiphase impellers and each of the optional single-phase impellers may have substantially the same geometry, with each of the multiphase impellers having a generally frustoconical shape. As can be seen in this example, the impellers are oriented such that the central axis of each of the impellers1018is aligned with the axis1022of the drive shaft1018. The impellers are designed such that a fluid flows from the smaller diameter end of the each impeller1018and towards the larger diameter end. In this example, each impeller1018comprises a solid frustum-cone shape with at least one channel therein, extending in both an axial and radial direction through the impeller1018. The skilled person will also appreciate that there may be some examples in which there is no diametrical difference in the impellers, such that the diameter of the side of fluid entry to the impeller1018is the same as the diameter of the side of fluid exit from the impeller1018. Upon exit from each impeller1018, the multiphase fluid may have both an axial and a radial component of velocity. The axial component of velocity, or a majority of the axial component of velocity, may be considered to be acting in a direction that is tangential to the blades of each impeller1018. Additionally, the axial component of the velocity may be the important component of velocity for driving a fluid through the multiphase pump1010, and generating the head of the multiphase pump1010. To assist in passing the multiphase fluid through the multiphase pump1010, the multiphase pump1010may comprise a fluid diffuser1034located axially adjacent at least one impeller1018. For example the multiphase pump1010may comprise a fluid diffuser1034located axially between every two impellers1018on the drive shaft1016. The fluid diffuser1034may assist to direct fluid from the outlet of a one impeller1018to the inlet of the following impeller1018. Between each fluid diffuser1034and the drive shaft may be a seal or arrangement of seals, and/or a bushing to assist in permitting rotation of the drive shaft1016relative to each fluid diffuser1034. In the example shown, the impellers1018may be coupled to the drive shaft1016, or they may be integrally formed with the drive shaft1016. Either side of the central support part1024are located a plurality of impellers1018according to this example. On one side of the drive shaft1016, which may be the proximal side of the drive shaft1018to the inlet1030and/or the first support housing1012a, the impellers1018may be configured such that each of the impellers1018faces a first direction, while on the opposite side of the drive shaft, which may be the distal side of the drive shaft to the inlet1030and/or the second support housing1012c, the impellers1018may be configured such that each of the impellers1018faces a second direction, which may be opposite to the first direction. The impellers1018facing the first direction may be considered to be a first impeller arrangement, while the impellers1018facing the second direction may be considered to be a second impeller arrangement. In this example, each of the impeller arrangements are configured to move a multiphase fluid being pumped towards the central support part1024. As will be described in further detail herein, the housing1012comprises a conduit, which may be defined by the housing1012itself, to transfer a multiphase fluid from an outlet1036of the first impeller arrangement to an inlet1038of the second impeller arrangement. The conduit may extend through the central support part1032and through the impeller housing1012btowards the connection part1028. The inlet1038of the second impeller arrangement may be located in the connection part1028, where the multiphase fluid may be delivered form the outlet1036of the first impeller arrangement. In this example, the first impeller arrangement is configured to receive fluid from the inlet1030at an inlet pressure, and pressurise the fluid to a mid-pressure as it is moved from the inlet towards the central support part1024and the outlet1036of the first impeller arrangement. Once the fluid reaches the outlet1036of the first impeller arrangement, the conduit (which in this case is defined by the housing) carries the mid-pressure multiphase fluid from the outlet1036of the first impeller arrangement to the inlet1038of the second impeller arrangement. The second impeller arrangement is then configured to move the multiphase fluid in a direction towards the central support part1024and towards the outlet1032. Once the multiphase fluid reaches the outlet1032, the multiphase fluid will be at the outlet pressure, which is the pressure of the multiphase fluid that is desired by a user. As such, a flow path may exist within the multiphase pump1010from the inlet1030to the outlet1032via the first impeller arrangement and the second impeller arrangement. Having a drive shaft1016with a first and second arrangement of impellers1018having opposite orientations may assist to balance forces (e.g. thrust forces) acting on the drive shaft1016as a result of the rotation of the impellers1018providing oppositely directed forces on either side of the bushing1026. As such, this arrangement may assist to minimise forces acting on, for example, a thrust bearing or bearings of the bearing arrangement1020which may improve operation, and prolong the lift, of the thrust bearings of the bearing arrangement1020. Such an arrangement may be known as a back-to-back impeller arrangement. Due to the nature of the back-to-back impeller arrangement, there may be a high pressure differential acting across the central support part1032, between the outlet1036of the first impeller arrangement and the outlet of the second impeller arrangement, leading to the outlet1032of the multiphase pump1010. In particular, the pressure acting across the central support part1032may be equal to the difference between the multiphase fluid at mid-pressure and at outlet pressure, which may be significant. As such, the bushing1026may provide significant sealing capacity in order to restrict fluid leakage through the central support part1032—in particular at the interface between the drive shaft1016and the central support part1032. Other techniques may be additionally employed to restrict fluid leakage, as will be described in the following paragraphs. As is illustrated, the housing1012comprises a cavity which has a shape corresponding to the rotor1014, so as to house the rotor therein. In particular, the cavity inside the housing may have a diameter that changes with the axial position along the housing, so as to accommodate each of the impellers1018and flow diffusers1034, while maintaining a low clearance between the rotor1014and the housing1012itself. Due to this low clearance, it may be necessary to include a wear ring between each impeller1018and the surrounding housing1012, to reduce wear on both the housing1012and impeller1018. The wear ring may be provided at least between the housing and the smaller diameter end of each frustoconical impeller1018. In some examples, the wear ring may additionally provide a degree of sealing between the relevant impeller1018and the surrounding housing1012. In this way, the wear ring may assist to prevent backflow of the multiphase fluid through the multiphase pump1010. As the rotor1014rotates within the housing, a centrifugal force may act upon the multiphase fluid as it flows through the flow path which may be defined the housing1012. Due to the multiphase fluid being comprised of fractions having differing densities, the centrifugal force may have the effect of at least partially separating the multiphase fluid into a liquid and a gas fraction, with the liquid fraction being located in a radially outer zone of the flow path, while the gas fraction may be located in a radially inner zone of the flow path, for example the zone surrounding the drive shaft1016. FIG.6Aillustrates the multiphase pump1010as previously described contained within an external pressure housing1040. The positioning of the inlet1030and the outlet1032can be more clearly viewed inFIG.6Aas compared toFIG.5. As can be seen, each of the inlet1030and the outlet1032have a corresponding attachment mechanism1030a,1032afor attachment of a conduit or device thereto. In this case, the attachment mechanisms1030a,1032aare suitable for bolting a flange thereto, although the skilled reader will appreciate that other attachment mechanisms may be possible. In order to prevent fluid leakage from the outlet1032to the inlet1030in the annulus between the pressure housing1040and the multiphase pump1010, the multiphase pump may engage the pressure housing1040at at least one location axially between the inlet1030and the outlet1032, and a seal or arrangement of seals may be located between the multiphase pump1010and the pressure housing1040. InFIG.6B, there is illustrated the rotor1014ofFIG.5. As can be seen, the rotor1014comprises eight impellers1018coupled to the drive shaft1016. In other examples, the impellers1018may be integrally formed with the drive shaft1016, and there may be more or fewer than eight. As previously described, the impellers1018are divided into a first and a second impeller arrangement. According to this example, each of the first and second impeller arrangements comprise an equal number of impellers1018, which here is four. The drive shaft1016additionally comprises sections of increased diameter1042, which may be treated or polished to minimise interference with the housing1012when the driveshaft rotates. For example, these sections1042may have a more polished surface to assist in sealing and to reduce wear between the drive shaft1016and the housing1012, and/or may comprise a different material to the rest of the drive shaft, which may be a harder material, to reduce the effect of wear on these parts of the drive shaft1016. FIGS.7A and7Billustrated cross-sectional views of sections of the multiphase pump1010, showing a channel1044for directing a liquid from a liquid source to a leak path1046in the multiphase pump1010. In the case ofFIG.7A, the leak path1046is located in the central support part1032adjacent the bushing1026, and in the direction from the outlet of the second impeller arrangement to the outlet of the first impeller arrangement, between which there may be a significant pressure difference. While the bushing1026may assist to provide a degree of sealing, due to the high pressure differential that may act across the bushing1026, some degree of leakage may be present. As the bushing1026surrounds the drive shaft1016, as the rotor1014(seeFIG.5) rotates, then the bushing1026may be located in a radially inner zone of the flow path. As previously described, the radially inner zone of the flow path may comprise a higher proportion of the gas fraction of the multiphase fluid, and therefore the leakage through the central support part1032may be mainly leakage of gas. This type of leakage (e.g. gas leakage) may be particularly problematic, as it may occur at high flow rates compared to leakage of a liquid. Further, any fluid leaking from the outlet of the second impeller arrangement to the outlet of the first impeller arrangement will experience a pressure drop from the outlet pressure to the mid-pressure at the outlet of the first impeller arrangement. This leaked fluid will require to be pressurised again, thereby reducing the efficiency of the pump. In order to reduce the flow rate of leaked fluid, the channel1044may be used to direct fluid flow from a zone of high-density flow (which may be liquid-rich flow) within the flow path. As previously described, due to the centrifugal force acting on the multiphase fluid, the fluid flow may form a higher-density zone at a radially outer region in the flow path, and a lower-density zone at a radially inner region of the flow path. As such there may be likely to be a higher proportion of the liquid fraction of the multiphase fluid at radially outer zones in the flow path. Therefore, in this example, the channel1044comprises an inlet1044alocated in a radially outer region of the flow path. In particular, here the outlet is located at the outlet of the second impeller arrangement, at the region of the flowpath and the final impeller1018of the second impeller arrangement where the diameter is widest. The channel1044also comprises an outlet1044blocated adjacent the bushing1026, at the side of the busing axially proximate the outlet of the second impeller arrangement. In this example, the channel1044is defined by the housing, in particular the impeller housing1012b. However, in some examples, the channel may be entirely defined by a conduit which may be contained within the housing. Having a channel1044as defined inFIG.7Amay assist to provide a source of liquid to the bushing1026. The liquid may displace any gas that was leaking through a leak path at the bushing1026. As the liquid fraction is of a greater density (and a greater viscosity) than the gas fraction, then the volume flow rate of the leaked liquid will be less than that of the leaked gas, meaning that there will be a smaller volume of fluid requiring to be repressurised as a result of the leak path. As such, having the channel1044may have the effect of increasing the efficiency of the multiphase pump1010. In addition, the provision of a liquid at the bushing1026may improve lubrication of the bushing1026, and may in some cases increase the dissipation of heat from the bushing as a result of friction from the rotating drive shaft1016—for example where some contact with the rotating drive shaft1016occurs as a result of general wear within the multiphase pump1010. Illustrated inFIG.7Bis an example of a multiphase pump1010, having a channel1144different to that as previously illustrated. As in the previous example, this channel is also defined by the impeller housing1012b, and the inlet1144aof the channel is located at a radially outer region of the flow path. As before, in particular the inlet1144aof the channel is located at the outlet of the second impeller arrangement, at the region of the flowpath and the final impeller1018of the second impeller arrangement where the diameter of the frustoconical impeller1018is the widest. In contrast, in this example the outlet of the channel1144bis located adjacent the smaller diameter end of the final impeller of the second impeller arrangement, which is located in a radially inner region compared to the channel outlet1144b. As previously described, the smaller diameter end of the final impeller may comprise a wear ring1048located radially adjacent thereto to reduce wear between the housing1112and the impeller1118, and which may also provide some degree of sealing between the impeller1118and the housing1112to prevent backflow of a fluid therethrough. However, the wear ring1148may also be the source of a leak path, which may be significant given that the wear ring may be located at a radially inner region of the flow path. As such, the presence of channel1144may assist to reduce the volume of leaked fluid, by displacing the leakage of gas with the leakage of liquid, as described in relation toFIG.7A. Similarly, the fluid may have a lubricating effect on the wear ring1148. As before, the channel1144is defined by the housing1112. However, it may be possible to define the channel1144by a conduit located in the housing, or by other means. While the channel1144is shown in respect of only one impeller1118in the multiphase pump1010, such a channel may be repeated for each impeller of the multiphase pump, thereby further improving the efficiency of the multiphase pump. Illustrated inFIGS.8A and8Bshow examples of a multiphase pump1210having a channel1244defined therein, that may be supplied by a liquid provided from a source external to the housing1212of the multiphase pump1010. In both cases, the outlet1244bof the channel1244is located adjacent bushing1226, similar to the example ofFIG.7A. However, the channel inlet1244ais located on an external surface of the housing1212. In the case ofFIG.8Athe inlet1244ais provided by a fluid source located between the housing1212and the pressure housing1240, while in the case ofFIG.8B, the fluid inlet1244ais provided with a source of fluid from a liquid tank. In this case, the liquid tank is a receptacle for the fluid exiting the multiphase pump1210, and therefore may be at or close to the outlet pressure of the pump1212. However, the skilled person will understand that other external sources of liquid may equally be plausible. The person skilled in the art realises that disclosure ofFIGS.5to8Bis not limited to the preferred embodiments described in relation to these Figures. The person skilled in the art further realises that modifications and variations are possible within the scope of the appended clauses. Additionally, variations to the disclosed embodiments can be understood and effected by the skilled person in practicing the disclosure, from a study of the drawings, the disclosure, and the following set of clauses. Some examples and aspects will now be described in the following numbered, non-limiting, clauses: CLAUSE A1. A multiphase pump1010, comprising:a housing1012comprising a flow inlet1030and a flow outlet1036fluidly connected by a flowpath;a rotor1014located in the flow path of the housing1012, configured to propel a fluid from the flow inlet1030to the flow outlet1036via the flow path, the rotor1014comprising a longitudinal axis1022extending the length of the rotor1014and a multiphase impeller arrangement1018;at least one leak path1046located in the multiphase pump1010, permitting reverse flow of a fluid from the flow outlet1036to the flow inlet1030; andat least one channel1044defined within the housing1012, and configured to direct a liquid from a liquid source to one of the at least one leak paths1046in the multiphase pump1010. CLAUSE A2. The multiphase pump1010according to clause A1, wherein the rotor1014comprises a drive shaft1016and the multiphase impeller arrangement1018is coupled to the drive shaft1016. CLAUSE A3. The multiphase pump1010according to clause A2, wherein the housing1012radially supports the drive shaft1016of the rotor1014via a bushing1026at an at least one engagement location, the bushing1026being located between the rotor1014and the housing1012. CLAUSE A4. The multiphase pump1010according to clause A3, wherein one of the at least one leak paths1046is located between the drive shaft1016and the housing1012at the at least one radial support location. CLAUSE A5. The multiphase pump1010according to any preceding clause, comprising a wear ring1048located between the multiphase impeller arrangement1018and the housing1012, and wherein one of the at least one leak paths1046is located between the wear ring1048and the multiphase impeller arrangement1018. CLAUSE A6. The multiphase pump1010according to any preceding clause, comprising a plurality of leak paths1046and a plurality of channels1044connecting a liquid source to the plurality of leak paths1046in the multiphase pump1010. CLAUSE A7. The multiphase pump1010according to any preceding clause, wherein the flow path comprises a higher-density zone located in a radially outer region of the flow path, and a lower-density zone located in a radially inner region of the flow path. CLAUSE A8. The multiphase pump1010according to clause A7, wherein the fluid source is at least partially defined by the higher-density zone of the flow path. CLAUSE A9. The multiphase pump1010according to clause A8, wherein the channel1044comprises an inlet1030located adjacent the higher-density zone so as to be in fluid communication therewith. CLAUSE A10. The multiphase pump1010according to any of clauses A7 to A9, wherein the housing1012comprises at least one location of reduced diameter, and wherein the housing1012engages the rotor1014at the at least one location of reduced diameter, and the engagement between the housing1012and the rotor1014is located in the radially inner lower-density zone of the flow path. CLAUSE A11. The multiphase pump1010according to clause A10, wherein the channel comprises an outlet1036at the location of engagement between the housing1012and the rotor1014and one of the at least one leak paths is located at the location of engagement between the housing1012and the rotor1014, such that the channel1044directs a liquid from the higher-density zone to the location of engagement between the housing1012and the rotor1014. CLAUSE A12. The multiphase pump1010according to any preceding clause, wherein the fluid source is at least partially defined by a source of liquid external to the multiphase pump1010, and the channel1044comprises an external inlet located on an external surface of the multiphase pump1010. CLAUSE A13. The multiphase pump1010according to any preceding clause, wherein the flow inlet1030and the flow outlet1036are defined by the housing1012, and the flow outlet1036is located at a midpoint along the longitudinal axis1022of the rotor1014. CLAUSE A14. The multiphase pump1010according to any preceding clause, wherein the rotor1014comprises at least two multiphase impeller arrangements, each of the multiphase impeller arrangements having opposite orientations, such that a first impeller arrangement is configured to impart a velocity to a fluid in a first direction parallel to the longitudinal axis1022, and a second impeller arrangement is configured to impart a velocity to a fluid in a second opposite direction parallel to the longitudinal axis1022. CLAUSE A15. The multiphase pump1010according to clause A14, wherein the housing1012comprises at least one location of reduced diameter, and wherein the housing1012engages the rotor1014at the at least one location of reduced diameter, and wherein the first impeller arrangement is located on a first axial side of the engagement between the housing1012and the rotor1014, and the second impeller arrangement is located on a second axial side of the engagement between the housing1012and the rotor1014. CLAUSE A16. The multiphase pump1010according to clause A14 or A15, wherein the flow inlet1030comprises a direct fluid connection to an inlet of the first impeller arrangement, the flow outlet1036comprises a direct fluid connection to an outlet1036of the second impeller arrangement, and an outlet of the first impeller arrangement and an inlet of the second impeller arrangement are in direct fluid connection via a connection conduit, the connection conduit being optionally defined by the housing. CLAUSE A17. The multiphase pump1010according to any one of clauses A14 to A16, wherein the first impeller arrangement is configured to pressurise a fluid from an inlet pressure to a mid-pressure, and the second impeller arrangement is configured to pressurise a fluid from the mid-pressure to an outlet pressure. CLAUSE A18. A method of pumping a multiphase fluid, comprising:providing a multiphase pump1010, the multiphase pump1010defining at least one channel1044therein configured to direct fluid from a liquid source to a leak path in the multiphase pump1010;operating the multiphase pump1010to pump a multiphase fluid from a flow inlet1030of the multiphase pump1010to a flow outlet1036of the multiphase pump1010; directing fluid from a liquid source to a leak path in the multiphase pump1010via a channel defined in the multiphase pump1010. A Subsea Pump and Method for Determining Motion of the Rotor Now referring toFIGS.9to11C, there is provided an improved subsea pump. According to an example embodiment there is provided a subsea pump, comprising: a housing; a rotor located inside the housing, a bearing arrangement being located between the rotor and the housing to facilitate rotation of the rotor therein, and the rotor comprising a motion indicator; a motion sensing arrangement comprising a pressure sealed housing and at least one sensor, the motion sensing arrangement being located inside the housing and in communication with the motion indicator, and the motion sensing arrangement being configured to detect movement of the motion indicator. The subsea pump may be used in a subsea location, which may be a downhole location, while the motion sensing arrangement and motion indicator may be able to provide the user with information regarding the operation of the pump. As will be described, the motion sensing arrangement may be configured to measure rotational, axial and radial movement of the rotor and may provide this information to a user to allow assessment of the performance of the subsea pump. In some examples, the motion sensing arrangement enable a user to measure the axial and/or rotational vibration of the rotor of the subsea pump, which may also be an indicator of the performance of the subsea pump. FIG.9illustrates a cross-sectional view of an exemplary subsea pump2010. In this example, the subsea pump2010is a multiphase pump such as a helico-mixed flow pump, or possibly a helico-axial pump. However, with regard to the description herein, the skilled person will appreciate that many of the described features and examples may be applicable to other types of subsea pumps, which may not be multiphase pumps, for example axial and/or centrifugal pumps and axial and/or centrifugal compressors. In this example, the subsea pump2010comprises an outer housing2012, and an inner housing2014. The outer housing2012of this example is comprised of two parts, which are connected together at a connection interface2032by a bolted flange arrangement, although the skilled reader will understand that other forms of connection arrangement may be possible such as a threaded connection, or a chemically bonded connection. While the outer housing contains a pump inlet2016and outlet2018and defines a flow path extending outside of the inner housing2014, the inner housing2014supports and contains moving components of the subsea pump2010. For example, as shown inFIG.9, the inner housing2014may support a drive shaft2020, having an impeller arrangement2022coupled thereto, and a drive arrangement2026which may be in the form of a motor such as an electrical motor. The configuration of the inner housing2014may be such that the drive shaft2020extends the entire length of the inner housing2014, or substantially the entire length of the inner housing2014, while the impeller arrangement2022may be confined to one axial side of the drive shaft2020, and the drive arrangement2026may be confined to an opposite side of the drive shaft2020, as is the case in this example. As such, the inner housing2014may be able to be divided into a drive section2028and a pumping section2030. Here, the inner housing2014contains a plurality of bearing arrangements2024—in this case four bearing arrangements2024a-d—which are located between the inner housing2014and the drive shaft2020. The bearing arrangements2024a-denable engagement between the inner housing2014and the drive shaft2020, and facilitate rotation of the drive shaft2020in the inner housing2014. Of the four bearing arrangements2024a-d, two are located in the drive section2028of the inner housing2014, while another two are located in the pumping section2030of the inner housing2014. Together, the bearing arrangements2024a-dsupport the entire drive shaft along its length and facilitate rotation thereof relative to the inner housing2014. The bearing arrangement may be or comprise any suitable type of bearing, for example a rotary bearing such as a thrust bearing. In this example, the inner housing2014is secured to the outer housing2012at a plurality of locations, such that the inner housing2014remains static relative to the outer housing2012during operation of the subsea pump2010. It can additionally be seen, in this example, that the impeller arrangement is divided into two sets2022a,2022b. The orientation of the impellers in the first set2022ais opposite to the orientation of the impellers in the second set2022b, such that the impellers are arranged in a back-to-back configuration. In doing so, some or all of the axial thrust caused by the first set2022ais cancelled or offset by an oppositely directed thrust from the second set2022bof impellers, thereby reducing the magnitude of any unbalanced axial force acting on the drive shaft2020as a result of the impellers2022. FIG.10Aillustrates an example of a motion sensing arrangement2040that may be used to detect motion in the subsea pump2010, such as motion of the drive shaft2020relative to the inner housing2014. The motion sensing arrangement2040as illustrated may be attached (e.g. fastened, bonded or coupled) to the inner housing2014, and located in proximity to the drive shaft2020such that the motion sensing arrangement2040is able to detect motion of the drive shaft2020. The motion sensing arrangement2040may be used to detect one, or more than one, aspect of motion of the drive shaft2020. For example, the motion sensing arrangement2040may be used to detect at least one, or all, of rotational, radial and axial movement of the drive shaft2020. The motion sensing arrangement2040may be used to detect vibration of the drive shaft2020, for example radial and/or axial vibration. The motion sensing arrangement may additionally be configured to detect an indicator used for vibration analysis, for example a once-per-revolution indicator for vibration analysis. The housing2012may contain a motor located therein, or may comprise a motor coupled thereto. The motor may comprise a drive arrangement for turning the drive shaft2020, and in some examples a motion sensing arrangement2040may be positioned so as to detect motion of the drive arrangement of the motor. In this way, the motion sensing arrangement2040may additionally or alternatively be used to detect motion of a motor. As illustrated inFIGS.10A-B, the motion sensing arrangement2040has the shape of a partial annulus. Here, the motion sensing arrangement2040has a shape between a quarter-annulus and a semi-annulus. The motion sensing arrangement2040may extend circumferentially anywhere from between 90 degrees and 180 degrees through an annulus. For example, anywhere from between 100 degrees to 170 degrees, between 110 degrees and 160 degrees, between 120 degrees and 150 degrees, between 130 degrees and 140 degrees, or the like. For example, the motion sensing arrangement2040may extend circumferentially 135 degrees through an annulus. In this example, the motion sensing arrangement2040may be shaped so as to fit around the drive shaft2020, and as such may comprise a radially inner and radially outer surface2044a,2044b, two axial surfaces2046a,2046band two circumferential surfaces2048a,2048b. This shape of motion sensing arrangement2040may be particularly beneficial as it may fit easily into a cylindrical or annular recess within the inner housing2014. In particular, having an annular or partial annular shape of motion sensing arrangement2040may permit the motion sensing arrangement2040to fit easily in an annulus defined between the drive shaft2020and the inner housing2014, while also permitting a large surface area of the drive shaft2020to be monitored. The skilled person will appreciate that other shapes of motion sensing arrangement2040may be possible, such as a cubic or cuboid shape, or a cylindrical shape. The shape of the motion sensing arrangement2040may be defined by a sensor housing2047. The sensor housing2047may be coupled (e.g. attached, affixed, bonded, or the like) to the inner housing2014(seeFIG.9) using bolts, chemical bonding, snapfits, or any other appropriate means. The sensor housing2047may be precisely fitted on the inner housing2014so as to permit the motion sensing arrangement2040to be installed in the subsea pump2010in a precise location relative to the drive shaft2020. As such, the distance between the motion sensing arrangement2040may be known, and therefore reconfiguration of sensors in the motion sensing arrangement2040after having been fitted to the inner housing2014may not be necessary. The sensor housing2047may contain electronic components of the motion sensing arrangement as well as at least partially, or fully, housing sensors of the motion sensing arrangement. The sensor housing2047may be sealed to both pressure and water. The sensor housing2047may contain sensors such as temperature sensors, and the temperature sensors may be considered to be part of the motion sensing arrangement. The temperature sensors may be located inside the sensor housing2047, and may be in the form of an integrated temperature measurement system within the housing. The integrated temperature measurement system may be used for signal correction purposes, as well as general condition monitoring of the sensing arrangement2040. The housing may additionally be sufficiently strong to withstand high pressures associated with subsea and/or downhole locations. For example, the housing2047may have a minimum thickness so as to be able to withstand the high pressure of subsea/downhole environments. In some examples, the subsea pump2010may be exposed to pressures in the range of 2300 to 1000 bar. In cases where the pump2010is shut-in, then the pressure may be particularly high (e.g. 1000 bar or higher) and as such the thickness of the housing2047may be selected based on this requirement. Additionally, any sealing involved in the housing may be selected based on this requirement. The motion sensing arrangement2040may comprise one, or a number, of sensors for detecting motion (e.g. a motion sensor or motion sensors such as an eddy-current sensor, capacitive sensor and/or an optical sensor). InFIG.10, the motion sensing arrangement comprises three sensors2042a,2042b,2042c. One sensor, hereinafter referred to as an axial sensor2042a, is located on one of the axial surfaces2046aof the motion sensing arrangement2040, while two sensors2042b,2042cc(hereinafter referred to as radial sensors) are located on the inner radial surface2044aof the motion sensing arrangement2040. Each of the sensors2042a-cmay be of the same type, or at least one or all of the sensors2042a-cmay be of differing types. In some examples, the sensors may also transmit a signal, the transmitted signal being used to detect motion. For example, in this example, the sensors2042a-cmay transmit an electromagnetic field or a beam of electromagnetic radiation, and may then sense an electromagnetic return signal, with changes in the electromagnetic return signal indicating motion of an object. In one example, at least one or all of the sensors2042a-cmay be motion sensors such as optical sensors, eddy-current sensors and/or capacitive sensors. In one example, at least one or all of the sensors may be in the form of proximity probes. In another example, some sensors may be proximity probes, while other sensors may be capacity probes. The sensor2042alocated on the axial surface2046aof the motion sensing arrangement2040may be considered to be an axial sensor2042a. When the motion sensing arrangement2040is positioned in proximity to the drive shaft2020, the axial sensor2042may be able to be used to sense at least one of axial and rotational movement of the drive shaft2020. The sensors2042b,2042cthat are located on the radially inner surface2044aof the motion sensing arrangement2040may be considered to be radial sensors2042b,2042c. The radial sensors may be able to be used to sense rotational movement of the drive shaft2020. In this example, the radial sensors2042b,2042cmay be offset by an angle, and positioned on the inner axial surface2044a. In this example, the angle of offset is approximately 90 degrees, which may be a preferable configuration for sensing radial movement of the drive shaft2020, as it may provide information of radial movement of the drive shaft2020in two directions (e.g. in the direction of an x-axis and in the direction of a y-axis). However, the skilled person will understand that other angles of offset may be possible if desired. In this example, each of the sensors2042a-care used to sense or detect movement of a motion indicator. The motion indicator may simply be a surface of the drive shaft2020. In some examples, the motion indicator may comprise a surface feature such as a depression and/or a protrusion, or may comprise a plurality of surface features such as a plurality of depressions and/or protrusions. The surface feature or features may be located on the drive shaft, in some examples. Although not shown in the Figures, the rotor may comprise a radially extending protrusion therefrom, for example a radially extending protrusion from the drive shaft2020. The radially extending protrusion may be in the form of a disc, or a partial disc, extending from the drive shaft2020, and the disc may be axially aligned with the drive shaft2020. The radially extending protrusion may be or form part of the motion indicator. For example, the motion indicator may be formed by the combination of the drive shaft (or a portion thereof) as well as the radially extending protrusion. The motion sensing arrangement2040may be positioned in the inner housing2014radially outwardly of the drive shaft2020. Where the motion sensing arrangement2040has an annular or partially annular shape, then the axis of the motion sensing arrangement2040may be aligned with the axis of the drive shaft2020, such that the radial surfaces2044a,2044brun generally parallel to the outer surface of the drive shaft2020. Each of the sensors may be positioned adjacent and/or in close proximity to a surface of the motion indictor. For instance, a sensing surface of each of the sensors2042a-cmay be positioned parallel to a surface of the motion indicator. Each of the radial sensors2042b,cmay be positioned parallel to a surface of motion indicator on the drive shaft, while the axial sensor2042amay be positioned parallel to a surface of the motion indicated on the radially extending protrusion. In some examples, the axial sensor2042amay be able to measure the axial movement of the rotor (e.g. relating to the axial position of the rotor, or to axial vibration of the rotor) by sensing a change in the distance between the sensor2042a, which may be coupled to the inner housing2014via the motion sensing arrangement2040. The axial sensor2042amay also be able to sense rotational movement of the rotor by sensing rotational movement of the radially extending protrusion, which may be in the form of a disc. The radially extending protrusion may comprise a surface feature, or a plurality of surface features thereon. The surface features may be in the form of one or more protrusions such as ribs, nipples and/or grooves, and/or may be in the form of one or more recesses, which may be of varying depth, height and/or width. In such an example, the radially extending protrusion may be considered to be a coded target disc, the rotation of which may be detected by the axial sensor2042a. As the rotor rotates, so too will the radially extending protrusion, and the axial sensor2042ais able to sense movement of the radially extending protrusion. Where there are surface features comprised on or defined by the radially extending protrusion, the axial sensor2042amay be able to detect differences in the geometry of each of these surfaces as they move, which may provide additional detail to a user regarding the nature of the rotational and/or axial movement of the rotor. For example, the axial sensor2042amay be able to provide information on the direction of rotation of the rotor (e.g. clockwise or anti-clockwise rotation of the rotor), thereby enabling the user to react quickly, for example, in a situation in which the rotor was rotating in the wrong direction. The radial sensors2042b,2042cmay be configured to detect rotational movement of the rotor by detecting rotational movement of the drive shaft2020. The drive shaft may comprise one or a plurality of surface features (e.g. one or a plurality of protrusions thereof and/or one or a plurality of recesses) thereon, and the radial sensors2042b,2042cmay be able to detect movement of the surface features on the drive shaft2020. The surface features may comprise protrusions and or recesses of different sizes (e.g. width, height or depth). As the drive shaft2020rotates, the radial sensors may be able to detect movement, as well as differences in the sizes of each of the surface features, which may provide additional detail to a user regarding the nature of the rotation of the drive shaft2020, and therefore the rotor. In some examples, the radial sensors2042b.2042cmay be able to provide information on the direction of rotation of the rotor (e.g. clockwise or anti-clockwise rotation of the rotor), as previously mentioned enabling the user to react quickly, for example, in a situation in which the rotor was rotating in the wrong direction. In addition, the radial sensors2042b,2042cmay be able to detect radial movement (e.g. radial vibration) of the rotor by detecting radial movement of the drive shaft2020. Similar to as previously described, the surface features may assist the radial sensors2042b,2042cto provide information relating to the radial movement of the drive shaft relative to the interior housing2014as a result of differing geometry of the surface features. In use, there may be several motion sensors2042a, b, c(e.g in the form of a or several motion sensing arrangement/s) located inside the interior housing and providing information regarding the movement of the rotor in at least one, more than one, or all of rotational, axial and radial movement. In one example, there may be a sensing arrangement2040located at or adjacent each of the bearing arrangements2024a-d(seeFIG.9). The sensors may then be used to provide a user with information regarding the motion of the rotor in the subsea pump2010, and therefore provide an indication on the functioning of the subsea pump without the need for a physical inspection of the pump2010. In particular, the motion sensing arrangement or arrangements2040may provide a user with information on the direction of rotation of the rotor. Such information may be highly critical for safe operation of a subsea pump2010. In having at least one motion sensing arrangement2040, a user may be able to have direct information regarding the direction of rotation of the rotor, for example, without having to deduce such information from calculations. As such, the sensing arrangement or arrangements2040may provide an inherently safe means of monitoring the behaviour of the rotor. Although not explicitly shown inFIG.10A, the motion sensing arrangement2040may comprise at least one pressure and/or temperature sensor, each of which may be located on an external surface thereof. The pressure and temperature sensor or sensors may provide a user with information regarding the pressure and temperature surrounding the motion sensing arrangement2040, which may be indicative of the pressure inside the subsea pump2010, thereby providing information on the operating condition of the subsea pump. In addition to the sensors2042a-c, the motion sensing arrangement2040may comprise a connection means2045(e.g. a connection point) for the physical and/or wireless connection of cabling for power and/or communications purposes. For example, the connection point2045may be used to provide electrical, and optionally fibre optic, cabling for the purposes of providing power to the motion sensing arrangement, as well as permitting input and output signals to be relayed to and from the motion sensing arrangement2040(e.g for communicating with the motion sensing arrangement2040) and may be used to relay signals from the sensors2042a-cto a location external to the motion sensing arrangement2040, e.g. to be sent to a user via cabling, or via wireless communication. In some examples, the motion sensing arrangement may comprise a signal amplifier, for example located inside the sensor housing2047. The motion sensing arrangement2040may comprise an integrated signal electronic conditioning system comprising amplifiers located inside the sensor housing2047. Having amplifiers within the motion sensing arrangement2040may permit the output signals being relayed to the connection means2045of the motion sensing arrangement2040to be very robust, and may be less affected by electric and magnetic noise, such as that from a motor. Having a sealed sensor housing2047(e.g. a pressure sealed housing) may enable a user to have such a system inside the sensor housing2047without experiencing damage during operation. It may be necessary for the sensor housing2047to comprise an aperture, or a number of apertures therein. For example, the connection point2045may require the housing to have an aperture therein, as may each of the sensors2042a-c. The sensor housing2047may comprise a sealing arrangement configured to prevent ingress of fluid (e.g. water or hydrocarbons) therein. In each the case of each aperture in the sensor housing2047, there may be a seal, or a plurality of seals. In some examples the housing may be hermetically sealed. The housing may be hermetically sealed by being hermetically welded. As such, production of the motion sensing arrangement2040(and the sensor housing2047thereof) may involve a step of hermetically sealing the housing by a hermetic welding process. In some examples, each aperture may comprise at least one O-ring style static seal extending around the periphery thereof to prevent ingress of fluid therethrough. Such sealing of the sensor housing2047, in this example by hermetic welding means, may provide an extremely robust solution with minimal risk of leakage, thereby enabling components of preferable quality and lifespan to be used inside the sensor housing2047. In contrast, known methods of sealing a sensor housing2047may rely on long, pressure-tight conduits and connections, which may be complex to manufacture, and provide an inferior seal, thereby also having an impact on the components that may be used inside the sensor housing2047. Illustrated inFIG.10Bis a side view of two motion sensing arrangements2040. As can be seen, each of the two motion sensing arrangements2040are arranged to form a central void2050. The rotor (e.g. the drive shaft of the rotor) may extend through the central void2050, such that each of the motion sensing arrangement2040are situated adjacent to the drive shaft of the rotor. In this arrangement, the inner radial surface2044ais located closer to the drive shaft than the outer radial surface2044b, and the surface of the inner radial surface2044amay extend substantially parallel to an outer surface of the drive shaft of the rotor. In addition, a cable is connected to each of the connection points2045each motion sensing arrangement2040. In this example, both of the motion sensing arrangements2040is located in a plane extending perpendicularly to the central axis of a drive shaft extending through the void2050, such that both of the motion sensing arrangements2040have the same axial location relative to the axis of the drive shaft of the rotor. However, the skilled person will realise that other arrangement may be possible. For example each of the two motion sensing arrangements2040may be located at different axial locations along the length of the drive shaft of the rotor. The arrangement ofFIG.10Bmay be used to provide a degree of redundancy of instrumentation in the subsea pump2010. For example, two motion sensing arrangements2040may be placed adjacent each bearing arrangement2024a-d, with the intention of using one of each pairs of motion sensing arrangements2040. In the situation that one of the motion sensing arrangements is damaged or inoperable, then the other of the motion sensing arrangements may be used. In such a scenario, then having a motion sensing arrangement2040that has a partial annulus shape may be beneficial, as it may allow multiple motion sensing arrangements2040to be placed at a single axial location relative to the drive shaft of the rotor, as is shown inFIG.10B. As can be seen the motion sensing arrangements2040extend at an angle of between 90 and 180 degrees in an annulus external to a drive shaft. FIGS.11A-Cillustrate various readings that may be obtained from the motion sensing arrangements2040.FIG.11Aillustrates a graph2060showing the proximity of a motion indicator to a motion sensing arrangement2040(e.g. to a sensor of a motion sensing arrangement). The X-axis2061indicates time in seconds, while the Y-axis2063indicates the proximity of the motion indicator to the motion sensing arrangement. As previously described, the motion indicator may comprise a surface feature, or a number of surface features thereon. In this example, the surface features cause the proximity of the motion indicator relative to the motion sensing arrangement2040to vary as the rotor is rotated, resulting in a predictable oscillation of the proximity of the motion indicator to the motion sensing arrangement2040and a number of peaks2062and troughs2064appearing on the graph2060. This feature may be useful, as it may indicated to a reader of the graph2060that the rotor is turning. In addition, when the proximity of the motion sensing arrangement is measured relative to time, then the rotational velocity of the rotor may be ascertained by measuring the frequency of the oscillations on the graph2060, and comparing this to an expected number of oscillations for one revolution of the rotor, based on the number of surface features that are present on the motion indicator. In this example, the motion indicator comprises two surface features that are greater in magnitude compared to the other surface features. In addition, of these two surface features, a first2064ais larger than a second2064b, resulting in there being two larger oscillations on the graph2060for every rotation of the drive shaft. The surface features on the motion indicator may be in the form of either depressions or protrusions, resulting in a greater increase or reduction in the distance between the motion indicator and the motion sensing arrangement2040. A user, knowing the configuration of the surface features on the motion indicator, will then be able to identify whether the rotor is turning in the correct direction based on the position of the first larger oscillation2064aand the second smaller oscillation2064b. For example, if it is expected that the first larger oscillation2064ashould appear first, followed by the second smaller oscillation2064bwhen the rotor is turning in the correct direction, then the user will be able to easily identify this on the graph2060, and identify that the rotor is turning in the correct direction. Should the user see a result that is unexpected, then this allows action to be taken before any damage is caused to the pump, or to any other components. The action may be in the form of action by a user—e.g. a manual reduction in the operating speed of the rotor—or automatic action taken by a control system that is configured to trigger a reduction or arrest of rotational speed of the rotor in the event of an unexpected result. In the case of this example, such rotational movement may be measured by the axial and/or radial sensors of the motion sensing arrangement2040. FIG.11Billustrates a further graph2070that may be obtained based on the readings of the motion sensing arrangement2060. In this example, radial movement of the rotor is measured, and the change in radial position as the shaft rotates may be plotted as a line2072,2074on the upper and lower graphs. The different graphs may relate to the radial movement of at different axial locations along the drive shaft. As such, a large difference between the readings on each graph may indicate to a user that the drive shaft is bending during use, which may be detrimental to its function. In addition, the graph2070may be used to measure the radial vibration of the drive shaft. In cases where there is a large degree of radial movement of the drive shaft, then the user may be able to identify a large degree of radial vibration of the drive shaft, which may be detrimental to the functioning of the drive shaft, or may indicate that a repair of the drive shaft is necessary—for example it may indicate that a bearing has broken, seized or worn, or that a rotor or drive shaft has become bent or fractured. Worn, broken or seized bearings, and bend or fractured drive shafts, may occur as a result of rotordynamic vibration issues, which may be identified by taking measurements of radial movement/vibration of the drive shaft. Such measurements may be produced by the radial sensors2024b-cof the motion sensing arrangement2040. The graph2080ofFIG.11Cillustrates axial movement of the drive shaft in the interior housing2014against force on a thrust bearing in the internal housing2014. Axial movement of the drive shaft of the rotor may be caused by an unbalanced axial force acting on the rotor as a result of rotation thereof, for example as a result of rotation of an impeller attached thereto. In the graph illustrated, a broken line2082is illustrated that shows a general thrust bearing force—displacement curve. This curve illustrates the force produced on a thrust bearing caused by an axial displacement and axial force acting on the rotor, for example the drive shaft of the rotor. Also illustrated are measurements which may be taken from a subsea pump of axial displacement plotted against a thrust bearing force on a thrust bearing. A motion sensing arrangement2040as previously described may be used to detect at least the axial displacement of the rotor for the plotting of graph2080. In this graph the Y-axis2084describes the axial displacement of the thrust bearing inn micrometres, while the X-axis describes the thrust bearing force in kilo-Newtons. An upper bearing limit2088and lower bearing limit2090are also illustrated in broken outline. These limits indicate the maximum displacement of the rotor before damage would likely be caused to the thrust bearing due to excessive force acting thereon. A user may then be able to use the value of axial displacement of the rotor provided by the motion sensing arrangement2040to check whether the subsea pump is operating in an acceptable condition, or whether operation of the subsea pump is likely to be causing damage to components thereof. Additionally or alternatively, the value of axial displacement provided in the graph ofFIG.11Cmay be used to evaluate dynamic axial motion of the rotor (e.g. motion of the rotor over time). In some cases, dynamic axial movement of the rotor may be in the form of resonant axial movements or vibrations, which may be detrimental to the operation of the pump, and therefore may be useful to identify for a user. Such motion may be identified on the graph ofFIG.11C. The person skilled in the art realises that disclosure ofFIGS.9to11Cis not limited to the preferred embodiments described in relation to these Figures. The person skilled in the art further realises that modifications and variations are possible within the scope of the appended clauses. Additionally, variations to the disclosed embodiments can be understood and effected by the skilled person in practicing the disclosure, from a study of the drawings, the disclosure, and the following set of clauses. Some examples and aspects will now be described in the following numbered, non-limiting, clauses: CLAUSE B1. A subsea pump, comprising:a housing;a rotor located inside the housing, a bearing arrangement being located between the rotor and the housing to facilitate rotation of the rotor therein, and the rotor comprising a motion indicator;a motion sensing arrangement comprising a pressure sealed housing and at least one sensor, the motion sensing arrangement being located inside the housing and in communication with the motion indicator, and the motion sensing arrangement being configured to detect movement of the motion indicator. CLAUSE B2. The subsea pump of clause B1, wherein the pressure sealed housing is hermetically sealed. CLAUSE B3. The subsea pump of clause B1 or B2, wherein the motion sensing arrangement is configured to detect the direction of rotational movement of the rotor. CLAUSE B4. The subsea pump of any preceding clause, wherein the motion indicator is in the form of a radially extending protrusion from the rotor. CLAUSE B5. The subsea pump of any preceding clause, wherein the motion indicator is or comprises the drive shaft of the rotor. CLAUSE B6. The subsea pump of any preceding clause, wherein the motion sensing arrangement is configured to detect at least one of rotational, axial and radial movement of the rotor. CLAUSE B7. The subsea pump of any preceding clause, wherein the motion sensing arrangement is configured to detect vibration of the rotor. CLAUSE B8. The subsea pump of any preceding clause, wherein the at least one sensor is an optical sensor, a capacitive sensor or an eddy-current sensor. CLAUSE B9. The subsea pump of any preceding clause, wherein the motion sensing arrangement comprises at least one axially oriented motion sensor, and at least two radially oriented motion sensors. CLAUSE B10. The subsea pump of clause B9, wherein the at least two radially oriented motion sensors are offset by 90 degrees. CLAUSE B11. The subsea pump of any preceding clause, wherein the motion indicator is in the form of a disc extending from the rotor and axially aligned with the rotor. CLAUSE B12. The subsea pump of clause B11, wherein the disc is a coded target disc and comprises at least two surface features on an axial surface thereof, and wherein the motion sensing arrangement is configured to detect rotational movement of the at least two surface features as a result of rotation of the rotor. CLAUSE B13. The subsea pump of clause B12, wherein a first of the at least two surface features has a different geometry to a second of the at least two surface features, and the motion sensing arrangement is configured to detect the circumferential direction of rotation of the at least two surface features. CLAUSE B14. The subsea pump of any preceding clause, wherein the motion sensing arrangement is configured to detect at least one of axial movement of the rotor, rotational velocity of the rotor, and a once-per-revolution indicator of vibration analysis. CLAUSE B15. The subsea pump of any preceding clause, wherein the pressure-sealed housing of the motion sensing arrangement is has a partial annulus shape. CLAUSE B16. The subsea pump of clause B15, wherein the partial annulus shape has a circumferential extension of between 120 degrees and 150 degrees. CLAUSE B17. The subsea pump of clause B13, wherein the motion sensing arrangement comprises at least three sensors, and wherein two sensors are located on a radially inner surface of the partial-annulus pressure sealed housing, and one sensor is located on an axial surface of the partial-annulus pressure sealed housing. CLAUSE B18. The subsea pump of any preceding clause, wherein the pressure sealed housing of the motion sensing arrangement is coupled to the housing at a predetermined distance from the motion indicator. CLAUSE B19. The subsea pump of any preceding clause, comprising a motor for turning the rotor, the motor additionally comprising a motion indicator, and the motion of the rotor being detectable by the motion sensing arrangement. CLAUSE B20. The subsea pump of any preceding clause, wherein the motion sensing arrangement comprises an integrated temperature measurement system located within the pressure sealed housing, the integrated temperature measurement system comprising at least one temperature sensor. CLAUSE B21. The subsea pump of any preceding clause, wherein the motion sensing arrangement comprises connection means for at least one of physical and wireless connection thereto for communications purposes, and the motion sensing arrangement comprises an integrated signal electronic conditioning system comprising signal amplifiers located inside the sensor housing, the integrated signal electronic conditioning system being in communication with the connection means to provide an output signal from the motion sensing arrangement. CLAUSE B22. A method for determining motion of a rotor in a subsea pump, comprising:providing a subsea pump in a subsea location, the subsea pump comprising a pressure-sealed motion sensing arrangement, and a motor comprising a motion indicator;operating the subsea pump to effect rotation of the rotor therein; using the motion sensing arrangement to detect movement of the rotor. CLAUSE B23. The method of clause B22, comprising determining the direction of rotation of the rotor by detecting the motion of a first surface feature and a second surface feature located on the motion indicator, the first surface feature having a different geometry to the second surface feature. CLAUSE B24. The method according to clause B22 or B23, comprising locating the pressure-sealed motion sensing arrangement in an annulus surrounding the rotor, the pressure-sealed motion sensing arrangement having a partial annulus shape. CLAUSE B25. The method according to clause B24, comprising detecting at least one of rotational movement and axial movement of the rotor via a motion sensor located on an axial surface of the pressure-sealed motion sensing arrangement. CLAUSE B26. The method according to clause B24 or B25, comprising detecting at radial movement of the rotor via at least two motion sensors located on an inner radial surface of the pressure-sealed motion sensing arrangement. CLAUSE B27. The method according to any of clauses B22 to B26, comprising installing the pressure sealed motion sensing arrangement at a predetermined distance from the motion indicator, without the requirement for readjusting said predetermined distance before operation of the pump. CLAUSE B28. A subsea pump, comprising:a housing;a rotor located inside the housing, a bearing arrangement being located between the rotor and the housing to facilitate rotation of the rotor therein, and the rotor comprising a motion indicator;a motion sensing arrangement comprising a hermetically sealed pressure sealed housing and at least one sensor, the motion sensing arrangement being located inside the housing and in communication with the motion indicator, and the motion sensing arrangement being configured to detect movement of the motion indicator. A Cooling and Lubrication System and Associated Method Now turning to the disclosure ofFIGS.12to14, the first aspect of this disclosure shows a cooling system for a subsea pump, comprising:a drive shaft, the drive shaft comprising a coolant/lubricant delivery flow path and a coolant/lubricant return flowpath extending therethrough;a fluid delivery inflow port and a fluid delivery outflow port, each located on a circumferential surface of the drive shaft, the fluid delivery inflow port being configurable to permit fluid flow from a coolant/lubricant source to the coolant/lubricant delivery flow path, and the fluid delivery outflow port being configurable to permit flow from the coolant/lubricant delivery flow path to a target location;a fluid return inflow port and a fluid return outflow port, the fluid return inflow port located on an axial end of the drive shaft, and the fluid return outflow port located on a circumferential surface of the drive shaft, the fluid return inflow port being configurable to permit fluid flow from the target location to the coolant/lubricant return flowpath, and the fluid return outflow port configurable to permit fluid flow from the coolant/lubricant return flowpath to a coolant/lubricant sink;wherein the turning of the drive shaft drives fluid flow through the coolant/lubricant delivery flowpath and the coolant/lubricant return flow path. FIG.12shows a sectional view of a pump and partial motor assembly3010, with the motor3010removed for simplicity. The pump and motor section comprises three main portions. Illustrated on the right-hand side of the Figure is a motor compartment3012. The motor compartment3012comprises a housing3014, which may house a motor (illustrated is thrust bearing3016, with the motor removed for clarity) therein, or which may have a motor affixed to an external surface thereof, and may optionally house a part of the motor. The motor is coupled to a drive shaft3018, which is able to be rotated by the motor in order to provide drive to operate a secondary device, for example. Here, the pump and motor assembly3010comprises a pump module3020, which is driven by the motor via the drive shaft3018. The pump module3020comprises a plurality of impellers3022, which are also coupled to the drive shaft3018, and are used to pump a fluid through the pump. In this example, the impellers3022are multiphase impellers, meaning that they can be used to pump a multiphase fluid (i.e. one that may comprise both a liquid and a gas fraction) through the pump and motor assembly3010, although similar setup wherein the multiphase impellers are replaced by single-phase liquid impellers and/or single-phase gas impellers may also be possible. The drive shaft3018is supported at either end in the pump and motor assembly3010by a set of bearings3024a,3024b(seeFIG.14). One of the sets of bearings3024ais located at the Non-Drive End (NDE) of the drive shaft3018, while the other of the sets of bearings3024bis located at the Drive End (DE) of the drive shaft3018. Together, the bearings both support the drive shaft3018, while permit rotation of the drive shaft3018about its axis. As will be described in further detail later, the drive shaft3018comprises a central bore3026that extends therethrough. The central bore3026, in this example, provides fluid communication between the NDE bearings3024a, and the motor3016. To enable this fluid communication, the drive shaft3018additionally comprises three radial fluid ports3028,3030,3032, and one axial fluid port3034. Each of the bore3026and the radial fluid ports3028,3030,3032may be drilled into the shaft, for example. One of the radial flow ports3030may be considered a fluid inflow port, while two of the radial flow ports3028,3032may be considered fluid outflow ports. The axial inflow port3034may also be considered a fluid inflow port. In this case, the fluid inflow port3034takes a fluid from the motor compartment3012and delivers this fluid to the NDE bearings3024avia the central bore3026and the outflow port3032. Axial outflow port3034delivers fluid from the NDE bearings back3024ato the motor compartment3012via the central bore3026, in particular via a flow tube3036. Inserted in the central bore3026is the flow tube3036(which may be considered to be a conduit), which may divide the central bore, such that it is able to comprise multiple flow paths, as will be described in further detail later. Having this configuration (e.g. where there is a central bore defined in the drive shaft) may permit a flow and distribution of a fluid throughout the pump and motor assembly3010without the requirement for external pipework or tubing, thereby reducing the complexity of the assembly, and providing fewer opportunities for a leakage of fluid. Referring now toFIG.13, a simplified schematic illustration of the pump and motor assembly3010is shown. In this example, flow paths of fluid are illustrated with arrows, as will be described. In common with theFIG.12, there is illustrated a drive shaft3018, having one end supported by NDE bearings3024a, and a second end supported by DE bearings3024b. The drive shaft comprises central bore3026, as well as three radial fluid ports3028,3030,3032and one axial flow port3034. Although, in this example, a single of each fluid port has been illustrated, having multiple of each fluid port may also be possible. For example, for the radial fluid ports3028,3030,3032, there may be a radial array of fluid ports, each radial array comprising several fluid ports. In such an example, having a radial array may permit a larger flow of fluid therethrough, or may provide protection against blocking of a single fluid port, thereby providing an element of redundancy. Further, a user may be able to have some control over the flow rate, by being able to decide the number of each type of fluid port. Where there is an array of each type of fluid port, each array may comprise the same number of fluid ports, or a different number of fluid ports. The fluid ports3028,3030,3032,3034permit fluid flow through the central bore3026in the shaft (illustrated by arrows, as will be further described) and define a cooling system for the pump and motor assembly3010. In particular, the fluid ports3028,3030,3032,3034define a cooling system for the NDE bearings3024aof the pump and motor assembly3010by permitting fluid to flow from the motor compartment (shown inFIG.12), to the NDE bearings3024a, and back to the motor compartment. As inFIG.12, a flow tube3036is located in the central bore3026of the drive shaft3018. The flow tube3036may permit two flow paths to be defined in the central bore3026—one inside the flow tube3036, and one in the annulus between the flow tube3036and the central bore3026. This thereby enables one single bore to be made in the drive shaft3018, which can accommodate two separate fluid flowpaths, thereby facilitating manufacture of the cooling system by requiring the manufacture of a single bore, for example as opposed to requiring several bores, which may be complex. In this example, there may be a reservoir of fluid in the motor compartment. The fluid may be, for example, barrier fluid, such as an oil or other lubricating fluid. The fluid may have coolant properties, and may therefore be considered a coolant. The fluid may additionally have lubricant properties. In some examples, the fluid may function principally as a coolant. The fluid may be a water/glycol mix (e.g. a mix of 60% water and 40% glycol), or may be pure water or oil. The radial fluid port3030, which may be an inflow fluid port, may be in communication with the coolant reservoir. Fluid communication between the fluid port3030and the coolant reservoir may be continuous, or it may be intermittent. For example, as inflow fluid port3030is located on the drive shaft3018, this fluid port3030will rotate with the drive shaft3018. As the drive shaft3018rotates, its position relative to the coolant reservoir may change. In some examples, the coolant reservoir may entirely surround the drive shaft3018(e.g. may entirely circumferentially surround the drive shaft3018). In such examples, rotation of the drive shaft3018may result in the inflow fluid port3030being constantly held within the coolant reservoir. As such, in these examples, the inflow fluid port3030may be in continuous fluid communication with the fluid reservoir. In other examples, the coolant reservoir may discontinuously surround the drive shaft3018(e.g. discontinuously circumferentially surround the drive shaft3018). In these examples, the coolant reservoir may circumferentially surround 90 degrees of the drive shaft, 180 degrees, 270 degrees, etc. In some examples the coolant reservoir may surround the drive shaft3018at various points, and the flow port3028may come into contact with the coolant reservoir at various points during a single 360 degree rotation thereof. In this example, the coolant fluid may flow from the coolant reservoir and through the radial port3030into the central bore3026, in the direction of arrow3080, which may correspond to a coolant delivery flow path. As a result of the flow tube3036being located in the central bore3026, the coolant fluid may flow into the annulus between the central bore3026and the flow tube3036. Once in the annulus, the coolant fluid may flow in the direction of arrows3082along the annulus in the central bore3026, and towards the radial flow port3032, also corresponding to the fluid delivery flow path. Once at the radial flow port3032, the fluid may flow out of the annulus and through the radial flow port3032in the direction of arrow3084. The radial flow port3032may be in fluid communication with a target location—which is in this example the NDE bearing (see, for example,FIG.12), where the coolant fluid may be used to cool and/or lubricate the NDE bearing, and may also provide lubrication and cooling to the NDE mechanical shaft seal. As more coolant fluid flows into the NDE bearing, the coolant fluid may flow through the NDE bearing, and towards axial flow port3034, in the direction of arrow3086. In this example, the axial flow port is defined by an aperture in the end of the flow tube3036. Adjacent the axial flow port3034, located between the flow tube3036and the walls of the central bore3026, may be a seal (such as an O-ring type seal). The seal may prevent coolant fluid from flowing from the NDE bearing and into the annulus between the flow tube3036and the central bore3026, thus directing all fluid flow through axial port3034in the flow tube3036, and in the direction of arrow3088, which may correspond to a fluid return flow path. The seal may additionally provide support for the flow tube3036, to ensure that it is located as desired in the central bore3026(e.g. to ensure that it is located centrally in the central bore3026). As such, the flow tube3036may be concentric with the central bore3026. Finally, the flow of coolant fluid may reach the radial flow port3028. The radial flow port3028may be in fluid communication with the flow tube3036such that fluid flow exits the flow tube3036, through the radial flow port3028and into a coolant sink. In this example, the coolant sink and the coolant source may be the same reservoir of coolant fluid. However, the skilled reader will recognise that it would also be possible to have a separate coolant source and coolant sink. It will be noted that the coolant delivery flow path is located in the annulus between the fluid bore3026and the flow tube3036, while the coolant return flow path is located inside the flow tube3036. This may facilitate fluid entry from the target location (e.g. the NDE bearing) to the coolant return flow path through the axial flow port3034, for example by permitting for a larger size of port3034, or by permitting fluid to flow into a rotating circular shaped port, as opposed to an annular shaped port. Further, the cylindrical coolant return flow path may be (at its widest point) wider than the annular coolant delivery flow path, which may reduce the likelihood of a blockage from debris that the coolant fluid may pick up at the target location (e.g. the NDE bearings). As can be observed inFIG.13, the central bore3026comprises a narrower section3042at one end thereof. In this example, there is a stepped transition between a wider and a narrower section3042of the central bore3026, forming a shoulder3040in the central bore3026. In this example, the flow tube3036is supported axially by the shoulder, and the radial flow port3028for fluid flow from the NDE bearings to the fluid sink is in fluid communication with the narrower section3042of the central bore3026. In this way, fluid is permitted to flow from the flow tube3036and out of the central bore3026via the narrower section3028thereof. The inner diameter of the flow tube3036and the diameter of the narrower section3042of the central bore3026may be the same, or similar. FIG.14illustrates the pump and motor assembly3010in further detail, with the flowpaths illustrated by arrows. In this view, it is possible once again to see the motor compartment3012and the pump module3020, with the drive shaft3018extending therethrough. As previously, the flow tube3036is held inside the central bore3026. In this Figure, it is possible to see that the flow tube3036is held inside the central bore3026by a plurality of tube supports3038, which may be in the form of spring-like elements. In this example, the tube supports3038are in the form of spring clips, although any appropriate member that provides support to the flow tube3036, while permitting fluid flow therethrough would be possible. The fluid is driven through the pump and motor assembly3010by the turning of the drive shaft3018. In particular, the centrifugal force generated by the turning of the drive shaft3018assists to encourage the flow of fluid through the central bore3026and radial flow ports3028,3030,3032of the drive shaft, and may be of sufficient magnitude that it is the only required force to drive the flow of fluid through the central bore (e.g. no external pumping or suction force may be necessary). In use, turning of the drive shaft creates a force acting away from the axis of rotation of the drive shaft3018. As the coolant source, coolant sink and NDE bearings are all located exterior to the drive shaft3018and away from its axis of rotation, the turning of the drive shaft creates a force driving coolant fluid outwards from the axis of rotation and towards these locations. As the axial flow port3034may be located on the axis of rotation of the drive shaft3018(e.g. the axial flow port3034may be concentric with the axis of rotation of the drive shaft), then rotation of the drive shaft3018has no significant effect regarding a force acting to drive a fluid through the axial flow port3034. Referring toFIGS.13and14, which contain arrows showing the direction of fluid flow of the coolant fluid it will be noted that, while the centrifugal force caused by rotation of the shaft3018causes fluid flow in a desirable direction in the case of fluid ports3028and3032(e.g. towards the NDE bearings and towards the coolant sink), the centrifugal force causes a force on the coolant fluid in a direction opposite to the desired direction in the case of fluid port3030(e.g. towards the coolant source). However, despite this undesirable directional force, rotation of the drive shaft3018causes fluid to flow in the desired direction (e.g. from the coolant source to the NDE bearing and to the coolant sink) because the forces acting on the fluid through ports3030and3032are generally equal and opposite, thereby the effect of the force on the fluid through port3030is effectively cancelled by the equivalent force acting on the fluid through port3032. In contrast, the flow of fluid through port3028is not cancelled out, due to the fluid port3034being located concentrically with, or close to, the axis of rotation of the shaft3018. As such, coolant fluid is able to flow through port3028. As the coolant fluid may a liquid, and can be assumed to be incompressible, the flow of coolant fluid through port3028creates a suction effect in the through bore3026and flow tube3036, which effectively drives coolant fluid into port3030(against the direction of the centrifugal force) and towards the NDE bearings for cooling purposes. The described cooling system can therefore be used to provide cooling to bearings in a pump, without the requirement for external propulsion of fluid (e.g. through use of a secondary pump), and without the use of further pipes or tubes for the transfer of a coolant fluid. The second aspect of this disclosure shows a method for providing cooling in a subsea pump, comprising: providing a driveshaft for a subsea pump comprising a coolant delivery flowpath and a coolant return flowpath therein; flowing a fluid through the coolant delivery flowpath, from a coolant source to a target location to cool the target location; flowing a fluid through the coolant return flowpath, from the target location to a coolant sink; driving fluid flow through the coolant delivery flowpath to the coolant return flowpath by turning the drive shaft. The method may also comprise connecting the coolant delivery flowpath to a coolant source, and connecting the coolant return flow path to a coolant sink. As previously described, the coolant return flow path and the coolant sink may be the same reservoir of fluid. The coolant return flow path and/or the coolant sink may be located in a motor. The coolant fluid may be barrier fluid. The method may comprise driving fluid flow through the coolant delivery flowpath to the coolant return flow by using centrifugal force generated by turning the drive shaft to drive the fluid through the relevant flow paths. The person skilled in the art realises that the disclosure ofFIGS.12to14is not limited to the preferred embodiments described above. The person skilled in the art further realises that modifications and variations are possible within the scope of the appended clauses. Additionally, variations to the disclosed embodiments can be understood and effected by the skilled person in practicing the claimed disclosure, from a study of the drawings, the disclosure, and the appended clauses. Some examples and aspects will now be described in the following numbered, non-limiting, clauses: CLAUSE C1. A cooling and lubricating system for a subsea pump3010, comprising:a drive shaft3018, the drive shaft3018comprising a coolant/lubricant delivery flow path and a coolant/lubricant return flowpath extending therethrough and being powered by a motor;a fluid delivery inflow port3030and a fluid delivery outflow port3032, each located on a circumferential surface of the drive shaft3018, the fluid delivery inflow port3030being configurable to permit fluid flow from a coolant/lubricant source to the coolant delivery flow path, and the fluid delivery outflow port3032being configurable to permit flow from the coolant/lubricant delivery flow path to a target location; anda fluid return inflow port3034and a fluid return outflow port3028, the fluid return inflow port3034located on an axial end of the drive shaft3018, and the fluid return outflow port3028located on a circumferential surface of the drive shaft3018, the fluid return inflow port3034being configurable to permit fluid flow from the target location to the coolant/lubricant return flowpath, and the fluid return outflow port3028configurable to permit fluid flow from the coolant/lubricant return flowpath to a coolant sink, the coolant sink being a reservoir of barrier fluid from the motor that powers the drive shaft3018;wherein the turning of the drive shaft3018drives fluid flow through the coolant/lubricant delivery flowpath and the coolant/lubricant return flow path. CLAUSE C2. The cooling and lubricating system according to clause C1, wherein the drive shaft3018comprises a central bore3026extending along the axis thereof, the central bore3026at least partially defining the coolant/lubricant delivery flow path. CLAUSE C3. The cooling and lubricating system according to clause C2, wherein the central bore3026at least partially defines the coolant return flow path. CLAUSE C4. The cooling and lubricating system according to any preceding clause, wherein the drive shaft3018comprises a central bore3026extending along the axis thereof, the central bore3026at least partially defining both of the coolant delivery flow path and the coolant return flow path. CLAUSE C5. The cooling and lubricating system according to any preceding clause, wherein the drive shaft3018comprises a central bore3026extending along the axis thereof, with a conduit3036located in the central bore3026, the conduit3036separating the coolant delivery flow path from the coolant return flow path. CLAUSE C6. The cooling and lubricating system according to clause C5, wherein the return inflow port3034is defined by at least one of the central bore3026and the conduit3036. CLAUSE C7. The cooling and lubricating system according to clause C5 or C6, wherein at least a part of the coolant delivery flow path is defined by a region radially outwards of the conduit3036, and at least part of the coolant return flow path is defined by a region radially inwards of the conduit36. CLAUSE C8. The cooling and lubricating system according to any of clauses C5 to C7, wherein the conduit3036is held in place by a radial support means3038such as a spring clip located between the central bore3026and the conduit3036. CLAUSE C9. The cooling and lubricating system according to any preceding clause, wherein at least part of the coolant delivery flow path and the coolant return flow path are concentric. CLAUSE C10. The cooling and lubricating system according to any preceding clause, comprising a plurality of fluid delivery inflow ports3030. CLAUSE C11. The cooling and lubricating system according to any preceding clause, comprising a plurality of fluid delivery outflow ports3032. CLAUSE C12. The cooling and lubricating system according to clauses C10 and C11, wherein the number of fluid delivery inflow ports3030and the number of fluid delivery outflow ports3032are the same. CLAUSE C13. The cooling and lubricating system according to clause C10, wherein the plurality of fluid delivery inflow ports3030are arranged on the drive shaft3018in a circumferential array. CLAUSE C14. The cooling and lubricating system according to clause C11, wherein the plurality of fluid delivery outflow ports3032are arranged on the drive shaft3018in a circumferential array. CLAUSE C16. The cooling and lubricating system according to clause C15, wherein the coolant source is a reservoir of barrier fluid from the motor. CLAUSE C18. The cooling and lubricating system according to any preceding clause, wherein the target location is a pump bearing. CLAUSE C19. The cooling and lubricating system according to any preceding clause, wherein the cooling system is for cooling bearings of a subsea pump. CLAUSE C20. The cooling and lubricating system according to any preceding clause, wherein the coolant and lubricant are the same fluid. CLAUSE C21. A method for providing cooling and lubrication in a subsea pump, comprising:providing a drive shaft3018for a subsea pump3010comprising a coolant delivery flowpath and a coolant/lubricant return flowpath therein, the drive shaft being powered by a motor;flowing a fluid through the coolant/lubricant delivery flowpath, from a coolant/lubricant source to a target location to cool said target location;flowing a fluid through the coolant/lubricant return flowpath, from the target location to a coolant/lubricant sink, the coolant sink being a reservoir of barrier fluid from the motor that powers the drive shaft3018;driving fluid flow through the coolant/lubricant delivery flowpath to the coolant/lubricant return flowpath by turning the drive shaft. CLAUSE C22. The method according to clause C20 or C21, comprising connecting the coolant/lubricant delivery flowpath to a coolant source, and connecting the coolant/lubricant return flow path to a coolant/lubricant sink. A Method for Providing a Visual Indication of the State of Operation of A Subsea Pump Looking now atFIGS.15to18, there is provided an improved method for providing visual indication of the state of operation of subsea pump. According to one aspect there is a method for providing a visual indication of the state of operation of a subsea pump, comprising:normalising an operating parameter;setting a desired operational range for the normalised parameter;setting an acceptable operational range for the normalised parameter;providing a first visual indicator for indicating that the normalised parameter is inside the desired operational range, providing a second visual indicator for indicating that an operating parameter is outside of the desired operational range and inside the acceptable operational range, and providing a third visual indicator for indicting that the operating parameter is outside the acceptable operational range;providing a numerical scale for assigning an operation number to the normalised parameter based on its operation;selectively displaying one of the first, the second and the third visual indicators, and the operation number on the numerical scale to a user. The use of pumps is common across various applications, ranging from the drilling of wells to the supply of water. Depending on the intended use for a pump, it may be required to have different capabilities. For example, pumps must be able to produce sufficient head to deliver a required volume of fluid per unit of time to a desired location, and may additionally be required to operate with a range of working fluids, from incompressible to compressible, and often multiphase fluids. The wider the application range for the pump is, the more difficult the operating conditions of the pump may be to monitor accurately, for example whether the pump is operating within its operational range, whether it is operating in an unfavourable pump condition etc., some of which may reduce the lifespan of a pump or may severely harm a pump. Since pumps and rotary machines are often installed in harsh environments, e.g. on the sea floor, routine inspection can become a cost intensive and/or complicated venture if required to be done physically. As such there is a demand for a pump monitoring system which gives a pump operator (human or computer) a detailed, easy to understand and quickly generated indication of the operational state of the pump. In some cases, it may be difficult to identify unfavourable pump conditions as the pump operating parameters are measured. For example, this may be due to identification of the pump conditions being dependent on multiple factors, for example the positioning and operation of the pump, which may have an effect on the measurement of parameters and therefore detailed analysis may be required in order to identify the unfavourable pump operating conditions. One way of preventing unfavourable pump conditions from damaging a subsea pump may be to set acceptable ranges for each measured operating parameter of the pump by choosing individual accepted maxima and minima for any of the measured pump operating parameters. This approach may permit a user to ascertain whether a pump is running in an acceptable manner or not, but may not give a detailed insight into pump conditions. In instances when the pump is in operation but not in its desired operational range, the pump may be degrading and/or at higher risk of failure due to high stress on pump parts, although this may be difficult to identify simply by setting acceptable ranges for each operating parameter. As unfavourable pump conditions may have an effect on measurement of multiple pump operating parameters, it can be difficult to identify the exact nature and/or cause of the unfavourable pump condition, which may be possible only by correlating pump operating parameters, which can be a complex and time consuming operation. Additionally, the pump operating parameters may be within their permissible operational range, but may be far from their normal or desired value. Furthermore, the pump operating parameters may be open to misinterpretation, and an unfavourable pump condition may be misidentified as one that is acceptable, or vice versa, using this method. This disclosure seeks to provide a system for recognition of unfavourable pump operation conditions by providing a more understandable analysis and indication of unfavourable pump operation conditions based on normalised pump operating parameters, which may be read individually, and without the requirement of the context or dependency of other pump operating parameters. This approach may therefore provide a detailed insight into how each pump parameter changes over time, allowing identification of the operational state of the pump with greater precision. A condition number may be attributed to each operating parameter to provide an indication of the acceptability of each performance parameter, and which may be combined with other performance values into a single value to provide an overall indication of the operational state of a pump. FIG.15is a schematic illustration of a piping system4010, in which the described system may be applicable. The piping system4010has a number of components, including various valves4012, a buffer tank4014, a recirculation valve4016, and a pump unit4018. In use, fluid may flow from a system inlet4020and into the buffer tank4014. In this example the fluid may be a multiphase fluid, although a fluid flowing in a single phase would also be possible. The pump4018induces the fluid to flow from the buffer tank4014to the pump4018at pump inlet4022, and exits the pump at the pump outlet4024. Thereafter, the fluid may be circulated back to the buffer tank via the recirculation valve4016, or may flow out of the illustrated piping system at the outlet4026. A sensor arrangement4028is illustrated inFIG.15, showing a Multiphase Flow Meter (Mpfm), a pressure sensor and a temperature sensor positioned proximate the pump inlet4022, and a pressure sensor and a temperature sensor positioned proximate the pump outlet4024. In this example, the sensor arrangement also comprises a fluid level sensor positioned inside the buffer tank4014. Although not visible inFIG.15, the sensor arrangement4028may additionally comprise sensors located inside the pump4018. The skilled reader will understand that, while only Mpfm, pressure, temperature and fluid level sensors are illustrated inFIG.15, the sensor arrangement may equally comprise other sensor types, for example the sensor arrangement4028may sense at least one of the pump speed, pump flow rate, fluid density, fluid viscosity, or the like. Although not illustrated inFIG.15, the sensor arrangement4028may be able to provide information to a user based on the sensed values. For example, the sensor arrangement4028may be in communication with a signal transmitter (e.g. a wireless signal transmitter) to transmit signals indicating each of the sensed values to a user with a receiver. Once the user has received this information, then this information may be able to be provided on a display for ease of understanding of the user. FIG.16shows an exemplary graph of the shaft power and the differential head of a pump in dependency of the volume flow through the pump and the rotational speed of the pump, which are values that may be calculated and/or measured through use of the sensor arrangement4028ofFIG.15. As can be seen inFIG.16, both the shaft power and the differential head of the pump depend on the volume flow rate through the pump and the rotational speed of the pump. Such interdependency between measurable parameters may present difficulties when observing the operational state of the pump. Observation of the pump operational state may comprise measuring at least one pump operating parameter, e.g. pump speed, pump flow, pump head, pump shaft power, cooler differential pressure, mechanical seal differential pressure, thrust bearing friction loss, cooler heat transfer coefficient, barrier fluid consumption, temperature, casing vibration, shaft vibration, shaft torque, motor slip or other measurable pump operation properties. In one example, pump shaft power, pump speed and pump flow may be measured to ensure an acceptable pump operational state e.g. an acceptable operational state of the pump shaft. Unfavourable or deteriorating pump operating conditions, e.g. the degradation of parts and/or increased friction in the pump, may have an effect on any of the various pump operating parameters. Other changes to operating conditions, e.g. changes in the density or compressibility of the working fluid, may result in similar effects on the various pump operating parameters making it difficult to identify events such as degradation of the operation of the pump, or even whether the current pump operation is within safe margins. It is therefore desirable to be able to monitor the operation of a pump such that adverse effects or conditions affecting operation of the pump can be easily identified. In particular, it may be desirable to be able to monitor the operation of a pump over a period of time to identify adverse effects or conditions, while simultaneously taking into account the effect of the present operating conditions on the pump itself. One possible method for monitoring the operation of a subsea pump to easily identify adverse effects or conditions on operation may be to measure and subsequently normalise a first operating parameter relative to a measurable second operating parameter of the pump. The normalisation of a first operating parameter may involve modifying the operating parameter such that it is no longer dependent on operating conditions, for example the pump speed, motor power, pump flow, differential pressure, or the like. The normalisation of a first operating parameter may involve the comparison of a measured parameter against an expected value for that parameter. For example, where the first parameter is pump flow rate, then the normalisation of pump flow rate may comprise the comparison of the measured pump flow rate at a measured pump speed (e.g. the rpm of the pump) with the expected value of the pump flow rate at the measured pump speed. In some examples, the measured operating parameter may be extrapolated before being compared to a known value of the operating parameter to produce the normalised parameter. For example, where the expected pump flow rate is only known at selected pump speeds, then the value of the measured pump flow rate at a measured speed may be extrapolated to that at a pump speed where an expected value is known, and the extrapolated value compared to the expected value to produce the normalised value. The expected values may be taken from the operation of a pump in test conditions, for example in optimal test conditions. Operation of the pump in optimal test conditions may provide test data of the expected optimal operation of the subsea pump, and a corresponding range of expected values of test parameters. The expected value may additionally or alternatively be taken from the operation of a pump in a non-used state, e.g. a brand new pump that had not before been used in operation. The expected values may be taken from the operation of a pump in non-optimal test conditions, and then extrapolated or processed in order to receive optimal test data. For example, the data received or measured in the non-optimal test conditions may be multiplied by a normalisation factor. The normalisation factor may be based upon, for example, the ratio or comparison of a real-time second operating parameter (e.g. speed of rotation of the pump motor) and a nominal second operating parameter (e.g. speed of rotation of the pump motor) which may have been measured in an optimal test environment, or for which there may be a rated or known value, and may therefore provide data permitting the user to extrapolate a measured or real-time value to provide an expected value. The second operating parameter may be selected based on availability of data, and/or based on the ease by which the operating parameter may be obtained. Once normalised, the first operating parameter may be compared against an expected value of the first operating parameter, where the expected value of the first operating parameter may be measured (or extrapolated based on measured data, as described above). The expected value may be generated or obtained based on operation of the subsea pump in a test environment and in a known working condition (e.g. in an as-new, non-used condition). In one example, where the nominal second operating parameter is speed of rotation of the pump motor, then the expected value of the first operating parameter may be generated or obtained based on operation of the subsea pump at the nominal speed of rotation of the pump motor. In this case, where operation of the subsea pump is exactly as expected, the ratio between the normalised parameter and the expected value may be 1, and deviation from the expected operation of the subsea pump may result in a ratio of less than one, or more than one. The ratio may be considered to be a parameter ratio, and may be based on the comparison of the measured parameter and expected parameter. In some cases, all or some parameter ratios may be measured at the start of operation of the pump, so as to provide a baseline parameter ratio. Such a baseline parameter ratio may permit a user to compare real-time operation of the pump with the initial operation of that particular pump, which may provide useful information for identifying factors that cause inhibition of the functioning of the pump. In some cases, the parameter ratio may be mapped to pump condition parameters that describe the pump performance for the various pump operating parameters. These mappings may set a value between e.g. 0 and 1, or a percentage value of between 0 and 100 percent, for each ratio previously calculated, describing how well the pump is performing for each pump operating parameter. The mappings may be different for all the various pump operating parameters and may differ for various pumps or differing pump applications. FIG.17is a graphical representation of a parameter ratio along the Y-axis4042(e.g. the ratio of a pump operating parameter and an expected value for said parameter as previously described—herein the parameter is the pump shaft power4042measured against time4040in hours) against time on the X-axis4040. As can be seen, the pump shaft power deviates from its expected value (which may be considered to be its value as would be expected during operation in an as-new state in identical conditions) which is denoted as parameter ratio 1 and is marked onFIG.17with a broken line4036. Between the values of 1.1 and 0.9 on the parameter ratio scale is defined a desired operational range4032, although it should be noted that the desired operational range may be between other values, such as between 0.8 and 1.15, 0.95 and 1.3, etc., and may vary depending on the parameter on which the parameter ratio is calculated e.g. pump flow rate, differential pressure etc.). As can be seen inFIG.17, the majority of the time the parameter ratio of the pump falls within a desired operational range4032. Between the parameter ratio values of 1.3 and 0.7 (although not including the range from 1.1 to 0.9) is an acceptable operational range4033. The acceptable operational range may be a range in which operation of the pump is possible, although may be suboptimal, or may be likely to cause damage to the pump if operated within this range for an extended period of time. As with the desired operational range, the acceptable operational range may deviate from the values shown inFIG.17. The subsea pump operating in this range may indicate that operation of the pump has dropped to a level that requires some degree of investigation by a user, which may be direct intervention by a user (e.g. by increasing or lowering the pump speed) or may indicate that the subsea pump requires more careful monitoring. As can be seen inFIG.17, the parameter ratio of the pump frequently enters the acceptable operational range4033. Although this may bear risks when operating the pump in this operation range for too long, in the case illustrated the vast majority of the time of operation of the pump is in the desired operational range4032, and therefore operation as illustrated inFIG.17may not require any intervention by the user. In some cases, the value of the parameter ratio may be outside of both the desired operational range and the acceptable operational range. Such an operational range may be termed a hazardous operational range4034, in which failure of the pump may be imminent. Due to the dangers posed by operation outside of both the desired and acceptable operational ranges, operation of the pump may be ceased and the pump shut down to prevent damage thereto. InFIG.17, there are very few instances in which operation of the pump is in the hazardous operational range4034. As can be seen fromFIG.17, every time the parameter ratio enters the hazardous operational range, it is quickly returned to either the acceptable or desired operational range. This may be due to user intervention (such as shut down or modification of pump operation) or it may be due to a brief anomaly occurring within the pump. Once the pump has been identified as operating in the hazardous operational range (e.g. outside both the desired and acceptable operational ranges) then any problem may be quickly addressed and running of the pump may continue. In all cases, there may be a minimum time period in which the parameter ratio should remain in either the acceptable operational range4033or the hazardous operational range4034before action is required on behalf of the user. For example, some operation of the pump in the acceptable operational range4033may be acceptable, or even expected, for several minutes or more, whereas any operation in the hazardous operational range may be considered to be unacceptable and may therefore require immediate intervention by a user. Illustrated on the right side ofFIG.17, a mapping4035for the parameter ratio to a condition number is provided. According to this mapping4035, the condition number is equal to 100 when the parameter ratio is in the desired operation range4032, the pump condition number is equal to 0 in the hazardous operation range4034and the pump condition parameter to a number in between 0 and 100 for the acceptable operation range4033. The mapping4035illustrates that, while the value of the parameter ratio is in the acceptable operational range, the corresponding condition number may vary between 0 and 100 in this example. Here, inside the desired operational range as well as at the boundary between the desired operational range and the acceptable operational range, the condition number is 100 (e.g. the maximum value of the condition number), while inside the hazardous operational range as well as at the boundary between the acceptable operational range and the hazardous operational range, the condition number is 0 (e.g. the minimum value of the condition number). When the parameter ratio is in the acceptable operational range, the condition number may be an intermediate value of between maximum value and the minimum value, which are 100 and 0 in this case. In the example ofFIG.17, there is a non-linear relationship between the variation of the parameter ratio in the acceptable range and the condition number, although in some examples, there may be a linear relationship. As illustrated inFIG.16, the non-linear relationship is such that an initial change in the parameter ratio from the boundary of the desired operational range towards the hazardous operational range has initially only a small effect on the mapped condition number, while as the parameter ratio moves towards the hazardous range, the relative change in the condition number becomes greater. The non-linear relationship may result in, for example, a quadratic or exponential variation (or other polynomial variation) in the condition number with a change in the parameter ratio, or in fact any arbitrary curve that best correlates with the experience and knowledge of the pump vendor. In use, the user may be able to see a graph as is indicated inFIG.17, or alternatively the skilled person may simply be given the parameter ratio and/or the condition number for a single reading, or for a number of readings. Such information may be provided on a display. The user may then be able to quickly identify whether the reading is acceptable, or whether action must be taken, based on whether the value falls into acceptable ranges that may be indicated by differing colours, as inFIG.17. The ranges (e.g. desired, acceptable and hazardous) for the parameter ratio and/or the condition number may be the same for different operating parameters. As such, the described method may permit the user to more quickly and accurately understand whether action must be taken, thereby reducing the likelihood and severity of any accidents that may occur. In other cases, the threshold values for the desired, acceptable and hazardous ranges may differ, in which case having a display that illustrates the ranges, for example with boundary lines and/or colour coding, may assist a user to understand very quickly the significance of the parameter ratio for different parameter. In some examples and as previously indicated applies toFIG.17, the parameter ratio and/or the condition number may be provided (e.g. displayed) in or with a colour. For example, each value may be provided in or with (e.g. in a coloured area, when the value is displayed graphically, or with a coloured number, when the value is displayed numerically) a green colour when in the desired operation range, a yellow colour when in the acceptable operational range, and a red colour when in the hazardous operational range. As such, with only a quick glance, and without even a need to register the value of the parameter ratio and/or condition number, the user may be able to identify whether action must be taken to preserve the life of the pump and/or to avert an accident. In some examples, a plurality of operating parameters may be measured, each may be normalised and a separate normalisation factor may be calculated for each of the operating parameters, and individual desired, acceptable and hazardous operational ranges may be set for each of the operating parameters. In such examples, the user may be provided with multiple parameter ratios and/or condition numbers, one corresponding to each of the measured operating parameters. In some examples, it may be possible to combine parameter ratios and/or condition numbers, to provide a global parameter ratio and/or condition number, which may be indicative of the overall health of the pump operation. Such values (which may be considered to be global values) may be provided by averaging, using weighted calculations, multiplying the values, or the like. Such a value may provide an operator a quick and easy way to assess the overall health of the pump operation. In some examples, at least one of the operating parameters, parameter ratio and condition number may be provided to a computerised system, which may itself be able to automatically take action without direct intervention by a user. For example, where a parameter ratio is identified as being in the hazardous range, the pump may be automatically stopped, or the speed reduced, without the user having to take action. This may enable the pump to be operated so as to avoid, or significantly reduce, the chance of failure of the pump in operation. The described method may facilitate a user to operate multiple pumps as only one value per pump, or per operating parameter, has to be checked and a quicker analysis may be carried out on any of the pump condition parameters, the parameter ratio or the calculated condition numbers, for example in the case that the pump is not operating within its desired range. It is easier for a person to check one value compared to multiple parameters, therefore, when displaying the statuses of multiple pumps on a screen in some examples it may be advantageous to display only one global parameter ratio/condition number per pump as this may enable a display of the condition of more pumps on the screen compared to displaying multiple parameters per pump on the same screen. Any or all of the pump operating parameters, the normalized pump operating parameters, the parameter ratio and the pump condition number may be displayed on a pump operation display to provide a pump operator with a visual indication of the pump's operational state. Most advantageously, any or all of the pump operating parameters, the normalized pump operating parameters, the pump parameter ratios and the pump condition number may be displayed on a gauge, for example with a needle display, and optionally the gauge may comprise colour segments corresponding to the ideal, intermediate and hazardous operation conditions to facilitate understanding of multiple pump operation statuses simultaneously. The display type may be chosen as another type which may suit the user or may facilitate understanding. The pump may advantageously be a pump wherein the early detection of unfavourable operational states yields a significant economical, technical or safety benefits, e.g. by not having to replace a pump in harsh conditions, for example a subsea pump. The example inFIG.18shows the measurement data of multiple pump operating parameters and multiple normalized pump operating parameters at the failure of the pump thrust bearing. In particular is illustrated a graph of the pump speed against time4050as well as parameter ratios for the pump relative flow rate against time4052, pump relative head against time4054, and power relative power against time4056. As can be seen from the time axis4060(the Y-axis) of each of the illustrated graphs, each parameter is shown as measured over a4024hour period, with the Y-axis4060relating to time elapsed, and the most recent event being shown at the top of the graph inFIG.18. Since the more time that has passed since an event, the less significant the event becomes, the time indicated on the Y-axis4060is gradually compressed from 0 to 24 hours. Indicated by a broken line4062is the time point on the Y-axis4060that corresponds with the data that is being shown on dials or gauges4070,4072,4074,4076, as indicated by the needle on the dials/gauges. While the graphs4050,4052,4054,4056illustrate data over time, the dials may illustrate real-time data, or may illustrate data with a lag compared to real-time. However, rather than displaying the parameter ratio, the dials illustrate the condition number of the displayed data. In this example, the condition number is shown as a percentage value of between 0 and 100 percent. The exact condition number is additionally shown as a figure located in a bar4090, located above each of the graphs, thereby providing the user with a more exact indication of the performance of the pump. Illustrated on both the graphs and the dials are coloured sections, which correspond to the desired operational range (4078, illustrated in green), the acceptable operational range (4080, illustrated in yellow) and the hazardous operational range (4082, illustrated in red), thereby making it easy for a user to see and rapidly evaluate in which operational range the pump is operating. The coloured sections may serve as visual indicators to a user of the operational range of each parameter or parameter ration that is being measured. In the example illustrated, the dials4070,4072,4074show that for the speed parameter, and the pump relative flow and pump relative head parameter ratios, the pump is in a desired operational range and the condition number is equal to 100%. In contrast, the parameter ratio for the pump relative power is in the hazardous operational range (e.g. outside of both the desired and the acceptable operational ranges) and equal to 0%, therefore indicating to a user that action must be taken in order to avoid failure. In addition to displaying a condition number, the bar4090is also able to display the condition number in a colour that corresponds to operational range of the parameter or parameter ratio of the pump, thereby serving as a visual indicator to a user. Above the dials4070,4072,4074,4076is illustrated an indication of the global or overall state of the pump operation4092. Here, an overall condition number is displayed, that a user may be able to view to assess whether intervention to the operation of the pump is needed or not. The overall condition number may be generated, for example, by multiplying together (or alternatively averaging) each of the condition numbers of the parameters and/or parameter ratios that are being measured. In this case, since three of the condition numbers are equal to 100, and one of the condition numbers is equal to 0, and therefore the overall condition number is calculated to be 0, again indicating that user intervention may be required. Having an overall condition number may be particularly useful to a user in cases where many parameters and/or parameter ratios are being measured in the acceptable operational range (e.g. with a condition number of between 0 and 100 percent). In such cases, having one parameter or parameter ratio being measured in the acceptable operational range may not seem too detrimental to the overall operation of the pump, where there are many parameters or parameter ratios being measured in this range, the cumulative effect may begin to be detrimental to the pump operation. Having an overall condition number may assist to quickly illustrate to a user the cumulative effect of each parameter in such a situation. In addition, it may be possible to give each measured parameter or parameter ratio a weighting, when calculating the overall condition number, thereby placing more importance on having some operation parameters or parameter ratios in the desirable operational range, than others. Were this information to be displayed in a different format, for example one that illustrated the pump relative power as a parameter, it may be difficult for a user to ascertain whether the value of power displayed was acceptable or not, particularly as pump power may be influenced by other parameters, which would then need to be assessed by a user, taking time and therefore increasing the likelihood of pump failure. Therefore, analysing the pump operational state with the normalized pump operating parameters may facilitate the detection of unfavourable pump operational states. Illustrated inFIG.19is a cause and effect matrix4095, which details a selection of causes4096of failure, or of inhibition of the operation of a pump, and corresponds each of these causes4096with an effect4097, or a number of possible effects. Although not illustrated in the matrix4095, the cause and effect matrix may additionally provide an indication of the probability of each of the causes, thereby guiding a user to the most effective way to intervene in the operation of the pump. Such a matrix4095may be used in combination with the information provided on the display ofFIG.18. For example, a user may be able to identify an effect4096in the matrix4095based on the condition numbers and operational ranges of parameters and parameter ratios that are available to them, and thereby be provided with a possible cause, or a range of causes,4097. The person skilled in the art realises that the disclosure ofFIGS.15to18is not limited to the preferred embodiments described above. The person skilled in the art further realises that modifications and variations are possible within the scope of the appended clauses. Additionally, variations to the disclosed embodiments can be understood and effected by the skilled person in practicing the claimed disclosure, from a study of the drawings, the disclosure, and the appended clauses. Some examples and aspects will now be described in the following numbered, non-limiting, clauses: CLAUSE D1. A method for providing a visual indication of the state of operation of a subsea pump, comprising:normalising an operating parameter to provide a parameter ratio;setting a desired operational range for the parameter ratio;setting an acceptable operational range for the parameter ratio;providing a first visual indicator for indicating that the parameter ratio is inside the desired operational range, providing a second visual indicator for indicating that the parameter ratio is outside of the desired operational range and inside the acceptable operational range, and providing a third visual indicator for indicting that the parameter ratio is outside both the acceptable operational range and the desired operational range;providing a numerical scale for assigning a condition number to the parameter ratio based on the operational range of the parameter ratio;selectively displaying one of the first, the second and the third visual indicators, and the condition number on the numerical scale to a user. CLAUSE D2. The method according to clause D1, comprising normalising an operating parameter based on a known value of the operating parameter and an expected value of the operating parameter. CLAUSE D3. The method according to clause D1 or D2, wherein normalising the operating parameter comprises comparing an operating parameter against an expected value for the operating parameter. CLAUSE D4. The method according to clause D2 or D3, wherein the expected value of the normalised operating parameter is based upon operation of the subsea pump in test conditions, and in a non-used state. CLAUSE D5. The method according to any preceding clause, wherein the parameter ratio is assigned a maximum condition number on the numerical scale when within the desired operational range, a minimum condition number on the numerical scale when outside both the acceptable operational range and the desired operational range, and an intermediate condition number on the numerical scale when outside the desired operational range and inside the acceptable operational range. CLAUSE D6. The method according to clause D5, wherein the intermediate condition number assigned to the parameter ratio varies linearly with change in the value of the parameter ratio between the desired operational range and the acceptable operational range. CLAUSE D7. The method according to clause D5, wherein the intermediate condition number assigned to the parameter ratio has a quadratic, exponential, or other polynomial variation with change in the value of the parameter ratio between the desired operational range and the acceptable operational range. CLAUSE D8. The method according to any of clauses D5 to D7, wherein the maximum condition number is a percentage value between 0 and 100. CLAUSE D9. The method according to any preceding clause, wherein one of the first, second and third visual indicators are selected to be displayed depending on whether the parameter ratio is inside the desired operational range, outside the desired operational range and inside the acceptable operational range, and outside the acceptable operational range and the desired operational range. CLAUSE D10. The method according to any preceding clause, wherein the first visual indicator is the colour green, the second visual indicator is the colour yellow, and the third visual indicator is the colour red. CLAUSE D11. The method according to any preceding clause, comprising plotting the value of the parameter ratio on a graph over time and displaying the graph to a user. CLAUSE D12. The method according to clause D11, comprising providing the visual indicators on the graph. CLAUSE D13. The method according to any preceding clause, comprising displaying the visual indicators and indicating the operation number on a gauge with a needle. CLAUSE D14. The method according to any preceding clause, comprising normalising a plurality of operating parameters to provide a plurality of parameter ratios, and:setting a desired operational range for each of the plurality of parameter ratios;setting an acceptable operational range for each of the plurality of parameter ratios;assigning a condition number to each of the plurality of parameters based on the operation of each thereof;selectively displaying each of the first, the second, and the third visual indicators, and each condition number on a display for each of the plurality of operating parameters. CLAUSE D15. The method according to clause D14, comprising averaging the condition number for each of the plurality of operation numbers to provide an overall condition number. CLAUSE D16. The method according to any preceding clause, wherein providing a parameter ratio comprises the steps of:obtaining test data by operating the subsea pump under optimal test conditions to provide test data of the expected optimal operation of the subsea pump;comparing the value of an operating parameter of the pump in operation with the expected value for that operating parameter based on the test data;providing a parameter ratio of the operating parameter based on the comparison. CLAUSE D17. The method according to clause D16 or D17, wherein optimal test data is obtained via non-optimal conditions and then extrapolating/processing to achieve the optimal test data. CLAUSE D18. The method according to any preceding clause, comprising providing a sensor arrangement in the subsea pump for measuring the operating parameter. CLAUSE D19. The method according to any preceding clause, wherein the operating parameter is one of: pump speed, pump flow rate, fluid density and fluid viscosity. CLAUSE D20. The method according to any preceding clause, comprising changing operation of the subsea pump based on the value of the parameter ratio, wherein changing the operation of the subsea pump comprises at least one of ceasing operation of the subsea pump and changing the pump speed of the subsea pump. CLAUSE D21. The method according to clause D20, comprising automatically changing the operation of the subsea pump. | 160,995 |
11859629 | DESCRIPTION OF THE EMBODIMENTS The following will describe an embodiment of the present disclosure in detail with reference to the accompanying drawings. Embodiment According to an embodiment, a turbo compressor10serves as a turbo fluid machine of this disclosure. The turbo compressor10is mounted on a fuel cell vehicle that includes a fuel cell system1. The fuel cell system1supplies oxygen and hydrogen to a fuel cell mounted on the vehicle to generate electricity. The turbo compressor10compresses air containing oxygen to be supplied to the fuel cell. As illustrated inFIG.1, the turbo compressor10, which serves as the turbo fluid machine of the present disclosure, includes a housing11. The housing11is made of metal, such as aluminum alloy. The housing11includes a motor housing12, a compressor housing13, a turbine housing14, a first plate15, a second plate16, and a third plate17. The motor housing12includes a plate-like end wall12aand a peripheral wall12b. The peripheral wall12bhas a cylindrical shape and protrudes from an outer peripheral portion of the end wall12a. The first plate15is connected to an open end of the peripheral wall12bof the motor housing12to close an opening of the peripheral wall12b. In the motor housing12, an inner surface121aof the end wall12a, an inner peripheral surface121bof the peripheral wall12b, and an end face15aof the first plate15adjacent to the motor housing12cooperate to form a motor chamber S1. The motor chamber S1accommodates an electric motor18. The first plate15has a first bearing holding portion20. The first bearing holding portion20projects from the center portion of the end face15aof the first plate15toward the electric motor18. The first bearing holding portion20has a cylindrical shape. The other end face15bof the first plate15is distant from the motor housing12, and has a recess15chaving a bottom surface15d. The recess15chas a circular hole shape. The cylindrical first bearing holding portion20is opened toward the bottom surface15dof the recess15cthrough the first plate15. The recess15cis formed coaxially with the first bearing holding portion20. The recess15chas an inner peripheral surface15ethrough which the end face15bis connected to the bottom surface15d. The motor housing12has a second bearing holding portion22. The second bearing holding portion22projects from the center portion of the inner surface121aof the end wall12aof the motor housing12toward the electric motor18. The second bearing holding portion22has a cylindrical shape. The cylindrical second beating holding portion22is opened on an outer surface122aof the end wall12athrough the end wall12aof the motor housing12. The first bearing holding portion20is formed coaxially with the second bearing holding portion22. As illustrated inFIG.2, the second plate16is connected to the end face15bof the first plate15. The second plate16has a shaft insertion hole16aat the center portion of the second plate16. The shaft insertion hole16ais communicated with the recess15c. The shaft insertion hole16ais formed coaxially with the recess15cand the first bearing holding portion20. The second plate16has an end face16bthat is located adjacent to the first plate15, and the end face16bcooperates with the recess15cof the first plate15to define a thrust bearing accommodation chamber S2. The compressor housing13has a cylindrical shape, and has a circular hole-shaped inlet13athrough which air is drawn into the compressor housing13. The compressor housing13is connected to the other end face16cof the second plate16that is distant from the first plate15. The inlet13aof the compressor housing13is formed coaxially with the shaft insertion hole16aof the second plate16and the first bearing holding portion20. The inlet13ais opened on an end face of the compressor housing13that is distant from the second plate16. A first bladed wheel chamber13b, a discharge chamber13c, and a first diffuser passage13dare formed between the compressor housing13and the end face16cof the second plate16. The first bladed wheel chamber13bis communicated with the inlet13a. The discharge chamber13cextends about the axis of the inlet13aaround the first bladed wheel chamber13b. The first bladed wheel chamber13bis communicated with the discharge chamber13cthrough the first diffuser passage13d. The first bladed wheel chamber13bis communicated with the shaft insertion hole16aof the second plate16. As illustrated inFIG.3, the third plate17is connected to the outer surface122aof the end wall12aof the motor housing12. The third plate17has a shaft insertion hole17aat the center portion of the third plate17. The shaft insertion hole17ais communicated with the second beating holding portion22. The shaft insertion hole17ais formed coaxially with the second bearing holding portion22. The turbine housing14has a cylindrical shape, and has a circular hole-shaped outlet14athrough which air is discharged. The turbine housing14is connected to the other end face17bof the third plate17that is distant from the motor housing12. The outlet14aof the turbine housing14is formed coaxially with the shaft insertion hole17aof the third plate17and the second bearing holding portion22. The outlet14ais opened on an end face of the turbine housing14that is distant from the third plate17. A second bladed wheel chamber14b, a suction chamber14c, and a second diffuser passage14dare formed between the turbine housing14and the end face17bof the third plate17. The second bladed wheel chamber14bis communicated with the outlet14a. The suction chamber14cextends about the axis of the outlet14aaround the second bladed wheel chamber14b. The second bladed wheel chamber14bis communicated with the suction chamber14cthrough the second diffuser passage14d. The second bladed wheel chamber14bis communicated with the shaft insertion hole17aof the third plate17. As illustrated inFIG.1, a rotating member24is accommodated in the housing11. The rotating member24has a rotary shaft24aas a shaft portion, a first supporting portion24b, a second supporting portion24c, and a third supporting portion24d. The rotary shaft24ahas a first end portion24eas an end adjacent to the compressor housing13and a second end portion24fas an end adjacent to the turbine housing14. The first supporting portion24bis formed in a part of an outer peripheral surface240aof the rotary shaft24aadjacent to the first end portion24e, and disposed in the first bearing holding portion20. The first supporting portion24bis formed integrally with the rotary shaft24aand projected from the outer peripheral surface240aof the rotary shaft24aso as to have a ring shape. The second supporting portion24cis formed in a part of the outer peripheral surface240aof the rotary shaft24aadjacent to the second end portion24f, and disposed in the second bearing holding portion22. The second supporting portion24chas a cylindrical shape such that the second supporting portion24cis projected from the outer peripheral surface240aof the rotary shaft24aso as to have a ring shape, and is fixed to the outer peripheral surface240aof the rotary shaft24a. The second supporting portion24cis rotatable together with the rotary shaft24a. The third supporting portion24dis disposed in the thrust bearing accommodation chamber S2. The third supporting portion24dhas a disc shape (i.e., plate-like shape) such that the third supporting portion24dextends from the outer peripheral surface240aof the rotary shaft24ain the radial direction so as to have a ring shape, and is fixed to the outer peripheral surface240aof the rotary shaft24a. The third supporting portion24dis rotatable together with the rotary shaft24a. The third supporting portion24dis disposed distant from the electric motor18in the axial direction of the rotary shaft24a. The third supporting portion24dserves as the thrust collar of the present disclosure. In the following description, directions, such as the axial direction, the circumferential direction, and the radial direction denote the directions of the rotary shaft24a. One and the other circumferential directions respectively denote opposite one and the other rotational directions of the rotary shaft24aabout its axis. One side and the other side in the axial direction respectively mean a side on which the first end portion24eof the rotary shaft24ais located and a side on which the second end portion24fof the rotary shaft24ais located. The first end portion24eof the rotary shaft24ais connected to a first bladed wheel25that serves as the operating part of the present disclosure. The first bladed wheel25is disposed closer to the first end portion24ethan to the third supporting portion24dof the rotary shaft24a. The first bladed wheel25is accommodated in the first bladed wheel chamber13b. The second end portion24fof the rotary shaft24ais connected to a second bladed wheel26. The second bladed wheel26is disposed closer to the second end portion24fthan to the second supporting portion24cof the rotary shaft24a. The second bladed wheel26is accommodated in the second bladed wheel chamber14b. The first bladed wheel25, the second bladed wheel26, and the rotating member24are accommodated in the housing11. A first sealing member27is disposed between the shaft insertion hole16aof the second plate16and the rotating member24. The first sealing member27suppresses leak of air from the first bladed wheel chamber13btoward the motor chamber S1. A second sealing member28is disposed between the shaft insertion hole17aof the third plate17and the rotating member24. The second sealing member28suppresses leak of air from the second bladed wheel chamber14btoward the motor chamber S1. The first sealing member27and the second sealing member28are each a seal ring, for example. The electric motor18includes a cylindrical rotor36and a cylindrical stator35. The rotor36is fixed to the rotary shaft24a. The stator35is fixed in the housing11. The rotor36is disposed radially inside the stator35and rotated together with the rotating member24. The rotor36includes a cylindrical rotor core36afixed to the rotary shaft24aand a plurality of permanent magnets, which is not illustrated, disposed in the rotor core36a. The stator35surrounds the rotor36. The stator35includes a stator core35aand a coil34. The stator core35ahas a cylindrical shape and is fixed to the inner peripheral surface121bof the peripheral wall12bof the motor housing12. The coil34is wound around the stator core35a. The coil34receives current from a battery (not illustrated) so that the rotor36is rotated together with the rotating member24. The fuel cell system1includes a fuel cell stack100as a fuel cell mounted on a vehicle, the turbo compressor10, a supply passage L1, a discharge passage L2, and a branched passage L3. The fuel cell stack100includes a plurality of fuel cells. The fuel cell stack100is connected to the discharge chamber13cthrough the supply passage L1. The fuel cell stack100is also connected to the suction chamber14cthrough the discharge passage L2. The branched passage L3in which an intercooler110is disposed branches off from the supply passage L1. The intercooler110cools air flowing through the branched passage L3. When the rotating member24is rotated together with the rotor36, the first bladed wheel25and the second bladed wheel26are rotated together with the rotating member24. Air, which has been drawn through the inlet13a, is compressed by the first bladed wheel25in the first bladed wheel chamber13b, and discharged from the discharge chamber13cthrough the first diffuser passage13d. The air discharged from the discharge chamber13cis supplied to the fuel cell stack100through the supply passage L1. The air supplied to the fuel cell stack100is used for electricity generation by the fuel cell stack100, and the used air is then discharged as exhaust from the fuel cell stack100to the discharge passage L2. The exhaust from the fuel cell stack100is drawn into the suction chamber14cthrough the discharge passage L2. The exhaust drawn into the suction chamber14cis then discharged to the second bladed wheel chamber14bthrough the second diffuser passage14d. The exhaust discharged into the second bladed wheel chamber14brotates the second bladed wheel26. The rotating member24is rotated by the electric motor18and also by the rotation of the second bladed wheel26by the exhaust from the fuel cell stack100. The first bladed wheel25serving as the operating part of the present disclosure is rotated together with the rotating member24to compress and discharge air, which serves as the fluid of the present disclosure. The exhaust discharged into the second bladed wheel chamber14bis discharged outside from the outlet14a. The turbo compressor10includes a pair of thrust foil bearings30,30and a pair of radial foil bearings40,40. The pair of thrust foil bearings30,30supports the rotary shaft24ain the axial direction of the rotary shaft24asuch that the rotary shaft24ais rotatable relative to the housing11. The pair of radial foil bearings40,40supports the rotary shaft24ain a direction perpendicular to the axial direction of the rotary shaft24asuch that the rotary shaft24ais rotatable relative to the housing11. The pair of thrust foil bearings30,30is disposed in the thrust bearing accommodation chamber S2. The thrust foil bearings30,30hold therebetween the third supporting portion24das the thrust collar. The thrust foil bearings30,30face the third supporting portion24din the axial direction of the rotary shaft24a. One of the thrust foil bearings30,30is located adjacent to the first end portion24eof the rotary shaft24awith respect to the third supporting portion24d. The other of the thrust foil bearings30,30is located adjacent to the second end portion24fof the rotary shaft24awith respect to the third supporting portion24d. The opposite end faces of the third supporting portion24dserve as bearing-contact surfaces241d,241d. One of the bearing-contact surfaces241d,241dadjacent to the first end portion24eof the rotary shaft24ais axially supported by the one of the thrust foil bearings30,30(seeFIGS.2and7). The other of the bearing-contact surfaces241d,241dadjacent to the second end portion24fof the rotary shaft24ais axially supported by the other of the thrust foil bearings30,30. Since one and the other of the thrust foil bearings30,30have the same configuration, the following description will focus on the one of the thrust foil bearings30,30, and will not elaborate the other of the thrust foil bearings30,30. In the following description, the rotary shaft24ais rotated in the one rotational direction about the axis of the rotary shaft24awhen the rotating member24is rotated together with the rotor36. In this embodiment, the one rotational direction about the axis of the rotary shaft24ameans the counterclockwise rotational direction of the rotary shaft24aillustrated inFIG.4, and is indicated by the arrow R inFIGS.4-8. As illustrated inFIGS.4and5, the thrust foil bearing30includes a bearing housing31, six bump foils32attached to the bearing housing31, and six top foils33attached to the bearing housing31and located at positions respectively corresponding to the bump foils32. Each of the bump foils32and each of the top foils33have an approximately fan-like outline in a plane view. The bump foils32and the top foils33are each formed of an elastic thin plate, which is made of metal, such as stainless steel, and have a predetermined shape. The bearing housing31is formed of a part of the second plate16. That is, the bearing housing31is formed of the end face16bof the second plate16at a part of the end face16bthat defines the thrust bearing accommodation chamber S2. The bearing housing31faces the third supporting portion24din the axial direction of the rotary shaft24a. The bearing housing31has an insertion hole31athrough which the rotary shaft24ais inserted. Additionally, the other of the thrust foil bearings30,30includes a bearing housing31that is formed of the recess15cof the first plate15that defines the thrust bearing accommodation chamber S2. In this embodiment, the six bump foils32are attached on an end face of the bearing housing31adjacent to the third supporting portion24d, and equally spaced from each other around the insertion hole31ain the circumferential direction of the rotary shaft24a. Each of the bump foils32has opposite ends in the circumferential direction, and one end of the opposite ends is fixed to the bearing housing31by welding. That is, the one end of the bump foil32is a fixed end32a, and the other end of the bump foil32, which is located behind the one end of the bump foil32in the one circumferential direction, is a free end32b. Reversely, the one end and the other end of the bump foil32may be respectively a free end and a fixed end. As illustrated inFIG.7, the bump foil32has a corrugated shape in which a plurality of projections32cand a plurality of depressions32dare alternatingly arranged in the circumferential direction of the rotary shaft24a. That is, a plurality of ridges32eof the projections32care arranged in the circumferential direction of the rotary shaft24a, and includes a plurality of outer ridges321eand a plurality of inner ridges322e. The projections32care projected toward the third supporting portion24dto come in contact with the top foil33so as to elastically support the top foil33. One of the opposite surfaces of the top foil33serves as a bearing surface33cthat faces the bearing-contact surface241dof the third supporting portion24din the axial direction, and the other of the opposite surfaces of the top foil33is elastically supported by the corresponding bump foil32. Each of the bump foils32is divided with respect to the radial direction of the rotary shaft24ainto an outer peripheral foil321and an inner peripheral foil322that are respectively arranged on the outer peripheral side and the inner peripheral side of the bump foil32. The outer peripheral foil321has one end and the other end that is located behind the one end of the outer peripheral foil321in the one circumferential direction. The inner peripheral foil322has one end and the other end that is located behind the one end of the inner peripheral foil322in the one circumferential direction. The one end of the outer peripheral foil321is integrally connected to the one end of the inner peripheral foil322by a connecting portion32f. This connection with the connecting portion32ffacilitates the handling and the assembly of the outer peripheral foil321and the inner peripheral foil322. This connection with the connecting portion32fdoes not interfere with the operation and the transformation of the outer peripheral foil321and the inner peripheral foil322. As illustrated inFIG.4, the outer peripheral foil321has the plurality of outer ridges321e, and an edge321a, which is one of the opposite edges of the outer peripheral foil321in the radial direction and located adjacent to the inner peripheral side with respect to the other of the opposite edges. The outer ridges321eare inclined in the other rotational direction while extending from the edge321atoward the outer peripheral side. The inner peripheral foil322has the plurality of inner ridges322e, and an edge322a, which is one of the opposite edges of the inner peripheral foil322in the radial direction and located adjacent to the outer peripheral side with respect to the other of the opposite edges. The inner ridges322eare inclined in the other rotational direction while extending from the edge322atoward the inner peripheral side. As illustrated inFIG.6, the outer peripheral foil321and the inner peripheral foil322respectively have an outer radial width Wout and an inner radial width Win in the radial direction, and the outer radial width Wout is equal to the inner radial width Win. Each outer ridge321eof the outer peripheral foil321and each inner ridge322eof the inner peripheral foil322respectively form an outer acute angle θout and an inner acute angle θin with the radial direction, and the outer acute angle θout is equal to the inner acute angle θin. The outer acute angle θout of the outer ridge321eof the outer peripheral foil321may mean an inclined angle of the outer ridge321eat which the outer ridge321eis inclined in the other rotational direction. The inner acute angle θin of the inner ridge322eof the inner peripheral foil322may mean an inclined angle of the inner ridge322eat which the inner ridge322eis inclined in the other rotational direction. In this embodiment, the six top foils33are attached on the end face of the bearing housing31adjacent to the third supporting portion24d, and the top foils33are disposed alongside around the insertion hole31aand equally spaced from each other in the circumferential direction of the rotary shaft24aso as to respectively correspond to the bump foils32. Each of the top foils33has opposite ends in the circumferential direction, and one end of the opposite ends is located in front of the other end of the opposite ends in the one circumferential direction of the rotary shaft24a. The other end of the opposite ends is folded toward the bearing housing31and fixed to the bearing housing31at the distal portion of the other end by welding. That is, the one end and the other end of the top foil33are a free end33band a fixed end33a, respectively. One of the radial foil bearings40,40is disposed in the first bearing holding portion20, and the other of the radial foil bearings40,40is disposed in the second bearing holding portion22. In the first bearing holding portion20, the first supporting portion24bof the rotating member24is rotatably supported by the one of the radial foil bearings40,40. The first supporting portion24bhas an outer peripheral surface that serves as a radial bearing-contact surface24gsupported by the one of the radial foil bearings40,40in the direction perpendicular to the axial direction of the rotary shaft24a. In the second bearing holding portion22, the second supporting portion24cof the rotating member24is rotatably supported by the other of the radial foil bearings40,40. The second supporting portion24chas an outer peripheral surface that serves as the radial bearing-contact surface24gsupported by the other of the radial foil bearings40,40in the direction perpendicular to the axial direction of the rotary shaft24a. Since one and the other of the radial foil bearings40,40have the same configuration, the following description will focus on the one of the radial foil bearings40,40, and will not elaborate the other of the radial foil bearings40,40. The radial foil bearing40includes a radial bearing housing41, a radial bump foil42, and a radial top foil43. The first bearing holding portion20serves as the radial bearing housing41of the one of the radial foil bearings40,40and the second bearing holding portion22serves as the radial bearing housing41of the other of the radial foil bearings40,40. The radial bump foil42and the radial top foil43are each formed of an elastic thin plate made of metal, such as stainless steel, and has a predetermined approximately cylindrical shape. The radial bump foil42and the radial top foil43each have opposite ends in the circumferential direction of the rotary shaft24a, and one end of the opposite ends is located in front of the other end of the opposite ends in the one circumferential direction of the rotary shaft24a. The other end of the opposite ends is folded outwardly in the radial direction and fixed to the radial bearing housing41. That is, the one end and the other end of each of the radial bump foil42and the radial top foil43are a free end and a fixed end, respectively. The radial bump foil42has a corrugated shape in which a plurality of projections projected toward the radial top foil43has ridges arranged in the circumferential direction of the rotary shaft24a. The radial bump foil42also has depressions alternating with the projections, and elastically supports the radial top foil43by the projections with the depressions supported by the radial bearing housing41. The radial top foil43is elastically supported by the radial bump foil42at one of the opposite surfaces of the radial top foil43, and the other surface of the radial top foil43serves as a radial bearing surface43a(seeFIGS.2and3) that faces the radial bearing-contact surface24gin the radial direction. As illustrated inFIG.7, the thrust foil bearings30,30support the rotary shaft24awith the bearing surface33cof the top foil33in contact with the bearing-contact surface241dof the third supporting portion24duntil the rotational speed of the rotary shaft24areaches a floating rotational speed at which the third supporting portion24dserving as the thrust collar floats off the thrust foil bearings30,30. As illustrated inFIG.8, when the rotational speed of the rotary shaft24areaches the floating rotational speed, a pressure of the fluid film generated between the top foil33and the third supporting portion24dcauses the top foil33to elastically deform with elastic deformation of the bump foil32, thereby causing the third supporting portion24dto float off the thrust foil bearings30,30. Accordingly, the thrust foil bearings30,30support the rotary shaft24awithout contacting the third supporting portion24d. The radial foil bearings40,40support the rotary shaft24awith the radial bearing surface43aof the radial top foil43in contact with the radial bearing-contact surface24gof the first supporting portion24band the radial bearing-contact surface24gof the second supporting portion24cuntil the rotational speed of the rotary shaft24areaches a floating rotational speed at which the first supporting portion24band the second supporting portion24cof the rotary shaft24afloat off the radial foil bearings40,40. When the rotational speed of the rotary shaft24areaches the floating rotational speed, a pressure of the fluid film generated between the radial top foil43and the first and second supporting portions24b,24ccauses the first and second supporting portions24b,24cto float off the radial foil bearings40,40. Accordingly, the radial foil bearings40,40support the rotary shaft24awithout contacting the first supporting portion24band the second supporting portion24c. As illustrated inFIGS.1-3, the housing11has a cooling passage50. Air serving as the fluid flows through the cooling passage50. The cooling passage50is formed through the second plate16, the first plate15, the motor housing12, and the third plate17. The cooling passage50includes a first passage51and a second passage52. The first passage51is formed in the second plate16. The first passage51has an inlet51aformed in a side wall surface of the second plate16. The inlet51aof the first passage51is connected to the supply passage L1through the branched passage L3. The first passage51is communicated with the motor chamber S1through the thrust bearing accommodation chamber S2and the one of the radial foil bearings40,40. The second passage52is formed in the third plate17. The second passage52has an outlet52aformed in a side surface of the third plate17. The second passage52is communicated with the motor chamber S1through the other of the radial foil bearings40,40. The air flowed through the supply passage L1toward the fuel cell stack100partly flows into the first passage51through the branched passage L3. The air in the first passage51has been cooled by the intercooler110while flowing through the branched passage L3. The cooled air in the first passage51flows into the thrust bearing accommodation chamber S2. The cooled air in the thrust bearing accommodation chamber S2flows from the inner peripheral side toward the outer peripheral side mainly through the one of the thrust foil bearings30,30. Specifically, the cooled air flows from the inner peripheral side of the top foil33toward the outer peripheral side of the top foil33through a gap between the top foil33and the bearing housing31of the one of the thrust foil bearings30,30. The cooled air flows radially outside of the third supporting portion24das the thrust collar, and flows from the outer peripheral side toward the inner peripheral side mainly through the other of the thrust foil bearings30,30. Specifically, the cooled air flows from the outer peripheral side of the top foil33toward the inner peripheral side of the top foil33through a gap between the top foil33and the bearing housing31of the other of the thrust foil bearings30,30. The cooled air flows through the thrust bearing accommodation chamber S2and then flows into the motor chamber S1through the one of the radial foil bearings40,40. Specifically, the cooled air flows from the one side toward the other side in the axial direction, through a gap between the radial top foil43and the radial bearing housing41of the one of the radial foil bearings40,40. The cooled air flows through the one of the radial foil bearings40,40and flows into the motor chamber S1. The air in the motor chamber S1, for example, flows through a gap between the rotor36and the stator35, and the air then flows into the second passage52through the other of the radial foil bearings40,40and is discharged from the outlet52a. Accordingly, the cooled air flows through the cooling passage50so as to directly cool the electric motor18, the pair of thrust foil bearings30,30, and the pair of radial foil bearings40,40. In this turbo compressor10, the bump foil32of each thrust foil bearing30is divided into the outer peripheral foil321on the outer peripheral side and the inner peripheral foil322on the inner peripheral side with respect to the radial direction of the rotary shaft24a, and an inclined angle of the ridge32eof each projection32cof the corrugated shape is different between the outer peripheral foil321and the inner peripheral foil322. Specifically, the outer ridges321eon the outer peripheral foil321are inclined in the other rotational direction while extending from the edge321aadjacent to the inner peripheral side toward the outer peripheral side. The inner ridges322eon the inner peripheral foil322are inclined in the other rotational direction while extending from the edge322aadjacent to the outer peripheral side toward the inner peripheral side. That is, the outer ridges321eon the outer peripheral foil321are inclined rearward in a rotational direction R while extending from the inner peripheral side toward the outer peripheral side. In contrast, the inner ridges322eon the inner peripheral foil322are inclined rearward in the rotational direction R while extending from the outer peripheral side toward the inner peripheral side. In this configuration, the rotation of the rotary shaft24aat a high rotational speed equal to or faster than the floating rotational speed causes the corrugated shape of the bump foil32to be transferred to the top foil33, so that the top foil33has a herringbone shape such that the peak of each V-shape formed by ridges of projections on the top foil33is oriented frontward in the one rotational direction, i.e., in the rotational direction R. In the bearing gap between the bearing surface33cof the top foil33and the bearing-contact surface241dof the third supporting portion24das the thrust collar, this herringbone configuration allows the fluid to be guided by each ridge toward the peak of the V-shape, in other words, toward the radially center portion of the top foil33from the outer peripheral side and the inner peripheral side of the top foil33. This configuration therefore suppresses a leak of the fluid compressed in the bearing gap from the outer peripheral side and the inner peripheral side, thereby suppressing a decrease in the pressure of the fluid film in the bearing gap. In contrast, the thrust foil bearing30is likely to be heated by sliding of the thrust collar on the top foil33at low speed rotation of the thrust collar because the thrust collar is supported by the top foil33with the thrust collar in contact with the top foil33. Since both of the bearing surface33cand the bearing-contact surface241dare not provided with a groove, area of contact between the bearing surface33cand the bearing-contact surface241dis not reduced by the presence of a groove at a low rotation speed of the rotary shaft24aat which the rotary shaft24arotates at a rotational speed lower than the floating rotational speed such that the bearing-contact surface241dslides on the bearing surface33c. This prevents a decrease in the durability of the top foil33by wear or burn-in. Accordingly, the turbo compressor10is capable of suppressing a decrease in the pressure of the fluid film on the thrust foil bearing30so as to suppress a decrease in a load capacity of the thrust foil bearing30without causing a decrease in the durability of the top foil33. The thrust foil bearing30may have a problem on a heat resistance of the top foil33. At high speed rotation of the thrust collar, the top foil33is likely to be heated by shearing of a fluid film between the thrust collar and the top foil33. The top foil33is formed of an elastic thin plate having a low heat capacity. Accordingly, the top foil33is likely to have high temperature. In this regard, the cooled air flows through the gap between the bearing housing31and the top foil33in the turbo compressor10so as to cool the top foil33. This alleviates the problem on the heat resistance of the top foil33. Similarly, the cooled air flows through the gap between the radial bearing housing41and the radial top foil43of each radial foil bearing40so as to cool the radial top foil43. This alleviates the problem on the heat resistance of the radial top foil43. If the first passage51of the cooling passage50is formed such that the cooled air flows through the gap between the bearing housing31and the top foil33of the thrust foil bearing30, the fluid from the inner and outer peripheral sides of the bearing gap flows outside the thrust bearing accommodation chamber S2through the first passage51together with the cooled air. The fluid leak from the inner and outer peripheral sides of the bearing gap directly leads to a decrease in the pressure of the fluid film. Accordingly, it is more important to suppress the fluid leak from the inner and outer peripheral sides of the bearing gap. In this regard, the turbo compressor10suppresses the fluid leak from the inner and outer peripheral sides of the bearing gap by the presence of the ridges of the projections on the top foil33, so that this configuration exhibits this advantageous effects of fluid leak suppression notably if the first passage51of the cooling passage50is formed in the above-described manner. The following will describe modification examples 1 to 3 in which the bump foil32of the thrust foil bearing30of the turbo compressor10is modified. Modification Example 1 of Bump Foil As illustrated inFIG.9, according to the modification example 1, the outer peripheral foil321and the inner peripheral foil322of the bump foil32respectively have the outer radial width Wout and the inner radial width Win in the radial direction, and the outer radial width Wout is greater than the inner radial width Win. The outer acute angle θout of the outer ridge321eof the outer peripheral foil321is equal to the inner acute angle θin of the inner ridge322eof the inner peripheral foil322. In each thrust foil bearing30, centrifugal force causes the fluid leak from the bearing gap of the top foil33on the outer peripheral side to be larger than that on the inner peripheral side. In the thrust foil bearing30of the modification example 1, the outer radial width Wout of the outer peripheral foil321on the outer peripheral side is greater than the inner radial width Win of the inner peripheral foil322on the inner peripheral side. This configuration increases the force that effectively gathers the fluid, which may leak from the outer peripheral side of the top foil33by the centrifugal force, into the center portion of the top foil33in the radial direction, thereby suppressing the fluid leak from the outer peripheral side of the bearing gap effectively. Modification Example 2 of Bump Foil As illustrated inFIG.10, in the bump foil32according to the modification example 2, the outer acute angle θout of the outer ridge321eof the outer peripheral foil321is greater than the inner acute angle θin of the inner ridge322eof the inner peripheral foil322. In the bump foil32according to the modification example 2, the outer radial width Wout of the outer peripheral foil321is equal to the inner radial width Win of the inner peripheral foil322. In this case, the centrifugal force increases the force that effectively gathers the fluid, which may leak from the outer peripheral side, into the radially center portion of the bearing gap in the top foil33, thereby suppressing the fluid leak from the outer peripheral side of the beating gap effectively. Modification Example 3 of Bump Foil As illustrated inFIG.11, the outer peripheral foil321of the bump foil32according to the modification example 3 is divided into some portions arranged in the radial direction of the rotary shaft24a. That is, the outer peripheral foil321is divided into a first outer peripheral foil323adjacent to the outer peripheral side and a second outer peripheral foil324adjacent to the inner peripheral side. The outer ridges321eof the outer peripheral foil321include first ridges323eon the first outer peripheral foil323and second ridges324eon the second outer peripheral foil324. Each first ridge323eof the first outer peripheral foil323and each second ridge324eof the second outer peripheral foil324respectively form a first outer acute angle θout1and a second outer acute angle θout2with the radial direction, and the first outer acute angle θout1is greater than the second outer acute angle θout2. The first outer acute angle θout1of the first ridge323eof the first outer peripheral foil323is greater than the inner acute angle θin of the inner ridge322eof the inner peripheral foil322, and the inner acute angle θin of the inner ridge322eis greater than the second outer acute angle θout2of the second ridge324eof the second outer peripheral foil324. Further, the first outer peripheral foil323and the second outer peripheral foil324respectively have a first outer radial width Wout1and a second outer radial width Wout2in the radial direction. The first outer radial width Wout1is greater than the second outer radial width Wout2, and the second outer radial width Wout2is greater than the inner radial width Win of the inner peripheral foil322. In this case, the centrifugal force increases the force that gathers the fluid, which may leak from the outer peripheral side, into the center of the bearing gap in the top foil33, thereby suppressing the fluid leak from the outer peripheral side of the bearing gap more effectively. Although the present disclosure has been described based on the above embodiment, the present disclosure is not limited to the above embodiment, and may be modified within the scope of the present disclosure. Although the thrust foil bearing30according to the embodiment includes the six bump foils32and the six top foils33, the number of the bump foils32and the top foils33is not limited thereto as long as the number of the bump foils32is not singular and matches the number of the top foils33. In the thrust foil bearing30according to the embodiment, the outer peripheral foil321is connected to the inner peripheral foil322by the connecting portion32f. However, the outer peripheral foil321may not be connected to the inner peripheral foil322. According to the embodiment, the housing11includes the second plate16and the first plate15. A part of the second plate16serves as the bearing housing31of the one of the thrust foil bearings30,30. A part of the first plate15serves as the bearing housing31of the other of the thrust foil bearings30,30. However, the configuration of the bearing housing31of each thrust foil bearing30is not limited thereto. The bearing housing31of each thrust foil bearing30may be formed of a member that is not a member of the housing11. The present disclosure is applicable to an air compressor or the like for fuel cell system. | 40,256 |
11859630 | First, referring toFIG.1an assembled side channel compressor which is illustrated there in its entirety and has the purpose of compressing a gas comprises an impeller2which is provided with impeller blades1and is mounted such that it can be driven in rotation about a longitudinal central axis4in a housing3of the side channel compressor. The longitudinal central axis4therefore forms a rotational axis. The housing3has a housing body5and a removable housing lid6, which are aligned together according toFIG.1and together enclose the impeller2which is arranged in rotationally fixed fashion on a driveshaft7and has the impeller blades1. The single-row impeller2is constructed in the manner of a disk. It has an impeller hub8with a central hub drilled hole9. The impeller hub8is formed by an internal hub foot10which adjoins the hub drilled hole9radially outward, and a circular-ring-shaped hub disk11which adjoins said hub foot10and runs radially outward from there. The impeller2also has a radially outer bearing ring12which adjoins the hub disk11radially on the outside and overlaps with it on both sides in the direction of the longitudinal central axis4. The bearing ring12accordingly has a bearing ring base13facing the longitudinal central axis4, and said bearing ring12has, distributed in a circumferential direction, a multiplicity of impeller blades1which are arranged equidistantly with respect to one another and project radially outward from the bearing ring12. The hub foot10, the hub disk11and the bearing ring13are embodied as a single-piece cast part. The housing body5has a first hub section14, which spatially bounds a first partial hub receptacle space15. The first hub section14is penetrated by a central shaft drilled hole16which opens into the first partial hub receptacle space15. A first side channel section17adjoins the first hub section14radially in the outward direction. The first hub section14and the first side channel section17are embodied as a single-piece cast part and form the housing body5. The housing lid6is screwed to the housing body5in the assembled state of the housing3. Said housing lid6has a second hub section18which spatially bounds a second partial hub receptacle space19. A second side channel section20adjoins the second hub section18in a radially outward direction. A roller bearing21for supporting the driveshaft7is arranged in the second hub section18. The driveshaft7has at the end side a bearing pin which is rotatably mounted by the roller bearing21. The second hub section18and the second side channel section20are embodied as a single-piece cast part and form the housing lid6. The housing body5and the housing lid6are connected to one another in such a way that the two partial hub receptacle spaces15,19together bound a hub receptacle space, and the two side channel sections17,20together spatially bound a side channel22for conducting or feeding a gas. The side channel22extends around the longitudinal central axis4in an annular shape, in a spaced-apart fashion. A gas inlet opening, which opens into the side channel22, is constructed in the housing3. In addition, a gas outlet opening, which also has a flow connection to the side channel22and is arranged adjacent, but separately, with respect to the gas inlet opening, is constructed in the housing3. An interrupter is arranged in the side channel22, between the gas inlet opening and the gas outlet opening. In the hub receptacle space there are the hub foot10and the hub disk11of the impeller2, wherein the hub drilled hole9is penetrated by the driveshaft7. The impeller blades1are located in the side channel22. In order to drive the impeller2in rotation in the circumferential direction, a conventional drive23is used which is embodied as an electric drive. The drive23is flanged onto the housing body5and has a drive housing24which spatially bounds a drive interior25. The drive housing24has a casing body26and an end plate27which is attached to the end side thereof, and a radiator cover28. Accommodated in the drive interior25is a drive stator29which in turn comprises a stator laminated core30which is attached to the inside of the casing body26, and a stator winding31. The stator winding31comprises a plurality of coils which are directly connected to the stator laminated core30. A second roller bearing32, which rotatably supports the driveshaft7, is accommodated in the end plate27. In the drive interior25there is also a rotor33which is arranged in a rotationally fixed fashion on the driveshaft7and runs within the drive stator29. The rotor33comprises a rotor laminated core34and rotor rods35. A drive radiator wheel36is arranged in a rotationally fixed fashion on an end section, guided through the end plate27, of the driveshaft27. The radiator lid28surrounds the drive radiator wheel36. The drive23operates in a conventional, generally known fashion. In the case of connection to the power grid, the stator winding31has a current flowing through it, as a result of which a magnetic field is produced in the drive stator29. The drive stator29thus interacts with the rotor33. The rotor33, and therefore also the driveshaft7, are then set in rotation about the longitudinal central axis4. For reasons of tightness, a driveshaft seal37is arranged in the housing body5, which driveshaft seal37rests in a seal-forming fashion on the outside of the driveshaft7and avoids a leakage current there. In addition, a seal assembly38is arranged both in the housing body5and in the housing lid6. These seal assemblies38are of identical design. In order to accommodate the seal assemblies38, an annular groove39is respectively formed in the housing body5and in the housing lid6, which annular grooves39are each spatially bounded by a radially inner internal edge40and a radially outer external edge41which lies opposite the respective internal edge40, and a base edge42which connects the respective internal edge40and external edge41. The internal edges40are at a shorter distance from the longitudinal central axis4than the external edges41. They run parallel and concentrically with respect to the external edges41. The base edges42run perpendicularly with respect to the adjacent internal edge40and external edge41. The annular grooves39run at a constant distance around the longitudinal central axis4and are open toward the hub receptacle space. Adjacent to each hub receptacle space, each internal edge40has a top surface which is formed on an annular web44which projects radially outward to form a retaining edge43. Each retaining edge43runs in an annular shape around the longitudinal central axis4and faces the adjacent base edge42of the respective annular groove39. Each retaining edge43runs parallel to the adjacent base edge42of the respective annular groove39. It has a radial height which is substantially smaller than the corresponding radial height of a base edge42. Between each annular groove39and the side channel22, the housing body5and the housing lid6have in each case a receptacle cutout45, so that the internal edges40are longer in the direction of the longitudinal central axis4and wider than the external edges41. The bearing ring12engages in the receptacle cutouts45. Each seal assembly38comprises a sealing-device-holding device46which is arranged adjacent to the respective internal edge40, and a sealing strip47which abuts radially against the outside of the respective sealing-device-holding device46. Each sealing-device-holding device46has an annular, ribbon-shaped main holding body48which runs at a constant distance around the longitudinal central axis4and has an axial width BF in the direction of the longitudinal central axis4, which axial width BF corresponds approximately to an axial length or width LN of an internal edge40in the direction of the longitudinal central axis4. Each main holding body48has as an inner abutment edge49which abuts against the respective base edge42. In addition, each sealing-device-holding device46has a multiplicity of tab-like spring projections50which are each bent out in the direction of the longitudinal central axis4to form a bending line51running parallel to the abutment edge49. The bending lines51run spaced apart from the abutment edge49. The spring projections50extend here obliquely or in a curved fashion with respect to the main holding body48. Starting from the respective bending line51, they run away from the adjacent abutment edge49. Each spring projection50has a free end52which abuts in a supporting fashion against the respective retaining edge43and internal edge40. As a result of the bending of the spring projections50out of the respective main holding body48, a multiplicity of bent-out openings53are formed therein and are closed on the circumferential side. In addition, a multiplicity of holding projections54project radially outward from each main holding body48and are arranged opposite the abutment edge49and are bent out of the main holding body48to form respective bending lines55. The bending lines55run parallel to the longitudinal central axis4. An axial distance AH between the holding projections54and the abutment edge49of the sealing-device-holding device46corresponds to an axial width BD of a sealing strip47. Each sealing strip47abuts radially on the outside of the assigned main holding body48, which therefore has a bearing surface56for the respective sealing strip47. The sealing strips47cover the bent-out openings53. The holding projections54abut against a side edge57of the respective sealing strip47, which side edge57faces away from the adjacent base edge42or faces the hub receptacle space. Each sealing strip47abuts against the associated base edge42and abuts against the adjacent external edge41. Each sealing strip47projects axially in the direction of the longitudinal central axis4with respect to the adjacent external edge41to form a free sealing region58. The sealing regions58abut in a seal-forming fashion against the bearing ring base13radially on the inside with respect to the longitudinal central axis4. During the operation of the side channel compressor, the impeller2moves over the sealing strips47, in particular over the free sealing regions58. Each sealing strip47overlaps a gap59between the bearing ring12and the housing body5or housing lid6. Each sealing strip47engages behind the adjacent bearing ring base13. Each sealing-device-holding device46is secured on both sides axially with respect to the longitudinal central axis4. This is achieved by means of the simultaneous abutment of the abutment edge49against the adjacent base edge42and the housing3and by the abutment of the spring projections50against the adjacent retaining edge43or the housing3. Each sealing strip47is secured on both sides axially with respect to the longitudinal central axis4. This is achieved by means of the simultaneous abutment of the respective sealing strip47against the adjacent base edge42or the housing3and against the holding projections54. Each sealing strip47is pressed radially outward in a sprung fashion by the spring projections50which are supported with respect to the internal edges40. The generated spring stress is elastic. Each sealing-device-holding device46continually transmits a radially outwardly directed spring stress to the adjacent sealing strip47and in this way also ensures, if appropriate, that there is automatic spatial adjustment thereof in the radially outward direction, with the result that wear or deformations of the respective sealing strip47are automatically compensated. The sealing strips47are pressed against the external edges41and the bearing ring base13. A second embodiment is described below with reference toFIGS.6to9. In contrast to the previous embodiment, to the description of which reference is explicitly made herewith, the spring projections50are bent out of the main holding body48here to form bending lines51which extend parallel to the longitudinal central axis4. Otherwise, there are no significant differences. The expressions “radially”, “axially” or the like which are used refer, in particular, to the longitudinal central axis4. | 12,168 |
11859631 | DETAILED DESCRIPTION As would be appreciated by those skilled in the art, turbomachinery involving rotors of tie bolt construction (also known in the art as thru bolt or tie rod construction) need to be sealed so that a process fluid (which could be flammable or otherwise hazardous) and which is pressurized by a turbomachine (e.g., a compressor) is inhibited from escaping to the atmosphere. In certain known rotor structures, this sealing is typically done using one or more seals (e.g., O-rings) disposed between the tie-bolt and the bore of a shaft section of the rotor. A respective O-ring may thus be subject to the process fluid internal pressure on one side and to atmospheric pressure on the other side. The present inventors have recognized that such known rotor structures lack features that would allow monitoring an incipient leakage of the process fluid about the tie bolt. Additionally, such known rotor structures lack features that would allow conveying a sealing fluid (such as a dry sealing fluid) about the tie bolt. Disclosed embodiments make use of an innovative venting/sealing arrangement providing reliable and cost-effective venting/sealing backups and/or venting/sealing redundancies, such as with features that may be effective for venting about the tie bolt so that, for example, an incipient leakage of the process fluid can be monitored and in turn malfunctioning seals can be appropriately and timely replaced before escalating to an undesirable condition. The venting may be carried out by way of a conduit—drilled or otherwise constructed through a stub shaft—that under certain operational conditions effectively functions as a vent. Additionally, such features may be effective for conveying an appropriately pressurized sealing fluid about the tie bolt effective for reducing the likelihood of the process fluid escaping to the atmosphere. The conveying of the sealing fluid to the tie bolt may be carried out by way of another conduit—similarly drilled or otherwise constructed through the stub shaft—that under certain operational conditions effectively permits conveying the sealing fluid to the tie bolt. In the following detailed description, various specific details are set forth in order to provide a thorough understanding of such embodiments. However, those skilled in the art will understand that disclosed embodiments may be practiced without these specific details that the aspects of the present invention are not limited to the disclosed embodiments, and that aspects of the present invention may be practiced in a variety of alternative embodiments. In other instances, methods, procedures, and components, which would be well-understood by one skilled in the art have not been described in detail to avoid unnecessary and burdensome explanation. Furthermore, various operations may be described as multiple discrete steps performed in a manner that is helpful for understanding embodiments of the present invention. However, the order of description should not be construed as to imply that these operations need be performed in the order they are presented, nor that they are even order dependent, unless otherwise indicated. Moreover, repeated usage of the phrase “in one embodiment” does not necessarily refer to the same embodiment, although it may. It is noted that disclosed embodiments need not be construed as mutually exclusive embodiments, since aspects of such disclosed embodiments may be appropriately combined by one skilled in the art depending on the needs of a given application. FIG.1illustrates a fragmentary cross-sectional view of one non-limiting embodiment of a disclosed rotor structure100, as may be used in industrial applications involving turbomachinery, such as without limitation, compressors (e.g., centrifugal compressors, etc.). In one disclosed embodiment, a tie bolt102extends axially between a pressurized (e.g., relatively high pressure) process side and an atmospheric pressure side of the turbomachine. As would be readily appreciated by one skilled in the art, a stub shaft1041is fixed to a first end of tie bolt102. A second stub shaft1042is fixed to a second end of tie bolt102. Second end of tie bolt102is axially opposite the first end of tie bolt102. The description will proceed in connection with a first venting/sealing arrangement arranged proximate the first end of tie bolt102, as illustrated inFIG.1. As would be appreciated by one skilled in the art, a second venting/sealing arrangement is arranged proximate the second end of tie bolt102. Since the first and second venting/sealing arrangements comprise identical structural and/or operational relationships in order to avoid pedantic and burdensome repetition the description will proceed in connection with just the first venting/sealing arrangement arranged proximate the first end of tie bolt102, as illustrated inFIG.1. Essentially, the first and second venting/sealing arrangements would exhibit structural symmetry with respect to one another about a radial plane101that cuts the longitudinal axis of the turbomachine. In one disclosed embodiment, a plurality of axially spaced apart annular seals106, such as annular seals1061,1062through106n(e.g., O-rings) may be arranged about a segment of tie bolt102in correspondence with a radially-inward segment108of respective stub shaft102. InFIG.2, the number of illustrated annular seals is equal to 5 and so in this example n=5. It will be appreciated that the foregoing should be construed as one non-limiting example. It will be further appreciated that each respective neighboring seal pair of the plurality of axially spaced apart annular seals106defines sealing sides of a respective chamber109of a plurality of axially sequential chambers, such as chambers1091,1092, as seen inFIG.2, disposed between the process side and the atmospheric pressure side of the turbomachine. In the foregoing example, four axially sequential chambers would be defined by annular seals1061,1062through1065. For the sake of simplicity of illustration just two of such chambers are shown inFIGS.2-5. In the general case, the relationship that defines the number of chambers formed by an n number of annular seals is n−1. Accordingly, if the number of annular seals is 5, then the number of chambers is n−1=4. A plurality of conduits107, such as conduits1071,1072through107n-1(e.g., drilled or otherwise constructed through the tie bolt) extend from a radially-outward segment111of the respective stub shaft102through the stub shaft to communicate with the plurality of axially sequential chambers109disposed between the process side and the atmospheric side of the turbomachine. In the foregoing example, four conduits would communicate with the four chambers defined by annular seals1061,1062through1065. In one disclosed embodiment, the plurality of conduits107may alternate between a first conduit1071fluidly coupled at the radially-outward segment of the respective stub shaft102to receive a sealing fluid and a second conduit1072fluidly connected at the radially-outward segment of the respective stub shaft to a venting outlet. It will be appreciated that the source of the sealing fluid and the venting outlet may be obtained by way of a dry fluid seal system130, such as is commonly used in process gas centrifugal compressors. Without limitation, dry fluid seal system130may involve a tandem seal configuration involving stationary and rotatable sealing elements. As would be appreciated by one skilled in the art, dry fluid seal system130may be disposed about the radially-outward segment111of the respective stub shaft102and, as noted above, may be used as the source of the sealing fluid and may be further used to provide a venting mechanism to a flow that may comprise the incipient leakage of the process fluid. In one non-limiting embodiment, a plurality of impeller stages140(just one is illustrated inFIG.1) may be disposed between stub shafts1041and1042. The plurality of impeller stages being supported by tie bolt102using any affixing technique appropriate for a given application. In one non-limiting embodiment, respective joint structures150may be arranged to couple contiguous impeller stages to one another. In one non-limiting embodiment, the respective joint structures150may, without limitation, comprise joining/stacking rotating elements, such as Hirth joint structures, Gleason curvic joints, and piloted rabbet or spigot-fit joints, each of which, as would be appreciated by one skilled in the art may center parts and transmit load but may also leak gas through the joint area. In one non-limiting embodiment, a computerized leakage monitor160may be coupled to second conduit/s (e.g., venting conduits1072,1073, etc.) to monitor a presence of any incipient leakage of process fluid in any of such venting conduits. FIGS.2through5respectively illustrate zoomed-in views of a portion of the cross-sectional view shown inFIG.1that may be used for illustrating and describing certain non-limiting structural and/or operational relationships of features in the disclosed rotor structure. FIG.2illustrates an example where annular seals1061,1062and1063are intact. That is, no seal malfunction is present in any of the annular seals. In this case, no fluid flow would develop in conduits1071and1072. This is essentially a static condition. FIG.3. illustrates an example where annular seal1061is broken and annular seals1062and1063are intact. That is, a seal malfunction is present in annular seal1061. In this case, pressurized process fluid would pass through malfunctioning annular seal1061into chamber1091; pressurized sealing fluid would flow into chamber1091and this would be effective to inhibit further progress of the pressurized process fluid in chamber1091, provided the internal pressure of the sealing fluid is relatively larger compared to the internal pressure of the process fluid passing into chamber1091. FIG.4. illustrates an example where annular seal1062is broken and annular seals1061and1063are intact. That is, a seal malfunction is present in annular seal1062. In this case, sealing fluid would pass through malfunctioning annular seal1062and into chamber1092, effectively forming a fluid buffer zone overlapping chambers1091and1092with venting through conduit1072. FIG.5. illustrates an example where annular seals1061and1062are broken and annular seal1063is intact. That is, seal malfunctions are present in annular seals1061and1062. In this case, sealing fluid mixed with pressurized process fluid would pass through malfunctioning annular seal1062and this mixture would be vented through conduit1072. In this example, this mixture would not advance beyond chamber1092. In one non-limiting embodiment, the alternating chambers1091,1092through109n-1include at least one backup first chamber (e.g., the chamber connected to first conduit1074fluidly coupled to receive the sealing fluid) relative to the first chamber1091, which is disposed downstream of the backup chamber connected to first conduit1074. (The term downstream is indicative of the direction of process fluid flow between the pressurized process side and the atmospheric pressure side of the turbomachine). Similarly, the alternating chambers1091,1092through109n-1includes at least one backup second chamber (e.g., the chamber connected to second conduit1073fluidly coupled for venting) relative to a second chamber1092disposed downstream of the chamber connected to second conduit1073. It will be appreciated that the first chamber (e.g., chamber1091) and the backup first chamber (e.g., chamber1094) is each independently arranged to receive sealing fluid, and the second chamber (e.g., chamber1092) and the backup chamber (e.g., chamber1093) is each independently arranged to permit venting, such as discussed in the context of the foregoing examples. In operation, for example, when one or more annular seals malfunctions in a respective neighboring seal pair of the plurality of annular seals1061,1062through106n, and the malfunction of the one or more annular seals leads to incipient leakage of process fluid, a first fluid flow may be established through the first conduit/s (e.g., conduits1071,1074) to convey sealing fluid into the respective chamber in communication with the first conduit/s, and/or a second fluid flow is established through the second conduit/s (e.g., conduits1072,1073) to permit venting of the respective chamber in communication with the second conduit/s. In operation, disclosed embodiments make use of innovative venting/sealing arrangements effective for venting the tie bolt rotor so that, for example, an incipient leakage of the process fluid can be monitored. Additionally, in operation disclosed embodiments are effective to, for example, convey to the tie bolt rotor a pressurized sealing fluid effective for reducing the likelihood of process fluid escaping to the atmosphere. While embodiments of the present disclosure have been disclosed in exemplary forms, it will be apparent to those skilled in the art that many modifications, additions, and deletions can be made therein without departing from the scope of the invention and its equivalents, as set forth in the following claims. | 13,267 |
11859632 | DETAILED DESCRIPTION OF THE INVENTION The present invention can be understood more readily by reference to the following detailed description of the invention and the Examples included therein. Before the present compounds, compositions, articles, systems, devices, and/or methods are disclosed and described, it is to be understood that they are not limited to specific synthetic methods unless otherwise specified, or to particular reagents unless otherwise specified, as such may, of course, vary. It is also to be understood that the terminology used herein is for the purpose of describing particular aspects only and is not intended to be limiting. Although any methods and materials similar or equivalent to those described herein can be used in the practice or testing of the present invention, example methods and materials are now described. While aspects of the present invention can be described and claimed in a particular statutory class, such as the system statutory class, this is for convenience only and one of skill in the art will understand that each aspect of the present invention can be described and claimed in any statutory class. Unless otherwise expressly stated, it is in no way intended that any method or aspect set forth herein be construed as requiring that its steps be performed in a specific order. Accordingly, where a method claim does not specifically state in the claims or descriptions that the steps are to be limited to a specific order, it is no way intended that an order be inferred, in any respect. This holds for any possible non-express basis for interpretation, including matters of logic with respect to arrangement of steps or operational flow, plain meaning derived from grammatical organization or punctuation, or the number or type of aspects described in the specification. In the following descriptions, like reference characters designate like or corresponding parts throughout the several views and embodiments. Also, it is to be understood that such terms as “forward,” “rearward,” “left,” “right,” “upwardly,” “downwardly,” and the like are words of convenience and are not to be construed as limiting terms. Locations, shapes, sizes, materials, numbers, relative positions, angular positions, velocities of motion, ranges of motion, electrical tolerances, mechanical tolerances, and other such properties of the devices within the embodiments may be altered and are not to be construed as limiting factors. Nor should the components comprising an assembly be construed as the only suggested components within that assembly. Referring now to the drawings, it will be understood that the illustrations are for the purpose of describing embodiments of the invention and are not intended to limit the invention thereto. Now referring toFIG.1shows the boundary-layer pump1dispersing a spray. A boundary-layer pump1is a pump in which greater than 20% of the motive force acting upon the fluid is derived from friction between the fluid and a surface of the pump. The boundary-layer pump1of this invention is also a continuous-flow pump. A continuous-flow pump is any pump in which the fluid flow path from inlet port to outlet port is uninterrupted by any valve, vane, tooth, lobe, or other obstruction. Now referring toFIGS.2-3is a view of a first embodiment of the boundary-layer pump1. The view shows a pump body22. The pump body22is a stationary part of a boundary-layer pump1. In this embodiment, the pump body22is generally tapered in shape with the wider end proximal21to the input shaft46and the narrower end distal23to the input shaft46. The pump body22is configured to receive a rotor assembly24. In this embodiment, the rotor assembly24is shown as a screw rotor. The rotor assembly24includes a laminar fluid flow channel40. A laminar fluid flow channel40provides non-turbulent flow for a particular fluid by restricting the depth of the laminar fluid flow channel40, such that no portion of the fluid flow is outside of the boundary-layer. The laminar fluid flow channel40in the rotor assembly24is configured to enable flow toward the outlet port34while maintaining a Reynolds number (Re) which is preferably below 2000. This measure depends on the particular fluid viscosity and the RPM of the pump in addition to the channel depth. In practice, these practical considerations result in a channel with a width-to-depth ratio generally greater than 5:1. The laminar fluid flow channel40is of less than the maximum width and depth necessary to maintain the laminar flow of its intended fluid, which may include machine oils, petroleum, crude oils, paints, protective coatings, additives, dyes, glues, sealants, caulks, slurries, resins, soaps, polishes, syrups, vegetable oils, fruit and vegetable pastes, dairy products, medicines, cosmetics, and many others. The laminar channel40shown here has a tapered helix configuration. However, the laminar channel40can also have a helix, or spiral configuration. The length of the laminar fluid flow channel40determines the general head pressure capacity of the boundary-layer pump1. An increased pressure capacity is often a desirable advantage over other pumps and begins to manifest approximately when the laminar fluid flow channel40length is greater than 2× the radius of the rotor assembly24or greater than five times the square root of the channel's cross-sectional area. The rotor assembly24rotates by means of an input shaft46. The input shaft46is a central rotating member of boundary-layer pump1driven by a conventional motor (not shown). The input shaft46is sealed by a shaft seal29, a seal cap26, a bearing28and an adjustment cap30. The shaft seal29and seal cap26retains the fluid within the pump body22. The boundary-layer pump1includes an adjustable gap45between rotor assembly24and pump body22. The adjustment cap30includes a threaded outside diameter which mates with a threaded inside diameter of the pump body22. By screwing or unscrewing the cap, the gap45between the rotor assembly24and the opposing wall49of the pump body is made variable. The adjustment cap30and bearing28may retract from the rotor assembly24when fluid has high viscosity or additive particles. At least one primary inlet port32and an at least one primary outlet port34is provided in the pump body22. A spray nozzle44is connected to the distal end of the boundary-layer pump1. A spray nozzle44is a precision device that facilitates dispersion of liquid into a spray. The boundary-layer pump1further includes a number of ports for sensors. These sensors include: a low-pressure sensor60and low-pressure sensor port36, a high-pressure sensor58and high-pressure sensor port38, a thermocouple62and thermocouple port42, and a sensor port47for any sensor64of: temperature, RPM, flow rate, x-rays, ultra-violet, visible light, infrared, video inspection, viscosity, dielectric, or conductivity. Preferred materials of construction of the pump body22and rotor assembly24may include hardened stainless steel, hardened tool steel, nitronic, PTFE, or polymer-ceramic, although any suitable material may be used. Boundary-layer pump1operates by continuously drawing fluid into the at least one primary inlet port32, by the rotation of an input shaft46. The fluid is pumped by the rotor assembly24towards the outlet port34. A continuous-flow pump is a pump in which the fluid flow path48(FIG.7) from at least one primary inlet port32to at least one primary outlet port34is uninterrupted by any valve, vane, tooth, lobe, or other obstruction. The fluid occupies a laminar fluid flow channel40within the rotor that is sufficiently shallow as to maintain non-turbulent fluid flow and boundary layer effect. A boundary-layer pump1is any pump having at least one boundary-layer surface which imparts greater than 20% of the kinetic energy to a fluid by means of friction between the boundary-layer surface and the fluid. The laminar fluid flow channel40has a defined cross-sectional area and thus the rotational velocity of the rotor assembly24provides precise volume flow metering. Additionally, the placement of an absolute pressure sensor at the low-pressure port36and high-pressure port38along with a thermocouple at the thermocouple port42provides precision mass flow metering, in accordance with Bernoulli's Principle. The variable screw or spiral, while turning, is a pump that is also a precise flow meter. This precision is derived from the extended path length of the fluid against the rotor, which effectively couples the fluid to the rotor and prevents fluid slippage. The pulsation-free, laminar flow is highly uniform from one time interval to the next, even into the millisecond range. The differential pressure between the inlet and outlet ports, the known cross-sectional area of the laminar channel, and the known velocity of the media demonstrate Bernoulli's Principal for flow rate. Pressure ports may be located through the stator walls over the laminar channel. The pressure may be measured by an absolute pressure sensor in an ideal, low-turbulent region affording accuracy and precision of measurement. Further, a temperature sensor may allow for conversion of the volumetric flow information to mass flow information. Multiple orifice or nozzle types built onto or added to the outlet port of the pump may dispense the media in different flow or ‘spray’ patterns. Adjustment of RPM and of outlet orifices can establish the ideal flow and pressure combination for a particular application. The boundary-layer pump1can include a spring-loaded or ratcheting auto-tensioner50&52to compensate for surface wear. Now referring toFIG.4is a side view of a first embodiment of the boundary-layer pump1. The view includes a rotor assembly24, an adjustment cap30, thrust bearing28, seal cap26, and a laminar fluid flow channel40. This laminar fluid flow channel40in the rotor assembly24enables flow toward a nozzle44while providing smooth fluid alignment. Any spray nozzle44for a particular application can be attached to the boundary-layer pump1. Now referring toFIGS.5-7, a second embodiment of the boundary-layer pump1is shown. In this embodiment, a rotor assembly24is made of a plurality of rotor discs25on a common shaft-type rotor27. Each of the rotor discs25is alternately positioned between a corresponding plurality of stator discs23, with the stator discs23rendered incapable of rotation by their coupling to a pump body22. In this exemplary embodiment, each rotor disc has at least one laminar fluid flow channel40arranged in the general form of an Archimedean spiral. The plurality of rotor discs25are organized in a stack. The stack is a coaxial alternating arrangement of rotor discs25and stator discs23, which when arranged in parallel flow does increase the effective cross-sectional area of laminar fluid flow channel40, and when arranged in series increases the effective length of laminar fluid flow channel40, without sacrificing the boundary layer effects on the fluid. On each end of the rotor27is a bearing28and shaft seal29, which allow free rotation of the rotor assembly24and prevent fluid from leaking out of the boundary-layer pump1, respectively. In an adjustment cap30, an at least one primary inlet port32and an at least one outlet port34, provides the primary ingress and egress of fluid to the boundary-layer pump1. Fluid flow is communicated from the at least one primary inlet port32through the laminar fluid flow channel40before recombining and exiting through the outlet port34. In this embodiment, the laminar fluid flow channel40comprises at least one secondary inlet port33positioned on each of the rotor discs25, said at least one secondary inlet port33configured to allow fluid communication to the plurality of rotor discs25. An at least one secondary outlet port35is positioned on each of the stator discs23configured to allow fluid communication to the at least one primary outlet port34. More specifically, the rotor discs25comprise a set of at least one axial secondary inlet port33that allows fluid communication to a plurality of rotor discs25, with all rotor discs25producing flow in parallel through at least one laminar fluid flow channel40. The flows exit each disc of the plurality of rotor discs25at the periphery and may combine to pass through at least one secondary outlet port35. In this embodiment, the fluid flow is communicated from the at least one primary inlet port32through the secondary inlet ports33of each rotor disc25, and in parallel through the laminar fluid flow channel40of each rotor disc35, before recombining and exiting through the secondary outlet port35and at least one primary outlet port34. Now referring toFIG.8is a front schematic view of a rotor disc25illustrating absolute and differential pressures. For an example, absolute pressure of 200 psi, fluid increases from 0 psi in a substantially linear fashion throughout the length of the channel. A pressure differential develops between subsequent turns of the laminar fluid flow channel40, and the channel face seal54of the rotor must endure this delta pressure56. Boundary-layer pump1operates by continuously drawing fluid into the at least one primary inlet port32by the rotation of an input shaft46. The fluid is pumped by the rotor assembly24towards the outlet port34. A continuous-flow pump is a pump in which the fluid flow path48(FIG.7) from at least one primary inlet port32to outlet port34is uninterrupted by any valve, vane, tooth, lobe, or other obstruction. The fluid occupies a laminar fluid flow channel40within the rotor that is sufficiently shallow as to maintain non-turbulent fluid flow and boundary-layer effect. A boundary-layer pump is any pump having at least one boundary-layer surface which imparts greater than 20% of the kinetic energy to a fluid by means of friction between the boundary-layer surface and the fluid. An adjustment cap30and bearing28may retract from the rotor when fluid has high viscosity or additive particles. A shaft seal29or seal cap26retains the fluid within the pump body22. The at least two embodiments of the present invention provide a unique, variable, laminar-channel rotor nesting in a stator that can be tightened or loosened from the stator, changing the effective cross-sectional area of the channel interface. The pump maintains low Reynold's numbers in the rotor channel thus also being a precision fluid volume and mass flow meter that is comparably simple to manufacture. Materials being pumped are not damaged by pumping action. Many other variations are possible. For example: although the embodiments illustrate particular geometries of the outlet port and associated spray nozzle, any configuration of outlets or spray nozzles can be used. The inlet or outlet may include a check valve or other valve type. Although the embodiments illustrate particular geometries for helical or spiraling laminar channels, any number, shape, proportion, or cross-sectional area may be used, providing laminar or non-laminar flow. Although the embodiments illustrate a laminar channel upon a rotor, the laminar channel may alternately or additionally be upon the stator. Although the embodiments illustrate particular geometries of adjustment cap, the variable channel cross-sectional area adjustment can be performed by any other means, such as a channel shim or channel spring. The adjustment feature may include a spring-loaded or ratcheting auto-tensioner to compensate for wear. The adjustment feature may be removed altogether and the gap distance may be fixed. Although the embodiments suggest rotor and stator materials of hardened stainless steel, any suitable material, including but not limited to tool steel, other metals, ceramic, glass, plastic, synthetic, or composite, may be used. Materials such as Nitrolic, PTFE, carbon fiber, Kevlar, and polymer-ceramic composite are of particular interest. Soft-sealing materials such as rubber, neoprene, silicone, and the like may be used at any sealing surface. Although the embodiments show thrust bearings and ball bearings on the rotor, other types of bearing may be used, including but not limited to bushings, journal bearings, tapered roller bearings, pressurized bushings, gas bearings, and magnetic suspension bearings. Although an embodiment shows a stack of rotor discs operating in parallel, they may be arranged to operate in series. Although the embodiments show a spiral channel upon a conical and disc rotor respectively, the channel may be upon a rotor of any shape, including but not limited to cylindrical, spherical, hyperbolic, or organic. Although the embodiments show rotors of substantially unitary construction, the rotors may include at least one clutch, allowing a variable number of rotor discs or segments to engage at a time. Although the embodiments show rotors within a single housing, the rotors may be contained within two or more housings, and upon a common drive shaft, such that they may pump a two-part resin or other formulaic mixture of fluids. Although the embodiments show accommodations for pressure sensors and thermocouples, these accommodations may be extended to include any variety of sensor, including but not limited to RPM, flow rate, x-rays, ultra-violet, visible light, infrared, video inspection, viscosity, dielectric, conductivity, and others. While the invention has been described with reference to details of the illustrated embodiments, these details are not intended to limit the scope of the invention as defined in the appended claims. The embodiment of the invention in which exclusive property or privilege is claimed is defined as follows. | 17,668 |
11859633 | DETAILED DESCRIPTION OF THE EMBODIMENTS More detailed descriptions of the specific embodiments of the disclosure are provided below with reference to the accompanying drawings. The features and advantages of the disclosure are described more clearly according to the following description and claims. It should be noted that all of the drawings use very simplified forms and imprecise proportions, only being used for assisting in conveniently and clearly explaining the objective of the embodiments of the disclosure. FIG.1is a schematic perspective view of an embodiment of a centrifugal fan according to the disclosure. A centrifugal fan10is applicable to an electronic device such as a notebook computer, a desktop computer, or a mainboard, to improve heat dissipation efficiency of the electronic device. As shown in the figure, the centrifugal fan10includes a case11, a shaft12, and a plurality of blades14. The case11includes an air inlet112and an air outlet114. The blades14are arranged around the shaft12, and form a fan blade module as a whole. FIG.2is a schematic top view of an embodiment of the fan blade module inFIG.1, andFIG.3is a schematic cross-sectional view corresponding to a cross section A-A inFIG.2. The cross section A-A inFIG.3is a cross section in a circumferential direction B1of the fan blade module and at a position located at a preset distance d from an axial center of the shaft12. The blade14includes a non-air guiding portion142and an air guiding portion144. The air guiding portion144is connected to the non-air guiding portion142, and is located on a side of the non-air guiding portion142facing the air inlet112, that is, an upper side in the figure. In an embodiment, the blade14includes the air guiding portion144in a range corresponding to the air inlet112, to guide airflow from the air inlet112. Arrows in the figure show an airflow direction D1of the airflow from the air inlet112. The non-air guiding portion142includes a first straight line L1and a second straight line L2along the cross section in the circumferential direction B1. The air guiding portion144includes a first curve C1and a second curve C2along the cross section in the circumferential direction B1. The first curve C1and the first straight line L1are located on a leeward side of the blade14. The second curve C2and the second straight line L2are located on a windward side of the blade14. The first straight line L1is parallel to the second straight line L2, to form the non-air guiding portion142having a fixed thickness. The first straight line L1is connected to the first curve C1and tangent to the first curve C1. The second straight line L2is connected to the second curve C2. However, the second curve C2is different from the first curve C1. In an embodiment, a curvature radius of the second curve C2is greater than a curvature radius of the first curve C1. A cross section of the air guiding portion144presents, as a whole, a structure in which a central part is thick and two ends are thin. An air inflow channel16is formed between two adjacent air guiding portions144. The air inflow channel16is defined by a first curve C1of an air guiding portion14and a second curve C2of an adjacent air guiding portion14. The air inflow channel16is expanded in the airflow direction D1according to an expanding ratio. That is, the air inflow channel16is expanded in a direction away from the air inlet112. The air inflow channel16is expanded in the above manner to avoid or slow down a drastic change of airflow filling the space, and to achieve the purpose of reducing or eliminating a vortex phenomenon. A design process of the blade14in the disclosure is described in more detail in the subsequent paragraphs corresponding toFIG.4AtoFIG.4D. In an embodiment, the air guiding portion144includes a front edge144aand a rear edge144b. The front edge144ais an end of the air guiding portion144facing the air inlet112, and the rear edge144bis an end of the air guiding portion144connected to the non-air guiding portion142. A thickness of the front edge144ais less than a thickness of the rear edge144b, to ensure that the entire blade14has enough strength. FIG.4AtoFIG.4Dshow a design process of blades in the disclosure based on a specified first curve. First, as shown inFIG.4A, one first curve C1of the blade14is provided, and a third curve C3of an adjacent blade14ais constructed using the first curve C1. The first curve C1is a basic line type for blade design. The first curve C1and the third curve C3are curves located on leeward sides of the blades14and14a. Next, as shown inFIG.4B, a thickness t1of the non-air guiding portion142is specified. By using a starting point P0of the first curve C1and the thickness t1of the non-air guiding portion142, a starting point S0of the second curve C2and an exit width W0of the air inflow channel16are obtained. The starting point P0of the first curve C1is a connecting point at which the first curve C1and the non-air guiding portion142are connected. The starting point S0of the second curve C2is a connecting point at which the second curve C2and the non-air guiding portion142are connected. A starting point Q0of the third curve C3is a connecting point at which the third curve C3and the non-air guiding portion142aare connected. The exit width W0is a width of the air inflow channel16at a position close to the non-air guiding portion142. Subsequently, as shown inFIG.4C, a thickness t2of the front edge144aof the air guiding portion144is specified. A terminal point Sn of the second curve C2is constructed using a terminal point Pn of the first curve C1. By using the terminal point Sn of the second curve C2and the third curve C3, an entrance width Wn of the air inflow channel16and a closest point Qn on the third curve C3closest to the terminal point Sn of the second curve C2are obtained. Next, as shown inFIG.4D, between the starting point Q0of the third curve C3and the foregoing closest point Qn, a plurality of nodes Q1, . . . , Qn−1 are defined along the third curve C3. Since the exit width W0and the entrance width Wn of the air inflow channel16are known, width values W1, . . . , Wn−1 corresponding to the respective nodes Q1, . . . , Qn−1 are calculated by using a linear interpolation method. Subsequently, nodes S1, . . . , Sn−1 on the second curve C2are constructed by using positions of the nodes Q1, . . . , Qn−1 on the third curve C3and the corresponding width values W1, . . . , Wn−1. In an embodiment, an expansion is performed from the nodes Q1, . . . , Qn−1 on the third curve C3in a normal direction of the third curve respectively by distances corresponding to the width values W1, . . . , Wn−1, to obtain the nodes S1, . . . , Sn−1. These nodes S1, . . . , Sn−1 construct a line type of the second curve C2. A complete blade14is constructed by combining a line type of the first curve C1and the line type of the second curve C2with the non-air guiding portion142having a known thickness. FIG.5is a chart showing a linear interpolation method used inFIG.4D. A horizontal axis in the chart indicates distances from the starting point Q0of the third curve C3to the nodes Q1, . . . , Qn−1 between the starting point Q0and the closest point Qn. A vertical axis of the chart indicates the width values W1, . . . , Wn−1. A point Bn corresponds to the closest point Qn of the third curve C3, and a width value at the point Bn is the entrance width Wn. A point B0corresponds to the starting point Q0of the third curve C3, and a width value at the point B0is the exit width W0. The width values corresponding to the respective nodes Q1, . . . , Qn−1 are obtained by a linear interpolation method using a connecting line between the point Bn and the point B0. A slope of the connecting line is the expanding ratio of the air inflow channel16. FIG.6is a schematic cross-sectional view of blades of a centrifugal fan in a circumferential direction, showing another embodiment of the centrifugal fan according to the disclosure. Compared with the case in the embodiment shown inFIG.3, an air inlet of the centrifugal fan according to the embodiment is located on a lower side in the figure. A blade24includes a non-air guiding portion242and an air guiding portion244. The air guiding portion244is connected to the non-air guiding portion242, and is located below the non-air guiding portion242. FIG.7is a schematic cross-sectional view of blades of a centrifugal fan in a circumferential direction, showing still another embodiment of the centrifugal fan according to the disclosure. Compared with the case in the embodiment shown inFIG.3, a blade34of the centrifugal fan according to the embodiment includes one non-air guiding portion342and two air guiding portions344aand344b. The two air guiding portions344aand344bare respectively located above and below the non-air guiding portion342. The blade34is applicable to both an application environment in which the air inlet is located on the upper side and an application environment in which the air inlet is located on the lower side. In an embodiment, the air guiding portions344aand344bof the blade34adopt a roughly the same but inverted line type, and are constructed in accordance with the method described in the foregoingFIG.4AtoFIG.4D. The air guiding portions344aand344bare symmetric with respect to a rotational surface of the blade34. The blade34presents a structure concave towards a right side (that is, a moving direction of the blade). However, the foregoing embodiments are not limited thereto. In other embodiments, according to the actual requirements, the air guiding portions344aand344balso adopt different line types for blade design. Through the centrifugal fan10provided in the disclosure, the blades14,24, and34of the centrifugal fan respectively include the air guiding portions144,244, and344aand344bon sides of the blades facing the air inlet112, and the air inflow channel16between the adjacent air guiding portions144is evenly expanded in the direction away from the air inlet112. In this way, the airflow phenomenon at the air inflow channel16is effectively mitigated, to enhance the performance of the fan and reduce airflow noise. The above is merely exemplary embodiments of the disclosure, and does not constitute any limitation on the disclosure. Any form of equivalent replacements or modifications to the technical means and technical content disclosed in the disclosure made by a person skilled in the art without departing from the scope of the technical means of the disclosure still fall within the content of the technical means of the disclosure and the protection scope of the disclosure. | 10,680 |
11859634 | DETAILED DESCRIPTION The implementations described herein relate to an electric motor assembly for moving air in refrigeration equipment and other applications. The electric motor assembly includes an electric motor, a fan assembly coupled to the electric motor and configured to rotate therewith about an axis, and a shroud coupled to the electric motor and extending about the fan assembly. The shroud includes a central hub coupled to the electric motor, an inlet ring, and a plurality of arms extending between the central hub and the inlet ring. Each arm of the plurality of arms includes a curved radial portion extending from the central hub and a planar axial portion extending from the radial portion to the inlet ring. The fan assembly includes a hub including a cylindrical portion and an inlet surface coupled to an inlet end of the cylindrical portion. The fan assembly also includes a plurality of blades coupled to an outer periphery of the cylindrical portion, wherein the inlet surface is tapered to direct an inlet airflow toward the plurality of blades. An outlet end of the hub includes a core ring, a first inner ring circumscribing the core ring, and a first plurality of circumferentially-spaced ribs extending between the core ring and the first inner ring. The hub also includes a second inner ring circumscribing the first inner ring and a second plurality of circumferentially-spaced ribs extending between the first inner ring and the second inner ring. The electric motor assembly described herein delivers an increased airflow at a higher efficiency with a lower noise level than other known air moving assemblies. The shroud arms are curved and swept in the direction of the airflow to allow the air to more easily pass through to reduce turbulence and improve efficiency. Also, the shroud arms are spaced to reduce blade tones. Similarly, the hub inlet surface is tapered to guide the incoming airflow into the blades at a predetermined angle to increase the amount of air flowing through the fan assembly. Additionally, the hub includes pluralities or ribs and rings that provide structural support to the fan assembly to maintain the fan assembly in position on the rotor and prevent vibrations to result in a reduced noise level. Moreover, the fan assembly is easily replaceable. Furthermore, the electric motor assembly described herein occupies a smaller volume than other known air moving assemblies and therefore allows a user to utilize smaller refrigeration equipment to take up less floor space. Additionally, the smaller size of the electric motor assembly described herein provides additional space within the refrigeration equipment to place products for sale. FIG.1is a perspective view of an exemplary electric motor assembly100illustrating a shroud102, an electric motor104, and a fan assembly106.FIG.2is a partially exploded view of electric motor assembly100illustrating a rotor assembly105of electric motor104.FIG.3is a cross-sectional view of electric motor assembly100.FIG.4is an enlarged view of a portion of the cross-sectional view shown inFIG.3. In the exemplary embodiment, shroud102is fixedly coupled to electric motor104and fan assembly106is rotatably coupled to electric motor104such that operation of electric motor104causes fan assembly106to rotate about a rotational axis108. Fan assembly106includes a hub110having a cylindrical portion112and an inlet surface114coupled to cylindrical portion112. Additionally, fan assembly106includes a plurality of circumferentially-spaced blades116coupled to and extending from an outer periphery118of cylindrical portion112. In the exemplary embodiment, shroud102includes a central hub120, a plurality of arms122, and an inlet ring124. Arms122extend from central hub120to inlet ring124and are substantially s-shaped. That is, each arm122includes two curves as arm122extends radially away from central hub120. More specifically, each arm122includes a radial portion126extending from central hub120and an axial portion128extending from radial portion126to inlet ring124. As best shown inFIG.3, electric motor assembly100includes an inlet130defined by inlet ring124and an outlet132proximate radial portion126or arms122. In operation, as fan assembly106rotates about axis108, air is drawn into inlet130and is channeled through inlet ring124between blades116, passed motor104, and discharged at outlet132. In the exemplary embodiment, inlet ring124includes an inlet end134and an opposing outlet end136that define an axial ring height Hr therebetween. Similarly, each blade116includes a leading edge138proximate inlet130and an opposing trailing edge140that define an axial blade height Hb therebetween. As shown inFIG.3, trailing edge140of blades116is axially spaced from outlet end136of inlet ring124. Specifically, blades116and inlet ring124are positioned to expose a predetermined amount of blade height Hb. In one embodiment, for example when fan assembly106includes a diameter of 8 inches, between approximately 17% and approximately 25% of blade height Hb is positioned axially between inlet ring outlet end136and a point along blade trailing edge140where blade height Hb is at a maximum. That is, the axial distance between an axial plane aligned with inlet ring outlet end136and the point along blade trailing edge140where blade height Hb is at a maximum defines an exposed blade height He (shown inFIG.4) that is between approximately 17% and approximately 25% of blade height Hb. More specifically, the exposed blade height He is approximately 22% the distance of blade height Hb. In another embodiment, for example when fan assembly106includes a diameter of 7 inches, the axial distance between an axial plane aligned with inlet ring outlet end136and the point along blade trailing edge140where blade height Hb is at a maximum defines an exposed blade height He (shown inFIG.4) that is between approximately 28% and approximately 34% of blade height Hb. More specifically, in such an embodiment, the exposed blade height He is approximately 31% the distance of blade height Hb. Positioning trailing edge140axially offset from outlet end136reduces tones that may be produced by blades116and also reduces the stall point of the airflow through the blades. In the exemplary embodiment, as best shown inFIG.4, inlet ring124includes an axial portion142, a radial portion144, and a transition portion146extending between axial portion142and radial portion144. As shown inFIG.4, axial portion142may be obliquely oriented with respect to axis108such that a diameter of inlet ring124narrows from inlet end134to outlet end136. Alternatively, axial portion142is oriented parallel to axis108such that the diameter of inlet ring124is constant between ends134and136. Furthermore, leading edge138of blades116is positioned entirely within axial portion142of inlet ring124such that leading edge138overlap only axial portion142and do not extend into transition portion146. Such a configuration reduces noise generated by electric motor assembly100and also reduces the blade tones. In the exemplary embodiment, transition portion146is designed to increase the surface area of inlet ring124that interacts with the airflow being channeled therethrough to increase the flow rate. Transition portion146is defined by the curved inlet surface147of inlet ring124at inlet130and defines a non-symmetrical fillet design. Specifically, inlet surface147is defined between a first transition point149and a second transition point151. Transition point149represents the transition between axial portion142and transition portion146. Similarly, transition point151represents the transition between radial portion144and transition portion146. In the exemplary embodiment, inlet surface147extends a first distance D1in the radial direction between transition points149and151, as shown inFIG.4. Similarly, inlet surface147extends a second distance D2in the axial direction between transition points149and151, as shown inFIG.4. In the exemplary embodiment, radial distance D1is greater than axial distance D2. More specifically, radial distance D1is approximately 1.5 times the length of radial distance D2. Furthermore, as shown inFIG.4, inlet surface147extends from transition point149in an oblique direction at an angle ε, and inlet surface147extends from transition point151in an oblique direction at an angle δ that is smaller than angle ε. Specifically, angle ε is between approximately 25 degrees and approximately 35 degrees. More specifically, angle ε is approximately 30 degrees. Similarly, angle δ is between approximately 10 degrees and approximately 20 degrees. More specifically, angle δ is approximately 15 degrees. As such, inlet surface147is a continuously curved spline line between transition points149and151. FIG.5is a top view of electric motor assembly100illustrating the array of arms122of shroud102. In the exemplary embodiment, radial portion126of arms122is substantially S-shaped and includes a plurality of curves, while axial portion128is substantially linear. Furthermore, radial portion126includes a first, inner end148coupled to central hub120and an opposing second, outer end150coupled to axial portion128. In the exemplary embodiment, radial portion includes a radially inner first curved portion152extending from central hub120and a radially outer second curved portion154extending between first curved portion152and axial portion128. Specifically, first curved portion152includes a radius of between approximately 4.0 inches and approximately 4.5 inches. More specifically, first curved portion152includes a radius of approximately 4.2 inches. Similarly, second curved portion154includes a radius of between approximately 6.6 inches and approximately 7.0 inches. More specifically, second curved portion154includes a radius of approximately 6.7 inches. Furthermore, as shown inFIG.5, radial portion126defines a sweep angle α of between approximately 10 degrees and approximately 15 degrees. More specifically, in the exemplary embodiment, radial portion126defines a sweep angle α of approximately 12 degrees. As used herein, the term “sweep angle” is meant to describe the portion of the circumference of a circle taken up between a radial line connecting the axis108and inlet end148of radial portion126and a radial line connecting axis108and outlet end150of radial portion126. The configuration resulting from the combination of curved portions152and154and the sweep angle α increases the structural integrity of shroud102and also facilitates smoothing the airflow past arms122to reduce airflow turbulence and, therefore, the noise level of electric motor assembly100. Additionally, arms122are spaced about central hub120such that as one blade116begins to pass under one arm122, an immediately adjacent blade116is clearing an immediately adjacent arm122. Specifically, each blade116includes a root156that extends from hub periphery118and a tip158at the distal end of blade116. When the leading edge138at the tip158of one blade116begins to overlap one arm122, the trailing edge140at the tip158of an immediately adjacent blade116is ending its overlap with an immediately adjacent arm122. Such a configuration further reduces overall noise and blade tones. FIG.6is a top view of fan assembly106illustrating hub110and plurality of blades116.FIG.7is a side view of fan assembly106.FIG.8is an enlarged view of a portion of fan assembly100shown inFIG.7. In the exemplary embodiment, hub110includes cylindrical portion112having an inlet end160and an outlet end162. Furthermore, hub110includes inlet surface114coupled to inlet end160. As shown inFIGS.6-8, inlet surface114is tapered to direct airflow toward leading edges138of blades116. Such a configuration reduces the noise level and increases the airflow volume through fan assembly106for improved efficiency. In the exemplary embodiment, fan assembly106also includes a hub cap164configured for insertion into a cap cavity166defined in inlet surface114. Cavity166includes a central opening168having a planar portion170. A threaded fastener (not shown), such as a bolt, is configured to be inserted through central opening168and a corresponding faster, such as a nut, is inserted into cavity166to secure fan assembly106to a rotor assembly172of electric motor104. Hub cap164is inserted into cavity166to both secure the nut in place and also to eliminate turbulent airflow by providing a smooth transition to inlet surface114. Hub cap164includes a planar surface (not shown) that aligns with planar portion170of central opening168to secure hub cap164to hub110. Such a configuration prevents undesired removal of hub cap164from hub110and still allows hub cap164to be removed for replacement of fan assembly106. In the exemplary embodiment, inlet surface114includes a first portion174extending obliquely from inlet end of cylindrical portion112and a second portion176extending obliquely from first portion174. As shown inFIGS.6-8, first surface174circumscribes second portion176. As best shown inFIG.8, first portion174is oriented at a first angle θ with respect to a plane178perpendicular to axis108. Similarly, second portion176is oriented at a second angle β with respect to plane178. In the exemplary embodiment, first angle θ is greater than second angle β. Specifically, first angle θ of first portion174is oriented between approximately 5 degrees and approximately 10 degrees with respect to plane178. More specifically, first angle θ of first portion174is oriented approximately 7 degrees with respect to plane178. Similarly, second angle β of second portion176is oriented between approximately 2 degrees and approximately 5 degrees with respect to plane178. More specifically, second angle β of second portion176is oriented approximately 3 degrees with respect to plane178. Such a configuration provides for a smooth transition of airflow across inlet surface114and into blades116. FIG.9is a bottom view of outlet end162of hub110.FIG.10is a perspective view outlet end162.FIG.11is a cross-sectional view of the fan assembly shown inFIG.1nthe exemplary embodiment, hub110includes a core ring180, a first inner ring182circumscribing core ring180, and a first plurality of circumferentially-spaced ribs184extending radially between core ring180and first inner ring182. Additionally, hub110includes a second inner ring186circumscribing first inner ring182and a second plurality of circumferentially-spaced ribs188extending between first inner ring182and second inner ring186. As such, second plurality of ribs188are positioned radially outward of first plurality of ribs184. In the exemplary embodiment, the quantity of ribs in first plurality of ribs184is equal to the quantity of ribs in second plurality of ribs188. Furthermore, the quantity of blades116of fan assembly106is equal to the quantity of rib in both first and second pluralities184and188. More specifically, in one embodiment, each rib188is radially aligned with a circumferential midpoint of a corresponding blade along outer periphery118. As best shown inFIG.9, first plurality of ribs184define a first radial length L1, and second plurality of ribs188define a second radial length L2that is longer than the first radial length L1. Specifically, the second radial length L2is at least twice as long as first radial length L1. Furthermore, first plurality of ribs184is circumferentially offset from second plurality of ribs188. Specifically, each rib of first plurality of ribs184is connected to first inner ring182approximately midway between adjacent ribs of second plurality of ribs188. In operation, pluralities of ribs184and188provide structural reinforcement to maintain fan assembly106parallel to rotor assembly172by distributing loads from the shaft (not shown) of electric motor104evenly among blades116. In the exemplary embodiment, second plurality of ribs188are deformable to facilitate balancing fan assembly106. That is, a portion of at least one rib188can be removed from to balance fan assembly106and maintain its position parallel to rotor assembly172. In one embodiment, material can be removed from at least one rib188by carving blade188with a tool. In another embodiment, each rib188includes score marks that removal or predetermined portions of rib188as needed to balance fan assembly106. As such, material is removed from fan assembly106to facilitate balancing rather than adding weights or other counterbalancing devices that may not be available. As shown inFIGS.8and9, first inner ring182includes at least one alignment device190extending axially therefrom. Specifically, first inner ring182includes a plurality of alignment devices190equally spaced about first inner ring182and configured to mate with a respective one of a plurality of alignment openings192(shown inFIG.2) on rotor assembly172. Alignment devices190engage alignment openings192to facilitate attaching fan assembly106to motor104and to distribute rotational loads from rotor assembly172. In the exemplary embodiment, hub110also includes an outer ring194that circumscribes second inner ring186to define a radial gap196therebetween. Gap194forms a continuous circle around second inner ring186and is configured to receive at least one balancing weight for balancing fan assembly106. By either removing material from second plurality of ribs188or adding a weight to gap196, or both, the balance of fan assembly106can be adjusted without adding weights to blades116or outer periphery118of hub110to maintain a clean visual appearance of fan assembly106. Outer ring194forms a portion of cylindrical portion112and outer periphery118of hub110. Specifically, outer ring194includes an axial height H1that is equal to the axial length of cylindrical portion112. Additionally, as shown inFIG.11, second inner ring186includes an axial height H2that is less than axial height H1of outer ring194. Furthermore, as shown inFIG.11, outer ring194includes a first radial thickness T1, and second inner ring186includes a second radial thickness T2that is substantially similar to first radial thickness T1. FIG.12is a top view of blade116of fan assembly106. In the exemplary embodiment, blade112is defined by leading edge138, trailing edge140, inner profile198extending between edges138and140at root156, and outer profile200extending between edges138and140at tip140. As shown inFIG.12, inner profile198is defined by a curve having a radius R1, and outer profile200is defined by a curve having a radius R2that is larger than radius R1. Specifically, radius R2of outer profile200is approximately twice as large as radius R1of inner profile198. More specifically, radius R1of inner profile198is between approximately 40 millimeters (mm) and approximately 60 mm. Even more specifically, radius R1of inner profile198is approximately 50 mm. Similarly, radius R2of outer profile200is between approximately 90 mm and approximately 110 mm. Even more specifically, radius R2of outer profile200is approximately 100 mm. Furthermore, in the exemplary embodiment, inner profile198defines a sweep angle γ of between approximately 18 degrees and approximately 24 degrees along root156between edges138and140. More specifically, inner profile198defines a sweep angle γ of approximately 21 degrees. Similarly, outer profile200defines a sweep angle λ of between approximately 28 degrees and approximately 32 degrees along tip158between edges138and140. More specifically, outer profile200defines a sweep angle λ of approximately 30 degrees. As such, the sweep angle λ of outer profile200is greater than sweep angle γ of inner profile198. Overall, blade116defines a sweep angle σ of between approximately 30 degrees and approximately 35 degrees from tip158of leading edge138to root156of trailing edge140. More specifically, blade116defines a sweep angle σ of approximately 33 degrees from tip158of leading edge138to root156of trailing edge140. As used herein, sweep angle is meant to describe the portion of the circumference of a circle taken up between radial lines connected at axis108. In the exemplary embodiment, trailing edge140is substantially planar between inner profile198and outer profile200. Leading edge138includes a radius R3of between approximately 165 mm and approximately 175 mm between inner profile198and outer profile200. More specifically, leading edge138includes a radius R3of approximately 170 mm between inner profile198and outer profile200. Additionally, in the exemplary embodiment, blade116includes a pressure side, a suction side, and a blade thickness defined therebetween. The blade thickness varies between leading edge138and trailing edge140such that the blade thickness is greatest approximately one third the distance from leading edge138to trailing edge140. Furthermore, each blade116may include at least one are of surface roughness to retain the airflow on blade and improve efficiency. Specifically, the pressure side of blade116may have one surface roughness, and the suction side of blade116may include a different surface roughness. Additionally, the surface roughness may vary between root156and tip158on the same side of blade116. Surface roughness can include either protrusions extending upward from blade116, or may include dimples that are formed in the surface of blade116. The implementations described herein relate to an electric motor assembly for moving air in refrigeration equipment and other applications. The electric motor assembly includes an electric motor, a fan assembly coupled to the electric motor and configured to rotate therewith about an axis, and a shroud coupled to the electric motor and extending about the fan assembly. The shroud includes a central hub coupled to the electric motor, an inlet ring, and a plurality of arms extending between the central hub and the inlet ring. Each arm of the plurality of arms includes a curved radial portion extending from the central hub and a planar axial portion extending from the radial portion to the inlet ring. The fan assembly includes a hub including a cylindrical portion and an inlet surface coupled to an inlet end of the cylindrical portion. The fan assembly also includes a plurality of blades coupled to an outer periphery of the cylindrical portion, wherein the inlet surface is tapered to direct an inlet airflow toward the plurality of blades. An outlet end of the hub includes a core ring, a first inner ring circumscribing the core ring, and a first plurality of circumferentially-spaced ribs extending between the core ring and the first inner ring. The hub also includes a second inner ring circumscribing the first inner ring and a second plurality of circumferentially-spaced ribs extending between the first inner ring and the second inner ring. The electric motor assembly described herein delivers an increased airflow at a higher efficiency with a lower noise level than other known air moving assemblies. The shroud arms are curved and swept in the direction of the airflow to allow the air to more easily pass through to reduce turbulence and improve efficiency. Also, the shroud arms are spaced to reduce blade tones. Similarly, the hub inlet surface is tapered to guide the incoming airflow into the blades at a predetermined angle to increase the amount of air flowing through the fan assembly. Additionally, the hub includes pluralities or ribs and rings that provide structural support to the fan assembly to maintain the fan assembly in position on the rotor and prevent vibrations to result in a reduced noise level. Moreover, the fan assembly is easily replaceable. Furthermore, the electric motor assembly described herein occupies a smaller volume than other known air moving assemblies and therefore allows a user to utilize smaller refrigeration equipment to take up less floor space. Additionally, the smaller size of the electric motor assembly described herein provides additional space within the refrigeration equipment to place products for sale. This written description uses examples to disclose various implementations, including the best mode, and also to enable any person skilled in the art to practice the various implementations, including making and using any devices or systems and performing any incorporated methods. The patentable scope of the disclosure is defined by the claims, and may include other examples that occur to those skilled in the art. Such other examples are intended to be within the scope of the claims if they have structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal language of the claims. | 24,697 |
11859635 | DETAILED DESCRIPTION Embodiments will be described below. [General Configuration of Axial-Flow Fan] FIG.1is a view illustrating an axial-flow fan according to the present disclosure as seen from a first side in a rotation axis direction.FIG.2is a view illustrating the axial-flow fan according to the present disclosure as seen from a second side in the rotation axis direction.FIG.3is a view illustrating the axial-flow fan according to the present disclosure as seen in a direction orthogonal to the rotation axis direction. An axial-flow fan11is driven by a fan motor (not illustrated) to rotate about a center axis C. Accordingly, the center axis C of the axial-flow fan11corresponds to an axis of rotation of the axial-flow fan11. In this specification, therefore, reference sign C also denotes the axis of rotation of the axial-flow fan11, in addition to the center axis of the axial-flow fan11. In this specification, the term “rotation axis direction” as used herein refers to a direction along which the center axis C of the axial-flow fan11extends and a direction parallel to this direction. The term “radial direction” as used herein refers to a direction orthogonal to the center axis C of the axial-flow fan11. The term “circumferential direction” as used herein refers to a direction around the center axis C of the axial-flow fan11. As illustrated inFIGS.1to3, the axial-flow fan11is a propeller fan. The axial-flow fan11is made of, for example, a synthetic resin material such as an acrylonitrile-styrene (AS) copolymer, or a synthetic resin material reinforced with glass fiber. The axial-flow fan11includes a hub12and a plurality of blades13. The plurality of blades13are disposed on an outer peripheral surface of the hub12, and are spaced apart from each other in the circumferential direction. The axial-flow fan11according to one or more embodiments includes three blades13. The hub12and the blades13are integrally formed with a synthetic resin material. It should be noted that the material for the axial-flow fan11is not limited to the foregoing synthetic resin and is changeable as appropriate. As illustrated inFIG.1, the axial-flow fan11rotates counterclockwise (i.e., in a direction indicated by an arrow A) as seen from the first side in the rotation axis direction. In this specification, a front side and a rear side in a rotational direction are defined with respect to a rotational direction of the axial-flow fan11. [Configuration of Blade] As illustrated inFIGS.1to3, each blade13has a plate shape and includes an inner peripheral edge portion31, an outer peripheral edge portion32, a front edge portion33, and a rear edge portion34. The inner peripheral edge portion31corresponds to a radially inner end portion of the blade13. The inner peripheral edge portion31is slanted to the first side in the rotation axis direction, from the front side in the rotational direction toward the rear side in the rotational direction. The inner peripheral edge portion31is connected to the outer peripheral surface of the hub12. The outer peripheral edge portion32corresponds to a radially outer end portion of the blade13. The outer peripheral edge portion32is slanted to the first side in the rotation axis direction, from the front side in the rotational direction toward the rear side in the rotational direction. The outer peripheral edge portion32is longer in circumferential length than the inner peripheral edge portion31. The front edge portion33corresponds to an end portion, closer to the front side in the rotational direction, of the blade13. The front edge portion33connects an end portion, closer to the front side in the rotational direction, of the inner peripheral edge portion31and an end portion, closer to the front side in the rotational direction, of the outer peripheral edge portion32. The rear edge portion34corresponds to an end portion, closer to the rear side in the rotational direction, of the blade13. The rear edge portion34connects an end portion, closer to the rear side in the rotational direction, of the inner peripheral edge portion31and an end portion, closer to the rear side in the rotational direction, of the outer peripheral edge portion32. The axial-flow fan11, when rotating about the center axis C in the direction indicated by the arrow A, generates a negative pressure at the second side in the rotation axis direction and also generates a positive pressure at the first side in the rotation axis direction. Therefore, the axial-flow fan11, when rotating about the center axis C in the direction indicated by the arrow A, causes air to flow from the second side in the rotation axis direction to the first side in the rotation axis direction. In this specification, the term “positive pressure surface13a” refers to a blade surface, closer to the first side in the rotation axis direction, of the blade13, and the term “negative pressure surface13b” refers to a blade surface, closer to the second side in the rotation axis direction, of the blade13. The blade13curves gently toward the second side in the rotation axis direction as seen in the circumferential direction such that the positive pressure surface13ais recessed. [Configuration of Hub] FIG.4is a perspective view illustrating the hub of the axial-flow fan as seen obliquely from the first side in the rotation axis direction.FIG.5is a perspective view illustrating the hub of the axial-flow fan as seen obliquely from the second side in the rotation axis direction.FIG.6is a view illustrating the hub of the axial-flow fan as seen from the second side in the rotation axis direction. The hub12has an outer wall15, an inner wall16, a boss17, and a sidewall18. The outer wall15has a tubular shape. Specifically, the outer wall15has a cylindrical shape. The outer wall15has a center aligned with the center axis C of the axial-flow fan11. The outer wall15has an outer peripheral surface15acorresponding to the outer peripheral surface of the hub12. The blades13are connected to the outer peripheral surface15aof the outer wall15. The inner wall16has a tubular shape. Specifically, the inner wall16has a cylindrical shape. The inner wall16is located radially inward of the outer wall15. The inner wall16has a center aligned with the center of the outer wall15. The boss17has a tubular shape. Specifically, the boss17has a cylindrical shape. The boss17is located radially inward of the inner wall16. The boss17has a center aligned with the center of the inner wall16and the center of the outer wall15. The boss17has a through hole17apassing through the center of the boss17. An output shaft of a motor (not illustrated) is inserted in the through hole17aand attached to the boss17. FIG.7is a schematic sectional view taken along line D-D inFIG.6.FIG.8is a schematic sectional view taken along line E-E inFIG.6.FIG.9is a schematic sectional view taken along line F-F inFIG.6. In the hub12, the inner wall16is shorter in axial length than the outer wall15. An end portion, closer to the first side in the rotation axis direction, of the inner wall16is located closer to the second side in the rotation axis direction (e.g., the upper side inFIG.8) than an end portion, closer to the first side in the rotation axis direction, of the outer wall15is. An end portion, closer to the second side in the rotation axis direction, of the inner wall16is located closer to the first side in the rotation axis direction (e.g., the lower side inFIG.8) than an end portion, closer to the second side in the rotation axis direction, of the outer wall15is. In the hub12, the sidewall18is located on the end portions, closer to the first side in the rotation axis direction, of the outer wall15, inner wall16, and boss17. The sidewall18closes the end portions, closer to the first side in the rotation axis direction, of the outer wall15and inner wall16each having a cylindrical shape. The sidewall18corresponds to an end surface, closer to the first side in the rotation axis direction, of the hub12. The sidewall18includes a first sidewall21and a second sidewall22. The first sidewall21connects the end portion, closer to the first side in the rotation axis direction, of the outer wall15and the end portion, closer to the first side in the rotation axis direction, of the inner wall16. The second sidewall22connects the end portion, closer to the first side in the rotation axis direction, of the inner wall16and the end portion, closer to the first side in the rotation axis direction, of the boss17. The first sidewall21has an annular portion21aand a slanted portion21blocated radially inward of the annular portion21a. The annular portion21ahas an annular shape, and extends in a direction orthogonal to the center axis C of the axial-flow fan11. The annular portion21ahas a radially outer end portion connected to the end portion, closer to the first side in the rotation axis direction, of the outer wall15. The slanted portion21bhas a conical shape, and extends obliquely to the center axis C of the axial-flow fan11. The slanted portion21bhas a radially outer end portion connected to a radially inner end portion of the annular portion21a. The slanted portion21balso has a radially inner end portion connected to the end portion, closer to the first side in the rotation axis direction, of the inner wall16. The second sidewall22has an annular shape, and extends in a direction orthogonal to the center axis C of the axial-flow fan11. The second sidewall22has a radially outer end portion connected to the radially inner end portion of the slanted portion21band the end portion, closer to the first side in the rotation axis direction, of the inner wall16. The second sidewall22also has a radially inner end portion connected to the end portion, closer to the first side in the rotation axis direction, of the boss17. The second sidewall22closes the end portion, closer to the first side in the rotation axis direction, of the inner wall16having a cylindrical shape. In the hub12, the sidewall18has a recessed portion18adefined by the slanted portion21band the second sidewall22and recessed toward the second side in the rotation axis direction. The slanted portion21bcorresponds to a peripheral wall of the recessed portion18a. The second sidewall22corresponds to a bottom wall of the recessed portion18a. In the hub12, as illustrated inFIG.4, the sidewall18has a protrusion24protruding toward the first side in the rotation axis direction. Specifically, the annular portion21aof the first sidewall21has the protrusion24. The annular portion21ahas a plurality of protrusions24spaced apart from each other in the circumferential direction. In one or more embodiments, three protrusions24are equally spaced by 120° apart from each other in the circumferential direction. FIG.10is a view illustrating a part of the hub of the axial-flow fan as seen from the first side in the rotation axis direction. Each protrusion24extends within a range of a center angle θ, which is less than 60° , about the center axis C of the axial-flow fan11. The protrusion24has an outer wall portion (a first wall portion)25, an inner wall portion (a second wall portion)26, a pair of end wall portions (a third wall portion and a fourth wall portion)27and28, and a top wall portion (a fifth wall portion)29. As illustrated inFIG.9, the outer wall portion25extends from the outer wall15of the hub12, toward the first side in the rotation axis direction. The outer wall portion25has an outer peripheral surface25athat is flush with the outer peripheral surface15aof the outer wall15. The outer wall portion25extends in the circumferential direction of the hub12, and curves in an arc shape as seen in the rotation axis direction. The inner wall portion26of the protrusion24extends from the slanted portion21bof the first sidewall21of the hub12, toward the first side in the rotation axis direction. The inner wall portion26has an inner peripheral surface26bthat is flush with an inner peripheral surface21b1of the slanted portion21b(i.e., an inner peripheral surface21b1of the recessed portion18a). The inner wall portion26extends obliquely to the center axis C. The inner wall portion26extends in the circumferential direction of the hub12, and curves in an arc shape as seen in the rotation axis direction. The outer peripheral surface25aof the outer wall portion25is connected to an end portion, closer to the rear side in the rotational direction A, of each blade13(seeFIG.4). The inner wall portion26is located radially inward of the outer wall portion25, and is spaced apart from the outer wall portion25. The outer wall portion25is located opposite the inner wall portion26in the radial direction. FIG.11is a schematic sectional view taken along line G-G inFIG.9. The pair of end wall portions27and28are located on two ends of the protrusion24so as to face each other in the circumferential direction. The pair of end wall portions27and28extend in the radial direction of the hub12. Each of the end wall portions27and28extends from the annular portion21aof the first sidewall21, toward the first side in the rotation axis direction. Each of the end wall portions27and28has such a trapezoidal shape that a radial length, closer to the first side in the rotation axis direction, is shorter. The radial length of each of the end wall portions27and28is shorter than a circumferential length of each of the outer wall portion25and the inner wall portion26. The protrusion24has a substantially rectangular section orthogonal to the center axis C, and this section is defined by the outer wall portion25, the inner wall portion26, and the pair of end wall portions27and28. The protrusion24has a space S3defined by the outer wall portion25, the inner wall portion26, and the pair of end wall portions27and28. In other words, the interior of the protrusion24is hollow. As illustrated inFIG.9, the space S3in the protrusion24communicates with a space S4defined between the outer wall15and the inner wall16of the hub12. The space S3in the protrusion24is closed with the top wall portion29at the first side in the rotation axis direction. The top wall portion29extends in a direction orthogonal to the center axis C of the axial-flow fan11. A plate-shaped rib (a third outer rib45) to be described later is located in the space S3in the protrusion24. The rib45extends from the space S3in the protrusion24toward the second side in the rotation axis direction, and reaches the space S4in the hub12. In the hub12, as illustrated inFIG.4, the outer wall15has a plurality of recessed portions15c. Specifically, each recessed portion15cis located in the end portion, closer to the second side in the rotation axis direction, of the outer wall15. Each recessed portion15cis equal in phase to the corresponding protrusion24in the circumferential direction. FIG.12is an explanatory view illustrating a state in which a plurality of axial-flow fans are stacked on top of each other. Each recessed portion15chas a trapezoidal shape as seen from the outside in the radial direction. Each protrusion24also has a trapezoidal shape as seen from the outside in the radial direction. The recessed portion15cis larger in outside shape than the protrusion24as seen from the outside in the radial direction. Specifically, a circumferential length L1of an open end (i.e., a lower end inFIG.12) of the recessed portion15cis slightly longer than a circumferential length L2of a root portion of the protrusion24. A circumferential length L3of a bottom portion of the recessed portion15cis slightly longer than a circumferential length L4of a distal end portion of the protrusion24. A length (i.e., a depth) L5of the recessed portion15cin the rotation axis direction is slightly longer than a length (i.e., a height) L6of the protrusion24. The axial-flow fans11, after manufacture, are stacked in the rotation axis direction for storage and transportation purposes. The protrusion24is located on the end surface located closer to the first side in the rotation axis direction of the axial-flow fan11, and the recessed portion15cis located in the end surface closer to the second side in the rotation axis direction of the axial-flow fan11. In stacking the plurality of axial-flow fans11on top of each other, the protrusion24of a lower one of the axial-flow fans11is inserted in the recessed portion15cof an upper one of the axial-flow fans11. This configuration thus enables reduction in total height of the stacked axial-flow fans11in the stacking direction as much as possible. This configuration also enables reduction in circumferential displacement of the axial-flow fans11arranged in the stacking direction. (Configuration of Rib) As illustrated inFIGS.5and6, the hub12has a plurality of ribs41,42,43,44, and45. The hub12according to one or more embodiments has outer ribs43,44, and45, and inner ribs41and42. The outer ribs43,44, and45are located between the outer wall15and the inner wall16. The inner ribs41and42are located between the inner wall16and the boss17. Each of the ribs41,42,43,44, and45has a plate shape and extends in the radial direction from the center axis C of the axial-flow fan11. Each of the ribs41,42,43,44, and45may alternatively extend in a direction oblique to the radial direction. The inner ribs41and42according to one or more embodiments connect an inner peripheral surface16bof the inner wall16and an outer peripheral surface17bof the boss17. The hub12has six inner ribs41and42spaced apart from each other in the circumferential direction. These inner ribs include three first inner ribs41and three second inner ribs42. The first inner ribs41and the second inner ribs42are arranged alternately in the circumferential direction. Attention is now focused on a certain one of the first inner ribs41. The first inner rib41and the second inner rib42adjacent thereto at the first side in the circumferential direction form an angle θ1. In addition, the first inner rib41and the second inner rib42adjacent thereto at the second side in the circumferential direction form an angle θ2. The angle θ1and the angle θ2satisfy a relation of θ1≤θ2. The first inner rib41and the second inner rib42that form the angle θ1constitute a set X. The hub12according to one or more embodiments has three sets X respectively constituted of the first inner ribs41and the second inner ribs42. These sets X are spaced apart from each other in the circumferential direction. One of the sets X, which is constituted of the first inner rib41and the second inner rib42, and the adjacent set X, which is constituted of the first inner rib41and the second inner rib42, form the circumferential angle θ2. The angle θ1between the first inner rib41and the second inner rib42, which constitute each set X, satisfies the following relation (1): θ1≤360/2N(°). . . (1) (N: the number of blades13). The axial-flow fan11according to one or more embodiments includes the three blades13. Therefore, the angle θ1satisfies the following relation (2). θ1≤60° . . . (2) The angle θ2between one of the sets X and the adjacent set X satisfies the following relation (3). θ2≥360/2N(°) . . . (3) The axial-flow fan11according to one or more embodiments includes the three blades13. Therefore, the angle θ2satisfies the following relation (4). θ2≥60° . . . (4) As illustrated inFIG.8, an end portion41c, closer to the second side in the rotation axis direction, of each first inner rib41and an end portion17c, closer to the second side in the rotation axis direction, of the boss17are located at the same position in the rotation axis direction. The end portion41c, closer to the second side in the rotation axis direction, of each first inner rib41is located closer to the first side in the rotation axis direction (e.g., the lower side inFIG.8) than an end portion16c, closer to the second side in the rotation axis direction, of the inner wall16is. The second inner ribs42are equal in shape to the first inner ribs41. Therefore, the positional relationships between each second inner rib42and the boss17and inner wall16in the rotation axis direction are also equal to the positional relationships between each first inner rib41and the boss17and inner wall16in the rotation axis direction. As illustrated inFIG.6, the outer ribs43,44, and45according to one or more embodiments connect an inner peripheral surface15bof the outer wall15and an outer peripheral surface16aof the inner wall16. The hub12has nine outer ribs43,44, and45spaced apart from each other in the circumferential direction. The nine outer ribs43,44, and45are equally spaced apart from each other in the circumferential direction. The outer ribs43,44, and45each have a plate shape, and are smaller in thickness than the inner ribs41and42. The inner ribs41and42are smaller in number than the outer ribs43,44, and45, but are larger in thickness than the outer ribs43,44, and45, which therefore contribute to improvement in strength. The outer ribs43,44, and45include three first outer ribs43, three second outer ribs44, and three third outer ribs45. These outer ribs are arranged ordinary. For example, the first outer rib43, the second outer rib44, the third outer rib45, the first outer rib43, the second outer rib44, the third outer rib45, the first outer rib43, the second outer rib44, and the third outer rib45are arranged in this order in the opposite direction to the rotational direction A. Of the first outer ribs43, second outer ribs44, and third outer ribs45arranged as described above, three outer ribs43,44, and45are provided for each blade13. The first outer rib43has a radially outer end portion located near a radially inner end portion of the front edge portion33of the blade13. The third outer rib45has a radially outer end portion located near a radially inner end portion of the rear edge portion34of the blade13. The second outer rib44has a radially outer end portion located in correspondence with a middle portion of the blade13in the rotational direction A. As illustrated inFIG.6, each first outer rib43is located between the first inner rib41and the second inner rib42, which constitute the corresponding set X, in the circumferential direction. Specifically, each first outer rib43has a radially inner end portion43alocated between a radially outer end portion41bof the corresponding first inner rib41and a radially outer end portion42bof the corresponding second inner rib42in the circumferential direction. As illustrated inFIG.7, an end portion43c, closer to the second side in the rotation axis direction, of each first outer rib43is located closer to the second side in the rotation axis direction (e.g., the upper side inFIG.7) than an end portion42c, closer to the second side in the rotation axis direction, of each second inner rib42is. The end portion43c, closer to the second side in the rotation axis direction, of each first outer rib43is flush with the end portion16c, closer to the second side in the rotation axis direction, of the inner wall16at a joint between the first outer rib43and the inner wall16. The second outer ribs44are equal in shape to the first outer ribs43. Therefore, the positional relationships between each second outer rib44and the corresponding first inner rib41(and second inner rib42) and inner wall16in the rotation axis direction are equal to the positional relationships between each first outer rib43and the corresponding first inner rib41(and second inner rib42) and inner wall16in the rotation axis direction. As illustrated inFIG.9, each third outer rib45is located in the space S3in the corresponding protrusion24as described above. Each third outer rib45extends from the space S3in the corresponding protrusion24to the space S4between the outer wall15and the inner wall16, toward the second side in the rotation axis direction. An end portion45c, closer to the second side in the rotation axis direction, of each third outer rib45extends to the slanted portion21bof the first sidewall21, and reaches the inner wall16beyond the slanted portion21b. The end portion45c, closer to the second side in the rotation axis direction, of each third outer rib45is located closer to the first side in the rotation axis direction than the bottom portion of the recessed portion15cin the outer wall15is. The end portion45c, closer to the second side in the rotation axis direction, of each third outer rib45is located closer to the first side in the rotation axis direction than the end portion42c, closer to the second side in the rotation axis direction, of each second inner rib42is. The axial-flow fan11having the foregoing configuration generates a centrifugal force by rotation, so that a load traveling through each blade13is imposed on the hub12to pull the hub12radially outward. The hub12according to one or more embodiments has the first outer ribs43, the second outer ribs44, and the third outer ribs45. These outer ribs43,44, and45are capable of supporting the outer wall15of the hub12against the radial load that travels through each blade13and then reaches the outer wall15. In particular, when the axial-flow fan11rotates, the hub12receives the maximum radial load at a position near the front edge portion33of each blade13. As illustrated inFIG.6, the radially inner end portion43aof each first outer rib43, which is located near the radially inner end portion of the front edge portion33of the corresponding blade13, is located between the first inner rib41and the second inner rib42, which constitute the corresponding set X, in the circumferential direction. Therefore, the first inner rib41and the second inner rib42are capable of receiving, together with the first outer rib43, the large load imposed on the outer wall15through the position near the front edge portion33of each blade13, via the inner wall16. This configuration therefore further improves the strength of the hub12, and causes the hub12to further resist deformation. The hub12also receives, in addition to the radial load, a circumferential load traveling through each blade13. As illustrated inFIG.4, the hub12has the protrusions24on the end surface, closer to the first side in the rotation axis direction, of the hub12. The protrusions24each have the outer wall portion25and the inner wall portion26each extending in the circumferential direction, and the pair of end wall portions27and28each extending in the radial direction. The protrusions24each have the substantially rectangular section in the direction orthogonal to the center axis C (seeFIG.11). In each protrusion24, the pair of end wall portions27and28are capable of causing the hub12to resist deformation mainly owing to the radial load imposed on the hub12. In each protrusion24, the outer wall portion25and the inner wall portion26are capable of causing the hub12to resist deformation mainly owing to the circumferential load imposed on the hub12. Therefore, the protrusions24allow the hub12to have a structure resistant to both the radial load and the circumferential load. The strength of the hub12is thus improved. Each blade13is partly connected to the outer wall portion25of the corresponding protrusion24, so that the outer wall portion25directly receives the radial load and the circumferential load from the blade13. However, the protrusion24having the substantially rectangular section is capable of properly supporting the outer wall15of the hub12against these loads. [Configuration of Air Conditioner] FIG.13is a schematic plan view illustrating an inside of an air conditioner including the axial-flow fan according to the present disclosure, as seen from above.FIG.13illustrates an outdoor unit51of an air conditioner50. The air conditioner50is of a separate type and includes an outdoor unit and an indoor unit provided separately from the outdoor unit. The outdoor unit51includes the axial-flow fan11. The outdoor unit51includes a housing52. The housing52has a rectangular parallelepiped shape. The outdoor unit51also includes a partition53dividing the housing52into a machine chamber S1and a heat exchange chamber S2. The housing52has adjacent sidewalls52aand52blocated in the heat exchange chamber S2, and the sidewalls52aand52brespectively have air intake ports52a1and52b1. The housing52also has a sidewall52cadjacent to the sidewall52bhaving the air intake port52b1, and the sidewall52chas an air blow-out port52c1. The housing52houses, in the machine chamber51, a compressor54, a four-way switching valve (not illustrated), an accumulator (not illustrated), an oil separator (not illustrated), an expansion valve (not illustrated), and the like. The housing52also houses, in the heat exchange chamber S2, a heat exchanger55, a fan motor56, the axial-flow fan11, and the like. The axial-flow fan11is connected to the fan motor56with a shaft56a, and is driven by the fan motor56to rotate about the shaft56a. The shaft56ais mounted to the boss17(see, for example,FIGS.2,5) of the axial-flow fan11. The axial-flow fan11is placed with the positive pressure surface13a(seeFIG.3) facing the sidewall52chaving the air blow-out port52c1and the negative pressure surface13b(seeFIG.3) facing the sidewall52ahaving the air intake port52a1. When the fan motor56operates, the axial-flow fan11rotates. Air is thus taken in the housing52through the air intake ports52a1and52b1, and is then blown out of the housing52through the air blow-out port52c1. InFIG.8, arrows “a” each indicate a flow of air taken in the housing52through the air intake ports52a1and52b1, and arrows “b” each indicate a flow of air blown out of the housing52through the air blow-out port52c1. The heat exchanger55has an “L” shape in plan view. The heat exchanger55bends at a position near a corner portion52ebetween the sidewalls52aand52brespectively having the air intake ports52a1and52b1, and extends along the sidewalls52aand52b. The heat exchanger55includes a pair of headers61and62, a group of fins63arranged side by side such that their plate-shaped faces extend in parallel, and a heat transfer tube64passing through the group of fins63arranged side by side. A refrigerant, which circulates through a refrigerant circuit, flows into the heat transfer tube64of the heat exchanger55. The heat exchanger55is connected to the compressor54in the machine chamber S1with a pipe (not illustrated). In the air conditioner50according to one or more embodiments, the outdoor unit51includes the axial-flow fan11. In an air conditioner according to the present disclosure, alternatively, an indoor unit (not illustrated) may include the axial-flow fan11. The air conditioner50may include the axial-flow fan11placed with the axis of rotation extending in an up-and-down direction. The foregoing embodiments may be at least partially combined with each other in a given manner. [Action and Effects of Embodiments] During the rotation of the axial-flow fan, a load traveling through each blade is imposed on the outer wall portion of the hub to pull the hub radially outward. This load causes the outer wall portion of the hub to deform so as to expand radially outward. It has therefore been required to improve the strength of the hub in order to cause the hub to resist deformation. Therefore, one or more embodiments of the present disclosure provide an axial-flow fan including a hub with improved strength, and an air conditioner including the axial-flow fan. (Action and Effects) An axial-flow fan11according to one or more embodiments includes a hub12and a plurality of blades13disposed on an outer peripheral surface of the hub12and spaced apart from each other in a circumferential direction. The hub12includes: an outer wall15having a tubular shape; an inner wall16having a tubular shape, the inner wall16being located radially inward of the outer wall15; a boss17to which a shaft is mounted, the boss17being located radially inward of the inner wall16; a first sidewall21connecting an end portion, closer to a first side in an rotation axis direction of the hub12, of the outer wall15and an end portion, closer to the first side in the rotation axis direction, of the inner wall16; a second sidewall22connecting the end portion, closer to the first side in the rotation axis direction, of the inner wall16and an end portion, closer to the first side in the rotation axis direction, of the boss17; a first inner rib (a first rib)41connecting an inner peripheral surface of the inner wall16and an outer peripheral surface of the boss17; a second inner rib (a second rib)42adjacent to the first inner rib41in the circumferential direction, the second inner rib42connecting the inner peripheral surface of the inner wall16and the outer peripheral surface of the boss17; and a first outer rib (a third rib)43connecting an inner peripheral surface of the outer wall15and an outer peripheral surface of the inner wall16. The first outer rib43has a radially inner end portion located between a radially outer end portion of the first inner rib41and a radially outer end portion of the second inner rib42in the circumferential direction. When the axial-flow fan11rotates, a load traveling through each blade13is imposed on the outer wall15of the hub12to pull the hub12radially outward. The outer wall15of the hub12is supported by the first outer rib43, and is further supported by the first inner rib41and the second inner rib42through the inner wall16. This configuration thus allows the hub12to have a structure resistant to the radial load, and causes the hub12to resist deformation. The radially inner end portion of the single first outer rib43is located between the radially outer end portion of the first inner rib41and the radially outer end portion of the second inner rib42in the circumferential direction. Therefore, the single first outer rib43can be reinforced with the first inner rib41and second inner rib42. The first outer rib43has a radially outer end portion located near a radially inner end portion of a front edge portion33of each blade13in a rotational direction A of the hub12. The front edge portion33of each blade13in the rotational direction of the hub12corresponds to a portion where the maximum load resulting from air is imposed. In addition, the load imposed on the outer wall15of the hub12through each blade13also increases at the position near the radially inner end portion of the front edge portion33of each blade13. In view of this, the radially outer end portion of the first outer rib43is located near the radially inner end portion of the front edge portion33of each blade13. This configuration thus enables effective improvement in strength of the hub12at the portion where the large load is imposed through each blade13. The first inner rib41and the second inner rib42are arranged in the radial direction of the hub12, and an angle between the first inner rib41and the second inner rib42satisfies the following relation (1): θ≤360/2N . . .(1) (where θ represents the angle between the first rib and the second rib, and N represents the number of blades). If the angle between the first inner rib41and the second inner rib42is too large, there is a possibility of reduction in effect of supporting the first outer rib43in the radial direction. In view of this, a spacing between the first inner rib41and the second inner rib42may be set to satisfy the foregoing relation (1). The hub12includes: a first set X including a combination of the first inner rib41and the second inner rib42; and a second set X including a combination of the first inner rib41and the second inner rib42that are different from the first inner rib41and the second inner rib42in the first set X, the second set X being adjacent to the first set X in the circumferential direction. An angle between the first set X and the second set X is larger than an angle between the first inner rib41and the second inner rib42in each of the first set X and the second set X. According to this configuration, the first outer rib43can be effectively reinforced with the first inner rib41and the second inner rib42in each set X. The hub12according to the foregoing embodiments further includes a third outer rib (a fourth rib)45located between the first set X and the second set X in the circumferential direction, the third outer rib45connecting the inner peripheral surface15bof the outer wall15and the outer peripheral surface16aof the inner wall16. The third outer rib45has a radially outer end portion located near a radially inner end portion of a rear edge portion34of each blade13in the rotational direction A of the hub12. According to this configuration, when a load is applied to the outer wall15through the position near the rear edge portion34of each blade13so as to pull the outer wall15radially outward, the outer wall15is supported by the third outer rib45, so that the strength of the hub12can be improved. While various embodiments have been described herein above, it is to be appreciated that various changes in form and detail may be made without departing from the spirit and scope presently or hereafter claimed. For example, the number of outer ribs is not limited to that described in the foregoing embodiments, and is changeable as appropriate. For example, a plurality of second outer ribs44may be disposed between each first outer rib43and the adjacent third outer rib45. Alternatively, no second outer rib44may be disposed between each first outer rib43and the adjacent third outer rib45. In addition, the number of inner ribs is not limited to that described in the foregoing embodiments, and is changeable as appropriate. The number of sets corresponding to the combinations of the first inner ribs and the second inner ribs is changeable in accordance with the number of blades13. Two or more outer ribs may be disposed between the first inner rib and the second inner rib that constitute each set. The sidewall18of the hub12does not necessarily have the recessed portion18a. The number of protrusions24is changeable as appropriate in accordance with the number of blades13. Although the disclosure has been described with respect to only a limited number of embodiments, those skilled in the art, having benefit of this disclosure, will appreciate that various other embodiments may be devised without departing from the scope of the present disclosure. Accordingly, the scope of the disclosure should be limited only by the attached claims. REFERENCE SIGNS LIST 11axial-flow fan12hub13blade15outer wall15aouter peripheral surface15binner peripheral surface16inner wall16aouter peripheral surface16binner peripheral surface16cend portion17boss17bouter peripheral surface17cend portion18sidewall21first sidewall22second sidewall33front edge portion34rear edge portion41first inner rib (first rib)41bradially outer end portion41cend portion42second inner rib (second rib)42bradially outer end portion42cend portion43first outer rib (third rib)43aradially inner end portion43cend portion45third outer rib (fourth rib)50air conditionerA rotational direction | 39,086 |
11859636 | DETAILED DESCRIPTION FIG.1shows a schematically simplified motor vehicle2in the form of a passenger car, having an internal combustion engine4. The motor vehicle2is driven by means of the combustion engine4. For this purpose, the combustion engine4, by means of an unspecified drive train, is in active connection with at least one of the four wheels6of the motor vehicle2. In addition, the motor vehicle2comprises a radiator fan8, which serves to cool the combustion engine4. Thus, the radiator fan8is a main fan of the motor vehicle2. The radiator fan8is fluidically connected to the combustion engine4by means of a number of lines10, through which a coolant is led during operation from the radiator fan8to the combustion engine4and through cooling channels therein. By means of the coolant, excess heat is absorbed and led back to the radiator fan8, by means of which a cooling of the coolant takes place. The radiator fan8comprises a radiator12with a radiator network, not further shown, through which a number of pipes are passed and are thermally contacted with it. The pipes are fluidically coupled with the lines10, so that during operation, the coolant is passed through the pipes. The radiator fan8further comprises a fan frame14, which is arranged in a direction of travel16of the motor vehicle2behind the radiator12. An electric motor18is attached to the fan frame14. During operation, an air stream passes through the radiator12and is suitably shaped by means of the fan frame14. When the motor vehicle2is stopped, air is sucked through the radiator12by means of the electric motor18, so that the radiator12is essentially always, or at least depending on existing requirements, interspersed with the air stream during operation. Thus, a cooling of the radiator12takes place, which is why even after a comparatively long operation of the combustion engine4no overheating of the radiator fan8takes place. In addition, by means of the fan frame14, the air passing through the radiator fan8is directed to the combustion engine4and the latter is additionally cooled in this way from the outside. FIG.2shows the radiator fan8schematically simplified, in perspective in an exploded view, wherein the radiator12is omitted. On the radiator12, the fan frame14is attached, which completely covers the radiator network, not shown, and is congruent with this. The fan frame14is essentially flat and has a round recess20, which is oriented perpendicular to the direction of travel16, and which has a diameter of 30 cm. The fan frame14further comprises a motor mount22, which is arranged counter the direction of travel16above the recess20and held there by means of a plurality of mounting struts24. In the assembly state, the electric motor18is held by means of the motor mount22and the electric motor18thus attached to this. Here, the electric motor18is located on the opposite side of the radiator12of the fan frame14. A shaft26of the electric motor18protrudes in the direction of travel16through the motor mount22and is attached in a rotationally fixed manner to a hub28of a fan wheel30. Thus, the fan wheel30is driven by means of the electric motor18, which is held by means of the motor mount22. At the hub26, a number of fan blades32is connected. In the assembly state, the fan wheel30is arranged parallel to the recess20within this and is rotated during operation by means of the electric motor18about an axis of rotation34, which is parallel to the direction of travel16, and which extends through the center of the recess20. Thus, air is sucked through the recess20counter the direction of travel16during operation. In addition, the fan frame14comprises a dynamic pressure damper36, which comprises an opening which is covered by a flap38. If there is a comparatively high (air) pressure in the direction of travel16in front of the fan frame14, in particular with a comparatively fast movement of the motor vehicle2, the passage of air through the recess20is partially hindered due to the fan wheel30or the fan wheel2830can be rotated comparatively quickly. However, this would lead to an increased load on the electric motor18and the other component and to increased noise. From a certain pressure, the flap38is therefore swiveled and the opening released so that air can flow through it. Thus, an air stream through the radiator12, which is located in the direction of travel16in front of the fan frame14, is increased. At a comparatively low air pressure in front of the fan frame14, as is the case with a standstill of the motor vehicle2, the flap38is closed, so that the formation of a circular air stream passing only through the opening of the dynamic pressure damper36and the recess20is prevented. Thus, the radiator12is always interspersed by means of a sufficient air stream. FIG.3andFIG.4show, enlarged in sections in perspective in a semi-transparent representation, the fan wheel30which is rotationally symmetrical with respect to the axis of rotation34. The fan wheel34comprises the pot-shaped hub28, to which in this example a total of nine fan blades32are connected, which run partly radially and partly tangential with respect to the axis of rotation34. In other words, the fan blades have a crescent shape, wherein these constantly face the same direction in the tangential direction. To create the air stream through the fan frame14, the fan blades32are inclined slightly perpendicular to a plane perpendicular to the axis of rotation34. The radial ends of the fan blades32with respect to the axis of rotation34are bluntly designed in this embodiment, and the fan wheel30is thus without an outer ring. Each of the fan blades32comprises a stabilizing structure40, which is formed by means of three spaced struts42. The struts42, and thus the respective stabilizing structure40, is made of a first material, namely a steel. As a result, the struts42have a comparatively high stability, but the weight is increased. The struts42are identical to each other or at least built from the same by means of cutting to length and suitable bending so that all struts42have the same cross-section over their complete course. Here, the course of the struts42is substantially equal to the course of the respective fan blade32, wherein the radial outer ends of the struts42of the respective stabilizing structure40are offset to each other, so that do not have a completely parallel course. The struts42extend in this embodiment from the radial outer end of the respective fan blade32to the hub28. In a variant, not shown, the struts42are shortened so that they are radially offset outwards from the hub28. The struts42have a substantially rectangular cross-section perpendicular to their course. Here, their extension is increased in the axial direction, i.e., parallel to the axis of rotation34. In this way, the stability of struts42in this direction is increased. Each of the fan blades32further comprises a body44which is made of a second material, namely a plastic, by overmolding the respective stabilizing structure40. Thus, the second material differs from the first material. Each body44is also arranged between the individual struts42of the same fan blade32, and these are held captively by means of the respective body44. By means of the respective body44, the external shape of the respective fan blade32is predetermined, and the struts42, and consequently also each stabilizing structure40, are completely surrounded by the respective body44, except for their respective ends. The bodies44are made of the second material, namely a polyamide, wherein the hub is also made of the second material. The hub28and the body44are one-piece, so that a separate attachment of the fan blades32to the hub28is not required. Robustness is also increased in this way. For the production of the fan wheel30, the stabilizing structures40are suitably positioned within a mold, which is subsequently filled by means of the second material by injection molding, so that all cavities of the mold are filled. As a result, the bodies44and the hub28are created, wherein the stabilizing structures40are surrounded by the respective bodies44. FIG.5shows an alternative embodiment of the fan wheel30, wherein the hub28and the fan blades32are not changed. However, the fan blades32are surrounded by an outer ring46arranged vertically and concentrically to the axis of rotation34. Thus, the outer ring46is also concentric to the hub28, and these are essentially arranged in a common plane which is perpendicular to the axis of rotation34. The radial outer ends of the fan blades32are attached to the outer ring46. The outer ring46is created one-piece from the second material and formed on the bodies44. In production, the outer ring46is created in one step with the hub28and the bodies44by injection molding. The outer ring46has an essentially L-shaped cross-section, which thus comprises two legs. In this case, one of the legs is arranged parallel to the axis of rotation34, and the remaining one points radially outwards from this. In this way, stability is increased, wherein the weight of the fan wheel30is not excessively increased. In the assembly state, an unspecified contour arranged on the radially outwardly projecting leg engages in a corresponding contour of the fan frame14, which surrounds the recess20, so that a labyrinth seal is created. In this way, leakage air between the fan wheel30and the fan frame14is minimized. FIG.6shows a further modification of the fan wheel30. The hub28is not changed. Also, the outer ring46is again present. However, this is no longer merely designed in one piece, but has a further stabilizing structure48, which is formed by means of a hollow cylinder made of a further first material and arranged concentrically to the hub28and thus also to the axis of rotation34. The other first material is equal to the first material and thus a steel. Compared to the preceding embodiment, in the fan blades32, the struts42are slightly extended at their radial outer end, and welded to the further stabilizing structure48, i.e., the hollow cylinder. Thus, the stabilizing structures40and the further stabilizing structure48are directly attached to each other. The further stabilizing structure48of the outer ring46is surrounded by another body50from the further second material. By means of the further body50, the outer shape of the outer ring46is specified, which corresponds to the outer shape of the preceding embodiment. The further second material is the same as the second material, and the further body50is formed in one piece with the respective bodies44. To produce this fan wheel30, the further stabilizing structure48, to which the stabilizing structures40are already attached, is inserted into a corresponding mold, which is subsequently filled by means of the second material, which also forms the further second material, so that the stabilizing structures40and the further stabilizing structure48are overmolded by means of the second material and thus surrounded. The hub28is also created. Due to the further stabilizing structure48, the positioning of the stabilizing structures40within the mold is facilitated. The invention is not limited to the embodiments described above. Rather, other variants of the invention can be derived from it by the skilled person without departing from the subject-matter of the invention. In particular, all the individual features described in connection with the individual embodiments can also be combined in other ways without departing from the subject-matter of the invention. The invention being thus described, it will be obvious that the same may be varied in many ways. Such variations are not to be regarded as a departure from the spirit and scope of the invention, and all such modifications as would be obvious to one skilled in the art are to be included within the scope of the following claims. | 11,916 |
11859637 | DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Advantages and features of the present disclosure and methods to achieve them will become apparent from the descriptions of exemplary embodiments herein below with reference to the accompanying drawings. However, the present disclosure is not limited to exemplary embodiments disclosed herein but may be implemented in various different ways. The exemplary embodiments are provided for making the disclosure of the present disclosure thorough and for fully conveying the scope of the present disclosure to those skilled in the art. It is to be noted that the scope of the present disclosure is defined only by the claims. Like reference numerals denote like elements throughout the descriptions. FIG.1is a perspective view of a washing machine according to an embodiment of the present invention.FIG.2is a side cross-sectional view of the washing machine shown inFIG.1.FIG.3illustrates an assembly in which a distribution pipe is installed at a gasket.FIG.4illustrates the configuration of the assembly, shown inFIG.3, from the front.FIG.5is an enlarged view of a portion marked with a dotted line inFIG.4.FIG.6illustrates the configuration of a gasket from the rear.FIG.7is a front view of a first distribution pipe and a second distribution pipe.FIG.8is a partial cut-away view of a pump.FIG.9is an enlarged view of a portion marked with a dotted line inFIG.8. Referring toFIGS.1and3, a washing machine according to an embodiment of the present invention includes a casing10forming an exterior appearance of the washing machine, a tub30disposed in the casing10and containing wash water, a drum40rotatably installed in the tub30and receiving laundry, and a motor50rotating the drum40. A front panel11having a laundry entry hole12formed therein may be disposed at front of the casing10. A door20for opening and closing the laundry entry hole12, and a dispenser14to which detergent is introduced may be installed at the front panel11. In addition, a water supply valve15, a water supply pipe16, and a water supply horse17may be installed inside the casing10. Upon a water supply, wash water having passed through the water supply valve15and the water supply pipe16may be mixed with detergent in the dispenser14and then supplied to the tub30through the water supply horse17. Meanwhile, a direct water supply pipe18may be connected to the water supply valve15so that wash water is not mixed with detergent but supplied directly to the tub30through the direct water supply pipe18. There may be provided a direct nozzle19for spraying water, supplied through the direct water supply pipe18, into the drum40. Referring toFIGS.2to4, there are provided a first distribution pipe80(1) and a second distribution pipe80(2), which are for guiding water pumped by a pump70. The first distribution pipe80(1) and the second distribution pipe80(2) may be provided on both sides of a gasket60, respectively. The distribution pipes80(1) and80(2) may be formed of synthetic resin that is harder or stiffer than the gasket60. The distribution pipes80(1) and80(2) maintains a predetermined shape in spite of vibration occurring during operation of the washing machine, and the distribution pipes80(1) and80(2) are rigid relative to the gasket60, which is so flexible to transforms in response to vibration of the tub30. In addition, circulation pipes86(a) and86(2) may be so flexible to transform in response to vibration of the tub30. In this case, the distribution pipes80(1) and80(2) may be formed of synthetic resin that is more solid or stiffer than the circulation pipes86(1) and86(2). The pump70and the tub30are connected via a discharge horse72, and the first distribution pipe80(1) and the second distribution pipe80(2) are connected to the pump70by the first circulation pipe86(1) and the second circulation pipe86(2). The pump70includes a first circulation port71bconnected to the first circulation pipe86(1), and a second circulation port71cconnected to the second circulation pipe86(2). When the pump70operates, wash water contained in the tub30may be sprayed into the drum40through the first distribution pipe80(1) and the second distribution pipe80(2) such that the wash water circulates. The pump70may be connected to a drain pipe74to thereby discharge the wash water to the outside through the drain pipe74. The above-described pump70functions as a circulation pump for circulating pump and as a drain pump for discharging wash water. On the contrary, the circulation pump and the drain pump may be installed separately. In the case where the circulation pump and the drain pump are installed separately, it is obvious that the drain pipe74is connected to the drain pump and that the first circulation pipe86(1) and the second circulation pipe86(2) are connected to the circulation pump. Meanwhile, the tub30may be formed as a single tub body or may be formed as a first tub body30aand a second tub body30bare fastened to each other. Regarding the embodiment of the present invention, the example in which the first tub body39aand the second tub body30bare fastened to form the tub30is described. Hereinafter, the first tub body30awill be referred to merely as a “tub”30. An opening is formed on a front surface31of the tub30to correspond to the laundry entry hole12formed in the front panel11. The gasket60is disposed between an edge of the laundry entry hole12formed in the front panel11, the edge which defines the laundry entry hole12, and an edge of the tub30, the edge which defines the opening. The gasket60is formed of a flexible substance such as rubber and has an approximate cylindrical shape. For example, the gasket60may be formed of a substance such as Ethylene Propylene Diene Monomer (EPDM), Thermo Plastic Elastomer (TPE), or the like, but aspects of the present invention are not limited thereto. A front edge of the gasket60is connected to the edge of the laundry entry hole12, and a rear edge of the gasket60is connected to the edge of the opening of the tub30, thereby sealing between the tub30and the front panel11. The door20and a front end of the gasket60are tightly brought into contact in the state in which the door20is closed, sealing between the door20and the gasket60to thereby prevent a leakage of water wash. Referring toFIGS.4to6, the first and second distribution pipes80are installed at the gasket60. At least one balancer90may be fastened to the front surface31of the tub30. A first balancer90(1) may be disposed over the front surface31, and a second balancer90(2) may be disposed under the front surface31. A pipe80may include an inlet port81through which water discharged from the pump70is introduced, a transport conduit82which guides the water introduced through the inlet port81, and a plurality of outlet ports83and84which are branched from the transport conduit82. Through the inlet port81, water discharged from the pump70is introduced. The inlet port81may be connected to the pump70by the circulation pipe86(1). The pump70may include a circulation port through which circulating water is discharged, and the number of which corresponds to the number of the distribution pipes80. In the present embodiments, the pump70includes a first circulation port and a second circulation port, wherein the first circulation port is connected to an inlet port81of the first distribution pipe80(1) by the first circulation pipe86(1) and the second circulation port is connected to an inlet port81of the second distribution pipe80(2) by the second circulation pipe86(2). The transport conduit82is positioned external to a passage60P defined by the gasket60, and guides water, introduced through the inlet port81, in an upward direction. The transport conduit82constitutes a flow path communicating with the inlet port81, and the flow path may be bent in a shape approximately corresponding to an outer circumferential surface of the gasket60and extends in an up-down direction. The plurality of outlet ports83and84are branched from the transport conduit82. Circulating water transported along the transport conduit82is discharged through the plurality of outlet ports83and84. The outlet ports83and84are branched from the transport conduit82from above the inlet port81. That is, an entrance hole of each of the outlet ports83and84(which is a portion of each of the outlet ports83and84being connected to the transport conduit82) is located further higher than the exit of the inlet port81(which is a portion of the inlet port81being connected to the transport conduit82). The plurality of outlet ports83and84includes two outlet ports83and84formed at different heights. Hereinafter, a lower outlet port in the two outlet ports83and84is referred to as a lower outlet port83, and the other outlet port located higher than the lower outlet port83is referred to as an upper outlet port84. First to fourth port receiving pipes64a,64b,64c, and64dmay be formed on an outer circumferential surface61of the gasket60to protrude outwardly so as to correspond to four outlet ports83and84, respectively. The four outlet ports83and84may be inserted into and connected to the first to fourth port receiving pipes64a,64b,64c, and64d. At least one pair of nozzles for spraying water into the drum40is provided. In the present embodiment, first to fourth nozzles66a,66b,66c, and66drespectively communicating with the first to fourth port receiving pipes64a,64b,64c, and64dare provided on an inner circumferential surface62of the gasket60. In an embodiment of the present invention, the first to fourth nozzles66a,66b,66c, and66dare formed integrally with the integrally with the gasket60. On the contrary, the first to fourth nozzles66a,66b,66c, and66dmay be formed as components separately from the gasket60and coupled to the gasket60or may be separated from the gasket60and flow-path-connected to the first to fourth port receiving pipes64a,64b,64c, and64dvia a separate flow path connecting member (not shown). First to Fourth protrusions65a,65b,65c, and65dmay protrude toward the interior of the gasket60from the inner circumferential surface62of the gasket60, and the first to fourth nozzles66a,66b,66c, and66dmay be formed at the first to fourth protrusions65a,65b,65c, and65d, respectively. Accordingly, circulating water discharged through the outlet ports83and84in the respective distribution piping80(1) and80(2) may be sprayed into the drum40through the first to fourth nozzles66a,66b,66c, and66d. The number of each of port receiving pipes64, protrusions65, and nozzles66, and positions thereof may be modified, as does the number of outlet ports84. The first to fourth nozzles66a,66b,66c, and66dmay include nozzles66aand66bto which water is supplied through the first distribution piping80(1), and nozzles66cand66dto which water is supplied through the second distribution pipe80(2). Hereinafter, when necessary to distinguish, the nozzles to which water is supplied through the first distribution piping80(1) are referred to as first nozzles66aand66b, and the nozzles to which water is supplied through the second distribution pipe80(2) are referred to as second nozzles66cand66d. In addition, among the nozzles66aand66bor66cand66dto which water is supplied through the distributing pipe80(1) or80(2), a nozzle at an upper position is an upper nozzle66bor66d, and a nozzle at a position lower than the upper nozzle66bor66dis a lower nozzle66aor66c. That is, a first lower nozzle66aand a first upper nozzle66b, to which water is supplied through the first distribution piping80(1), and a second lower nozzle66cand a second upper nozzle66d, to which water is supplied through the second distribution piping80(2), are provided in the gasket60in the present embodiment. Referring toFIGS.8and9, the pump70includes a pump housing71, an impeller72disposed in the pump housing71, and a pump motor73for providing a torque to rotate the impeller72. The pump motor73is capable of controlling a direction of rotation. For example, the pump motor73may be preferably, but not limited to, a Brushless Direct Current Motor (BLDG). There may be provided a controller (not shown) that controls a direction of rotation of the pump motor73. The controller may include a processor that accesses a medium, in which a program is recorded, to thereby perform computation according to the recorded program. Further, the controller may control not just the pump motor73but also other electronic components included in the washing machine. The pump housing71forms a space71swhere the impeller72is housed. The pump housing71includes a water introducing port71a, along which water discharged from the tub30is guided to the space71s, and a first circulation port71band a second circulation port71c, through which water pumped by the impeller72is discharged. The first circulation port71band the second circulation port71care connected to the first circulation pipe86(1) and the second circulation pipe86(2). Thus, a water current formed upon rotation of the impeller72by the pump motor73is discharged through the first circulation port71band the second circulation port71cat the same time. In this case, water discharged through the first circulation port71bis supplied to the first distribution pipe80(1) through the first circulation pipe86(1), and water discharged through the second circulation port71cis supplied to the second distribution pipe80(2) through the second circulation pipe86(2). In the pump housing71, an inner circumferential surface710defining the space71sincludes a rotating water current guide part711and a biased current guide part712. The rotating water current guide part711extends in a direction of rotation of the impeller72from a cut-off point75, at which a first flow F1running in the direction of rotation of the impeller72and a second flow F2running toward the entrance hole of the first circulation port71bare branched. The first circulation port71bis disposed between the cut-off point75and the second circulation port71c, and a distance from the center of rotation O of the impeller72to the cut-off point75may be shorter than a distance from the center of rotation to the first circulation port71b. While extending along a circumference of the impeller72, the rotating water current guide part711may form a curved surface that is rolled in the direction of rotation of the impeller, and the first flow F1is guided to the second circulation port71cby the rotating water current guide part711. While extending from the cut-off point75, the biased water current guide part712may form an angle greater than 180° relative to the rotating water current guide part711. The rotating water current guide part711and the biased water current guide part712may form an edge, respectively, and the edge may constitute the cut-off point75. The biased water current guide part712extends from the rotating water current guide part711in a direction Vd, which is biased from the radial direction Vcr in a direction opposite to the direction of rotation of the impeller72, thereby guiding a water current (or the first flow F1) guided by the rotating water current guide part711to the first circulation port71b. Due to this structure, the second circulation port71cdischarges a first portion of the first flow F1, and the first circulation port71bdischarges an amount of water added with a second flow F2that is branched at the cut-off point75in a second portion of water corresponding to the rest of the first flow F1. Suppose that the cut-off point75does not exist, that the inner circumferential surface710is symmetric between the left and right sides, and that the impeller72rotates in a counter-clockwise direction with reference toFIG.8. In this case, a portion of the rotating water current is discharged through the second circulation port71clocated at the upper stream of the water current, and the rest of the rotating water current is discharged through the first circulation port71b. However, since the second circulation port71cis at a location higher than the first circulation port71band almost in contact with the inner circumferential surface710of the pump housing71, the amount of water discharged through the second circulation port71cis larger than the amount of water discharged through the first circulation port71b. On the contrary, in the present invention, the second flow F2branched at the cut-off point75is further discharged through the first circulation port71b. Accordingly, it is possible to increase the discharge flowrate of the first circulation port71b, compared to the conventional technology, and to reduce a deviation in the discharge flow rate between the first circulation port71band the second circulation port71c. Meanwhile, the cut-off point75may be formed at a location spaced apart from an entrance hole h1of the first circulation port71btoward the center of rotation O of the impeller72. The biased water current guide part712may extend, from the cut-off point75, with a component (which is a component of the direction Vc inFIG.9) opposite to the direction of rotation of the impeller72. InFIG.9, Vcr indicates the radial direction from the cut-off point75(which is a line connecting the center of rotation O (seeFIG.8) of the impeller72and the cut-off point75. The first circulation port71band the second circulation port71cmay extend in parallel with each other. At the cut-off point75, the biased water current guide part712may form an acute angle θ relative to a line component Vr, which is parallel to the first circulation port71b, in the direction of rotation of the impeller72. On the inner circumferential surface710of the pump housing71, an entrance hole h1of the first circulation port71band an entrance hole h2of the second circulation port71cmay be disposed in an acute-angle area SE1that forms a predetermined acute angle relative to the center of rotation of the impeller72. In this case, the rotating water current guide part711extends to the entrance hole h2of the second circulation port71cby passing through a reflex-angle area SE2, forming a reflex angle relative to the acute angle, along the direction of rotation of the impeller72from the cut-off point75. In addition, the biased water current guide part712is bent at the cut-off point75to thereby guide the second flow F2to the first circulation port71b. Although some embodiments have been described above, it should be understood that the present invention is not limited to these embodiments, and that various modifications, changes, alterations and variations can be made by those skilled in the art without departing from the spirit and scope of the invention. Therefore, it should be understood that the above embodiments are provided for illustration only and are not to be construed in any way as limiting the present invention. | 18,852 |
11859638 | DESCRIPTION OF REFERENCE NUMERALS 10refers to pump shell11refers to pump body111refers to main barrel112refers to real cover113refers to line passing pipe12refers to pump cover13refers to sealing ring101refers to mounting cavity102refers to pump cavity103refers to water inlet104refers to water outlet105refers to first external thread106refers to second external thread107refers to convex ring108refers to hook portion109refers to annular groove20refers to rotating shaft30refers to rotor40refers to stator50refers to impeller51refers to clamping spring60refers to water discharge connector61refers to threaded sleeve70refers to handle seat71refers to handle72refers to sucker701refers to clamping groove702refers to cavity80refers to filter cover DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS With reference toFIG.1toFIG.6, a specific structure of a preferred embodiment of the present invention is shown, which comprises a pump shell10, a rotating shaft20, a rotor30, a stator40and an impeller50. A mounting cavity101and a pump cavity102which are isolated from each other are arranged in the pump shell10, the pump shell10is provided with a water inlet103and a water outlet104, and the water inlet103and the water outlet104are both communicated with the pump cavity102. Specifically, the pump shell10comprises a pump body11and a pump cover12, the above mounting cavity101is located in the pump body11, the pump cover12is rotatably mounted at a front end of the pump body11at an adjustable angle and forms the above pump cavity102in an enclosing way, and the above water inlet103and the above water outlet104are both located on the pump cover12. In the embodiment, the pump body11has a horizontal cylindrical structure. Specifically, the pump body11comprises a main barrel111and a rear cover112, and the rear cover112is hermetically mounted at a rear end of the main barrel111to form the mounting cavity101in an enclosing way. The rear cover112is provided with a line passing pipe113, and the line passing pipe113communicates the mounting cavity101with the outside, has a simple structure, and is convenient to assemble. The water inlet103is provided with a first external thread105, so as to be connected with a pumping pipe as needed. The water outlet104is provided with a second external thread106. The water outlet104is detachably provided with a water discharge connector60, the water discharge connector60is provided with a threaded sleeve61, and the threaded sleeve61is threadedly connected with the second external thread106for fixing, so as to be quickly connected with a water discharge pipe. Meanwhile, a multi-caliber universal water discharge connector60may be provided, thus having diversity and aesthetics. Moreover, the water inlet103is coaxially arranged with a rotation center of the pump cover12, so that water inflow is smooth. The water outlet104is perpendicular to the rotation center of the pump cover12, so that water discharge is smooth. A convex ring107radially extends from an outer side surface of a front end of the pump body11, a plurality of hook portions108extend from a rear end of the pump cover12, and the plurality of hook portions108hook the convex ring107and rotate back and forth along the convex ring107, so that the pump cover12rotates steadily. A sealing ring13is clamped between the rear end of the pump cover12and the front end of the pump body11, so as to realize hermetic mounting. Moreover, the outer side surface of the front end of the pump body11is concavely provided with an annular groove109, the annular groove109is located on a front side of the convex ring107, and the sealing ring13is embedded in the annular groove109for fixing, so that the sealing ring13is mounted firmly. The pump body11is provided with a handle seat70, and a top portion of the handle seat70is provided with a handle71, so as to carry by the handle. The handle seat70is detachably sleeved on the pump body11, which is convenient for disassembly and assembly. Moreover, a bottom portion of the handle seat70is provided with a sucker72, so as to be adsorbed and fixed with the outside. Moreover, various corners of the bottom portion of the handle seat70are all provided with a clamping groove701, and one sucker72is clamped and fixed in each clamping groove701, so that the adsorption with the outside is firmer. The bottom portion of the handle seat70is provided with a cavity702, and a plurality of suckers72are located on an outer periphery of the cavity702, thus further improving the firmness of the adsorption with the outside. The handle seat70has an integrated3D molded structure, which is simple in structure and good in intensity. A front side of the pump cover12is provided with a filter cover80, and the filter cover80covers the water inlet103. The filter cover80is detachably mounted on the front side of the pump cover12, which may be disassembled and assembled as needed, thus being flexible and convenient to use. Moreover, the filter cover80is cylindrical, and has an integrated3D molded structure, which is simple in structure and good in intensity. The rotating shaft20is rotatably arranged in the pump shell10, a front end of the rotating shaft20is located in the pump cavity102, and a rear end of the rotating shaft20is located in the mounting cavity101. The rotor30is arranged at the rear end of the rotating shaft20and located in the mounting cavity101. The stator40is arranged in the mounting cavity101and encloses an outer periphery of the rotor30. The stator40is cooperated with the rotor to make the rotor30rotate. The impeller50is arranged at the front end of the rotating shaft20and located in the pump cavity102, an input side of the impeller50is opposite to the water inlet103, and an output side of the impeller50is opposite to the water outlet104. In the embodiment, the impeller50is fixedly mounted at the front end of the rotating shaft20through a clamping spring51. A working principle of the embodiment is described in detail as follows. During working, the product may be integrally immersed in water, and a water pipe is connected with the water discharge connector60. When a power supply is turned on, the stator40is cooperated with the rotor30to make the rotor30rotate, so that the rotating shaft20drives the impeller50to rotate at a high speed. After being filtered by the filter cover80, water enters the pump cavity102from the water inlet103, under drive of the impeller50, the water is pressurized to be output from the water outlet104, and then the water is output from the water pipe to a designated place. By manually rotating the pump cover12left and right, a water discharge direction may be changed. Keys of design of the present invention are that: firstly, the water inlet and the water outlet are both arranged on the pump cover, and the pump cover is rotatably mounted at the front end of the pump body at the adjustable angle, so that the water discharge direction can be adjusted at any angle according to the needs of use, and the water pump can work normally, thus bringing convenience to use. Secondly, the handle seat is provided, the bottom portion of the handle seat is provided with the sucker, and the handle seat may be used for transportation in advance, thus being very convenient, and the sucker may be used for equilibrium adsorption on a plane, thus improving a pumping stability of the water pump. Technical principles of the present invention are described above with reference to specific embodiments. These descriptions are only for the purpose of explaining the principles of the present invention, and cannot be interpreted as limiting the scope of protection of the present invention in any way. Based on the explanation herein, those skilled in the art may think of other specific embodiments of the present invention without going through any creative work, which will all fall within the scope of protection of the present invention. | 7,958 |
11859639 | DETAILED DESCRIPTION OF THE INVENTION Exemplary embodiments of the present invention will be described in detail hereafter with reference to the accompanying drawings. FIG.1is a perspective view of fan motor according to an embodiment of the present invention,FIG.2is an exploded perspective view of the fan motor according to an embodiment of the present invention, andFIG.3is a cross-sectional view showing the inside of the fan motor according to an embodiment of the present invention. A fan motor according to the present embodiment may include: a motor housing1; a rotary shaft2, a rotor3mounted on the rotary shaft2; a stator5disposed inside the motor housing1and surrounding the rotor3; an impeller6connected to the rotary shaft2; and an impeller cover7surrounding the outer circumferential surface of the impeller6. The impeller cover7may include a coating layer74for minimizing the gap between the impeller6and the impeller cover7. A space S1where the rotor3and the stator5are accommodated may be formed inside the motor housing1. A bearing housing portion11for supporting a bearing4to be described below may be formed at the motor housing1. An air outlet12through which air flowing in the space S1by the impeller6is discharged to the outside may be formed at the motor housing1. The rotor3and the bearing4may be mounted on the rotary shaft2and the rotary shaft2may constitute a rotary shaft assembly R together with the rotor3and the bearing4. The rotary shaft2may be elongated into the impeller cover7from the inside of the motor housing1. A portion of the rotary shaft2may be positioned inside the motor housing1and the other portion of the rotary shaft2may be positioned inside the impeller cover7. The rotary shaft2may be positioned inside the motor housing1and inside the impeller cover7. The rotary shaft2, which rotates with the rotor3, may be supported by the bearing4. The rotary shaft2may be rotated by the rotor3while being rotated by the bearing4. The impeller6may be connected to the rotary shaft2, and when the rotary shaft2is rotated, the impeller6may be rotated inside the impeller cover7. The rotor3may be mounted to surround a portion of the rotary shaft2. The rotor3may be rotatably positioned in the stator5. The rotor3may be formed in a hollow cylindrical shape. The rotor3may include a rotor core31fixed to the rotary shaft2, a magnet32installed on the rotor core31, and a pair of end plates33and34fixing the magnet32. The rotor3may be mounted to surround a portion between an end and the other end of the rotary shaft2. At least one bearing4may be installed on the rotary shaft2. A pair of bearings4A and4B may be disposed on the rotary shaft2. Any one4A of the pair of bearings4may be supported by the bearing housing portion11formed at the motor housing1. The other one4B of the pair of bearings4may be supported by a bearing housing portion91formed at a motor bracket9. The stator5may be mounted in the motor housing1. The stator5may be mounted in the motor housing1and may be disposed in the motor housing1to surround the rotor3. The stator5may be mounted in the motor housing1by fasteners such as screws. The stator5may be formed in a hollow cylindrical shape. The stator5may be mounted to surround the outer circumferential surface of the rotor3. The stator5may be configured as an assembly of several members. The stator5may include a stator core51, a pair of insulators52and53combined with the stator core51; and coils54disposed at the insulators52and53. The impeller6may be configured as a centrifugal impeller that axially suctions air and centrifugally blows the air and may be configured as a mixed-flow impeller that axially suctions air and blows the air diagonally between the axial direction and the centrifugal direction. The impeller6may include a hub61connected to the rotary shaft2and at least one blade62formed on the outer surface of the hub61. The hub61may be connected to an end, which is positioned inside the impeller cover7, of the rotary shaft2. A hole in which the rotary shaft2is inserted may be formed at the center of the hub61. The hub61may be formed in a shape of which the outer diameter gradually increases toward the rotor3. In the hub61, the outer diameter of the end close to an air inlet71is the smallest and the outer diameter of the other end close to the rotor3may be may be the largest. The maximum outer diameter of the hub61may be the outer diameter of the end close to the rotor3of both ends of the hub61. A plurality of blades62may be formed on the outer surface of the hub61and the plurality of blades62may be spaced apart from each other in the circumferential direction of the impeller6. The blade may be formed in a curved plate shape and both sides thereof may include a pressure-side surface and a suction-side surface. The blade62may be formed in a3D shape and may include a leading edge63at the foremost end in the airflow direction and a trailing edge64at the rearmost end in the airflow direction. The blade62may have a blade tip65positioned at the outermost side from the center axis of the hub61. The blade tip65may be an outer tip positioned at the outermost side of the blade62. In the blade62, the leading edge63and the trailing edge64may be connected to the blade tip65. The blade tip65may connect the farthest tip from the hub61of the leading edge63and the farthest tip from the hub61of the trailing edge64. The blade tip65may include an air inlet-facing area65A (seeFIG.4) axially facing the air inlet71and a coating layer-facing area65B (seeFIG.4) axially facing the coating layer74. The entire blade tip65may radially face the coating layer74. When the impeller6is rotated, some of air blown by the impeller6can slide over the blade tip65by the pressure difference between the pressure-side surface62A of the blade62, and this flow may be leakage flow. When the impeller6is rotated, relatively high pressure may be generated around the pressure-side surface62A and relatively low pressure may be generated around the suction-side surface62B. When the tip clearance between the blade tip65and the inner circumferential surface of the impeller cover7is large, air around the pressure-side surface62A can slide over the blade tip65and move around the suction-side surface62B and a vortex may be formed around the suction-side surface62B. When the tip clearance between the blade tip65and the impeller cover7is large, the amount of leakage flow is large, so it is preferable that the tip clearance is set such that leakage flow is minimized. The impeller cover7may include a coating layer74that can minimize the leakage flow. The coating layer74may be formed in advance at the shroud73before the fan motor is assembled, and a portion of the coating layer74may be ground off by the blade62of the impeller6when the fan motor is assembled. Hereafter, the impeller cover7is described in detail. The air inlet71may be formed at the impeller cover7. When the impeller6is rotated, the air outside the fan motor can be suctioned into the impeller cover7through the air inlet71. The impeller cover7may include the shroud73surrounding the outer circumferential surface of the impeller6and the coating layer74coated on the inner circumferential surface of the shroud73. The inner diameter of the shroud73may be increased in the airflow direction. The shroud73, which guides air being suctioned to the impeller6, may have a structure of which the inner radius D1of an end73A and the inner radius D2of the other end73B are different. The shroud73may be formed such that the inner radius D2of the other end73B is larger than the inner radius D2of the end73A. The shroud73may gradually increase in inner diameter from the end73A to the other end73B. The shroud73, for example, may be formed such that the entire area between the end73A and the other end73B gradually increases in inner diameter in the airflow direction. Further, the impeller6may be positioned inside the shroud73and the entire blade tip65may radially faces the shroud73. The shroud73, as another example, may include a small-diameter portion73C, a large-diameter portion73D, and an expanding portion73E. The small-diameter portion73C includes the end73A of the shroud73and may be smaller in inner diameter than the large-diameter portion73D. The air inlet72through which the air outside the fan motor flows into the shroud73may be formed in the small-diameter portion73C. The large-diameter portion73D includes the other end73B of the shroud73and may be larger in inner diameter than the small-diameter portion73C. The expanding portion73E may connect the small-diameter portion73C and the large-diameter portion73D and may be formed such that the inner diameter gradually increases. The expanding portion73E may be positioned between the small-diameter portion73C and the large-diameter portion73D in the airflow direction, air can flow into the expanding portion73E through the inside the small-diameter portion73C and can flow into the large-diameter portion73D from the expanding portion73E. Further, the impeller6may be positioned inside the small-diameter portion73C and inside the expanding portion73E, some area of the blade tip65may radially face the small-diameter portion73C, and the other area of the blade tip65may radially face the expanding portion73E. The shroud73, as another example, may include a large-diameter portion73D and an expanding portion73E without the small-diameter portion73C. In this case, the expanding portion73E may include the end73A of the shroud73, the air inlet71through which external air is suctioned into the fan motor may be formed at the expanding portion73E, and the inner diameter of the expanding portion73E may gradually increase toward the large-diameter portion73D. Further, the impeller6may be positioned inside the expanding portion73E and the blade tip65may radially faces the expanding portion73E. The shroud73may be formed integrally with the motor housing1. The coating layer74may be formed on the inner circumferential surface of the shroud73. The coating layer74is not ground through a separate grinding process and may be ground by the blade62when the fan motor is assembled. That is, a portion of the coating layer74may be cut off by the blade62when the fan motor is assembled. The coating layer74may be a kind of self-sacrifice coating. In order to be smoothly ground by the blade62, the coating layer74may include a soft polymer74A having hardness lower than the hardness of the blade62. It is preferable that the coating layer74is formed to be able to surround a portion of the leading edge63, the entire of the blade tip65, and a portion of the trailing edge64. To this end, the height H1of the coating layer74may be larger than the height H2of the impeller6. The height H1of the coating layer74and the height H2of the impeller6may be the axial length of the fan motor. Further, when the fan motor is assembled, the coating layer may be disposed to surround the entire outer circumferential surface of the impeller6. The coating layer74will be described in more detail later. On the other hand, the maximum outer diameter of the impeller6may be larger than the diameter of the air inlet71. The maximum outer diameter of the impeller6may be larger than the minimum inner diameter of the small-diameter portion73C and may be smaller than the maximum inner diameter of the expanding portion73E. The maximum outer diameter of the impeller6may be the larger outer diameter of the maximum outer diameter of the hub61and the maximum outer diameter of the blade62. The maximum outer diameter of the blade62may be double the maximum distance between the rotational center axis of the impeller6and the blade tip65. The closer the blade tip65goes to the rotor3, the farther the blade tip65may go away from the rotational center axis of the impeller6, and the maximum outer diameter of the blade62may be double the distance from the rotational center axis of the impeller6to the tip that is the farthest from the hub61of the blade tip65. That is, the maximum distance between the center axis of the impeller6and the blade tip65of the blade62may be the maximum radius of the impeller6and the maximum radius of the impeller6may be larger than the radius of the air inlet71. On the other hand, the fan motor may further include a diffuser8that guides air blown by the impeller6. The air blown from the impeller6may be guided by the diffuser8. The diffuser8may be disposed inside the impeller cover7. The diffuser8may be mounted on at least one of the motor housing1and the motor bracket9to be described below. A gap through which air that is guided to the diffuser8can pass may be formed between the diffuser8and the impeller cover7. The diffuser8may partially face the impeller6and a gap may be formed between a surface of the diffuser8and the diffuser-facing surface of the impeller6. The diffuser8may have a hole81surrounding the outer circumferential surface of the bearing housing portion9. The diffuser8may include a body part85being larger in size than the impeller cover7and positioned inside the impeller cover7, and diffuser vanes86protruding from the outer circumferential surface of the body part85. The body part85can guide air centrifugally blown from the impeller6to the inner circumferential surface of the impeller cover7, between the impeller6and the stator5, and the air that has passed through the outer circumferential surface of the body part85and the inner circumferential surface of the impeller cover7can be guided between the body part85and the stator5. The diffuser vanes86may protrude from the body part to be positioned between the outer circumferential surface of the body part85and the impeller cover7. The diffuser vane86can convert the dynamic pressure of the air, which has passed through the impeller6, into static pressure. The diffuser8may further include guide vanes87that guide air to the rotor3and the stator5. The guide vanes87may be formed behind the diffuser vanes86in the airflow direction. Further, the fan motor may further include the motor bracket9supporting the bearing4. The motor bracket9may be combined with at least one of the motor housing1and the diffuser8. The bearing housing portion91accommodating the bearing4may be formed at the motor bracket9. A rotary shaft-through hole92through which the rotary shaft2passes may be formed at the bearing housing portion91. The motor bracket9may be mounted in the motor housing1. The motor bracket9may further include a fastening portion94fastened to the motor housing1by fasteners93such as screws. The motor bracket9may include at least one connecting portion95connecting the fastening portion94and the bearing housing portion91. FIG.4is a cross-sectional view enlarging the portion A shown inFIG.3,FIG.5is a view showing that a coating layer without a bead is ground by a blade,FIG.6is a view showing that a coating layer according to an embodiment of the present invention is ground by a blade, andFIG.7is a view illustrating in detail the portion that is ground by a blade in a coating layer. As described above, the coating layer74is not ground through a separate grinding process and may be ground by the blade62when the fan motor is assembled. In this case, that is, the portion that is ground by the blade62of the coating layer74may include a portion being in contact with the blade62. In more detail, the blade62applies stress to the coating layer74in contact with the coating layer74, the coating layer74is not accurately ground only at the portion being in contact with the blade62, but may be ground even at a portion of the portion not being in contact with the blade62. Accordingly, a fine gap may be formed between the blade62and the ground surface. In order to minimize the gap, the coating layer74may include a polymer74ahaving hardness lower than the hardness of the blade62and a plurality of beads74B mixed with the polymer74A and having hardness higher than the polymer74A. The polymer74A may include soft polymer resin. The hardness of the polymer74A may be lower than the hardness of the blade62. Accordingly, the polymer74A can be easily ground by the blade62, and in this process, damage to the blade62can be minimized. The beads74B may have hardness higher than the polymer74A. That is, the polymer74A may be soft and the beads74B may be hard. The plurality of beads74B may be mixed with the polymer74A and uniformly distributed in the polymer74A. Further, some of the plurality of beads74B may be positioned on the surface of the polymer74A. The plurality of beads74B can prevent the coating layer74from being excessive cut off while the coating layer74is ground by the blade62. For example, a coating layer74′ without a bead may be composed of only a soft polymer74A, as shown inFIG.5. In this case, when the blade62comes in contact with the coating layer74′, stress of the blade62is transmitted into the soft polymer74A, so crack may be generated in the polymer74A. Since the cracks are randomly generated, a portion of the polymer74A may be cut off in a lump, depending on the shape of the cracks. Accordingly, the gap k between the ground surface74C′ formed on the polymer74A and the blade62may increase and the efficiency of the fan motor may be reduced due to leakage flow of the air flowing through the gap k. However, as shown inFIGS.6and7, when the coating layer74includes beads74B and the blade62comes in contact with the coating layer74, cracks C that are formed by stress of the blade62may be formed to connecting at least some of a plurality of beads74B to each other. This is because the stress that is applied into the soft polymer74A concentrates around the hard beads74B. That is, unlike the coating layer without the bead74B, the cracks C formed in the polymer74A of the coating layer according to the present invention may be formed in accordance with a plurality of beads74B and a portion GR of the polymer74A may be separated along the cracks C. Accordingly, the polymer74A can be cut off in a relative lump and the gap between the ground surface74C and the blade62can be minimized. Accordingly, the coating layer74can be precisely cut. When the coating layer74is ground by the blade62, some of a plurality of beads74B may be positioned on the ground surface74C of the polymer74A. In this case, the beads74B positioned on the ground surface74C of the polymer74A may be the beads74B connected with the cracks C in the ground portion. On the other hand, referring toFIG.4, the coating layer74may include a first area A1having a first thickness T1and a second area A2having a second thickness T2smaller than the first thickness T1and having a step from the first area A1. The second area A2may continue after the first area A1in the airflow direction. In this case, the plurality of beads74B may be uniformly distributed in the first area A1and the second area A2. Further, the coating layer74may further include a third area A3having the first thickness T1and continues after the second area A2. In this case, the plurality of beads may be uniformly distributed in the first area A1, the second area A2, and the third area A3. It is preferable that the coating layer74is formed to having a thickness that does not increase much the weight of the fan motor and considering the grinding depth by the blade62and the assembly tolerance of the impeller6. The thickness of the coating layer74may mean the thickness of the polymer74A. The coating layer74may have a uniform thickness in the airflow direction before the fan motor is assembled. In more detail, the coating layer74may be formed with the first thickness on the inner circumferential surface of the shroud73before the fan motor is assembled. The first thickness T1may be the same as or larger than the minimum distance between the inner circumferential surface of the shroud73and the blade62. For example, the minimum distance between the inner circumferential surface of the shroud73and the blade62may be 0.3 mm and the first thickness T1may be 0.3 mm to 0.6 mm. When the first thickness T1is smaller than 0.3 mm, the coating layer74may not be ground by the blade62, and when the first thickness T1is larger than 0.6 mm, the coating layer74may not be smoothly ground by the blade62. When the impeller6is rotated, the blade62can come in contact with a portion of the coating layer74. In this case, in the coating layer74a portion including the portion brought in contact with the blade62can be ground by the blade62. The ground portion of the coating layer74can decrease in thickness from the first thickness T1to the second thickness T2and the non-ground portion can maintain the first thickness T1. The portion not ground by the blade62of the coating layer74may be the first area A1and the third area A3and the remaining portion after a portion of the coating layer74is ground by the blade62may be the second area A2. The second area A2may include the ground surface74C. In more detail, the surface of the second area A2may be the ground surface74C. Accordingly, some of the plurality of beads74B included in the coating layer74may be positioned on the surface of the second area A2. Meanwhile, the second thickness T2of the second area A2may be uniform or changed in the airflow direction. When the second thickness T2of the second area A2is changed in the airflow direction, the thickness of the thickest portion of the second area A2may be smaller than the first thickness T1of each of the first area A1and the third area A3. Further, when the second thickness T2of the second area A2is changed in the airflow direction, the average thickness of the second area A2may be smaller than the first thickness T1of each of the first area A1and the third area A3. Further, the first thickness T1of the first area A1may be uniform or changed in the airflow direction. Further, the first thickness T1of the third area A3may be uniform or changed in the airflow direction. When the thickness of the first area A1and the thickness of the third area A3are each changed in the airflow direction, the thickness of the thickest portion of the second area A2may be smaller than the average thickness of the first area A1and the average thickness of the third area A3. The average thickness of the second area A2may be smaller than the average thickness of the first area A and the average thickness of the third area A3. Since the plurality of beads74B included in the coating layer74are uniformly distributed, the number of the beads74B positioned in the second area A2may be smaller than the number of the beads74B positioned in the first area A1or the third area A3, depending on the thickness differences of the areas A1, A2, and A3. The number of the beads74B may mean the number of beads included in a cross-section cut in the thickness direction of each of the areas A1, A2, and A3. The blade62of the impeller6may radially face the small-diameter portion73C (seeFIG.3) and the expanding portion73E (seeFIG.3) of the shroud73, and a portion of the portion coated on the inner circumferential surface of the small-diameter portion73C and a portion of the portion coated on the inner circumferential surface of the expanding portion73E of the coating layer74may be ground by the blade62. In grinding by the blade62described above, the first area A1and the third area A3that are non-ground portions may be positioned with the second area A2that is a ground portion therebetween. Further, the blade62of the impeller6may radially face the second area A2. When the shroud73includes all the small-diameter portion73C and the large-diameter portion73D (seeFIG.3) and the expanding portion73E, the second area A2may be formed on the inner surface of the small-diameter portion73C and the inner surface of the expanding portion73E or on the inner surface of the expanding portion73E. In this case, the second area A2may be formed on a portion of the inner surface of the small-diameter portion73C and may be formed on a portion or the entire of the inner surface of the expanding portion73E. However, when the shroud73includes the large-diameter portion73D and the expanding portion73E without the small-diameter portion73C, the second area A2may be formed in the inner surface of the expanding portion73E. In this case, the second area A2may be formed on a portion of the inner surface of the expanding portion73E. Hereafter, the material of the blade62, the material of the polymer74A, and the beads74B are described. The blade62may be made of a nonmetallic material. The blade62may include polyether ether ketone (hereafter, referred to as PEEK). The blade62may be formed integrally with the hub61by injection molding, and in this case, the entire impeller6may be made of a nonmetallic material, particularly, PEEK. PEEK, which is engineering plastic developed by ICI in U.K., is engineering plastic having excellent heat resistance, hardness, and flameproof ability. The blade62may include PEEK 1000, PEEK HPV, PEEK GF30, PEEK CA30, etc., and may have tensile strength of 100 MPa, elongation of 55%, and compression strength of 128 Mpa. The polymer74A may be lower in hardness than the impeller6that is made of a nonmetallic material, particularly, the blade62, and can be ground by the blade62. It is preferable that the polymer74A is made of a soft material having hardness of 80% or less of the hardness of the blade62. The polymer74A may be synthetic resin. The polymer74A may be a material having low bending hardness. The polymer74A may include silicon having hardness lower than that of PEEK. For example, the polymer74A may include Polydimethylsiloxane (PDMS). The silicon has a meaning including silicon compounds. In this case, the Shore hardness of the polymer74A may be 30 to 50. In more detail, the polymer74A may include silicon-based resin having Shore hardness of 30 Shore A to 50 Shore A. When the hardness of the polymer74A is less than Shore 30A, the polymer74A is severely worn, so the gap between the coating layer74and the blade62may increase and the efficiency of the fan motor may be deteriorated. Further, when the hardness of the polymer74A exceeds Shore 50A, grinding by the blade62may not be smoothly performed or the blade62may be worn. Accordingly, it is preferable that the polymer74A has hardness of 30 Shore A to 50 Shore A. However, the hardness is not limited thereto and the polymer74A may include Teflon having hardness lower than PEEK. In this case, the polymer74A may include polytetra fluoro ethylene (PTFE) or ethylene tetrafluoroethylene (hereafter, referred to as ETFE). Meanwhile, the beads74B may be higher in hardness than the polymer74A and may concentrate stress that is transmitted into the polymer74A by the blade62, thereby forming cracks C in the polymer74A. The bead74B may be hard and the polymer74A may be soft. The beads74B may include at least one of metal and ceramic. The beads74B may be metal powder or ceramic powder. For example, the beads74B may include an aluminum oxide that is a kind of ceramic. The diameter of the beads74B may be smaller than the length corresponding to the thickness of the polymer74A. The diameter of the beads74B may be smaller than the length corresponding to the second thickness T2of the polymer74A. When the shapes of the beads74B are not uniform, the diameter of the beads74B may mean the diameter d of a circumscribed circle R of the beads74B. The diameter of the beads74B may be 0.01 mm to 0.1 mm. When the diameter of the beads74B is less than 0.01 mm, the cohesion between the plurality of beads74B excessively increases, so they may not be uniformly distributed and the manufacturing cost of the beads74B may increase. Further, when the diameter of the beads74B exceeds 0.1 mm, the coating layer74may be excessively cut off by grinding by the blade62. In more detail, when the diameter of the beads74B is larger than 0.11, the forming density of the cracks C may be relatively reduced in comparison to when the diameter of the beads74B is 0.1 mm or less. That is, the cracks C may be relatively sparsely formed and a portion of the polymer74A may be cut off in a large lump by the shape of the cracks C. Further, while the coating layer74is ground, the beads74B may be cut off the polymer74A and grooves may be formed on the polymer74A by cutting-off of the beads74B. In this case, when the diameter of the beads74B is larger than 0.1 mm, the sizes of the grooves are also large, so the gap between the grooves and the blade62may be increased. It is preferable that the beads74B are included in the coating layer74with weight density such that the blade62is not damaged and the polymer74A can be precisely ground. The coating layer74may include beads74B of 0.01 wt % to 10 wt %. Preferably, the coating layer74may include beads74B of 3 wt % to 10 wt %. When the coating layer74includes beads74B less than 3 wt %, the distribution density of the beads74B is low, so the distances between the beads74B may increase and cracks C may not be smoothly formed. Further, when the coating layer74includes beads74B more than 10 wt %, the adhesion of the polymer74A decreases, so the coating layer74may not be smoothly bonded to the inner circumferential surface of the shroud73or may be separated from the inner circumferential surface. FIG.8is a flowchart showing a method of manufacturing a fan motor according to an embodiment of the present invention andFIG.9is a side view before the fan motor according to an embodiment of the present invention is assembled. A method of manufacturing a fan motor of the present embodiment may include an impeller cover manufacturing step (S1), an impeller rotating step (S2), and an impeller cover combining step (S3). The impeller cover manufacturing step (S1) may be a step of manufacturing the impeller cover7by forming the coating layer74having the first thickness T1on the inner circumferential surface of the shroud73of which the inner diameter increases in an airflow direction. The impeller cover manufacturing step (S1) may be formed in a preparation process before the fan motor is assembled and the impeller cover7may be provided to the assembly line of the fan motor with the coating layer with the first thickness T1formed on the inner circumferential surface of the shroud73. The polymer74A of the coating layer may be a soft material having hardness lower than the hardness of the blade62and the beads74B may be a hard material having hardness higher than the polymer74A. The blade62of the impeller6that is rotated in the impeller rotating step (S2) may be made of PEEK. The polymer94A of the coating layer74that is coated in the impeller cover manufacturing step (S1) may be synthetic resin such as silicon and the beads74B may be metal such as alumina. The coating layer74may be formed coating the polymer74A mixed with the beads74B on the inner circumferential surface of the shroud73. The coating layer74may be formed on the inner circumferential surface of the shroud73by spray coating. However, the coating method of the coating layer74is not limited thereto. For example, the coating layer may be formed on the inner circumferential surface of the shroud73by electrostatic painting. The detailed coating process of the coating layer74may include a process of adding and mixing the polymer74A and the beads74B, a process of repeatedly spray-coating the polymer74A mixed with the beads74B to the inner circumferential surface of the shroud73, and a process of firing the polymer73A coated on the inner circumferential surface of the shroud73. In coating of the coating layer74described above, the coating layer74may be formed with a uniform first thickness T1throughout the inner circumferential surface of the shroud73. The impeller rotating step (S2) may be a step rotating the impeller6having the blade62on the hub61while inserting the impeller6into the impeller cover7, as shown inFIG.9. When the impeller6is inserted and rotated, the impeller6can be forcibly fitted into the impeller cover7with the impeller6and the shroud73aligned with concentric axis O, and the blade tip65of the blade62can grind a portion of the coating layer74into the second thickness T2smaller than the first thickness T1by rubbing on a portion of the coating layer74. In this grinding process, the polymer74A of the coating layer74can be ground along cracks C formed to connect at least some of a plurality of beads74B and the coating layer74can be very precisely machined such that the gap between the ground surface74C of the polymer74A and the blade62of the impeller6is small. In the grinding described above, the coating layer74may include the first area A1and the third area A3not ground by the blade62and a second area A1ground by the blade62, and the blade62may radially face the second area A1. In more detail, the blade62may radially face the surface of the second area A2that is the ground surface. The second area A2may be an area recessed with a thickness smaller than the thickness of the first area A1and the third area A3, and an end thereof may be stepped from the first area A1in the airflow direction and the other end may be stepped from the third area A3in the airflow direction. As described above, when the second area A2is stepped from the first area A1and the third area A3, the interface A12of the first area A1and the second area A2, in the first area A1, may axially cover the outer tip of the leading edge63. The outer tip of the leading edge63may the farthest tip fro the hub61of the leading edge63. Further, the interface A23between the second area A2and the third area A3, in the third area A3, may radially cover the outer tip of the trailing edge64. The trailing edge64may be the farthest tip from the hub61. In the coating layer74, a blade tip accommodating groove G in which at least a portion of the blade tip65is accommodated may be formed between the interface A12of the first area A1and the second area A2and the interface A23of the second area A2and the third area A3. The coating layer74having the second thickness T2remains between the blade tip65of the blade62and the inner circumferential surface of the shroud73, and a minimum gap is formed between the blade tip65and the coating layer74. The impeller cover combining step (S3) may be a step of coupling the impeller cover7to the motor housing1. The impeller cover7may be fastened to the motor housing1with the gap formed by an adhesive member such as an adhesive or a fastener such as a screw, and the gap between the impeller6and the impeller cover7may be maintained without expanding. FIG.10is a cross-sectional view showing a second area of a coating layer of a fan motor according to another embodiment of the present invention. Hereafter, the repeated configuration is omitted and the difference from the above description is mainly described hereafter with reference toFIGS.10and3. In a fan motor according to the present embodiment, the rotary shaft2may be eccentrically disposed with respect to the center axis O of the shroud73. In more detail, the center axis P of the rotary shaft2and the center axis O of the shroud73may be eccentric without meeting. The center axis P of the rotary shaft2and the center axis O of the shroud73may be virtual axes. Since the impeller6is connected to the rotary shaft2and rotated, the center axis P of the rotary shaft2may mean the center axis of the impeller6and the impeller6and the shroud73may not be concentric. By this configuration, the second area A2of the coating layer74may be non-uniformly ground in the inner circumferential direction of the shroud73. That is, a portion of the second area A2may be ground relatively deep and the other portion of the second area A2may be ground relatively thin. That is, the second thickness T2of the second area A2may be changed in the inner circumferential direction of the shroud73. The second thickness T2may change from the maximum thickness t2ato the minimum thickness t2bin the inner circumferential direction of the shroud73. As an example of eccentric arrangement of the impeller6and the shroud73, the impeller6and the shroud73that are coaxially maintained when the fan motor is assembled may become eccentric to each other due to vibration etc. by long-time use of the fan motor. Before eccentricity is generated between the center axis P of the impeller6and the center axis O of the shroud73, the blade tip65of the blade62can rotate along a first virtual path Ri and grind the second area A2. Thereafter, when eccentricity is generated between the center axis P of the impeller6and the center axis O of the shroud73, the blade tip65of the blade62can rotate along a second virtual path Rf and additionally grind a portion of the second area A2. In this case, the maximum thickness t2aof the second thickness T2of the second area A2may be the same as the thickness of the second area A2grounded by the blade62before eccentricity is generated between the center axis P of the impeller6and the center axis O of the shroud73. Further, the second thickness T2of the second area A2may be formed at the portion where the center axis P of the impeller6is eccentric to the center axis O of the shroud73and the second area A2is additionally ground. When the center axis P of the impeller6is eccentric to the center axis O of the shroud73, a gap K may be formed between the blade62and the second area A2. The gap K may be formed between a portion of the inner circumference of the second area A2and the blade tip65. The gap K may change in the circumferential direction of the impeller6. The gap K may be formed between the area having the maximum thickness t2aof the second thickness T2of the second area A2and the second movement path Rf. As another example of eccentric arrangement of the impeller6and the shroud73, the rotary shaft2of the impeller6may be forcibly inserted eccentrically to the center axis O of the shroud73when the fan motor is assembled. The blade tip65of the blade62can rotate along the second virtual path Rf and can grind at least a portion of the second area A2. In this case, at least a portion of the second area A2facing the impeller6in the radial direction of the impeller6may have the second thickness T2smaller than the first thickness T1. That is, at least a portion of the second area A2can be ground to have the second thickness T2by the blade62of the impeller6of which the blade tip65rotates along the second virtual path Rf. When there is severe eccentricity between the center axis P of the impeller6and the center axis O of the shroud73, the thickness of a portion of the second area A2may be the same as the first thickness that is the thickness of the first area A1. That is, the maximum thickness t2aof the thickness of the second area A2may be the same as the first thickness T1. This is because the blade62of the impeller6being eccentric to the shroud73does not grind a portion of the second area A2. In this case, the gap K formed between the blade62and the second area A2can be changed in the circumferential direction of the impeller6and may be formed between the area having the same thickness as the first thickness T1of the second thickness T2of the second area A2and the second movement path Rf. The above description merely explains the spirit of the present invention and the present invention may be changed and modified in various ways without departing from the spirit of the present invention by those skilled in the art. Accordingly, the embodiments described herein are provided merely not to limit, but to explain the spirit of the present invention, and the spirit of the present invention is not limited by the embodiments. The protective range of the present invention should be construed by the following claims and the scope and spirit of the invention should be construed as being included in the patent right of the present invention. | 40,068 |
11859640 | DETAILED DESCRIPTION OF THE DISCLOSURE FIG.1shows a perspective view of a fan1according to the disclosure of axial design with a housing2. A guide device15is, in an embodiment, made integral with the housing2by plastic injection molding, and in the exemplary embodiment essentially consists of a hub ring4, an outer ring5, inner guide blades3extending in between and outer guide blades3a, which extend between the outer ring5and the housing2. In the assembled state of the fan according to the disclosure, this guide device15is arranged downstream of an impeller (not visible) within the housing2, so that an air duct (outer flow-through region)6is created between the guide device15or its outer ring5and the wall of the housing2, through which part of the air flowing out of the impeller is directed. Another part of the air flowing out of the impeller is guided through the inner flow-through region7, which, seen in the span direction, is limited towards the axis by the hub ring4, and which, seen in the span direction, is bounded towards the outer flow-through region6by the outer ring5. The inner flow-through region7is traversed by inner guide blades3(in the exemplary embodiment 17 pieces, in an embodiment 9-23 pieces), which stabilize the swirling flow close to the axis exiting the impeller, by reducing the twist in the flow. This increases the efficiency. The hub ring4and the outer ring5run essentially over the entire circumference around the axis. The hub ring4surrounds an inner receiving region8in which, for example, the drive motor of the fan is arranged. The receiving region8is not traversed or is only traversed by a small air volume flow (0.1%-2% of the total air volume flow), in order to be able to remove the waste heat produced by the engine. The flow through the receiving region8can also take place counter to the main conveying direction, in particular if it is driven by a pressure difference between the outflow and inflow sides. The outer flow-through region6has a small number of outer guide blades3a, which in an embodiment provide the static connection of the outer ring5to the housing2. Due to the small number of outer guide blades3ain this region, little additional noise is caused in this region as a result of the interaction of the flow emerging from the impeller with the outer guide blades3a. A large number of free-standing guide elements16are attached to the inner wall of the housing2, in the exemplary embodiment 54 pieces, in another embodiment 30-100 pieces. They are, in an embodiment, integrally connected to the housing2, for example by plastic injection molding. A metal casting is also conceivable. It is also conceivable that free-standing guide elements made of plastic or metal are glued, welded or the like into a housing. The free-standing guide elements16are attached in a region on the housing wall on the inflow side of the guide device15, but can also overlap with it, as seen in the axial direction. It is of importance that the free-standing guide elements16are mounted essentially directly downstream of the impeller (not shown here) at a short distance, which is, in an embodiment, no greater than the axial extent of the corresponding free-standing guide element16. They have a free end facing away from the wall of the housing2and protrude from the wall of the housing2at only a relatively small height. The free-standing guide elements16ensure stabilization of the, depending on the operating point, strongly swirling flow in the region downstream of the radial gap between impeller and housing2(see alsoFIG.6in particular) and thus help to prevent flow separation and/or turbulence on the inner wall of the housing in the region of the impeller and downstream of it, at least to reduce it, or to transport it away in an accelerated manner in the direction of flow. Overall, a fan is obtained, which is quiet and has a high degree of efficiency, namely as a result of the flow stabilization or the flow acceleration in the direction of flow through the free-standing guide elements16on the wall of the housing2, which in particular can improve the effectiveness of the outer diffuser10integrated in the housing2. FIG.2shows the fan1with the housing2according to the disclosure fromFIG.1in a side view and in a section on a plane through the axis. The impeller19, the motor34as well as the guide device15of the fan are readily seen. In a section through the guide device15, the outer flow-through region6with the outer guide blades3a, the inner flow-through region7with the inner guide blades3and a receiving region8within the hub ring4can be seen. The impeller19is arranged upstream of the guide device15. When the fan1is in operation, the air flows approximately from left to right in this view, firstly through the inlet nozzle9integrated into the housing2, then through the impeller19before it is divided into the outer flow-through region6and the inner flow-through region7, in which the flow is stabilized by outer guide blades3aand inner guide blades3(especially in the inner flow-through region7) and in which kinetic energy of the flow is converted into pressure energy. In the exemplary embodiment, both the inner guide blades3and the outer guide blades3a, in a section on a cylinder jacket coaxial to the fan axis, have an inflow edge angle on their inflow-side edge facing the impeller19that optimally matches the flow angle of the flow emerging from the impeller19and impinging on the outer guide blades3aand the inner guide blades3. The inflow edge angle measured relative to a plane through the axis is, in an embodiment, in a range between 20° and 70°. In an embodiment, the inner guide blades3and/or the outer guide blades3ahave a rounded inflow edge, and further include a variable thickness with a profile similar to that of an airfoil or a drop. The free-standing guide elements16are attached to the wall of the housing2in a front region of the guide device15in the flow direction or in front of the guide device15. They stabilize the flow flowing from the impeller19which is subject to strong twisting in the region of the outer wall of the housing2and/or accelerate it in the direction of flow and prevent or reduce separation or turbulence. As a result, blockage effects of the outer flow-through region6that are harmful to the efficiency and the air output are prevented, or at least reduced, by large detachment regions. There is a provision18for fastening a motor34in the region of the receiving region8within the hub ring4. The motor34, shown schematically, is attached thereto. The guide device15provides the connection of the motor34and, indirectly via this, also of the impeller19to the housing2. The motor34is connected to the guide device15on the stator side. On the rotor side, the motor34is connected to the impeller19by a fastening provision30. The impeller19consists essentially of a hub ring21and blades22attached thereto. The hub ring21is, in an embodiment, designed in such a way that the stagger angles of the blades22can be adjusted, depending on the needs of the ventilation application in which the fan1is used. There are basically two different support concepts for the motor34with the impeller19. On the one hand, as in the exemplary embodiment shown, a supporting guide device15can be provided. That is, a guide device15having an aerodynamic function connects the motor34to the housing2and supports it. On the other hand, the motor34can be attached to the housing2with a purely mechanical connection, for example consisting of rods, wire, flat material or the like. In such a case, a guide device15may or may not be provided. In other exemplary embodiments, a guide device15can also be designed without an outer ring5and/or with only one type of guide blades, which are load-bearing. It can be seen inFIG.2that supporting guide blades (here outer guide blades3a) are arranged in the same region as the free-standing guide elements16, viewed in the direction of flow. As a result, the free-standing guide elements16in the exemplary embodiment are not evenly distributed over the circumference, but are repeatedly interrupted by the outer guide blades3a. In the exemplary embodiment, nine, or four to twelve, free-standing guide elements16are arranged between two outer guide blades3athat are adjacent in the circumferential direction. In other embodiments, the free-standing guide elements16can also be distributed uniformly or in some other way non-uniformly over the circumference. FIG.3shows the housing2of the fan1fromFIGS.1and2in a side view and in a section on a plane through the axis. The outer flow-through region6with the outer guide blades3aand the inner flow-through region7with the inner guide blades3, separated by the outer ring5, are easily recognizable. In the exemplary embodiment, both the wall of the housing2and the hub ring4have a conical shape towards the outflow end. An outer diffuser10is thus integrated in the housing2. Both the inner flow-through region7and the outer flow-through region6are designed towards their outflow end as diffusers with a widening flow cross section. This is very advantageous for the static efficiency, especially with axial fans. The outer ring5of the guide device15is also slightly conical in the embodiment, slightly widening radially in the direction of flow. The inner flow-guiding wall of the housing2essentially has the contour of an inlet nozzle9, which is followed by a cylindrical region11, followed by the radially opening diffuser region10. The impeller runs at least for the most part in the region29in the flow direction at the level of the cylindrical flow-through region11. The free-standing guide elements16can be arranged at the end of the cylindrical region11or at the beginning of the diffuser region10or in the transition region between the two regions. In any case, the free-standing guide elements16are attached downstream of the impeller19or its blades22(seeFIG.2). For demolding the housing2from a casting tool, in particular a plastic injection molding tool, there are advantages if the free-standing guide elements16are arranged completely or largely in the cylindrical region11. For an axial compactness of the fan, however, it can be advantageous if the free-standing guide elements16are arranged at least to a large extent in the diffuser region10since the diffuser region16can then directly adjoin the impeller19. On a housing2and/or a guide device15, fastening provisions, for example fastening flanges, can be integrated or attached on both the inflow and outflow side, which provisions are used to fasten the fan to a higher-level system, for example an air conditioning system. FIG.4shows a perspective view, seen from the outflow side, of a further embodiment of a fan1with a housing according to the disclosure. In this exemplary embodiment, no guide device is provided downstream of the impeller19with the blades22. A support device (not shown here), for example made of rods or flat material, must establish the connection between the motor34and the housing2in order to fix the motor34relative to the housing2. The free-standing guide elements16are distributed evenly over the circumference and run directly downstream of the impeller22or the outer ends of its blades22on the inner, flow-guiding wall of the housing2. The housing2has an outflow-side edge25at the outflow-side end of the outer diffuser10, from which the air flows out of the fan1during operation. The blades22are provided with so-called winglets20at their outer end, namely special geometric structures which positively influence the flow in the outer region of the blades22near the housing with regard to the noise emission of the fan1and/or with regard to its efficiency. FIG.5shows the fan1with the housing2according toFIG.4in a side view and in a section on a plane through the axis. It can be seen, that the free-standing guide elements16are directly connected to the impeller19or its blades22, which are attached to the hub21in the flow direction, essentially from left to right in the figure. FIG.6shows a detailed view ofFIG.5, the region of the free-standing guide elements16on the wall of the housing2being shown enlarged and provided with additional designations. A blade22of the impeller19with its winglet20can be seen at the radially outer end. The blades22run in the region of the cylindrical region11at a distance from the housing2, so that a grazing of the impeller19is excluded during operation. As a result, a radial gap of width d12is formed between the blade22and the wall of the housing2, through which a regular return flow (leakage flow) of air occurs counter to the actual flow direction. As a result, a flow region with very high velocity components in the circumferential direction and low velocity components in the flow direction is created locally near the wall of the housing2in the region of the blades22. This flow region induces high flow losses and noise emissions, and in particular can lead to a blockage effect of a subsequent diffuser. These losses can be significantly reduced by the free-standing guide elements16, which run very close to the blades22downstream of the same. These free-standing guide elements16convert part of the velocity components in the circumferential direction into those in the axial direction, namely they direct the local flow more in the axial direction. This causes a reduction in the return flow region in the region of the radial gap with width d12and thus a reduction in the losses and the generation of noise as well as the (partial) blockage of a subsequent diffuser delimited to the outside by an outer diffuser10. The free-standing guide elements16run radially only very locally in the region of the radial gap of the impeller with the width d12or only by a small factor beyond this. In practice, the free-standing guide elements16have the height h23, measured from the wall of the housing2. The ratio of h23to d12is, in an embodiment, in the range of 0.8-3. The axial distance between the free-standing guide elements16and the blade22on the wall of the housing2is, in an embodiment, less than 8 times the gap width d12. In the exemplary embodiment, the free-standing guide elements16run in the region of the outer diffuser10. In other embodiments, they can also run in the cylindrical region11. If, as in the exemplary embodiment, they run in the region of the outer diffuser10, demolding of a one-piece cast housing2is made more difficult. In an embodiment, special demolding regions (not shown) are incorporated, which allow demolding with an open-close tool with demolding directions parallel to the axis without additional slides. According to the disclosure, the free-standing guide elements16deflect the strongly swirling flow in the region of the wall of the housing2more in the axial direction. Other geometric solutions are also conceivable in other embodiments, in which the free-standing guide elements are, for example, more integrated into the contour of the housing, for example in the form of depressions, elevations or the like. It is of importance that this flow influencing takes place only near the housing wall and in the immediate vicinity of the impeller blades, where an interaction with a leakage flow of a radial gap between the impeller blades and the housing takes place. FIG.7shows a perspective view, seen from the outflow side, of a further embodiment of a housing2according to the disclosure, which has no guide devices. The free-standing guide elements16are here distributed approximately evenly over the circumference on the wall of the housing2. On its flow-guiding inner wall, the housing2essentially has an inlet nozzle9, a cylindrical region11and an outer diffuser10, which ends at the outflow-side edge25of the housing2. FIG.8shows a side view and a section on a plane through the axis26, of the housing2according toFIG.7. The free-standing guide elements16are approximately arranged in the transition region between the cylindrical region11and the outer diffuser10, and this means that they extend across the boundary between the cylindrical region11and the outer diffuser10, which is characterized in that, seen in the flow direction, it gradually widens radially. The one-sided opening angle of the contour of the outer diffuser10is approximately 12° in the exemplary embodiment, 6°-18°. FIG.9shows a detailed view fromFIG.8in the region of the fan axis, with a region of the individual free-standing guide elements16being shown enlarged and provided with additional designations. As a result of the high magnification and the view of an region close to the axis (in the projection shown), an approximately planar section of the wall of the housing2is shown. The free-standing guide elements16have an inflow edge13, which is, in an embodiment, at least approximately rounded, and an outlet edge14, which is thin compared to the rest of the profile. Viewed in cross section, the free-standing guide elements16have approximately the profiled contour of an airfoil. In other embodiments, other cross-sectional contours are also possible, for example a thin contour with an essentially constant thickness. The free-standing guide elements16have a chord length s31and an axial extent I32. In terms of values, I32is small, for example 0.2%-5% of the impeller diameter or 10%-60% of the axial extension of an impeller blade. The chord length s31is greater than I32by a factor of about 1.2-2. Viewed in the circumferential direction, adjacent free-standing guide elements16do not overlap, in order to enable easier demolding of the housing2from a casting tool. The inflow angle α27is assigned to the inflow edge13. This is the local angle there between the chord37or its tangential extension and a line parallel to the axis26. The outflow angle β28is assigned to the outflow edge14. This is the local angle there between the skeleton line37or its tangential extension and a line parallel to the axis26. The angle β28is smaller than the angle α27, in an embodiment, by at least 20°. As a result, the swirling flow is more likely to be deflected in the axial direction. In this case the free-standing guide elements16have a front end24. FIG.10shows a further detailed view fromFIG.8in the region of the section through the housing wall2at the top, with a region of the individual free-standing guide elements16being shown enlarged and provided with additional designations, The free-standing guide elements16have a blunt free end24. In the cross section shown, viewed approximately along the height of the free-standing guide elements16, the free-standing guide elements16have approximately the contour of a rectangle. However, a rounded transition region17to the wall of the housing2is formed. FIG.11shows a further embodiment of a housing2according to the disclosure in a detailed view similar to the embodiment according toFIG.10, the free-standing guide elements16being provided with a first type of winglets38aat their open end. At the free end of the free-standing guide elements16, a contour with a thickness of 1 mm to 3 mm protrudes toward the concave side of the free-standing guide elements16. In the cross section shown, viewed approximately along the height of the free-standing guide elements16, the free-standing guide elements16have an approximately L-shaped contour. FIG.12shows a further embodiment of a housing2according to the disclosure in a detailed view similar to the embodiment according toFIG.10, the free-standing guide elements16being provided with a second type of winglets38bat their open end. On the convexly curved side of the free-standing guide elements16, towards the free-standing edge, a type of chamfer is formed, so that the free-standing guide elements16taper approximately to a point towards their open end. At the outer end, however, the free-standing guide elements16are not completely pointed, but are provided with a very thin, finitely thick end. FIG.13shows a further embodiment of a housing2according to the disclosure in a detailed view similar to the embodiment according toFIG.10, the free-standing guide elements16being provided with a third type of winglets38cat their open end. On the concavely curved side of the free-standing guide elements16, towards the free-standing edge, a type of rounding is formed, so that the free-standing guide elements16appear to have a quarter-circle rounding towards their open end. The edge to the convex side of the free-standing guide elements16remains at least approximately pointed. To avoid repetition with regard to further embodiments of the fan according to the disclosure with the housing according to the disclosure, in order to avoid repetitions, reference is made to the general part of the description and to the appended claims. Finally, it should be expressly noted that the above-described exemplary embodiments of the fan according to the disclosure and of the housing according to the disclosure are used solely to explain the claimed teaching, but do not restrict it to the exemplary embodiments. LIST OF REFERENCE NUMERALS 1fan2housing3inner guide blade3aouter guide blade4hub ring, inner ring of the guide device5outer ring of the guide device6outer flow-through region7inner flow-through region8receiving region inside the hub ring9inlet nozzle10outer diffuser11cylindrical flow region of the housing12width d of the radial gap of the impeller13inflow edge of a free-standing guide element14outflow edge of a free-standing guide element15guide device16free-standing guide element17transition region of a free-standing guide element to the housing18fastening provision for motor on guide device19impeller20winglet of a blade of the impeller21hub ring of the impeller22impeller blades23height h of a free-standing guide element24front end of a free-standing guide element25outflow edge of the housing26axis of the fan27inflow angle α of a free-standing guide element28outflow angle β of a free-standing guide element29region for an impeller30provision for fastening the motor to the impeller31chord length s of a free-standing guide element32axial extension I of a free-standing guide element34motor37skeleton line of a free-standing guide element with tangential extension38a, winglets of free-standing guide38b, elements38c | 22,345 |
11859641 | Systems, apparatus, and methods according to present disclosure will now be described more fully with reference to the accompanying drawings, which illustrate various exemplary embodiments. Concepts according to the present disclosure may, however, be embodied in many different forms and should not be construed as being limited by the illustrated embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough as well as complete and will fully convey the scope of the various concepts to those skilled in the art and the best and preferred modes of practice. DETAILED DESCRIPTION Certain aspects of the present disclosure include apparatus, systems, and methods for noise abatement in equipment, such as air blowers. As used herein, “noise abatement” refers to the elimination or reduction of noise. For example, a piece of equipment may emit noise at a first intensity (decibels) during operation of the piece of equipment without the noise abatement features disclosed herein incorporated into the piece of equipment. After incorporation of the noise abatement features disclosed herein into the piece of equipment, the piece of equipment may emit noise at a second intensity (decibels) during operation of the piece of equipment, wherein the second intensity is less than the first intensity. In some embodiments, the apparatus, systems, and/or methods for noise abatement disclosed herein function to dampen the noise produced by the equipment. During propagation of sound, sound waves can be reflected, refracted, and/or attenuated by the noise abatement features disclosed herein. The apparatus, systems, and/or methods for noise abatement disclosed herein may be incorporated into equipment including, but not limited to air blowers. Air Blowers Some embodiments of the present disclosure include apparatus, systems, and methods for the abatement of noise produced by air blowers, also referred to as extracting blowers. The noise abatement apparatus, systems, and methods disclosed herein may be used in air blowers that supply air to equipment or local environments. As used herein, a “local environment” is a discrete, at least partially enclosed space. For example, the local environment may be a residence, a building, a mobile enclosure or other facility or interior space thereof. Air blowers can be used for cooling and ventilation, in sand blasting booths, and other applications. Air blowers operate to intake atmospheric air, which may include liquid and solid particles, and to separate the liquid and solid particles from the atmospheric air to generate clean air. Air blowers can be used in a variety of industries to provide cooling air to personnel, structures and equipment. In some embodiments, the air supplied is cooling air (i.e., the air is supplied to cool, for example, a piece of equipment or an environment). For example, and without limitation, in some embodiments the noise abatement apparatus, systems, and methods disclosed herein are used in air blowers that supply cooling air to electric motors for cooling the motors. However, the noise abatement apparatus, systems, and methods disclosed herein are not limited to use with air blowers that supply cooling air to electric motors, and may be used in other air blower applications as well. In some embodiments, the noise abatement apparatus, systems, and methods disclosed herein are used in an extracting blower in accordance with U.S. Pat. No. 6,648,935. For example, an extracting blower in accordance with U.S. Pat. No. 6,648,935 may be retrofitted and/or modified to include the noise abatement apparatus and/or systems disclosed herein, or an extracting blower otherwise in accordance with U.S. Pat. No. 6,648,935 may include the noise abatement apparatus and/or systems disclosed herein. With reference toFIGS.1A-1D, an air blower (also referred to as a “blower”) in accordance with at least one embodiment will now be described. Blower100includes impeller assembly102including impeller housing110. Impeller102is powered by blower motor112, such that blower motor112drives rotation of the blades (not shown) of impeller102. Blower100includes air intake housing104including air inlet108. With impeller blades rotating, impeller102draws intake air through air inlet108and into impeller housing110, optionally air is cleaned within impeller assembly102, and then impeller102expels the air from air outlet106. For example, the air may be expelled from air outlet106and into an electric motor for cooling the electric motor, into a local environment for cooling the environment, or to another location or piece of equipment. The movement of the blades of the impeller102within impeller housing110, and the movement of inlet air through air intake housing104and impeller housing110produces noise. Blower100includes multiple noise abatement components that reduce the noise emanating from blower100, relative to the noise that would emanate from the blower if the blower did not include the noise abatement components. The noise abatement components of blower100include: (1) a non-linear (e.g., circuitous or serpentine) air inlet flow path (not shown) of intake air into inlet108and from inlet108to impeller102; (2) flow modulator tube assembly114; and (3) sound damper116. The structure and operation of each of these noise abatement components will be described in more detail below with reference toFIGS.2A-3B. Noise Abatement Features in the Air Blower With reference toFIG.2A, air intake housing104is shown in isolation from the remainder of the blower. In operation, intake air enters air intake housing104through a grill118. Air intake housing104provides a sufficiently broad opening for intake air such that a low-pressure drop is maintained, lowering the risk of the intake air from becoming turbulent within air intake housing104. Air intake housing104includes angled housing walls and/or baffles positioned along the flow path of air and sound therethrough, which function to modulate the direction of flow of air therethrough and the propagation of sound therethrough. For example, as shown inFIG.2A, air intake housing104includes first baffle120positioned adjacent inlet108and second baffle122positioned opposite the inlet from the air intake housing104into the flow modulator tube assembly114. Baffles120and122contribute to the formation of a circuitous flow path of the intake air within intake housing104, such that the intake air follows a non-linear flow path within intake housing104, prior to entering flow modulator tube assembly114. FIG.2Bshows flow modulator tube assembly114, which is in fluid communication with air intake housing104and positioned for receipt of the intake air therefrom. As shown inFIGS.2B and2D, flow modulator tube assembly114includes vanes124positioned within shell126. In some embodiments, flow modulator tube assembly114includes eight vanes124. However, flow modulator tube assembly114may include more or less than eight vanes. Vanes124may function as straightening vanes, modulating the flow of intake air therethrough to conduct the intake air into the impeller102in a more uniformly-distributed and orderly manner than would occur in the absence of vanes124. In the embodiment shown inFIG.2D, flow modulator tube assembly114divides the flow of intake air into eight separate portions or modulated flow paths128, as defined by the space between adjacent vanes124. Without being bound by theory, vanes124may operate to straighten the flow of intake air by reducing the occurrence of turbulent flow of intake air. Each pair of adjacent vanes124defines a modulated flow path128therebetween through which the intake air flows. Each modulated flow path128may be isolated from other modulated flow paths of the flow modulator tube assembly114.FIG.2Cdepicts vanes124a-124harranged together, but in isolation from the shell that surrounds the vanes in the flow modulator tube assembly114. The flow modulator tube assembly disclosed herein may include vanes positioned and arranged to define modulated flow paths of equal volume, as shown, or vanes positioned and arranged to define modulated flow paths of different volumes. The vanes124may extend axially within shell126. InFIG.2D, the inlet into impeller102, from flow modulator tube assembly114, is shown, where the inlet air is drawn by the impeller blades130of impeller102. Without being bound by theory, it is believed that at least some of the sound that enters flow modulator tube assembly114may become at least temporarily trapped therein, propagating back and forth within the flow modulator tube assembly114. With reference toFIG.2E, the impeller blades130of impeller102rotate to draw air in from air intake housing104and direct air through outlet106. The impeller blades130may be arranged within the impeller housing110to direct contaminates within the intake air, such as dust or water, to the contaminate outlet132. Contaminate outlet132, or a flow path thereto, is at least partially defined by baffle wall131. In some embodiments, the impeller assembly102is arranged in a manner that is the same as or similar to the blower of U.S. Pat. No. 6,648,935 to expel contaminates. As such, impeller assembly102provides at least partially cleaned air to outlet106, where the at least partially cleaned air is provided to a piece of equipment or a local environment as intake air to that piece of equipment or local environment, for example. The rotation of impeller blades130is driven by blower motor112. For example, blower motor112, which may be an electric motor, may include or be coupled with drive shaft134. Blower motor112drives the rotation of shaft134, which is coupled with impeller plate136, such that shaft134drives the rotation of plate136. Plate136includes impeller blades130thereon, such that plate136drives rotation of impeller blades130, drawing air into impeller assembly102and pushing the air out of outlet106. Impeller blades130include one or more features that improve efficiency of blower100and reduce noise produced by blower100. For example, impeller blades130include backward-inclined blades, as shown inFIG.2E. Also, the outer tips of each blade130are bent (e.g., by approximately 20°) to reduce the tendency of air turbulence in impeller assembly102, as shown inFIG.2Eas bent tips133. With references to bothFIG.3A, the flow path of air through air blower100is depicted. Intake air109flows upwards into air intake housing104to the entrance of the flow modulator tube assembly114. The flow path for intake air109into the flow modulator tube assembly114is at an angle (e.g., a nominally 90° angle) relative to the flow path for intake air into inlet108. As shown by the broken line arrows, at least some of the intake air109impacts first baffle120within intake housing104, contributing to the circuitous flow path of the intake air109within intake housing104. Also, at least some of the intake air109impacts second baffle122within intake housing104, contributing to the circuitous flow path of the intake air109within intake housing104. The intake air109, after following a non-linear path within intake housing104, enters the flow modulator tube assembly114. Thus, intake air109turns (e.g., 90°) within air intake housing104to enter the flow modulator tube assembly114. After passing through impeller assembly102, exhaust air111is expelled from impeller assembly102through air outlet106. Exhaust air111may be cleaner than intake air109. That is, exhaust air111may have a reduced content of contaminate (e.g., particulate) relative to the content of contaminate in intake air109due to the removal of contaminates by impeller assembly102. Mechanisms of Noise Reduction in Air Blowers The noise abatement components of blower100significantly reduce the amount of unwanted sound emanating from the blower100. The operation of blowers, as well as the equipment that the blowers are providing air to, produces both airborne and structure-borne sounds. That is, the flow of air into the blower produces sounds, and the movement and vibration of portions of the blower, such as the impeller, also produces sounds. The noise abatement components of blower100effectively reduce the amount of noise that would otherwise emanate from the blower, while still providing sufficient air to equipment or environments. The propagation of sound in and through air blower100will now be discussed with reference toFIG.3B. In operation, when sound emanates from blower100, such as sound produced by impeller assembly102or by equipment that is downstream of and fluidly coupled with impeller assembly102, at least some of the sound travels from or through impeller assembly102and toward air intake housing104. The sound113emanating from impeller housing110, or from equipment downstream of impeller housing110, exits impeller housing110and enters the flow modulator tube assembly114. The flow modulator tube assembly114at least partially muffles the sound that enters the flow modulator tube assembly114. Without being bound by theory, the shape, volume, length, or combinations thereof of the modulated flow paths128of the flow modulator tube assembly114operate to modulate the sound passing therethrough. Furthermore, at least some of the sound passing from impeller housing110is reflected, refracted, attenuated, or combinations thereof by and/or within the flow modulator tube assembly114(e.g., by vanes124and/or shell126). Additionally, the directionality of the modulated flow paths128of the flow modulator tube assembly114direct the sound that propagates therethrough along a path to impact with sound damper116. InFIG.3B, the propagation of sound113is represented by broken lines. Sound damper116is positioned within air intake housing104to receive at least some of the sound that enters air intake housing104from the flow modulator tube assembly114, and sound damper116absorbs at least some of the sound that impacts sound damper116. Thus, sound damper116reduces the sound that emanates from blower100(e.g., that emanates out of air intake inlet108). Sound damper116may be or include sound absorbing material, such as a foam or a metal. In one exemplary embodiment, sound damper116is or includes a compartment that contains steel wool (e.g., corrosion-resistant steel wool) that acts to absorb sound. Sound damper116may be a chamber or compartment within or coupled with air intake housing104, and may include a pad of sound absorbing material positioned to receive sound waves that emanate from the flow modulator tube assembly114. Additionally, the non-linear flow path discussed with reference toFIG.3A, also contributes to the attenuation of the sound emanating from blower100. Sound that is not absorbed by sound damper116is reflected therefrom and, depending on the angle of reflection, may impact with baffles120and/or122, or housing wall121. Upon impact with baffles120and/or122or housing wall121, sound may be absorbed, refracted, or reflected. Sound reflected from baffles120and/or122or housing wall121may be directed to sound damper116for absorption, or may continue to be reflected within housing104for further attenuation of sound. As such, the sound that emanates from blower100, such as through inlet108, is reduced in comparison with the sound that would emanate from blower100if blower100did not include the flow modulator tube assembly114, sound damper116, and the non-linear air intake flow path. The sound abatement components disclosed herein, separate or combined, provide effective noise abatement for blower100, while also providing ample air, such as for cooling of electric motors to maintain the motor at acceptable operating temperatures. As shown inFIGS.4A and4B, in some embodiments, blower100is fluidly coupled with equipment (e.g., electric motor) or local environment200in system1000. Blower100operates to provide cooling air and/or ventilation to equipment or local environment200. Equipment or local environment200may be an induction motor used to drive a drawworks, a pump (e.g., a mud pump), a top drive, a drilling motor, or another piece of oil and gas drill site equipment. While described for use with oil and gas drill site equipment, the blower and motor disclosed herein may be used in other applications. Equipment or local environment200may be a local environment, such as a warehouse, factory, or other localized, generally enclosed environment. Cooling air may enter air blower100through inlet108, pass through air blower100as described above, and exit air blower100through outlet106. The outlet106may be in fluid communication with the equipment or local environment200, such that the air exiting outlet106, air111, enters equipment or local environment200through an inlet, which is in fluid communication with outlet106. Air111then flows through equipment or local environment200and exits at exit202. The blower disclosed herein may be used in many different industrial applications such as sand blasting booths and ventilation. The electric motor disclosed herein may be used with a standard blower (as opposed to the noise abated blower disclosed herein) or without any blower at all. Exemplary Embodiments Some exemplary embodiments will now be described. Embodiment 1. An air blower, the air blower comprising: an intake housing comprising an inlet, the inlet positioned to receive air into the air blower; a impeller, the impeller positioned to draw the air through the inlet and into the impeller; an outlet, the outlet positioned to receive air from the impeller and expel the air from the air blower; a flow modulator tube assembly positioned to receive the air from the intake housing and direct the air to the impeller, wherein the flow modulator tube assembly comprises a plurality of vanes positioned within a shell, the vanes extending axially along a length of the shell, wherein the vanes define a plurality of modulated air flow paths through the flow modulator tube assembly; and a sound damper positioned within the intake housing, wherein the flow modulator tube assembly is positioned to direct at least some sound traveling therethrough to the sound damper, and wherein the sound damper absorbs at least some of the sound directed thereto; wherein the flow modulator tube assembly and the sound damper attenuate sound emanating from the air blower during operation of the air blower. Embodiment 2. The air blower of embodiment 1, wherein the intake housing and the flow modulator tube assembly are arranged relative to one another to define a non-linear flow path of the air from the intake housing into the flow modulator tube assembly. Embodiment 3. The air blower of embodiment 1 or 2, wherein sound exiting the flow modulator tube assembly into the intake housing is directed away from the inlet. Embodiment 4. The air blower of any of embodiments 1 to 3, wherein the inlet is at a 90-degree angle relative to the entrance of the flow modulator tube assembly. Embodiment 5. The air blower of any of embodiments 1 to 4, further comprising one or more baffles positioned within the intake housing to deflect air, deflect sound, or combinations thereof. Embodiment 6. The air blower of any of embodiments 1 to 5, wherein the vanes straighten the flow of the air and the propagation of sound through the flow modulator tube assembly. Embodiment 7. The air blower of any of embodiments 1 to 6, wherein the vanes divide the air and sound into multiple, separate paths. Embodiment 8. The air blower of any of embodiments 1 to 7, wherein the sound damper comprises foam, metal, or combinations thereof. Embodiment 9. The air blower of any of embodiments 1 to 8, wherein the sound damper comprises stainless steel wool. Embodiment 10. The air blower of any of embodiments 1 to 9, wherein at least some of sound is reflected from the sound damper within the intake housing. Embodiment 11. A method of attenuating sound emanating from an air blower, the method comprising: directing at least some sound within the air blower through a flow modulator tube assembly that is positioned within an intake housing of the air blower, wherein the flow modulator tube assembly comprises a plurality of vanes positioned within a shell, the vanes extending axially along a length of the shell, and wherein the vanes define a plurality of modulated flow paths through the flow modulator tube assembly; and directing at least some of the sound from the flow modulator tube assembly to a sound damper that is positioned within the intake housing of the air blower, wherein the sound damper absorbs at least some of the sound. Embodiment 12. The method of embodiment 11, wherein an intake housing of the air blower and the flow modulator tube assembly are arranged to define a non-linear flow path of air from the inlet to the entrance of the flow modulator tube assembly. Embodiment 13. The method of embodiment 11 or 12, wherein sound exiting the flow modulator tube assembly is directed away from the inlet. Embodiment 14. The method of any of embodiments 11 to 13, further comprising positioning one or more baffles within the air intake housing to deflect air, sound, or combinations thereof. Embodiment 15. A system for providing cooling or ventilation, the system comprising: an air blower, the air blower comprising an intake housing comprising an inlet, the inlet positioned to receive air into the air blower; a impeller, the impeller positioned to draw the air through the inlet and into the impeller; an outlet, the outlet positioned to receive air from the impeller and expel the air from the air blower; a flow modulator tube assembly positioned to receive the air from the intake housing and direct the air to the impeller, wherein the flow modulator tube assembly comprises a plurality of vanes positioned within a shell, the vanes extending axially along a length of the shell, wherein the vanes define a plurality of modulated air flow paths through the flow modulator tube assembly; and a sound damper positioned within the intake housing, wherein the flow modulator tube assembly is positioned to direct at least some sound traveling therethrough to the sound damper, and wherein the sound damper absorbs at least some of the sound directed thereto; wherein the flow modulator tube assembly and the sound damper attenuate sound emanating from the air blower during operation of the air blower; wherein the outlet of the air blower is fluidly coupled with equipment or a local environment to provide air into the equipment or a local environment. Embodiment 16. The system of embodiment 15, wherein the intake housing and the flow modulator tube assembly are arranged relative to one another to define a non-linear flow path of the air from the inlet into the flow modulator tube assembly. Embodiment 17. The system of embodiment 15 or 16, wherein sound exiting the flow modulator tube assembly into the intake housing is directed away from the inlet. Embodiment 18. The system of any of embodiments 15 to 17, wherein the inlet is at a 90-degree angle relative to the entrance of the flow modulator tube assembly. Embodiment 19. The system of any of embodiments 15 to 18, further comprising one or more baffles positioned within the intake housing to deflect air, deflect sound, or combinations thereof. Embodiment 20. The system of any of embodiments 15 to 19, wherein the vanes straighten the flow of the air and the propagation of sound through the flow modulator tube assembly. Embodiment 21. The system of any of embodiments 15 to 20, wherein the vanes divide the air and sound into multiple, separate paths. Embodiment 22. The system of any of embodiments 15 to 21, wherein the sound damper comprises foam, metal, or combinations thereof. Embodiment 23. The system of any of embodiments 15 to 22, wherein the sound damper comprises stainless steel wool. Embodiment 24. The system of any of embodiments 15 to 23, wherein at least some of the sound is reflected from the sound damper within the intake housing. Embodiment 25. A method of attenuating sound emanating from an air blower and equipment or a local environment, the method comprising: directing at least some sound through a flow modulator tube assembly that is positioned within an intake housing of the air blower, wherein the flow modulator tube assembly comprises a plurality of vanes positioned within a shell, the vanes extending axially along a length of the shell, and wherein the vanes define a plurality of modulated flow paths through the flow modulator tube assembly; and directing at least some of the sound from the flow modulator tube assembly to a sound damper that is positioned within the intake housing of the air blower, wherein the sound damper absorbs at least some of the sound, wherein the sound is sound generated by the air blower, sound generated by the equipment, or sound emanating from the local environment. Embodiment 26. The method of embodiment 25, wherein the intake housing of the air blower and the flow modulator tube assembly are arranged to define a non-linear flow path of air from the inlet to the entrance of the flow modulator tube assembly. Embodiment 27. The method of embodiment 25 or 26, wherein sound exiting the flow modulator tube assembly is directed away from the inlet. Embodiment 28. The method of any of embodiments 25 to 27, further comprising positioning one or more baffles within the air intake housing to deflect air, sound, or combinations thereof. Although the present embodiments and advantages have been described in detail, it should be understood that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the disclosure. Moreover, the scope of the present application is not intended to be limited to the particular embodiments of the process, machine, manufacture, composition of matter, means, methods and steps described in the specification. As one of ordinary skill in the art will readily appreciate from the disclosure, processes, machines, manufacture, compositions of matter, means, methods, or steps, presently existing or later to be developed that perform substantially the same function or achieve substantially the same result as the corresponding embodiments described herein may be utilized according to the present disclosure. Accordingly, the appended claims are intended to include within their scope such processes, machines, manufacture, compositions of matter, means, methods, or steps. | 26,570 |
11859642 | DETAILED DESCRIPTION OF THE INVENTION FIG.1Ais a schematic block diagram of an embodiment of a mechanical and computing system that includes a set of head units10-1through10-N, objects12-1through12-3, computing entities20-1through20-N associated with the head units10-1through10-N, and a computing entity22. The objects include any object that has mass and moves. Examples of an object include a door, an aircraft wing, a portion of a building support mechanism, and a particular drivetrain, etc. The cross-sectional view ofFIG.1Aillustrates a head unit that includes a chamber16, a piston36, a plunger28, a plunger bushing32, and a chamber bypass40. The chamber16contains a shear thickening fluid (STF)42. The chamber16includes a back channel24and a front channel26, where the piston partitions the back channel24and the front channel26. The piston36travels axially within the chamber16. The chamber16may be a cylinder or any other shape that enables movement of the piston36and compression of the STF42. The STF42is discussed in greater detail with reference toFIGS.1B and1C. The plunger bushing32guides the plunger28into the chamber16in response to force from the object12-1. The plunger bushing32facilitates containment of the STF within the chamber16. The plunger bushing32remains in a fixed position relative to the chamber16when the force from the object moves the piston36within the chamber16. In an embodiment the plunger bushing32includes an O-ring between the plunger bushing32and the chamber16. In another embodiment the plunger bushing32includes an O-ring between the plunger bushing32and the plunger28. The piston36includes a piston bypass38between opposite sides of the piston to facilitate flow of a portion the STF between the opposite sides of the piston (e.g., between the back channel24and the front channel26) when the piston travels through the chamber in an inward or an outward direction. Alternatively, or in addition to, the chamber bypass40is configured between opposite ends of the chamber16, wherein the chamber bypass40facilitates flow of a portion of the STF between the opposite ends of the chamber when the piston travels through the chamber in the inward or outward direction (e.g., between the back channel24and the front channel26). In alternative embodiments, the piston bypass38and the chamber bypass40includes mechanisms to enable STF flow in one direction and not an opposite direction. In further alternative embodiments, a control valve within the piston bypass38and/or the chamber bypass40controls the STF flow between the back channel24and the front channel26. The plunger28is operably coupled to a corresponding object by one of a variety of approaches. A first approach includes a direct connection of the plunger28to the object12-1such that linear motion in any direction couples from the object12-1to the plunger28. A second approach includes the plunger28coupled to a cap44which receives a one way force from a strike48attached to the object12-2. A third approach includes a pushcap46that receives a force from a rotary-to-linear motion conversion component that is attached to the object12-3. In an example, the object12-3is connected to a camshaft110which turns a cam109to strike the pushcap46. In an embodiment, two or more of the head units are coupled by a head unit connector112. When so connected, actuation of a piston in a first head unit is essentially replicated in a piston of a second head unit. The head unit connector112includes a mechanical element between plungers of the two or more head units and/or direct connection of two or more plungers to a common object. For example, plunger28of head unit10-1and plunger28of head unit10-2are directly connected to object12-1when utilizing a direct connection. Further associated with each head unit is a set of emitters and a set of sensors. For example, head unit10-N includes a set of emitters114-N-1through114-N-M and a set of sensors116-N-1through116-N-M. Emitters includes any type of energy and or field emitting device to affect the STF, either directly or indirectly via other nanoparticles suspended in the STF. Examples of emitter categories include light, audio, electric field, magnetic field, wireless field, etc. Specific examples of fluid manipulation emitters include a variable flow valve associated with a bypass or injector or similar, a mechanical vibration generator, an image generator, a light emitter, an audio transducer, a speaker, an ultrasonic sound transducer, an electric field generator, a magnetic field generator, and a radio frequency wireless field transmitter. Specific examples of magnetic field emitters include a Helmholtz coil, a Maxwell coil, a permanent magnet, a solenoid, a superconducting electromagnet, and a radio frequency transmitting coil. Sensors include any type of energy and/or field sensing device to output a signal that represents a reaction, motion or position of the STF. Examples of sensor categories include bypass valve position, mechanical position, image, light, audio, electric field, magnetic field, wireless field, etc. Specific examples of fluid flow sensors include a valve opening detector associated with the chamber16or any type of bypass (e.g., piston bypass38, chamber bypass40, a reservoir injector, or similar), a mechanical position sensor, an image sensor, a light sensor, an audio sensor, a microphone, an ultrasonic sound sensor, an electric field sensor, a magnetic field sensor, and a radio frequency wireless field sensor. Specific examples of magnetic field sensors include a Hall effect sensor, a magnetic coil, a rotating coil magnetometer, an inductive pickup coil, an optical magnetometry sensor, a nuclear magnetic resonance sensor, and a caesium vapor magnetometer. The computing entities20-1through20-N are discussed in detail with reference toFIG.2A. The computing entity22includes a control module30and a chamber database34to facilitate storage of history of operation, desired operations, and other aspects of the system. In an example of operation, the head unit10-1controls motion of the object12-1and includes the chamber16filled at least in part with the shear thickening fluid42, the piston36housed at least partially radially within the chamber16, and the piston36is configured to exert pressure against the shear thickening fluid42in response to movement of the piston36from a force applied to the piston from the object12-1. The movement of the piston36includes one of traveling through the chamber16in an inward direction or traveling through the chamber16in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. The shear thickening fluid42(e.g., dilatant non-Newtonian fluid) has nanoparticles of a specific dimension that are mixed in a carrier fluid or solvent. Force applied to the shear thickening fluid42results in these nanoparticles stacking up, thus stiffening and acting more like a solid than a flowable liquid when a shear threshold is reached. In particular, viscosity of the shear thickening fluid42rises significantly when shear rate is increased to a point of the shear threshold. The relationship between viscosity and shear rates is discussed in greater detail with reference toFIGS.1A and1B. In another example of operation, the object12-1applies an inward motion force on the plunger28which moves the piston36in words within the chamber16. As the piston moves inward, shear rate of the shear thickening fluid42changes. A sensor116-1-1associated with the chamber16of the head unit10-1outputs chamber I/O160to the computing entity20-1, where the chamber I/O160includes a movement data associated with the STF42as a result of the piston36moving inwards. Having received the chamber I/O160, the computing entity20-1interprets the chamber I/O160to reproduce the movement data. The computing entity20-1outputs the movement data as a system message162to the computing entity22. The control module30stores the movement data in the chamber database34and interprets the movement data to determine whether to dynamically adjust the viscosity of the shear thickening fluid. Dynamic adjustment of the viscosity results in dynamic control of the movement of the piston36, the plunger28, and ultimately the object12-1. Adjustment of the viscosity affects velocity, acceleration, and position of the piston36. The control module30determines whether to adjust the viscosity based on one or more desired controls of the object12-1. The desired controls include accelerating, deaccelerating, abruptly stopping, continuing on a current trajectory, continuing at a constant velocity, or any other movement control. For example, the control module30determines to abruptly stop the movement of the object12-1when the object12-1is a door and the door is detected to be closing at a rate above a maximum closing rate threshold level and when the expected shear rate versus viscosity of the shear thickening fluid42requires modification (e.g., boost the viscosity now to slow the door from closing too quickly). When determining to modify the viscosity, the control module30outputs a system message162to the computing entity20-1, where the system message162includes instructions to immediately boost the viscosity beyond the expected shear rate versus viscosity of the shear thickening fluid42. Alternatively, the system message162includes specific information on the relationship of viscosity versus shear rate. Having received the system message162, the computing entity20-1determines a set of adjustments to make with regards to the shear thickening fluid42within the chamber16. The set of adjustments includes one or more of adjusting STF42flow through the chamber bypass40, adjusting STF42flow through the piston bypass38, and activating an emitter of a set of emitters114-1-1through114-N-1. The flow adjustments include regulating within a flow range, stopping, starting, and allowing in one particular direction. For example, the computing entity20-1determines to activate emitter114-1-1to produce a magnetic field such as to interact with magnetic nanoparticles within the STF42to raise the viscosity. The computing entity20-1issues another chamber I/O160to the emitter114-1-1to initiate a magnetic influence process to boost the viscosity of the STF42. In an alternative embodiment, the computing entity22issues another system message162to two or more computing entities (e.g.,20-1and20-2) to boost the viscosity for corresponding head units10-1and10-2when the head unit connector112connects head units10-1and10-2and both head units are controlling the motion of the object12-1. For instance, one of the head units informs the computing entity22that the object12-1is moving too quickly inward and the predicted stopping power of the expected viscosity versus shear rate of the STF42of the head unit, even when boosted, will not be enough to slow the object12-1to a desired velocity or position. When informed that one head unit, even with a modified viscosity, is not enough to control the object12-1, the control module30determines how many other head units (e.g., connected via the head unit connector112) to apply and to dynamically modify the viscosity. In yet another alternative embodiment, the computing entity22issues a series of system messages162to a set of computing entities associated with a corresponding set of head units to produce a cascading effect of altering of the viscosity of the STF42of each of the chambers16associated with the set of head units. For example, 3 head units are controlled by 3 corresponding computing entities to adjust viscosity in a time cascaded manner. For instance, head unit10-1abruptly changes the viscosity to attempt to slow the object12-1followed seconds later by head unit10-2abruptly changing the viscosity to attempt to further slow the object12-1, followed seconds later by head unit12-3abruptly changing the viscosity to attempt to further slow the object12-1. In a still further alternative embodiment, the computing entity22conditionally issues each message of the series of system messages162to the set of computing entities associated with the corresponding set of head units to produce the cascading effect of altering of the viscosity of the STF42of each of the chambers16associated with the set of head units only when a most recent adaptation of viscosity is not enough to slow the object12-1with desired results. For example, the 3 head units are controlled by the 3 corresponding computing entities to adjust viscosity in a conditional time cascaded manner. For instance, head unit10-1abruptly changes the viscosity to attempt to slow the object12-1followed seconds later by head unit10-2abruptly changing the viscosity if head unit10-1was unsuccessful to attempt to further slow the object12-1, followed seconds later by head unit12-3abruptly changing the viscosity if head unit10-2was unsuccessful to attempt to further slow the object12-1. FIG.1Bis a graph of viscosity vs. shear rate for an aspect of an embodiment of a mechanical and computing system that includes a chamber, a shear thickening fluid, and a piston that moves through the chamber applying forces on the shear thickening fluid. The shear thickening fluid includes a non-Newtonian fluid since the relationship between shear rate and viscosity is nonlinear. A relationship between compressive impulse (e.g., shear rate) and the viscosity of the shear thickening fluid is nonlinear and may comprise one or more inflection points as the piston travels within the chamber in response to different magnitudes of forces and different accelerations. The viscosity of the STF may also be a function of other influences, such as electric fields, acoustical waves, magnetic fields, and other similar influences. As a first example of a response of a shear thickening fluid, a first range of shear rates in zone A has a decreasing viscosity as the shear rate increases and then in a second range of shear rates in zone B the viscosity increases abruptly. As a second example of a response of a diluted shear thickening fluid, the first range of shear rates in zone A extends to a higher level of shear rates with the decreasing viscosity and then in the still higher second range of shear rates in zone B the viscosity increases abruptly similar to that of the shear thickening include. The shear thickening fluid includes particles within a solvent. Examples of particles of the shear thickening fluid include oxides, calcium carbonate, synthetically occurring minerals, naturally occurring minerals, polymers, or a mixture thereof. Further examples of the particles of the shear thickening fluid include SiO2, polystyrene, or polymethylmethacrylate. The particles are suspended in a solvent. Example components of the solvent include water, a salt, a surfactant, and a polymer. Further example components of the solvent include ethylene glycol, polyethylene glycol, ethanol, silicon oils, phenyltrimethicone or a mixture thereof. Example particle diameters range from less than 100 μm to less than 1 millimeter. In an instance, the shear thickening fluid is made of silica particles suspended in polyethylene glycol at a volume fraction of approximately 0.57 with the silica particles having an average particle diameter of approximately 446 nm. As a result, the shear thickening fluid exhibits a shear thickening transition at a shear rate of approximately 102-103 s−1. A volume fraction of particles dispersed within the solvent distinguishes the viscosity versus shear rate of different shear thickening fluids. The viscosity of the STF changes in response to the applied shear stress. At rest and under weak applied shear stress, a STF may have a fairly constant or even slightly decreasing viscosity because the random distribution of particles causes the particles to frequently collide. However, as a greater shear stress is applied so that the shear rate increases, the particles flow in a more streamlined manner. However, as an even greater shear stress is applied so that the shear rate increases further, a hydrodynamic coupling between the particles may overcome the interparticle forces responsible for Brownian motion. The particles may be driven closer together, and the microstructure of the colloidal dispersion may change, so that particles cluster together in hydroclusters. The viscosity curve of the STF can be fine-tuned through changes in the characteristics of the particles suspended in the solvent. For example, the particles shape, surface chemistry, ionic strength, and size affect the various interparticle forces involved, as does the properties of the solvent. However, in general, hydrodynamic forces dominate at a high shear stress, which also makes the addition of a polymer attached to the particle surface effective in limiting clumping in hydroclusters. Various factors influence this clumping behavior, including, fluid slip, adsorbed ions, surfactants, polymers, surface roughness, graft density (e.g., of a grafted polymer), molecular weight, and solvent, so that the onset of shear thickening can be modified. In general, the onset of shear thickening can be slowed by the introduction of techniques to prevent the clumping of particles. For example, influencing the STF with emissions from an emitter in proximal location to the chamber. FIG.1Cis a graph of piston velocity vs. force applied to the piston for an aspect of an embodiment of a mechanical and computing system that includes a chamber, a shear thickening fluid, and a piston that moves through the chamber applying forces on the shear thickening fluid. The shear thickening fluid includes a non-Newtonian fluid since the relationship between shear rate and viscosity is nonlinear. An example curve for a shear thickening fluid indicates that as more force is applied to the piston in zone A, a higher piston velocity is realized until the corresponding transition to zone B occurs where the shear threshold affect takes hold and the viscosity abruptly increases significantly. When the viscosity increases abruptly, the piston velocity slows back down and may even stop. Another example curve for a diluted shear thickening fluid indicates that as more force is applied to the piston in zone A, an even higher piston velocity is realized until the corresponding transition to zone B occurs where the shear threshold affect takes hold and the viscosity abruptly increases significantly. When the viscosity increases abruptly, the piston velocity slows back down and may even stop. FIG.2Ais a schematic block diagram of an embodiment of the computing entity (e.g.,20-1through20-N; and22) of the mechanical and computing system ofFIG.1. The computing entity includes one or more computing devices100-1through100-N. A computing device is any electronic device that communicates data, processes data, represents data (e.g., user interface) and/or stores data. Computing devices include portable computing devices and fixed computing devices. Examples of portable computing devices include an embedded controller, a smart sensor, a social networking device, a gaming device, a smart phone, a laptop computer, a tablet computer, a video game controller, and/or any other portable device that includes a computing core. Examples of fixed computing devices includes a personal computer, a computer server, a cable set-top box, a fixed display device, an appliance, and industrial controller, a video game counsel, a home entertainment controller, a critical infrastructure controller, and/or any type of home, office or cloud computing equipment that includes a computing core. FIG.2Bis a schematic block diagram of an embodiment of a computing device (e.g.,100-1through100-N) of the computing entity ofFIG.2Athat includes one or more computing cores52-1through52-N, a memory module102, a human interface module18, an environment sensor module14, and an input/output (I/O) module104. In alternative embodiments, the human interface module18, the environment sensor module14, the I/O module104, and the memory module102may be standalone (e.g., external to the computing device). An embodiment of the computing device is discussed in greater detail with reference toFIG.3. FIG.3is a schematic block diagram of another embodiment of the computing device100-1of the mechanical and computing system ofFIG.1that includes the human interface module18, the environment sensor module14, the computing core52-1, the memory module102, and the I/O module104. The human interface module18includes one or more visual output devices74(e.g., video graphics display, 3-D viewer, touchscreen, LED, etc.), one or more visual input devices80(e.g., a still image camera, a video camera, a 3-D video camera, photocell, etc.), and one or more audio output devices78(e.g., speaker(s), headphone jack, a motor, etc.). The human interface module18further includes one or more user input devices76(e.g., keypad, keyboard, touchscreen, voice to text, a push button, a microphone, a card reader, a door position switch, a biometric input device, etc.) and one or more motion output devices106(e.g., servos, motors, lifts, pumps, actuators, anything to get real-world objects to move). The computing core52-1includes a video graphics module54, one or more processing modules50-1through50-N, a memory controller56, one or more main memories58-1through58-N (e.g., RAM), one or more input/output (I/O) device interface modules62, an input/output (I/O) controller60, and a peripheral interface64. A processing module is as defined at the end of the detailed description. The memory module102includes a memory interface module70and one or more memory devices, including flash memory devices92, hard drive (HD) memory94, solid state (SS) memory96, and cloud memory98. The cloud memory98includes an on-line storage system and an on-line backup system. The I/O module104includes a network interface module72, a peripheral device interface module68, and a universal serial bus (USB) interface module66. Each of the I/O device interface module62, the peripheral interface64, the memory interface module70, the network interface module72, the peripheral device interface module68, and the USB interface modules66includes a combination of hardware (e.g., connectors, wiring, etc.) and operational instructions stored on memory (e.g., driver software) that are executed by one or more of the processing modules50-1through50-N and/or a processing circuit within the particular module. The I/O module104further includes one or more wireless location modems84(e.g., global positioning satellite (GPS), Wi-Fi, angle of arrival, time difference of arrival, signal strength, dedicated wireless location, etc.) and one or more wireless communication modems86(e.g., a cellular network transceiver, a wireless data network transceiver, a Wi-Fi transceiver, a Bluetooth transceiver, a 315 MHz transceiver, a zig bee transceiver, a 60 GHz transceiver, etc.). The I/O module104further includes a telco interface108(e.g., to interface to a public switched telephone network), a wired local area network (LAN)88(e.g., optical, electrical), and a wired wide area network (WAN)90(e.g., optical, electrical). The I/O module104further includes one or more peripheral devices (e.g., peripheral devices1-P) and one or more universal serial bus (USB) devices (USB devices1-U). In other embodiments, the computing device100-1may include more or less devices and modules than shown in this example embodiment. FIG.4is a schematic block diagram of an embodiment of the environment sensor module14of the computing device ofFIG.2Bthat includes a sensor interface module120to output environment sensor information150based on information communicated with a set of sensors. The set of sensors includes a visual sensor122(e.g., to the camera, 3-D camera, 360° view camera, a camera array, an optical spectrometer, etc.) and an audio sensor124(e.g., a microphone, a microphone array). The set of sensors further includes a motion sensor126(e.g., a solid-state Gyro, a vibration detector, a laser motion detector) and a position sensor128(e.g., a Hall effect sensor, an image detector, a GPS receiver, a radar system). The set of sensors further includes a scanning sensor130(e.g., CAT scan, Mill, x-ray, ultrasound, radio scatter, particle detector, laser measure, further radar) and a temperature sensor132(e.g., thermometer, thermal coupler). The set of sensors further includes a humidity sensor134(resistance based, capacitance based) and an altitude sensor136(e.g., pressure based, GPS-based, laser-based). The set of sensors further includes a biosensor138(e.g., enzyme, microbial) and a chemical sensor140(e.g., mass spectrometer, gas, polymer). The set of sensors further includes a magnetic sensor142(e.g., Hall effect, piezo electric, coil, magnetic tunnel junction) and any generic sensor144(e.g., including a hybrid combination of two or more of the other sensors). FIGS.5A-5Dare schematic block diagrams of another embodiment of a mechanical and computing system illustrating an example of determining operational aspects. The mechanical and computing system includes the head unit10-1ofFIG.1, the object12-1ofFIG.1, and the computing entity20-1ofFIG.1. In particular, the head unit10-1for controlling motion of the object12-1includes a chamber16filled at least in part with a shear thickening fluid (STF)42, where the STF includes a multitude of magnetic nanoparticles170. The head unit10-1further includes a piston36housed at least partially radially within the chamber16. The piston36is configured to exert pressure against the shear thickening fluid42in response to movement of the piston36from a force applied to the piston36from the object12-1. The movement of the piston36includes one of traveling through the chamber16in an inward direction or traveling through the chamber16in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. The head unit10-1further includes a set of magnetic field sensors116-1-1and116-1-2positioned proximal to the chamber16. For instance, the magnetic field sensors are implemented utilizing Hall effect sensors. FIG.5Aillustrates an example of operation of a method for the determining the operational aspects. A first step of the example of operation includes the computing entity20-1interpreting magnetic response180-1-2from the set of magnetic field sensors (e.g., in response to varying fields from the magnetic nanoparticles170) to produce a piston velocity and position. The set of magnetic field sensors are positioned proximal to the head unit10-1for controlling motion of the object12-1, where the head unit includes the chamber filled at least in part with a shear thickening fluid (STF). The STF includes a multitude of magnetic nanoparticles. The piston is housed at least partially radially within the chamber and the piston configured to exert pressure against the shear thickening fluid in response to movement of the piston from a force applied to the piston from the object12-1. The movement of the piston includes one of traveling through the chamber in an inward direction or traveling through the chamber in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. As an example of interpreting the magnetic response180-1-2, the computing entity20-1compares the magnetic response180-1-2to previous measurements of magnetic fields versus piston velocity and position to produce the piston velocity182and piston position184. As another example of the interpreting the magnetic response180-1-2, the computing entity20-1extracts the piston velocity182and the piston position184directly from the magnetic response180-1-2when the sensor116-1-2generates the velocity and piston position directly. FIG.5Bfurther illustrates the example of operation of the method for the determining the operational aspects. A second step of the example of operation includes the computing entity interpreting magnetic response180-1-1from the set of magnetic field sensors to produce updated piston velocity and position as previously discussed. For example, the computing entity interprets the magnetic response180-1-1to determine the updated piston velocity182and piston position184. For instance, the computing entity20-1determines that the position of the piston is further inward within the chamber16and moving inward with a higher velocity as compared to the previous interpretation step. FIG.5Cfurther illustrates the example of operation of the method for the determining the operational aspects. A third step of the example of operation includes the computing entity20-1determining a shear force186based on the updated piston velocity182and piston position184. For example, the computing entity20-1compares the updated velocity and position to stored data for instantaneous velocity and position versus shear force for the STF42. As another example, the computing entity20-1receives the shear force186from at least one of the set of sensors when at least one sensor provides the shear force186directly. FIG.5Dfurther illustrates the example of operation of the method for the determining the operational aspects. A fourth step of the example of operation includes the computing entity determining whether a shear threshold has been obtained based on the shear force186. The shear threshold is associated with the increasing viscosity in response to the second range of shear rates. For example, the computing entity20-1compares the shear force186to data associated with the viscosity versus shear rate curve and indicates via a shear threshold indicator188that the shear threshold has been obtained when the shear force186compares favorably to the data associated with the viscosity versus shear rate curve for the shear threshold effect. As another example, the computing entity20-1interprets the piston velocity182over time to produce acceleration and indicates the shear threshold via the shear threshold indicator188when detecting a sudden deceleration. The method described above in conjunction with a processing module of any computing entity of the mechanical and computing system ofFIG.1can alternatively be performed by other modules of the system ofFIG.1or by other devices. In addition, at least one memory section that is non-transitory (e.g., a non-transitory computer readable storage medium, a non-transitory computer readable memory organized into a first memory element, a second memory element, a third memory element, a fourth element section, a fifth memory element, a sixth memory element, etc.) that stores operational instructions can, when executed by one or more processing modules of the one or more computing entities of the computing system10, cause one or more computing devices of the mechanical and computing system ofFIG.1to perform any or all of the method steps described above. FIGS.6A-6Care schematic block diagrams of another embodiment of a mechanical and computing system illustrating an example of controlling operational aspects. The mechanical and computing system includes the head unit10-1ofFIG.1, the object12-1ofFIG.1, and the computing entity20-1ofFIG.1. In particular, the head unit10-1for controlling motion of the object12-1includes the chamber16filled at least in part with the shear thickening fluid (STF)42, where the STF includes a multitude of magnetic nanoparticles170. The piston is housed at least partially radially within the chamber16. The piston36is configured to exert pressure against the shear thickening fluid in response to movement of the piston36from a force applied to the piston36via the plunger28from the object12-1. The movement of the piston36includes one of traveling through the chamber16in an inward direction or traveling through the chamber16in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. The head unit10-1further includes a set of magnetic field sensors positioned proximal to the chamber16and a set of magnetic field emitters positioned proximal to the chamber16. The set of magnetic field sensors provide a magnetic response from the multitude of magnetic nanoparticles. The set of magnetic field emitters provide a magnetic activation to the multitude of magnetic nanoparticles which in turn affects the STF. For example, sensors116-1-1and116-1-2and emitters114-1-1and114-1-2, where the sensors and emitters sense and emit magnetic waves respectively to interact with the magnetic nanoparticles170. FIG.6Aillustrates an example of operation of a method for the controlling the operational aspects. A first step of the example of operation includes the computing entity20-1interpreting magnetic response180-1-1and180-1-2from the set of magnetic field sensors (e.g., in response to varying fields from the magnetic nanoparticles170) to produce a piston velocity and piston position. The set of magnetic field sensors are positioned proximal to the head unit10-1for controlling motion of the object12-1, where the head unit includes the chamber filled at least in part with a shear thickening fluid (STF). The STF includes a multitude of magnetic nanoparticles. The piston is housed at least partially radially within the chamber and the piston configured to exert pressure against the shear thickening fluid in response to movement of the piston from a force applied to the piston from the object12-1. The movement of the piston includes one of traveling through the chamber in an inward direction or traveling through the chamber in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. The interpreting the magnetic response from the set of magnetic field sensors to produce the piston velocity and the piston position of the piston includes a series of sub-steps. A first sub-step includes inputting, from one or more magnetic field sensors of the set of magnetic field sensors, a set of magnetic field signals over a time range. For example, the computing entity20-1inputs a magnetic field signal from sensor116-1-1during a first timeframe of the time range and another magnetic field signal from sensor116-1-2during a second timeframe of the time range. A second sub-step includes determining the magnetic response of the set of magnetic field sensors based on the set of magnetic field signals. For example, the computing entity20-1interprets the magnetic field signals based on a type of magnetic sensor to produce magnetic responses180-1-1and180-1-2. A third sub-step includes determining the piston velocity based on the magnetic response of the set of magnetic field sensors over the time range. For example, the computing entity20-1calculates velocity based on changes in the magnetic responses over the time range. A fourth sub-step includes determining the piston position based on the piston velocity and a real-time reference. For example, the computing entity20-1calculates the piston position based on time and the piston velocity as the piston moves through the chamber. As another example of interpreting the magnetic response180-1-2, the computing entity20-1compares the magnetic response180-1-2to previous measurements of magnetic fields versus piston velocity and piston position to produce the piston velocity182and piston position184. As a still further example of the interpreting the magnetic response180-1-2, the computing entity20-1extracts the piston velocity182and the piston position184directly from the magnetic response180-1-2when the sensor116-1-2generates the piston velocity and piston position directly. A second step of the example of operation includes the computing entity20-1determining a shear force186based on the piston velocity182and piston position184. The determining the shear force based on the piston velocity and the piston position includes one approach of a variety of approaches. A first approach includes extracting the shear force directly from the magnetic response when one or more magnetic field sensors of the set of magnetic field sensors outputs a shear force encoded signal. For example, the computing entity20-1extracts the shear force186directly from the magnetic responses180-1-1and180-1-2. In an instance, the shear force186reveals the piston velocity versus force applied to the piston curve as illustrated inFIG.6A, where at a current time of interpreting the magnetic response, the force and piston velocity are at a point X1. A second approach includes determining the shear force utilizing the piston velocity and stored data for piston velocity versus shear force for the STF. For example, the computing entity20-1compares the velocity and position to stored data for instantaneous velocity and position versus shear force for the STF42. A third approach includes determining the shear force utilizing the piston position and stored data for piston position versus shear force for the STF within the chamber. For example, the computing entity20-1compares the velocity and position to stored data for instantaneous velocity and position versus shear force for the STF42. FIG.6Bfurther illustrates the example of operation of the method for the controlling the operational aspects. A third step of the example of operation includes the computing entity20-1determining a desired response188for the STF based on one or more of the shear force186and the piston velocity182and the piston position184. The desired response188includes continuing to follow a nominal response curve associated with the STF without modifying the functioning of the STF. The desired response188further includes modifying the function of the STF to further slow down the object12-1or to allow the object12-1to speed up at a velocity associated with the nominal response. The determining the desired response for the STF based on one or more of the shear force, the piston velocity, and piston position includes one or more approaches. A first approach includes interpreting a request associated with modifying one or more of object velocity and object position. For example, the computing entity20-1interprets a request from another computing entity to update the desired response for the STF to increase viscosity to slow down the object12-1. A second approach includes interpreting guidance from a chamber database. For example, the computing entity20-1interprets data from the chamber database34ofFIG.1Ato identify an updated response for the STF. For instance, the response for the STF is updated to decrease viscosity when historical information in the chamber database34indicates that a decrease in viscosity is desired based on a current piston position and current shear force. A third approach includes establishing the desired response to include facilitating the second range of shear rates to slow down the object when detecting that the piston position is greater than a maximum piston position threshold level. A fourth approach includes establishing the desired response to include facilitating the first range of shear rates to speed up the object when detecting that the piston position is less than a minimum piston position threshold level. A fifth approach includes establishing the desired response to include facilitating the second range of shear rates to slow down the object when detecting that the piston velocity is greater than a maximum piston velocity threshold level. A sixth approach includes establishing the desired response to include facilitating the first range of shear rates to speed up the object when detecting that the piston velocity is less than a minimum piston velocity threshold level. A seventh approach includes establishing the desired response to include facilitating the second range of shear rates to slow down the object when detecting that the shear force is less than a minimum shear force threshold level. An eighth approach includes establishing the desired response to include facilitating the first range of shear rates to speed up the object when detecting that the shear force is greater than a maximum shear force threshold level. A ninth approach includes detecting an environmental condition warranting a change in viscosity of the STF. For example, the computing entity20-1determines to change the viscosity of the STF when a triggering of a vehicular airbag sensor is detected. As another example, the computing entity20-1determines to change the viscosity of the STF when detecting an earthquake. As yet another example, the computing entity20-1determines to change the viscosity of the STF when detecting a proximity warning (e.g., of a certain collision). Having determined the desired response188for the STF, a fourth step of the example method of operation includes the computing entity20-1generating a magnetic activation based on the desired response for the STF, where the magnetic activation is output to the set of magnetic field emitters positioned proximal to the chamber16. The generating the magnetic activation based on the desired response for the STF includes one or more approaches. A first approach includes determining magnetic output values for the magnetic activation based on a difference between actual viscosity of the STF and a desired viscosity of the STF. For example, the computing entity20-1determines the magnetic activation to affect the STF such that the viscosity is raised to lead to an abrupt slow down of the piston through the STF. A second approach includes determining the magnetic activation based on the desired response for the STF and utilizing a magnetic activation table for magnetic output values versus the desired viscosity of the STF. For example, the computing entity20-1performs a lookup in a magnetic activation table for magnetic output values versus desired viscosity increases. A third approach includes receiving the magnetic activation from another computing device. Having determined the magnetic activation, in a fourth approach, the computing entity20-1outputs the magnetic activation to the set of magnetic field emitters. For instance, the computing entity20-1outputs the magnetic activation181-1-1and181-1-2to the emitters114-1-1and114-1-2respectively to affect the viscosity of the STF42. FIG.6Cfurther illustrates the example of operation of the method for the controlling the operational aspects where, having generated the magnetic activation, the computing entity20-1determines an error level190from the desired response for the STF42. For example, the computing entity20-1re-measures the magnetic response to determine one or more of piston velocity182, piston position184, and shear force186. Having determined velocity and position, the computing entity20-1determines actual response at a time X2 and compares the piston velocity versus force applied to the piston to the desired response curve. The computing entity20-1determines the error level190based on the comparison. Having determined the error level, a sixth step of the example of operation of the method for the controlling the operational aspects includes the computing entity20-1generating an updated magnetic activation based on the error level and the desired response. The error level is at least one of substantially zero (e.g., the actual response is on top of the desired response), a positive error level (e.g., when the actual response includes a piston velocity that is too high for the force applied to the piston), and a negative error level (e.g., when the actual response includes a piston velocity that is too low for the force applied to the piston). In an example of generating the updated magnetic activation, the computing entity20-1determines that the error level190is a positive error level, determines the updated magnetic activation to further increase the viscosity of the STF42, and outputs magnetic activation181-1-1and181-1-2to the emitters114-1-1and114-1-2respectively to facilitate slowing down the piston velocity back to the desired response curve. The method described above in conjunction with a processing module of any computing entity of the mechanical and computing system ofFIG.1can alternatively be performed by other modules of the system ofFIG.1or by other devices. In addition, at least one memory section that is non-transitory (e.g., a non-transitory computer readable storage medium, a non-transitory computer readable memory organized into a first memory element, a second memory element, a third memory element, a fourth element section, a fifth memory element, a sixth memory element, etc.) that stores operational instructions can, when executed by one or more processing modules of the one or more computing entities of the computing system10, cause one or more computing devices of the mechanical and computing system ofFIG.1to perform any or all of the method steps described above. FIGS.7A-7Dare schematic block diagrams of another embodiment of a mechanical and computing system illustrating another example of determining operational aspects. The mechanical and computing system includes the head unit10-1ofFIG.1, the object12-1ofFIG.1, and the computing entity20-1ofFIG.1. In particular, the head unit10-1for controlling motion of the object12-1includes a chamber16filled at least in part with a shear thickening fluid (STF)42, where the STF includes a multitude of reflective nanoparticles200. The head unit10-1further includes a piston36housed at least partially radially within the chamber16. The piston36is configured to exert pressure against the shear thickening fluid42in response to movement of the piston36from a force applied to the piston36from the object12-1. The movement of the piston36includes one of traveling through the chamber16in an inward direction or traveling through the chamber16in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. The head unit10-1further includes a set of optical sensors116-1-1and116-1-2positioned proximal to the chamber16. For instance, the optical sensors are implemented utilizing image sensors (e.g., cameras). FIG.7Aillustrates an example of operation of a method for the determining the operational aspects. A first step of the example of operation includes the computing entity20-1interpreting an optical response from the set of optical sensors (e.g., in response to varying light patterns from the reflective nanoparticles200) to produce a piston velocity and position. The set of optical sensors are positioned proximal to the head unit10-1for controlling motion of the object12-1, where the head unit includes the chamber filled at least in part with a shear thickening fluid (STF). The STF includes the multitude of reflective nanoparticles. The piston is housed at least partially radially within the chamber and the piston configured to exert pressure against the shear thickening fluid in response to movement of the piston from a force applied to the piston from the object12-1. The movement of the piston includes one of traveling through the chamber in an inward direction or traveling through the chamber in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. As an example of interpreting the optical response, the computing entity20-1compares the optical response202-1-2to previous measurements of light fields versus piston velocity and position to produce the piston velocity182and piston position184. As another example of the interpreting the optical response202-1-2, the computing entity20-1extracts the piston velocity182and the piston position184directly from the optical response202-1-2when the sensor116-1-2generates the velocity and piston position directly. FIG.7Bfurther illustrates the example of operation of the method for the determining the operational aspects. A second step of the example of operation includes the computing entity20-1interpreting optical response202-1-1from the set of optical sensors to produce updated piston velocity and position as previously discussed. For example, the computing entity20-1interprets the optical response202-1-1to determine the updated piston velocity182and piston position184. For instance, the computing entity20-1determines that the position of the piston is further inward within the chamber16and moving inward with a higher velocity as compared to the previous interpretation step. FIG.7Cfurther illustrates the example of operation of the method for the determining the operational aspects. A third step of the example of operation includes the computing entity20-1determining a shear force186based on the updated piston velocity182and piston position184. For example, the computing entity20-1compares the updated velocity and position to stored data for instantaneous velocity and position versus shear force for the STF42. As another example, the computing entity20-1receives the shear force186from at least one of the set of sensors when at least one sensor provides the shear force186directly. FIG.7Dfurther illustrates the example of operation of the method for the determining the operational aspects. A fourth step of the example of operation includes the computing entity determining whether a shear threshold has been obtained based on the shear force186. The shear threshold is associated with the increasing viscosity in response to the second range of shear rates. For example, the computing entity20-1compares the shear force186to data associated with the viscosity versus shear rate curve and indicates via a shear threshold indicator188that the shear threshold has been obtained when the shear force186compares favorably to the data associated with the viscosity versus shear rate curve for the shear threshold effect. As another example, the computing entity20-1interprets the piston velocity182over time to produce acceleration and indicates the shear threshold via the shear threshold indicator188when detecting a sudden deceleration. The method described above in conjunction with a processing module of any computing entity of the mechanical and computing system ofFIG.1can alternatively be performed by other modules of the system ofFIG.1or by other devices. In addition, at least one memory section that is non-transitory (e.g., a non-transitory computer readable storage medium, a non-transitory computer readable memory organized into a first memory element, a second memory element, a third memory element, a fourth element section, a fifth memory element, a sixth memory element, etc.) that stores operational instructions can, when executed by one or more processing modules of the one or more computing entities of the computing system cause one or more computing devices of the mechanical and computing system ofFIG.1to perform any or all of the method steps described above. FIGS.8A-8Care schematic block diagrams of another embodiment of a mechanical and computing system illustrating another example of controlling operational aspects. The mechanical and computing system includes the head unit10-1ofFIG.1, the object12-1ofFIG.1, and the computing entity20-1ofFIG.1. In particular, the head unit10-1for controlling motion of the object12-1includes the chamber16filled at least in part with the shear thickening fluid (STF)42, where the STF includes a multitude of piezoelectric nanoparticles210. The piston is housed at least partially radially within the chamber16. The piston36is configured to exert pressure against the shear thickening fluid in response to movement of the piston36from a force applied to the piston36via the plunger28from the object12-1. The movement of the piston36includes one of traveling through the chamber16in an inward direction or traveling through the chamber16in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. The head unit10-1further includes a set of electric field sensors positioned proximal to the chamber16and a set of electric field emitters positioned proximal to the chamber16. For example, sensors116-1-1and116-1-2and emitters114-1-1and114-1-2, where the sensors and emitters sense and emit electric waves respectively to interact with the piezoelectric nanoparticles210. FIG.8Aillustrates an example of operation of a method for the controlling the operational aspects. A first step of the example of operation includes the computing entity20-1interpreting electric response212-1-1and212-1-2from the set of piezoelectric nanoparticles210(e.g., in response to varying fields from the piezoelectric nanoparticles210) to produce a piston velocity and position. The set of electric field sensors are positioned proximal to the head unit10-1for controlling motion of the object12-1, where the head unit includes the chamber filled at least in part with a shear thickening fluid (STF). The STF includes the multitude of piezoelectric nanoparticles210. The piston is housed at least partially radially within the chamber and the piston configured to exert pressure against the shear thickening fluid in response to movement of the piston from a force applied to the piston from the object12-1. The movement of the piston includes one of traveling through the chamber in an inward direction or traveling through the chamber in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. As an example of interpreting the electric response212-1-1and212-1-2, the computing entity20-1compares the electric response212-1-1and212-1-2to previous measurements of electric fields versus piston velocity and position to produce the piston velocity182and piston position184. As another example of the interpreting the electric response212-1-1and212-1-2, the computing entity20-1extracts the piston velocity182and the piston position184directly from the electric response212-1-1and212-1-2when the sensors116-1-1and116-1-2generate the velocity and piston position directly. A second step of the example of operation includes the computing entity20-1determining a shear force186based on the piston velocity182and piston position184. For example, the computing entity20-1compares the velocity and position to stored data for instantaneous velocity and position versus shear force for the STF42. As another example, the computing entity20-1receives the shear force186from at least one of the set of sensors when at least one sensor provides the shear force186directly. In an instance, the shear force186reveals the piston velocity versus force applied to the piston curve as illustrated inFIG.8A, where at a current time of interpreting the electric response, the force and piston velocity are at a point X1. FIG.8Bfurther illustrates the example of operation of the method for the controlling the operational aspects. A third step of the example of operation includes the computing entity20-1determining a desired response188for the STF based on one or more of the shear force186and the piston velocity182and the piston position184. The desired response188includes continuing to follow a nominal response curve associated with the STF without modifying the functioning of the STF. The desired response188further includes modifying the function of the STF to further slow down the object12-1or to allow the object12-1to speed up at a velocity associated with the nominal response. The determining the desired response188includes one or more of interpreting a request, interpreting guidance from the chamber database34, detecting that the piston velocity is greater than a maximum piston velocity threshold level (e.g., too fast), detecting that the piston velocity is less than a minimum piston velocity threshold level (e.g., too slow), and detecting an environmental condition warranting changing the viscosity (e.g., a triggering of a vehicular airbag sensor, detection of an earthquake, a proximity warning, etc.). For instance, the computing entity20-1determines that the desired response188to slow down the object12-1is warranted based on reaching a maximum piston velocity threshold level for object12-1. Having determined the desired response188for the STF, a fourth step of the example method of operation includes the computing entity20-1generating an electric activation based on the desired response for the STF, where the electric activation is output to a set of electric field emitters positioned proximal to the chamber16. The generating of the electric activation includes one or more of performing a lookup in an electric activation table for electric field output values versus desired viscosity increases, dynamically calculating the electric field output values based on a gap in viscosity levels, and receiving the electric activation from another computing entity. For example, the computing entity20-1determines the electric activation to affect the STF such that the viscosity is raised to lead to an abrupt slow down of the piston through the STF. Having determined the electric activation, the computing entity20-1outputs electric activation214-1-1and214-1-2to the emitters114-1-1and114-1-2respectively to affect the viscosity of the STF42. FIG.8Cfurther illustrates the example of operation of the method for the controlling the operational aspects where, having generated the electric activation, the computing entity20-1determines an error level190from the desired response for the STF42. For example, the computing entity20-1re-measures the electric response to determine one or more of piston velocity182, piston position184, and shear force186. Having determined velocity and position, the computing entity20-1determines actual response at a time X2 and compares the piston velocity versus force applied to the piston to the desired response curve. The computing entity20-1determines the error level190based on the comparison. Having determined the error level, a sixth step of the example of operation of the method for the controlling the operational aspects includes the computing entity20-1generating an updated electric activation based on the error level and the desired response. The error level is at least one of substantially zero (e.g., the actual response is on top of the desired response), a positive error level (e.g., when the actual response includes a piston velocity that is too high for the force applied to the piston), and a negative error level (e.g., when the actual response includes a piston velocity that is too low for the force applied to the piston). In an example of generating the updated electric activation, the computing entity20-1determines that the error level190is a positive error level, determines the updated electric activation to further increase the viscosity of the STF42, and outputs electric activation214-1-1and214-1-2to the emitters114-1-1and114-1-2respectively to facilitate slowing down the piston velocity back to the desired response curve. The method described above in conjunction with a processing module of any computing entity of the mechanical and computing system ofFIG.1can alternatively be performed by other modules of the system ofFIG.1or by other devices. In addition, at least one memory section that is non-transitory (e.g., a non-transitory computer readable storage medium, a non-transitory computer readable memory organized into a first memory element, a second memory element, a third memory element, a fourth element section, a fifth memory element, a sixth memory element, etc.) that stores operational instructions can, when executed by one or more processing modules of the one or more computing entities of the computing system10, cause one or more computing devices of the mechanical and computing system ofFIG.1to perform any or all of the method steps described above. FIGS.9A-9Care schematic block diagrams of another embodiment of a mechanical and computing system illustrating another example of controlling operational aspects. The mechanical and computing system includes the head unit10-1ofFIG.1, the object12-1ofFIG.1, and the computing entity20-1ofFIG.1. In particular, the head unit10-1for controlling motion of the object12-1includes the chamber16filled at least in part with the shear thickening fluid (STF)42. The piston is housed at least partially radially within the chamber16. The piston36is configured to exert pressure against the shear thickening fluid in response to movement of the piston36from a force applied to the piston36via the plunger28from the object12-1. The movement of the piston36includes one of traveling through the chamber16in an inward direction or traveling through the chamber16in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. The head unit10-1further includes a set of audio sensors positioned proximal to the chamber16and a set of audio emitters positioned proximal to the chamber16. For example, sensors116-1-1and116-1-2and emitters114-1-1and114-1-2, where the sensors and emitters sense and emit acoustic waves respectively to interact with the STF42. For instance, sensor116-1-1is implemented utilizing a microphone and emitter114-1-1is implemented utilizing an ultrasonic transducer. FIG.9Aillustrates an example of operation of a method for the controlling the operational aspects. A first step of the example of operation includes the computing entity20-1interpreting audio responses222-1-1and222-1-2from the STF42(e.g., in response to varying acoustic responsiveness of the particles of the STF) to produce a piston velocity and position. The set of audio sensors are positioned proximal to the head unit10-1for controlling motion of the object12-1, where the head unit includes the chamber filled at least in part with a shear thickening fluid (STF). In another embodiment, the STF is mixed with acoustic nanoparticles to enhance the transmission of acoustic waves through the STF. The piston is housed at least partially radially within the chamber and the piston configured to exert pressure against the shear thickening fluid in response to movement of the piston from a force applied to the piston from the object12-1. The movement of the piston includes one of traveling through the chamber in an inward direction or traveling through the chamber in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. As an example of interpreting the audio response222-1-1and222-1-2, the computing entity20-1compares the audio response222-1-1and222-1-2to previous measurements of audio waves versus piston velocity and position to produce the piston velocity182and piston position184. As another example of the interpreting the audio response222-1-1and222-1-2, the computing entity20-1extracts the piston velocity182and the piston position184directly from the audio response222-1-1and222-1-2when the sensors116-1-1and116-1-2generate the velocity and piston position directly. A second step of the example of operation includes the computing entity20-1determining a shear force186based on the piston velocity182and piston position184. For example, the computing entity20-1compares the velocity and position to stored data for instantaneous velocity and position versus shear force for the STF42. As another example, the computing entity20-1receives the shear force186from at least one of the set of sensors when at least one sensor provides the shear force186directly. In an instance, the shear force186reveals the piston velocity versus force applied to the piston curve as illustrated inFIG.9A, where at a current time of interpreting the audio response, the force and piston velocity are at a point X1. FIG.9Bfurther illustrates the example of operation of the method for the controlling the operational aspects. A third step of the example of operation includes the computing entity20-1determining a desired response188for the STF based on one or more of the shear force186and the piston velocity182and the piston position184. The desired response188includes continuing to follow a nominal response curve associated with the STF without modifying the functioning of the STF. The desired response188further includes modifying the function of the STF to further slow down the object12-1or to allow the object12-1to speed up at a velocity associated with the nominal response. The determining the desired response188includes one or more of interpreting a request, interpreting guidance from the chamber database34, detecting that the piston velocity is greater than a maximum piston velocity threshold level (e.g., too fast), detecting that the piston velocity is less than a minimum piston velocity threshold level (e.g., too slow), and detecting an environmental condition warranting changing the viscosity (e.g., a triggering of a vehicular airbag sensor, detection of an earthquake, a proximity warning, etc.). For instance, the computing entity20-1determines that the desired response188to slow down the object12-1is warranted based on reaching a maximum piston velocity threshold level for object12-1. Having determined the desired response188for the STF, a fourth step of the example method of operation includes the computing entity20-1generating an audio activation based on the desired response for the STF, where the audio activation is output to the set of audio emitters positioned proximal to the chamber16. The generating of the audio activation includes one or more of performing a lookup in an audio activation table for audio wave output values versus desired viscosity increases, dynamically calculating the audio wave output values based on a gap in viscosity levels, and receiving the audio activation from another computing entity. For example, the computing entity20-1determines the audio activation to affect the STF such that the viscosity is raised to lead to an abrupt slow down of the piston through the STF. Having determined the audio activation, the computing entity20-1outputs audio activation224-1-1and224-1-2to the emitters114-1-1and114-1-2respectively to affect the viscosity of the STF42. FIG.9Cfurther illustrates the example of operation of the method for the controlling the operational aspects where, having generated the audio activation, the computing entity20-1determines an error level190from the desired response for the STF42. For example, the computing entity20-1re-measures the audio response to determine one or more of piston velocity182, piston position184, and shear force186. Having determined velocity and position, the computing entity20-1determines actual response at a time X2 and compares the piston velocity versus force applied to the piston to the desired response curve. The computing entity20-1determines the error level190based on the comparison. Having determined the error level, a sixth step of the example of operation of the method for the controlling the operational aspects includes the computing entity20-1generating an updated audio activation based on the error level and the desired response. The error level is at least one of substantially zero (e.g., the actual response is on top of the desired response), a positive error level (e.g., when the actual response includes a piston velocity that is too high for the force applied to the piston), and a negative error level (e.g., when the actual response includes a piston velocity that is too low for the force applied to the piston). In an example of generating the updated audio activation, the computing entity20-1determines that the error level190is a positive error level, determines the updated audio activation to further increase the viscosity of the STF42, and outputs audio activation224-1-1and224-1-2to the emitters114-1-1and114-1-2respectively to facilitate slowing down the piston velocity back to the desired response curve. The method described above in conjunction with a processing module of any computing entity of the mechanical and computing system ofFIG.1can alternatively be performed by other modules of the system ofFIG.1or by other devices. In addition, at least one memory section that is non-transitory (e.g., a non-transitory computer readable storage medium, a non-transitory computer readable memory organized into a first memory element, a second memory element, a third memory element, a fourth element section, a fifth memory element, a sixth memory element, etc.) that stores operational instructions can, when executed by one or more processing modules of the one or more computing entities of the computing system10, cause one or more computing devices of the mechanical and computing system ofFIG.1to perform any or all of the method steps described above. FIGS.10A-10Care schematic block diagrams of another embodiment of a mechanical and computing system illustrating another example of controlling operational aspects. The mechanical and computing system includes the head unit10-1ofFIG.1, the object12-1ofFIG.1, and the computing entity20-1ofFIG.1. In particular, the head unit10-1for controlling motion of the object12-1includes the chamber16filled at least in part with the shear thickening fluid (STF)42. The piston is housed at least partially radially within the chamber16. The piston36is configured to exert pressure against the shear thickening fluid in response to movement of the piston36from a force applied to the piston36via the plunger28from the object12-1. The movement of the piston36includes one of traveling through the chamber16in an inward direction or traveling through the chamber16in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. The head unit10-1further includes a set of fluid flow sensors (e.g., any type) positioned proximal to the chamber16and a set of fluid manipulation emitters (e.g., any type) positioned proximal to the chamber16. For example, sensors116-1-1and116-1-2and emitters114-1-1and114-1-2, where the sensors and emitters sense and emit energy respectively to interact with the STF42. FIG.10Aillustrates an example of operation of a method for the controlling the operational aspects. A first step of the example of operation includes the computing entity20-1interpreting fluid responses232-1-1and232-1-2from the STF42(e.g., in response to varying responsiveness of the particles of the STF) to produce a piston velocity and position. The set of fluid flow sensors are positioned proximal to the head unit10-1for controlling motion of the object12-1, where the head unit includes the chamber filled at least in part with the shear thickening fluid (STF)42. In another embodiment, the STF is mixed with nanoparticles to enhance the transmission of energy through the STF. The piston is housed at least partially radially within the chamber and the piston configured to exert pressure against the shear thickening fluid in response to movement of the piston from a force applied to the piston from the object12-1. The movement of the piston includes one of traveling through the chamber in an inward direction or traveling through the chamber in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. As an example of interpreting the fluid response232-1-1and232-1-2, the computing entity20-1compares the fluid response232-1-1and232-1-2to previous measurements of fluid responses versus piston velocity and position to produce the piston velocity182and piston position184. As another example of the interpreting the fluid response232-1-1and232-1-2, the computing entity20-1extracts the piston velocity182and the piston position184directly from the fluid response232-1-1and/or232-1-2when the sensors116-1-1and116-1-2generate the velocity and piston position directly. A second step of the example of operation includes the computing entity20-1determining a shear force186based on the piston velocity182and piston position184. For example, the computing entity20-1compares the velocity and position to stored data for instantaneous velocity and position versus shear force for the STF42. As another example, the computing entity20-1receives the shear force186from at least one of the set of sensors when at least one sensor provides the shear force186directly. In an instance, the shear force186reveals the piston velocity versus force applied to the piston curve as illustrated inFIG.10A, where at a current time of interpreting the audio response, the force and piston velocity are at a point Y1. That curve further illustrates nominal responses for both positive and negative velocities corresponding to inward and outward movement of the piston. FIG.10Bfurther illustrates the example of operation of the method for the controlling the operational aspects. A third step of the example of operation includes the computing entity20-1determining a desired response188for the STF based on one or more of the shear force186and the piston velocity182and the piston position184. The desired response188includes continuing to follow a nominal response curve associated with the STF without modifying the functioning of the STF. The desired response188further includes modifying the function of the STF to further slow down the object12-1or to allow the object12-1to speed up at a velocity associated with the nominal response. The determining the desired response188includes one or more of interpreting a request, interpreting guidance from the chamber database34, detecting that the piston velocity is greater than a maximum piston velocity threshold level (e.g., too fast), detecting that the piston velocity is less than a minimum piston velocity threshold level (e.g., too slow), and detecting an environmental condition warranting changing the viscosity (e.g., a triggering of a vehicular airbag sensor, detection of an earthquake, a proximity warning, etc.). For instance, the computing entity20-1determines that the desired response188to slow down the object12-1is warranted based on reaching a maximum piston velocity threshold level for object12-1. Having determined the desired response188for the STF, a fourth step of the example method of operation includes the computing entity20-1generating a fluid activation based on the desired response for the STF, where the fluid activation is output to the set of fluid manipulation emitters positioned proximal to the chamber16. The generating of the fluid activation includes one or more of performing a lookup in a fluid activation table for fluid activation output values versus desired viscosity increases, dynamically calculating the fluid activation output values based on a gap in viscosity levels, and receiving the fluid activation from another computing entity. For example, the computing entity20-1determines the fluid activation to affect the STF such that the viscosity is raised to lead to an abrupt slow down of the piston through the STF as the actual response moves from a position at a time associated with Y1 to another position at another time associated with Y2. Having determined the fluid activation, the computing entity20-1outputs fluid activation234-1-1and234-1-2to the emitters114-1-1and114-1-2respectively to affect the viscosity of the STF42. FIG.10Cfurther illustrates the example of operation of the method for the controlling the operational aspects where, having generated the fluid activation, the computing entity20-1detects an oscillation associated with the object12-1and piston36. For example, the computing entity20-1re-measures the fluid response to determine one or more of piston velocity182, piston position184, and shear force186. Having determined velocity and position, the computing entity determines actual response at a time Y2 going to Y3 and compares the piston velocity versus force applied to the piston to the desired response curve. The computing entity20-1indicates the acylation when the velocity changes between positive and negative for several cycles. Having detected the oscillation, a sixth step of the example of operation of the method for the controlling the operational aspects includes the computing entity20-1generating an updated fluid activation based on the detected oscillation. The oscillation has an associated frequency and magnitude pattern. In an example of generating the updated fluid activation, the computing entity20-1determines that and updated desired response should include a dampened oscillation to lead the piston and object12-12lower magnitudes of the oscillation. The computing entity20-1outputs the fluid activation234-1-1and234-1-2to the emitters114-1-1and114-1-2respectively to facilitate slowing down the oscillation to that of the updated desired response. The method described above in conjunction with a processing module of any computing entity of the mechanical and computing system ofFIG.1can alternatively be performed by other modules of the system ofFIG.1or by other devices. In addition, at least one memory section that is non-transitory (e.g., a non-transitory computer readable storage medium, a non-transitory computer readable memory organized into a first memory element, a second memory element, a third memory element, a fourth element section, a fifth memory element, a sixth memory element, etc.) that stores operational instructions can, when executed by one or more processing modules of the one or more computing entities of the computing system cause one or more computing devices of the mechanical and computing system ofFIG.1to perform any or all of the method steps described above. FIGS.11A-11Bare schematic block diagrams of another embodiment of a mechanical and computing system illustrating another example of controlling operational aspects. The mechanical and computing system includes the head unit10-1ofFIG.1, the object12-1ofFIG.1, and the computing entity20-1ofFIG.1. In particular, the head unit10-1for controlling motion of the object12-1includes shear thickening fluid (STF)42. The STF42is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. The second range of shear rates are greater than the first range of shear rates. The head unit10-1further includes a chamber16, the chamber configured to contain a portion of the STF. The chamber includes a piston compartment23and an auxiliary compartment241. The head unit10-1further includes an auxiliary bypass244configured within the chamber16. The auxiliary bypass244couples the piston compartment23and the auxiliary compartment241controlling flow of the STF42between the piston compartment and the auxiliary compartment. The head unit10-1further includes a piston36housed at least partially radially within the piston compartment23of the chamber16. The piston is configured to exert pressure against the shear thickening fluid in response to movement of the piston from a force applied to the piston from the object12-1. The movement of the piston includes one of traveling through the piston compartment of the chamber in an inward direction (e.g., towards a back channel partition242separating the piston compartment23from the auxiliary compartment241) or traveling through the piston compartment of the chamber in an outward direction (e.g., towards a plunger bushing32). The head unit10-1further includes a set of fluid flow sensors116-1-1and116-1-2positioned proximal to the chamber. The set of fluid flow sensors provide a fluid response232-1-1and232-1-2from the STF. The head unit10-1further includes a set of fluid manipulation emitters114-1-1and114-1-2positioned proximal to the chamber. The set of fluid manipulation emitters provide a fluid activation to the STF such that one of the first range of shear rates or the second range of shear rates is selected for the STF within the piston compartment. The fluid activation further includes controlling the auxiliary bypass244. FIG.11Aillustrates an example of operation of a method for the controlling the operational aspects. A first step of the example of operation includes the computing entity20-1interpreting a fluid response from the set of fluid flow sensors to produce a piston velocity and a piston position of the piston associated with the head unit device. For example, the computing entity20-1interprets fluid responses232-1-1and232-1-2from the STF42(e.g., in response to varying responsiveness of the particles of the STF) to produce the piston velocity and the piston position. The interpreting the fluid flow response from the set of fluid flow sensors to produce the piston velocity and the piston position of the piston includes a series of sub-steps. A first sub-step includes inputting, from one or more fluid flow sensors of the set of fluid flow sensors, a set of fluid flow signals over a time range. For example, the computing entity20-1receives fluid responses232-1-1and232-1-2over the time range, where the fluid responses include the fluid flow signals. A second sub-step includes determining the fluid flow response of the set of fluid flow sensors based on the set of fluid flow signals. For example, the computing entity20-1interprets the fluid flow signals to produce the fluid flow response. A third sub-step includes determining the piston velocity based on the fluid flow response of the set of fluid flow sensors over the time range. For example, the computing entity20-1calculates piston velocity based on changes in the fluid flow response over the time range. A fourth sub-step includes determining the piston position based on the piston velocity and a real-time reference. For example, the computing entity20-1calculates the piston position based on time in the piston velocity as the piston moves through the chamber. As yet another example of interpreting the fluid response232-1-1and232-1-2, the computing entity20-1compares the fluid response232-1-1and232-1-2to previous measurements of fluid flow versus piston velocity and piston position to produce the piston velocity182and piston position184. As a still further example of the interpreting the fluid response232-1-1and232-1-2, the computing entity20-1extracts the piston velocity182and the piston position184directly from the fluid response232-1-1and/or232-1-2when the sensors116-1-1and116-1-2generate the piston velocity and piston position directly. A second step of the example of operation includes the computing entity20-1determining a shear force186based on the piston velocity182and the piston position184. The determining the shear force based on the piston velocity and the piston position includes one approach of a variety of approaches. A first approach includes extracting the shear force directly from the fluid flow response when one or more fluid flow sensors of the set of fluid flow sensors outputs a shear force encoded signal. For example, the computing entity20-1extracts the shear force186directly from the fluid responses232-1-1and232-1-2. In an instance, the shear force186reveals the piston velocity versus force applied to the piston curve as illustrated inFIG.11A, where at a current time of interpreting the fluid flow response, the force and piston velocity are at a point X1. A second approach includes determining the shear force utilizing the piston velocity and stored data for piston velocity versus shear force for the STF. For example, the computing entity20-1compares the velocity and position to stored data for instantaneous velocity and position versus shear force for the STF42. A third approach includes determining the shear force utilizing the piston position and stored data for piston position and an auxiliary bypass status246versus shear force for the STF within the chamber. For example, the computing entity20-1compares the velocity and position to stored data for instantaneous velocity and position versus shear force for the STF42based on an actual valve opening status of the auxiliary bypass244. FIG.11Bfurther illustrates the example of operation of the method for the controlling the operational aspects. A third step of the example of operation includes the computing entity20-1determining a desired response188for the STF based on one or more of the shear force186and the piston velocity182and the piston position184. The desired response188includes continuing to follow a nominal response curve associated with the STF without modifying the functioning of the STF. The desired response188further includes modifying the function of the STF to further slow down the object12-1or to allow the object12-1to speed up at a velocity associated with the nominal response. The determining the desired response for the STF based on one or more of the shear force, the piston velocity, and piston position includes one or more approaches. A first approach includes interpreting a request associated with modifying one or more of object velocity and object position. For example, the computing entity20-1interprets a request from another computing entity to update the desired response for the STF to decrease viscosity to speed up the object12-1. A second approach includes interpreting guidance from a chamber database. For example, the computing entity20-1interprets data from the chamber database34ofFIG.1Ato identify a response for the STF. For instance, the response for the STF is updated to decrease viscosity when historical information in the chamber database34indicates that a decrease in viscosity is desired based on a current piston position and current shear force. A third approach includes establishing the desired response to include facilitating the second range of shear rates to slow down the object when detecting that the piston position is greater than a maximum piston position threshold level. A fourth approach includes establishing the desired response to include facilitating the first range of shear rates to speed up the object when detecting that the piston position is less than a minimum piston position threshold level. A fifth approach includes establishing the desired response to include facilitating the second range of shear rates to slow down the object when detecting that the piston velocity is greater than a maximum piston velocity threshold level. A sixth approach includes establishing the desired response to include facilitating the first range of shear rates to speed up the object when detecting that the piston velocity is less than a minimum piston velocity threshold level. A seventh approach includes establishing the desired response to include facilitating the second range of shear rates to slow down the object when detecting that the shear force is less than a minimum shear force threshold level. An eighth approach includes establishing the desired response to include facilitating the first range of shear rates to speed up the object when detecting that the shear force is greater than a maximum shear force threshold level. A ninth approach includes detecting an environmental condition warranting a change in viscosity of the STF. For example, the computing entity20-1determines to change the viscosity of the STF when an emergency is detected. A tenth approach includes establishing the desired response to include activation of the auxiliary bypass to cause flow of the STF from the piston compartment to the auxiliary compartment when establishing the desired response to include facilitating the first range of shear rates. An eleventh approach includes establishing the desired response to include activation of the auxiliary bypass to cause flow of the STF from the auxiliary compartment to the piston compartment when establishing the desired response to include facilitating the second range of shear rates. Having determined the desired response188for the STF, a fourth step of the example method of operation includes the computing entity20-1activating the auxiliary bypass244in accordance with the desired response188for the STF to adjust the STF flow between the piston compartment23and the auxiliary compartment241to cause selection of one of the first range of shear rates or the second range of shear rates for the STF within the piston compartment23. The activating the auxiliary bypass in accordance with the desired response for the STF to adjust the STF flow between the piston compartment and the auxiliary compartment includes one or more of a variety of approaches. A first approach includes generating a fluid activation to cause flow of the STF from the piston compartment to the auxiliary compartment when the desired response for the STF includes facilitating the first range of shear rates. For instance, the computing entity20-1outputs the fluid activation234-1-1to the auxiliary bypass244to cause the STF to retreat to the auxiliary compartment241thusly reducing STF shear force in the piston compartment23and selecting the first range of shear rates (e.g., lower viscosity to speed up the object12-1moving from position X1 to a position X2 as illustrated inFIG.11B). A second approach includes generating the fluid activation to cause flow of the STF from the auxiliary compartment to the piston compartment when the desired response for the STF includes facilitating the second range of shear rates. For instance, the computing entity20-1outputs the fluid activation234-1-1to the auxiliary bypass244to cause the STF to move into the piston compartment23thusly increasing STF shear forces in the piston compartment23and selecting the second range of shear rates (e.g., higher viscosity to slow down the object12-1). In an embodiment, the process repeats where further fluid response is utilized to recalculate the desired response. The computing entity20-1updates the adjustment to the auxiliary bypass244and/or the emitters114-1-1and114-1-2based on the recalculated desired response. The method described above in conjunction with a processing module of any computing entity of the mechanical and computing system ofFIG.1can alternatively be performed by other modules of the system ofFIG.1or by other devices. In addition, at least one memory section that is non-transitory (e.g., a non-transitory computer readable storage medium, a non-transitory computer readable memory organized into a first memory element, a second memory element, a third memory element, a fourth element section, a fifth memory element, a sixth memory element, etc.) that stores operational instructions can, when executed by one or more processing modules of the one or more computing entities of the computing system10, cause one or more computing devices of the mechanical and computing system ofFIG.1to perform any or all of the method steps described above. FIGS.12A-12Bare schematic block diagrams of another embodiment of a mechanical and computing system illustrating another example of controlling operational aspects. The mechanical and computing system includes the head unit10-1ofFIG.1, the object12-1ofFIG.1, and the computing entity20-1ofFIG.1. In particular, the head unit10-1for controlling motion of the object12-1includes shear thickening fluid (STF)42. The STF42is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. The second range of shear rates are greater than the first range of shear rates. The head unit10-1further includes an alternative shear thickening fluid (ASTF)256. The ASTF256is configured to have a decreasing viscosity in response to a third range of shear rates and an increasing viscosity in response to a fourth range of shear rates. The fourth range of shear rates are greater than the third range of shear rates. The head unit10-1further includes a chamber16. The chamber configured to contain a portion of the STF and a portion of the ASTF. The chamber includes a piston compartment23and an alternative reservoir250. The head unit10-1further includes a reservoir injector254configured within the chamber. The reservoir injector254couples the piston compartment23and the alternative reservoir250controlling flow of the ASTF256from the alternative reservoir250to the piston compartment23. In an embodiment, a reservoir petition252separates the alternative reservoir250and the piston compartment23within the chamber16. The head unit10-1further includes a piston36housed at least partially radially within the piston compartment23of the chamber16. The piston is configured to exert pressure against one or more of the STF42and the ASTF256in response to movement of the piston36from a force applied to the piston from the object12-1. The movement of the piston includes one of traveling through the piston compartment of the chamber in an inward direction or traveling through the piston compartment of the chamber in an outward direction. The head unit10-1further includes a set of fluid flow sensors116-1-1and116-1-2positioned proximal to the chamber16. The set of fluid flow sensors provide a fluid response232-1-1and232-1-2from the STF42. The head unit10-1further includes a set of fluid manipulation emitters114-1-1and114-1-2positioned proximal to the chamber16. The set of fluid manipulation emitters provide a fluid activation to the one or more of the STF42and the ASTF256such that one of the first range of shear rates, the second range of shear rates, a modified first range of shear rates, or a modified second range of shear rates is selected for the one or more of STF and the ASTF within the piston compartment23. The fluid activation further includes controlling the reservoir injector254to control inflow of the alternative shear thickening fluid256from the alternative reservoir250to the piston compartment23causing a mixture of the two shear thickening fluids. In an example, such inflow occurs only once, during an emergency. The mixture of the STF and the ASTF is configured to have a decreasing viscosity in response to the modified first range of shear rates and an increasing viscosity in response to the modified second range of shear rates. The modified second range of shear rates are greater than the modified first range of shear rates. FIG.12Aillustrates an example of operation of a method for the controlling the operational aspects. A first step of the example of operation includes the computing entity20-1interpreting fluid responses232-1-1and232-1-2from the fluid flow sensors of the STF42(e.g., in response to varying responsiveness of the particles of the STF) to produce a piston velocity and piston position of the piston associated with the head unit. For example, the computing entity20-1interprets fluid responses232-1-1and232-1-2from the sensors116-1-1and116-1-24the STF42(e.g., in response to varying responsiveness of the particles of the STF) to produce the piston velocity and the piston position. The interpreting the fluid flow response from the set of fluid flow sensors to produce the piston velocity and the piston position of the piston includes a series of sub-steps. A first sub-step includes inputting, from one or more fluid flow sensors of the set of fluid flow sensors, a set of fluid flow signals over a time range. For example, the computing entity20-1receives fluid responses232-1-1and232-1-2over the time range, where the fluid responses include the fluid flow signals. A second sub-step includes determining the fluid flow response of the set of fluid flow sensors based on the set of fluid flow signals. For example, the computing entity20-1interprets the fluid flow signals to produce the fluid flow response. A third sub-step includes determining the piston velocity based on the fluid flow response of the set of fluid flow sensors over the time range. For example, the computing entity20-1calculates piston velocity based on changes in the fluid flow response over the time range. A fourth sub-step includes determining the piston position based on the piston velocity and a real-time reference. For example, the computing entity20-1calculates the piston position based on time in the piston velocity as the piston moves through the chamber. As yet another example of interpreting the fluid response232-1-1and232-1-2, the computing entity20-1compares the fluid response232-1-1and232-1-2to previous measurements of fluid flow versus piston velocity and piston position to produce the piston velocity182and piston position184. As a still further example of the interpreting the fluid response232-1-1and232-1-2, the computing entity20-1extracts the piston velocity182and the piston position184directly from the fluid response232-1-1and/or232-1-2when the sensors116-1-1and116-1-2generate the piston velocity and piston position directly. A second step of the example of operation includes the computing entity20-1determining a shear force186based on the piston velocity182and the piston position184. The determining the shear force based on the piston velocity and the piston position includes one approach of a variety of approaches. A first approach includes extracting the shear force directly from the fluid flow response when one or more fluid flow sensors of the set of fluid flow sensors outputs a shear force encoded signal. For example, the computing entity20-1extracts the shear force186directly from the fluid responses232-1-1and232-1-2. In an instance, the shear force186reveals the piston velocity versus force applied to the piston curve as illustrated inFIG.12A, where at a current time of interpreting the fluid flow response, the force and piston velocity are at a point X1. A second approach includes determining the shear force utilizing the piston velocity and stored data for piston velocity versus shear force for the STF, the ASTF, and the mixture of the STF and the ASTF. For example, the computing entity20-1compares the velocity and position to stored data for instantaneous velocity and position versus shear force. A third approach includes determining the shear force utilizing the piston position and stored data for piston position and a status of the reservoir injector versus shear force for the one of the STF, the ASTF, and the mixture of the STF and the ASTF within the chamber. For example, the computing entity20-1compares the velocity and position to stored data for instantaneous velocity and position versus shear force based on an actual valve opening status of the reservoir injector254. In an instance, the shear force186reveals the piston velocity versus force applied to the piston curve as illustrated inFIG.12A, where at a current time of interpreting the fluid response, the force and piston velocity are at a point X1. FIG.12Bfurther illustrates the example of operation of the method for the controlling the operational aspects. A third step of the example of operation includes the computing entity20-1determining a desired response188, for the one or more of the STF and the ASTF based on one or more of the shear force186and the piston velocity182and the piston position184, where the desired response188includes injecting the alternative STF256into the back channel24. As an example, the desired response188further includes modifying the function of the STF by mixing it with the alternative STF to further slow down the object12-1associated with the new desired response. The determining the desired response for the one or more of the STF and the ASTF based on one or more of the shear force, the piston velocity, and piston position includes one or more approaches. A first approach includes interpreting a request associated with modifying one or more of object velocity and object position. For example, the computing entity20-1interprets a request from another computing entity to update the desired response for the STF to increase viscosity to slow down the object12-1. A second approach includes interpreting guidance from a chamber database. For example, the computing entity20-1interprets data from the chamber database34ofFIG.1Ato identify a response. For instance, the response is established and/or updated to decrease viscosity when historical information in the chamber database34indicates that a decrease in viscosity is desired based on a current piston position and current shear force. A third approach includes establishing the desired response to include facilitating the second range of shear rates to slow down the object when detecting that the piston position is greater than a maximum piston position threshold level. A fourth approach includes establishing the desired response to include facilitating the first range of shear rates to speed up the object when detecting that the piston position is less than a minimum piston position threshold level. A fifth approach includes establishing the desired response to include facilitating the second range of shear rates to slow down the object when detecting that the piston velocity is greater than a maximum piston velocity threshold level. A sixth approach includes establishing the desired response to include facilitating the first range of shear rates to speed up the object when detecting that the piston velocity is less than a minimum piston velocity threshold level. A seventh approach includes establishing the desired response to include facilitating the second range of shear rates to slow down the object when detecting that the shear force is less than a minimum shear force threshold level. An eighth approach includes establishing the desired response to include facilitating the first range of shear rates to speed up the object when detecting that the shear force is greater than a maximum shear force threshold level. A ninth approach includes detecting an environmental condition warranting a change in viscosity of the STF. For example, the computing entity20-1determines to change the viscosity of the STF when a previous emergency has been resolved. A tenth approach includes establishing the desired response188to include activation of the reservoir injector to cause flow of the ASTF from the alternative reservoir to the piston compartment when establishing the desired response to include facilitating the modified first range of shear rates. In an embodiment, the modified first range of shear rates is less than the first range of shear rates. An eleventh approach includes establishing the desired response to include activation of the reservoir injector to cause flow of the ASTF from the alternative reservoir to the piston compartment when establishing the desired response to include facilitating the modified second range of shear rates. In an embodiment, the modified second range of shear rates is greater than the second range of shear rates. In an instance, the desired response188includes slowing down the velocity of the piston from the point X1 to a point X2 as illustrated inFIG.12B. Having determined the desired response188for the STF, a fourth step of the example method of operation includes the computing entity20-1activating the reservoir injector254in accordance with the desired response188for the one or more of the STF and the ASTF to adjust the flow of the ASTF256from the alternative reservoir250to the piston compartment23to cause selection of one of the first range of shear rates, the second range of shear rates, the modified first range of shear rates, or the modified second range of shear rates for the one or more of STF and the ASTF within the piston compartment23. The activating the reservoir injector in accordance with the desired response for the one or more of the STF and the ASTF to adjust the ASTF flow from the alternative reservoir to the piston compartment includes one or more sub-steps. A first sub-step includes generating a fluid activation to cause flow of the ASTF from the alternative reservoir to the piston compartment when the desired response for the one or more of the STF and the ASTF includes facilitating the modified first range of shear rates. For example, the computing entity20-1generates the fluid activation234-1-1to open the reservoir injector254when the alternative STF256is associated with the third range of shear rates (e.g., less than the first range of shear rates) such that the modified first range of shear rates is less than the first range of shear rates. A second sub-step includes generating the fluid activation to cause flow of the ASTF from the alternative reservoir to the piston compartment when the desired response for the one or more of the STF and the ASTF includes facilitating the modified second range of shear rates. For example, the computing entity20-1generates the fluid activation234-1-12open the reservoir injector254when the alternative STF256is associated with the fourth range of shear rates (e.g., greater than the second range of shear rates) such that the modified second range of shear rates is greater than the second range of shear rates to raise the viscosity of the fluid within the piston compartment23and slow down the object12-1moving from the point X1 to the point X2 as illustrated inFIG.12B. A third sub-step includes outputting the fluid activation to the reservoir injector. For example, the computing entity20-1outputs the fluid activation234-1-1to the reservoir injector254to facilitate opening of the reservoir injector254enabling the mixing of the alternative STF256and the STF42to produce the mixture. Having established the mixture within the piston compartment23, the object12-1moves in accordance with the desired response188. In an alternative embodiment, the reservoir injector254, on its own, mechanically detects an undesired attribute within the back channel24(e.g., pressure greater than a high pressure over threshold level) and opens to initiate the inflow of the alternative STF256into the back channel24to mix with the STF42to enable an emergency slow down of the object12-1. The method described above in conjunction with a processing module of any computing entity of the mechanical and computing system ofFIG.1can alternatively be performed by other modules of the system ofFIG.1or by other devices. In addition, at least one memory section that is non-transitory (e.g., a non-transitory computer readable storage medium, a non-transitory computer readable memory organized into a first memory element, a second memory element, a third memory element, a fourth element section, a fifth memory element, a sixth memory element, etc.) that stores operational instructions can, when executed by one or more processing modules of the one or more computing entities of the computing system cause one or more computing devices of the mechanical and computing system ofFIG.1to perform any or all of the method steps described above. FIGS.13A-13Bare schematic block diagrams of another embodiment of a mechanical and computing system illustrating another example of controlling operational aspects. The mechanical and computing system includes the head unit10-1ofFIG.1, the object12-1ofFIG.1, and the computing entity20-1ofFIG.1. In particular, the head unit10-1for controlling motion of the object12-1includes the chamber16filled at least in part with the shear thickening fluid (STF)42. The chamber16includes a piston compartment. The piston compartment includes the front channel26and the back channel24, where the variable partition260partitions the back channel24. The piston is housed at least partially radially within the piston compartment of the chamber16. The piston36is configured to exert pressure against the shear thickening fluid in response to movement of the piston36from a force applied to the piston36via the plunger28from the object12-1. The movement of the piston36includes one of traveling through the chamber16in an inward direction or traveling through the chamber16in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. The head unit10-1further includes a variable partition260positioned within the chamber between the piston and a closed end of the chamber to dynamically affect volume of the chamber based on activation of the variable partition. The head unit10-1further includes a set of fluid flow sensors positioned proximal to the chamber16and a set of fluid manipulation emitters positioned proximal to the chamber16. The set of fluid flow sensors provide a fluid response from the STF. The set of fluid manipulation emitters provide a fluid activation to the STF. For example, sensors116-1-1and116-1-2and emitters114-1-1and114-1-2are proximal to the chamber, where the sensors and emitters sense and emit energy respectively to interact with the STF42. FIG.13Aillustrates an example of operation of a method for the controlling the operational aspects. A first step of the example of operation includes the computing entity20-1interpreting fluid responses232-1-1and232-1-2from the STF42(e.g., in response to varying responsiveness of the particles of the STF) to produce a piston velocity and a piston position of the piston36. The set of fluid sensors are positioned proximal to the head unit10-1for controlling motion of the object12-1, where the head unit includes the chamber filled at least in part with a shear thickening fluid (STF). The piston is housed at least partially radially within the chamber and the piston configured to exert pressure against the shear thickening fluid in response to movement of the piston from a force applied to the piston from the object12-1. The movement of the piston includes one of traveling through the chamber in an inward direction or traveling through the chamber in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. The chamber includes the variable partition to dynamically affect volume of the chamber. The interpreting the fluid flow response from the set of fluid flow sensors to produce the piston velocity and the piston position of the piston includes a series of sub-steps. A first sub-step includes inputting, from one or more fluid flow sensors of the set of fluid flow sensors, a set of fluid flow signals over a time range. For example, the computing entity20-1receives fluid responses232-1-1and232-1-2over the time range, where the fluid responses include the fluid flow signals. A second sub-step includes determining the fluid flow response of the set of fluid flow sensors based on the set of fluid flow signals. For example, the computing entity20-1interprets the fluid flow signals to produce the fluid flow response. A third sub-step includes determining the piston velocity based on the fluid flow response of the set of fluid flow sensors over the time range. For example, the computing entity20-1calculates piston velocity based on changes in the fluid flow response over the time range. A fourth sub-step includes determining the piston position based on the piston velocity and a real-time reference. For example, the computing entity20-1calculates the piston position based on time in the piston velocity as the piston moves through the chamber. As yet another example of interpreting the fluid response232-1-1and232-1-2, the computing entity20-1compares the fluid response232-1-1and232-1-2to previous measurements of fluid flow versus piston velocity and piston position to produce the piston velocity182and piston position184. As a still further example of the interpreting the fluid response232-1-1and232-1-2, the computing entity20-1extracts the piston velocity182and the piston position184directly from the fluid response232-1-1and/or232-1-2when the sensors116-1-1and116-1-2generate the piston velocity and piston position directly. A second step of the example of operation includes the computing entity20-1determining a shear force186based on the piston velocity182and the piston position184. The determining the shear force based on the piston velocity and the piston position includes one approach of a variety of approaches. A first approach includes extracting the shear force directly from the fluid flow response when one or more fluid flow sensors of the set of fluid flow sensors outputs a shear force encoded signal. For example, the computing entity20-1extracts the shear force186directly from the fluid responses232-1-1and232-1-2. In an instance, the shear force186reveals the piston velocity versus force applied to the piston curve as illustrated inFIG.13A, where at a current time of interpreting the fluid flow response, the force and piston velocity are at a point X1. A second approach includes determining the shear force utilizing the piston velocity and stored data for piston velocity versus shear force for the STF. For example, the computing entity20-1compares the velocity and position to stored data for instantaneous velocity and position versus shear force for the STF42. A third approach includes determining the shear force utilizing the piston position and stored data for piston position versus shear force for the STF within the chamber. For example, the computing entity20-1compares the velocity and position to stored data for instantaneous velocity and position versus shear force for the STF42. FIG.13Bfurther illustrates the example of operation of the method for the controlling the operational aspects. A third step of the example of operation includes the computing entity20-1determining a desired response188for the STF based on one or more of the shear force186, the piston velocity182, and the piston position184, where the desired response188includes moving the variable partition260within the back channel24. The determining the desired response for the STF based on one or more of the shear force, the piston velocity, and piston position includes one or more approaches. A first approach includes interpreting a request associated with modifying one or more of object velocity and object position. For example, the computing entity20-1interprets a request from another computing entity to update the desired response for the STF to increase viscosity to slow down the object12-1. A second approach includes interpreting guidance from a chamber database. For example, the computing entity20-1interprets data from the chamber database34ofFIG.1Ato identify an updated response for the STF. For instance, the response for the STF is updated to decrease viscosity when historical information in the chamber database34indicates that a decrease in viscosity is desired based on a current piston position and current shear force. A third approach includes establishing the desired response to include facilitating the second range of shear rates to slow down the object when detecting that the piston position is greater than a maximum piston position threshold level. A fourth approach includes establishing the desired response to include facilitating the first range of shear rates to speed up the object when detecting that the piston position is less than a minimum piston position threshold level. A fifth approach includes establishing the desired response to include facilitating the second range of shear rates to slow down the object when detecting that the piston velocity is greater than a maximum piston velocity threshold level. A sixth approach includes establishing the desired response to include facilitating the first range of shear rates to speed up the object when detecting that the piston velocity is less than a minimum piston velocity threshold level. A seventh approach includes establishing the desired response to include facilitating the second range of shear rates to slow down the object when detecting that the shear force is less than a minimum shear force threshold level. An eighth approach includes establishing the desired response to include facilitating the first range of shear rates to speed up the object when detecting that the shear force is greater than a maximum shear force threshold level. A ninth approach includes detecting an environmental condition warranting a change in viscosity of the STF. For example, the computing entity20-1determines to change the viscosity of the STF when a triggering of a vehicular airbag sensor is detected. As another example, the computing entity20-1determines to change the viscosity of the STF when detecting an earthquake. As yet another example, the computing entity20-1determines to change the viscosity of the STF when detecting a proximity warning (e.g., of a certain collision). A tenth approach includes establishing the desired response to include activation of the variable partition to expand the volume of the chamber (e.g., move the variable partition away from the piston) when establishing the desired response to include facilitating the first range of shear rates. An eleventh approach includes establishing the desired response to include activation of the variable partition to contract the volume of the chamber (e.g., move the variable partition towards the piston) when establishing the desired response to include facilitating the second range of shear rates. Having determined the desired response188for the STF, a fourth step of the example method of operation includes the computing entity20-1activating the variable partition260in accordance with the desired response188for the STF to adjust the volume of the chamber. The activating the variable partition in accordance with the desired response for the STF to adjust the volume of the chamber includes one or more approaches. A first approach includes generating a variable partition activation235to expand the volume of the chamber when the desired response for the STF includes facilitating the first range of shear rates. A second approach includes generating the variable partition activation to contract the volume of the chamber when the desired response for the STF includes facilitating the second range of shear rates. A third approach includes outputting the variable partition activation to the variable partition. For example, the computing entity20-1outputs the variable partition activation235to the variable partition260facilitate moving of the variable partition260. Alternatively, or in addition to, the activating the variable partition260includes adjustment via one or more of the emitters. For example, the computing entity20-1determines to move the variable partition260further inwards to lower the viscosity of the STF to affect increasing the velocity of the object12-1as the actual response moves from the X1 to a position X2 by outputting fluid activation234-1-1and234-1-2to the emitters114-1-1and114-1-2respectively to move the variable partition260further inwards. In an alternative embodiment, the variable partition260, on its own, mechanically detects an undesired attribute within the back channel24(e.g., pressure greater than a high pressure over threshold level) and moves further inward to initiate the speeding up of the object12-1. The method described above in conjunction with a processing module of any computing entity of the mechanical and computing system ofFIG.1can alternatively be performed by other modules of the system ofFIG.1or by other devices. In addition, at least one memory section that is non-transitory (e.g., a non-transitory computer readable storage medium, a non-transitory computer readable memory organized into a first memory element, a second memory element, a third memory element, a fourth element section, a fifth memory element, a sixth memory element, etc.) that stores operational instructions can, when executed by one or more processing modules of the one or more computing entities of the computing system10, cause one or more computing devices of the mechanical and computing system ofFIG.1to perform any or all of the method steps described above. FIGS.14A-14Bare schematic block diagrams of an embodiment of a mechanical system illustrating an example of controlling operational aspects. The mechanical system includes the head unit10-1ofFIG.1and the object12-1ofFIG.1. In particular, the head unit10-1for controlling motion of the object12-1includes the chamber16filled at least in part with the shear thickening fluid (STF)42. The chamber16includes the front channel26and the back channel24. The piston is housed at least partially radially within the piston compartment of the chamber16. The piston36is configured to exert pressure against the shear thickening fluid in response to movement of the piston36from a force applied to the piston36via the plunger28from the object12-1. The movement of the piston36includes one of traveling through the chamber16in an inward direction or traveling through the chamber16in an outward direction. The piston36travels toward the back channel24and away from the front channel26when traveling in the inward direction. The piston travels toward the front channel26and away from the back channel24when traveling in the outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates. The piston36includes a first piston bypass38-1between opposite sides of the piston that controls flow of the STF between the opposite sides of the piston from the back channel24to the front channel26when the piston is traveling through the chamber in the inward direction to cause the STF to react with a first shear threshold effect. The piston36further includes a second piston bypass38-2between the opposite sides of the piston that controls flow of the STF between the opposite sides of the piston from the front channel26to the back channel24when the piston36is traveling through the chamber in the outward direction to cause the STF to react with a second shear threshold effect. In another embodiment, the piston includes a single piston bypass between opposite sides of the piston that controls flow of the STF between the opposite sides of the piston between the back channel and the front channel when the piston is traveling through the chamber to cause the STF to react with a shear threshold effect. When the piston36includes two or more piston bypasses, each piston bypass includes a one-way check valve and a variable flow valve. When the piston includes one piston bypass, the piston bypass includes the variable flow valve. The first piston bypass38-1and the second piston bypass38-2are configured with a particular diameter of the variable valve to allow the STF to flow through from one channel to the other of the chamber in accordance with a desired overall effect on viscosity of the STF42. The graph ofFIG.14Aillustrates a nominal response curve for plunger velocity versus force applied to the plunger taking into account different diameters of the piston bypasses. For example, when the first piston bypass38-1has a larger diameter opening as compared to the opening of the second piston bypass38-2, the (positive) velocity of the piston is allowed to travel faster since the effect on the viscosity is to lower the viscosity and hence raise the velocity of the piston traveling inward within the chamber. FIG.14Aillustrates an example of operation of the mechanical system for the controlling the operational aspects. A first step of the example of operation includes the piston moving inwards in response to the object12-1applying an inward force to the plunger28(e.g., pushing). The actual response is depicted on the graph ofFIG.14Awhere the actual response follows the nominal response expected for the STF as a point in time of Y1 is reached. When the piston is traveling through the chamber in the inward direction, the first shear threshold effect includes the first range of shear rates when the STF is configured to have the decreasing viscosity and the second range of shear rates when the STF is configured to have the increasing viscosity. A first setting of the variable flow valve of the first piston bypass38-1facilitates the first range of shear rates when the STF is to have the decreasing viscosity and a second setting of the variable flow valve facilitates the second range of shear rates when the STF is to have the increasing viscosity. When the piston is traveling through the chamber in the inward direction, the one-way check valve of the second piston bypass38-2prevents STF flow through second piston bypass38-2. In the alternative embodiment with the one piston bypass, when the piston is traveling through the chamber, a first setting of the variable flow valve of the one piston bypass facilitates the first range of shear rates when the STF is to have the decreasing viscosity and a second setting of the variable flow valve of the one piston bypass facilitates the second range of shear rates when the STF is to have the increasing viscosity. A second step of the example of operation includes the STF moving from the back channel24through the first piston bypass38-1to the front channel26at a first velocity to cause the STF to react with a first shear threshold effect. Larger diameters of the first piston bypass38-1lowers pressure and shear force within the back channel24leading to higher piston velocity as the piston moves inwards. FIG.14Bfurther illustrates the example of operation of the mechanical system for the controlling the operational aspects. A third step of the example of operation includes the piston36moving outwards in response to the object12-1applying an outward force to the plunger28(e.g., pulling). The actual response is depicted on a graph ofFIG.14Bwhere the actual response moves to follow the nominal response expected for the STF, at a point in time of Y2, when moving in the outward direction (e.g., negative piston velocity). When the piston is traveling through the chamber in the outward direction, the second shear threshold effect includes the first range of shear rates when the STF is configured to have the decreasing viscosity and the second range of shear rates when the STF is configured to have the increasing viscosity. In the alternative embodiment with the one piston bypass, when the piston is traveling through the chamber, the shear threshold effect includes the first range of shear rates when the STF is configured to have the decreasing viscosity and the second range of shear rates when the STF is configured to have the increasing viscosity. When the piston is traveling through the chamber in the outward direction, the one-way check valve of the first piston bypass prevents STF flow through the first piston bypass38-1. When the piston is traveling through the chamber in the outward direction a first setting of the variable flow valve of the second piston bypass facilitates the first range of shear rates when the STF is to have the decreasing viscosity and a second setting of the variable flow valve of the second piston bypass facilitates the second range of shear rates when the STF is to have the increasing viscosity. A third step of the example of operation includes the STF moving from the front channel26through the second piston bypass38-2to the back channel24at a second velocity to cause the STF42to react with a second shear threshold effect. The second velocity is less than the first velocity and the second shear threshold effect is more abrupt than the first shear threshold effect when the diameter of the second piston bypass38-2is less than the diameter of the first piston bypass38-1. As a result, the mechanical system provides an unequal bidirectional response for the inward and outward motion of the object12-1. It is noted that terminologies as may be used herein such as bit stream, stream, signal sequence, etc. (or their equivalents) have been used interchangeably to describe digital information whose content corresponds to any of a number of desired types (e.g., data, video, speech, text, graphics, audio, etc. any of which may generally be referred to as ‘data’). As may be used herein, the terms “substantially” and “approximately” provides an industry-accepted tolerance for its corresponding term and/or relativity between items. For some industries, an industry-accepted tolerance is less than one percent and, for other industries, the industry-accepted tolerance is 10 percent or more. Other examples of industry-accepted tolerance range from less than one percent to fifty percent. Industry-accepted tolerances correspond to, but are not limited to, component values, integrated circuit process variations, temperature variations, rise and fall times, thermal noise, dimensions, signaling errors, dropped packets, temperatures, pressures, material compositions, and/or performance metrics. Within an industry, tolerance variances of accepted tolerances may be more or less than a percentage level (e.g., dimension tolerance of less than +/−1%). Some relativity between items may range from a difference of less than a percentage level to a few percent. Other relativity between items may range from a difference of a few percent to magnitude of differences. As may also be used herein, the term(s) “configured to”, “operably coupled to”, “coupled to”, and/or “coupling” includes direct coupling between items and/or indirect coupling between items via an intervening item (e.g., an item includes, but is not limited to, a component, an element, a circuit, and/or a module) where, for an example of indirect coupling, the intervening item does not modify the information of a signal but may adjust its current level, voltage level, and/or power level. As may further be used herein, inferred coupling (i.e., where one element is coupled to another element by inference) includes direct and indirect coupling between two items in the same manner as “coupled to”. As may even further be used herein, the term “configured to”, “operable to”, “coupled to”, or “operably coupled to” indicates that an item includes one or more of power connections, input(s), output(s), etc., to perform, when activated, one or more its corresponding functions and may further include inferred coupling to one or more other items. As may still further be used herein, the term “associated with”, includes direct and/or indirect coupling of separate items and/or one item being embedded within another item. As may be used herein, the term “compares favorably”, indicates that a comparison between two or more items, signals, etc., provides a desired relationship. For example, when the desired relationship is that signal1has a greater magnitude than signal2, a favorable comparison may be achieved when the magnitude of signal1is greater than that of signal2or when the magnitude of signal2is less than that of signal1. As may be used herein, the term “compares unfavorably”, indicates that a comparison between two or more items, signals, etc., fails to provide the desired relationship. As may be used herein, one or more claims may include, in a specific form of this generic form, the phrase “at least one of a, b, and c” or of this generic form “at least one of a, b, or c”, with more or less elements than “a”, “b”, and “c”. In either phrasing, the phrases are to be interpreted identically. In particular, “at least one of a, b, and c” is equivalent to “at least one of a, b, or c” and shall mean a, b, and/or c. As an example, it means: “a” only, “b” only, “c” only, “a” and “b”, “a” and “c”, “b” and “c”, and/or “a”, “b”, and “c”. As may also be used herein, the terms “processing module”, “processing circuit”, “processor”, “processing circuitry”, and/or “processing unit” may be a single processing device or a plurality of processing devices. Such a processing device may be a microprocessor, micro-controller, digital signal processor, microcomputer, central processing unit, field programmable gate array, programmable logic device, state machine, logic circuitry, analog circuitry, digital circuitry, and/or any device that manipulates signals (analog and/or digital) based on hard coding of the circuitry and/or operational instructions. The processing module, module, processing circuit, processing circuitry, and/or processing unit may be, or further include, memory and/or an integrated memory element, which may be a single memory device, a plurality of memory devices, and/or embedded circuitry of another processing module, module, processing circuit, processing circuitry, and/or processing unit. Such a memory device may be a read-only memory, random access memory, volatile memory, non-volatile memory, static memory, dynamic memory, flash memory, cache memory, and/or any device that stores digital information. Note that if the processing module, module, processing circuit, processing circuitry, and/or processing unit includes more than one processing device, the processing devices may be centrally located (e.g., directly coupled together via a wired and/or wireless bus structure) or may be distributedly located (e.g., cloud computing via indirect coupling via a local area network and/or a wide area network). Further note that if the processing module, module, processing circuit, processing circuitry and/or processing unit implements one or more of its functions via a state machine, analog circuitry, digital circuitry, and/or logic circuitry, the memory and/or memory element storing the corresponding operational instructions may be embedded within, or external to, the circuitry comprising the state machine, analog circuitry, digital circuitry, and/or logic circuitry. Still further note that, the memory element may store, and the processing module, module, processing circuit, processing circuitry and/or processing unit executes, hard coded and/or operational instructions corresponding to at least some of the steps and/or functions illustrated in one or more of the Figures. Such a memory device or memory element can be included in an article of manufacture. One or more embodiments have been described above with the aid of method steps illustrating the performance of specified functions and relationships thereof. The boundaries and sequence of these functional building blocks and method steps have been arbitrarily defined herein for convenience of description. Alternate boundaries and sequences can be defined so long as the specified functions and relationships are appropriately performed. Any such alternate boundaries or sequences are thus within the scope and spirit of the claims. Further, the boundaries of these functional building blocks have been arbitrarily defined for convenience of description. Alternate boundaries could be defined as long as the certain significant functions are appropriately performed. Similarly, flow diagram blocks may also have been arbitrarily defined herein to illustrate certain significant functionality. To the extent used, the flow diagram block boundaries and sequence could have been defined otherwise and still perform the certain significant functionality. Such alternate definitions of both functional building blocks and flow diagram blocks and sequences are thus within the scope and spirit of the claims. One of average skill in the art will also recognize that the functional building blocks, and other illustrative blocks, modules, and components herein, can be implemented as illustrated or by discrete components, application specific integrated circuits, processors executing appropriate software and the like or any combination thereof. In addition, a flow diagram may include a “start” and/or “continue” indication. The “start” and “continue” indications reflect that the steps presented can optionally be incorporated in or otherwise used in conjunction with one or more other routines. In addition, a flow diagram may include an “end” and/or “continue” indication. The “end” and/or “continue” indications reflect that the steps presented can end as described and shown or optionally be incorporated in or otherwise used in conjunction with one or more other routines. In this context, “start” indicates the beginning of the first step presented and may be preceded by other activities not specifically shown. Further, the “continue” indication reflects that the steps presented may be performed multiple times and/or may be succeeded by other activities not specifically shown. Further, while a flow diagram indicates a particular ordering of steps, other orderings are likewise possible provided that the principles of causality are maintained. The one or more embodiments are used herein to illustrate one or more aspects, one or more features, one or more concepts, and/or one or more examples. A physical embodiment of an apparatus, an article of manufacture, a machine, and/or of a process may include one or more of the aspects, features, concepts, examples, etc., described with reference to one or more of the embodiments discussed herein. Further, from figure to figure, the embodiments may incorporate the same or similarly named functions, steps, modules, etc., that may use the same or different reference numbers and, as such, the functions, steps, modules, etc., may be the same or similar functions, steps, modules, etc. or different ones. Unless specifically stated to the contra, signals to, from, and/or between elements in a figure of any of the figures presented herein may be analog or digital, continuous time or discrete time, and single-ended or differential. For instance, if a signal path is shown as a single-ended path, it also represents a differential signal path. Similarly, if a signal path is shown as a differential path, it also represents a single-ended signal path. While one or more particular architectures are described herein, other architectures can likewise be implemented that use one or more data buses not expressly shown, direct connectivity between elements, and/or indirect coupling between other elements as recognized by one of average skill in the art. The term “module” is used in the description of one or more of the embodiments. A module implements one or more functions via a device such as a processor or other processing device or other hardware that may include or operate in association with a memory that stores operational instructions. A module may operate independently and/or in conjunction with software and/or firmware. As also used herein, a module may contain one or more sub-modules, each of which may be one or more modules. As may further be used herein, a computer readable memory includes one or more memory elements. A memory element may be a separate memory device, multiple memory devices, or a set of memory locations within a memory device. Such a memory device may be a read-only memory, random access memory, volatile memory, non-volatile memory, static memory, dynamic memory, flash memory, cache memory, a quantum register or other quantum memory and/or any other device that stores data in a non-transitory manner. Furthermore, the memory device may be in a form of a solid-state memory, a hard drive memory or other disk storage, cloud memory, thumb drive, server memory, computing device memory, and/or other non-transitory medium for storing data. The storage of data includes temporary storage (i.e., data is lost when power is removed from the memory element) and/or persistent storage (i.e., data is retained when power is removed from the memory element). As used herein, a transitory medium shall mean one or more of: (a) a wired or wireless medium for the transportation of data as a signal from one computing device to another computing device for temporary storage or persistent storage; (b) a wired or wireless medium for the transportation of data as a signal within a computing device from one element of the computing device to another element of the computing device for temporary storage or persistent storage; (c) a wired or wireless medium for the transportation of data as a signal from one computing device to another computing device for processing the data by the other computing device; and (d) a wired or wireless medium for the transportation of data as a signal within a computing device from one element of the computing device to another element of the computing device for processing the data by the other element of the computing device. As may be used herein, a non-transitory computer readable memory is substantially equivalent to a computer readable memory. A non-transitory computer readable memory can also be referred to as a non-transitory computer readable storage medium. While particular combinations of various functions and features of the one or more embodiments have been expressly described herein, other combinations of these features and functions are likewise possible. The present disclosure is not limited by the particular examples disclosed herein and expressly incorporates these other combinations. | 142,269 |
11859643 | DETAILED DESCRIPTION Now referring to the drawings, wherein like elements refer to like reference numbers, there is illustrated inFIG.1an exemplary embodiment of a reciprocating pump system (generally referred to by the reference numeral10) including a power end portion12and a fluid end portion14operably coupled thereto. The power end portion12includes a housing16in which a crankshaft (not shown) is disposed, as is known, the crankshaft being operably coupled to an engine or motor (not shown), as is known, which is configured to drive the crankshaft. The fluid end portion14includes a fluid end block18, which is connected to the housing16via a plurality of stay rods20. The fluid end block18includes a fluid inlet passage22and a fluid outlet passage24, which are spaced in a parallel relation. A plurality of fluid end retainer nut assemblies26, one of which is shown inFIG.1, is connected to the fluid end block18opposite the stay rods20. A plurality of cover assemblies28, one of which is shown inFIG.1, is connected to the fluid end block18opposite the fluid inlet passage22. A plunger rod assembly30extends out of the housing16and into the fluid end block18. Other configurations of a reciprocating pump system10are contemplated. In embodiments, as illustrated inFIG.2with continuing reference toFIG.1, the plunger rod assembly30includes a plunger32, which extends through a bore34formed in the fluid end block18, and into a fluid chamber36formed in the fluid end block18. The plunger32is reciprocally disposed in the fluid chamber36to generate fluid pressure therewithin. In embodiments, a plurality of parallel-spaced bores may be formed in the fluid end block18, with one of the bores being the bore34, a plurality of fluid chambers may be formed in the fluid end block18, with one of the fluid chambers being the fluid chamber36, and a plurality of parallel-spaced plungers may extend through respective ones of the bores and into respective ones of the fluid chambers, with one of the plungers being the plunger32. The fluid end block18includes inlet and outlet fluid passages38and40formed therein, which are generally coaxial along a fluid passage axis42. Under conditions to be described below, fluid flows from the inlet fluid passage38toward the outlet fluid passage40along the fluid passage axis42. The fluid inlet passage22is in fluid communication with the fluid chamber36via the inlet fluid passage38. The fluid chamber36is in fluid communication with the fluid outlet passage24via the outlet fluid passage40. The inlet fluid passage38may include an enlarged-diameter portion38aand a reduced-diameter portion38bextending downward therefrom (as in the figure), which direction may also be considered the upstream direction. Downstream from the enlarged-diameter portion38ais an inlet fluid passage neck38c, which is reduced in diameter relative to the enlarged-diameter portion. The enlarged diameter portion38adefines a tapered internal shoulder43and thus a frusto-conical surface44of the fluid end block18. The reduced-diameter portion38bdefines an inside surface46of the fluid end block18. Similarly, the outlet fluid passage40includes an enlarged-diameter portion40aand a reduced-diameter portion40bextending downward therefrom. The enlarged-diameter portion40adefines a tapered internal shoulder48and thus a frusto-conical surface50of the fluid end block18. The reduced-diameter portion40bdefines an inside surface52of the fluid end block18. The frusto-conical surfaces44,50form valve seats for respective inlet and outlet valves54,56. An inlet valve54is disposed in the inlet fluid passage38, and engages at least the frusto-conical surface44and the inside surface46. Similarly, an outlet valve56is disposed in the outlet fluid passage40, and engages at least the frusto-conical surface50and the inside surface52. In an exemplary embodiment, each of valves54and56is a spring-loaded valve that is actuated by a predetermined differential pressure thereacross. A counterbore58is formed in the fluid end block18, and is generally coaxial with the outlet fluid passage40along the fluid passage axis42. In embodiments, the fluid end block18may include a plurality of parallel-spaced counterbores, one of which may be the counterbore58, with the quantity of counterbores equaling the quantity of plunger throws included in the pump system10. The cover assembly28shown inFIGS.1and2includes at least a plug64and a fastener66. In embodiments, the cover assembly28may be disconnected from the fluid end block18to provide access to, for example, the counterbore58, the fluid chamber36, the plunger32, the outlet fluid passage40or the outlet valve56. In embodiments, the pump system10may include a plurality of plugs, one of which is the plug64, and a plurality of fasteners, one of which is the fastener66, with the respective quantities of plugs and fasteners equaling the quantity of plunger throws included in the pump system10. A counterbore60is formed in the fluid end block18, and is generally coaxial with the bore34along an axis62. The counterbore60defines an internal shoulder60aand includes an internal threaded connection60badjacent the internal shoulder60a. In embodiments, the fluid end block18may include a plurality of parallel-spaced counterbores, one of which may be the counterbore60, with the quantity of counterbores equaling the quantity of plunger throws included in the pump system10. The counterbore60is sized and shaped to receive a retainer nut assembly26(seeFIGS.3-6) according to embodiments disclosed herein. In embodiments, the retainer nut assembly26may be disconnected from the fluid end block18to provide access to, for example, the counterbore60, the fluid chamber36, the plunger32, the inlet fluid passage38, or the inlet valve54. The retainer nut assembly26may then be reconnected to the fluid end block in accordance with the foregoing. In several exemplary embodiments, the pump system10may include a plurality of plugs, one of which is the plug68, and a plurality of fasteners, one of which is the fastener70, with the respective quantities of plugs and fasteners equaling the quantity of plunger throws included in the pump system10. Focusing now on the inlet fluid passage38, a biasing member71is positioned within the inlet fluid passage38. The biasing member71may be a coil spring. In one embodiment the biasing member71is a conical coil spring. The biasing member71may be retained in place by a spring stop72as is known. When installed as shown inFIG.2, the biasing member71exerts a selected biasing force on the inlet valve54that holds the inlet valve against the frusto-conical surface44to create a closed or sealed condition. When a pressure differential on the inlet valve54exceeds the closing force generated by the biasing member71, the inlet valve opens and permits fluid media to enter the fluid chamber36. Turning toFIGS.3-6, the retainer nut assembly26includes a fastener70that is sized and shaped to be threaded, i.e., advanced, into the fluid end block18via an external thread70aof the fastener70. The external thread70ais configured to engage with the internal threads60bof the counterbore60. The external thread70ais formed at a first end70bof the generally cylindrical fastener70. The thread70amay be segmented to permit fluid to escape from inside the fluid chamber36. The fastener70holds a load piston104, which abuts and holds in place a suction cap or plug68in the fluid end block18when installed. The retainer nut assembly26includes a mechanism to preload the assembly when installed in the fluid end block18to reduce cyclical changes in force on the threaded connection70a,60bdue to the large changes in pressure generated inside the fluid end block. The large changes in pressure can cause alternating stress on the threaded connection70a,60b, which can cause the retainer nut assembly to loosen and the threads of the fastener to fatigue. Moreover, failure of the fluid end portion14can occur from the large amplitude of alternating stress and resulting damage caused to the retainer nut assembly26. For example, cracks can develop in the fluid end portion14from high cyclic stress. The retainer nut assembly26also may include a mechanism to determine if the assembly is preloaded a specified amount. Both of these mechanisms will be detailed hereinbelow. The plug68is sized and shaped to be disposed in the counterbore60, engaging the internal shoulder60aand sealingly engaging an inside cylindrical surface defined by the reduced-diameter portion of the counterbore60. In an exemplary embodiment, the plug68may be characterized or referred to as a suction cap. The load piston104may be provided with an annular load seal110disposed in an annular load groove112that is formed on the outer, circular periphery of the load piston. The fastener70may include two or more outwardly extending tabs or lugs80configured to be engaged and rotated by a tool82(FIG.6). The tabs80may each be a generally rectangular, outwardly extending part attached to the fastener70, for example by welding, in a configuration suitably spaced apart so as to enable the application of a sufficient amount of torque to rotate and secure the fastener70in place using the tool82. Each of the tabs80may have an opening84formed therethrough for receiving the tool82. For example, a pair of tabs80a,80bare arranged across from each other on opposite sides of or adjacent the outer periphery of the outer surface or second end86of the fastener70such that the openings84sufficiently align to enable the tool82to be inserted through both of the tabs. Applying a torque via the tool82conveys the torque through the tabs80a,80bto the fastener70. A clockwise torque (as viewed inFIG.6) with right-handed threads70aformed on the fastener70would have the effect of advancing the fastener into the fluid end block18, and vice versa. Two pairs of tabs80may be arranged at 90 degree orientations about and adjacent the periphery of the second end86to enable easy access via the tool82. Other configurations of tabs or engageable features are contemplated. The tool82may be a cylindrical bar, for example, or any suitable means of engaging the tabs80and exert a suitable amount of torque to advance the fastener70into the fluid end block18. The second end86of the fastener70also, as seen inFIG.3, includes a lock piece or locking bolt88, which may be a threaded fastener such as a hex bolt. Insertion and rotation of the lock piece88applies the preload to the retainer nut assembly26as will be explained below. As shown inFIGS.4-5, the lock piece88is threaded into the fastener70by engaging an internally threaded passage90formed in or through the fastener70. The internally threaded passage90may be formed in the center of the fastener, i.e., centered on an axial center92of the fastener70. The fastener70also may include a lock indicator93, which may include a piston or pressure transducer, sensor, or any suitable mechanism that responds to pressure as will be explained more fully herein and provides an indication when a specified preload force is being applied to the retainer nut assembly26. The lock indicator93may be biased by a spring106, wavy washer, or cone washer, or any suitable mechanism such that until a specified amount of force is acting on the lock indicator, the lock indicator does not extend from the second end86. The lock indicator93extends outwardly from the second end86when a specified preload force acts on the indicator. In alternative embodiments, the lock indicator93may be a sensor that generates a signal indicative of the forces being sensed thereby. In alternative embodiments, the lock indicator93may be a green-red hydraulic bypass indicator. In embodiments, the lock indicator93includes a post portion114disposed in a bore115formed in or through the fastener70and a piston portion116that is disposed in a port117. The port117has a greater diameter than that of the bore115so as to retain the lock indicator93when the lock indicator is being urged outwardly by fluid pressure in the port117. The fastener70includes formed in the first end70a, opposite the second end86, a cavity96with an annular groove100formed in the sidewall of the fastener adjacent the end opposite the outer surface. The groove100is sized and shaped to retain a snap ring102. The cylindrical cavity96is sized and shaped to movably receive the load piston104and, when the load piston is positioned within the cavity, the snap ring102is positioned to retain the load piston therein. The snap ring102may retain the load piston104by stopping against a shoulder108formed at the inner edge of the load piston. The shoulder108is configured to permit a limited amount of axial movement of the load piston104in the cavity96such that the load piston can be moved against the suction cap68. The fastener70also includes a pressure piston94disposed in a bore96formed in the fastener along the axis92. The pressure piston94is provided with two or more seals101. The seals101may include elastomeric O-rings, or any suitable means of sealing the bore96and pressure piston94. The bore96is also formed on the axial center92and is in communication with or open to the internally threaded passage90such that the lock piece88when inserted inwardly contacts the pressure piston94and can exert a force against the piston. The piston94has an axial length that is less than the length of the bore96and the bore is filled with a hydraulic fluid, such as grease for example. When the lock piece88is threaded inwardly and presses against the piston94, hydraulic pressure is generated within the bore96, which in turn is conveyed to the load piston104. When the load piston104is loaded via hydraulic pressure generated by advancing the lock piece88pressing against the piston94, the load piston generates pressure via the hydraulic fluid in the bore96, and the load piston104exerts pressure on the cap68. In return, a force opposite in direction is generated that urges the fastener70outwardly from the fluid end block18, which preloads the threads70a. Fluid pressure generated by the pressure piston94pushes fluid into the space between the cavity96and the load piston104and acts on the piston portion116of the indicator93to urge the indicator outwardly to provide an indication of hydraulic pressure being generated. Changes in pressure generated by the plunger32within the fluid chamber36act indirectly on the fastener70. When the threads70aare not preloaded, the threaded connection70a,60bbetween the fastener70and the fluid end block18experiences cyclical changes of stress. When the threads70aare preloaded, static stress is increased and peak to peak cyclic stress amplitude is greatly reduced. As a result, the threaded connection is more reliable, the status of the fluid end retainer nut assembly26is easily discernable, and the need for frequent maintenance is reduced. INDUSTRIAL APPLICABILITY The industrial applicability of the system described herein will be readily appreciated from the forgoing discussion. The foregoing discussion is applicable to fluid ends of reciprocating pump assemblies, in particular, for pumping fluid media in fracturing operations and similar applications. One example of the industrial application of the system according to embodiments of the disclosure, and referring also toFIGS.1-6, a method of installing a retainer nut assembly26includes manually threading the retainer nut assembly into a fluid end block18of a fluid end14of a reciprocating pump system10. In embodiments, with the suction cap68in position in the fluid end block18, and the load piston104positioned on the fastener70, in step120, the installation includes engaging a fastener portion70with a tool82and rotating/threading the fastener into the fluid end block18. Once the retainer nut assembly26is fully threaded into the fluid end block18, in step122, a locking bolt88is tightened. The locking bolt88may be tightened by rotating and advancing the locking bolt into the fastener70. In step124, advancement of the locking bolt88engages a pressure piston94, the advancement of which generates fluid pressure on a load piston104. The load piston104, in step126, generates a force on a suction cap68, which presses the suction cap into the fluid end block18. In step128, the fluid pressure generated also imparts a reaction load or force on the fastener70, which loads the fastener threads70a, in the outward direction relative to the fluid end block18. In step130, a lock indicator93, which is configured to respond to the generated fluid pressure and provide an indication whether a specified installation pressure is reached, provides an indication of the generated fluid pressure. It will be appreciated that the foregoing description provides examples of the disclosed system and technique. However, it is contemplated that other implementations of the disclosure may differ in detail from the foregoing examples. All references to the disclosure or examples thereof are intended to reference the particular example being discussed at that point and are not intended to imply any limitation as to the scope of the disclosure more generally. All language of distinction and disparagement with respect to certain features is intended to indicate a lack of preference for those features, but not to exclude such from the scope of the disclosure entirely unless otherwise indicated. Recitation of ranges of values herein are merely intended to serve as a shorthand method of referring individually to each separate value falling within the range, unless otherwise indicated herein, and each separate value is incorporated into the specification as if it were individually recited herein. All methods described herein can be performed in any suitable order unless otherwise indicated herein or otherwise clearly contradicted by context. Unless explicitly excluded, the use of the singular to describe a component, structure, or operation does not exclude the use of plural such components, structures, or operations or their equivalents. The use of the terms “a” and “an” and “the” and “at least one” or the term “one or more,” and similar referents in the context of describing the invention (especially in the context of the following claims) are to be construed to cover both the singular and the plural, unless otherwise indicated herein or clearly contradicted by context. The use of the term “at least one” followed by a list of one or more items (for example, “at least one of A and B” or one or more of A and B”) is to be construed to mean one item selected from the listed items (A or B) or any combination of two or more of the listed items (A and B; A, A and B; A, B and B), unless otherwise indicated herein or clearly contradicted by context. Similarly, as used herein, the word “or” refers to any possible permutation of a set of items. For example, the phrase “A, B, or C” refers to at least one of A, B, C, or any combination thereof, such as any of: A; B; C; A and B; A and C; B and C; A, B, and C; or multiple of any item such as A and A; B, B, and C; A, A, B, C, and C; etc. Accordingly, this disclosure includes all modifications and equivalents of the subject matter recited in the claims appended hereto as permitted by applicable law. Moreover, any combination of the above-described elements in all possible variations thereof is encompassed by the disclosure unless otherwise indicated herein or otherwise clearly contradicted by context. | 19,528 |
11859644 | DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS A piston assembly according to a preferred embodiment of the invention is illustrated inFIG.1and shown generally at reference numeral10. The assembly10comprises a piston rod12partially positioned within a hollow, cylindrical pressure tube14, shown in cross-section inFIG.1. A circular opening19is formed at one end of the tube14to allow for sliding movement of the piston rod12therethrough. The piston rod12includes a cylindrical piston head13, shown in cross-section inFIGS.1and2. The tube14can be a gas pressure tube made of carbon steel or other suitable material. A bore is formed at the outboard end of the piston rod12and receives a connecting rod16, as shown inFIG.1. A cylindrical sealing member24, shown in cross-section inFIGS.1and2, is positioned within the pressure tube14adjacent the opening19in the tube14and around the rod12to prevent leakage of gas and/or liquid from the pressure tube14. Threads18are formed on the external surface of the rod12at the outboard end of the rod12, as shown inFIG.1. A lock nut28engages the threads28on the piston rod12. The lock nut28has a diameter greater than the opening in the pressure tube14and prevents further movement of the piston rod12when the lock nut28contacts the tube14during a compression stroke of the rod12. Alternatively, a jam nut or other fastener can be used in place of the lock nut28. The piston assembly10includes a linear position sensing system. The linear position sensing system comprises a position sensor20. Preferably, the position sensor is a waveguide sensor. The sensor20is attached to the connecting rod16and positioned within a housing22. The sensor housing22has an inner diameter greater than the outer diameter of the sensor20so that the sensor housing22can receive the sensor20. Preferably, the sensor housing22is made of aluminum or nylon 6/6. A cap section23is attached to the housing22to enclose the sensor20within the housing22, as shown inFIGS.3and4. The cap23can be attached to the housing22with screws25or other suitable fasteners. The end fittings31,32can be positioned at opposite ends of the piston assembly10, as shown inFIG.1. A cylindrical magnet30, shown in cross-section inFIGS.1and2, is positioned inside the pressure tube14. The magnet30can be comprised of iron, nickel, cobalt or other suitable magnetic material. The piston rod12can be comprised of a non-magnetic material, such as a non-ferrous metal or an austenitic stainless steel. Preferably, the magnet30is embedded in a cylindrical plastic spacer33, shown in cross-section inFIGS.1and2. The magnet30can be attached to the spacer33by an adhesive or can be over-molded into the plastic spacer33. External grooves15,17can be formed on the pressure tube14. The magnet30and spacer33can be held in place relative to the pressure tube14by the grooves15,17. The waveguide sensor20detects the position of the magnet30and the distance between the sensor20and the magnet30. The sensor20is connected to the rod12, and as the sensor20moves with the rod12the sensor20transmits a signal indicating the position of the rod12relative to the magnet30. The sensor20can detect the relative position of the rod12without contacting the rod12or magnet30. As the rod12moves through extension and compression strokes, the magnetic field goes though the non-magnetic rod12and is detected by the sensor20. The sensor20detects the relative position of the magnet30and gives a corresponding output signal. The position is not lost during power interruptions or movement during non-powered situations. This can be helpful in medical, off-highway, agriculture, manufacturing, processing equipment, and automobile applications, and gas springs used in conjunction with linear actuators. A computing device, such as an electronic control unit (hereinafter “ECU”) can be operatively connected to the position sensor20. The sensor20detects the position of the magnet30and provides this position data to the ECU which can determine the relative position of the pressure tube14and the rod12. During movement, the ECU can process this position data from the sensor20and convert it to velocity of extending or compressing to control the speed of extension/compression. The ECU can transmit this data to a receiving device that can speed up or slow down movement of the piston rod12in response to data transmitted by the sensor ECU. According to an embodiment of the invention, the piston assembly10can be connected to a moveable part, such as a lid. The piston assembly10can be used to open, lift, lower and close the lid. The position sensor20can detect a relative distance to the magnet30and the time taken in moving the detected distance to calculate the velocity or change in velocity of the lid. This data can be transmitted to a receiving device that can speed up or slow down movement of the piston rod12in response to data transmitted by the sensor ECU. The sensor20is contained within the sensor housing22and the magnet30is contained within the tube14, as shown inFIG.4. As such, the sensor20and the magnet30are sealed off from the external environment and are protected from contamination by dust and other debris. According to an embodiment of the invention, the piston assembly10can be utilized in a gas spring. An embodiment of the invention comprises an electric pallet jack comprising a gas spring comprising the piston assembly10. The pallet jack includes an arm that is used by the operator to steer the pallet jack. A gas spring comprising the piston assembly10is connected to the pallet jack arm and returns the arm to the fully upright position. The arm of the jack can be attached to the end fitting31of piston assembly10, and the sensor ECU can be operatively connected to the jack arm. The position sensor20detects the position of the jack arm. The position of the arm controls the speed and direction of the jack. The further the arm is pushed from neutral, the faster the pallet jack moves. The position sensor20can replace the position sensitive throttle switch that is used to vary the speed and direction of the pallet jack in prior art pallet jacks. A piston assembly according to another embodiment of the invention is illustrated inFIG.2and shown generally at reference numeral10′. The assembly10′ comprises the same structural features of the above-described piston assembly10, and also includes a mechanical spring40operatively connected to the rod12. The spring40can be connected to the rod12via mounting members, such as a pair of e-clips41,42. The piston assembly10′ can be used with a self-centering damping apparatus such as is described in International Publication No. WO2020/01853, which is incorporated herein by reference. According to an embodiment of the invention, the piston assembly10′can be used in a self-centering damper with a solar tracking device, such as the solar tracking devices described in U.S. Pat. Nos. 10,648,528 and 9,995,506, which are incorporated herein by reference. According to an embodiment of the invention, the piston assembly10′ can be used in devices in which a mechanical system or hydraulic system is being replaced by a drive-by-wire system, such as when a gas engine powered zero-turn riding (“ZTR”lawn mower is converted to an electrical motor driven device. The dampening force or output force can simulate the feel of the mechanical system. Other uses for the piston assembly10′ include electrification for skid steer or agricultural equipment. According to another embodiment of the invention, the piston assembly10′ can be used with self-centering dampers in zero-turn riding (“ZTR”) lawn mowers having hydrostatic drive transmissions. An embodiment of the invention comprises an electric motor driven ZTR lawn mower comprising a pair of dampers, wherein each damper comprises the piston assembly10′. Each damper is operatively connected to one of the steering levers of the mower to provide resistance to quick movements of the levers. The end fitting31of each damper can be attached to a lever of the mower. The ECU of the position sensor20is operatively connected to a drive motor of the mower. The piston rod12moves in unison with the steering lever. The position sensor20collects data regarding the position of the piston rod12and the steering lever. The sensor ECU uses the data to determine an optimum speed and direction to rotate the drive wheels and transmits optimum speed/direction instructions to the drive motor which rotates the drive wheels in accordance with the instructions. This helps the electric motor driven mower have the same feel as mowers having hydro static drive motors powered by internal combustion engines. Piston assemblies and methods of using same are described above. Various changes can be made to the invention without departing from its scope. The above description of various embodiments of the invention are provided for the purpose of illustration only and not limitation—the invention being defined by the claims and equivalents thereof. | 9,047 |
11859645 | DESCRIPTION OF EMBODIMENTS The inventors have tried to form an embossed surface having a directionality along a front-rear direction of a vehicle body on a surface of a corner portion of a front bumper member provided at a front portion of the vehicle body. According to the embossed surface along the front-rear direction, an airflow flowing along the front-rear direction of the vehicle body is likely to flow in a manner of following an outer surface of the corner portion when the airflow flows on the embossed surface of the corner portion. An airflow that blows out from the corner portion toward an outer side in a vehicle width direction is reduced. A characteristic of the airflow following the outer surface of the vehicle body is improved. However, it has been newly found that an occupant such as a driver of a vehicle may feel strangeness about, for example, steering stability and steering responsiveness of the vehicle body due to the formation of the embossed surface having the directionality along the front-rear direction of the vehicle body on the surface of the corner portion of the front bumper member. This strange feeling is not recognized as a remarkable feeling that lowers the steering stability and the steering responsiveness of the vehicle as compared with a case where the embossed surface is not provided, but this strange feeling can be felt, for example, when steering is performed during straight traveling. As described above, it is desirable to improve an airflow around the vehicle body by the embossed surface in a vehicle, so that an occupant such as a driver of the vehicle does not feel strangeness about, for example, the steering stability and the steering responsiveness of the vehicle body. In the following, some embodiments of the disclosure are described in detail with reference to the accompanying drawings. Note that the following description is directed to illustrative examples of the disclosure and not to be construed as limiting to the disclosure. Factors including, without limitation, numerical values, shapes, materials, components, positions of the components, and how the components are coupled to each other are illustrative only and not to be construed as limiting to the disclosure. Further, elements in the following example embodiments which are not recited in a most-generic independent claim of the disclosure are optional and may be provided on an as-needed basis. The drawings are schematic and are not intended to be drawn to scale. Throughout the present specification and the drawings, elements having substantially the same function and configuration are denoted with the same numerals to avoid any redundant description. FIG.1Ais a plan view showing an automobile1according to an embodiment. FIG.1Bis a left side view showing the automobile1inFIG.1A. The automobile1is an example of a vehicle. The automobile1inFIGS.1A and1Bhas a vehicle body2. The automobile1can travel forward or rearward by a manual operation of an occupant or by autonomous driving. The automobile1can travel in a right front direction, a left front direction, a right rear direction, and a left rear direction by steering. Airflows flowing along a shape of the vehicle body2are generated around the vehicle body2during traveling as indicated by dashed arrows in the drawings. Air at a traveling direction side of the vehicle body2hits a front bumper member10that is provided on a front surface3of the vehicle body2, and then is divided toward left and right side surfaces4and5and an upper surface of the vehicle body2and flows along the side surfaces4and5and the upper surface of the vehicle body2, and airflows join at a rear side of the vehicle body2. A slight vortex flow is generated at the rear side of the vehicle body2due to the entrainment of the airflows. These airflows are one factor that hinders traveling of the automobile1. The front bumper member10is provided at a lower portion of the front surface3of the vehicle body2. The front bumper member10is, for example, a component formed of a resin material. The front bumper member10includes a front surface portion11constituting the front surface3of the vehicle body2, and side surface portions12at left and right sides of the front surface portion11in a vehicle width direction of the vehicle body2. Each of the side surface portions12extends to a wheel house6for a front wheel. Both left and right end portions of the front surface portion11of the front bumper member10are lowered to a rear side from a central portion. The left and right end portions are inclined surfaces that do not face the traveling direction. Corner portions where the front face portion11and the left and right side surface portions12of the front bumper member10are connected are formed into a smooth curved surface shape. Since the front bumper member10has such an outer shape, after air at the traveling direction side of the vehicle body2hits the front bumper member10provided on the front surface3of the vehicle body2, the air is likely to flow along the outer shape of the front bumper member10. A CD value (Coefficient of Drag value) and the like can be improved. However, even when the shape of the vehicle body2such as the front bumper member10is devised, it cannot be said that the airflow flows in a manner of well following the outer surface of the vehicle body2including the corner portions. As indicated by “X” in the drawing, it cannot be said that it is possible to sufficiently prevent an airflow from blowing out from the corner portions toward an outer side in the vehicle width direction. The vehicle needs to be improved in order to cause an airflow to flow in a manner of well following the outer surface of the vehicle body2. Therefore, on at least the entire surface of each of the side surface portions12of the front bumper member10, an embossed surface20that has a directionality for assisting an airflow to flow along the surface in one direction than in another direction is formed in the present embodiment. In the present embodiment, the embossed surface20having such directionality controls an airflow and improves aerodynamic characteristics of the automobile1. FIG.2is a schematic view showing the embossed surface20having the directional pattern that can be formed on the front bumper member10of the automobile1inFIG.1A. The embossed surface20inFIG.2includes a base surface21and a plurality of minute protruding portions22formed in a manner of protruding from the base surface21. The base surface21may be an outer surface of the front bumper member10. In this case, the embossed surface20may be formed simultaneously with the front bumper member10during molding of the front bumper member10. The base surface21may be a sheet attached to an outer surface of the front bumper member10. The plurality of protruding portions22include a plurality of elongated protrusions. Each of the elongated protrusions22may have a long elliptical shape with both ends in the longitudinal direction rounded. The elongated protrusion22may have, for example, a cubic shape having a quadrangular cross section. Some of the plurality of protruding portions22may not have an elongated shape, and may have, for example, a regular cubic shape or a columnar shape. The plurality of protruding portions22are formed side by side on the entire base surface21in a short-side direction and a long-side direction of the elongated shape. A protruding height of the protruding portion22from the base surface21may be, for example, several micrometers or more. First recessed portions23which are minute are formed between elongated protrusions22among the plurality of protruding portions22which are adjacent in the short-side direction of the elongated shape. Each of the first recessed portions23linearly extends along the long-side direction of the elongated protrusions22on the entire base surface21. Second recessed portions24which are minute are formed between elongated protrusions22among the plurality of protruding portions22which are adjacent in the long-side direction of the elongated shape. The second recessed portions24are formed in a manner in which one of the second recessed portions24is shifted in the long-side direction relative to another of the second recessed portions24formed between other elongated protrusions22adjacent in the short-side direction of the elongated shape among the plurality of protruding portions22. In particular, in order to obtain uniform airflow characteristics over the entire base surface21, the plurality of second recessed portions24are formed over the entire base surface21in a constant pattern in which the second recessed portions24are bent in the short-side direction in the present embodiment. Accordingly, each of the second recessed portions24is not formed in a manner of linearly extending over the entire base surface21along the short-side direction. In the embossed surface20having such a surface structure, an airflow in a direction along the long-side direction of the elongated protrusions22becomes an airflow along the directional pattern, so that the airflow is likely to flow on the embossed surface20. On the other hand, an airflow in a direction along the short-side direction of the elongated protrusions22is less likely to flow on the embossed surface20. As described above, the embossed surface20having the directional pattern inFIG.2have a directionality in which an airflow flowing along a surface of the embossed surface20is likely to flow in one direction and is less likely to flow in another direction. FIG.3Ais a view showing an airflow at the side surface portion12of the front bumper member10on which the embossed surface20having the directional pattern inFIG.2is formed. FIG.3Ais a schematic view corresponding to A-A cross section ofFIG.2showing the embossed surface20formed on the side surface portion12of the front bumper member10as viewed from a front side of the automobile1. InFIG.3A, an upper-lower direction of the paper surface coincides with the short-side direction of the elongated protrusion22. In this case, the embossed surface20having the directional pattern for assisting an airflow to flow in a direction along a front-rear direction of the vehicle body2is formed over the entire surface of the side surface portion12of the front bumper member10provided at a front portion of the vehicle body2. As shown inFIG.3A, when an airflow flowing on the side surfaces4and5of the vehicle body2flows on the embossed surface20, a longitudinal vortex32is generated between a main flow31that flows along the side surfaces4and5of the vehicle body2and a surface of the embossed surface20. The longitudinal vortex32is formed on a surface of the protruding portion22for each protruding portion22. The flow induced by the longitudinal vortex32is less likely to flow into the first recessed portion23. A contact area between the embossed surface20and the airflow is reduced by a width of the first recessed portion23. Frictional resistance of the airflow relative to the embossed surface20is reduced. FIG.3Bis a schematic horizontal sectional view showing the side surface portion12of the front bumper member10on which the embossed surface20having the directional pattern inFIG.3Ais formed. The directional pattern of the embossed surface20inFIG.3Bis a directional pattern for assisting an airflow to flow in a direction along the front-rear direction of the vehicle body2. InFIG.3B, a left-right direction of the paper surface coincides with the long-side direction of the elongated protrusion22. Different from the case shown inFIG.3B, in a case where the embossed surface20is not formed on the side surface portion12of the front bumper member10, the main flow33that flows along the side surface portion12of the front bumper member10flows in a manner in which the airflow is slightly separated away from the surface of the side surface portion12as indicated by a dash-dot line in the drawing. On the other hand, when the embossed surface20is formed on the side surface portion12of the front bumper member10as shown inFIG.3B, the frictional resistance of the airflow relative to the embossed surface20is reduced. As a result, the main flow31that flows along the side surface portion12of the front bumper member10flows in a manner in which the airflow is close to the surface of the side surface portion12as indicated by a solid line in the drawing. In this manner, the embossed surface20is formed on the side surface portion12of the front bumper member10, and the directionality of the embossed surface20in one direction is a direction along the front-rear direction of the vehicle body2, so that the airflow flows in a manner of well following a surface shape of the side surface portion12of the front bumper member10. It is possible to positively prevent the airflow from blowing out from the corner portions of the front bumper member10toward an outer side in the vehicle width direction. The airflow flows in a manner of well following the outer surface of the vehicle body2. FIG.4is a view showing a traveling state of the automobile1in which aerodynamic characteristics are improved by the embossed surface20inFIG.3A. InFIG.4, the automobile1in which the embossed surface20having the directional pattern inFIG.2is formed on a surface of the side surface portion12of the front bumper member10as shown inFIG.3Atravels on a straight road. As shown inFIG.4, when steering for changing a position of the automobile1in the vehicle width direction is performed during straight traveling, the automobile1changes a direction to the right at a point P1during straight traveling, and then changes a direction to the left at a point P2. A posture of the vehicle body is changed during a steering period. At a point P3after the steering is completed, the automobile1returns to travel in a straight traveling direction, and a posture of the vehicle body is stabilized. Such steering during straight traveling may cause an occupant such as a driver of the automobile1to feel strangeness about a behavior of the vehicle body2, for example, about steering stability and steering responsiveness. For example, an occupant such as a driver of the automobile1may have an strange feeling such as a reduction of a ground contact feeling at the front of vehicle body2, a reduction in response to steering, a reduction in responsiveness to steering, and a prolongation of a damping property of a posture change of the automobile1during steering in straight traveling. These strange feelings are not recognized as remarkable feelings that lower the steering stability and the steering responsiveness of the automobile1as compared with a case where the embossed surface20is not provided, and these strange feelings are subtle feelings. FIG.5is a view showing the embossed surface20formed on the side surface portion12of the front bumper member10in the present embodiment. In the present embodiment, as shown inFIG.5, the embossed surface20having the directional pattern inFIG.2is formed such that the directionality of the embossed surface20in one direction does not have angle of 0 degrees along the front-rear direction of the vehicle body2as shown inFIG.3A, but has a rear raising angle relative to the front-rear direction of the automobile1. In one example, the embossed surface20is formed such that the first recessed portion23that extends linearly in the embossed surface20has a rear raising angle of, for example, 20 degrees, relative to the front-rear direction of the vehicle body2. The embossed surface20is formed on the entire surface of the side surface portion12of the front bumper member10provided at the front portion of the vehicle body2. Accordingly, even when steering or the like is performed during straight traveling, an occupant such as a driver of the automobile1does not feel strangeness about the behavior of the vehicle body2, for example, about the steering stability or the steering responsiveness. An occupant such as a driver of the automobile1does not have a strange feeling such as a reduction of ground contact feeling at the front of vehicle body2, a reduction in response to steering, a reduction in responsiveness to steering, and a prolongation of a damping property of a posture change of the automobile1when steering is performed during straight traveling. Pitching of the automobile1may occur not only during steering but also due to road surface disturbance or the like. The road surface disturbance may occur even when the automobile1travels straight. A behavior change of the automobile1at the time of such pitching does not give an occupant such as a driver of the automobile1an strange feeling. Although it is difficult to quantitatively describe a cause of such a strange feeling, a qualitative example will be described below. FIG.6is a comparative view showing a case where the embossed surface20having a directional pattern is formed as shown inFIG.2and a case where the embossed surface20having a directional pattern is formed as shown inFIG.5according to the present embodiment. An upper part inFIG.6shows a direction change due to a posture change of the vehicle body2with respect to the embossed surface20having a directionality along the front-rear direction of the vehicle body2inFIG.2. A lower part shows a direction change due to a posture change of the vehicle body2with respect to the embossed surface20having a directionality that has a rear raising angle relative to the front-rear direction of the vehicle body2as shown inFIG.5. InFIG.6, a plurality of elongated protrusions formed on the embossed surface20are arranged side by side in the short-side direction of the protruding portions. A left part of each stage is a neutral state in which no steering or the like is performed. In the neutral state, the vehicle body2may be horizontal and parallel to a road surface. A center part of each stage is a state in which the vehicle body2is lowered forward, that is, raised rearward, due to steering or the like. The vehicle body2is changed from a horizontal posture in the neutral state to a posture in which a pitch is rotated in a forward direction. A right part of each stage is a state in which the vehicle body2is raised forward, that is, lowered rearward, due to steering or the like. The vehicle body2is changed from a horizontal posture in the neutral state to a posture in which a pitch is rotated in a rearward direction. In the embossed surface20having the directionality along the front-rear direction of the vehicle body2as shown in the upper part inFIG.6, the plurality of elongated protrusions have the directionality along the front-rear direction of the vehicle body2in the neutral state shown in the left part. In this case, an airflow flowing from a front side to a rear side on the side surfaces4and5of the vehicle body2flows substantially parallel to a longitudinal direction of the protruding portions. Neither a pushing-down force nor a pushing-up force is generated by the airflow on the embossed surface20. When a posture of the vehicle body2is changed to a posture in which the vehicle body2is lowered forward, that is, raised rearward, the plurality of elongated protrusions are in a posture in which the protruding portions are raised rearward relative to a direction along the front-rear direction of the vehicle body2. In this case, an airflow flowing from the front side to the rear side on the side surfaces4and5of the vehicle body2may generate a pushing-down force on the embossed surface20. On the other hand, when a posture of the vehicle body2is changed to a posture in which the vehicle body2is raised forward, that is, lowered rearward, the plurality of elongated protrusions are in a posture in which the protruding portions are lowered rearward relative to the direction along the front-rear direction of the vehicle body2. In this case, an airflow flowing from the front side to the rear side on the side surfaces4and5of the vehicle body2may generate a pushing-up force on the embossed surface20. The pushing-up force is a force for lifting up the vehicle body2. In this manner, a force for changing a posture of the vehicle body2so as to lift up or push down the vehicle body2can be applied in accordance with a change in a posture (pitch) of the vehicle body2on the embossed surface20having the directionality along the front-rear direction of the vehicle body2. In the vehicle body2whose posture is changed during steering, for example, as shown inFIG.4, an outer front side of the vehicle body2is lowered, and a rear inner side of the vehicle body2is raised in first steering. In second reverse steering, an inner front side of the vehicle body2is raised and a rear outer side of the vehicle body2is lowered. During a steering period, a change direction of a posture of the vehicle body2is switched between an upper side and a lower side. As a result, a force that pushes down a front portion of the vehicle body2acts on the vehicle body2in the first steering, and a force that pushes up (a force that lifts up) the front portion of the vehicle body2acts on the vehicle body2in the second reverse steering. During the steering period, there is a change point where the directionality of the force acting on the vehicle body2changes. Since a behavior manner of the vehicle body2changes before and after the change point, it is considered that an occupant such as a driver of the automobile1feels strangeness about the behavior of the vehicle body2, for example, about the steering stability and the steering responsiveness, when steering or the like is performed during straight traveling. On the embossed surface20having a directionality that has a rear raising angle relative to the front-rear direction of the vehicle body2shown in the lower part inFIG.6, in the neutral state shown in the left part, the plurality of elongated protrusions have a directionality that has a rear raising angle relative to the front-rear direction of the vehicle body2. In this case, an airflow flowing from the front side to the rear side on the side surfaces4and5of the vehicle body2may generate a pushing-down force on the embossed surface20. When a posture of the vehicle body2is changed to a posture in which the vehicle body2is lowered forward, that is, raised rearward, the plurality of elongated protrusions are in a posture in which the protruding portions are raised rearward at a large angle relative to the direction along the front-rear direction of the vehicle body2. In this case, an airflow flowing from the front side to the rear side on the side surfaces4and5of the vehicle body2may generate a pushing-down force on the embossed surface20. When a posture of the vehicle body2is changed to a posture in which the vehicle body2is raised forward, that is, the vehicle body2is lowered rearward, the plurality of elongated protrusions are in a posture in which the protruding portions are raised rearward at a small angle relative to the direction along the front-rear direction of the vehicle body2. In this case, an airflow flowing from the front side to the rear side on the side surfaces4and5of the vehicle body2may generate a pushing-down force on the embossed surface20. As described above, on the embossed surface20having the directionality that has a rear raising angle relative to the front-rear direction of the vehicle body2, even when a posture (pitch) of the vehicle body2is changed, a force for pushing down the vehicle body2continues to act on the vehicle body2while constantly maintaining a state of having a rear raising angle relative to the front-rear direction of the vehicle body2. Even when steering is repeatedly performed, a direction of a force acting on the vehicle body2during the steering period is maintained in a direction of pushing down the vehicle body2, and it is difficult to change the direction of the force. Since there is no change point, a behavior manner of the vehicle body2may continue to be continuous. An occupant such as a driver of the automobile1does not feel strangeness about the behavior of the vehicle body2, for example, about the steering stability and the steering responsiveness, when steering or the like is performed during straight traveling. As described above, in the present embodiment, the embossed surface20having the directional pattern in which an airflow is more likely to flow in one direction along the surface than in another direction is formed on the entire surface of the side surface portion12of the front bumper member10provided at a lower portion of the front surface3of the vehicle body2. The embossed surface20is formed such that the one direction in which the airflow is likely to flow is raised rearward relative to the front-rear direction of the vehicle body2. Accordingly, similar to a case in which the embossed surface20is formed such that the one direction is the front-rear direction of the vehicle body2, the airflow is likely to flow in a manner of following the shape of the side surface portion12of the front bumper member10. After the air at a traveling direction side of the vehicle body2hits the front surface3of the vehicle body2and flows toward the side surfaces4and5of the vehicle body2, the airflow is less likely to blow out from a corner portion of the vehicle body2toward an outer side in the vehicle width direction. The air at the traveling direction side of the vehicle body2is likely to flow in a manner of following the shape of the vehicle body2including the corner portion of the vehicle body2. In the present embodiment, the embossed surface20is formed such that the one direction in which an airflow is likely to flow is not the front-rear direction of the vehicle body2, but a direction raised rearward relative to the front-rear direction of the vehicle body2. Accordingly, for example, even when steering is performed during straight traveling of the automobile1, an occupant such as a driver of the automobile1is less likely to have an strange feeling about, for example, the steering stability and the steering responsiveness of the vehicle body2. This is because that the one direction of the embossed surface20is formed in a manner of being raised rearward relative to the front-rear direction of the vehicle body2, so that even when a posture of the vehicle body2is changed to an inclined posture due to steering in straight traveling, the one direction of the embossed surface20can be maintained in a state in which the one direction of the embossed surface20is raised rearward relative to the front-rear direction of the vehicle body2, or can be maintained in a state in which the one direction of the embossed surface20is at least substantially the front-rear direction of the vehicle body2. This is because that an airflow that flows in a manner of following an outer surface of the vehicle body2in accordance with the directionality of the embossed surface20during straight traveling can continue to maintain the same flow as before even when a posture of the vehicle body2is changed by steering. This is because that even when the vehicle body2returns to straight traveling after a posture of the vehicle body2is changed by steering, the airflow that flows in a manner of following the outer surface of the vehicle body2in accordance with the directionality of the embossed surface20during the posture change can continue to maintain the same flow as before. As a result, even at the time of steering during straight traveling, a ground contact feeling at the front of the vehicle body2can be stabilized, a response to steering can be stably improved, responsiveness to steering can be improved, and a damping property of a posture change of the automobile1can be improved in the present embodiment. An occupant such as a driver of the automobile1is less likely to feel strangeness about the steering stability, the steering responsiveness, and the like of the vehicle body2. On the other hand, for example, in a case where the one direction of the embossed surface20is formed in a manner in which the one direction is along the front-rear direction of the vehicle body2or is formed in a manner in which the one direction is lowered rearward relative to the front-rear direction of the vehicle body2, when a posture of the vehicle body2is changed by steering during straight traveling, the directionality of the embossed surface20may be changed so as to be lowered rearward or raised rearward relative to the front-rear direction of the vehicle body2in accordance with the posture change. When the directionality of the embossed surface20is changed in such a manner, a direction of an airflow flowing on the embossed surface20is changed to be upward or downward. The direction of the airflow is changed in a disturbed manner. When such a change of the airflow occurs due to steering during straight traveling, a force for changing a posture of the vehicle body2so as to lift up or push down the vehicle body2acts on the vehicle body2whose posture is changed by steering. As a result, an occupant such as a driver of the automobile1feels strangeness about, for example, the steering stability and the steering responsiveness of the vehicle body2, when steering or the like is performed during straight traveling. An occupant such as a driver of the automobile1has an strange feeling such as a reduction of a ground contact feeling at the front of vehicle body2, a reduction in response to steering, a reduction in responsiveness to steering, and a prolongation of a damping property of a posture change of the automobile1when steering is performed during straight traveling. In contrast thereto, in accordance with the embodiments, an occupant such as a driver of the automobile1does not feel strangeness due to a behavior change of the automobile1not only at the time of pitching of the automobile1during steering but also at the time of pitching due to road surface disturbance or the like. The above-described effects can be obtained without greatly changing an exterior design (shape) of the vehicle body2or adding a large aerodynamic part to the vehicle body2in the present embodiment. The embodiment described above is an example of a preferred embodiment of the present disclosure, the present disclosure is not limited thereto, and various modifications or changes can be made without departing from the gist of the disclosure. For example, in the embodiment described above, the embossed surface20having the directional pattern is formed on the surface of the side surface portion12of the front bumper member10provided at the lower portion of the front surface3of the vehicle body2. On the other hand, for example, the embossed surface20having the directional pattern may be formed on a surface of the side surface portion12and on a surface of the front surface portion11of the front bumper member10. The embossed surface20that does not have the directional pattern may be formed on the surface of the front surface portion11of the front bumper member10. Since the embossed surface20having the directional pattern is formed on at least the surface of the side surface portion12of the front bumper member10, the same effects as those in the embodiment described above can be achieved. In the embodiment described above, the directionality of the embossed surface20is formed such that one direction of the embossed surface20is raised rearward at an angle of 20 degrees relative to the front-rear direction of the vehicle body2. On the other hand, for example, the directionality of the embossed surface20may be formed such that one direction of the embossed surface20has an angle at which one direction of the embossed surface20can be maintained to be raised rearward during a posture change of the vehicle body2that may occur during normal traveling of the automobile1. For example, the directionality of the embossed surface20may be formed such that one direction of the embossed surface20is raised rearward at an angle larger than 20 degrees. For example, the directionality of the embossed surface20may be formed such that one direction of the embossed surface20is raised rearward at an angle in a range of 10 degrees or more and 40 degrees or less. | 32,320 |
11859646 | DETAILED DESCRIPTION OF EMBODIMENT(S) Hereinafter, embodiments will be described with reference to the drawings. The embodiments below are merely exemplary ones in nature, and are not intended to limit the scope, applications, or use of the present invention. A vortex ring generation device (10) according to an embodiment discharges vortex ring-shaped air (a vortex ring (R)). The vortex ring generation device (10) causes a predetermined discharge component to be contained in the vortex ring (R), and then supplies the vortex ring (R) containing the discharge component to, for example, a subject. The discharge component contains substances such as a scent component, water vapor, and a substance having predetermined efficacy. The discharge component is preferably a gas, but may be a liquid. In the case of liquid, the discharge component is preferably a particulate liquid. As illustrated inFIG.1, the vortex ring generation device (10) includes: a casing (20) having a discharge port (25); an extrusion mechanism (30); a passage forming member (40); and a component supply device (50). An air passage (gas passage) (C) through which air flows is formed inside the casing (20). In the vortex ring generation device (10), the air in the air passage (C) is extruded by the extrusion mechanism (30), formed into the vortex ring (R), and discharged from the discharge port (25). The vortex ring (R) discharged from the discharge port (25) contains the discharge component supplied from the component supply device (50). Casing The casing (20) includes a casing body (21) having a front side open, and a substantially plate-like front panel (22) blocking the open face on the front side of the casing body (21). The casing (20) has a hollow cuboid shape. A middle portion of the front panel (22) has the discharge port (25) in the circular shape passing therethrough in a front-rear direction. A peripheral wall (23) in a substantially cylindrical shape continues on a rear surface of the front panel (22). The peripheral wall (23) extends rearward from an inner peripheral edge (26) of the discharge port (25). The peripheral wall (23) has a tapered shape whose diameter becomes smaller frontward. An outer peripheral end of the peripheral wall (23) is fixed to an inner wall of the casing body (21). A front leading end portion of the peripheral wall (23) is continuous with the inner peripheral edge (26) of the discharge port (25). An center axis of the peripheral wall (23) substantially coincides with that of the discharge port (25). Passage Forming Member The passage forming member (40) is disposed rearward of the peripheral wall (23). The passage forming member (40) is formed in a substantially cylindrical shape along an inner peripheral surface of the peripheral wall (23). The passage forming member (40) has a tapered shape whose diameter becomes smaller frontward (i.e., downstream of the air passage (C)). A center axis of the passage forming member (40) substantially coincides with that of the discharge port (25). The center axis of the passage forming member (40) substantially coincides with that of the peripheral wall (23). A component chamber (27) in which the discharge component is temporarily stored is defined in space surrounded by the inner wall of the casing body (21), the peripheral wall (23), and the passage forming member (40). The component chamber (27) is a substantially cylindrical space formed around the passage forming member (40). Extrusion Mechanism The extrusion mechanism (30) is disposed in the rearward inside the casing (20). The extrusion mechanism (30) has a vibration plate (31) that is a movable member, and a linear actuator (35) that displaces the vibration plate (31) back and forth. The vibration plate (31) includes a vibration plate body (32) and a frame-shaped elastic support (33) disposed at an outer peripheral edge of the vibration plate body (32). The vibration plate (31) is fixed to an inner wall of the casing (20) via the elastic support (33). The linear actuator (35) constitutes a drive unit that vibrates the vibration plate (31) back and forth. A base end (rear end) of the linear actuator (35) is supported by a rear wall of the casing body (21). A leading end (front end) of the linear actuator (35) is coupled with a center portion of the vibration plate (31). The linear actuator (35) vibrates the vibration plate (31) between a reference position and an extrusion position. Thus, the air (indicated by an open arrow inFIG.1) in the air passage (C) is extruded forward. Air Passage The air passage (C) extends from the vibration plate (31) to the discharge port (25) in the casing (20). The air passage (C) includes a first passage (C1) and a second passage (C2) continuous with a downstream end of the first passage (C1). The first passage (C1) is surrounded by the inner wall of the casing body (21). A passage area of the first passage (C1) is constant. The second passage (C2) is formed inside the passage forming member (40). Specifically, the second passage (C2) is surrounded by the peripheral wall (23). The second passage (C2) constitutes a throttle passage whose passage area becomes smaller toward its downstream. Thus, in the second passage (C2), the flow rate of air gradually increases toward its downstream. Component Supply Device The component supply device (50) supplies, into the casing (20), the discharge component to be applied to the vortex ring (R). Specifically, the component supply device (50) supplies, via a supply passage (51), the predetermined discharge component to the component chamber (27) defined inside the casing (20). The component supply device (50) includes a component generation unit (not shown) that generates the discharge component and a conveyance unit (not shown) that conveys the discharge component generated in the generation unit. The component generation unit is, for example, of a vaporizing type that vaporizes the discharge component from a component raw material. The conveyance unit is, for example, an air pump. The component supply device (50) appropriately supplies, to the component chamber (27), the discharge component whose concentration has been adjusted to a predetermined concentration. Component Supply Port The vortex ring generation device (10) has a component supply port (60) for supplying the discharge component to the air passage (C). In the present embodiment, the casing (20) has one component supply port (60). The component supply port (60) is located adjacent to the discharge port (25). More specifically, the component supply port (60) is disposed between a downstream end (41) of the passage forming member (40) in a cylinder axial direction and the inner peripheral edge (26) of the discharge port (25). Thus, one annular (strictly speaking, toric) component supply port (60) is formed around the downstream end of the air passage (C). Specifically, one annular component supply port (60) is formed near the discharge port (25) in the air passage (C). Operation The basic operation of the vortex ring generation device (10) will be described with reference toFIG.1. When the vortex ring generation device (10) is in operation, the linear actuator (35) vibrates the vibration plate (31). When the vibration plate (31) deforms forward, the volume of the air passage (C) decreases. As a result, the air in the air passage (C) flows toward the discharge port (25). The air in the first passage (C1) flows into the second passage (C2). In the second passage (C2), the passage area gradually decreases, so that the flow rate of air increases. When the flow rate of the air increases, the pressure of the air decreases. In particular, an outlet end of the second passage (C2) has the smallest passage area. Therefore, the flow rate of the air at the outlet end of the second passage (C2) is substantially the highest in the air passage (C). Consequently, the pressure of the air at the outlet end of the second passage (C2) is substantially the lowest. The component supply port (60) is located at the outlet end of the second passage (C2). Therefore, when the air at low pressure passes through the component supply port (60), the discharge component in the component chamber (27) is sucked into the air passage (C) due to the difference between the pressure of the air and the pressure in the component chamber (27). When the discharge component in the component chamber (27) is sucked into the air passage (C), the discharge component is dispersed in the air passing through the component supply port (60). The constant flow rate of the air passing through the component supply port (60) allows a constant amount of the discharge component to be sucked from the component supply port (60). This allows the concentrations of the discharge component in the air and the vortex ring (R) to be controlled to be constant. Since the component supply port (60) has an annular shape surrounding the air passage (C), the discharge component in the component chamber (27) is dispersed over the entire circumference of the air passage (C). Further, the discharge component is easily applied to the air flowing through the air passage (C), in particular, to the air near the outer periphery. This allows, in the air passage (C), the discharge component to be uniformly applied to the air near the outer periphery. In this way, the air containing the discharge component reaches the discharge port (25) immediately. The air passing through the discharge port (25) has a relatively high flow rate, whereas the air around the discharge port (25) is still. For this reason, a shearing force acts on the air at discontinuous planes of both air flows, and a vortex flow is generated adjacent to an outer peripheral edge of the discharge port (25). The vortex flow forms a vortex ring-shaped air (vortex ring (R) schematically shown inFIG.1) moving forward from the discharge port (25). The vortex ring (R) containing the discharge component is supplied to the subject. As described above, the discharge component is supplied over the entire circumference of the air flow from the component supply port (60). Therefore, the discharge component is also dispersed in the vortex ring (R) circumferentially. This allows reduction in uneven distribution of the discharge component in the vortex ring (R). The discharge component is supplied from the component supply port (60), in particular, to the air at an outer peripheral side. This allows most of the discharge component in the component chamber (27) to be contained in the vortex ring (R). The component supply port (60) is located adjacent to the discharge port (25). If the component supply port (60) and the discharge port (25) are relatively far away from each other, the discharge component supplied into the air may diffuse before reaching the discharge port (25), and the amount of the discharge component contained in the vortex ring (R) may decrease. To address this problem, the component supply port (60) and the discharge port (25) are made close to each other, thereby allowing reduction in such diffusion of the discharge component. The component supply port (60) located adjacent to the discharge port (25) is located substantially at the most downstream end of the air passage (C). This allows a sufficient distance between the component supply port (60) and the extrusion mechanism (30) (strictly speaking, the vibration plate (31)) to be secured. This sufficient distance allows reduction in adhesion of the discharge component which has been supplied from the component supply port (60), to the extrusion mechanism (30) even if the air in the air passage (C) flows slightly backward due to the vibration of the vibration plate (31). This reduction allows avoidance of an increase in frequency of maintenance of the extrusion mechanism (30) and peripheral components thereof required due to adhesion of the discharge component, for example. Since the component supply port (60) is annular in shape, the flow rate of the air passing through the discharge port (25) is equalized circumferentially, as compared to a case in which the component supply port (60) is unevenly distributed circumferentially, for example. This allows the vortex ring (R) to be stably formed at the discharge port (25). Configuration For Stabilizing Generation of Vortex Ring Test Example 1 of Vortex Ring Generation Test A vortex ring generation test was conducted using the vortex ring generation device (10) of the present embodiment. In the vortex ring generation test, the casing (20) of the vortex ring generation device (10) was formed into a hollow cuboid having about 100 mm to about 150 mm sides, and the discharge port (25) had a diameter D of 30 mm, as shown inFIGS.2A The vortex ring generation test was performed at a plurality of different values of extrusion frequency f (vibration frequencies of the vibration plate (31)) of air, ranging from 2 Hz to 30 Hz. When, in addition to D (mm) representing the diameter of the discharge port (25), V (m3) represents an extrusion volume, L (mm) represents a length of the cylinder having the diameter D and the volume V (equivalent length of the cylinder), and U (m/s) represents an extrusion flow rate, the extrusion flow rate U varied within a range of 0.4 m/s to 3.2 m/s in response to the different values of extrusion frequency f. Further, the extrusion volume V ranged from 0.004 m3to 0.65 m3, and the equivalent length L of the cylinder ranged from 6 mm to 92 mm (0.006 m to 0.092 m). FIG.3is a graph plotting test results (values at measurement points) where the vertical axis represents the Reynolds number Re, and the horizontal axis represents the L/D ratio. In the graph ofFIG.3, representative values of the extrusion frequency f are indicated on the respective lines each of which is obtained by connecting plotted points of the same value of the extrusion frequency f. As can be seen from the representative values and the lines, the smaller the extrusion frequency f is, the smaller the Reynolds number Re is and the wider the L/D ratio range is (the smaller the line inclination angle is), whereas the larger the extrusion frequency f is, the wider the Reynolds number is and the smaller the L/D ratio range is (the larger the line inclination angle is). The Reynolds number Re is a value expressed by an equation Re=UD/v (v: coefficient of kinematic viscosity (m2/s)), and L/D is a value expressed by an equation UT/D (T: extrusion time (sec)). When specific values of the Reynolds number Re, the L/D ratio, the extrusion frequency f, the flow rate U, the extrusion volume V, and the equivalent length L of the cylinder, at a point P shown in the graph are shown as the representative values, Re=1865, L/D=1.54, f=10 Hz, U=0.9 m/s, V=0.33 m3, and L=46.1 mm (0.0461 m). FIG.3shows a region in which a vortex ring having an outreach A of 20 to 40 (cm) was generated, a region in which a vortex ring having an outreach A of 50 (cm) or more was generated, a region in which a vortex ring was generated, but diffused a little more, a region in which a vortex ring was not generated, and a region in which the vibration plate (31) (linear actuator (35)) could not be fully controlled. The region in which the vortex ring was not generated is a region in which the extrusion frequency f was low. The region in which the vibration plate (31) could not be fully controlled is a region in which the extrusion frequency was high. In the range of the extrusion frequency f from 5 to 30 (Hz), a vortex ring was substantially generated, although the outreach A and the extent of diffusion were different. In the range (A) in which the Reynolds number Re and the L/D ratio satisfy relationships of 500≤Re≤3000 and 0.5≤L/D≤2.0 inFIG.3, a straight flow was hardly generated in the vortex ring, and a stable vortex ring whose lingering was hardly observed was generated. In the graph, the outreach A of the vortex ring at a point Q where Re=3000 and L/D=2 was about 1 m. In the range (B) in which the Reynolds number Re and the L/D ratio satisfy relationships of 1000≤Re≤2500 and 0.75≤L/D≤2.0, the straight flow generated was less than that in the range (A), and a more stable vortex ring was generated. The range (C) in which the Reynolds number Re and the L/D ratio satisfy relationships of 1500≤Re≤2000 and 1.0≤L/D≤2.0 substantially corresponds to the region in which the outreach A of the vortex ring was 50 (cm) or more, and the straight flow generated was less than that in the range (B), and a further stable vortex ring was generated. The above results show that the present embodiment allows only the vortex ring to be conveyed to a desired place without substantially generating a straight flow. Thus, the present embodiment allows the scent component not to be conveyed to an unintended place. Test Example 2 of Vortex Ring Generation Test Results of the test performed with the change in diameter of the discharge port (25) show that the outreach A (m) of the vortex ring increases approximately in proportion to the size of the diameter D (mm) of the discharge port (25). Therefore, when the test is performed under the same conditions as in Test Example 1 with the diameter D of the discharge port (25) set to 60 mm (0.06 m), the outreach A of the vortex ring at the point Q is about 2 m. The above-described vortex ring generation test showed that the diameter D (mm) of the discharge port (25) suitable for increasing the outreach A of the vortex ring, the blow-out flow rate U (m/s), and the equivalent length L (mm) of the cylinder were within the following ranges. The range of the diameter D of the discharge port (25): 60 mm≤D≤150 mm (0.06 m≤D≤0.15 m) The range of the blow-out flow rate U: 0.30 m/s≤U≤0.75 m/s The range of the equivalent length L of the cylinder was: 120 mm≤L≤300 mm (0.12 m≤L≤0.3 m) The extrusion time T was 0.16≤T≤0.99 (sec). At that time, the Reynolds number Re was Re=3000 within the range (A) of 500≤Re≤3000, and the L/D ratio was L/D=2.0 within the range (A) of the range of 0.5≤L/D≤2.0. Under the above-described conditions, a stable vortex ring having the outreach A of about 2 m was generated as described above. As described above, since the outreach A (m) of the vortex ring becomes longer in substantial proportion to the diameter D (mm) of the discharge port (25), a stable vortex ring having an outreach A of about 5 m can be generated at D=150 mm. Further, the range of the blow-out flow rate U (m/s) and the range of the equivalent length L (m) of the cylinder correspond to the generation of a vortex ring having a long outreach A if the range of the diameter D is set to 60 mm≤D≤150 mm. As described above, in Test Example 2 of the vortex ring generation test of the present embodiment, the Reynolds number Re and the L/D ratio were limited to the range (A), and the diameter D (mm) of the discharge port (25), the blow-out flow rate U (m/s), and the equivalent length L (mm) of the cylinder were set to the ranges described above. Thus, it was possible to generate the vortex ring achieving the outreach A of 2 m≤A≤5 m. Advantages of Embodiment It has been difficult to generate a stable vortex ring by using a known vortex ring generation device. This is because, for example, the known vortex ring generation device requires the L/D ratio set to more than 2, which causes the vortex ring not to be stable and linger, and also requires the Reynolds number Re set to more than 3000, which causes the vortex to be turbulent and easily disappear due to its movement with dispersion. As can be seen from the test results of the vortex ring generation tests described above, in the present embodiment, setting the Reynolds number Re and the L/D ratio within the range (A) that satisfies the relationships of 500≤Re≤3000 and 0.5≤L/D≤2.0 allows a stable vortex ring including substantially no straight flow to be generated. Further, setting the Reynolds number Re and the L/D ratio within the range (B) satisfying the relationships of 1000≤Re≤2500 and 0.75≤L/D≤2.0 allows a vortex ring more stable than that in the range (A) to be generated. In addition, setting the Reynolds number Re and the L/D ratio within the range (C) satisfying the relationship of 1500≤Re≤2000 and 1.0≤L/D≤2.0 allows a vortex ring more stable than that in the range (B) to be generated. In particular, setting the diameter D (mm) of the discharge port (25), the blow-out flow rate U (m/s), and the equivalent length L (mm) of the cylinder to satisfy relationships of 0.06≤D≤0.15, 0.12≤L≤0.3, and 0.3≤U≤0.75 allows a stable vortex ring achieving an outreach A of 2 m≤A≤5 m to be generated. As described above, the Reynolds number exceeding 3000 or being a large value such as 5000, 10000, or more causes diffusion of the vortex ring even if generated, and causes the vortex ring to be less likely to be generated. By contrast, in the present embodiment, the Reynolds number is limited to a relatively small range and the L/D ratio is also limited to a value suitable for this range of the Reynolds number, thereby allowing a prominent advantage of generating a stable vortex ring to be exhibited, as compared to the known device. Therefore, the present embodiment allows a stable vortex ring with almost no straight flow to be generated and to be conveyed to the intended place. This allows avoidance of the conveyance of the scent to the unintended places when the vortex ring containing the scent component is conveyed. As a result, the present embodiment enables avoidance of situations in which the scent remains in a wide range including a place to which the scent component is not intended to be conveyed, which causes the olfactory sense to be accustomed to the effect, or people who are in the place where the scent is not intended to be conveyed to feel discomfort. OTHER EMBODIMENTS The above embodiment may also be configured as follows. For example, in the above embodiment, the range (A) satisfying the relationships of 500≤Re≤3000 and 0.5≤L/D≤2.0, the range (B) satisfying the relationships of 1000≤Re≤2500 and 0.75≤L/D≤2.0, and the range (C) satisfying the relationships of 1500≤Re≤2000 and 1.0≤L/D≤2.0 are described. However, the range may be suitably changed into any range as long as it does not exceed the range (A). For example, a range satisfying relationships of 1000≤Re≤2500 and 0.5≤L/D≤2.0 may be employed instead of the range (B), or a range satisfying relationships of 1500≤Re≤2000 and 0.5≤L/D≤2.0 may be employed instead of the range (C). In the above-described embodiment, the discharge component such as a scent component is contained in the vortex ring. However, in the vortex ring generation device of the present disclosure, the discharge component such as the scent component may not be included in the vortex ring. While the embodiments and variations thereof have been described above, various changes in form and details may be made without departing from the spirit and scope of the claims. The embodiments and the variations thereof may be combined and replaced with each other without deteriorating intended functions of the present disclosure. As described above, the present disclosure is useful for a vortex ring generation device. | 23,310 |
11859647 | DETALED DESCRIPTION OF PREFERRED EMBODIMENTS The detailed description set forth below in connection with the appended drawings is intended as a description of presently preferred embodiments of the invention, and is not intended to represent the only forms in which the present invention may be practised. It is to be understood that the same or equivalent functions may be accomplished by different embodiments that are intended to be encompassed within the spirit and scope of the invention. In the drawings, like numerals are used to indicate like elements throughout. Furthermore, terms “comprises,” “comprising,” or any other variation thereof, are intended to cover a non-exclusive inclusion, such that module, circuit, device components, structures and method steps that comprises a list of elements or steps does not include only those elements but may include other elements or steps not expressly listed or inherent to such module, circuit, device components or steps. An element or step proceeded by “comprises . . . a” does not, without more constraints, preclude the existence of additional identical elements or steps that comprises the element or step. Referring now toFIGS.1and2, schematic exploded and assembled perspective views of a fastener100in accordance with an embodiment of the present invention are shown. The fastener100comprises a main body102with a through hole104longitudinally formed therein. The main body102includes a tubular portion106defining walls108that surround an upper part of the through hole104, and a split portion110extending from a lower end of the tubular portion106with a free distal end facing away from the tubular portion106. In a preferred embodiment, the split portion110comprises at least two expansible members112annularly surrounding a lower part of the through hole104. In a preferred embodiment, the expansible members112integrally extend from lower ends of the walls108. In a preferred embodiment, two adjacent expansible members112are spaced by a gap113. FIG.3is a schematic front view of a main body102of the fastener ofFIG.1in accordance with an embodiment of the present invention, andFIG.4is a schematic cross-sectional side view of the main body102ofFIG.3from line A-A. In a preferred embodiment, the split portion110longitudinally comprises a tapered section114that tapers in a direction towards the tubular portion106. The tapered section114is preferably truncated-conical shaped. In a preferred embodiment, the tapered section defines an external annular recess116surrounding the split portion108. In a preferred embodiment, an outer diameter of an upper end of the tapered section114is less than an outer diameter of the lower end of the tubular portion106, which forms the external annular recess116. In a preferred embodiment, an outer diameter of the lower end of the tapered section114is equal to or less than an outer diameter of the tubular portion106. In a preferred embodiment, the gap113longitudinally extends from the upper end of the tapered section114to the free distal end of the split portion110. In a preferred embodiment, the split portion110also comprises a neck section118located between the tubular portion106and the tapered section114, wherein a minimum outer diameter of the neck section118is less than the outer diameter of the lower end of the tubular portion106. In a preferred embodiment, a height of the neck section118is less than a height of the tapered section114. In a preferred embodiment, the height of the neck section118is ⅛-⅓ of the height of the tapered section114. In a preferred embodiment, the tubular portion106, the neck section118and the tapered section114are co-axial and integrally formed. In another preferred embodiment, the tapered section114directly integrally extends from the lower end of the tubular portion106. In a preferred embodiment, the split portion110further comprises a base section120extending from the lower end of the tapered section114with an outer diameter of an upper end thereof equal to the outer diameter of the lower end of the tapered section114. In a preferred embodiment, the base section120is substantially cylindrical-shaped. In another preferred embodiment, the base section120tapers in a direction towards the tapered section114with a taper less than a taper of the tapered section114. In a preferred embodiment, the base section120and the tapered section114are co-axial and integrally formed. In a preferred embodiment, a height of the base section120is ⅙-⅓ of a height of the tapered section114. As shown inFIG.4, the upper part122of the through hole104is threaded for engaging a threaded male member, such as a bolt, or a threaded rod. In a preferred embodiment, the lower part124of the through hole104tapers in a direction away from the upper part122of the through hole104such that the expansible members112expand outwardly when a plug is inserted from the upper part122into the lower part124of the through hole. In a preferred embodiment, the main body102is integrally formed from a raw metal material by cold forming or machining. Referring back toFIGS.1and2, the fastener100further comprises an expansion sleeve126disposed annularly about the split portion110and at least partially received in the external annular recess116. The expansion sleeve126comprises a ring portion128annularly surrounding the split portion110, and a plurality of expansion segments130disposed along and integrally extending from the ring portion128towards the free distal end of the split portion110. In a preferred embodiment, the ring portion128is C-shaped and annularly surrounds the split portion110. FIGS.5and6are respective top and bottom plan views of the fastener ofFIG.1in accordance with an embodiment of the present invention. In a preferred embodiment, the split portion110comprises four expansible members112substantially evenly distribute around the through hole104. In a preferred embodiment, the expansion sleeve126comprises four expansible segments130substantially evenly distribute around the through hole104. However, the number of the expansible members112or the expansible segments130is not limited to four, and the numbers of the expansible members112and the expansible segments130are not necessarily to be identical. FIG.7is a schematic front view of the fastener ofFIG.1in accordance with an embodiment of the present invention, andFIG.8is a schematic cross-sectional side view of the fastener ofFIG.7from line B-B in accordance with an embodiment of the present invention. In a preferred embodiment, the expansion sleeve126longitudinally extends from the lower end of the tubular portion106to the lower end of the tapered section114, for example, the expansion sleeve126longitudinally extends across the tapered section114. In another preferred embodiment, the expansible segments130longitudinally extend beyond the lower end of the tapered section114and annularly surround the base section120of the split portion110. In a preferred embodiment, the expansion sleeve126longitudinally covers no less than ⅓ of the height of the base section120. In yet another preferred embodiment, the expansible segments130longitudinally extends to a lower end of the base section120. In a preferred embodiment, the expansion sleeve126is substantially cylindrical shaped. In a preferred embodiment, an outer diameter of the expansion sleeve126is no less than the outer diameter of the tubular portion106. In a preferred embodiment, a radial thickness of the expansion sleeve126gradually gets thinner from the ring portion128to free distal ends of the expansible segments130, and an inner surface of the expansion sleeve126inclines and mates with a side surface of the tapered section114. With reference toFIG.9, a schematic isometric view of a partially-formed expansion sleeve126in accordance with an embodiment of the present invention is shown. In a preferred embodiment, the expansion sleeve126is formed by rolling a stamped metal strip200around the split portion110of the main body102. The metal strip200is cut off from a metal sheet material preferably by stamping or punching, wherein notches202with an inverted “U” shape or inverted “V” shape are formed along a side of the metal strip200by punching or cutting to form the expansible segments130. In a preferred embodiment, an upper surface204of the metal strip200is substantially flat, while an opposite lower surface206of the metal strip200is inclined with respect to the upper surface204, such that a thickness of the metal strip200gradually gets thinner from the ring portion128to the free distal ends of the expansible segments130. After rolling the metal strip200around the split portion110to form the expansion sleeve126, the expansion sleeve126is at least partially received in the external annular recess116, and an inner surface of the expansion sleeve126, i.e. the lower surface206of the metal strip200, mates with the side surface of the tapered section114. Referring back toFIGS.1and2, in another preferred embodiment, the expansion sleeve126can also be formed by machining. A slit132is formed for clamping the expansion sleeve126to the split portion110. FIG.10is a schematic cross-sectional side view of the fastener100ofFIG.1that is installed into a hole of a target structure300in accordance with an embodiment of the present invention. The expansion segments130of the expansion sleeve126are expanded outwardly by the expansible members112when a plug302is inserted into the lower part124of the through hole104. A bolt304is threaded into the upper part122of the through hole104for hanging objects to the target structure300. As shown inFIG.10, the expansion segments130longitudinally extend to the lower end of the tapered section114, where a greater expansion force is generated, which achieves a tight engagement between the expansion sleeve126and the target structure300. In addition, since the entire tapered section114is longitudinally covered by the expansion sleeve126, when the fastener100is pulled outward, the tapered section114will not be stopped by the lower edge of the expansion sleeve126and there is no significant friction between the main body102and walls of the hole. The smooth relative sliding between the main body102and the expansion sleeve126results in a sustained expansion of the expansion sleeve126, which ensures a reliable locking engagement between the fastener100and the target structure300when there are cracks in the target structure300or under seismic conditions. Referring toFIG.11, a schematic front view of a fastener400having an expansion sleeve402in accordance with another embodiment of the present invention is shown. Similar to the fastener100ofFIG.1, the fastener400includes a main body404having a tubular portion406and a split portion408, wherein the split portion408longitudinally includes a tapered section410that tapers in a direction towards the tubular portion406. FIG.12is a schematic cross-sectional side view of the fastener ofFIG.11from line C-C in accordance with an embodiment of the present invention. The tapered section410defines an external annular recess412surrounding the split portion408, wherein the expansion sleeve402annularly surrounds the split portion408and is at least partially received in the recess412. Similar to the fastener100ofFIG.1, in a preferred embodiment, the split portion408further includes a neck section414between the tubular portion406and the tapered section410, and a base section416extending from a lower end of the tapered section410. In a preferred embodiment, there is a longitudinal distance d between a lower end of the expansion sleeve402and the lower end of the tapered section410of the split portion408. In a preferred embodiment, the longitudinal distance d between the lower end of the expansion sleeve402and the lower end of the tapered section410is equal to or less than 15% of a longitudinal distance h between an upper end of the recess412and the lower end of the tapered section410. In another preferred embodiment, the longitudinal distance d between the lower end of the expansion sleeve402and the lower end of the tapered section410is equal to or less than 10% of the longitudinal distance h between the upper end of the recess412and the lower end of the tapered section410. In a preferred embodiment, the expansion sleeve402downwardly extends to or beyond a reference plane417located between the upper end of the recess412and the lower end of the tapered section410, and substantially perpendicular to a longitudinal axis of the main body404, wherein a longitudinal distance between the reference plane417and the lower end of the tapered section410is equal to or less than 15% of the longitudinal distance h between the upper end of the recess412and the lower end of the tapered section410. In a preferred embodiment, the longitudinal distance between the reference plane417and the lower end of the tapered section410is equal to or less than 10% of the longitudinal distance h between the upper end of the recess412and the lower end of the tapered section410, such that the lower end of the expansion sleeve402substantially longitudinally extends to or beyond the lower end of the tapered section410after a plug is set into a lower part418of a longitudinal hole420of the fastener400. The description of the preferred embodiments of the present invention has been presented for purposes of illustration and description, but is not intended to be exhaustive or to limit the invention to the forms disclosed. It will be appreciated by those skilled in the art that changes could be made to the embodiments described above without departing from the broad inventive concept thereof. It is understood, therefore, that this invention is not limited to the particular embodiment disclosed, but covers modifications within the spirit and scope of the present invention as defined by the appended claims. | 13,928 |
11859648 | DETAILED DESCRIPTION Embodiments are described herein with reference to the attached figures wherein like reference numerals are used throughout the figures to designate similar or equivalent elements. The figures are not drawn to scale, and they are provided merely to illustrate aspects disclosed herein. Several disclosed aspects are described below with reference to non-limiting example applications for illustration. It should be understood that numerous specific details, relationships, and methods are set forth to provide a full understanding of the embodiments disclosed herein. One having ordinary skill in the relevant art, however, will readily recognize that the disclosed embodiments can be practiced without one or more of the specific details or with other methods. In other instances, well-known structures or operations are not shown in detail to avoid obscuring aspects disclosed herein. The embodiments are not limited by the illustrated ordering of acts or events, as some acts may occur in different orders and/or concurrently with other acts or events. Furthermore, not all illustrated acts or events are required to implement a methodology in accordance with the embodiments. Notwithstanding that the numerical ranges and parameters setting forth the broad scope are approximations, the numerical values set forth in specific non-limiting examples are reported as precisely as possible. Any numerical value, however, inherently contains certain errors necessarily resulting from the standard deviation found in their respective analytically predicted results based on finite element analysis. Furthermore, unless otherwise clear from the context, a numerical value presented herein has an implied precision given by the least significant digit. Thus, a value 1.1 implies a value from 1.05 to 1.15. The term “about” is used to indicate a broader range centered on the given value, and unless otherwise clear from the context implies a broader range around the least significant digit, such as “about 1.1” implies a range from 1.0 to 1.2. If the least significant digit is unclear, then the term “about” implies a factor of two, e.g., “about X” implies a value in the range from 0.5× to 2×, for example, about 100 implies a value in a range from 50 to 200. Moreover, all ranges disclosed herein are to be understood to encompass any and all sub-ranges subsumed therein. For example, a range of “less than 10” can include any and all sub-ranges between (and including) the minimum value of zero and the maximum value of 10, that is, any and all sub-ranges having a minimum value of equal to or greater than zero and a maximum value of equal to or less than 10, e.g., 1 to 4. FIG.1shows an embodiment of a joint. The joint100, connector, support device, joining device or single sided radial flexure ring, has a plurality of radial extensions, or flexors,110extending in at least a first direction from the joint100. The radial extensions110may be a multitude of radially compliant beams110or “flexures” that are pressed into a notch or notch area125in an adjoining part of a structure,120. At a distal end of the radial extensions110, a securing device may be used to further secure the joint100to the adjoining part of the structure. A contact surface135is provided along a length of the radial extensions110. This contact surface135is provided to engage or contact the radial extensions110to constrain a shape of the radial extensions110. Thus, the contact surface135improves the structural capability of the radial extensions110such as, but not limited to, preventing buckling and reducing radial extension stresses by spreading those stresses along the length of each radial extension110. Additionally, as disclosed, an amount of deflection of the radial extension110is reduced, thus allowing for thicker radial extensions110, which enables a more structurally capable embodiment. As further shown inFIG.1, the securing device may comprise openings or holes130at the distal end of the radial extensions110through which bolts310may be inserted. In another non-limiting example, the securing device may be a ring that slides over the distal end of the radial extensions110once they are within the notch or notch area125. Because of the arrangement of the radial extensions110, the joint100provides for an additional area for equipment120to fit within the joint100at an end135where the radial extensions110attach to the joint100. Though not shown, the joint100may comprise a connector attachable to a first part of an object that is a part of a structure. The connector may have a threaded component and the object that the joint may attach to may comprise receiving threads. FIG.2shows an embodiment of an upper cross section of the joint engaged with a receiving part andFIG.3shows the upper cross section of the joint shown inFIG.2with bolts310engaged. As shown, the radial extensions110engage notch or notch area125of the structure120. In another non-limiting example, a clamp may be used to secure the radial extensions110to the structure120. As further shown inFIG.3, bolts310are inserted through the openings130to secure the radial extensions110to the structure120. When the radial extensions110, which begin in an initially curved arrangement as disclosed herein, are connected to the notched area125, they may be pressed into a straight arrangement by way of the contact surface135. In an embodiment, the radial extensions110may have a downward curved arrangement to create a smaller diameter than when the radial extensions are not within the notched area125. In another embodiment, the radial extensions may have a curved arrangement in an opposite or upward direction. Utilizing the embodiments disclosed herein, more rapid connecting or separation from an adjacent part of a structure is realized while not compromising the strength of the joint when fully assembled when compared to prior art joints. Thus, as explained above, the plurality of radial extensions110may be configured to be flexible between a first position to a second position where the first position may provide for a curved arrangement and the second position provides for a straight arrangement. The first position is realized prior to assembly and after disassembly of the support device100(or as disclosed below400) to or from the receiving device120. The second position is realized when the support device100and the receiving device120are assembled. Thus, the support device mentioned above may also be the dual sided flexure ring400as discussed further herein. FIG.4shows an embodiment of a dual sided flexure ring. Though shown as a ring or having a cylindrical arrangement, this geometric shape is not limiting as any geometric shape may be provided. The geometric shape of the dual sided flexure ring400may be which is best based on an intended connection of the parts of a structure. A ring is shown herein as a ring shape may be a preferred embodiment for a small-scale missile. FIG.5shows a cross sectioned view of the dual sided flexure ring. The dual sided flexure ring400has two sets of plurality of radial extensions110. As shown, the two sets of plurality of radial extensions110extend in opposite directions from the ring400. A distal end510of each radial extension110may have an insertion element520,530that fits within the notched area125of the adjacent part120. The first insertion elements520of a set of radial extensions110extended in a same direction may be facing in a downward direction. The second insertion elements530of a second set of radial extensions110extended in a second same direction may be facing in an upward direction. Though the dual sided flexure ring400is shown having insertion elements520,530extending in opposite directions based on the direction the radial extensions extend, this arrangement is not limiting. In another embodiment, the insertion elements520,530may extend in a same direction, either upward or downward. As disclosed further herein, the dual sided flexure ring400may be used as a separating joint in conjunction with an actuation device and a release mechanism. FIGS.6and7show installation of the dual sided flexure ring as a joint.FIGS.6and7are cross sections of an upper half of the dual sided flexure ring400between the structure120such as, but not limited to, a missile, and the joint100. As discussed above, at the distal ends of the radial extensions110, the insertion elements520,530are provided. As discussed above, depending on the placement of the notched area,125, the insertion elements520,530may be facing in a first direction on the first plurality of radial extensions110and in an opposite direction on the second plurality of radial extensions110. The arrangement of the insertion elements520,530may be determined by the location of the respective notched areas125. Also shown inFIGS.6and7is a release mechanism660that may comprise a piston or movable device. By placement of the piston660when connecting the structure (i.e., receiving device120) and the joint100, the piston660may move towards the structure joint120. As the piston660is moved towards the structure120, the piston660may engage with a back side of the first plurality of radial extensions110and locks them into the notched area125. In another embodiment, such as disclosed below with respect toFIGS.13through17, the piston660may move radially outward to engage and lock the extensions110. As explained later herein, the movable device660may be used to cause separation of the joint100from the structure120. Also shown inFIGS.6and7is a retention device670. The retention device670may be a frangible bolt or screw which holds the movable device660. The retention device670is designed to break when under load. As shown inFIGS.4-6, the flexures or radial extensions110are curved and in a disengaged position in their initial, undeflected state. The curved arrangement is subtle in these figures. The curved arrangement positions the distal engaging end520,530away from the notched area125that it will engage as disclosed herein. Therefore, during connection or assembly, the radial extensions110are deflected towards the engagement groove, or notch area125. Prior art references are known to have flexures initially in a disengaged position, but where the disengaged position has the flexures initially straight, and where the flexures are in a curved arrangement when engaged with an engagement groove with no additional support along the length of the flexure. In such prior art, the structural effectiveness of the flexures is limited as they are susceptible to buckling when engaged as the flexures have a curved arrangement. As disclosed herein with respect to the pending embodiments, by being initially curved as taught herein, the radial extensions110overcome this limitation because their shape is provided so that when deflected to their assembled position, they then have a straight arrangement and are fully supported by the contact surface135. As a beam that is fully supported on both sides has a significantly higher allowable buckling load than an unsupported beam. In other words, the internal stress inside the straightened flexure may act as one side of a constraint or wall and the contact surface135acts as the other side. Being straight in the assembled position and constrained into a shape improves the structural effectiveness over the prior art. As also shown inFIGS.6-13, a connector, or locking device,680is shown. The connector680may be a threaded component, as disclosed. The connector680may be put in place once the dual sided flexure ring400is locked into place. Though a threaded arrangement is disclosed, other securing components may be used such as, but not limited to, a clamping device, detent device, etc. FIG.8shows a second installation of the dual sided flexure ring as a joint.FIG.8is a cross sections of an upper half of the dual sided flexure ring400between the first and second part100,120such as, but not limited to, parts of a missile. As discussed above, at the distal ends of the radial extensions110, the insertion elements520,530are provided. Depending on the placement of the notched area,125, the insertion elements520may be facing in a first direction on the first plurality of radial extensions110and in an opposite direction on the second plurality of radial extensions530. The arrangement of the insertion elements520,530may be determined by the location of the respective notched areas125. FIGS.9-13show separation of two parts of a structure at the dual sided flexure ring. As disclosed above with respect toFIGS.5-8, the first plurality of radial extensions110and the second plurality of radial extensions110are locked into place by the piston660and the locking part680. As shown inFIGS.9-13, by application of a force by the actuation device such as, but not limited to, an explosion from an explosive device or movement by an electro-mechanical device, the piston660is forced to disengage from the first plurality of radial extensions110. The force further causes the piston660to push against the first part100which causes the first part100to move away from the second part120. By the first part100moving away from the second part120, the locking device680releases the second plurality of radial extensions110. The first part100is now disconnected from the second part120, which provides for separation. In addition to the first part100and second part120separating, the dual sided flexure ring400may also separate from the first part100. Thus, in general, an actuation device such as, but not limited to, a directed explosion caused by an explosive device or a force generated by an electro-mechanical device, may activate the piston660which will disengage from the first plurality of radial extensions110. The piston660continues moving towards and then past the first plurality of radial extensions110and impinges on the first part100and starts pushing the first part100away. In a non-limiting embodiment, the first part100is a booster of the small-scale missile. As the first part100moves away from the second part120, the locking device680disengages from the second plurality of radial extensions110. Since no other components are holding either element in place, the second part120and the joint400fall away from the first part100. The radial extensions110exert their own disengagement force as they spring back to their initial position. This eliminates a need for springs/plungers, or any other hardware to disengage the radial extensions110from the notched area125. FIGS.14and15show a second embodiment of movable device.FIG.14shows the other movable device660′ once all parts are connected andFIG.15shows a view of the parts separated. The movable device660′ comprises a plurality of individual petals1410that move outwards to engage the extensions110and direct the extensions110into the notched areas125as a second ring1420is inserted onto a retaining device1430. Though the second ring1420and the retaining device1430are shown with a threaded engagement relationship, other engagement techniques may be utilized. More specifically, the movable device660′ comprises a plurality of individual petals1410that expand perpendicular towards a back side of the individual radial extensions110of at least a first plurality of radial extensions and a second plurality of radial extensions to direct a distal engagement end520,530of the individual radial extensions110of at least the first plurality of radial extensions110within the first notched receiver125and the second plurality of radial extensions110within the second notch area125. The petals1410may also retract to disengage the back side of the individual radial extensions110of at least the first plurality of radial extensions and the second plurality of radial extensions to release the distal engagement end520,530of the individual radial extensions of at least the first plurality of radial extensions from within the first notched receiver125and the second plurality of radial extension from within the second notch area125. The movable device660′ may also comprise an inner engagement element1420,1430that when activated causes the plurality of individual petals1410to extend perpendicularly towards the back side of the individual radial extensions110of at least the first plurality of radial extensions and the second plurality of radial extensions. When the engagement element1420,1430is deactivated it causes the plurality of individual petals1410to retract from the back side of the individual radial extensions110of at least the first plurality of radial extension and the second plurality of radial extensions. FIGS.16and17show the movable device in operation.FIG.16shows the retaining device1420before it is fully engaged with the retaining device1430. As shown, the petals1410have not fully engaged the extensions110resulting in the extensions110engaging the notched area125. As second ring1420is placed upon the retaining device1430, the individual petals1410are pushed radially outward to engage the extensions110into the notched areas125. FIG.18shows simulation results of embodiments disclosed herein against prior art. A graphical representation1800of joint stiffness is provided. The x-axis1810of the chart1800provides for stiffness and the y-axis1820provides for moment. As shown, the embodiments disclosed herein provide for improved strength and stiffness when compared to a bolted joint. FIG.19shows a method of separation adjacent parts of a structure. The method1900comprises activating a force to cause a device to move away from the force, at1910. Though not limited, the force may be the result of a detonation, such as an explosive detonation. The method1900further comprises releasing a first plurality of radial extensions held by the device to a first notched receiver of a first structure as the device moves away from the force which causes the first structure to move away from a second structure, at1920. The method1900further comprises releasing the second plurality of radial extensions held by the first structure to the second notched receiver of the second structure as the first structure moves away from the second structure, at1930. The method1900may further comprise transitioning the first plurality of radial extensions, at least one of the radial extensions having curved arrangement, and the second plurality of radial extensions, at least one of the radial extensions having a curved arrangement, to a straight arrangement when the first plurality of radial extensions are engaged with the first notched receiver and the second plurality of radial extensions are engaged with the second notched receiver, at1940. Unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art to which embodiments belong. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein. In particular, unless specifically stated otherwise as apparent from the discussion, it is appreciated that throughout the description, discussions utilizing terms such as “processing” or “computing” or “calculating” or “determining” or “displaying” or the like, refer to the action and processes of a computer system, or similar electronic computing device, that manipulates and transforms data represented as physical (electronic) quantities within the computer system's registers and memories into other data similarly represented as physical quantities within the computer system memories or registers or other such data storage, transmission or display devices. The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting. As used herein, the singular forms “a,” “an,” and “the” are intended to include the plural forms as well, unless the context clearly indicates otherwise. Furthermore, to the extent that the terms “including,” “includes,” “having,” “has,” “with,” or variants thereof are used in either the detailed description and/or the claims, such terms are intended to be inclusive in a manner similar to the term “comprising.” Moreover, unless specifically stated, any use of the terms first, second, etc., does not denote any order or importance, but rather the terms first, second, etc., are used to distinguish one element from another. As used herein the expression “at least one of A and B,” will be understood to mean only A, only B, or both A and B. While various disclosed embodiments have been described above, it should be understood that they have been presented by way of example only, and not limitation. Numerous changes, omissions and/or additions to the subject matter disclosed herein can be made in accordance with the embodiments disclosed herein without departing from the spirit or scope of the embodiments. Also, equivalents may be substituted for elements thereof without departing from the spirit and scope of the embodiments. In addition, while a particular feature may have been disclosed with respect to only one of several implementations, such feature may be combined with one or more other features of the other implementations as may be desired and advantageous for any given or particular application. Furthermore, many modifications may be made to adapt a particular situation or material to the teachings of the embodiments without departing from the scope thereof. Further, the purpose of the Abstract is to enable the U.S. Patent and Trademark Office and the public generally and especially the scientists, engineers and practitioners in the relevant art(s) who are not familiar with patent or legal terms or phraseology, to determine quickly from a cursory inspection the nature and essence of this technical disclosure. The Abstract is not intended to be limiting as to the scope of the present disclosure in any way. Therefore, the breadth and scope of the subject matter provided herein should not be limited by any of the above explicitly described embodiments. Rather, the scope of the embodiments should be defined in accordance with the following claims and their equivalents. | 22,485 |
11859649 | DETAILED DESCRIPTION Certain example embodiments will now be described to provide an overall understanding of the principles of the structure, function, manufacture, and use of the devices and methods disclosed herein. One or more examples of these embodiments are illustrated in the accompanying drawings. The devices and methods specifically described herein and illustrated in the accompanying drawings are non-limiting example embodiments and the scope of the present disclosure is defined solely by the claims. The features illustrated or described in connection with one example embodiment may be combined with the features of other embodiments. Such modifications and variations are intended to be included within the scope of the present disclosure. Additionally, to the extent that linear, circular, or other dimensions are used in the description of the disclosed systems and methods, such dimensions are not intended to limit the types of shapes that can be used in conjunction with such systems and methods. Equivalents to such linear, circular, or other dimensions can be determined for any geometric shape. Further, in the present disclosure, like-numbered components of the embodiments generally have similar features. Still further, sizes and shapes of the systems, and the components thereof, can depend at least on the anatomy of the subject in which the systems will be used, the size and shape of components with which the devices will be used, and the methods and procedures in which the devices will be used. Devices, systems, and methods for selectively coupling components, such as alignment guides or other tools to a modular handle for use in retaining and applying torque to the alignment guide or other tool are disclosed herein. In operation, the bearing assemblies disclosed herein can be used to receive a proximal end of an alignment guide or other instrument, with the bearing assembly securing the alignment guide or instrument upon insertion without any toggling of the alignment guide or instrument with respect to the bearing assembly (e.g., movement of the alignment guide or instrument in one direction into the bearing assembly can result in the alignment guide or instrument being secured without any possible subsequent movement of the alignment guide being possible). Similarly, once coupled, the alignment guide or instrument can be decoupled from the bearing assembly without any movement of the alignment guide or instrument with respect to the bearing assembly by depressing an endcap of the bearing assembly to release the internal clamping mechanism. This operation and related structural features, movements, and arrangements are discussed in more detail below. FIG.1Ais an isometric view of one embodiment of a surgical tool assembly10including an alignment guide200and a one-way axial and radial bearing assembly100(hereinafter referred to interchangeably as “the bearing assembly100”) according to aspects of the present disclosure. The surgical tool assembly10can be any arrangement of the bearing assembly100and the alignment guide200, for example, as a coupled arrangement (as shown inFIG.1A) or uncoupled (as shown inFIG.2A). The alignment guide200can be used to provide, for example, access to a polyaxial bone screw implanted in a patient during spine surgery. The alignment guide200can couple to the polyaxial bone screw inside the patient's body and can extend outside the patient's body, thereby providing a surgeon or other user with a means for manipulating the polyaxial bone screw position/orientation, providing access to the bone screw through an inner lumen of the alignment guide (e.g., for set screw application, etc.), etc. While the illustrated embodiment features the alignment guide200, the bearing assemblies disclosed here can be utilized in combination with any of a variety of other types of surgical instruments that may benefit from selective coupling with other components, such as a modular handle for the application of torque, etc. Returning toFIG.1A, the bearing assembly100includes a housing101, inside of which a proximal end of the alignment guide200is disposed and secured, as well as a handle102extending from the housing101and configured to enable a user of the bearing assembly100to position and/or deliver torque to the alignment guide200. The bearing assembly100secures the alignment guide200inside such that the alignment guide cannot be removed from the bearing assembly without proximal depression of an end cap120that is configured to release the internal mechanism of the bearing assembly100that secures the alignment guide to the bearing assembly. The bearing assembly100also rotatably secures the alignment guide200about its central axis99such that torque applied to the bearing assembly via the handle102is delivered to the alignment guide. As a convention, the free end of the alignment guide is established as the distal end (‘D’ inFIG.1A) and the opposite, captured end of the alignment guide200is established as the proximal end (‘P’ inFIG.1A), and the same convention is used hereinafter for the bearing assembly100as well.FIGS.1B,1C, and1Dare, front, side, and rear views, respectively, of the surgical tool assembly10ofFIG.1A.FIGS.1B and1Dillustrate that both the bearing assembly100and the alignment guide200can have a central passage109that extends entirely therethrough. In operation, this enables a user to insert an additional tool, such as a driver, through both the bearing assembly100and the alignment guide200in order to manipulate a fastener, shank, or other hardware inside of the proximal end of the alignment guide. Insertion of the alignment guide200into the bearing assembly100involves translating a proximal end210of the alignment guide200into a central opening of the bearing assembly100, as illustrated inFIG.2A. In some embodiments, the endcap120is depressed proximally to facilitate the ability to insert the alignment guide200into the bearing assembly100, but in some embodiments no actuation of the endcap120is required to insert the alignment guide200into the bearing assembly, with the endcap120only being used to release the alignment guide200, as explained in more detail below.FIG.2Bis cross-sectional view of the proximal end210of the alignment guide200ofFIG.2A, which shows that the proximal end has an exterior surface with a plurality of longitudinal grooves211formed therein and forming a series of ridges212therebetween. In operation, and as explained in more detail below, the insertion of the alignment guide200into the bearing assembly100includes the longitudinal grooves211being engaged by locking elements (e.g., ball bearings) that are radially coupled with the bearing assembly such that the alignment guide cannot freely rotate inside the bearing assembly. Additionally, the insertion also causes the locking elements to clamp onto the alignment guide200(e.g., radially inward toward the central axis99) in such a way that subsequent distal movement of the alignment guide relative to the bearing assembly100is prevented. FIG.3Ashows an exploded view of the various internal components of the one-way axial bearing assembly100ofFIG.2A. The bearing assembly100includes the housing101, an insert160, a bias element150, an inner race140, an outer race130, and the end cap120. The housing101defines a cavity108with an open distal end through which the insert160is inserted along the central axis99. The insert160includes flat sides161that are sized and shaped to abut corresponding flat sides106of the cavity108in the housing101such that, when inserted, the insert cannot rotate about the central axis99with respect to the housing. The inner race140is moveably disposed inside a cavity of the insert160, with the inner race having a series of protrusions141extending radially from the exterior of the inner race. The protrusions141are configured to engage with corresponding longitudinal grooves169on an inner surface of the cavity of the insert160such that the inner race can translate along the central axis99with movement of the protrusions141along the corresponding longitudinal grooves169, but rotational movement of the inner race relative to the insert about the central axis is prevented. Additionally, the bias element150is positioned in the cavity of the insert160proximal to inner race140such that the bias element urges the inner race distally and enables the inner race to be moved proximally against the force of the bias element150. The inner race140also includes a central passageway148and a plurality of ball bearings170that are positioned or captured in bores of the inner race and able to partially extend into the central passageway148. The outer race130is configured to be inserted into the housing101and the insert160around the exterior of the inner race140. The outer race130includes a distal flange that has flat edges131sized and shaped to be aligned with the flat sides161of the insert160when the outer race is disposed in the insert. The flat edges131also engage with the corresponding flat sides106of the cavity108in the housing101such that, when inserted, the outer race130cannot rotate in the housing160. The flange having the flat edges131also locates the outer race130proximally against a distal face of the insert160. Finally, the endcap120is configured to be threaded onto a distal end of the inner race140that protrudes distally beyond the distal face of the outer race130.FIG.3Bis a side-view of the exploded illustration ofFIG.3A, showing how the components of bearing assembly100can be secured together using a series of holes137,167,107through which a locking member (e.g., pin, bolt, etc.) can be disposed. When the insert160is disposed in the housing101, the hole107through the housing can be aligned with the hole167through the insert, and when the inner race140is disposed in the insert160and the outer race130is disposed around the inner race in the insert, the hole137in the outer race can also be aligned with the holes167,107in the insert and housing. When aligned, a pin or other locking member can be placed through all three holes to prevent removal of any and all of the outer race130, inner race140, bias element150, and insert160from the cavity of the housing101. FIG.3Cis an isometric cross-section illustration of the one-way axial bearing assembly100with all of the components assembled together.FIG.3Cshows that the proximal end143of the inner race140defines a stop position of the inner race in the insert160where proximal movement of the inner race against the bias element150is prevented due to contact of the proximal end143of the inner race with an inner distal-facing surface163of the proximal end of the insert160. Also visible inFIG.3Cis the central passageway148of the inner race140, which communicates with the bores147containing the ball bearings170.FIG.3Cshows the ball bearings170in a clamped position where the ball bearings are held in a radially-inward position by the outer race130, as explained in more detail below. FIG.3Dis an isometric cross-section of the insert160, showing the flat sides161, the longitudinal grooves169, the distal-facing inner surface163formed in a proximal portion of the insert, and the hole167. In some instances, the length of the longitudinal grooves169can be used alone (or in additional to the distal-facing inner surface163) to define a stop position of the inner race140in the insert160. The proximal portion of the insert160also defines an opening109that is present in both the distal end of the insert160and the distal end of the cavity108of the housing101. The opening109is sized smaller than the distal end of the inner race140to allow access to the inner passage219of the alignment guide while still forming a stop to prevent distal movement of the inner race140in operation. The opening109is also sized smaller than the proximal end210of the alignment guide200to form a proximal stop for the alignment guide and define a fully-inserted position of the alignment guide200within the bearing assembly100. In some embodiments, a proximal-facing surface of the housing101is configured to enable a user to impact the proximal-facing surface and direct an impulse to the alignment guide200via the terminal end of the alignment guide200being in direct contact with the proximal end of the insert160, and the proximal end of the insert160being in direct contact with the proximal end of the housing101. FIG.3Eis an isometric cross-section of the outer race130, showing the flat edges131.FIG.3Ealso shows the inner surface of the outer race130that is configured to be positioned around the inner race140. The inner surface includes a distal surface134portion and a proximal surface135portion. The proximal surface135is positioned to be disposed around the bores147of the inner race140and defines a tapered diameter that increases proximally from the diameter of the distal surface134. In some instances, the distal surface134defines a constant diameter or is otherwise configured to enable the outer race130to move concentrically long the exterior of the inner race140.FIG.3Fis an isometric view of the inner race140with the bores147and protrusions141visible. The inner race140has an exterior surface143that is sized and shaped to have the inner surface of the outer race130disposed around the exterior surface143with the inner race140being free to move along the central axis99relative to the outer race130when assembled. Additionally, the exterior surface143includes a flange142that extends radially outward and includes the protrusions141. The outer race130can include a terminal proximal edge139that is configured to be a distal stop for the inner race140such that distal movement of the inner race with respect to the outer race130is prevented once the flange142contacts the terminal proximal edge139, as shown in more detail inFIG.4A. FIG.4Ais a side cross-sectional view of the one-way axial bearing assembly100ofFIG.3Cin a fully extended or resting configuration, such that the bias element150has moved the inner race140distally with respect to the housing101, insert160, and inner race130until the flange142of the inner race140abuts the terminal proximal edge139of the outer race130. The distal movement (as indicated by arrow401) of the inner race140slides the ball bearings170against the tapered distal surface134of the outer race130and the decreasing tapered diameter of the distal surface134forces the ball bearings radially inward in their bores147, towards the central axis99, and into the central passageway148of the inner race140. In some instances, and as shown inFIG.4A, the distal movement of the inner race140can translate the ball bearings170distally until the ball bearings are positioned against the distal surface134of the out race130. In this position, without any taper on the distal surface134, forcing of the ball bearings170radially outward against the distal surface134will not urge the inner race proximally. This position of the inner race140and ball bearings170can be described as a fully-extended or resting position, as this is the default position of the bearing assembly100without an alignment guide200inserted. Insertion of the alignment guide can begin with a user depressing the flange122of the end cap120, as shown inFIG.4B, or simply with the insertion of the proximal end210of the alignment guide200into the central passageway148. InFIG.4B, a user depresses the endcap120proximally (arrows403) and moves the inner race140proximally until the proximal end143of the inner race140contacts the inner distal-facing surface163of the proximal end of the insert160. The proximal movement of the inner race140translates the ball bearings proximally along the proximal surface135of the outer race130and the increasing tapered diameter of the proximal surface135allows the ball bearings to move away from the central axis99and at least partially out of the central passage148. This position can be described as a compressed or unclamped position.FIG.4Balso illustrates the proximal end210of the alignment guide being inserted proximally (as indicated by arrow402) into the central passageway148. Importantly, in some configurations, the user depressing the endcap120proximally is optional, and the proximal insertion402of the proximal end of the alignment guide200causes the proximal end210to contact the ball bearings170in the resting position (as shown inFIG.4A), after which further proximal insertion of the alignment guide200drives the inner race140proximally until the ball bearings have moved sufficiently proximally along the inner surface135such that the ball bearings170are moved out of the central passageway148far enough for the proximal end210of the alignment guide200to be fully inserted into the central passageway, as shown inFIG.4C. InFIG.4C, the user can continue to depress the endcap120to keep the inner race140in the unclamped position as the alignment guide200is fully inserted, whereby the terminal proximal end of the alignment guide200abuts the inner distal-facing surface163of the proximal end of the insert160. Regardless of whether the user depresses the endcap120to move the inner race140to the unclamped position or if insertion of the alignment guide200itself moves the inner race140proximally, the ball bearings170do not prevent movement of the alignment guide200in the proximal direction. However, once the user releases the endcap120or, in the case of alignment guide200insertion alone, once the alignment guide is fully inserted or proximal insertion is stopped, the bearing assembly100enters a clamped position with respect to the alignment guide200, as shown inFIG.4D, as a result of the force applied by bias element150on the inner race140in the distal direction. InFIG.4D, the alignment guide200is fully inserted and either the user has released the endcap120and the inner race140has moved distally (as indicated by arrows404) to the position shown, or the illustrated position indicates the arrangement of the inner race140during insertion of the alignment guide200, once the ball bearings170have moved sufficient to allow the alignment guide200to pass proximally. InFIG.4D, the ball bearings170are positioned between the inner surface135and the proximal end210of the alignment guide200such that the ball bearings170are wedged by the tapered diameter of the proximal surface135of the outer race130and any further distal movement of the inner race140is prevented. Accordingly, the engagement also strongly clamps the ball bearings170against the surface of the proximal end210of the alignment guide200(e.g., perpendicular to the central axis99), which prevents any distal movement of the alignment guide200with respect to the inner race140and, accordingly, with respect to the housing101. FIG.4Eis a front cross-sectional view of the C-C plane drawn on the one-way axial bearing assembly100inFIG.4D. InFIG.4Ethe radial locking of the components of the bearing assembly and of the alignment guide200is visible. The ball bearings170are seated in the longitudinal grooves211of the proximal end210of the alignment guide200and prevent rotation of the alignment guide with respect to the inner race140. The inner race140is rotatably coupled with the insert160via the protrusions being disposed in the grooves169of the insert160, and the insert160is coupled with the housing101via the flat surfaces161in a manner that prevents relative rotation. Additionally, the interaction between the ball bearings170and the longitudinal grooves211and ridges212on the proximal end210of the alignment guide200can create a self-aligning interaction such that insertion of the alignment guide without the ball bearings170being seated in the longitudinal grooves211is self-corrected due to the instability of the ball bearings170contacting the ridges212and the ability of the alignment guide200to rotate relative to the inner race140when the ridges212contact the ball bearings170. Accordingly, during insertion of the alignment guide200into the central passage148without user depression of the end cap120, once the ball bearings170are moved by the ridges212of the alignment guide, even subtle rotation of the alignment guide in either direction moves the ball bearings170off the ridges212and into the longitudinal grooves211. The ball bearings170entering the longitudinal grooves211allows the inner race140to move distally as the ball bearings can now move radially inward as urged by the bias element150(e.g., the longitudinal grooves211present a smaller diameter to the ball bearings170as compared to the ridges212), and once the ball bearings170are in the longitudinal grooves211further rotation of the alignment guide200relative to the inner race140is not possible. There are a number of different techniques for coupling two components together in a manner that prevents relative rotation, many of which may be suitable for use with aspects of the present disclosure. Similarly, while the clamping elements discussed herein are shown as ball bearings, other clamping elements may be suitable with minor modification, such as rollers, etc.FIG.4Fis a front view cross-section of the D-D plane drawn on the one-way axial bearing assembly100inFIG.4Dmore clearly showing the coupling between the inner race140and the insert160, and the insert160with the housing101, in a manner that prevents relative rotation therebetween. Turning toFIG.4G, in order to free the alignment guide200from the bearing assembly, a user can depress the endcap120proximally (as indicated by arrows405), which moves the inner race140to the unclamped position with the ball bearings170no longer being wedged against the alignment guide200due to the inner race140moving the ball bearings in the direction of the increasing tapered diameter of the inner surface135, thereby allowing the ball bearings170to move radially outward and away from the alignment guide and removing the clamping force. With the endcap120depressed, the alignment guide200is free to be withdrawn from the central passage148of the inner race140and thereby removed from the bearing assembly100, as shown inFIG.4H(where the distal removal of the alignment guide200is indicated by arrow406). While the components of the bearing assembly100have been shown as individual elements, one or more of the components can be formed as common structures. For examples, in some embodiments, the housing101and the insert160can be a single structure or otherwise permanently joined. Additionally, while the bearing assembly100and the alignment guide are both illustrated as being circular, other shapes are possible, such as rectangular or ovoid, with such configurations having central passageways148sized and shaped to accept the shape of the alignment guide, and, in some examples, can also be similarly shaped inside the bearing assembly, such as the inner and outer races have rectangular shapes to match the shape of the alignment guide. In such examples, there may be no need for coupling the alignment guide in a manner that prevents rotation, as a rectangular or polygonal shaped alignment guide may already be rotationally constrained within a corresponding rectangular or polygonal shaped central passage. Also, while the bearing assembly100has been illustrated as a hand-held device with a handle101, other uses are possible, such as integration into a stationary structure or surgical robot. The housing101can provide a cavity and a distal opening, and this arrangement can be provided in number of different structures. Other embodiments of the present disclosure include a bearing assembly that incorporates dual bearing assemblies in an opposed design to fully constrain movement of an alignment guide relative to the bearing assembly (e.g., as opposed to the above-described configurations where movement in one direction can be permitted while movement in an opposite direction is prevented). Such a configuration can utilize two separate inner races aligned to form a single central passageway but oriented to move in opposite axial directions such that manual actuation of the inner races (e.g., pressing both towards each other) clears the central passage (e.g., no ball bearings are forced into the central passage from either inner race) to allow an alignment guide to be positioned in the central passage through both inner races. Thereafter, once the inner races are released, they are moved in opposite directions by respective bias elements to respective clamping positions that prevent subsequent axial movement of the alignment guide in either axial direction. Rotation can be prevented as well, as described herein. This bi-directional or dual-axial constraint of the alignment guide is in contrast to the single-directional or axial constraint created by the bearing assembly100ofFIG.4A, where once the ball bearings170are clamped down onto the alignment guide, further proximal movement of the alignment guide is still permitted until the alignment guide contacts the inner distal-facing surface163of the proximal end of the insert160. One embodiment of surgical tool assembly including an alignment guide and handle with a fully-constrained axial bearing assembly50is shown inFIG.5. The assembly50can include a fully-constrained or dual-axial bearing assembly500, a housing501, inside of which a proximal end of the alignment guide200is disposed and secured, as well as a handle502extending from the housing and configured to enable a user of the assembly50to position and/or deliver torque to the alignment guide200. A cross-section of the dual-axial bearing assembly500(e.g., a fully-constrained axial bearing, as rotation is prevented as well) is illustrated inFIGS.6A-6C. Referring toFIG.6A, the dual-axial bearing assembly500includes a distal bearing section509aand a proximal bearing searing509b, with the distal bearing section509abeing arranged similarly to the bearing assembly100ofFIG.4A, but with an addition proximal bearing searing509bdirectly coupled to a common housing501and in an orientation that is flipped 180° about the proximal-distal direction of a common central axis99. The common housing501, as compared to the housing101ofFIG.4A, is extended in the proximal-distal direction to include an elongated cavity in which the components of the distal bearing section509aare disposed and the components of the proximal bearing section509bare disposed. As with the bearing assembly100ofFIG.4A, the housing501of the dual-axial bearing assembly500and one or both of the distal insert506aand the proximal insert560bcan be integrated with the common housing501. Additionally, and as shown inFIG.6A, a common insert560is disposed within the common housing501. In some instances this common insert560is separated into distal and proximal sections, but the cavity of the common housing501ofFIG.6Ais a through bore and enables a common insert560to be disposed therein and coupled to the common housing501using, for example, the same locking body through holes discussed in view ofFIG.3A. Returning toFIG.6A, the common insert560includes a central flange563that provides a distal face as a bearing surface, a distal bias element550a, and a proximal face as a bearing surface for a proximal bias element550b. The central flange563has a central opening to allow the respective central passageways548a,548bof the distal and proximal inner races540a,540bto be connected, however, the central flange563of the dual-axial bearing assembly500is shown to be slightly larger than the opening109of the bearing assembly100ofFIG.4A, as the central flange563of the dual-axial bearing assembly500is sized to allow an alignment guide200(shown inFIG.5) to pass through the distal central passageway548aand into the proximal central passageway548b. Other embodiments include a common insert560without a central flange563, with the distal bias element550aand the proximal bias element550bbeing either a single bias element or otherwise arranged to work together to bias the distal and proximal inner races540a,540bin their respective directions. In such a configuration, the inner stopping positions (e.g., the proximal-most location of the distal inner race540aand the distal-most location of the proximal inner race540b) can be defined by, for example, their respective interactions with the respective longitudinal grooves569a,569bin the common insert560, or another structural interface. Continuing to refer to the dual-axial bearing assembly500ofFIG.6A, the distal bearing section509aincludes a distal inner race540apositioned in a proximal section of the common insert560, and includes a flange541aand protrusions542athat are disposed in and travel along distal longitudinal grooves569ain the common insert560. The distal bearing section509aalso includes a distal outer race530aaround the distal inner race540a, with the distal inner race540aand the distal outer race530abeing arranged to function similar to the outer and inner races130,140of the bearing assembly100, such that ball bearings570ain the inner races are moved into the distal inner passage548awith distal movement of the distal inner race540awith respect to the distal outer race530adue to the ball bearings570aengaging with a tapered proximal inner surface535aof the distal outer race530a. A distal endcap520ais coupled with the distal end of the distal inner race540ato enable a user to depress the distal inner race540ain the proximal direction against the distal bias element until the distal inner race540acontacts the central flange563in a fully compressed or unclamped position. The proximal bearing section509bis arranged similarly, with a proximal inner race540bdisposed inside of a stationary or fixed proximal outer race530b, with the proximal inner race540bhaving ball bearings570bthat are engaged with a distal inner surface535bof the proximal outer race530bsuch that the proximal movement of the proximal inner race540bunder the urging of the proximal bias element550bmoves the ball bearings570binto the proximal central passage548and a user's depressing of the proximal endcap520battached the proximal inner race540bmoves the proximal inner race540bdistally where the tapering of the distal inner surface535ballows the ball bearings570bto move radially away from the central axis99. In operation, and as shown inFIG.6B, a user squeezes the distal endcap520aand the proximal endcap520btowards each other (as indicated by opposed arrows505aand505b), which compresses both the distal bias element550aand the proximal bias element550buntil the distal inner race540ais moved to a proximal-most position in the common insert560(e.g. the proximal end of the distal inner race540acontacts the distal-facing surface of the central flange563) and the proximal inner race540bis moved to a distal-most position in the common insert560(e.g. the distal end of the proximal inner race540bcontacts the proximal-facing surface of the central flange563). In this configuration that is shown inFIG.6B, the ball bearings570aof the distal inner race540aare free to move out of the distal inner passage548aand the ball bearings570bof the proximal inner race540bare free to move out of the proximal inner passage548a. Accordingly, in this arrangement, an alignment guide200(shown inFIG.5) is free to be inserted into the dual-axial bearing assembly500from either direction and to any axial position, and once the alignment guide is inserted past both the ball bearings570aof the distal inner race540aand the ball bearings570bof the proximal inner race540b, the user can release the squeezing force on both the distal endcap520aand the proximal endcap520b. This allows both (i) the distal bias element550ato move the distal inner race540ain the distal direction, thereby clamping the ball bearings570aonto the alignment guide and preventing distal movement of the alignment guide, and (ii) the proximal bias element550bto move the proximal inner race540bin the proximal direction, thereby clamping the ball bearings570bonto the alignment guide and preventing proximal movement of the alignment guide. This fully-clamped position of the dual-axial bearing assembly500is illustrated inFIG.6C. InFIG.6C, an elongated end210′ of an alignment guide200′ is captured by the dual-axial bearing assembly500such that an inner passage219′ of the alignment guide200′ is disposed through the entire central passage548aof the distal inner race540aand almost all of the central passage548bof the proximal inner race540b. The distal bias element550apushes the distal inner race540ain the distal direction (as indicated by arrows506a) and the proximal bias element550bpushes the proximal inner race540bin the proximal direction (as indicated by arrows506b). In this configuration, neither proximal nor distal movement of the alignment guide200′ is possible. Additionally, longitudinal grooves in the elongated proximal end210′ of the alignment guide200′ are engaged with both the ball bearings570aof the distal inner race540aand the ball bearings570bof the proximal inner race540bsuch that rotation of the alignment guide200′ with respect to the dual-axial bearing assembly500is prevented. While the bearing assembly100ofFIG.4Aand the dual-axial bearing assembly500ofFIG.6Aare illustrated as being user-actuated, either or both of these devices can be actuated by an automated mechanism such as a surgical robot or any mechanical actuator coupled to (or in place of) the end cap. For example, an electric motor, such as a Lorentz force actuator, can be integrated with either bearing assembly such that movement of the endcap to release the alignment guide can be triggered with an electrical signal that generates a force on a coil integrated with the inner race to move the inner race against the bias element. Such an actuator can also be used in the opposite direction to ensure complete locking of the inner race by assisting the bias element and delivering additional force onto the inner race after the inner race is moved to the clamping position. Additionally, while the bearing assembly100ofFIG.4Aand the dual-axial bearing assembly500ofFIG.6Aare illustrated as having 4 ball bearings in their respective inner races, any number of locking elements is conceived, including 1, 2, 3, or 5 or more ball bearings or other locking elements. Additionally, while each inner race is shown as having a single annular bank of ball bearings, it is conceived that two or more banks can be used with, for example, larger diameter ball bearings that enable the tapered surface of the outer race to engage with two sizes of ball bearings simultaneously. Additionally, it is within the scope of this disclosure to include a lock or other preventative mechanism for preventing unwanted depression of an endcap or a mechanism for holding an endcap in an unclamped position until released. While the bias elements are illustrated as being springs this is only a representative example of a bias element, and any number of different bias elements may be suitable for use with the bearing assembly100ofFIG.4Aand the dual-axial bearing assembly500ofFIG.6A, such as pneumatic springs or magnets. Additionally, while the bearing assembly100ofFIG.4Aand the dual-axial bearing assembly500ofFIG.6Aare each illustrated as having a single inner race for each axial direction that is constrained, it is also possible to have two or more sequential inner races that each operate independently in order to more securely clamp onto an elongated alignment guide. As noted above, any of a variety of surgical procedures can be performed utilizing the surgical tools described herein. In particular, the bearing assemblies disclosed herein can be utilized in connection with a variety of surgical instruments that can benefit from selective coupling with another instrument, such as a modular handle for application of torque/counter-torque, etc. These can include the alignment guides featured in the illustrated embodiments above, but also other instruments, such as drivers, other guide tubes, etc. The embodiments disclosed herein can find utility in various spine surgeries, such as in connection with open and/or minimally-invasive surgeries for treatment of acute and chronic instabilities or deformities of the spine. Alternative orthopedic applications and other types of surgeries can also benefit from use of the embodiments disclosed herein. It should be noted that any ordering of method steps expressed or implied in the description above or in the accompanying drawings is not to be construed as limiting the disclosed methods to performing the steps in that order. Rather, the various steps of each of the methods disclosed herein can be performed in any of a variety of sequences. In addition, as the described methods are merely exemplary embodiments, various other methods that include additional steps or include fewer steps are also within the scope of the present disclosure. The instruments, devices, and systems disclosed herein can be constructed from any of a variety of known materials. Exemplary materials include those which are suitable for use in surgical applications, including metals such as stainless steel, titanium, nickel, cobalt-chromium, or alloys and combinations thereof, polymers such as PEEK, ceramics, carbon fiber, and so forth. The various components of the instruments disclosed herein can have varying degrees of rigidity or flexibility, as appropriate for their use. Device sizes can also vary greatly, depending on the intended use and surgical site anatomy. Furthermore, particular components can be formed from a different material than other components. One or more components or portions of the instrument can be formed from a radiopaque material to facilitate visualization under fluoroscopy and other imaging techniques, or from a radiolucent material so as not to interfere with visualization of other structures. Exemplary radiolucent materials include carbon fiber and high-strength polymers. The devices, systems, and methods disclosed herein can be used in minimally-invasive surgery and/or open surgery. While the devices and methods disclosed herein are generally described in the context of orthopedic surgery on a human patient, it will be appreciated that the methods and devices disclosed herein can be used in any of a variety of surgical procedures with any human or animal subject, or in non-surgical procedures. The devices disclosed herein can be designed to be disposed of after a single use, or they can be designed to be used multiple times. In either case, however, the device can be reconditioned for reuse after at least one use. Reconditioning can include any combination of the steps of disassembly of the device, followed by cleaning or replacement of particular pieces, and subsequent reassembly. In particular, the device can be disassembled, and any number of the particular pieces or parts of the device can be selectively replaced or removed in any combination. Upon cleaning and/or replacement of particular parts, the device can be reassembled for subsequent use either at a reconditioning facility, or by a surgical team immediately prior to a surgical procedure. Those skilled in the art will appreciate that reconditioning of a device can utilize a variety of techniques for disassembly, cleaning/replacement, and reassembly. Use of such techniques, and the resulting reconditioned device, are all within the scope of the present application. The devices described herein can be processed before use in a surgical procedure. First, a new or used instrument can be obtained and, if necessary, cleaned. The instrument can then be sterilized. In one sterilization technique, the instrument can be placed in a closed and sealed container, such as a plastic or TYVEK bag. The container and its contents can then be placed in a field of radiation that can penetrate the container, such as gamma radiation, x-rays, or high-energy electrons. The radiation can kill bacteria on the instrument and in the container. The sterilized instrument can then be stored in the sterile container. The sealed container can keep the instrument sterile until it is opened in the medical facility. Other forms of sterilization known in the art are also possible. This can include beta or other forms of radiation, ethylene oxide, steam, or a liquid bath (e.g., cold soak). Certain forms of sterilization may be better suited to use with different portions of the device due to the materials utilized, the presence of electrical components, etc. The embodiments of the present disclosure described above are intended to be merely examples; numerous variations and modifications are possible and considered within the scope of this disclosure. Accordingly, the disclosure is not to be limited by what has been particularly shown and described. All publications and references cited herein are expressly incorporated by reference in their entirety, except for any definitions, subject matter disclaimers or disavowals, and except to the extent that the incorporated material is inconsistent with the express disclosure herein, in which case the language in this disclosure controls. Examples of the above-described embodiments can include the following:1. An assembly, comprising:a housing defining a cavity with a central axis extending from a proximal end of the housing to a distal end of the housing, as well as an opening to the cavity formed at the distal end of the housing;an inner race disposed in the cavity of the housing and defining an interface between the housing and the inner race, the interface enabling translation of the inner race along the central axis and resisting rotation of the inner race about the central axis, the inner race comprising an inner surface defining a central passage configured to receive a portion of an alignment guide;a biasing element that urges the inner race distally along the central axis toward the opening;an outer race disposed in the cavity and fixed relative to the housing, the outer race including an inner surface surrounding an outer surface of the inner race, at least a portion of the inner surface defining a tapered region having decreasing diameter towards the opening to the cavity;a plurality of clamping elements carried by the inner race such that (i) movement of the inner race distally toward the opening of the cavity engages the plurality of clamping elements against the inner surface of the outer race, the inner surface of the outer race urging the plurality of clamping elements into the central passage of the inner race and towards the central axis, and (ii) movement of the inner race proximally away from the opening of the cavity translates the plurality of clamping elements along the tapered region such that the increasing diameter allows the plurality of clamping elements to move out of the central passage and away from the central axis;wherein, after insertion of an alignment guide sized to contact the plurality of clamping elements into the central passage of the inner race in the proximal direction, engagement of the plurality of clamping elements with the tapered region prevents movement of the inner race and the alignment guide in the distal direction.2. The assembly of claim1, wherein insertion of an alignment guide sized to contact the plurality of clamping elements into the central passage of the inner race in the proximal direction causes the inner race to be translated proximally with the alignment guide until the clamping elements are allowed to move sufficiently out of the central passage to allow the alignment guide to pass further into the central passage and the cavity.3. The assembly of any of claims1to2,wherein the inner race is moveable in the proximal direction to an unclamped position where the plurality of clamping elements are allowed to move away from the central axis to permit insertion of an alignment guide sized to contact the plurality of clamping elements into the central passage of the inner race in the proximal direction, andwherein the inner race is moveable in the distal direction to a clamped position wherein the plurality of clamping elements are urged towards the central axis to apply a clamping force to the alignment guide.4. The assembly of any of claims1to3,wherein the central passage of the inner race is cylindrical,wherein the plurality of clamping elements are circumferentially fixed with respect to the inner race; andwherein insertion of a cylindrical alignment guide comprising one or more grooves sized to receive and contact the plurality of clamping elements causes the cylindrical alignment guide to be rotationally fixed about the central axis with respect to the housing.5. The assembly of any of claims1to4, wherein, when an alignment guide is disposed in the central passage such that the plurality of clamping elements prevent movement of the alignment guide in the distal direction, translation of the inner race in the proximal direction enables removal of the alignment guide in the distal direction.6. The assembly of claim5, further comprising an end cap coupled to the inner race and extending out of the opening in the housing, the end cap defining a flange for applying a force to the inner race in the proximal direction to release an alignment guide.7. The assembly of any of claims1to6, wherein the biasing element is a compression spring.8. The assembly of any of claims1to7, wherein the housing comprises an insert disposed in an outer cavity of the housing, the insert defining the cavity containing the inner race to be inserted through the opening of the housing, the insert defining an inner cavity.9. The assembly of claim8,wherein the outer cavity defines a non-circular cross section parallel to the central axis, andwherein an exterior of the insert is configured to interface with the outer cavity such that the insert is rotationally fixed in the outer cavity about the central axis.10. The assembly of any of claims1to9,wherein the cavity comprises a plurality of grooves extending parallel to the central axis, andwherein the interface of the inner race comprises a plurality of protrusions, each of the plurality of protrusions being translatably disposed in a corresponding one of the plurality of protrusions.11. The assembly of any of claims1to10,wherein the housing defines a stop surface in the cavity positioned to be contacted by an end of an alignment guide such that the stop surface defines a position of maximum insertion of the alignment guide in the cavity, andwherein the stop enables an impact force to be directed from the housing to an end of a fully inserted alignment guide via the stop.12. The assembly of any of claims1to11, wherein the housing defines a second opening into the cavity formed at the proximal end of the housing, the second opening being arranged such that an inner lumen of an alignment guide disposed in the central cavity of the inner race is accessible through the second opening.13. The assembly of any of claims1to12, wherein the outer race is rotationally fixed in the cavity about the central axis.14. The assembly of any of claims1to13, wherein the outer race is configured to abut the inner race when the inner race is biased distally to a fully extended position.15. The assembly of claim14, wherein, in the fully extended position, the plurality of clamping members are urged toward a maximally inward position with respect to the central axis.16. The assembly of claim14,wherein the inner race is configured to abut the housing when the inner race is moved proximally to a fully compressed position, andwherein, in the fully compressed position, the plurality of clamping elements are free to move to a maximally outward position with respect to the central axis.17. The assembly of any of claims1to16, comprising a handle coupled to the housing, the handle configured to enable a user to apply torque to the housing, the torque being transferred to an alignment guide disposed in the central passage via the interface of the inner race and the plurality of clamping elements.18. The assembly of any of claims1to17, further comprising:a second opening to the cavity formed at the proximal end of the housing;a second inner race disposed in the cavity of the housing and translatable in the cavity along the central axis, the second inner race comprising a second inner surface defining a second central passage concentrically aligned with the central passage and configured to receive the portion of an alignment guide after passing through the central passage of the inner race;a second outer race disposed in the cavity and fixed along the central axis, the second outer race comprising a second inner surface surrounding a second outer surface of the second inner race, at least a portion of the second inner surface defining a second tapered region having decreasing diameter towards the second opening to the cavity, the decreasing diameter being with respect to the central axis;a second plurality of clamping elements carried by the second inner race such that (i) movement of the second inner race proximally toward the second opening of the cavity engages the plurality of clamping elements against the second inner surface of the second outer race, the second inner surface urging the second plurality of clamping elements into the second central passage of the second inner race and towards the central axis, and (ii) movement of the second inner race distally away from the second opening of the cavity translates the second plurality of clamping elements along the second tapered region such that the increasing diameter allows the second plurality of clamping elements to move out of the second central passage and away from the central axis.19. The assembly of claim18, further comprising a second biasing element that urges the second inner race proximally along the central axis toward the second opening.20. The assembly of claim18, further comprising an end cap coupled to the second inner race and extending out of the second opening in the housing, the end cap defining a flange for applying a force to the second inner race in the distal direction to release an alignment guide.21. The assembly of any of claims1to20, further comprising an alignment guide, the alignment guide comprising a hollow shaft with a plurality of longitudinally-extending parallel grooves formed around an exterior portion of the hollow shaft, the hollow shaft being configured to be inserted into the central passage and the plurality of parallel grooves being configured to engage with the plurality of clamping elements.22. The assembly of claim21, wherein the plurality of parallel grooves are spaced such that a misaligned engagement of the exterior portion with the plurality of clamping elements results in the biased movement of the inner race rotating the alignment guide about the central axis such that the plurality of clamping elements are engaged in the plurality of parallel grooves.23. The assembly of any of claims1to22, wherein the plurality of clamping elements comprises ball bearings.24. An assembly, comprising:a housing having a cavity with an opening disposed at a distal end of the housing;a first race disposed within the cavity and configured to translate relative to the housing along a longitudinal axis of the cavity extending from a proximal end thereof to the opening and remain locked against rotation relative to the housing about the longitudinal axis;a plurality of bearing elements disposed within bores formed in the first race and configured to move radially relative to the longitudinal axis of the housing;a second race disposed in the cavity of the housing and configured to remain fixed relative to the housing;wherein the first race is biased distally toward the opening of the cavity;wherein the second race surrounds the first race and includes an inner surface having a tapered diameter that decreases from a proximal position to a distal position;wherein the inner surface of the second race is configured to contact the plurality of bearing elements as the first race moves distally relative to the second race such that inner surface of the second race urges the plurality of bearing elements radially inward.25. The assembly of claim24, wherein insertion of an alignment guide proximally into an opening in the first race causes the first race to translate proximally until the plurality of bearing elements move radially outward a sufficient amount to allow the alignment guide to pass further.26. The assembly of any of claims24to25,wherein the first race is moveable in the proximal direction to an unclamped position where the plurality of bearing elements are allowed to move radially outward to permit insertion of an alignment guide proximally into an opening of the first race, andwherein the first race is moveable in the distal direction to a clamped position wherein the plurality of bearing elements are urged radially inward to apply a clamping force to the alignment guide.27. The assembly of any of claims24to26, wherein, when an alignment guide is disposed such that the plurality of bearing elements prevent distal movement of the alignment guide, proximal translation of the first race enables distal movement of the alignment guide.28. The assembly of claim27, further comprising an end cap coupled to the first race, the end cap defining a flange for applying a force to the first race in the proximal direction to release an alignment guide.29. The assembly of any of claims24to28, wherein the housing defines a second opening into the cavity formed at the proximal end of the housing, the second opening being arranged such that an inner lumen of an alignment guide disposed in the housing is accessible through the second opening.30. The assembly of any of claims24to29, further comprising a handle coupled to the housing, the handle configured to enable a user to apply torque to the housing, the torque being transferred to an alignment guide disposed in the housing via the plurality of bearing elements.31. The assembly of any of claims24to30, further comprising:a second opening to the cavity formed at the proximal end of the housing;a third race disposed in the cavity of the housing and configured to translate relative to the housing along the longitudinal axis of the cavity and remain locked against rotation relative to the housing about the longitudinal axis;a second plurality of bearing elements disposed within bores formed in the third race and configured to move radially relative to the longitudinal axis of the housing;a fourth race disposed in the cavity of the housing and configured to remain fixed relative to the housing;wherein the third race is biased proximally toward the second opening of the cavity;wherein the fourth race surrounds the third race and includes an inner surface having a tapered diameter that decreases from a distal position to a proximal position;wherein the inner surface of the fourth race is configured to contact the second plurality of bearing elements as the third race moves proximally relative to the fourth race such that the inner surface of the fourth race urges the second plurality of bearing elements radially inward.32. The assembly of claim31, further comprising an end cap coupled to the third race and extending out of the second opening in the housing, the end cap defining a flange for applying a force to the third race in the distal direction to release an alignment guide.33. The assembly of any of claims24to32, further comprising an alignment guide, the alignment guide comprising a hollow shaft with a plurality of longitudinally-extending parallel grooves formed around an exterior portion of the hollow shaft, the hollow shaft being configured to be inserted into the cavity of the housing and the plurality of parallel grooves being configured to engage with the plurality of bearing elements.34. The bearing assembly of claim33, wherein the plurality of parallel grooves are spaced such that a misaligned engagement of the exterior portion with the plurality of bearing elements results in the biased movement of the first race rotating the alignment guide about the longitudinal axis such that the plurality of bearing elements are engaged in the plurality of parallel grooves.35. A surgical method, comprising:advancing a modular handle assembly distally over a proximal end of an alignment guide such that the alignment guide enters a cavity of the modular handle assembly and urges a race of the modular handle assembly in a proximal direction against a distal biasing force to permit a plurality of clamping elements coupled to the race to move radially outward from a central axis of the cavity and thereby permit proximal movement of the alignment guide relative to the race; andselectively locking the modular handle assembly relative to the alignment guide such that the modular handle assembly can be further advanced distally over the alignment guide but cannot be retracted proximally and cannot be rotated relative to the alignment guide.36. The method of claim35, wherein selectively locking the modular handle assembly includes urging the race in a distal direction to cause the plurality of clamping elements coupled to the race to move radially inward toward the central axis of the cavity and contact an outer surface of the alignment guide.37. The method of any of claims35to36, further comprising unlocking the modular handle assembly relative to the alignment guide by moving the race of the modular handle assembly in a proximal direction to permit the plurality of clamping elements coupled to the race to move radially outward from the central axis of the cavity.38. The method of claim37, further comprising rotating the modular handle assembly about the alignment guide while the modular handle assembly is unlocked relative to the alignment guide.39. The method of any of claims35to38, wherein moving the race of the modular handle assembly includes applying a proximal force to a flange of an end cap coupled to the race.40. The method of claim38, further comprising selectively locking the modular handle assembly relative to the alignment guide to prevent relative rotation between the two components.41. A surgical method, comprising:unlocking a modular handle assembly;moving the modular handle assembly relative to an alignment guide such that the alignment guide passes through a cavity of the modular handle assembly; andlocking the modular handle assembly relative to the alignment guide such that the modular handle assembly cannot be translated or rotated relative to the alignment guide.42. The method of claim41, wherein unlocking the modular handle assembly includes moving a first race in a proximal direction against a distal biasing force to permit a first plurality of clamping elements coupled to the first race to move radially outward from a central axis of a cavity of the modular handle assembly and moving a second race in a distal direction against a proximal biasing force to permit a second plurality of clamping elements coupled to the second race radially outward from the central axis of the cavity.43. The method of any of claims41to42, wherein locking the modular handle assembly includes moving the first race in a distal direction to urge the first plurality of clamping elements radially inward toward a central axis of the cavity and moving the second race in a proximal direction to urge the second plurality of clamping elements radially inward toward the central axis of the cavity. | 59,714 |
11859650 | DESCRIPTION OF EMBODIMENTS An embodiment of the present invention is elaborated below with reference to the accompanying drawings. FIG.1is a perspective view illustrating a state where a gear device of an embodiment of the present invention is used,FIG.2is a rear perspective view of the gear device, andFIG.3is a longitudinal sectional view of the gear device taken along the axis direction.FIG.4is an exploded perspective view of the gear device of the embodiment of the present invention. In the following description, the horizontal direction inFIGS.1and3is referred to as axial direction. In addition, the left direction inFIGS.1and3is referred to as one side in the axial direction, and the right direction is referred to as the other side in the axial direction. Unless otherwise noted, the axial direction means the axis direction of each member that makes up the gear device. In addition, the direction orthogonal to the axial direction inFIGS.1and3is referred to as radial direction. Unless otherwise noted, the radial direction means the radial direction of each member that makes up the gear device. The outside in the radial direction means a direction away from center of each member that makes up the gear device in the radial direction. The inside in the radial direction means a direction approaching toward the center of each member that makes up the gear device in the radial direction. In addition, inFIGS.1and3, the direction around the central axis of the gear device that is parallel to the axial direction is referred to as circumferential direction. Unless otherwise noted, the circumferential direction means the circumferential direction of each member that makes up the planetary gear device. Gear device1illustrated inFIGS.1to4is attached to motor2, and makes up actuator10. Motor2includes motor body21and rotation shaft22. Motor2operates under the control of a control part (not illustrated in the drawing), and drives gear device1by rotating rotation shaft22. At the end surface on the other side in the axial direction (the right end surface inFIG.1), motor body21includes support surface211for supporting gear device1. Motor body21includes, at support surface211, a plurality of (two, in the present embodiment) motor side fixation holes23aand23b.Rotation shaft22is a connection shaft connected to gear mechanism (for example, described later planetary gear mechanism)6in gear device1. Fixation holes23aand23bare, for example, motor side engagement parts that engage with gear side engaging parts502aand502bof gear device1when gear device1is attached to motor2. At support surface211, fixation holes23aand23bare provided at even intervals (at 180° intervals) in the circumferential direction. Gear device1is fixed to motor2by engaging fixation holes23aand23bwith protruding gear side engaging parts502aand502bprovided in gear device1illustrated inFIGS.2and3. Gear device1is fixed to motor2by pressing gear side engaging parts502aand502binto motor side fixation hole23(23a,23b). Motor2is a member for supporting gear device1described later. Note that the type of the motor is not limited, and various electric motors known in the related art may be employed. Gear device1is, for example, a planetary gear device. For example, gear device1is attached to motor2, and is used as an actuator of an electric back door of an automobile used for opening and closing the back door of actuator1. While gear device1is described as a planetary gear device in the following description, gear device1may include any gear mechanism as long as gear device1is driven by being connected with rotation shaft22inserted from the outside via a through hole. Gear device1outputs the rotation input from motor2after decelerating it at a predetermined deceleration ratio. Gear device1includes housing4that houses the planetary gear mechanism as gear mechanism6, and housing cover5disposed at an end portion on one end portion side in the axis direction (one end portion in the axial direction) of housing4. Housing4 In the present embodiment, housing4houses gear mechanism6together with housing cover5and achieves the deceleration of multiple stages. In housing4, gear mechanism6decelerates, in two stages, the rotation of rotation shaft22under the drive of the motor2and outputs it from shaft connecting part87. Housing4is a cylindrical member that is open at an end portion on one side in the axial direction where housing cover5is attached. In housing4, annular part46including support cylindrical part47is joined at the end portion on the other side in the axial direction of body cylindrical part45with a cylindrical shape. For example, it is preferable that housing4be made of synthetic resin, and that body cylindrical part45be shaped integrally with annular part46including support cylindrical part47by injection molding. Body cylindrical part45has a cylindrical shape and houses gear mechanism6inside. In body cylindrical part45, engaging protrusion451aand housing engaging hole451bare provided at one end portion, which is the end portion on one side in the axial direction. Engaging protrusion451aextends in the axial direction at plural positions in the circumferential direction of the opening edge of one end portion of body cylindrical part45. When one end portion of body cylindrical part45is fitted on housing cover5from the outside, engaging protrusion451aengages with engaging recess523. A plurality of (four, in the present embodiment) housing engaging holes451bextends in the circumferential direction at one end portion of body cylindrical part45. Housing engaging hole451bis formed in a slit shape extending in the circumferential direction. Housing engaging hole451bengages with engaging claw part531of housing cover5when fitted on connection cylindrical part53of housing cover5from the outside. When engaging protrusion451aand housing engaging hole451bengage with engaging recess523of housing cover5and engaging claw part531of housing cover5, respectively, key protrusion451cengages with cutout part524. In housing4, the movement in the axial direction and the circumferential direction with respect to housing cover5is limited through the engagement of housing engaging hole451band engaging claw part531. In addition, in housing4, the movement in the circumferential direction with respect to connection cylindrical part53is limited through the engagement of engaging protrusion451aand engaging recess523. In addition, in housing4, housing cover5can be assembled to a predetermined position through the engagement key protrusion451cand cutout part524. Body cylindrical part45houses first planetary gear mechanism7and second planetary gear mechanism8in order from one side in the axial direction (the left side inFIG.3) to the other side (the right side inFIG.3). Body cylindrical part45houses second planetary gear mechanism8in the state where output axis connecting part87is protruded from the end portion on the other side (the right side inFIG.3) in the axis direction of body cylindrical part45, to the other side. At a portion facing the outer peripheral surface of first inner gear74described later in the radial direction at the inner peripheral surface of body cylindrical part45, ridge451dthat engages with outer periphery groove part741cof the outer periphery of first inner gear74described later in the circumferential direction extends in the axial direction. A plurality of (for example, four) ridges451dis provided in a manner corresponding to outer periphery groove part741c. Ridge451dmakes point contact or line contact with outer periphery groove part741cin a small gap in the radial direction between the inner peripheral surface of body cylindrical part45and the outer peripheral surface of first inner gear74. In this manner, body cylindrical part45movably supports first inner gear74such that the axis line of first inner gear74is slightly tilted with respect to the central axis of body cylindrical part45(housing4). That is, body cylindrical part45supports first inner gear74in a floating manner. Body cylindrical part45includes second inner gear part4522including teeth extending in the axial direction at the inner peripheral surface on the other side in the axial direction. Second inner gear part4522is a helical gear, and engages with planetary gear82of second planetary gear mechanism8described later. Note that second inner gear part4522may be a spur gear. In addition, a portion on the other side of body cylindrical part45may be interpreted as an inner gear of second planetary gear mechanism8. In addition, the inner gear of second planetary gear mechanism8may be a member provided separately from body cylindrical part45, i.e., housing4. In this case, the second inner gear part provided at the inner peripheral surface of the inner gear provided separately from housing4. Then, this inner gear is fixed (internally fitted) to housing4. This inner gear may be supported by housing4in a floating manner, as with first inner gear74of first planetary gear mechanism7described later. Annular part46has an annular shape, and is connected to the other end portion of body cylindrical part45in the axis direction. More specifically, the outer end portion of annular part46in the radial direction is provided integrally with the end portion on the other side of housing4. Support cylindrical part47has a cylindrical shape contiguous with the center opening of annular part46, and is provided upright along the axial direction on the other side in the axial direction, i.e., the output side. Support cylindrical part47rotatably supports output shaft connecting part87, with its connection port externally exposed. In this manner, the torque output by output shaft connecting part87can be transmitted to the external mechanism by connecting the output shaft, or the output destination member of the rotational force to output shaft connecting part87. Housing4having the above-mentioned configuration is fixed to motor2through housing cover5in the state where it is housed in gear mechanism6. Gear Mechanism6 As illustrated inFIGS.3and4, gear mechanism6is a planetary gear mechanism. Gear mechanism6is housed in housing4, and outputs the rotation transmitted from motor2through shaft connecting part87after decelerating it. Gear mechanism6includes second planetary gear mechanism8and first planetary gear mechanism7disposed along the axis direction. First planetary gear mechanism7includes sun gear71, the plurality of planetary gears72disposed around sun gear71, first carrier73that rotatably supports the plurality of planetary gears72, and first inner gear74. While it suffices that first planetary gear mechanism7includes one or more planetary gears72, it includes three planetary gears72in the present embodiment. Sun gear71is an outer gear with a sun teeth portion formed in the outer peripheral surface, and is connected to rotation shaft22of motor2, which is a connection shaft inserted into gear device1through center opening51. Sun gear71can rotate with the same axis as rotation shaft22through the driving of motor2. Sun gear71includes spiral teeth cut obliquely to the axis of sun gear71, for example. Sun gear71is a so-called helical gear. Planetary gear72is an outer gear with the planetary teeth formed in the outer peripheral surface. The plurality of planetary gears72is disposed at even intervals between sun gear71and first inner gear74, and engages with both sun gear71and first inner gear74. The plurality of planetary gears72, for example, is disposed on the same circle around the axis of first planetary gear mechanism7, and rotatably supported by first carrier73. The planetary teeth include spiral teeth cut obliquely to the shaft of planetary gear72, for example. Planetary gear72is a so-called helical gear. Each planetary gear72rotates around its own central axis (planetary shaft part7344) on the basis of the rotation of sun gear71. In addition, each planetary gear72rotates around sun gear71on the basis of its rotation and the engagement with first inner gear74. The central axis of the rotation of planetary gear72may coincide with the central axis of sun gear71. First carrier73supports planetary gear72such that planetary gear72is rotatable (on its own axis). Additionally, first carrier73rotates on the basis of the rotation of planetary gear72, and transmits the rotation to second planetary gear mechanism8. First carrier73includes carrier body732and carrier cover734that engages with carrier body732. First carrier73is formed in a cylindrical shape with carrier body732and carrier cover734, and houses planetary gear72in housing opening73aformed in its outer peripheral surface. Each planetary gear72is supported such that it is rotatable by planetary shaft part7344directed to the axis direction in housing opening73a.A part of planetary gear72is attached through housing opening73asuch that it protrudes outward in the radial direction. In this manner, the planetary teeth mesh with the inner teeth of first inner gear74. First carrier73houses the sun gear and planetary gear72in a turnable state, and sun gear81of second planetary gear mechanism8that rotates around the same axis as the sun gear is fixed to carrier body732. Carrier cover734is attached from one side in the axial direction with respect to carrier body732, and supports the shaft of planetary gear72. Carrier cover734is disposed next to housing cover5in the axial direction inside housing4, and is slidable on housing cover5. First inner gear74is a cylindrical member disposed at the periphery of planetary gear72, and engages with planetary gear72at the first inner teeth provided in the inner peripheral surface. The first inner teeth includes spiral teeth cut obliquely to the central axis (the central axis common to the central axis of rotation shaft22of motor2) of first inner gear74, and first inner gear74is a helical gear. A plurality (in the present embodiment, three for each of end portions separated in the axial direction) first ridges741aincluding outer periphery groove part741cis provided at the outer peripheral surface of first inner gear74. First ridge741aextends in the circumferential direction. The rotation of first inner gear74with respect to housing4is limited through the engagement of outer periphery groove part741cand ridge451d. In first inner gear74, the end portion of first inner gear74on one side in the axis direction faces housing cover5with a small gap therebetween in the axial direction, in housing4. The movement to one side in the axial direction is limited to a predetermined amount by housing cover5. On the other hand, the end portion of first inner gear74on the other side in the axis direction faces a step in housing4with a predetermined gap therebetween in the axial direction, and the movement of first inner gear74to the other side in the axis direction is limited to a predetermined amount by the step. Second planetary gear mechanism8outputs the rotation transmitted from first planetary gear mechanism7after decelerating it at predetermined deceleration ratio. Second planetary gear mechanism8is provided on the other side in the axial direction (the output side and the right side ofFIG.1) relative to first planetary gear mechanism7. In the housing space of housing4, second planetary gear mechanism8is housed on the other side of body cylindrical part45of housing4in the axis direction. More specifically, it is disposed at a portion corresponding to second inner gear part4522of body cylindrical part45. Note that second planetary gear mechanism8may be omitted. Second planetary gear mechanism8includes sun gear81, planetary gear82, and second carrier83that rotatably supports planetary gear82. While second planetary gear mechanism8includes three planetary gears82, it suffices that second planetary gear mechanism8includes one or more planetary gears82. Sun gear81is an outer gear, and includes the sun teeth portion at the outer peripheral surface. In the present embodiment, the sun teeth portion includes spiral teeth cut obliquely to the central axis of sun gear81, and sun gear81is a so-called helical gear. In the present embodiment, sun gear81is fixed in the state where each axis line coincides with first carrier73of first planetary gear mechanism7. In this manner, sun gear81rotates in the same rotational direction as first carrier73and at the same rotational speed as first carrier73in association with the rotation of first carrier73of first planetary gear mechanism7along with the rotation of first carrier73of first planetary gear mechanism7. Planetary gear82is an outer gear with the planetary teeth formed in the outer peripheral surface. The plurality of planetary gears82is disposed at even intervals between sun gear81and second inner gear part4522, and engages with both sun gear81and second inner gear part4522. The plurality of planetary gears82is disposed on the same circle around the axis of second planetary gear mechanism8, and is supported by planetary shaft86of second carrier83in a rotatable manner. In the present embodiment, the planetary teeth include spiral teeth cut obliquely to the axis of planetary gear82, and planetary gear82of the present embodiment is a so-called helical gear. Each planetary gear82rotates around its own central axis (planetary shaft86) on the basis of the rotation of sun gear81. In addition, each planetary gear82rotates around sun gear81on the basis of its own rotation and the engagement with second inner gear part4522. The central axis of the rotation of planetary gear82may coincide with the central axis of sun gear81. Second carrier83supports planetary gear82such that it is rotatable (on its own axis). Additionally, second carrier83rotates on the basis of the rotation of planetary gear82, and transmits it to the output shaft connected to output shaft connecting part87. Second carrier83includes gear holding part834and second carrier body835that holds output shaft connecting part87. Gear holding part834includes planetary shaft86provided in the axis direction at a ring part disposed at the outer periphery of sun gear81. Planetary gear82is inserted to planetary shaft86such that planetary gear82is rotatably supported. Gear holding part834is joined to second carrier body835. Each planetary gear82is exposed from housing opening83aformed in the outer peripheral surface of second carrier body835. The planetary teeth of planetary gear82engages with the teeth of second inner gear part4522through housing opening83a. Output shaft connecting part87is provided upright on the other side (output side) than second carrier body835, and is formed in a cylindrical shape with a smaller size than second carrier body835. Inside output shaft connecting part87in the radial direction, a tooth in a knurling shape is provided and connected to the output shaft. Housing Cover5 Housing cover5is a member for attaching motor2to gear device1, for example. In addition, housing cover5is provided with assembling mechanism50that allows for detachable assembling of other housing cover5A (seeFIGS.8to9) having the same configuration as that of housing cover5. Housing cover5is disposed at one end portion of housing4in the axis direction. Housing cover5is an annular member, and includes, at the center portion, center opening51for disposing rotation shaft22, which is a connection shaft for planetary gear mechanism (gear). Center opening51is disposed to have the same axis with sun gear71inside housing4. Rotation shaft22of motor2is inserted to center opening51, and rotation shaft22is fixed to sun gear71in housing4. In housing cover5, assembling mechanism50is provided around center opening51of outer surface5aof housing cover5. Housing cover5includes annular outer surface part52, and cylindrical connection cylindrical part53protruded in the axial direction from the outer periphery part of outer surface part52. Outer surface part52and connection cylindrical part53of housing cover5are made of synthetic resin and shaped integrally with each other by injection molding, for example. Outer surface part52is a portion to be fixed to support surface211of motor body21on outer surface5aside in the axial direction. Outer surface part52is disposed at one end portion of housing4in the axis direction, and attached to close the opening at one end portion of housing4in the axis direction in the state where center opening51is continuous. FIG.5is a diagram illustrating an outer surface of a housing cover,FIG.6is a partially enlarged diagram of the housing cover illustrating the engaging part, andFIG.7is a partially enlarged diagram of the housing cover illustrating the engagement part. As illustrated inFIGS.2,3, and5, assembling mechanism50includes, at outer surface part52, engaging part502(502a,502b) and engagement part504(504a,504b) disposed at different positions around center opening51. In engaging part502and engagement part504, mutual engaging part502and mutual engagement part504face each other when outer surface5aof housing cover5and outer surface5aof other housing cover5A of other gear device1A configured in a manner similar to gear device1face each other (seeFIG.8). That is, engaging part502and engagement part504of housing cover5are disposed at positions where engaging part502and engagement part504of other housing cover5A face each other, and engagement part504and engaging part502A of other housing cover5A face each other. For example, each engaging part502and each engagement part504include two gear side engaging parts502aand502band two gear side engagement parts504aand504b,respectively. At outer surface5a,engaging part502and engagement part504are alternately provided with intervals of 90° around the axis. Engaging part502is gear side engaging parts502aand502b,and are axial direction protrusions formed in a shape protruding in the axial direction from outer surface5a,which is the outer surface in the axial direction. A plurality of axis direction recesses5022depressed in the axis direction of gear side engaging parts502aand502bis provided at the outer periphery of gear side engaging parts502aand502bas the axial direction protrusions. With axis direction recess5022, each of gear side engaging parts502aand502bis formed in a cross shape extending in the axial direction. In addition, gear side engaging parts502aand502bare located at positions corresponding to motor side fixation holes23aand23bof motor body21, at outer surface part52. By inserting (for example, press-fitting) and engaging gear side engaging parts502aand502bto fixation holes23aand23b,housing cover5is fixed to motor2in the state where the rotation of housing cover5, i.e., the rotation of gear device1is limited. Note that when gear side engaging parts502aand502bengage with fixation holes23aand23b,the outer peripheral end parts of gear side engaging parts502aand502bmake contact with the inner walls of fixation holes23aand23b. On the other hand, engagement part504includes axial direction recess5042depressed from outer surface5ain the axial direction. Axis direction recess5042of engagement part504is formed in a shape that matches engaging part502. Engagement part504is fit with engaging part502of other housing cover5A at axial direction recess5042, and thus housing cover5including engagement part504and other housing cover5A can be assembled. Engagement part504includes gear side engagement parts504aand504b,which are disposed in a point symmetrical manner about the shaft part. A plurality of axis direction protrusions5044is provided at the inner periphery of axial direction recess5042of each of gear side engagement parts504aand504b.Axis direction protrusion5044protrudes in the axis direction of axial direction recess5042, and can be installed in axis direction recess5022of other housing cover5A. The plurality of axis direction protrusions5044forms a cross-shaped space where axis direction recess5022fit, for example. It is preferable that the vertexes of the plurality of axis direction protrusions5044be formed in shapes such that the interval of vertexes is smaller than that of the base ends, and that they can be press-fit toward the bottom portion of axis direction recess5022. Housing cover5and other housing cover5A are detachably assembled by pressing the apex of axis direction protrusion5044into axis direction recess5022of other housing cover5A. At this time, the apex of axis direction protrusion5044makes pressure contact with axis direction recess5022of other housing cover5A, without making pressure contact with the outer peripheral end part of gear side engaging part502A of other housing cover5A. Thus, the apex of axis direction protrusion5044does not deform the outer peripheral end part of gear side engaging part502A of other housing cover5A, and the fixation of other housing cover5A to the motor is not destabilized. In addition, at the outer periphery portion, outer surface part52includes a plurality of (the present embodiment, five) recessed engaging recesses523and cutout parts524cut in the axial direction. Engaging recess523and cutout part524engage with key protrusion451cand engaging protrusion451aof housing4in the axial direction. In addition, outer surface part52includes sliding part (seeFIGS.3and4)526that slides on one end portion of gear mechanism6, at the other end portion of outer surface part52in the axis direction, i.e., surface5bon housing4side. It is preferable that one of sliding part526and one end portion of gear mechanism6that slides on sliding part526include a cone-shaped part whose diameter varies in the axial direction, and the other include a sliding part that slides on the peripheral surface of the cone-shaped part with the same axis as the axis of the cone-shaped part. Connection cylindrical part53is configured in a cylindrical shape with a plurality of arched wall parts530protruded from the outer periphery of housing cover inner surface5bof outer surface part52, and extending in the circumferential direction. Connection cylindrical part53is provided integrally with outer surface part52, and includes a plurality of (four, in the present embodiment) engaging claw parts531that engages with one end portion of housing4in the axis direction at the outer peripheral surface of predetermined arched wall part530. Connection cylindrical part53is connected to housing4through engaging claw part531. Effect of Gear Device1 In gear device1having the above-mentioned configuration, engaging part502and engagement part504are provided around center opening51at outer surface5a,which is an end surface provided with center opening51where rotation shaft22is inserted. That is, gear device1includes engaging part502and engagement part504, which are assembling mechanism50that can detachably assemble other housing cover5A with the same configuration as housing cover5, to housing cover5including center opening51. When carrying gear device1, first, their housing covers5and5A are disposed in an opposite manner by using another gear device1A, as illustrated inFIGS.8and9. Then, in their housing covers5and5A, one engaging part502is fit to the other engagement part504, and one engagement part504is fit to the other engaging part502. This fitting is achieved through press-fitting in the axial direction, and therefore they are detachable. As described above, by fitting engaging part502of one of housing covers5and5A to engagement part504of the other of housing covers5and5A, and fitting one engagement part504to the other engaging part502, center openings51of gear devices1and1A are set to a closed state. In this manner, it can be used by attaching it to motor2while preventing intrusion and mixing of foreign matters from their center openings51. In addition, a separate member such as a cap for sealing center opening51during conveyance that becomes unnecessary thereafter is not used, and thus unnecessary members are not produced after the conveyance. Note that in the present embodiment, engaging part502and engagement part504as assembling mechanism50are fit through press-fitting in the axial direction, but any assembling structure may be employed as long as their center openings are sealed using a gear device with a similar configuration. For example, it is possible to employ a configuration in which an engaging part and an engagement part with shapes that can be fit each other in the circumferential direction are fit each other by fitting the housing cover of the gear device and the housing cover of the other gear device each other in the axial direction and rotating them in the circumferential direction. The above is a description of an embodiment of the present invention. The embodiments disclosed here should be considered illustrative in all respects and not restrictive. The scope of the invention is indicated by the claims rather than the description given above, and it is intended that all changes within the meaning and scope of the claims be included. In other words, the above description of the configuration of the device and the shape of each part is an example, and it is clear that various changes and additions to these examples are possible within the scope of the present invention. INDUSTRIAL APPLICABILITY The gear device according to the embodiment of the present invention provides an effect of achieving safe conveyance while preventing intrusion and mixture of foreign matters and preventing generation of unnecessary material after the conveyance, and is useful for gear devices that are assembled to the driving part on the job site. REFERENCE SIGNS LIST 1,1aGear device2Motor4Housing5,5aHousing cover5aOuter surface5bSurface6Gear mechanism7First planetary gear mechanism8Second planetary gear mechanism10Actuator21Motor body22Rotation shaft23a,23bFixation hole45Body cylindrical part46Annular part47Support cylindrical part50Assembling mechanism51Center opening52Outer surface part53Connection cylindrical part71,81Sun gear72,82Planetary gear73First carrier73a,83aHousing opening74First inner gear83Second carrier86Planetary shaft87Output shaft connecting part211Support surface451aEngaging protrusion451bHousing engaging hole451cKey protrusion451dRidge502,502aEngaging part502a,502bGear side engaging part (axial direction protrusion)504Engagement part504a,504bGear side engagement part523Engaging recess524Cutout part526Sliding part530Arched wall part531Engaging claw part732Carrier body734Carrier cover741aFirst ridge741cOuter periphery groove part834Gear holding part835Second carrier body4522Second inner gear part5022Axis direction recess5042Axial direction recess5044Axis direction protrusion7344Planetary shaft part | 30,725 |
11859651 | DETAILED DESCRIPTION OF A PREFERRED EMBODIMENT OF THE INVENTION The present invention generally comprises a method and apparatus for locking a pair of opposing components that are joined together in end-to-end configuration using threaded connection(s); said locking system of the present invention prevents said members from inadvertently unscrewing, decoupling, loosening, disconnecting and/or unintentionally detaching from each other. By way of illustration, but not limitation, downhole electric line tools generally comprise a plurality of substantially cylindrical members that are commonly joined together in end-to-end relationship using threaded connections. Although the present invention is described herein as being employed in connection with downhole electric line tools used in subterranean oil and gas wells, it is to be understood that such downhole electric line tools are just one illustrative example of devices or tools that can beneficially employ the locking system of the present invention. As such, although described herein in connection with said downhole electric line tools, it is to be observed that the locking system of the present invention can also be beneficially used in connection with other applications. FIG.1depicts a front view of a lock ring10of the present invention. In a preferred embodiment, said lock ring10comprises a substantially circular central ring body member11forming a “doughnut” configuration and defining a center hole12. At least one spacer stand-off member13is disposed within said central hole12and is oriented radially inward from the inner surface11aof said central ring body member11. In the embodiment depicted inFIG.1, three (3) stand-off members13are disposed equidistantly around the circumference of said inner surface11aat approximately 120-degrees separation between each of said stand-off members13; however, it is to be observed that the number and spacing of said stand-off members13depicted inFIG.1are illustrative only, and said stand-off members13can number more or less than 3, and can be positioned relative to ring body member11differently than the depiction shown inFIG.1. Said at least one spacer stand-off member13ensures that said central ring body member11is beneficially positioned at a desired distance relative to one or both of said joined tool members as more fully described herein. Still referring toFIG.1, a plurality of external locking tabs14extend radially outward from said central ring body member11. Said plurality of external locking tabs14are generally disposed around the outer circumference of said central ring member in spaced relationship along outer surface11bof said ring body member11. The number and spacing of said external locking tabs14depicted inFIG.1are also illustrative only, and the actual number and spacing of said locking tabs14can be altered without departing from the scope of the present invention. FIG.2depicts a side view of a lock ring10of the present invention. In a preferred embodiment, said lock ring10comprises central ring body member11having a substantially planar or flat shape when viewed from the side. As depicted inFIG.2, a plurality of locking tabs14have been selectively bent or intentionally deformed so that said locking tabs14aare at least partially oriented out of planar alignment with said central ring body member11. Put another way, said locking tabs14can be selectively bent so that at least one of said locking tabs14can be re-positioned out of planar alignment with central ring body member11. In the embodiment depicted inFIG.2, said locking tabs14aare intentionally bent to until they are oriented in approximately a 90-degree angle relative planar central body member11. FIG.3depicts a side perspective view of a lock ring10of the present invention. In a preferred embodiment, said lock ring10comprises central ring body member11having a substantially planar or flat shape, as well as a center hole12defining inner surface11a. As depicted inFIG.3, a plurality of spacer stand-off members13is disposed within said central hole12in spaced relationship around said inner surface11a; said spacer stand-off members13are oriented radially inward from inner surface11aof said central ring body member11. A plurality of external locking tabs14extend radially outward in spaced relationship from outer surface11bof said central ring body member11. Referring toFIGS.2and3, it is to be understood that said external locking tabs14can be selectively bent or intentionally deformed so that they are, at least partially, out of planar alignment with said central ring body member11. In a preferred embodiment, at least one of said locking tabs14acan be repositioned at a right angle, or an acute angle, relative to central ring body member11. Nonetheless, in the configuration depicted inFIGS.2and3, the particular locking tabs14athat are bent/deformed are illustrative only and are not in any particular pattern. Said locking tabs can be bent or deformed as desired by hand, or using common or readily available tools (such as pliers), but without requiring specialized tools. FIG.4depicts an overhead perspective and partially exploded view of a locking system of the present invention, whileFIG.5depicts a bottom perspective and partially exploded view of said locking system. Substantially cylindrical first member100and substantially cylindrical second member200are disposed in end-to-end relationship, while lock ring10is positioned between said first member100and second member200. For illustration purposes, said members100and200can represent components of a downhole electric line tool; however, it is to be understood that the present invention is not limited solely to use with electric line tools or similar applications. First member100generally comprises body member110and male or “pin” threaded connection member120having external threads and defining shoulder surface140(best viewed inFIG.5). Second member200generally comprises body member210defining shoulder surface240, and female or “box” connection member220having internal threads. Referring toFIG.4, a plurality of notches230are disposed in spaced relationship around said shoulder surface240of second member200. Referring toFIG.5, a plurality of notches130are disposed in spaced relationship around shoulder surface140of first member100. The number and spacing of notches230and130depicted in the figures are illustrative only; the actual number and spacing of said notches230and130can be varied. When joined, threaded connection member120of first member100is received within female threaded connection member220of second member200. Application of torque forces causes external threads of threaded connection member120to engage with (that is, “screw into”) internal threads of threaded connection member220. In this configuration, lock ring10is disposed between said first member100and second member200. Still referring toFIGS.4and5, lock ring10comprises central ring body member11having a substantially planar or flat shape, and defining a center hole12. At least one spacer stand-off member13is disposed within said central hole12and is oriented radially inward from the inner surface11aof said central ring body member11. It is to be observed that threaded connection member120of first member100can be received within said central hole12of lock ring10. Said at least one spacer stand-off member13disposed around inner surface11bof said lock ring10ensures that said central ring body member11remains positioned a desired radial distance away from threaded connection member120of first member100. A plurality of external locking tabs14extend radially outward from said central ring body member11of lock ring10and can be selectively bent or deformed so that at least one of said locking tabs14aare at least partially disposed at an acute or right angle relative to central ring body member11. FIG.6depicts a detailed overhead perspective view of a locking system of the present invention, whileFIG.7depicts a detailed bottom perspective view of said locking system. First member100generally comprises body member110and male or “pin” threaded connection member120having external threads. Second member200generally comprises body member210and female or “box” connection member220having internal threads. In the configurations depicted inFIGS.6and7, it is to be observed that male or “pin” external threads120of first member100are being inserted through hole12of lock ring10and into female or “box” connection member220of second member200having internal threads. Referring toFIG.6, body member210of second member200defines shoulder surface240. A plurality of notches230are disposed in spaced relationship around said shoulder surface240. Referring toFIG.7, body member110of first member100defines shoulder surface140. A plurality of notches130are disposed in spaced relationship around said shoulder surface140. Said first member100and second member200can be joined and connected to each other in end-to-end relationship so that shoulder surfaces140and240oppose each other, and are in close proximity to each other. Still referring toFIGS.6and7, lock ring10is disposed between said first member100and second member200. At least one spacer stand-off member13is disposed radially inward from said central ring member11. Said at least one spacer stand-off member13ensures that said central ring member11is positioned a desired radial distance away from external threads120of first member100when said threads120are received within hole12of locking ring10. A plurality of locking tabs14extend radially outward from said central ring member11; said locking tabs14are disposed around the circumference of said central ring member11in spaced relationship. In a preferred embodiment, said locking tabs14are attached to central ring member11in a substantially co-planar orientation, but can be selectively bent so that at least a portion of said locking tabs14aare oriented out of planar alignment with said central ring member11. Put another way, said locking tabs14acan be selectively bent or partially repositioned, and can be bent or repositioned by hand and/or without the use of specialized tools. FIG.8depicts an overhead perspective view of an assembled locking system of the present invention, whileFIG.9depicts a detailed perspective view of the assembled locking system depicted inFIG.8. Referring toFIG.8, body section110of first member100, and body section210of second member200, are joined to each other in end-to-end relationship so that shoulder surfaces140and240oppose each other. Lock ring10is disposed or “sandwiched” between said shoulder surface140of first member100and shoulder surface240of second member200. Referring toFIG.9, a portion of at least one locking tab14aof lock ring10can be selectively bent or otherwise displaced into at least one notch230of second member200. In this configuration, said at least one locking tab14ais received between side walls231formed by notch230; said locking tab14acooperates with said side walls231to prevent side-to-side movement and rotation of lock ring10relative to shoulder240and second member200(such as around the longitudinal axis of said second member200). Similarly, a portion of at least one locking tab14aof lock ring10can be selectively bent or otherwise displaced into at least one notch130of first member100. In this configuration, said at least one locking tab14ais received between side walls131formed by notch130; said locking tab14acooperates with said side walls131to prevent side-to-side movement and rotation of lock ring10relative to shoulder140and first member100(such as around the longitudinal axis of said first member100). In this configuration, lock ring10will not rotate relative to body section110of first member100. Similarly, lock ring10will not rotate relative to body section210of second member200. In this manner, lock ring10effectively acts as an intermediate linkage member disposed between first member100and second member200that interlocks said components and effectively prevents unwanted rotation of said first member100relative to said second member200, and vice versa. As such, the lock ring of the present invention interlocks and prevents relative rotation between said first and second members. It is to be observed that first member100and second member200can have the same number of notches (130and230, respectively). However, under this scenario, it is possible that notches130and230may become aligned with each other when first member100and second member200are threadedly connected. When this occurs, it can negatively affect connection of said first member100to said second member200, and use of lock ring10, particularly when said connection occurs at a wellsite or other remote location. Therefore, in a preferred embodiment, said first member100has a different number of notches130than the number of notches230in second member200. When configured in this manner, at least one of said notches is effectively ensured to be out of direct alignment with an opposing notch. Additionally, it is possible to “pre-bend” at least one locking tab14aof lock ring10to fit into notches in one of said members (such as, for example, notches130of first member100). By way of illustration, but not limitation, lock ring10can be installed on said first member100and said pre-bent locking tab(s)14acan be received within notch(es)130of said first member100; said pre-bent locking tab(s)14acooperate with notch(es)130to prevent rotation or spinning of lock ring10when second member200is threadedly connected to said first member100. Thereafter, following threaded connection of first member100to second member200, additional locking tab(s)14acan be bent or deformed to be received within notch(es)230of second member200. It is to be understood that locking tab(s)14acan be bent or deformed into the desired configuration without the use of specialized tools; said tabs can be bent and/or deformed (including on a well site or other remote location) by hand or by using conventional pliers or other commonly available tools. In the case of downhole electric line tools, said tools can be exposed to contact or jarring with the surrounding wellbore, casing, tubing and/or other objects, particularly while said tools are being conveyed in and/or out of the wellbore. Such contact can frequently result in the application of torque or other forces to the components of said tools, thereby causing said components to inadvertently unscrew, decouple, loosen and/or otherwise disconnect from each other. The locking system of the present invention can secure said components together without requiring use of set screws or other conventional locking means that can significantly damage said components and/or require substantial alterations to at least one of said components. Further, the locking system of the present invention is inexpensive and efficient to manufacture and deploy. The above-described invention has a number of particular features that should preferably be employed in combination, although each is useful separately without departure from the scope of the invention. While the preferred embodiment of the present invention is shown and described herein, it will be understood that the invention may be embodied otherwise than herein specifically illustrated or described, and that certain changes in form and arrangement of parts and the specific manner of practicing the invention may be made within the underlying idea or principles of the invention. | 15,588 |
11859652 | DETAILED DESCRIPTION Improved bolts, bolt and nut fasteners, and bolted joints are disclosed. I Turning now to the drawings, like reference characters indicating corresponding elements throughout the several views,FIGS.1and2illustrate fastener50constructed and arranged according to the invention. Fastener50is useful in forming bolted joints and includes bolt52and nut54configured to be repeatedly and quickly assembled and disassembled. All diameters referenced throughout this specification related to fastener50are constant. InFIGS.1,2, and3, bolt52includes longitudinally straight cylindrical shank60extending from proximal end62configured with enlarged head100to distal end64, and external threads70and80on either side of unthreaded body90, including a diameter92inFIG.3. Head100has wrench flats102, six in this example, for bolt-turn purposes, and underside104. Shank60extends outwardly to distal end64from proximal end62affixed centrally to underside104of head100. Radial bearing surface or radius104A of underside232radiates outwardly from body90. InFIGS.1-3, external thread70near head100twists in a left-hand direction and is exemplary of a standard left-handed external thread. InFIG.3, external thread70includes thread length71extending from closely adjacent to proximal end62and radial bearing surface104to runout72on a proximal side of body70, minor diameter73, major diameter74, and pitch75, the distance between adjacent peaks or crests of the thread. Minor diameter73occurs at the roots of external thread70, and major diameter74occurs at the crests of external thread70. InFIGS.1-3, external thread80near distal end64twists in a right-hand direction opposite to the left-hand direction of external thread70and is exemplary of a standard right-handed external thread. InFIG.3, external thread80includes thread length81extending from distal end64to runout82on a distal side of body70, minor diameter83, major diameter84, and pitch85, the distance between adjacent peaks or crests of the thread. Minor diameter83occurs at the roots of external thread80. Major diameter84occurs at the crests of external thread80. External threads70and80twist in opposite directions, as described. Accordingly, external threads70and80are counter-threads configured to threadedly receive counter-rotating internally-threaded elements. External thread70is the proximal left-handed external thread of bolt52near or otherwise proximate to radial bearing surface104of head100. External thread80opposite to external thread70is the distal right-handed external thread proximate to distal end64. Thread length81of external thread80is greater than thread length71of external thread70and less than grip length94of body90extending from runout72to runout82. Grip length94is the length of the unthreaded portion of shank60, namely, body90. Grip length94is the free length of bolt52that is stretched under tension. Pitch75is slightly larger than pitch85, and this can be reversed in an alternate embodiment. Pitches75and85can be the same in a specific embodiment. Minor diameter73of external thread70is larger than diameter92of body90and major diameter84of external thread80. Accordingly, external thread70is the major external thread of bolt52, and external thread80is the minor external thread of bolt52. InFIGS.1and2, nut54and is an annular block configured with a threaded hole111, including internal thread112. Threaded hole111extends through nut54from an inner side54A of nut54to an outer side54B of nut54. Inner and outer sides54A and54B of nut54are radial bearing surfaces. Nut54has a thickness from inner side54A to outer side54B. Internal thread112runs along the inside of nut54between the opposed inner and outer sides54A and54B and twists in the same left-hand direction as external thread70. InFIG.6, internal thread112includes minor diameter113, major diameter114, and pitch115, the distance between adjacent peaks or crests of the thread. Minor diameter113occurs at the crests of internal thread112, and major diameter114occurs at the roots of internal thread112. Pitches75and115are identical. Minor diameter113of internal thread112is greater than diameter92of body90and major diameter84of external thread80. Minor and major diameters113and114of internal thread112correspond to the respective minor and major diameters73and74of external thread70. External thread70and internal thread112correspond by being the same size and having identical pitches. Since minor diameter113of internal thread112is greater than major diameter84of external thread80and diameter92of body90, threaded hole111is configured to receive therethrough in a direction from outer side54B of body54to inner side54A of body54distal end64shank60and sequentially pass over external thread80and body90to runout72of external thread70without interference from external thread80. Since pitch115of internal thread112and pitch75of external thread70are the same, minor and major diameters113and114of internal thread112correspond to the respective minor and major diameters73and74of external thread70, internal thread112twists in the same left-hand direction as external thread70, and internal and external threads112and70are correspondingly sized, internal thread112corresponds to and is configured to thread rotationally over and on external thread70from runout72in the direction of arrow B inFIGS.4-6when rotated in the direction of arrow A and off external thread70from runout72in the direction of arrow D when rotated in the direction of arrow C. Accordingly, internal thread112corresponds to and is configured to thread over and on external thread70but not on external thread80. Nut54advances toward underside104of head100and away from distal end64in the direction of arrow B inFIGS.4-6, when nut is54is rotated over and on external thread70in a counterclockwise direction of arrow A inFIGS.4and5when seen from the point of view facing distal end64on the central longitudinal axis of shank60. Nut54is suitably sized to extend entirely over external thread70from outer side54B of nut54tightened directly against underside104of head100to inner side54A of nut54proximate to body90outboard of external thread70in the assembled fastener50, when nut54is tightened directly against underside104of head100by rotating it in the direction of arrow A tightly against underside104of head100. Nut54withdraws from underside104of head100and away from distal end64in the direction of arrow D inFIGS.4-6when nut54is rotated on external thread70in a clockwise direction of arrow C inFIGS.4and5when seen from the point of view facing distal end64on the central longitudinal axis of shank60. Once nut54is free from external thread70, the user may withdraw nut54from bolt52in the direction of arrow D to separate nut54from bolt52. The described process for assembling and disassembling fastener50is repeatable is needed. InFIGS.1,2,4, and5, nut54has parallel and circumferentially spaced-apart wrench grooves118for nut-turn purposes. Repeated reference to the described directions of arrows A, B, C, and D is made throughout this specification with the various embodiments disclosed herein and used in the various figures for reference purposes. The assembled fastener50inFIGS.4-6is useful in forming bolted joints, such as bolted joint120inFIG.7.FIG.7illustrates two members122and124secured together by assembled fastener50. Members122and124, metal plates in this example, have registered through bores126and128, respectively. Bore128is tapped with internal thread130, and is exemplary of a tapped or internally threaded bore128. Thread130is a right-hand thread and corresponds to external thread80, enabling it to thread conventionally on external thread80when bolt52is turned in the direction of arrow A. A user forms bolted joint120with fastener50to secure members122and124together by inserting bolt60distal end64first into and through bore126to bore128. He threads internal thread130over and on external thread80and advances bolt52in the direction of arrow D by rotating bolt52in the direction of arrow A until inner side54A of nut54tightens against member122. Bolt length94, the free length of bolt52that is stretched under tension, extends through bore126of member122to external thread80threaded to internally threaded bore128. He alternately rotates nut54and bolt52in the direction of arrow A while holding the other one stationary. This alternately tightens outer side54B of nut54against underside104of head100and inner side54A of nut54against member122until the desired tension is achieved, tightly clamping member122between member124and inner side54A of nut54and tightly clamping nut54between underside104of head100and member122. Since rotation of bolt52in the direction of arrow A urges bolt52in the direction of arrow D and rotation of nut54relative to bolt52in the same direction of arrow A urges nut54in the opposite direction of arrow B, nut54with its outer side54B tightened directly against underside104of head100and its inner side54A tightened directly against member122disables bolt52from loosening by rotating in the direction of arrow C. Accordingly, nut54serves as a locknut counter-rotated relative to bolt52aggressively disabling bolt52from loosening by rotating in the direction of arrow C. Fastener50securing bolted joint120is surprisingly strong and aggressive and resistant to axial failure, shear failure, and loosening in response to vibrational and prevailing torsional forces. Nut54additionally serves to distribute the load of fastener50. The user need only reverse this operation to release bolted joint120and withdraw fastener50. The skilled artisan will readily appreciate that handedness of the threads described in conjunction with fastener50can be reversed in alternate embodiments. The assembled fastener50inFIGS.4-6is also useful with a nut140and washer148inFIG.8to form an alternate embodiment of a fastener50′ useful in forming bolted joint160inFIG.10, including members162and164secured together by fastener50′. Fastener50′ is the assembly of bolt52, nut54, nut140, and washer148. Members162and164inFIG.10, metal plates in this example, have registered through bores166and168, respectively.FIG.9is a section view along9-9of fastener50′ ofFIG.8illustrating the assembly of bolt52, nut54, nut140, and washer148. The assembly of bolt52and nut54inFIGS.9and10incorporate the reference characters as fastener50inFIGS.6and7. Nut140is an annular block configured with a threaded hole141, including internal thread142. Threaded hole141extends through nut140from an inner side140A of nut140to an outer side140B of nut140. Inner and outer sides140A and140B of nut140are radial bearing surfaces. Internal thread142runs along the inside of nut140between the opposed inner and outer sides140A and140B and twists in the same right-hand direction as external thread80. Internal thread142includes minor diameter143, major diameter144, and pitch145, the distance between adjacent peaks or crests of the thread. Minor diameter143occurs at the crests of internal thread142, and major diameter144occurs at the roots of internal thread142. Pitch145is identical to pitch85. Minor and major diameters143and144of internal thread142correspond to the respective minor and major diameters83and84of external thread80. Since pitch145of internal thread142and pitch85of external thread80are the same, minor and major diameters143and114of internal thread142correspond to the respective minor and major diameters83and84of external thread80, internal thread142twists in the same right-hand direction as external thread80, and internal and external threads142and80are correspondingly sized, internal thread142corresponds to and is configured to thread rotationally over and on external thread80from distal end64and off external thread80from distal end64. External thread80and internal thread142correspond by being the same size and having identical pitches. InFIG.10, a user forms bolted joint160with fastener to secure members162and164together by inserting bolt60distal end64first into and through bore166to bore168to bring inner side54A of nut54against member162on one side of the bolted joint160and extend external thread80outwardly from bore168to distal end64on the opposite side of the bolted joint160. The user locates washer148over external thread80. He threads internal thread142on external thread80by inserting distal end64into threaded hole141and rotating nut140in the direction of arrow C. This advances nut140in the direction of arrow B until nut140is tightened directly against washer148initially clamped between outer side140B of nut54and member164. Bolt length94extends through bores166and168to external thread80, extending outwardly from bore166to distal end64. He either holds nut140from rotating or urges rotation of nut140in the direction of arrow C and at the same time alternately rotates nut54and bolt52in the direction of arrow A while holding the other one stationary as in joint120. As described above, this alternately tightens outer side54B of nut54against underside104of head100and inner side54A of nut54against member122until the desired tension is achieved, tightly clamping members162and164between washer148and inner side54A of nut54and tightly clamping nut54between underside104of head100and member162. Nut54serves as a locknut counter-rotated relative to bolt52aggressively disabling bolt52from loosening by rotating in the direction of arrow C in bolted joint160as in bolted joint120. Fastener50′ securing bolted joint160is surprisingly strong and aggressive and resistant to axial failure, shear failure, and loosening in response to vibrational and prevailing torsional forces. Nut54serves to distribute the load of fastener50′ as described above in bolted joint120. The user need only reverse this operation to release bolted joint160and withdraw fastener50′. The skilled artisan will readily appreciate that handedness of the threads described in conjunction with fastener50′ can be reversed in alternate embodiments. II FIGS.11-13illustrate another embodiment of a fastener180constructed and arranged according to the invention. Fastener180is useful in forming bolted joints and includes bolt182and nut184is configured to be repeatedly and quickly assembled and disassembled. All diameters referenced throughout this specification related to fastener180are constant. Bolt182includes longitudinally straight cylindrical shank190extending from proximal end192configured with enlarged head230to distal end194. External threads200and210are on either side of unthreaded body220, including a diameter222inFIG.13. Head230, an enlarged cylindrical body, includes underside232and opposed outer side234. Head230is circumferentially enlarged relative to shank190and is externally threaded with thread200extending between underside232and outer side234. Shank190extends outwardly to distal end194from proximal end192affixed centrally to underside232of head230. Radial bearing surface or radius232A of underside232radiates outwardly from body220to external thread200. InFIG.12, blind keyway236for bolt-turn purposes extends into head230centrally from outer side234. All diameters referenced related to fastener180are constant. InFIGS.11-13, external thread200near proximal extremity192twists in a left-hand direction and is exemplary of a standard left-handed external thread. InFIG.13, external thread200includes thread length201extending between underside232adjacent to proximal end192and outer side234, minor diameter203, major diameter204, and pitch205, the distance between adjacent peaks or crests of the thread. Minor diameter203occurs at the roots of external thread200, and major diameter204occurs at the crests of external thread200. External thread210near distal end194twists in a right-hand direction opposite to the left-hand direction of external thread200and is exemplary of a standard right-handed external thread. InFIG.13, external thread200includes thread length211extending from distal end194to runout212, minor diameter213, major diameter214, and pitch215, the distance between adjacent peaks or crests of the thread. Minor diameter213occurs at the roots of external thread210. Major diameter214occurs at the crests of external thread200. External threads200and210twist in opposite directions, as described. Accordingly, external threads200and210are counter-threads configured to threadedly receive counter-rotating internally-threaded elements. External thread200is the proximal left-handed external thread of bolt182proximate to proximal end192. External thread210opposite to external thread200is the distal right-handed external thread of bolt182proximate to distal end194. Thread length211of external thread210is greater than thread length201of external thread200and less than grip length224of body220extending from underside232of externally-threaded head230to runout212. Grip length224, the length of the unthreaded portion of shank190, namely, body220, is the free length of bolt182that is stretched under tension. Pitches205and215are identical. Minor diameter203of external thread200is larger than diameter222of body190and major diameter214of external thread210. Accordingly, external thread200is the major external thread of bolt182, and external thread210is the minor external thread of bolt182. External threads200and210are the same size and have identical pitches. InFIGS.11and12, nut184is an annular block configured with a threaded hole240, including internal thread242. Threaded hole240extends through nut184from an inner side184A of nut184to an outer side184B of nut184. Inner and outer sides184A and184B of nut184are radial bearing surfaces. Nut184has a thickness from inner side184A to outer side184B. Internal thread142runs along the inside of nut184between the opposed inner and outer sides184A and184B and twists in the same left-hand direction as external thread200. InFIG.16, internal thread242includes minor diameter243, major diameter244, and pitch245, the distance between adjacent peaks or crests of the thread. Minor diameter243occurs at the crests of internal thread242, and major diameter244occurs at the roots of internal thread242. Pitches205,215, and245are identical. Minor diameter243of internal thread242is greater than diameter222of body220and major diameter214of external thread210. Minor and major diameters243and244of internal thread242correspond to the respective minor and major diameters203and204of external thread200. External thread200and internal thread242correspond by being the same size and having identical pitches. Further, external threads200and210and internal thread242are the same size and have identical pitches. Since pitch245of internal thread242and pitch205of external thread200are the same, minor and major diameters243and244of internal thread242correspond to the respective minor and major diameters203and204of external thread200, internal thread242twists in the same left-hand direction as external thread200, and internal and external threads242and200are correspondingly sized, internal thread242corresponds to and is configured to thread rotationally over and on external thread200and off external thread200from outer side234of head230. Accordingly, internal thread242corresponds to and is configured to thread over and on external thread200but not on external thread210. A user assembles fastener180inFIGS.14,15, and16by inserting bolt182outer side234of head230first into threaded hole241from inner outer side184A. He advances nut184in the direction of arrow D toward underside232of head230by rotating nut184in the direction of arrow A over external thread200. Nut184is suitably sized to extend entirely over external thread200from inner side184A of nut184proximate to underside232of head230to outer side184B of nut184proximate to outer side234of head230, when internal thread242is completely threaded over external thread200in the assembled fastener180inFIGS.14-16. A user withdraws nut184from head230to disassemble fastener180by reversing this operation. The described process for assembling and disassembling fastener180is repeatable as needed. InFIGS.11-15, nut184has parallel and circumferentially spaced-apart wrench grooves248for nut-turn purposes. The assembled fastener180inFIGS.14-16is useful in forming bolted joint250inFIG.17.FIG.17illustrates two members252and254secured together by assembled fastener180. Members252and254, metal plates in this example, have registered through bores256and258, respectively. Bore258of member254is tapped with internal thread260and is exemplary of a tapped or internally threaded bore258. Thread130corresponds to external thread80, enabling it to thread conventionally on external thread80. A user forms bolted joint250with fastener180inFIG.17to secure members252and254together by inserting bolt190distal end194first into and through bore256to bore258. He threads internal thread260on external thread210to advance bolt182in the direction of arrow D by rotating bolt182in the direction of arrow A until radial bearing surface232A of underside232of head230and inner side184A of nut184initially tighten against member252. Bolt length224extends through bore256of member252to external thread210threaded to internally threaded bore258. He alternately rotates nut184and bolt182in the direction of arrow A while holding the other one stationary. This alternately tightens outer side184B of nut54and radial bearing surface232A of underside232of head230against member252until the desired tension is achieved, clamping member252between member254and both inner side184A of nut54and radial bearing surface232A of head232. Since rotation of bolt182in the direction of arrow A urges bolt52in the direction of arrow D and rotation of nut184relative to bolt182in the same direction of arrow A urges nut184in the opposite direction of arrow B, nut184serves as a locknut counter-rotated relative to head230of bolt184aggressively disabling bolt182from loosening by rotating in the direction of arrow C. Radial bearing surface232A of head230additionally serves to distribute the load of fastener180without the need for a washer, although one can use a separate washer between radial bearing surface232A and member252if desired. Since external threads200and210and internal thread242are identically sized and have the same pitches, the threaded attachments are strong and resistant to stripping. Fastener180securing bolted joint250is surprisingly strong and aggressive and resistant to axial failure, shear failure, and loosening in response to vibrational and prevailing torsional forces. The user need only reverse this operation to release bolted joint250and withdraw fastener180. Like fastener50′, the assembled fastener180inFIGS.14-16is also useful with a nut and washer to form an alternate embodiment of a fastener useful in forming a bolted joint. The skilled artisan will readily appreciate that handedness of the threads described in conjunction with fastener180can be reversed in alternate embodiments. Keyway236inFIGS.12and15-17is multifaced and exemplary of an Allen keyway configured to accept an Allen key of a tool used to drive bolt182rotationally. In an alternate embodiment of a fastener180′ inFIG.18that, in common with fastener180, shares bolt182and nut184, bolt182is configured with a key265for bolt-turn purposes. Key265is multifaced and exemplary of a standard Allen key configured to accept a standard Allen keyway of a tool used to drive bolt182rotationally. InFIG.18, key265for bolt-turn purposes extends outwardly from head230centrally from outer side234. FIG.19illustrates yet another embodiment of a fastener300constructed and arranged according to the invention. Fastener300is useful in forming bolted joints and includes bolt302, anchor nut304, and locknut306configured to be repeatedly and quickly assembled and disassembled. Anchor nut304and locknut306are configured to be repeatedly assembled inFIGS.22and23to form an anchor nut assembly345and disassembled inFIGS.19and21independently from bolt302. All diameters referenced throughout this specification related to fastener300are constant. InFIGS.19and20, bolt302includes longitudinally straight cylindrical shank310extending from proximal end312configured with enlarged lug or head340to distal end314, external thread320and unthreaded body330, including a diameter332inFIG.20. Shank60extends outwardly to distal end314from proximal end312affixed centrally to head240configured to be anchored in a counterbore. External thread320twists in a right-hand direction and is exemplary of a standard right-handed external thread. InFIG.20, external thread320includes thread length321extending from distal end314to runout322on a distal side of body330, minor diameter323, major diameter324, and pitch325, the distance between adjacent peaks or crests of the thread. Minor diameter323occurs at the roots of external thread320. Major diameter324occurs at the crests of external thread320. Thread length321of external thread320is less than grip length334of body330extending from head340to runout322. Grip length334, the length of the unthreaded portion of shank310, namely, body330, is the free length of bolt302that is stretched under tension. InFIGS.19and21, anchor nut304is an annular block or body including open inner end350, open outer end352, flange354, head356, external thread360, and hole370configured with internal thread372. Hole370extends through anchor nut304from open inner end350to open outer end352. Head356has wrench flats358, six in this example, for nut-turn purposes, and extends from open inner end350to the inner or proximal side of flange354. Flange354extends from its inner side at head356to its outer or distal side, including radial bearing surface354A. Radial bearing surface354A faces external thread360. External thread360extends between radial bearing surface354A and outer end352, twists in a left-hand direction opposite to external thread320of bolt302, and is exemplary of a standard left-handed external thread. Head356and flange354together form an integrated flanged head of anchor nut304. InFIG.21, left-handed external thread360includes thread length361extending along the length of anchor nut304between radial bearing surface354A and outer end352, minor diameter363, major diameter364, and pitch365, the distance between adjacent peaks or crests of the thread. Minor diameter363occurs at the roots of external thread360, and major diameter364occurs at the crests of external thread360. External threads320and360twist in opposite directions, as described. Accordingly, external threads320and360are counter-threads configured to threadedly receive counter-rotating internally-threaded elements. Hole370extending through anchor nut304from open inner end350to open outer end352inFIG.21has an internally threaded part370A and coaxial unthreaded part370B. Internally threaded part370A includes internal thread372extending from open inner end50to runout374at an intermediate location of hole370between open inner end350and open outer end352. Unthreaded part extends from runout374to open outer end352. Unthreaded part370B has internal diameter376greater than major diameter324of external thread320and diameter332of body330inFIG.20. InFIG.21, internal thread372runs along the inside of anchor nut304between open inner end350and runout374and twists in the same right-hand direction as external thread320of bolt302opposite to the left-hand direction of external thread360. Internal thread372includes minor diameter383, major diameter384, and pitch385, the distance between adjacent peaks or crests of the thread. Minor diameter383occurs at the crests of internal thread372, and major diameter384occurs at the roots of internal thread372. Pitches325,365, and385are identical. Minor and major diameters383and384of internal thread372correspond to the respective minor and major diameters323and324of external thread320. External thread320and360and internal thread372are the same size and have identical pitches. Since diameter376of unthreaded part370B of hole370of anchor nut304is greater than major diameter324of external thread320, unthreaded part370B of hole370is configured to receive therethrough in a direction from open outer end352distal end324of shank310and pass over external thread320until external thread320at proximal end314encounters runout374. Since pitch385of internal thread372and pitch325of external thread320are the same, minor and major diameters383and384of internal thread372correspond to the respective minor and major diameters323and324of external thread320, internal thread372twists in the same right-hand direction as external thread320, and internal and external threads372and320are correspondingly sized, internal thread372corresponds to and is configured to thread rotationally over and on external thread320from runout374inFIG.27and off external thread320from runout374. Accordingly, internal thread372corresponds to and is configured to thread over and on external thread320. InFIGS.19and21, locknut306and is an annular block configured with a threaded hole401, including internal thread402. Threaded hole401extends through locknut306from an inner or first side306A of locknut306to an outer or second side306B of locknut306. Inner and outer sides306A and306B of locknut306are radial bearing surfaces. Nut locknut306has a thickness406from inner side306A to outer side306B. InFIG.21, internal thread402runs along the inside of locknut306between the opposed inner and outer sides306A and306B and twists in the same left-hand direction as external thread360opposite to the right-hand hand direction of external thread320of bolt302and internal thread372of anchor nut304. Internal thread402includes minor diameter403, major diameter404, and pitch405, the distance between adjacent peaks or crests of the thread. Minor diameter403occurs at the crests of internal thread402, and major diameter404occurs at the roots of internal thread402. Pitches325,365,385, and405are identical. Minor and major diameters403and404of internal thread402correspond to the respective minor and major diameters363and364of external thread360. External threads320and360and internal threads372and402are the same size and have identical pitches. InFIGS.19,22, and24-26, locknut306has parallel and circumferentially spaced-apart wrench grooves408for nut-turn purposes. Since pitch405of internal thread402and pitch365of external thread360are the same, minor and major diameters403and404of internal thread402correspond to the respective minor and major diameters363and364of external thread360, internal thread402twists in the same left-hand direction as external thread360, and internal and external threads402and360are correspondingly sized, internal thread402corresponds to and is configured to thread rotationally over and on external thread360from open outer end352of anchor nut304inFIG.23and off external thread360from open outer end352. Accordingly, internal thread402corresponds to and is configured to thread over and on external thread360for assembling anchor nut304and locknut306to form anchor nut assembly345inFIGS.22and23. Internal threads372and402twist in opposite directions, as described, internal thread372in the same direction as external thread320and internal thread402in the same direction as external thread360. Accordingly, internal threads372and402are counter-threads configured to threadedly receive counter-rotating externally-threaded elements. InFIG.23, a user assembles anchor nut assembly345by threading internal thread402over and on external thread360. The user threads internal thread402over and on external thread360by inserting open outer end352of anchor nut304into threaded hole401from inner side306A and rotating locknut306in the direction of arrow C. This advances locknut306in the direction of arrow D until inner side306A of locknut306is tightened directly against radial bearing surface354A of flange354. Locknut306is suitably sized to extend entirely over external thread360from inner side306A of locknut306tightened directly against radial bearing surface354A, shown also inFIG.22, to outer side306B of locknut306outboard of open outer end352in the assembly of anchor nut304and locknut306inFIG.23, when locknut306is tightened directly against radial bearing surface354A of flange304by rotating it in the direction of arrow C tightly against radial bearing surface354A of flange304. Accordingly, the dimension of locknut306from inner side306A to outer side306B, the thickness406of locknut306from inner side306A to outer side306B inFIG.21, is greater than the dimension of anchor nut304from radial bearing surface354A to open outer end352, the thickness366of anchor nut304from radial bearing surface354A to open outer end352inFIG.21. Rotating locknut306in the direction of arrow A opposite to the direction of arrow C withdraws locknut306from radial bearing surface354A in the direction of arrow B. Accordingly, a user need only reverse the operation threading locknut306on anchor nut304to separate locknut306from anchor nut304. Anchor nut304and locknut306may be repeatedly assembled and disassembled as needed. The assembly of bolt302and anchor nut assembly345forms fastener300inFIGS.24-27. Referring toFIGS.24-27in relevant part, a user assembles anchor nut assembly345and bolt302by inserting bolt302distal end314first into and through unthreaded part370A of bore370through open outer end352until external thread320at distal end314encounters runout374. He threads internal thread372on external thread320and advances anchor nut assembly345in the direction of arrow D by rotating bolt302in the direction of arrow A until internal thread372is threaded completely on external thread320inFIG.27. InFIG.27, locknut306is between radial bearing surface354A and head340, inner side306A is tightened directly against radial bearing surface354A, and external thread320extends through unthreaded part370B of hole370from open outer end352to runout374and through threaded part370A of hole370from runout374to open inner end350and beyond open inner end350to distal end314without interference from locknut306threaded on external thread360of anchor nut304. External threads320and360twist in opposite right and left directions, as described. Accordingly, anchor nut304threaded on bolt302and locknut306threaded on anchor nut306are counter-rotated. Rotating anchor nut304equipped with its attached locknut306in the direction of arrow A opposite to the direction of arrow C withdraws anchor nut assembly345from external thread320of bolt302in the direction of arrow D. Accordingly, a user need only reverse the operation threading anchor nut304on bolt302to separate anchor nut assembly345from bolt302. Bolt302and anchor nut assembly345may be repeatedly assembled and disassembled as needed. Fastener300is useful in forming bolted joint410inFIG.28, including members412and414secured together by fastener300, the assembly of bolt302, anchor nut304, and locknut306. Members412and414, metal plates in this example, have registered through bores416and418, respectively. A user forms bolted joint410to secure members412and414together by inserting bolt302free of anchor nut assembly345distal end314first into and through bore416to bore418to seat head340in bore's416counterbore416A on one side of the bolted joint410and extend external thread320outward from bore418to distal end314on the opposite side of bolted joint410. Head340and counterbore416A are correspondingly shaped. The user installs anchor nut assembly345on bolt302to assemble fastener300by inserting bolt310distal end314first into and through unthreaded part370A of bore370through open outer end352until external thread320at distal end314encounters runout374. He threads internal thread372on external thread320by rotating anchor nut304equipped with its installed locknut306in the direction of arrow C. This advances anchor nut assembly345in the direction of arrow B until internal thread372is threaded completely on external thread320between distal end324and member414and outer side306B of locknut306is tightened directly against member414initially clamping locknut306between radial bearing surface354A of anchor nut304and member414. Since the dimension of locknut306from inner side306A to outer side306B is greater than the dimension of anchor nut304from radial bearing surface354A to open outer end352, open outer end352is disabled from coming into direct contact against member414. Bolt length334extends through bores416and418from head340in counterbore416A to external thread320, extending outward from bore418to anchor nut assembly345and distal end314outboard of open inner end350. He alternately rotates anchor nut304and locknut306in the direction of arrow C. This alternately tightens inner side306A of locknut306against radial bearing surface354A and outer side306B of locknut306against member414until the desired tension is achieved, tightly clamping members412and414between head340anchored in counterbore416A on one side of bolted joint410and outer side306B of locknut306on the opposite side of bolted joint410and tightly clamping locknut306between radial bearing surface354A tightened directly against inner side306A of locknut306and member414tightened directly against outer side306B of locknut306. Locknut306tightened directly against radial bearing surface354A and member414serves its function as a locknut counter-rotated relative to external thread320of bolt302and internal thread372of anchor nut304aggressively disabling bolt302from loosening by rotating in the direction of arrow C. Since external threads320and360and internal threads372and402are identically sized and have the same pitches, the threaded attachments are strong and resistant to stripping. Fastener300securing bolted joint410is surprisingly strong and aggressive and resistant to axial failure, shear failure, and loosening in response to vibrational and prevailing torsional forces. The user need only reverse this operation to release bolted joint410and withdraw fastener300. The skilled artisan will readily appreciate that handedness of the threads described in conjunction with fastener300can be reversed in alternate embodiments. The thickness406of locknut306from inner side306A to outer side306B inFIG.21is greater than the thickness366of anchor nut304from radial bearing surface354A to open outer end352inFIG.21. This disables open outer end352from coming into direct contact against member414. In an alternate embodiment, the thickness406of locknut306from inner side306A to outer side306B inFIG.21can be the same or slightly less than the thickness366of anchor nut304from radial bearing surface354A to open outer end352inFIG.21to enable open outer end352to come into direct contact against member414. In yet another embodiment, anchor nut304can be internally threaded by thread372from open inner end350to open outer end352. IV FIG.29illustrates still another embodiment of a fastener450constructed and arranged according to the invention. Fastener450is useful in forming bolted joints and includes the previously-described bolt302appropriately marked as needed with its corresponding reference numerals for reference purposes, anchor nut454, and locknut456configured to be repeatedly and quickly assembled and disassembled. Anchor nut454and locknut456are configured to be repeatedly assembled inFIG.30to form an anchor nut assembly458and disassembled inFIG.29independently from bolt452. All diameters referenced throughout this specification related to fastener450are constant. InFIGS.29and30, anchor nut454is an annular block or body including open inner end460, open outer end462, head464, external thread470, and hole480configured with internal thread482. Hole480extends through anchor nut454from open inner end460to open outer end462. Head464has wrench flats466, six in this example, for nut-turn purposes, and extends from open inner end460to radial bearing surface458of head464. Radial bearing surface458faces external thread470. External thread470extends between radial bearing surface458and outer end462, twists in a left-hand direction opposite to external thread320of bolt302, and is exemplary of a standard left-handed external thread. InFIG.30, left-handed external thread470extends between radial bearing surface458and outer end462and includes minor diameter473, major diameter474, and pitch475, the distance between adjacent peaks or crests of the thread. Minor diameter473occurs at the roots of external thread470, and major diameter474occurs at the crests of external thread470. External threads320and470twist in opposite directions, as described. Accordingly, external threads320and470are counter-threads configured to threadedly receive counter-rotating internally-threaded elements. Hole480extending through anchor nut454from open inner end460to open outer end462inFIG.21is internally threaded by internal thread482from open inner end460to open outer end462. Internal thread482runs along the inside of anchor nut454from open inner end460to open outer end462and twists in the same right-hand direction as external thread320of bolt302opposite to the left-hand direction of external thread470. Internal thread482includes minor diameter483, major diameter484, and pitch485, the distance between adjacent peaks or crests of the thread. Minor diameter483occurs at the crests of internal thread482, and major diameter484occurs at the roots of internal thread482. Pitch485of internal thread482and pitch325of external thread320of bolt302inFIG.31are identical. Minor and major diameters483and484of internal thread482correspond to the respective minor and major diameters323and324of external thread320inFIG.31. Internal thread482and external thread320correspond and are the same size and have identical pitches. Since pitch485of internal thread482and pitch325of external thread320are the same, minor and major diameters483and484of internal thread482correspond to the respective minor and major diameters323and324of external thread320, internal thread482twists in the same right-hand direction as external thread320, and internal and external threads482and320are correspondingly sized, internal thread482corresponds to and is configured to thread rotationally over and on external thread320from open outer end462inFIGS.30and31and off external thread320from open outer end462. Accordingly, internal thread482corresponds to and is configured to thread over and on external thread320. InFIGS.29and30, locknut456and is an annular block configured with a threaded hole491, including internal thread492. Threaded hole491extends through locknut456from an inner side456A of locknut306to an outer side456B of locknut306inFIG.30. Inner and outer sides456A and456B of locknut456are radial bearing surfaces. Locknut456has a thickness486from inner side456A to outer side456B. InFIG.30, internal thread492runs along the inside of locknut456between the opposed inner and outer sides456A and456B and twists in the same left-hand direction as external thread470opposite to the right-hand hand direction of external thread320of bolt302and internal thread482of anchor nut454. Internal thread492includes minor diameter493, major diameter494, and pitch495, the distance between adjacent peaks or crests of the thread. Minor diameter493occurs at the crests of internal thread492, and major diameter494occurs at the roots of internal thread492. Pitches475and495are identical and somewhat smaller than pitches485and325. Minor and major diameters493and494of internal thread492correspond to the respective minor and major diameters473and474of external thread470. External thread470and internal thread492are the same size and have identical pitches. InFIG.29, locknut456has parallel and circumferentially spaced-apart wrench grooves498for nut-turn purposes. Since pitch495of internal thread492and pitch475of external thread470are the same, minor and major diameters493and494of internal thread492correspond to the respective minor and major diameters473and474of external thread470, internal thread492twists in the same left-hand direction as external thread470, and internal and external threads492and470are correspondingly sized, internal thread492corresponds to and is configured to thread rotationally over and on external thread470from open outer end462of anchor nut454inFIGS.30and31and off external thread470from open outer end462. Accordingly, internal thread492corresponds to and is configured to thread over and on external thread470for assembling anchor nut454and locknut456to form anchor nut assembly458inFIGS.30and31. Internal threads482and492twist in opposite directions, as described, internal thread482in the same direction as external thread320of bolt302and internal thread492in the same direction as external thread470. Accordingly, internal threads482and492are counter-threads configured to threadedly receive counter-rotating externally-threaded elements. InFIG.30, a user assembles anchor nut assembly458by threading internal thread492over and on external thread470. The user threads internal thread492over and on external thread470by applying open outer end462of anchor nut454into threaded hole491from inner side456A and rotating locknut456in the direction of arrow C. This advances locknut456in the direction of arrow D until inner side456A of locknut456and radial bearing surface468of head466are juxtaposed. Locknut456is suitably sized to extend entirely over external thread470from inner side456A of locknut456juxtaposed with radial bearing surface468to outer side456B of locknut456at open outer end462in the assembly of anchor nut454and locknut456inFIG.30, when locknut456is threaded on anchor nut454. The dimension of locknut456from inner side456A to outer side456B, the thickness486of locknut456from inner side456A to outer side456B, is less than the dimension of anchor nut454from radial bearing surface468to open outer end462, the thickness476of anchor nut454from radial bearing surface468to open outer end462. Rotating locknut456in the direction of arrow A opposite to the direction of arrow C withdraws locknut456from radial bearing surface468and off anchor nut454in the direction of arrow B. Accordingly, a user need only reverse the operation threading locknut456on anchor nut454to separate locknut456from anchor nut454. Anchor nut454and locknut456may be repeatedly assembled and disassembled as needed. The assembly of bolt302and anchor nut assembly458forms fastener450inFIG.31. A user assembles anchor nut assembly458and bolt302by inserting bolt302distal end314first into open outer end462until external thread320at distal end314encounters internal thread482at open outer end462. He threads internal thread482on external thread320and advances anchor nut assembly458in the direction of arrow D by rotating bolt302in the direction of arrow A until internal thread482is threaded completely on external thread320. Locknut456is between radial bearing surface468and head340, inner side456A and radial bearing surface468are juxtaposed, outer side456B and open outer end462are juxtaposed, and external thread320extends through internally threaded hole480from open outer end462to open inner end460and beyond open inner end460to distal end314without interference from locknut456threaded on external thread470of anchor nut454. External threads320and470twist in opposite right and left directions, as described. Accordingly, anchor nut454threaded on bolt302and locknut456threaded on anchor nut454are counter-rotated. Rotating anchor nut454equipped with its attached locknut456in the direction of arrow A opposite to the direction of arrow C withdraws anchor nut assembly458from external thread320of bolt302in the direction of arrow D. Accordingly, a user need only reverse the operation threading anchor nut454on bolt302to separate anchor nut assembly458from bolt302. Bolt302and anchor nut assembly458may be repeatedly assembled and disassembled as needed. Fastener450is useful in forming bolted joint500inFIG.31, including members502and504secured together by fastener450, the assembly of bolt302, anchor nut454, and locknut456. Members502and504, metal plates in this example, have registered through bores506and508, respectively. A user forms bolted joint500to secure members502and504together by inserting bolt310distal end314first into and through bore506to bore508to seat head340in bore's506counterbore506A on one side of the bolted joint500and extend external thread320outwardly from bore508to distal end314on the opposite side of bolted joint500. Head340and counterbore506A are correspondingly shaped. The user installs anchor nut assembly458on bolt302to assemble fastener450by inserting bolt310distal end314first into open outer end462so external thread320at distal end314encounters internal thread482. He threads internal thread482on external thread320by rotating anchor nut454equipped with its installed locknut456in the direction of arrow C. This advances anchor nut assembly458in the direction of arrow B until internal thread482is threaded completely on external thread320and outer side456B of locknut456and open outer end456are is concurrently tightened directly against member504. Since the dimension of locknut456from inner side456A to outer side456B is less than the dimension of anchor nut454from radial bearing surface468to open outer end462, open outer end462is enabled to come into direct contact against member414. Bolt length334extends through bores506and508from head340in counterbore506A to external thread320, extending outwardly from bore508to anchor nut assembly458and distal end314. He alternately rotates anchor nut454and locknut456in the direction of arrow C. This alternately tightens outer side456B of locknut456and open outer end462of anchor nut454against member504until the desired tension is achieved, clamping members502and504between head340anchored in counterbore506A on one side of bolted joint500and outer side456B of locknut456and open outer end462of anchor nut454concurrently tightened directly against member504on the opposite side of bolted joint500. With both outer side456B of locknut456and open outer end462of anchor nut454concurrently tightened directly against member504, locknut456serves its function as a locknut counter-rotated relative to external thread320of bolt302and internal thread372of anchor nut454aggressively disabling bolt302from loosening by rotating in the direction of arrow C. Fastener450securing bolted joint500is surprisingly strong and aggressive and resistant to axial failure, shear failure, and loosening in response to vibrational and prevailing torsional forces. The user need only reverse this operation to release bolted joint500and withdraw fastener450. The skilled artisan will readily appreciate that handedness of the threads described in conjunction with fastener450can be reversed in alternate embodiments. The thickness486of locknut456from inner side456A to outer side456B is less than the thickness476of anchor nut454from radial bearing surface468to open outer end462. In an alternate embodiment, the thickness486of locknut456from inner side456A to outer side456B can be the same as the thickness476of anchor nut454from radial bearing surface468to open outer end462. V The person having ordinary skill in the art will readily appreciate that disclosed are exemplary bolts, bolt and nut fasteners, and bolted joints formed therewith. The various embodiments are configured to be readily and quickly assembled and disassembled, efficient, and are structured and arranged as disclosed to be suitably resistant to loosening in response to vibrational, shear and prevailing torque forces, even when exposed to or submerged in oil or other lubricant. The various embodiments disclosed herein are manufactured of standard materials routinely used in the manufacture of bolts and nuts and may be appropriately sized to relate to specific applications. The present invention is described above with reference to illustrative embodiments. Those skilled in the art will recognize that changes and modifications may be made in the described embodiments without departing from the nature and scope of the present invention. Various changes and modifications to the embodiments herein chosen for purposes of illustration will readily occur to those skilled in the art. To the extent that such modifications and variations do not depart from the spirit of the invention, they are intended to be included within the scope thereof. | 52,490 |
11859653 | DETAILED DESCRIPTION The present invention concerns various embodiments of a Battery-Cartomizer connector for an Electronic Cigarette that creates an air-intake path that enters through the male connector (i.e. the Battery section), without the need to modify the female connector (i.e. the Cartomizer section) thereof. Accordingly, the present invention permits flexibility of design and product diversification for the E-cigarette manufacturer, maintains ease of manufacture and mass-production, and creates additional advantages such as reducing noise and hissing during air-intake (i.e. a “puff or “drag”). FIGS.5-13depict various embodiments of the connector of the present invention. It is understood that these figures depict a sectional view of an E-cigarette connector1, which joins the Battery section to the Cartomizer section by a threaded engagement. As shown inFIGS.5-13, it is intended that the male Battery connector M at the proximal end3of the connector mates to a female portion of a Cartomizer, and the distal end5of the connector is attached, through a pressure or friction fit, or through other suitable means, to the Battery portion B (not shown) and functions as a “cap” thereof. In some embodiments of the present invention, an air intake path starts at the outer circumference of the connector1between the Battery and the Cartomizer of the E-cigarette, running inside notch9on connector1. The air is thus brought into the Battery through grooves10formed on the attachment (i.e., non-threaded) distal end5of the connector. Once inside the battery, the air path loops around and exits the Battery housing towards the Cartomizer, via a hole along the central axis of connector1. In accordance with the desired air-intake path, notch9is cut out on the side of connector1at strategic location and with strategic geometry. In most E-cigarettes, connector1has a flange7that appears from the outside as a metallic ring when the separate parts of the E-cigarette are screwed together, like that shown inFIG.1. The resulting ring is usually very thin, and has little purpose other than cosmetic—to create a decorative divider between the two major parts of the E-cigarette (i.e. the Battery section and the Cartomizer section) and to cover the inside edge of the Battery housing. Cutting into this ring or removing a portion of it to create the desired air-intake characteristics of the present invention would expose the dull edge of the Battery housing and detracts from the esthetics of the product. However, in some embodiments of the present invention, the thickness of the flange is increased so that a portion of it can be cut or milled away, resulting in notch9, while the remaining portion of the flange thickness will still retain the aesthetic design and still cover the internal edge of the housing. Accordingly, as shown inFIG.5, in some embodiments of connector1, notch9begins at the outer perimeter of the flange7, toward distal end5and travels toward the center axis of flange7, resulting in a rectangular shape. In some embodiments, such as inFIG.6, aperture11is bored through the wall of the distal end5of connector1at substantially the same radial location as notch9. This configuration increases the air-intake volume, permitting less-constricted air flow through the connector1and the Battery section. In some embodiments, such as inFIG.7, slot13is milled along the curved wall of the distal end5of connector1, with notch9located substantially across from the center of slot13, radially. As shown, slot13is oriented perpendicular to the longitudinal axis of connector1. In some embodiments, such as inFIG.8, channel15is milled across the outer surface of the distal end5of connector1, beginning at notch9and terminating at the end of distal end5. In this configuration, notch9has a substantially curved profile that transitions uniformly into channel15. In this configuration, channel15is milled substantially parallel to the longitudinal axis of connector1. In some embodiments, such as inFIG.9, fanned channel17is milled across the outer surface of the distal end5of connector1, beginning at notch9and terminating at the end of distal end5. Notch9has a substantially curved profile that transitions into fanned channel17. Fanned channel17is milled substantially parallel to the longitudinal axis of connector1. In some embodiments, such as inFIG.10, channel19is milled away all around the outer circumference of flange7, along its distal edge. The purpose of channel19is to allow for air intake even when a user happens to hold his finger over notch9during smoking. When that happens, air enters channel19and runs along the channel until it reaches and enters notch9. In some embodiments, such as inFIG.11, channel21is milled away all around the outer circumference of flange7, substantially in the middle of the flange. Several apertures23are bored through the wall of the flange. The purpose of channel21is to allow for air intake even when a user holds his finger over an aperture23during smoking. When that happens, air enters channel21and runs along the channel until it reaches and enters an aperture23. In some embodiments, such as inFIG.12, notch25is cut out through the wall of flange7on the side of connector1at strategic location and with strategic geometry. Slot27is cut out of the distal end5of connector1, beginning at notch25and terminating at the end of distal end5. In this configuration, notch25has a rectangular profile that transitions uniformly into slot27. Another embodiment of the connector of the present invention is shown inFIGS.13-15.FIG.13shows the connector without a battery post,FIG.14shows the battery post andFIG.15shows the battery post and connector assembled. As shown inFIG.13, instead of a notch in the outer perimeter of the flange7, toward distal end5, perpendicular surface channels30are drilled on shelf31of flange7. The channels continue and penetrate through the shaft32of connector1(in which threads are not shown for purposes of clarity) at orifices33and continue through inner shelf45. The engaging battery post34, shown inFIG.14, includes a longitudinal orifice35(beginning on the surface of post head37and continuing longitudinally completely through the post) that forms the pressure differential channel, as well as a groove36which assists in guiding air inhaled or exhaled through perpendicular surface channel30and orifice33. It should be noted here that although inFIG.15groove36is shown aligned with perpendicular surface channel30and orifice33, because the outer diameter of post head37is smaller than the inner diameter of shaft32, such alignment is not necessary to allow for unimpeded air flow through connector1. The airflow104through the connector and battery post combination shown inFIGS.13-15is illustrated inFIG.16. As shown inFIG.16, one possible draw-back of this arrangement is that upon exhalation, any excess fluid116(vapor, saliva, etc.) could be blown through orifice35, into the pressure differential channel and into the Battery B. An alternative embodiment for a battery post designed to minimize this problem is shown inFIG.17. As shown in this figure, there is no orifice drilled through post head37. Rather, the air path to the pressure differential channel is created by channel38which is drilled beneath groove36on the side39of post head37. Channel38perpendicularly intersected by the pressure differential channel (not shown) which is drilled longitudinally from battery post end40. The airflow through a connector such as that shown inFIG.13using the battery post shown inFIG.17is illustrated inFIG.18. As is shown in this figure, there is no direct path for excess liquid116to migrate into the Battery compartment B. The connector1of the present invention has an additional major advantage in that those embodiments shown inFIGS.5-18allow for a substantially silent air-intake without the excessive hissing or noise associated with other known E-cigarettes. Another major advantage of the present invention is its application in newly introduced V-Go and E-go (large-capacity electronic cigarettes) E-cigarettes. V-go and E-go E-cigarettes, which almost always have a side-intake, cannot be used with non-vented female Cartomizers. Heretofore manufacturers always had to resort either to vented female Cartomizers or non-vented male Cartomizers. However, with the present invention, it is possible to create V-go and E-go E-cigarettes that will be interchangeable with Tip-Intake E-cigarettes so that they are compatible with the same existing female unvented Cartomizers, without the need to modify the Cartomizers. It should be appreciated that although the above-described embodiments demonstrate that some embodiments of the present invention are designed such that the Battery comprises the “male” connection and the Cartomizer comprises the “female” connection, the reverse configuration may be equally suitable, depending on design requirements. Accordingly, the Cartomizer may comprise the “male” connection and the Battery may comprise the “female” connection. It will be understood that the preferred embodiments of the present invention have been disclosed by way of example and that other modifications and alterations may occur to those skilled in the art without departing from the scope of the disclosure herein. | 9,370 |
11859654 | DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Please refer toFIGS.1to10for a preferable embodiment of the present invention. A carrying rack connecting device1of the present invention includes a connection rod1and a connection assembly2. The connection rod1includes a first through hole11extending along a first direction91and a second through hole12extending along a second direction92, and the connection rod1is configured to be connected to a mounting rod8in a third direction93, wherein the first direction91, the second direction92and the third direction93are perpendicular to one another. The connection assembly2includes a base3, an urging member4and an operation member5, the base3is positioned inside the connection rod1, the base3includes an operation space35, and the operation space35is in communication with the first through hole11and the second through hole12. The urging member4is received within the operation space35and movable along the first direction91to be protrusive beyond the first through hole11for urging an inner wall of the mounting rod8, which can eliminates assembling gap between the connection rod1and the mounting rod8, and improves assembling stability of the connection rod1and the mounting rod8. The urging member4includes a first abutting portion41, the operation member5is configured to be disposed through the mounting rod8, extends within the operation space35via the second through hole12and is connected to the base3. Specifically, the operation member5is movable in the second direction92by rotating the operation member5. The operation member5includes a threaded portion51and an enlarged portion52connected with each other, the threaded portion51has a diametric dimension smaller than a diametric dimension of the enlarged portion52, the threaded portion51is screwed to the base, and the enlarged portion52includes a second abutting portion53. At least one of the second abutting portion53and the first abutting portion41extends in a direction tilted to the first direction91and the second direction92so that when the second abutting portion53pushes the first abutting portion41in the second direction92, the first abutting portion41slides relatively on the second abutting portion53so that the enlarged portion52pushes the urging member4to protrude out from the first through hole11in the first direction91. Specifically, the threaded portion51has a length larger than a length of the enlarged portion52, and the enlarged portion52is cylindrical. The first abutting portion41and the second abutting portion53extend inclinedly relative to the first direction91and the second direction92, thus providing smooth movement. The enlarged portion52is screwed to and disposed around the threaded portion51, and the threaded portion51is protrusive out beyond the enlarged portion52and screwed to the base3. In this embodiment, the enlarged portion52is detachably connected with the threaded portion51. The second abutting portion53has rigidity smaller than rigidity of the first abutting portion41so that the first abutting portion41is not easy to be worn and there just is a need to replace the enlarged portion52. The urging member4includes a channel42disposed therethrough, the operation member5is disposed through the channel42and connected to the base3, the first abutting portion41extends arcuately at a periphery of the channel42, and the second abutting portion53extends arcuately at the distal end of the enlarged portion52. Preferably, the operation member5further includes an extension portion54, the extension portion54is connected with the threaded portion51and configured to be connected with and protrusive out the mounting rod8, and the extension portion54is configured to be connected with a fastener7. The fastener7can stably secure the operation member5, the mounting rod8and the connection rod1. In this embodiment, the extension portion54has a diametric dimension smaller than a diametric dimension of the threaded portion51, a distal end of the extension portion54is arcuate, the first abutting portion41faces toward the second through hole12, and the base3further includes a threaded hole37within which the threaded portion51is screwed. When the operation member5is not within the operation space35, the urging member is abutted against a bottom wall36of the operation space35in the first direction91and is not protrusive beyond the base3so that the first abutting portion41and the threaded hole37overlap in the second direction92. During insertion of the operation member5, the distal end of the extension portion54pushes the first abutting portion41to move the urging member, the urging member is disengaged from the bottom wall36and slidably abutted against the extension portion54(first stage); when the operation member5moves in a direction through the base3, the threaded portion51pushes the first abutting portion41to further move the urging member (second stage), the urging member is slidably abutted against the threaded portion51; when the operation member5keeps moving in the direction through the base3, the second abutting portion53pushes the first abutting portion41to further move the urging member (third stage) so that the urging member is urgingly abutted against the inner wall of the mounting rod8. In other words, during insertion of the operation member5, the urging member is pushed by three-stage pushing of the urging member through so that the urging member can move stably and smoothly in the first direction91. Specifically, the base3further includes a first inner side wall31perpendicular to the second direction92and two second inner side walls32perpendicular to the second direction92. The two second inner side walls32are separately arranged and laterally connected with the first inner side wall31to define the operation space35, and the urging member4is kept slidably abutted against the first inner side wall31and the two second inner side walls32. The first inner side wall31and the two second inner side walls32can effectively restrict, limit and guide the urging member4to move along the first direction91. Specifically, the base3further includes a third inner side wall33and a perforation34, the third inner side wall33corresponds to the first inner side wall31and is connected with the two second inner side walls32, and the third inner side wall33inclinedly extends relative to the second direction92. The first inner side wall31, the two second inner side walls32and the third inner side wall33define the operation space35, the perforation34is disposed through the third inner side wall33in the second direction92, and the perforation34is in communication with the operation space35and the second through hole12. The urging member4further includes an inclined wall43. When the operation member5is not within the operation space35, the inclined wall43is abutted against the third inner side wall33. The inclined wall43and the third inner side wall33increase contact area therebetween. As the operation member5is not within the base3and the connection rod1, the urging member4can be stably supported and guided. The difference between the first inner side wall31and the third inner side wall33provides definite indication for assembling. In this embodiment, in the first direction91, the first inner side wall31and the two second inner side walls32is of the same height, and the third inner side wall33is lower than the first inner side wall31so as to form an opening38. When the inclined wall43is abutted against the third inner side wall33, the urging member4is partially exposed from the opening38, which is easy to grip the urging member4from the opening38. When the operation member5is within the operation space35and connected to the base3and the second abutting portion53does not push the first abutting portion41, the urging member4is abutted against a portion of the threaded portion51located within the operation space35. The urging member4further includes a projection44, and the projection44is located at a side of the urging member4opposite to the operation member5. When the urging member4is abutted against the threaded portion51, in the first direction91, a distance between an end of the projection44opposite to the operation member5and the threaded portion51is defined as a first distance61, a distance between the first through hole11and the threaded portion51is defined as a second distance62, the first distance61is greater than the second distance62, and the projection44is inserted within the first through hole11to enforce support to the urging member4. Specifically, the urging member4further includes a main body45and two leg portions46, the projection44and the two leg portions46are disposed at two opposing sides of the main body45, the inclined wall43extends from a side of the main body45to a side of the two leg portions46, the two leg portions46are arranged in interval and form the channel42with the main body45, the channel42is an open structure, and the operation member5is disposed between the two leg portions46. In an embodiment shown inFIGS.11and12, the base3A further includes a threaded hole37A within which the threaded portion51A is screwed, and a recess39. The recess39is recessed in the second direction92and in communication with the threaded hole37A, and the second abutting portion53A is inclined. The enlarged portion52A further includes a third abutting portion55, and the third abutting portion55extends along the second direction92and is connected with a topmost portion of the second abutting portion53A. When first abutting portion41A slides from the second abutting portion53A to the third abutting portion55and protrudes out beyond first through hole11A, the second abutting portion53A is inserted within the recess39. It is noted that the third abutting portion55is preferably thick and has good structural strength so as to effectively and reliably urge urging member4A. The second abutting portion53A is partially engaged within the recess39, which improves stability of assembling of the base3A. Although particular embodiments of the invention have been described in detail for purposes of illustration, various modifications and enhancements may be made without departing from the spirit and scope of the invention. Accordingly, the invention is not to be limited except as by the appended claims. | 10,381 |
11859655 | DESCRIPTION OF EMBODIMENTS Next, a configuration of coupling mechanism1according to an embodiment of the present invention is described with reference toFIGS.1to5. Note that in the following description, the arrow directions illustrated inFIGS.1to5define the up-down direction, front-rear direction, and left-right directions of coupling mechanism1(or coupling mechanism101of the other embodiment) for the sake of convenience. Here “up” in the above-mentioned “up-down direction” is a relative position when sliding surface31ais assumed as the lower side with respect to sliding surface31aof slider3that slides with bottom surface41a1of bottom side member41with an operation of inner cables2A and2B, not the upper and lower side of the state where coupling mechanism1is attached to an attaching object such as a vehicle body. The same applies to “down” in the above-mentioned “up-down direction”. In addition, in the following description, the direction of arrow D illustrated inFIGS.1,2A, and4Adefines the sliding direction of slider3(or slider103of the other embodiment) with respect to joint case4for the sake of convenience. Coupling mechanism1of the present embodiment is a mechanism for transmitting the operating force of the operation member to the actuation member, and couples one cable attached to the actuation member or the operation member and the other cable attached to the actuation member or the operation member. That is, coupling mechanism1couples at least two types of cables,2A and2B, and transmits an operating force applied to one inner cable2A to the other cable2B (or transmits an actuation power applied to the other cable2B to one inner cable2A) as illustrated inFIG.1, for example. One end portion (for example, a front end portion in the present embodiment) of inner cable2A is connected to coupling mechanism1side (slider3side described later), and the other end portion (for example, a rear end portion in the present embodiment) thereof is directly or indirectly connected to an operation member (not illustrated) for applying an operating force to inner cable2A. In addition, one end portion (for example, a rear end portion in the present embodiment) of cable2B is connected to coupling mechanism1side (slider3side), and the other end portion (for example, a front end portion in the present embodiment) thereof is directly or indirectly connected to an actuation member side member (not illustrated). The actuation member is operated when an operating force applied to the operation member is transmitted to cable2B through inner cable2A and slider3. Here, it suffices that the operation member can operate inner cable2A, and the operation member may be, for example, a member that is manually operated such as a shift lever and a handle, or a member for pulling operation of cables through electric driving. In addition, the actuation member is not limited as long as it is remotely operated by the operation member operated, and may be, for example, a locking mechanism in an opening closing member such as a vehicle hood, a trunk, and a fuel lid, and a seat locking mechanism for locking the reclining state of seats. It suffices that inner cables2A and2B can transmit the operating force applied by the operation member to the actuation member, and, for example, publicly known control cables may be adopted. Here, while the inner cable inserted to the outer casing is adopted as described later in the present embodiment, this is not limitative, and a control cable composed only of inner cable2may also be adopted. Configuration of Coupling Mechanism1 First, a configuration of coupling mechanism1of the present embodiment is described with reference toFIG.1. Coupling mechanism1mainly includes inner cables2A and2B as an example of a cable, slider3coupled with end portions of inner cables2A and2B, joint case4including housing space S for housing slider3in a slidable manner, and the like. In addition, slider3includes bottom surface part31(seeFIG.2B) including sliding surface31afor sliding on joint case4, and slides inside housing space S of joint case4through a pulling operation of any of inner cables2A and2B. Inner cables2A and2B are members for transmitting, through slider3, an operating force applied by the operation member (not illustrated) composed of a seat lever or the like, to the actuation member (not illustrated) composed of a seat locking mechanism or the like. Inner cables2A and2B are inserted to outer casings21A and21B, respectively, in a slidable manner. In addition, one end portion (for example, a front end portion in the present embodiment) of outer casing21A and one end portion (for example, a rear end portion in the present embodiment) of outer casing21B are both fixed to joint case4, and portions between both end portions of inner cables2A and2B are protected by outer casings21A and21B. Cable ends22A and22B are provided at one end portion (for example, a front end portion in the present embodiment) of inner cable2A and one end portion (for example, a rear end portion in the present embodiment) of inner cable2B, respectively, and inner cables2A and2B are coupled with slider3through cable ends22A and22B. In addition, although not shown in the drawings, cable ends (not illustrated) are also provided at the other end portion (for example, a rear end portion in the present embodiment) of inner cable2A and the other end portion (for example, a front end portion in the present embodiment) of inner cable2B, and inner cable2A and inner cable2B are coupled with the operation member and the actuation member, respectively, through the cable ends. Here, the shapes of cable ends22A and22B are not limited as long as inner cables2A and2B can be coupled with slider3and they have a strength enough to transmit the operating force applied by the operation member to the actuation member through slider3, and the shape may be any shapes such as spherical, columnar, and rectangular prism shapes. Note that the shapes of cable ends22A and22B are described in detail later. Incidentally, in the present embodiment, one inner cable2A is extended from slider3to one side (for example, the rearward side in the present embodiment) and coupled with the slider3, and two inner cables2B are extended from slider3to the other side (for example, the forward side in the present embodiment) and coupled with the slider3. In addition, two inner cables2B include first inner cable2B1and second inner cable2B2disposed parallel to each other, and long coupling end2B3for coupling first inner cable2B1and second inner cable2B2at an end portion. Specifically, coupling end2B3is cable end22B provided at inner cable2B, has a function of coupling inner cable2B with slider3, and has a function of coupling first inner cable2B1and second inner cable2B2with each other in the longitudinal direction. Here, the number of inner cables2A and2B may be appropriately changed in accordance with the usage of coupling mechanism1. Specifically, as long as a configuration for coupling inner cables through slider3is provided, it is possible to adopt a configuration provided with two or more inner cables2A on one side and two or more inner cables2B on the other side. It is also possible to adopt a configuration provided with two or more inner cables2A on one side and one inner cable2B on the other side. It is also possible to adopt a configuration provided with one inner cable2A on one side and one inner cable2B on the other side, for example. Note that in coupling mechanism1of the present embodiment, it is preferable to provide a plurality of inner cables extended on at least one side since it makes easy to maintain the state where the inner cable is locked and coupled with slider3. Cable end22A of inner cable2A is locked with first coupling part33provided at a side part on one side (for example, the rear side in the present embodiment) of slider3. In this manner, inner cable2A is coupled with slider3. In addition, cable end22B of inner cable2B is locked with second coupling part34provided at a side part on the other side (for example, the front side in the present embodiment) of slider3. In this manner, inner cable2B is coupled with slider3. In this manner, slider3is a member for coupling inner cable2A on one side and inner cable2B on the other side. In addition, slider3transmits, to inner cable2B on the other side, an operating force applied to inner cable2A on one side by the operation member by coupling inner cable2A on one side and inner cable2B on the other side. Slider3is housed inside housing space S of joint case4in a slidable manner in such a manner that the operating three applied by the operation member is transmitted to the actuation member through inner cables2A and2B. For example, in the present embodiment, when inner cable2A is operated and pulled rearward by the operation member, slider3is pulled by inner cable2A to slide rearward inside housing space S of joint case4since it is locked with cable end22A of inner cable2A. As a result, inner cable2B with cable end22B locked with slider3is also pulled rearward together with slider3. In this manner, the operating force applied by the operation member is transmitted to the actuation member through inner cable2A, slider3, and inner cable2B in this order. Slider3has, for example, a substantially cuboid shape in its entirety in the present embodiment, and can be coupled with cable end22A of inner cable2A and cable end22B of inner cable2B through first coupling part33provided at the rear side part and second coupling part34provided at the front side part as described above. In addition, slider3is configured to be slidable in sliding direction D (for example, the front-rear direction in the present embodiment) inside housing space S of joint case4. Here, the entire shape of slider3is not limited to the present embodiment, and may be appropriately modified in accordance with the usage as long as it can be coupled with inner cables2A and2B and it can slide in movement direction D inside housing space S of joint case4. Note that slider3will be described in detail later. Joint case4is a housing member that houses slider3in a slidable manner. Joint case4includes bottom side member41provided with bottom surface41a1and lid side member42provided with lid surface42a1, and is configured such that lid side member42can open and close with respect to bottom side member41. Bottom side member41includes bottom part41aprovided with bottom surface41a1where slider3slide, a pair of side wall parts41buprightly provided facing each other on bottom part41aand extended toward sliding direction D of slider3, a pair of end wall parts41cuprightly provided facing each other at both end portions in sliding direction D at bottom part41a, and the like, and housing space S is composed of bottom part41a, side wall part41b, and end wall part41c. Further, housing space S is configured such that when inner cable2A (or inner cable2B) is operated, slider3can slide in the direction of transmitting the operating force to inner cable2B (or inner cable2A). In the present embodiment, the pair of side wall parts41bare provided in parallel with each other with a gap with a size approximately equal to the size of slider3in the width direction (a direction parallel to bottom surface41a1and orthogonal to sliding direction D) such that slider3is linearly guided and slid, and thus housing space S with a substantially cuboid shape extending in sliding direction D of slider3is formed. Note that housing space S has not only a function of guiding the sliding direction of slider3, but also a function of housing slider3and holding the assembling posture of slider3when assembling inner cables2A and2B to joint case4, for example. Lid side member42includes lid part42aincluding lid surface42a1that covers housing space S of bottom side member41, engagement part42bthat engages with bottom side member41, and the like, and the state where housing space S is closed is maintained when lid side member42is engaged with bottom side member41. In addition, lid side member42is coupled with bottom side member41through hinge43, and is configured to open and close about hinge43with respect to the bottom side member41. Specifically, engagement part42bshown as an engage claw is formed in lid side member42, and the state where housing space S is closed is maintained by engaging engagement pan42bwith engaged pan41dformed in bottom side member41while simultaneously closing housing space S by covering bottom side member41with lid side member42. In this manner, with lid surface42a1of lid side member42, it is possible to prevent slider3housed in housing space S of bottom side member41from being come out and dropped off from the housing space S. Note that the configurations of engagement part42bprovided in lid side member42and engaged part41dprovided in bottom side member41are not limited to the present embodiment, and other engagement structures may be adopted. In bottom side member41, first fixing part41c1that can engage with casing end23A provided in the front end portion of outer casing21A is formed in end wall part41cprovided on one side (for example, the rearward side in the present embodiment) in sliding direction D. The front end portion of outer casing21A is fixed to joint case4without coming off from bottom side member41by engaging first fixing part41c1and casing end23A. In addition, in bottom side member41, second fixing part41c2that can engage with casing end23B provided in the rear end portion of outer casing21B is formed in end wall part41cprovided on the other side (for example, the forward side in the present embodiment) in sliding direction D. The rear end portion of outer casing21B is fixed to joint case4without coming off from bottom side member41by engaging second fixing part41c2and casing end23B. Here, in the present embodiment, reduced diameter part23A1whose cross-sectional diameter is reduced in comparison with other regions is provided at a middle part of casing end23A in sliding direction D, first fixing part41c1is formed in a recessed shape that can engage with the outer periphery of the reduced diameter part23A1, reduced diameter part23A1is engaged with first fixing part41c1, and thus, outer casing21A is prevented from coming off from joint case4. In addition, reduced diameter part23B1whose cross-sectional diameter is reduced in comparison with other regions is provided at a middle part of casing end23B in sliding direction D, second fixing part41c2is formed in a recessed shape that can engage with the outer periphery of the reduced diameter part23B1, reduced diameter part23B1is engaged with second fixing part41c2, and thus, outer casing21B is prevented from coming off from joint case4. Note that the engagement structures of casing ends23A and23B and first fixing part41c1and second fixing part41c2are not limited to the present embodiment, and any configuration can be adopted as long as reliable fixing to joint case4without separation from bottom side member41can be achieved. Configuration of Slider3 Next, a configuration of slider3is described with reference toFIGS.2A to2C. Slider3includes sliding surface31athat is slidable on bottom surface41a1of bottom side member41, and a pair of contact surfaces32athat can make contact with side wall part41bof bottom side member41, and first coupling part33and second coupling part34are provided on the one side (rear side) and the other side (front side) of the sliding surface31a, respectively. For example, as illustrated inFIGS.2A and2B, slider3has a substantially cuboid shape in its entirety, and in the state where it is housed in housing space S of joint case4(seeFIG.1), the side surface located on bottom surface41a1side of bottom side member41functions as sliding surface31a. Further, the pair of side surfaces provided to face side wall part41bof bottom side member41at both sides in the width direction (the direction parallel to bottom surface41a1and orthogonal to sliding direction D, and, for example, the left-right direction in the present embodiment) functions as contact surface32a. Note that in the present embodiment, sliding surface31ais formed in a flat shape, but this is not limitative, and it is possible to adopt a configuration in which a recess (or through hole) or the like is provided optionally to reduce the frictional resistance with the bottom surface41a1of bottom side member41, for example. First coupling part33engages with cable end22A provided at the front end portion of inner cable2A, and couples the inner cable2A with slider3. As illustrated inFIG.2Afor example, first coupling part33is composed of first passage part33athrough which inner cable2A can be inserted, and first cable end housing part33bcommunicated with first passage part33aand in which cable end22A can be housed. First passage part33ais formed in a groove shape that extends through rear end surface39aof slider3in sliding direction D, from the top toward the bottom of slider3as illustrated inFIG.2C. In addition, the size (gap) in the width direction (left-right direction) of first passage part33ais set to a size approximately equal to the wire diameter of inner cable2A. First cable end housing part33bis formed in a recessed shape communicated with first passage part33aat a rear part in the top surface of slider3, and its size in the width direction (left-right direction) is set to a size approximately equal to the outer diameter of cable end22A. Note that first cable end housing part33bis extended forward so as to be communicated with second cable end housing part34bdescribed later in the present embodiment, but this is not limitative, and it may be provided separately from second cable end housing part34bas long as it has a size in the longitudinal direction (the front-rear direction in the present embodiment) that can house at least cable end22A. Further, as illustrated inFIG.2A, inner cable2A is inserted to first passage part33a, cable end22A is housed in first cable end housing part33b, and rear end surface22A1of cable end22A is brought into contact with end surface39a(more specifically, the front side of the rear end portion of slider3with end surface39a) of slider3. Thus, the cable end22A is engaged with end surface39aof slider3, and inner cable2A is coupled with slider3through first coupling part33. Note that the configuration of first coupling part33is not limited to the present embodiment, and it is possible to adopt a configuration similar to second coupling part34described later, or fourth coupling part134of slider103of the other embodiment, for example. Second coupling part34is an example of an embodiment of the present invention, and engages with cable end22B provided at the rear end portion of inner cable2B, and couples the inner cable2B to slider3. Second coupling part34includes separation restraining part34athat prevents inner cable2B from being separated from slider3, and second cable end housing part34bthat houses cable end22B. As illustrated inFIG.2B, separation restraining part34ais mainly composed of installation space35, inlet36, passage part37, first restriction part38, second restriction part39and the like. Installation space35is a space where inner cable2B extended from cable end22B toward sliding direction D of slider3(the forward direction in the present embodiment) is disposed in the state where inner cable2B is coupled with slider3. Installation space35is a space extending through front end surface39bof slider3in sliding direction D, and is partitioned by bottom surface part31including sliding surface31aprovided on bottom part41aside of joint case4(more specifically, bottom side member41), and a pair of side wall parts32including contact surface32aprovided in the direction (the left-right direction in the present embodiment) perpendicular to the extending direction of inner cable2B in the present embodiment, for example. As described above, in the present embodiment, two inner cables2B disposed parallel to each other (more specifically, first inner cable2B1and second inner cable2B2) are provided, and first inner cable2B1and second inner cable2B2are disposed in installation space35in the state where they are separated from each other in the width direction (left-right direction). Inlet36is a gap provided as an entrance for introducing inner cable2B into installation space35. Inlet36is provided on the upper side of installation space35, to open in the direction (the left-right direction in the present embodiment) perpendicular to the axis of the inner cable2B, with a gap equal to or greater than the wire diameter of each inner cable2B (first inner cable2B1or second inner cable2B2). Further, inlet36is configured to allow first inner cable2B1and second inner cable2B2to pass through it by sequentially moving each single inner cable2B (first inner cable2B1or second inner cable2B2) in the direction (the up-down direction in the present embodiment) perpendicular to the axis. Note that in the present embodiment, a gap of a pair of top plate parts51that makes up first restriction part38makes up inlet36as described later, for example. Passage part37is a space for guiding each inner cable2B that has passed inlet36to installation space35. As with the above-described installation space35, passage part37, which is a space extending through front end surface39bof slider3in sliding direction D, is set to communicate with the installation space35and inlet36and have a gap approximately equal to the wire diameter of each inner cable2B, and is configured such that each inner cable2B can move to installation space35through inlet36. Note that in the present embodiment, a gap of a pair of guide parts52that makes up second restriction part39makes up passage part37, and passage part37is provided to extend in the direction (the up-down direction in the present embodiment) perpendicular to the width direction (left-right direction) of slider3at a portion between installation space35and inlet36as described later for example. First restriction part38is a portion for blocking the movement direction of inner cable2B when inner cable2B disposed at installation space35unexpectedly moves in the direction (the upward direction in the present embodiment, for example) parallel to the extending direction (up-down direction) of passage part37. First restriction part38is provided on the side opposite to the bottom surface part31side, i.e., the upper side, in installation space35, and for example, in the present embodiment, first restriction part38is composed of the pair of top plate parts51that extends from the upper end portion of the pair of side wall parts32toward the center portion of slider3in the width direction and forms the front end surface39bof slider3. Here, as described above, first inner cable2B1and second inner cable2B2that make up inner cable2B are disposed in installation space35in the state where they are separated from each other in the width direction (left-right direction), and the pair of top plate parts51that makes up first restriction part38are provided at respective locations at least on the upper side of these first inner cable2B1and second inner cable2B2. Further, when at least one of first inner cable2B1and second inner cable2B2unexpectedly moves upward in installation space35, it makes contact with the end surface (the lower end surface in the present embodiment) on bottom surface part31side of top plate part51, and the top plate part51functions as first restriction part38. Incidentally, the pair of top plate parts51is configured such that the gap between the end surfaces facing each other is set to be equal to or greater than the wire diameter of first inner cable2B1(or second inner cable2B2), and the above-described inlet36is composed of the gap of the pair of top plate parts51. Second restriction part39is a portion for restricting the movement of inner cable2B disposed in installation space35to passage part37. Second restriction part39is provided adjacent to the above-described first restriction part38, and is composed of the pair of guide parts52, each of which is provided to extend in the direction (the downward direction in the present embodiment) perpendicular to the width direction of slider3, from an protrusion end portion (i.e., an end portion on the side opposite to side wall part32side of the pair of top plate parts51) of the pair of top plate parts51that makes up first restriction part38toward the bottom surface part31side, in the present embodiment, for example. Further, for example, when an unexpected external force is applied to first inner cable2B1and second inner cable2B2disposed in installation space35in the state where they are separated from each other in the width direction (left-right direction), and first inner cable2B1(or second inner cable2B2) is about to move to passage part37while being uplifted about second inner cable2B2(or first inner cable2B1) as a fulcrum, the first inner cable2B1(or second inner cable2B2) makes contact with the side surface on the side opposite to side wall part32of guide part52, and thus the side surface functions as second restriction part39. Incidentally, the pair of guide parts52is set such that the gap between the side surfaces facing each other is approximately equal to the wire diameter of first inner cable.2B1(or second inner cable2B2), and the above-described passage part37is composed of the gap of the pair of guide parts52. As illustrated inFIG.2A, second cable end housing part34bis formed in a recessed shape in communication with installation space35(seeFIG.2B), inlet36, and passage part37at the front part of the top surface of slider3. In addition, second cable end housing part34bhouses cable end22B in the state where the rear end portion of first inner cable2B1and second inner cable2B2that make up inner cable2B is disposed through installation space35. As illustrated inFIG.2C, second cable end housing part34bincludes a pair of inner surfaces32bprovided on both sides in the width direction (left-right direction) and formed in side wall part32, and the pair of inner surfaces32bfunctions as third restriction part40that restricts the rotation of cable end22B housed in second cable end housing part34b. That is, as described above, cable end22B provided at inner cable2B is composed of long coupling end2B3that couples first inner cable2B1and second inner cable2B2in the longitudinal direction, and cable end22B is housed in second cable end housing part34bwith its longitudinal direction oriented in the width direction in the state where the rear end portions of first inner cable2B1and second inner cable2B2are disposed in installation space35in the state where they are separated in the width direction of slider3. In this state, the pair of inner surfaces32bare provided respectively facing the both end surfaces of housed cable end22B in the longitudinal direction (the left-right direction in the present embodiment). For example, when an unexpected external force is applied to cable end22B through inner cable2B, one end surface of cable end22B in the longitudinal direction is uplifted and the cable end22B acts to rotate, any of both end surfaces of cable end22B in the longitudinal direction makes contact with inner surface32bof second cable end housing part34bin such a manner as to restrict the rotation of cable end22B, and thus the inner surface32bfunctions as third restriction part40. Procedure for Assembling Coupling Mechanism1 Next, a procedure for assembling coupling mechanism1of the present embodiment is described with reference toFIGS.1to3D. Note that the assembling procedure described below is merely an example, and is not limitative. First, as illustrated inFIG.1, joint case4is in a state where lid side member42is opened, and slider3is inserted to the housing space S of bottom side member41with sliding surface31a(see FIG.2B1directed toward bottom surface41a1side of bottom side member41. Here, while the position where slider3is inserted in housing space S may be any position in sliding direction D, it is desirable that the position is the vicinity of a center portion in sliding direction D for ensuring the operation space for coupling inner cables2A and2B to slider3later. In addition, in the present embodiment, slider3is inserted to housing space S with second coupling part34and first coupling part33directed forward and rearward, respectively, but this is not limitative, and may be appropriately changed in accordance with the usage of coupling mechanism1. It is possible to insert slider3to housing space S with first coupling part33and second coupling part34directed forward and rearward, respectively. After completion of insertion operation of slider3into housing space S, a coupling operation of slider3and inner cables2A and2B is performed. Here, while after inner cable2A on one side is coupled to slider3, inner cable2B on the other side is coupled to slider3as described below in the present embodiment, this is not limitative, and inner cable2A on one side may be coupled to slider3after inner cable2B on the other side is coupled to slider3. The coupling operation of inner cable2A on one side and slider3is performed in the following procedure. First, inner cable2A is pulled out by a predetermined length from casing end23A provided at an end portion (the front end portion in the present embodiment) of outer casing21A. Next, the end portion (the front end portion in the present embodiment) of inner cable2A pulled out from casing end23A is inserted to first coupling part33of slider3from above, inner cable2A is inserted to first passage part33aas illustrated inFIG.2A, cable end22A is housed in first cable end housing part33b, and the cable end22A is engaged with end surface39aof slider3. In this manner, the end portion (front end portion) of inner cable2A is coupled with slider3. Thereafter, as illustrated inFIG.1, casing end23A of outer casing21A is inserted to first fixing part41c1of bottom side member41from above, and casing end23A is engaged with first fixing part41c1through reduced diameter part23A1. In this manner, the end portion of outer casing21A is fixed to joint case4, and the coupling operation of slider3and inner cable2A on one side is completed. Note that while casing end23A of outer casing21A is fixed to joint case4after the end portion (front d portion) of inner cable2A is coupled with slider3in the present embodiment, this is not limitative. The end portion (front end portion) of inner cable2A may be coupled with slider3after casing end23A of outer casing21A is fixed to joint case4in consideration of the efficiency of the operation and the like. In addition, after the end portion (front end portion) of inner cable2A is coupled with slider3, in accordance with the procedure described below, the end portion (rear end portion) of inner cable2B may be coupled with slider3once, and then casing end23A of outer casing21A and casing end23B of outer casing21B may be collectively fixed to joint case4. After completion of the coupling operation of inner cable2A on one side and slider3, a coupling operation of inner cable2B on the other side and slider3is performed. The coupling operation of inner cable2B on the other side and slider3is performed in the following procedure. First, inner cable2B is pulled out by a predetermined length from casing end23B provided at the end portion (the rear end portion in the present embodiment) of outer casing B. Next, the end portion (the rear end portion in the present embodiment) of inner cable2B pulled out from casing end23B is inserted to second coupling part34of slider3from above, inner cable2B is inserted to separation restraining part34a, cable end22B (coupling end2B3) is housed in second cable end housing part34b, and the cable end22B (coupling end2B3) is engaged with end surface39bof slider3as illustrated inFIG.2A. In this manner, the end portion (rear end portion) of inner cable2B is coupled with slider3. Here, a procedure for inserting inner cable2B to separation restraining part34ais described in detail with reference toFIGS.3A to3D. In the present embodiment, as described above, two inner cables2B (first inner cable2B1and second inner cable2B2) are provided, and inner cables2B are sequentially entered one by one into passage part37from inlet36, and guided by the passage part37to installation space35. More specifically, first, in the state where, out of two inner cables2B, one inner cable2B (first inner cable2B1in the present embodiment) is directed toward slider3side (the lower side in the present embodiment) with respect to the other inner cable (second inner cable2B1in the present embodiment), the first inner cable2B1is entered into passage part37from inlet36. Next, first inner cable2B1entered into passage part37is moved to bottom surface part31side of slider3along the passage part37such that first inner cable2B1reaches installation space35as illustrated inFIG.3A. Here, in the state where first inner cable2B1has reached installation space35, second inner cable2B2is not yet entered into passage part37, and is located in the vicinity of inlet36. After first inner cable2B1has reached installation space35, cable end22B (coupling end2B3) is rotated around the virtual axis parallel to sliding direction D (seeFIG.1) while it is slightly moved in the width direction of slider3(left-right direction) in second cable end housing part34bas illustrated inFIG.3B. In this manner, first inner cable2B1is moved in an arc-like trajectory toward the side separated away from passage part37(in the present embodiment, right side with respect to passage part37), and second inner cable2B2is moved in an arc-like trajectory toward the side approaching inlet36. Thereafter, as illustrated inFIG.3C, by further rotating cable end22B (coupling end2B3) around the axis of first inner cable2B1that has reached a position separated from passage part37, second inner cable2B2is moved to installation space35while pressing the side surface of passage part37on one side (left side in the present embodiment) and being guided by the passage part37. Note that slider3is formed of a member with elasticity such as resin, and the pair of guide parts52that makes up passage part37is configured to be bendable about the base part on top plate part51side as a fulcrum. As a result, second inner cable2B2is moved to installation space35while pressing the side surface of passage part37on one side (left side) and widening the gap of the passage part37. Further, as illustrated inFIG.3D, when cable end22B (coupling end2B3) further rotates and second inner cable2B2is come off from passage part37, first inner cable2B1and second inner cable2B2are disposed in installation space35in the state where they are separated from each other in the width direction (left-right direction). As described above, installation space35that makes up separation restraining part34aof slider3of the present embodiment is configured such that when one of first inner cable2B1and second inner cable2B2(for example, first inner cable2B1) moves to passage part37through inlet36and it reaches a position separated from passage part37by the rotation of cable end22B (coupling end2B3) at second cable end housing part34b, the other of first inner cable2B1and second inner cable2B2(for example, second inner cable2B2) can move to installation space35from passage part37. Further, when first inner cable2B1and second inner cable2B2are disposed in installation space35respectively, cable end22B (coupling end2B3) is engaged with end surface39bof slider3and the end portion (rear end portion) of inner cable2B is coupled with slider3. Thereafter, as illustrated inFIG.1, casing end23B of outer casing21B is inserted to second fixing part41c2of bottom side member41from above, and casing end23B is engaged with second fixing part41c2through reduced diameter part23B1, in this manner, the end portion of outer casing21B is fixed to joint case4, and thus the coupling operation of slider3and inner cable2B on the other side is completed. Incidentally, the coupling operation of slider3and inner cables2A and2B may be performed before or after slider3is inserted to housing space S of bottom side member41, but, when slider3is inserted to housing space S of bottom side member41in advance, the posture of slider3is held by bottom side member41and the subsequent coupling operation of slider3and inner cables2A and2B can be readily performed. Therefore, as described in the present embodiment, it is preferable to perform the coupling operation of slider3and inner cables2A and2B after slider3is inserted to housing space S of bottom side member41. When the coupling operation of slider3and inner cables2A and2B is completed, lid side member42is closed and engagement part42bis engaged with engaged part41dof bottom side member41so as to maintain the closed state of the lid side member42. In this manner, at housing space S of bottom side member41, the closed state with lid side member42is reliably maintained, and it is thus possible to prevent drop off of the slider3from joint case4due to an unexpected external force applied to slider3through inner cables2A and2B, for example. Upon completion of the operation of closing lid side member42at joint case4, the assembling operation of coupling mechanism1is completed. Configuration of Coupling Mechanism101of Other Embodiment Next, a configuration of coupling mechanism101of the other embodiment is described with reference toFIGS.4A to5D. Coupling mechanism101of the other embodiment has a configuration substantially similar to that of the above-described coupling mechanism1, and differs from the above-described coupling mechanism1in the configuration of fourth coupling part134provided on the other side (the front side in the present embodiment) of mainly slider103. Therefore, in the following description, differences from the above-described coupling mechanism1are mainly described, and configurations similar to that of the coupling mechanism1are omitted. Slider103includes sliding surface131athat is slidable on bottom surface141a1of bottom side member141of joint case104, and third coupling part133and fourth coupling part134are provided on one side (rear side) and the other side (front side) of the sliding surface131a, respectively. Note that the above-mentioned joint case104, sliding surface131a, and third coupling part133have configurations similar to those of the above-described joint case4, sliding surface31a, and first coupling part33in coupling mechanism1, and therefore descriptions thereof are omitted. Fourth coupling part134, which is an example of an embodiment of the present invention, engages with cable end122B provided at the rear end portion of inner cable102B, and couples the inner cable102B to slider103. Fourth coupling part134includes separation restraining part134athat prevents inner cable102B from coming off from slider103, and third cable end housing part134bthat houses cable end122B. Note that the above-mentioned inner cable102B and cable end122B have configurations similar to those of the above-described inner cable2B and cable end22B in coupling mechanism1, and therefore descriptions thereof are omitted. As illustrated inFIG.4B, separation restraining part134ais mainly composed of installation space135, inlet136, passage part137, fourth restriction part138, fifth restriction part139and the like. Note that the above-mentioned installation space135, inlet136, and passage part137have configurations similar to those of installation space35, inlet36, and passage part37of the above-described coupling mechanism1, and therefore descriptions thereof are omitted. Fourth restriction part138is a portion for blocking the movement direction of inner cable2B when inner cable102B disposed in installation space135unexpectedly moves toward the direction (for example, upward in the other embodiment) parallel to the extending direction (up-down direction) of passage part137. Fourth restriction part38is provided on the side opposite to bottom surface part131side in installation space135, i.e., the upper side. In the other embodiment, fourth restriction part138is composed of top plate part151that forms front end surface139bof slider103and extends from the upper end portion of one (for example, the left one in the other embodiment) of a pair of side wall parts132toward the upper end portion of the other (for example, the right one in the other embodiment) side wall part132, for example. Note that bottom surface part131, side wall part132, and end surface139bhave configurations similar to those of bottom surface part31, side wall part32, and end surface39bin the above-described coupling mechanism1, and therefore descriptions thereof are omitted. Here, first inner cable102B1and second inner cable2B2that make up inner cable102B are disposed in installation space135in the state where they are separated from each other in the width direction (left-right direction), and top plate part151that makes up fourth restriction part138is continuously provided at a location on the upper side of at least first inner cable102B1and second inner cable102B2. Further, when at least one of first inner cable102B1and second inner cable102B2unexpectedly moves upward in installation space135, it makes contact with the end surface (the lower end surface in the present embodiment) on bottom surface part131side in top plate part151, and the top plate part151functions as fourth restriction part138. Incidentally, top plate part151is set such that the gap from side wall part132on the other side (right side) is equal to or greater than the wire diameter of first inner cable102B1(or second inner cable102B2), and inlet136is composed of the gap between top plate part151and side wall part132on the other side (right side). Fifth restriction part139is a portion for restricting the movement of inner cable102B disposed in installation space135to passage part137. Fifth restriction part139is provided adjacent to the above-described fourth restriction part138, and in the other embodiment, fifth restriction part139is composed of guide part152provided to extend in the direction (the downward direction in the other embodiment) perpendicular to the width direction of slider103, from the extending end portion (i.e., the end portion on the side opposite to side wall part132in top plate part151) of top plate part151that makes up fourth restriction part138toward bottom surface part131side, for example. Further, for example, when an unexpected external force is applied to first inner cable102B1and second inner cable102B2disposed in installation space135in the state where they are separated from each other in the width direction (left-right direction) and first inner cable102B1is about to move to passage part137while being uplifted about second inner cable102B2as a fulcrum, the first inner cable102B1makes contact with the side surface on the side opposite to passage part137side in guide part152and thus the side surface functions as fifth restriction part139. Incidentally, guide part152is set such that the gap from side wall part132on the other side (right side) is approximately equal to the wire diameter of first inner cable102B1(or second inner cable102B2), and passage part137is composed of the gap between guide part152and side wall part132of the other side (right side). Third cable end housing part134bhas a configuration substantially similar to that of second cable end housing part.34bof the above-described coupling mechanism1, but has a shape slightly extended to passage part137side to avoid interference with cable end122B when coupling slider3and inner cable102B as described later. Note that the shape of third cable end housing part134bis not limited to that of the other embodiment, and may have a configuration similar to that of second cable end housing34bby appropriately changing the design of the configuration of cable end122B in inner cable2B, for example. Coupling mechanism101of the other embodiment with the above-described configuration is assembled in a procedure substantially similar to that of the above-described coupling mechanism1, and coupling mechanism101of the other embodiment is different from the above-described coupling mechanism1in the procedure of inserting inner cable102B to separation restraining part134a. Here, awhile a procedure of inserting inner cable102B to separation restraining part134ais described below with reference toFIGS.5A to5D, other operation procedures are similar to those of the above-described coupling mechanism1, and therefore descriptions thereof are omitted. First, in the state where one of two inner cables102B (first inner cable102B1in the other embodiment) is directed toward slider103side (the lower side in the other embodiment) with respect to the other inner cable (second inner cable102B1in the other embodiment), the first inner cable102B1is entered into passage part137from inlet136. Next, first inner cable102B1entered into passage part137is moved to bottom surface part.131side of slider103along the passage part137such that first inner cable102B1reaches installation space135as illustrated inFIG.5A. Here, in the state where first inner cable102B1has reached installation space135, second inner cable102B2is not yet entered into passage part137and is located in the vicinity of inlet136. After first inner cable102B1has reached installation space135, cable end122B is moved to the side (the left side in the other embodiment) separated away from passage part137in the width direction of slider3in third cable end housing part134bas illustrated inFIG.5Bsuch that first inner cable102B1reaches an approximate center portion in the width direction in installation space135. Thereafter, cable end122B is rotated around the virtual axis parallel to sliding direction D (seeFIG.4A) while it is further moved in the width direction (left direction) of slider3in second cable end housing part34b. In this manner, first inner cable102B1is moved in an arc-like trajectory toward the side (left side) separated away from passage part137, and second inner cable102B2is moved in an arc-like trajectory toward the side approaching inlet136. Then, as illustrated inFIG.5C, cable end122B is further rotated around the axis of first inner cable102B1that has reached a position separated from passage part137, and thus second inner cable102B2is moved to installation space135while, being guided by passage part137. Thereafter, as illustrated inFIG.5D, when cable end122B is further rotated and second inner cable102B2is come off from passage part137, first inner cable102B1and second inner cable102B2are disposed in installation space135in the state where they are separated from each other in the width direction (left-right direction). As described above, as with installation space135of the above-described coupling mechanism1, installation space135of the other embodiment is configured such that when one (for example, first inner cable102B1) of first inner cable102B1and second inner cable102B2moves through passage part.137through inlet136and it reaches a position separated from passage part137by the rotation of cable end122B at third cable end housing part134b, the other (for example, second inner cable102B2) of first inner cable102B1and second inner cable102B2can move to installation space135from passage part137. When first inner cable102B1and second inner cable102B2are disposed in installation space135respectively, cable end122B is engaged with end surface139bof slider103(seeFIG.4A) and the end portion (rear end portion) of inner cable102B is coupled with slider103. Effects As described above, coupling mechanism1of the present embodiment (or coupling mechanism101) is a coupling mechanism including inner cable2B (or inner cable102B) including cable end22B (or cable end122B) at an end portion, slider3(or slider103) including second coupling part34(or fourth coupling part134) that couples with the end portion of inner cable2B (inner cable102B), and joint case4(or joint case104) including housing space S that houses slider3(slider103) in a slidable manner. In addition, second coupling part34(fourth coupling part134) includes second cable end housing part34b(or third cable end housing part134b) that houses cable end22B (cable end122B), and separation restraining part34a(or separation restraining part134a) that restrains separation of inner cable2B (inner cable102B) from slider3(slider103). Further, separation restraining part34a(separation restraining part134a) includes installation space35(or installation space135), inlet36(or inlet136), passage part37(or passage part137), and first restriction part38(or fourth restriction part138). Here, installation space35(installation space135) is a space extending in sliding direction D of slider3(slider103), and a space in which inner cable2B (inner cable102B) extended from cable end22B (or cable end122B) is disposed in the state where inner cable2B (inner cable1028) is coupled with slider3(slider103). In addition, inlet36(inlet136) is a gap that opens with a gap equal to or greater than the wire diameter of the inner cable2B (inner cable102B) in the direction perpendicular to the axis of inner cable2B (inner cable102B), and allows inner cable2B (inner cable102B) to pass through it by moving it in the direction perpendicular to the axis. In addition, passage part37(passage part137) is a space communicated with installation space35(installation space135) and inlet36(inlet136), and is a space in which inner cable2B (inner cable102B) can move to the installation space35(installation space135) through inlet36(inlet136). Further, first restriction part38(fourth restriction part138) is a part that blocks the movement direction of inner cable2B (inner cable102B) when inner cable2B (inner cable102B) disposed in installation space35(installation space135) moves in the direction parallel to the extending direction of passage part37(or passage part137). In this manner, in coupling mechanism1of the present embodiment (or coupling mechanism101of the other embodiment), the gap of inlet36(inlet136) is set to be equal to or greater than the wire diameter of inner cable2B (inner cable102B), and thus, when the end portion of inner cable2B (inner cable102B) is pushed into installation space35(installation space135) from the inlet36(inlet136), it can be smoothly guided to passage part37(passage part137) through inlet36(inlet136). As a result, the end portion of the inner cable2B (inner cable102B) can be readily coupled with slider3(slider103) while preventing buckling and the like at the end portion of inner cable2B (inner cable102B). In addition, after the end portion of inner cable2B (inner cable102B) is disposed in installation space35(installation space135), first restriction part38(fourth restriction part138) can prevent the end portion of the inner cable2B (inner cable102B) from moving to the side opposite to sliding surface31a(sliding surface131a) side of joint case4(joint case104) and from being dropped from slider3(slider103). In addition, in coupling mechanism1of the present embodiment (or coupling mechanism101), separation restraining part34a(separation restraining part134a) includes second restriction part39(or fifth restriction part139) adjacent to first restriction part38(fourth restriction part138), and configured to restrict the movement of inner cable2B (inner cable102B) disposed in installation space35(installation space135) to passage part37(passage part137). With the above-mentioned configuration, second restriction part39(or fifth restriction part139) can prevent the end portion of inner cable2B (inner cable102B) disposed in installation space35(installation space135) from again passing through passage part37(passage part137) and from being dropped from slider3(slider103) through inlet36(inlet136). In addition, in coupling mechanism1(or coupling mechanism101) of the present embodiment, inner cable2B (inner cable102B) includes first inner cable2B1(or first inner cable102B1) and second inner cable2B2(or second inner cable102B2) disposed parallel to each other, and coupling end2B3that couples first inner cable2B1(first inner cable102B1) and second inner cable2B2(second inner cable102B2). Further, installation space35(installation space135) is configured such that when, out of first inner cable2B1(first inner cable102B1) and second inner cable2B2(second inner cable102B2), one inner cable2B (inner cable102B) moves through passage part37(passage part137) through inlet36(inlet136) and it reaches a position separated from passage part37(passage part137) by a rotation of coupling end2B3at second cable end housing part34b(third cable end housing part134b), out of first inner cable2B1(first inner cable102B1) and second inner cable2B2(second inner cable102B2), the other inner cable2B (inner cable102B) can move from passage part37(passage part137) to installation space35(installation space135). With the above-mentioned configuration, even with a plurality of (two) inner cables2B (inner cable102B), it is easy to perform the coupling with second coupling part34(fourth coupling part134) of slider3(slider103). In addition, in coupling mechanism1of the present embodiment, coupling end2B3that couples first inner cable2B1and second inner cable2B2is long cable end22B that couples first inner cable2B1and second inner cable2B2in the longitudinal direction, and second coupling part34includes third restriction part40that restricts the rotation by making contact with the both end surfaces of the cable end22B in the longitudinal direction when cable end22B is rotated in the state where the end portions of first inner cable2B1and second inner cable2B2are extended through and disposed in installation space35. With the above-mentioned configuration, for example, even when external forces are applied to first inner cable2B1and second inner cable2B2from directions three-dimensionally different from each other, third restriction part40can limit the fluttering of cable end22B. It is thus possible to prevent a situation where first inner cable2B1and second inner cable2B2move in a twisted direction (for example, a direction in which one of first inner cable2B1and second inner cable2B2is rotated around the other of first inner cable2B1and second inner cable2B2) together with the cable end22B, and first inner cable2B1and second inner cable2B2unexpectedly pass through passage part37and dropped from slider3through inlet36. In addition, in coupling mechanism1of the present embodiment, separation restraining part34aincludes bottom surface part31on the bottom part side of joint case4and the pair of side wall parts32provided in the direction perpendicular to the extending direction of inner cable2B, and bottom surface part31and the pair of side wall parts32partition installation space35. First restriction part38is composed of the pair of top plate parts51provided on the side opposite to bottom surface part31side of installation space35, inlet36is composed of the gap of the pair of top plate parts51, and passage part37is composed of the gap of the pair of guide parts52on the side opposite to side wall part32at the pair of top plate parts51. With the above-mentioned configuration, with the pair of top plate parts51extended from the end portion of side wall part32, both the function of first restriction part38and the function of inlet36can be achieved, and the configuration of second coupling part34can be simplified. REFERENCE SIGNS LIST 1,101Coupling mechanism2A,2B,102B Inner cable2B1,102B1First inner cable2B2,102B2Second inner cable2B3Coupling end3,103Slider4,104Joint case21A Outer casing22A,22B,122B Cable end22A1End surface23A1,23B1Reduced diameter part31,131Bottom surface part31a,131aSliding surface32,132Side Tall part32aContact surface32bInner surface33First coupling part33aFirst passage part33hFirst cable end housing part34Second coupling part34a,134aSeparation restraining part34b,134hSecond cable end housing part35,135Installation space36,136Inlet37,137Passage part38First restriction part39Second restriction part39a,39b,139bEnd surface40Third restriction part41,141Bottom side member41a,141aBottom part41a1Bottom surface41bSide wall part41cEnd wall part41c1First fixing part41c2Second fixing part41dEngaged part42Lid side member42aLid part42a1Lid surface42bEngagement part43Hinge51,151Top plate part52,152Guide part133Third coupling part134Fourth coupling part138Fourth restriction part139Fifth restriction partD Sliding direction.S Housing space | 56,855 |
11859656 | DETAILED DESCRIPTION An embodiment according to the present invention will be explained below in reference to the drawings. In the explanation below, identical reference symbols in different drawings indicate parts with identical functions, and redundant explanations will be omitted as appropriate in each of the drawings. As illustrated inFIG.1, the thrust converting mechanism1comprises, at least, shafts2(2R and2L), linear motion members3(3R and3L), a case10, a rocking member4, and a moving member5. The thrust converting mechanism can also be considered a mechanism to convert a linear driving force. The shaft2here is equipped with split shafts2R and2L that are equipped facing each other linearly, but it may instead be a single shaft2that spans these. Helical mated portions2aand2bare formed on the shaft2, with the helical directions thereof formed in mutually opposite directions. The mated portions2aand2bmay be formed through male threads or female threads, or may be formed through a helical cam groove or cam protrusion, as illustrated. The shaft2is held, on one end side thereof, by a holding member11, in the example in the figure. The linear motion member3comprises a left-right pair of linear motion members3R and3L, where the linear motion member3R comprises a mating portion3athat engages with a mated portion2a, and the linear motion member3L comprises a mating portion3bthat engages with a mated portion2b. The mating portions3aand3bare nuts, for the case of the mated portions2aand2bbeing screws, or, for example, in the case of the mated portions2aand2bbeing cam grooves, are mating protrusions, or the like, that engaged therewith. The linear motion members3(3R and3L) move linearly along the shaft2through the shaft2rotating relative thereto. The rocking member4has an axle hole4afor bearing a shaft protrusion3cthat is provided on one of the linear motion members3L, and a mating portion4bfor engaging the mating protrusion3dthat is provided on the other linear motion member3R, where the pair of linear motion members3(3R and3L) revolves around the shaft protrusion3cto become closer or more separated, along the shaft2. The moving member5has mating portions5aand5bthat engage with mating protrusions4mand4nand that are provided on the rocking member4. In the example in the figure, when the rocking member4rocks by revolving to the left around the shaft protrusion3c, the mating protrusion4mengages with the mating portion5a, and when the rocking member4rocks by revolving to the right around the shaft protrusion3c, the mating protrusion4nengages with the mating portion5b. Through the engagement of the mating protrusions4mand4nwith the mating portions5aand5b, when the rocking member4rocks around the shaft protrusion3c, the moving member5moves in a direction that is perpendicular to the shaft2. At this time, in the example in the figure, in the rocking member4the distance from the axle hole4ato the mating protrusion4mwill be different from the distance from the axle hole4ato the mating protrusion4n, where the distance from the axle hole4ato the mating protrusion4nis longer than the distance from the axle hole4ato the mating protrusion4m, and because step differences are provided in the mating portions5aand5bin the moving member5, the amount of movement of the moving member5will be greater in the case of the rocking member4rocking by revolving to the right than when the rocking member4rocks by revolving to the left. The case10is borne on shaft2. In the example in the figure, the case10has a bearing portion10athat is borne on the split shaft2R and a bearing portion10bthat is borne on the split shaft2L, where the tip end protrusions2cof the split shafts2R and2L are supported on the bearing portion10c. The case10supports the linear motion members3(3R and3L) so as to support movement along the shaft2, and supports indirectly the rocking member4, which is supported on the linear motion members3(3R and3L). In the example in the figure, an elongated hole3eis provided along the shaft2on the linear motion member3L, where a supporting protrusion10dthat is provided on the case10is inserted into the elongated hole3e. The case10supports the moving member5so as to enable movement in a direction that is perpendicular to the shaft2. A guide hole5cof an elongated hole along the direction of movement is provided in the moving member5, and a guide protrusion10ethat is provided on the case10is inserted into this guide hole5c. A hook portion5dis provided on the moving member5, where a spring6, which has one end thereof hooked on the hook portion5d, has the other end thereof hooked on a hook portion10fof the case10. Through this, the moving member5is biased by the spring toward the shaft2, in a state wherein it is supported on the case10. Through this spring biasing, the mating portions5aand5bof the moving member5will always be in a state of engagement with one or both of the mating protrusions4mand4nof the rocking member4. Moreover, a joining protrusion5e, for joining with another component, is provided on the moving member5. This joining protrusion5emay be provided so as to pass through an opening7aof a dividing plate7that is provided if necessary. In such a thrust converting mechanism1, the two shafts2are held in parallel by a holding member11, making it possible to produce the hinge apparatus20shown inFIG.2throughFIG.4. In the hinge apparatus20, the two shafts2, which each have mated portions2aand2b, are secured in a state wherein end portions thereof are held by the holding member11, where the two shafts2that are secured are borne by the respective cases10(10A and10B). The hinge apparatus20enables the pair of cases10(10A and10B) to be changed to a opened state, wherein they are positioned in a plane, as illustrated inFIG.2, an inward state wherein they have been rotated in the direction of the arrow T1from the state wherein they are positioned in a plane (referencingFIG.3), and an outward folded state wherein they have been rotated in the direction of the arrow T2from the state wherein they are positioned in a plane (referencingFIG.4). In such a hinge apparatus20, the thrust that causes the linear motion members3(3R and3L) to move along the shaft2is produced through rotation of the case10(10A or10B) in respect to the shaft2that is secured to the holding member11. That is, the rotational force of the operation for folding or unfolding the case10(10A and10B) is converted, in the hinge apparatus20, into linear thrust of the linear motion members3(3R and3L). At this time, the pair of linear motion members3(3R and3L) will be in a neutral position in the opened state that is depicted inFIG.2, or will be in a state wherein they are nearest to each other in the inwardly folded state that is depicted inFIG.3, or a state wherein they are furthest apart from each other in the outwardly folded state that is depicted inFIG.4. Here the relative rotation of the linear motion members3(3R and3L), in respect to the shaft2, is limited to a rotation of 360° from the inwardly folded state that is depicted inFIG.3to the outwardly folded state that is depicted inFIG.4, but the mating portions3aand3bof the linear motion members3, which engage with the pair of mated portions2aand2b, have twice the amount of relative movement when compared to the movement of either alone. Additionally, the movement of the linear motion members3(3R and3L) along the shaft2is converted into a revolution of the rocking member4, and further, the revolution of the rocking member4is converted into movement in the direction perpendicular to the shaft2in the moving member5, thus making it possible to convert the direction of movement into a direction that is different from the direction along the shaft2, while securing a large amount of movement in respect to the limited rotation of the shaft2. This makes it possible to increase the scope of application of the hinge apparatus20. FIG.5throughFIG.7depict examples of operation when the hinge apparatus20is used in a mobile information terminal. In this case, when a folding operation is carried out through rotating the case10(10A and10B) in respect to the shaft2, through the hinge apparatus20, a flat-panel display (hereinafter termed simply “display”) FP, which is a flat panel member that is combined with the moving member5, moves in a direction that is perpendicular to the shaft2. In the opened state inFIG.5, the cases10A and10B are positioned in a plane, where the display FP that is combined with the moving members5will be in a state wherein the end portions, which faced each other across a junction portion S, will be mutually abutting, with no gap therebetween. The state of the hinge apparatus20at this time is that wherein the linear motion members3(3R and3L) are in a neutral position in respect to the shaft2, and the mating protrusions4mand4nand of the rocking member4are both engaged with the mating portions5aand5bof the moving member5, and the moving member5is in a state that is nearest to the shaft2. In contrast, in the inwardly folded state, depicted inFIG.6, the state of the hinge apparatus20is a state wherein the linear motion members3(3R and3L) are nearest to each other along the shaft2, where the rocking member4has revolved to the right around the shaft protrusion3cso that the mating protrusion4mof the rocking member4pushes the mating portion5bof the moving member5upward, so that the moving member5moves to a state that is away from the shaft2. Through this, the display FP that is combined with the moving member5will be in a state wherein the end portion thereof is away from the junction portion S. Moreover, in the outwardly folded state, depicted inFIG.7, the state of the hinge apparatus20is a state wherein the linear motion members3(3R and3L) are most separated from each other along the shaft2, where the rocking member4has revolved around the shaft protrusion3cso that the mating protrusion4nof the rocking member4pushes the mating portion5aof the moving member5upward, so that the moving member5moves to a state that is away from the shaft2. Through this, the display FP that is combined with the moving member5will be in a state wherein the end portion thereof is away from the junction portion S, but the end portion of the display FP will be closer to the junction portion S than the state depicted inFIG.6. Through this hinge apparatus20, in the opened state of the cases10(10A and10B), the state will be one wherein the end portions of the pair of displays FP are abutting each other without a gap, as depicted inFIG.8a. Additionally, in the inwardly folded state of the cases10(10A and10B), the state will be one wherein the pair of displays FP are enclosed on the inside of the holding member11, as depicted inFIG.8b. Additionally, in the outwardly folded state of the cases10(10A and10B), the state will be one wherein the pair of displays FP is disposed in a position wherein they are covered by the holding member11, and do not protrude from the holding member11, as depicted inFIG.8c. In the hinge apparatus20the shafts2that bear the respective cases10A and10B are separated from each other, and thus when the pair of cases10(10A and10B) are rotated to the opened state or the folded state, 180° rotation of the cases10(10A and10B) around the shaft2is possible without the end portions of the cases10(10A and10B) interfering with each other. Moreover, magnets M are attached to each of the cases10(10A and10B) and the moving members5in the hinge apparatus20. The magnets M that are attached to both are at positions that are adjacent in the cases10(10A and10B) in the opened state, and which move away from each other in the state wherein the cases10(10A and10B) are folded. When the magnets M that are attached to both attract each other, the cases10(10A and10B) are held in the opened state by the attractive force, and when the magnets M that are attached to both repel each other, the folded state is maintained by the repulsive force. FIG.9throughFIG.12depict examples of operation of the thrust converting mechanism1through a briefcase handle H. The term “briefcase” is used generically for any handle of a bag for a briefcase, purse, etc. The one illustrated example is similar to that of a briefcase, but one of ordinary skill can contemplate other handle examples. In this briefcase, the handle H is provided rotatably on a hinge portion J that is provided in a briefcase main unit K, where the shaft2of the thrust converting mechanism1is rotated through rotation of the handle H. In such a briefcase, when the handle H is grasped, the handle H goes into the 90° standing state, as depicted inFIG.10b, and when the handle H is released, the handle H goes into a state wherein it is laying down, at 0° or 180°, as depicted inFIG.11borFIG.12b. At this time, when the handle H is rotated from 0° to 180° in respect to the briefcase main unit K, the shaft2rotates relatively from 0° to 180° in respect to the frame10that is secured to the briefcase main unit K. The thrust converting mechanism1comprises the features described above, as illustrated inFIG.9, and thus at this time, in the state wherein the handle H is standing at 90°, the linear motion members3(3R and3L) will be in the neutral position, as depicted inFIG.10a, and the moving member5will move to a state that is nearest to the shaft2, and in the state wherein the handle H is laying over at 0° or 180°, the linear motion members3(3R and3L) will move to the state wherein they are furthest apart from each other or the state wherein they are nearest to each other, and the moving member5will move to a state wherein it is furthest from the shaft2, as depicted inFIG.11aorFIG.12a. In the examples depicted inFIG.9throughFIG.12, the mating protrusions4mand4nof the rocking member4are provided at equal distances from the axle hole4a. In a briefcase that is provided with such a handle H, the locking mechanism of the briefcase can be actuated, or the like, linked to the movement of the moving member5in the thrust converting mechanism1. For example, when the handle H is in the 90° standing state, as illustrated inFIG.9, inward motion of the lock releasing lever P is prevented by the protrusion5P that is provided on the moving member5, and when the handle H goes into the state that is laying down at 0° or 180°, the movement of the protrusion5P in the moving member5allows inward motion of the lock releasing lever P. This can eliminate problems with the briefcase coming open through the lock being released through unintentional inward motion of the lock releasing lever P, in the state wherein the handle H is standing at 90°, that is, the state wherein the handle H is grasped. Moreover, in a state wherein the handle H is laying down at 0° or 180°, that is, a state wherein the handle H has been released, it is possible to open the briefcase quickly, because the lock releasing lever P can be moved in without performing another operation. Note that in the example in the figure, in the thrust converting mechanism1, magnets M are provided on the case10and the moving member5, where the repulsive force between the magnets M produce a state wherein the handle H lies down at 0° or 180° when the handle H is released. This can eliminate a state wherein the lock releasing lever P is unable to move in, which would be caused by the handle H remaining in the standing state despite the handle H being released. While in the two embodiments described above, the “direction perpendicular to the shaft2” was illustrated as directions crossing the direction in which the shaft2extends, it may be another direction instead. For example, in another embodiment the “direction crossing the shaft2” may cross, at an angle other than 90°, the direction in which the shaft2extends. FIG.13throughFIG.18depict a thrust converting mechanism1A according to another embodiment and a hinge apparatus21provided therewith. The thrust converting mechanism1A, as with the example described above, comprises at least shafts2(2R and2L), linear motion members3(3R and3L), cases10, and a rocking member4, and a moving member5. The case10supports the shaft2, rotatably, by the bearing portions10aand10b, and the tip end portions of shafts2R and2L are supported by the bearing portion10c. Moreover, the case10is hinged together by a hinge frame30, and can be rotated to a case angle of 90°, as depicted inFIG.13a, a case angle of 180°, as depicted inFIG.14a, or a case angle of 270°, as depicted inFIG.15a, in respect to the hinge frame30. As with the case10, hinge frames30can be attached with axial symmetry, and when a pair of cases10is hinged on the hinge frame30, each case10is supported so as to enable rotation of 180° in respect to the hinge frame30. The shafts2(2R and2L) are connected in respect to the hinge frame30, and when the case10rotates in respect to the hinge frame30, the shaft2rotates relative to the case10. Similarly to the example described above, in the thrust converting mechanism1A, when the shaft2rotates relative to the case10, the linear motion members3(3R and3L) that are engaged with the shaft2will move linearly along the shaft2. Given this, in the same manner as with the example described above, with the pair of linear motion members3R and3L, through rotation of the shaft2in one direction, the pair of linear motion members3R and3L will move toward each other, as depicted inFIG.13(FIG.16), and when the shaft2is rotated in the opposite direction, the pair of linear motion members3R and3L will move apart from each other, as depicted inFIG.15(FIG.18). At this time, each of the linear motion members3R and3L have elongated holes3fthat extend in the direction along the shaft2, where these elongated holes3fengage with guide protrusions10fthat are provided on the case10, to guide the linear movement of the linear motion members3R and3L. In contrast, as depicted inFIG.16throughFIG.18, the rocking member4is a lever member wherein the center portion is borne on a shaft protrusion3gthat is provided on one of the linear motion members3L, with an elongated hole4cfor engaging a mating portion3hof the other linear motion member3R provided on one end side and a mating protrusion4pprovided on the other end side, serving as a mechanism that rocks around the shaft protrusion3g, as depicted inFIG.16throughFIG.18, through the movement of the linear motion members3R and3L toward each other and away from each other along the shaft2. The moving member5is provided with a guide hole5fof an elongated hole shape in a direction that crosses the shaft2, where this guide hole5fengages with two mating protrusions3jand3kthat are provided on one of the linear motion members3L. The mating protrusions3jand3kare provided in positions that are separated from each other in the direction that crosses the shaft2, and the guide hole5fengages the mating portions3jand3k, so that the moving member5will first move in a direction along the shaft2accompanying movement of the linear motion member3R. Additionally, the moving member5has a cam hole5g, where a mating protrusion4pof the rocking member4engages with the cam hole5g. The cam hole5ghas a cam face that extends in the direction along the shaft2, so as to correspond with the movement of the mating protrusion4palong the shaft2when the rocking member4rocks. Additionally, the cam hole5ghas a cam face for moving the moving member5in a direction that crosses the shaft2, using the movement of the mating protrusion4pin a direction that crosses the shaft2when the rocking member4rocks. With such a mechanism, when the case10is rotated in respect to the hinge frame30, the shaft2rotates in respect to the case10, and the pair of linear motion members3R and3L move along the shaft2so as to move toward each other or away from each other, where the rocking member4rocks around the shaft protrusion3gthrough the movement of these linear motion members3R and3L. Additionally, through the cam hole5gof the moving member5acting in respect to the rocking of the rocking member4, the moving member5moves in a direction that crosses the shaft2. A coupling portion5qis provided on the moving member5, and a coupled portion W of an object that is to be moved is connected to this coupling portion Sq. As can be appreciated from the explanation above, the moving member5moves not only in the direction that crosses the shaft2, but moves also in the direction along the shaft2, following the movement of the linear motion member3R, and thus the coupling portion5qis provided with a releasing guide that releases the movement of the moving member5along the shaft2, so as to convey, to the coupled portion W, only the movement that is perpendicular to the shaft2. As explained above, in the thrust converting mechanisms1and1A according to embodiments according to the present invention, the provision of the linear motion members3(3R and3L) that move toward each other or away from each other when rotation of the shaft2is converted into linear motion makes it possible to increase the amount of linear motion in respect to the limited rotation of the shaft2, without increasing the driving force for rotating the shaft2. Moreover, when structuring the hinge apparatuses20and21, the connection of the displays, or the like, to moving members5that are provided for two cases10makes it possible to eliminate the gap, through moving the displays, or the like, in a direction that is perpendicular to the shaft2, when the two cases10are opened up, without interference between the end portions of the two cases10. Such thrust converting mechanisms1and1A and hinge apparatuses20and21can be used in a variety of applications. While embodiments of the present invention were described in detail above in reference to the drawings, the specific structures are not limited to these embodiments, but rather design changes, and the like, within a range that does not deviate from the spirit and intent of the present invention are included. In addition, the various embodiments described above may be combined through using each other's technology insofar as there are no particular inconsistencies or problems in the purposes and structures thereof. | 22,268 |
11859657 | DESCRIPTION OF THE ENABLING EMBODIMENT Referring to the Figures, wherein like numerals indicate corresponding parts throughout the several views, a ball socket assembly20in the form of a ball joint20for a vehicle is generally shown inFIG.1. The exemplary of the ball joint20is of the type which may experience either high compression loads (positive loads) or high tension loads (negative loads) and configured for use in a steering and suspension system (not shown) of a vehicle. For example, the ball joint20could be employed to operably connect a control arm (not shown) with a knuckle (not shown) or it could be a part of a tie rod end (not shown) for connecting a steering rack (not shown) with the knuckle. Other automotive and non-automotive applications are also contemplated. Referring now toFIGS.2and3, the exemplary embodiment of the ball joint20includes a cartridge-style housing22which can be press-fit into an opening of a first component, such as the control arm. The housing22has a cylindrical exterior surface which may be knurled to provide an improved interference fit with the first component. The housing22also has a radially outwardly extending flange24which defines a stopping point for press-fitting the housing22into the opening during an installation procedure. The housing22also has a circumferentially extending groove26which is spaced from the flange24for receiving a retainer ring (not shown) to lock the housing22with the first component. As shown inFIG.4, the housing22has an inner bore which extends along a vertical central axis A from a lower wall28at a closed first end30to an open second end32. In the axial direction from the closed first end30to the open second end32, the inner bore has first, second, and third zones34,36,38with progressively increasing diameters D1, D2, D3. More specifically, the first zone34adjacent the closed first end30has a first diameter D1, the second zone36has a greater second diameter D2, and the third zone38adjacent the open second end32has a still greater third diameter D3. Between the second and third zones36,38, the housing22presents a shoulder40which faces towards the open second end32. The housing22is preferably made as a single, monolithic piece of metal, such as steel or an alloy steel, and may be shaped through any suitable process or processes including, for example, casting, forging, machining from a billet, etc. At least the lower wall28is preferably shaped to its final form via at least one of the casting, forging, and machining operations. That is, the lower wall28is not bent or otherwise plastically deformed to its final shape. As discussed in further detail below, shaping the lower wall28to its final form without plastic deformation allows the ball joint20to be compression loaded whereby positive axial loads are exerted on the lower wall28when the ball joint20is installed in a vehicle suspension system. Referring now additionally toFIGS.2and3, a backing bearing42is disposed in the first zone34of the inner bore and has an outer diameter which is less than the first diameter D1such that the backing bearing42can radially move, or float, within the inner bore. A Belleville washer44(also known as a washer spring) that is made of spring steel is disposed in the first zone34of the inner bore between the backing bearing42and the lower wall28to apply an upward (i.e., toward the open second end32) biasing force on the backing bearing42. When the ball socket assembly20is assembled, the Belleville washer44may flatten to allow the backing bearing42to float radially within the inner bore. The ball joint20further includes a ball stud46, which has a ball portion48and a shank portion50. The ball portion48is disposed in the inner bore of the housing22and has a semi-spherically curved outer surface with a lower hemisphere, an equator, and an upper hemisphere. The backing bearing42has a curved first bearing surface which supports the lower hemisphere of the ball portion48for transferring positive axial forces (upward with respect to the orientations of the components in the Figures) between ball stud46and the lower wall28of the housing22. The shank portion50of the ball stud46projects out of the housing22through the open second end32for attachment with a second component (such as a knuckle) of the steering/suspension system. The ball stud46is preferably made of a single, monolithic piece of metal, such as steel or an alloy steel and may be shaped through any suitable process or combination of processes. A boot (not shown) is preferably sealed against the housing22and the shank portion50of the ball stud46for retaining a lubricant within and keeping contaminants out of the inner bore of the housing22. An annular exit bearing52is disposed in the second and third zones36,38of the inner bore of the housing22and supports both the equator and the upper hemisphere of the ball portion48of the ball stud46for transferring both radial and negative axial (downward, with respect toFIG.2) forces between the ball stud46and the housing22. An upper edge of the housing22is deformed, such as through a swaging operation, to present a radially inwardly extending lip54which directly engages a planar top surface of the exit bearing52to capture the exit bearing52, ball portion48, backing bearing42, and Belleville washer44within the inner bore of the housing22. The exit bearing52is made as two pieces, namely a plastic piece56and a metal piece58. In the exemplary embodiment, the plastic and metal pieces56,58are fixedly attached with one another by way of an overmolding connection whereby the metal piece58is fully or substantially encapsulated within the plastic piece56. Fabrication of the exit bearing52involves pre-forming the metal piece58(such as through casting or stamping) and inserting the metal piece58into a cavity of a mold (not shown). A melted plastic material is then injected into the cavity around at least a portion of the metal piece58. The plastic material is allowed to cool and solidify to form the plastic piece56around and in a fixed engagement with the metal piece58. In the exemplary embodiment, the metal piece58includes a plurality of circumferentially spaced apart openings60. The material of the plastic piece56extends through these openings60to strengthen the connection between the plastic and metal pieces56,58. The metal piece58is preferably made of steel, an alloy steel, aluminum, or an aluminum alloy. However, any suitable metallic material may be employed. In the exemplary embodiment, the plastic piece56is made of a polyamide material which is reinforced with 30-33% wt. glass fibers. This material has been found to provide the exit bearing52with exceptional strength, durability, and wear resistance. Referring now to bothFIGS.2and5, the plastic piece56has an inner surface which faces towards the central axis A and an outer surface which faces away from the central axis A. The outer surface has a first cylindrical portion64and a flange portion66. The cylindrical portion64extends axially from a planar bottom surface of the plastic piece56to the flange portion66and sits within the second zone36of the inner bore of the housing22. The flange portion66extends radially outwardly from the first cylindrical portion64and then axially to the top surface of the plastic piece56. Thus, the flange portion66has a greater diameter than the first cylindrical portion64and sits within the third zone38of the inner bore of the housing22. The flange portion66rests against a shoulder which separates the second and third zones36,38of the inner bore of the housing22. During the swaging operation, the contact between the flange portion66and the shoulder holds the exit bearing52in a fixed location within the inner bore. Starting from the bottom surface and going towards the top surface of the plastic piece, the inner surface sequentially includes a second cylindrical portion68, a first angled portion70, and a second angled portion72. The second cylindrical portion68has a diameter which is similar to an outer diameter of the ball portion48of the ball stud46and is in direct contact with an equator of the ball portion48for transferring radial forces between the ball stud46and the housing22. The second cylindrical portion68extends axially past the equator in both axial directions, i.e., both above and below the equator. The first angled portion70is angled towards the central axis A at a constant first angle α, which is preferably in the range of fifteen to twenty-five degrees (15-25°) relative to the axial direction and is in direct surface-to-surface contact with the ball portion48of the ball stud46. The second angled portion72is angled away from the central axis A by a greater angle than the first angled portion70, which allows for an increased swing angle of the ball stud46relative to the housing22. The inner surface further includes a plurality of circumferentially spaced apart and axially extending lubricant grooves74which extend from the bottom surface through the second cylindrical portion68and through the first angled portion70. In the exemplary embodiment, the inner surface includes four lubricant grooves74which are oriented at ninety degrees (90°) relative to one another for distributing the lubricant around the surface-to-surface area of contact between the plastic piece56and the ball portion48. The metal piece58has a shape which is similar to the shape of a Belleville washer. That is, the metal piece58has a generally constant thickness and has an outer surface which approximates the shape of a frustum of a cone, i.e., the metal piece58is semi-conical in shape. The metal piece58has an outer edge76and an inner edge78which lie in different planes that are spaced axially from one another with the inner edge78being closer to the closed first end30of the housing22and with the outer edge76being closer to the open second end32of the housing22. The outer edge76is at or adjacent to an intersection between the top surface and the outer surface of the plastic piece56. The inner edge78is located at or immediately adjacent to the first angled portion70of the inner surface of the plastic piece56immediately adjacent to where the inner surface contacts the ball portion48of the ball stud46. As viewed in cross-section, the metal piece58extends at an angle that is generally perpendicular to the first angled portion70of the inner surface. This configuration has been found to maximize the reinforcing performance of the metal piece58to allow the exit bearing52to resist increased forces being transferred through the exit bearing52between the ball portion48of the ball stud46and the housing22without compromising the structural integrity of the plastic piece56. As viewed in cross-section, the ball portion48of the ball stud46is in direct contact with the plastic piece56of the exit bearing52in two axially spaced apart locations. The first location is between the second cylindrical portion68of the inner surface and the equator of the ball portion48for transferring radial forces between the ball stud46and the housing22via the exit bearing52. The second location is between the first angled portion70of the inner surface and the upper hemisphere of the ball portion48for transferring axial forces between the ball stud46and the housing22via the exit bearing52. The angled configuration of the metal piece58within the plastic piece56reinforces the exit bearing52to resist deformation when subjected to increased forces as compared to the exit bearings in other known ball socket assemblies. Another aspect of the present invention is related to a method of making a ball socket assembly20, such as the ball joint20shown inFIGS.1-3. An exemplary embodiment of the method includes the step of injection molding the plastic piece56around at least a portion of the metal piece58to create the exit bearing52. The method continues with the step of inserting the ball portion48of the ball stud46into the inner bore of the housing22through the open second end32of the housing22. The method continues with the step of inserting the exit bearing52into the inner bore of the housing22and supporting the ball portion48of the ball stud46with the exit bearing52. The method proceeds with the step of deforming the housing22adjacent the open second end32to capture the exit bearing52within the inner bore of the housing22. Obviously, many modifications and variations of the present invention are possible in light of the above teachings and may be practiced otherwise than as specifically described while within the scope of the appended claims. It should also be appreciated that the use of directional terms, such as “upper”, “lower”, “top”, and “bottom” are with reference to the orientations of certain features in the Figures and are not intended to require any particular orientation. Additionally, it is to be understood that all features of all claims and all embodiments can be combined with each other as long as they do not contradict each other. | 13,045 |
11859658 | DETAILED DESCRIPTION Before turning to the figures, which illustrate certain exemplary embodiments in detail, it should be understood that the present disclosure is not limited to the details or methodology set forth in the description or illustrated in the figures. It should also be understood that the terminology used herein is for the purpose of description only and should not be regarded as limiting. According to an exemplary embodiment, a vehicle of the present disclosure includes a control arm and steering knuckle assembly with an independent suspension that includes a control arm, a steering knuckle, and a ball joint coupling assembly coupling the control arm to the steering knuckle. The ball joint coupling assembly includes a steering sensor and various components that facilitate monitoring steering angle motion of the steering knuckle, and therefore a wheel hub and wheel coupled thereto, in every position of the suspension. Specifically, the steering monitoring is independent of and not directly affected by relative movement of the steering knuckle and the control arm during articulation of the suspension between full joust and full rebound. Overall Vehicle According to the exemplary embodiment shown inFIGS.1-3, a machine or vehicle, shown as vehicle10, includes a chassis, shown as frame12; a body assembly, shown as body20, coupled to the frame12and having an occupant portion or section, shown as cab30; operator input and output devices, shown as operator interface40, that are disposed within the cab30; a drivetrain, shown as driveline50, coupled to the frame12and at least partially disposed under the body20; a vehicle steering and suspension assembly, shown as steering and suspension system100, configured to facilitate steering the vehicle10; and a vehicle control system, shown as control system300, coupled to the operator interface40, the driveline50, and the steering and suspension system100. In other embodiments, the vehicle10includes more or fewer components. According to an exemplary embodiment, the vehicle10is an off-road machine or vehicle. In some embodiments, the off-road machine or vehicle is an agricultural machine or vehicle such as a tractor, a telehandler, a front loader, a combine harvester, a grape harvester, a forage harvester, a sprayer vehicle, a speedrower, and/or another type of agricultural machine or vehicle. In some embodiments, the off-road machine or vehicle is a construction machine or vehicle such as a skid steer loader, an excavator, a backhoe loader, a wheel loader, a bulldozer, a telehandler, a motor grader, and/or another type of construction machine or vehicle. In some embodiments, the vehicle10includes one or more attached implements and/or trailed implements such as a front mounted mower, a rear mounted mower, a trailed mower, a tedder, a rake, a baler, a plough, a cultivator, a rotavator, a tiller, a harvester, and/or another type of attached implement or trailed implement. According to an exemplary embodiment, the cab30is configured to provide seating for an operator (e.g., a driver, etc.) of the vehicle10. In some embodiments, the cab30is configured to provide seating for one or more passengers of the vehicle10. According to an exemplary embodiment, the operator interface40is configured to provide an operator with the ability to control one or more functions of and/or provide commands to the vehicle10and the components thereof (e.g., turn on, turn off, drive, turn, brake, engage various operating modes, raise/lower an implement, etc.). The operator interface40may include one or more displays and one or more input devices. The one or more displays may be or include a touchscreen, a LCD display, a LED display, a speedometer, gauges, warning lights, etc. The one or more input device may be or include a steering wheel, a joystick, buttons, switches, knobs, levers, an accelerator pedal, a brake pedal, etc. According to an exemplary embodiment, the driveline50is configured to propel the vehicle10. As shown inFIG.3, the driveline50includes a primary driver, shown as prime mover52, and an energy storage device, shown as energy storage54. In some embodiments, the driveline50is a conventional driveline whereby the prime mover52is an internal combustion engine and the energy storage54is a fuel tank. The internal combustion engine may be a spark-ignition internal combustion engine or a compression-ignition internal combustion engine that may use any suitable fuel type (e.g., diesel, ethanol, gasoline, natural gas, propane, etc.). In some embodiments, the driveline50is an electric driveline whereby the prime mover52is an electric motor and the energy storage54is a battery system. In some embodiments, the driveline50is a fuel cell electric driveline whereby the prime mover52is an electric motor and the energy storage54is a fuel cell (e.g., that stores hydrogen, that produces electricity from the hydrogen, etc.). In some embodiments, the driveline50is a hybrid driveline whereby (i) the prime mover52includes an internal combustion engine and an electric motor/generator and (ii) the energy storage54includes a fuel tank and/or a battery system. As shown inFIG.3, the driveline50includes a transmission device (e.g., a gearbox, a continuous variable transmission (“CVT”), etc.), shown as transmission56, coupled to the prime mover52; a power divider, shown as transfer case58, coupled to the transmission56; a first tractive assembly, shown as front tractive assembly70, coupled to a first output of the transfer case58, shown as front output60; and a second tractive assembly, shown as rear tractive assembly80, coupled to a second output of the transfer case58, shown as rear output62. According to an exemplary embodiment, the transmission56has a variety of configurations (e.g., gear ratios, etc.) and provides different output speeds relative to a mechanical input received thereby from the prime mover52. In some embodiments (e.g., in electric driveline configurations, in hybrid driveline configurations, etc.), the driveline50does not include the transmission56. In such embodiments, the prime mover52may be directly coupled to the transfer case58. According to an exemplary embodiment, the transfer case58is configured to facilitate driving both the front tractive assembly70and the rear tractive assembly80with the prime mover52to facilitate front and rear drive (e.g., an all-wheel-drive vehicle, a four-wheel-drive vehicle, etc.). In some embodiments, the transfer case58facilitates selectively engaging rear drive only, front drive only, and both front and rear drive simultaneously. In some embodiments, the transmission56and/or the transfer case58facilitate selectively disengaging the front tractive assembly70and the rear tractive assembly80from the prime mover52(e.g., to permit free movement of the front tractive assembly70and the rear tractive assembly80in a neutral mode of operation). In some embodiments, the driveline50does not include the transfer case58. In such embodiments, the prime mover52or the transmission56may directly drive the front tractive assembly70(i.e., a front-wheel-drive vehicle) or the rear tractive assembly80(i.e., a rear-wheel-drive vehicle). As shown inFIGS.1and3, the front tractive assembly70includes a first drive shaft, shown as front drive shaft72, coupled to the front output60of the transfer case58; a first differential, shown as front differential74, coupled to the front drive shaft72; a first axle, shown front axle76, coupled to the front differential74; and a first pair of tractive elements, shown as front tractive elements78, coupled to the front axle76. In some embodiments, the front tractive assembly70includes a plurality of front axles76. In some embodiments, the front tractive assembly70does not include the front drive shaft72or the front differential74(e.g., a rear-wheel-drive vehicle). In some embodiments, the front drive shaft72is directly coupled to the transmission56(e.g., in a front-wheel-drive vehicle, in embodiments where the driveline50does not include the transfer case58, etc.) or the prime mover52(e.g., in a front-wheel-drive vehicle, in embodiments where the driveline50does not include the transfer case58or the transmission56, etc.). The front axle76may include one or more components. As shown inFIGS.1and3, the rear tractive assembly80includes a second drive shaft, shown as rear drive shaft82, coupled to the rear output62of the transfer case58; a second differential, shown as rear differential84, coupled to the rear drive shaft82; a second axle, shown rear axle86, coupled to the rear differential84; and a second pair of tractive elements, shown as rear tractive elements88, coupled to the rear axle86. In some embodiments, the rear tractive assembly80includes a plurality of rear axles86. In some embodiments, the rear tractive assembly80does not include the rear drive shaft82or the rear differential84(e.g., a front-wheel-drive vehicle). In some embodiments, the rear drive shaft82is directly coupled to the transmission56(e.g., in a rear-wheel-drive vehicle, in embodiments where the driveline50does not include the transfer case58, etc.) or the prime mover52(e.g., in a rear-wheel-drive vehicle, in embodiments where the driveline50does not include the transfer case58or the transmission56, etc.). The rear axle86may include one or more components. According to the exemplary embodiment shown inFIG.1, the front tractive elements78and the rear tractive elements88are structured as wheels. In other embodiments, the front tractive elements78and the rear tractive elements88are otherwise structured (e.g., tracks, etc.). In some embodiments, the front tractive elements78and the rear tractive elements88are both steerable. In other embodiments, only one of the front tractive elements78or the rear tractive elements88is steerable. In still other embodiments, both the front tractive elements78and the rear tractive elements88are fixed and not steerable. In some embodiments, the driveline50includes a plurality of prime movers52. By way of example, the driveline50may include a first prime mover52that drives the front tractive assembly70and a second prime mover52that drives the rear tractive assembly80. By way of another example, the driveline50may include a first prime mover52that drives a first one of the front tractive elements78, a second prime mover52that drives a second one of the front tractive elements78, a third prime mover52that drives a first one of the rear tractive elements88, and/or a fourth prime mover52that drives a second one of the rear tractive elements88. By way of still another example, the driveline50may include a first prime mover that drives the front tractive assembly70, a second prime mover52that drives a first one of the rear tractive elements88, and a third prime mover52that drives a second one of the rear tractive elements88. By way of yet another example, the driveline50may include a first prime mover that drives the rear tractive assembly80, a second prime mover52that drives a first one of the front tractive elements78, and a third prime mover52that drives a second one of the front tractive elements78. In such embodiments, the driveline50may not include the transmission56or the transfer case58. As shown inFIG.3, the driveline50includes a power-take-off (“PTO”), shown as PTO 90. While the PTO 90 is shown as being an output of the transmission56, in other embodiments the PTO 90 may be an output of the prime mover52, the transmission56, and/or the transfer case58. According to an exemplary embodiment, the PTO 90 is configured to facilitate driving an attached implement and/or a trailed implement of the vehicle10. In some embodiments, the driveline50includes a PTO clutch positioned to selectively decouple the driveline50from the attached implement and/or the trailed implement of the vehicle10(e.g., so that the attached implement and/or the trailed implement is only operated when desired, etc.). According to an exemplary embodiment, the vehicle10includes a braking system that includes one or more brakes (e.g., disc brakes, drum brakes, in-board brakes, axle brakes, etc.) positioned to facilitate selectively braking (i) one or more components of the driveline50and/or (ii) one or more components of a trailed implement. In some embodiments, the one or more brakes include (i) one or more front brakes positioned to facilitate braking one or more components of the front tractive assembly70and (ii) one or more rear brakes positioned to facilitate braking one or more components of the rear tractive assembly80. In some embodiments, the one or more brakes include only the one or more front brakes. In some embodiments, the one or more brakes include only the one or more rear brakes. In some embodiments, the one or more front brakes include two front brakes, one positioned to facilitate braking each of the front tractive elements78. In some embodiments, the one or more front brakes include at least one front brake positioned to facilitate braking the front axle76. In some embodiments, the one or more rear brakes include two rear brakes, one positioned to facilitate braking each of the rear tractive elements88. In some embodiments, the one or more rear brakes include at least one rear brake positioned to facilitate braking the rear axle86. Accordingly, the braking system may include one or more brakes to facilitate braking the front axle76, the front tractive elements78, the rear axle86, and/or the rear tractive elements88. In some embodiments, the one or more brakes additionally include one or more trailer brakes of a trailed implement attached to the vehicle10. The trailer brakes are positioned to facilitate selectively braking one or more axles and/or one more tractive elements (e.g., wheels, etc.) of the trailed implement. Steering and Suspension System As shown inFIG.4, the steering and suspension system100includes an operator input device, shown as steering wheel102; a gearing assembly, shown as steering box104, coupled to the steering wheel102(e.g., by a steering column, etc.); a linkage assembly, shown as steering linkage assembly106, coupled to the steering box104and including a plurality of linkages (e.g., tie rods, knuckle arms, a pitman arm, a center linkage, etc.); and a pair of control arm and steering knuckle assemblies, shown as control arm and steering knuckle assemblies108, coupled to the steering linkage assembly106. According to an exemplary embodiment, manipulating the steering wheel102facilitates turning components (e.g., steering knuckles, wheel hubs, etc.) of the control arm and steering knuckle assemblies108to steer and turn the vehicle10. In some embodiments, the vehicle10does not include the steering wheel102, rather the operator input device is or includes a joystick, a steering handlebar, or still another input device that allows an operator of the vehicle10to control steering thereof. According to an exemplary embodiment, the control arm and steering knuckle assemblies108facilitate implementing an independent front suspension that provides independent articulation of opposing ends of the front axle76. As shown inFIGS.4-8, each of the control arm and steering knuckle assemblies108includes a tractive element spindle or steering knuckle, shown as steering knuckle110; a first control arm, shown as lower control arm130; a second control arm, shown as upper control arm140; a suspension assembly, shown as coilover150; a first coupler, shown as lower coupler160; a second coupler, shown as intermediate coupler170; and a third coupler, shown as upper coupler180. According to an exemplary embodiment, the steering knuckle110is configured to couple to a respective wheel hub and tractive element of the vehicle10. As shown inFIGS.4-8, the steering knuckle110includes a main body, shown as knuckle body112, having (i) a first portion, shown as lower knuckle arm114, protruding or extending from a lower end of the knuckle body112, (ii) a second portion, shown as intermediate knuckle arm116, protruding or extending from the knuckle body112between the lower end and an upper end thereof, and (iii) a third portion, shown as upper knuckle arm118, protruding or extending from the upper end of the knuckle body112. According to an exemplary embodiment, the knuckle body112is configured to interface with a respective front tractive element78of the vehicle10. In some embodiments (e.g., a four-wheel-drive embodiment, a front-wheel-drive embodiment, etc.), the driveline50is configured to drive the wheel hubs coupled to the steering knuckles110to drive the front tractive elements78. According to an exemplary embodiment, the lower knuckle arm114defines a first interface, passage, or slot that receives the lower coupler160. In another embodiment, the lower coupler160is integrally formed with the lower knuckle arm114. According to an exemplary embodiment, the lower coupler160is or includes a ball joint. As shown inFIGS.4and6, the intermediate knuckle arm116defines a second interface or passage, shown as intermediate knuckle slot120, that receives the intermediate coupler170. In another embodiment, the intermediate coupler170is integrally formed with the intermediate knuckle arm116. According to the exemplary embodiment shown inFIG.6, the intermediate coupler170is a ball joint. As shown inFIGS.4-8, the upper knuckle arm118defines a third interface or passage, shown as upper knuckle slot122, that receives a lower portion (e.g., the tapered shaft230of the ball joint210) of the upper coupler180. According to the exemplary embodiment shown inFIGS.5-8, the upper coupler180is configured as a ball joint coupling assembly. As shown inFIG.4, the lower control arm130has a first end, shown as frame end132, pivotally coupled to the frame12and an opposing second end, shown as knuckle end134, coupled to the lower knuckle arm114of the steering knuckle110by the lower coupler160. As shown inFIGS.4and5, an end of a component of the steering linkage assembly106(e.g., a tire rod, etc.) is coupled to the intermediate knuckle arm116of the steering knuckle110by the intermediate coupler170. Such coupling between the steering linkage assembly106and the steering knuckle110facilitates turning the steering knuckle110using the steering wheel102. As shown inFIGS.4-8, the upper control arm140has a first end, shown as frame end142, pivotally coupled to the frame12and an opposing second end, shown as knuckle end144, coupled to the upper knuckle arm118of the steering knuckle110by the upper coupler180. As shown inFIG.4, each of the coilovers150extends from a mounting location on the frame12to the lower control arm130. Each of the coilovers150includes a damper152and a coil spring154disposed around and along the damper. In other embodiments, other suitable suspension arrangements can be used. As shown inFIGS.5-8, the knuckle end144of the upper control arm140has an upper, flat surface, shown as upper mounting surface146, and a lower, flat surface, shown as lower mounting surface147. The knuckle end144of the upper control arm140defines an interface or passage, shown as upper control arm slot148, that extends through the knuckle end144from the upper mounting surface146to the lower mounting surface147, and that receives a portion (e.g., the ball joint housing182and the ball220of the ball joint210) of the upper coupler180. As shown inFIGS.5-14, the upper coupler180includes various components, including a housing, shown as ball joint housing182; an upper support, shown as mounting plate200; a pivoting joint, shown as ball joint210; a sensor, shown as steering sensor240; and a cover, shown as mounting plate cover270. As shown inFIGS.8,11,13, and14, the upper coupler180defines a first longitudinal center axis, shown as longitudinal axis280. As shown inFIGS.8-12and14, the ball joint housing182has a first upper portion, shown as insert184, and a second lower portion, shown as lip186, extending around the lower periphery of the insert184. The insert184defines a recess, shown as ball pocket188, extending from the lower end of the insert184partially towards the upper end of the insert184; a first aperture or passageway, shown as sensor passageway190, extending through a center of the upper end of the insert184and connecting to the ball pocket188; and a plurality of apertures, shown as plate coupling apertures192, extending from the upper end of the insert184and at least partially through the body thereof, and disposed radially outward of and about the sensor passageway190. As shown inFIGS.8,9, and11, the mounting plate200has a first portion, shown as center portion202, with second portions, shown as flanges204, extending laterally outward from opposing sides of the center portion202. The center portion202defines (i) a second aperture or passageway, shown as sensor passageway206, at a center thereof and (ii) a plurality of slots, shown as insert coupling slots208extending therethrough, and disposed radially outward of and about the sensor passageway206. Each of the flanges204defines a coupling aperture, shown as lid coupling aperture209. As shown inFIGS.8,9, and11, the insert184of the ball joint housing182is insertable into the upper control arm slot148positioned at the knuckle end144of the upper control arm140such that the lip186of the ball joint housing182engages with the lower mounting surface147of the knuckle end144of the upper control arm140. The mounting plate200is positionable along the upper mounting surface146of the knuckle end144of the upper control arm140above the upper control arm slot148and the ball joint housing182, with the flanges extending outside of the upper control arm slot148and engaging with the upper mounting surface146of the knuckle end144of the upper control arm140. The insert coupling slots208of the mounting plate200align with the plate coupling apertures192of the insert184of the ball joint housing182such that fasteners (e.g., screws, bolts, etc.) may be received by the insert coupling slots208and the plate coupling apertures192to couple the mounting plate200to the ball joint housing182. Such coupling of the mounting plate200to the insert184(i) aligns the sensor passageway206of the mounting plate200and the sensor passageway190of the insert184and (ii) causes the lip186of the insert184and the flanges204of the mounting plate200to engage with the lower mounting surface147and the upper mounting surface146, respectively, of the knuckle end144of the upper control arm140to secure the upper end of the upper coupler180to the upper control arm140. As shown inFIGS.5-8and11-14, the ball joint210has an upper portion, shown as ball220, and a lower portion, shown as tapered shaft230, extending from a lower end of the ball220. The ball220defines a recess, shown as conical recess222, that has an opening positioned at the upper end of the ball220, extends into and tapers along the body of the ball220, and terminates with a pocket, shown as shaft head pocket224. According to an exemplary embodiment, the shaft head pocket224is positioned at or substantially positioned at a center point of the ball220. According to an exemplary embodiment, the shaft head pocket224has a hex shape (e.g., like a hex or socket screw). In other embodiments, the shaft head pocket224has another suitable shape. As shown inFIGS.5-8,11, and14, the ball pocket188of the ball joint housing182receives and retains the ball220of the ball joint210such that the ball220is at least partially disposed within the upper control arm slot148. As shown inFIGS.6and8, the upper knuckle slot122of the upper knuckle arm118of the steering knuckle110receives the tapered shaft230of the ball joint210. The free end of the tapered shaft230may engage with a fastener (e.g., a nut, etc.) on the bottom side of the upper knuckle arm118to secure the tapered shaft230within the upper knuckle slot122of the upper knuckle arm118. In another embodiment, the ball joint210is integrally formed with the steering knuckle110. Accordingly, the ball joint210is configured to pivotably couple the steering knuckle110to the upper control arm140. According to an exemplary embodiment, the ball220is configured to rotate within the ball pocket188about the longitudinal axis280(e.g., in response to the steering knuckle110turning via an input to the steering wheel102). As shown inFIG.14, the ball220is configured to pivot within the ball pocket188such that (i) the tapered shaft230swings or articulates laterally relative to the longitudinal axis280and (ii) a second longitudinal, center axis, shown as longitudinal axis290, of the ball joint210is angled relative to the longitudinal axis280of the upper coupler180(e.g., in response to jounce and rebound of the coilover150). As shown inFIGS.8,11, and12, the steering sensor240includes (i) a main housing or head, shown as sensor head242, having a port, shown as connector port244, extending radially outward therefrom and (ii) a sensor drive assembly, shown as sensor drive assembly246, coupled to and extending downward from the sensor head242. According to an exemplary embodiment, the connector port244facilitates connecting the steering sensor240to the control system300to facilitate data transfer therebetween. As shown inFIGS.8,11, and12, the sensor head242is coupled (e.g., fastened, using screws, using bolts, etc.) to the top surface of center portion202of the mounting plate200and over the sensor passageway206such that the sensor drive assembly246extends (i) through (a) the sensor passageway206of the mounting plate200and (b) the sensor passageway190of the ball joint housing182and (ii) into (a) the ball pocket188of the ball joint housing182and (b) the conical recess222of the ball220of the ball joint210. As shown inFIGS.11and12, the sensor drive assembly246includes a bushing, shown as drive bushing248, positioned within the sensor passageway206of the mounting plate200and the sensor passageway190of the ball joint housing182. The drive bushing248defines a first chamber, shown as upper chamber250, positioned at a first end of the drive bushing248and a second chamber, shown as lower chamber252, positioned at an opposing second end of the drive bushing248. The sensor drive assembly246additionally includes a retainer, shown as shaft retaining ring256, disposed within the lower chamber252of the drive bushing248; a sensor drive connector, shown as sensor D drive258, disposed within the upper chamber250of the drive bushing248, and extending between the drive bushing248and the sensor head242; and a shaft, shown as driveshaft260, having a first end, shown as upper head262, disposed within the lower chamber252of the drive bushing248and an opposing second end, shown as lower head264, disposed within the shaft head pocket224of the conical recess222of the ball220. As shown inFIG.12, the shaft retaining ring256is positioned to engage with the upper head262of the driveshaft260to retain the upper head262of the driveshaft260within the lower chamber252of the drive bushing248. The shaft retaining ring256is at a specific position within the lower chamber252such that a gap, shown as wear space254, is formed between the upper wall of the lower chamber252and the upper head262of the driveshaft260. The clearance provided by the wear space254is configured to accommodate wear of the ball joint210over time. As shown inFIG.13, the lower head264of the driveshaft260is disposed within the shaft head pocket224of the conical recess222of the ball220such that a center of the lower head264is coincident with or substantially coincident with a center of the ball220defined at the intersection of the longitudinal axis280and a center, lateral axis, shown as lateral axis282, of the ball220. As shown inFIG.15, the driveshaft260is configured as a hex shaft where the upper head262and the lower head264are hex-shaped heads (e.g., like a ball-end hex key). According to an exemplary embodiment, the insert coupling slots208of the mounting plate200facilitate rotating the mounting plate200and, therefore, the driveshaft260about the longitudinal axis280relative to the ball joint housing182and the ball joint210during installation to allow for minor adjustments such that the lower head264of the driveshaft260is properly received by and sits within the shaft head pocket224of the conical recess222of the ball220. According to an exemplary embodiment, the shape of the shaft head pocket224, the shape of the lower chamber252, the shape of the upper head262, and the shape of the lower head264(i) prevent relative movement/rotation between the drive bushing248, the ball220, and the driveshaft260about the longitudinal axis280, but (ii) permit pivoting/articulating movement of the ball220(see, e.g.,FIG.14) relative to the longitudinal axis280and the lower head264of the driveshaft260. Accordingly, the steering sensor240is configured to facilitate acquiring steering data regarding turning of the steering knuckle110as the ball joint210and the sensor drive assembly246turn therewith, while not being affected by the pivoting motion or articulation of the ball joint210during jounce and rebound of the coilovers150. As shown inFIG.14, the conical recess222accommodates a range of articulation of the ball joint210relative to the driveshaft260and the longitudinal axis280up to an angle θ in each direction (i.e., −θ to +θ). According to an exemplary embodiment, the angle θ is dependent on the amount of suspension travel of the coilovers150and, thereby, movement of the lower control arm130and the steering knuckle110relative to the upper control arm140. In one embodiment, the angle θ is at least 10 degrees. In another embodiment, the angle θ is at least 15 degrees. In still another embodiment, the angle θ is at least 20 degrees. In yet another embodiment, the angle θ is at least 25 degrees. As shown inFIGS.5,8, and11, the mounting plate cover270extends over the mounting plate200and the upper control arm slot148at the knuckle end144of the upper control arm140, enclosing the upper end of the upper coupler180(e.g., preventing dirt, debris, etc. from entering into the upper control arm slot148or components of the upper coupler180). According to an exemplary embodiment, the mounting plate cover270is coupled (e.g., secured, attached, etc.) to the mounting plate200using fasteners that engage with the lid coupling apertures209of the mounting plate200. According to the exemplary embodiment shown inFIG.16, the control system300for the vehicle10includes a controller310. In one embodiment, the controller310is configured to selectively engage, selectively disengage, control, or otherwise communicate with components of the vehicle10. As shown inFIG.16, the controller310is coupled to (e.g., communicably coupled to) the operator interface40, the driveline50, and the steering sensors240. By way of example, the controller310may send and receive signals (e.g., control signals) with the operator interface40, the driveline50, and/or the steering sensors240. The controller310may be implemented as a general-purpose processor, an application specific integrated circuit (“ASIC”), one or more field programmable gate arrays (“FPGAs”), a digital-signal-processor (“DSP”), circuits containing one or more processing components, circuitry for supporting a microprocessor, a group of processing components, or other suitable electronic processing components. According to the exemplary embodiment shown inFIG.21, the controller310includes a processing circuit312and a memory314. The processing circuit312may include an ASIC, one or more FPGAs, a DSP, circuits containing one or more processing components, circuitry for supporting a microprocessor, a group of processing components, or other suitable electronic processing components. In some embodiments, the processing circuit312is configured to execute computer code stored in the memory314to facilitate the activities described herein. The memory314may be any volatile or non-volatile computer-readable storage medium capable of storing data or computer code relating to the activities described herein. According to an exemplary embodiment, the memory314includes computer code modules (e.g., executable code, object code, source code, script code, machine code, etc.) configured for execution by the processing circuit312. In some embodiments, the controller310may represent a collection of processing devices. In such cases, the processing circuit312represents the collective processors of the devices, and the memory314represents the collective storage devices of the devices. In some embodiments, the controller310is configured to receive the steering data from the steering sensors240. The controller310may be configured to utilize the steering data to accurately monitor the steering position of the steering knuckle110and, thereby, the wheel hubs and the front tractive elements78. The controller310may use the steering data in controlling front suspension controls, cab suspension controls, and control other means to improve ride quality and vehicle operability. In some embodiments, the controller310is configured to provide feedback to the operator of the vehicle10via the operator interface40regarding the steering position of the front tractive elements78. In some embodiments, the controller310is configured to utilize the steering data for guidance purposes. By way of example, the controller310may function as a guidance system and use the steering data to facilitate autonomous driving of the vehicle10or provide guidance assistance. It should be understood that the description of the control arm and steering knuckle assemblies108as applying to the front axle76of the vehicle10is for example purposes only. The control arm and steering knuckle assemblies108can similarly be applied to a steerable rear axle86of the vehicle10. As utilized herein with respect to numerical ranges, the terms “approximately,” “about,” “substantially,” and similar terms generally mean +/−10% of the disclosed values, unless specified otherwise. As utilized herein with respect to structural features (e.g., to describe shape, size, orientation, direction, relative position, etc.), the terms “approximately,” “about,” “substantially,” and similar terms are meant to cover minor variations in structure that may result from, for example, the manufacturing or assembly process and are intended to have a broad meaning in harmony with the common and accepted usage by those of ordinary skill in the art to which the subject matter of this disclosure pertains. Accordingly, these terms should be interpreted as indicating that insubstantial or inconsequential modifications or alterations of the subject matter described and claimed are considered to be within the scope of the disclosure as recited in the appended claims. It should be noted that the term “exemplary” and variations thereof, as used herein to describe various embodiments, are intended to indicate that such embodiments are possible examples, representations, or illustrations of possible embodiments (and such terms are not intended to connote that such embodiments are necessarily extraordinary or superlative examples). The term “coupled” and variations thereof, as used herein, means the joining of two members directly or indirectly to one another. Such joining may be stationary (e.g., permanent or fixed) or moveable (e.g., removable or releasable). Such joining may be achieved with the two members coupled directly to each other, with the two members coupled to each other using a separate intervening member and any additional intermediate members coupled with one another, or with the two members coupled to each other using an intervening member that is integrally formed as a single unitary body with one of the two members. If “coupled” or variations thereof are modified by an additional term (e.g., directly coupled), the generic definition of “coupled” provided above is modified by the plain language meaning of the additional term (e.g., “directly coupled” means the joining of two members without any separate intervening member), resulting in a narrower definition than the generic definition of “coupled” provided above. Such coupling may be mechanical, electrical, or fluidic. References herein to the positions of elements (e.g., “top,” “bottom,” “above,” “below”) are merely used to describe the orientation of various elements in the figures. It should be noted that the orientation of various elements may differ according to other exemplary embodiments, and that such variations are intended to be encompassed by the present disclosure. The hardware and data processing components used to implement the various processes, operations, illustrative logics, logical blocks, modules, and circuits described in connection with the embodiments disclosed herein may be implemented or performed with a general purpose single- or multi-chip processor, a digital signal processor (DSP), an application specific integrated circuit (ASIC), a field programmable gate array (FPGA), or other programmable logic device, discrete gate or transistor logic, discrete hardware components, or any combination thereof designed to perform the functions described herein. A general purpose processor may be a microprocessor, or, any conventional processor, controller, microcontroller, or state machine. A processor also may be implemented as a combination of computing devices, such as a combination of a DSP and a microprocessor, a plurality of microprocessors, one or more microprocessors in conjunction with a DSP core, or any other such configuration. In some embodiments, particular processes and methods may be performed by circuitry that is specific to a given function. The memory (e.g., memory, memory unit, storage device) may include one or more devices (e.g., RAM, ROM, Flash memory, hard disk storage) for storing data and/or computer code for completing or facilitating the various processes, layers and modules described in the present disclosure. The memory may be or include volatile memory or non-volatile memory, and may include database components, object code components, script components, or any other type of information structure for supporting the various activities and information structures described in the present disclosure. According to an exemplary embodiment, the memory is communicably connected to the processor via a processing circuit and includes computer code for executing (e.g., by the processing circuit or the processor) the one or more processes described herein. The present disclosure contemplates methods, systems, and program products on any machine-readable media for accomplishing various operations. The embodiments of the present disclosure may be implemented using existing computer processors, or by a special purpose computer processor for an appropriate system, incorporated for this or another purpose, or by a hardwired system. Embodiments within the scope of the present disclosure include program products comprising machine-readable media for carrying or having machine-executable instructions or data structures stored thereon. Such machine-readable media can be any available media that can be accessed by a general purpose or special purpose computer or other machine with a processor. By way of example, such machine-readable media can comprise RAM, ROM, EPROM, EEPROM, or other optical disk storage, magnetic disk storage or other magnetic storage devices, or any other medium which can be used to carry or store desired program code in the form of machine-executable instructions or data structures and which can be accessed by a general purpose or special purpose computer or other machine with a processor. Combinations of the above are also included within the scope of machine-readable media. Machine-executable instructions include, for example, instructions and data which cause a general purpose computer, special purpose computer, or special purpose processing machines to perform a certain function or group of functions. Although the figures and description may illustrate a specific order of method steps, the order of such steps may differ from what is depicted and described, unless specified differently above. Also, two or more steps may be performed concurrently or with partial concurrence, unless specified differently above. Such variation may depend, for example, on the software and hardware systems chosen and on designer choice. All such variations are within the scope of the disclosure. Likewise, software implementations of the described methods could be accomplished with standard programming techniques with rule-based logic and other logic to accomplish the various connection steps, processing steps, comparison steps, and decision steps. It is important to note that the construction and arrangement of the vehicle10and the systems and components thereof (e.g., the driveline50, the steering and suspension system100, the control system300, etc.) as shown in the various exemplary embodiments is illustrative only. Additionally, any element disclosed in one embodiment may be incorporated or utilized with any other embodiment disclosed herein. | 41,249 |
11859659 | DETAILED DESCRIPTION FIG.1depicts an example of a compliant foil thrust bearing comprising a compliant foil thrust bearing subassembly100and a thrust plate200. The compliant foil thrust bearing subassembly100comprises a fluid plate110, a force transfer plate120and a spring plate130. As shown inFIG.1, the force transfer plate120and the spring plate130are at least substantially planar. Whereas the fluid foil plate110may comprise out-of-plane features, the force transfer plate120and spring plate130may be planar. In the example shown, the force transfer plate120and spring plate130are formed with a fixed cross-sectional profile. The provision of planar and axially uniform plates of a compliant foil thrust bearing offers significantly simplified manufacturing. In particular, the plates may be formed as cut-outs from sheet metal. In the example shown, the plates of the compliant foil thrust bearing subassembly100are arranged to share a common axis running through their centers. In the example ofFIG.1, this common axis extends vertically through the plate centres. The thrust plate200is arranged to share the common axis. The fluid foil elements114may be evenly distributed around the circumference of the annular mating ring112. The fluid foil elements114may be formed in radially opposing pairs, as shown inFIG.2. Such a symmetrical distribution, especially in combination with the same in respect of correspondingly distributed force transfer elements124and deflection elements134, facilitates uniform circumferential load distribution, helping safeguard against any localized stress concentrations, which would otherwise increase losses and wear. FIG.2depicts a fluid plate110suitable for receiving a rotating thrust disk. The fluid plate110comprises an annular mating ring112and fluid foil elements114disposed radially inwardly from the fluid plate mating ring112. The fluid foil elements114are arranged to provide axial undulation in a circumferential direction. This circumferential undulation is responsible for generating a fluid film upon rotation of an adjacent thrust disk, this fluid film for axially supporting the rotating thrust disk. Axial force imparted by the rotating thrust disk onto the top side of the fluid plate is non-constant during both startup and normal operation. Such load variation is accommodated in thrust bearings by the provision of compliance, i.e. resilience in the form of an underlying spring mechanism coupled to the fluid plate underside. The fluid plate110may comprise notches118provided on the radially outer edge thereof for receiving a tab. Alternatively, the fluid plate110may comprise tabs, not shown, to be received by corresponding notches provided on the radially outer edges of one or more underlying plates. This notch and tab arrangement facilitates retention between one or more plates of the thrust bearing subassembly100. FIG.3depicts a force transfer plate120comprising an annular mating ring122and force transfer elements124disposed radially inwardly from the annular mating ring122. The force transfer elements124may extend radially inwards from the annular mating ring122. As shall be described in greater detail below, each force transfer element124may comprise through-holes126. As shown in this example, each force transfer element124may comprise a grid forming open126aand/or closed126bthrough-holes. As shown, the force transfer plate120may comprise notches128provided on the radially outer edge thereof for receiving a tab. FIG.4depicts a spring plate130comprising an annular mating ring132and deflection elements134disposed radially inwardly from the annular mating ring132. The deflection elements134may extend radially inwards from the annular mating ring132. Force transfer plate120and spring plate130of thrust bearing subassembly100together facilitate the axial transmission of axial load generated by the fluid foil elements114of fluid plate110. In particular, each of the circumferentially-spaced fluid foil elements114may be supported by a corresponding pair of axially overlapping force transfer elements124and deflection elements134. As shown inFIG.7a, the overlapping pairs of force transfer elements and deflection elements may comprise offset circumferential and/or radial portions, i.e. the offset circumferential and/or radial portions of the force transfer elements are offset, or non-overlapping, from those of the deflection elements. In the specific example ofFIG.7a, the force transfer elements124comprise interconnected circumferential and radial portions, and the corresponding deflection elements134comprise interconnected radial portions. The radial portions of the force transfer elements124are circumferentially offset with respect to the radial portions of the deflection elements134, and circumferential portions of the force transfer elements124are arranged to contact the radial portions of the deflection elements134. This overlapping contact facilitates transmission of axial force through the force transfer and spring plates120and130of subassembly100at circumferentially spaced regions thereby to support the axial load imparted by the circumferentially spaced fluid foil elements114of fluid plate110. It will be recognized that other forms of overlapping contact between the force transfer elements124and deflection elements134are possible. The force transfer elements124and deflection elements134may be circumferentially separate, thereby facilitating the provision of circumferentially spaced axial support channels within the thrust bearing upon stacking. As shall be described in greater detail below, each deflection element134may comprise radially extending portions135. These radially-extending portions may be arranged to overlap with axial through-holes126provided in the force transfer elements124, which axial through-holes126may be arranged to overlie the radially extending portions135. This facilitates resilient deflection of the deflection elements. Each deflection element134and/or each force transfer element124may comprise a grid forming open and/or closed through-holes126,136. In the example shown, only closed through-holes are present in the deflection elements124, though it will be recognized that further open through-holes could be provided, as shown in respect of the force transfer elements124of the force transfer plate120. The spring plate130may comprise notches138providing on the radially outer edge thereof for receiving a tab from an overlying or underlying plate. In the example shown, the spring plate130comprises tabs138. The tabs138are arranged to wrap into the notches of the overlying force transfer plate120and fluid plate110, securely retaining the plates of the thrust bearing subassembly100together. Alternatively the fluid plate110could comprise tabs arranged to wrap into notches of the force transfer plate and the spring plate. FIG.5depicts a thrust plate200comprising an annular mating surface242and a recessed surface244disposed radially inwardly from the annular mating surface242. The recessed surface244is axially recessed from the annular mating surface242. In the example shown, the annular mating surface242extends axially beyond the recessed surface244. Thus the thickness of the thrust plate140is radially non-uniform, with the thickness in the radially outer portion comprising the annular mating surface242greater than that of the radially inner portion comprising the recessed surface244. This contrasts with prior art arrangements in which a substantially flat thrust plate140is provided. The provision of the axially recessed surface244presents the opportunity for overlying deflection elements134to extend towards the thrust plate140and axially beyond the annular mating surface242. The facilitation of such axial deflection of the deflection elements134affords the provision of compliance by the spring plate. In this way the deflection elements134might be considered to act as radially inwardly extending cantilevers. Each fluid foil element114may be axially supported by underlying pairs of overlapping force transfer elements124and deflection elements134. Thus load imparted via the fluid film from a rotating thrust disk, not shown, may be transmitted via the fluid foil element114, through a corresponding force transfer element124and to a corresponding deflection element134, which may be caused to resiliently deflect in an axial direction towards the thrust plate140and into the recessed space formed by virtue of the recess provided in the thrust plate. In the example shown, the thrust plate140comprises supports246disposed radially inwardly from the annular mating surface242. The supports may be provided with the same height as that of the annular mating surface, i.e. the supports may terminate at an axial position that lies substantially within a plane defined by the annular mating surface242. The supports246may comprise a convex surface for contacting the overlying deflection elements134. The provision of such a convex surface facilitates bending of the deflection elements134around one or both sides of each support. The depth of the recess244and/or supports246serve to limit deflection of the deflection elements134in the axial direction. In this case the deflection elements134are arranged to deflect on one or both sides of each support246. For example, in the case a support246is provided that is radially outside a radially inner end of a deflection element134, the deflection element may bend on both radially outer and inner sides of the support246, whereas in the case a support246is disposed substantially at the radially inner end of the a deflection element134, the deflection element134may bend on the radially outer side of the support246. The axially recessed surface244may serve to limit deflection of the deflection elements134by way of contact therebetween following sufficient deflection of the deflection elements134. In the example shown, the supports246are annular and co-centric. However, the supports246may take other forms. For example, the supports246may extend in an annular direction underneath each deflection element134, optionally with annular discontinuities existing between the supports. Or the supports246take the form of other shapes such as rods. The provision of annular supports simplifies manufacturing. There may be provided a support246arranged to underlie each deflection element124. The one or more supports246may be arranged such that they are disposed radially outside of the radially inner edge of each deflection element134. The one or more supports246may be disposed radially inwardly of the mating surface132of the spring plate130and radially outwardly of the radially inner edge of the spring plate130. As shown inFIG.7a, the force transfer elements124may comprise interconnected circumferential and radial portions. Corresponding and underlying deflection elements134may comprise radial portions arranged to extend in between radial portions of the force transfer elements124. Circumferential portions of the force transfer elements124may be arranged to contact radial portions of the deflection elements134. Supports246may comprise circumferential portions arranged to extend between circumferential portions of the force transfer elements124and contact radial portions of the deflection elements134. In this way force transmission is provided through overlapping and circumferential/radial contacts. Downward axial load on the force transfer elements124may be transmitted to the deflection elements134via circumferential portions of the force transfer elements124, which contact with radial portions of deflection elements134, which in turn contact with circumferential portions of supports134, and are arranged to axially deflect into the axially recessed region244of thrust plate200. Attention is directed toFIGS.9aand9b, which show an exaggerated radial cross-section showing the layered structure of a compliant foil thrust bearing comprising the compliant foil thrust bearing subassembly100and thrust plate200. In the direction of increasing elevation, in the Z-direction shown inFIGS.9aand9b, there is shown the recessed surface244, supports246, deflection element134, force transfer element124and fluid foil element114. In this example, load imparted via the fluid film formed above the fluid foil element114by a rotating thrust disk is transferred from the fluid foil element114, through the corresponding force transfer element124and to the corresponding deflection element134, one or more portions of which is caused to deflect over the supports246and into an axial through-hole126, such deflection in the axial direction shown in the transition fromFIG.9atoFIG.9b. FIGS.6aand6bshow respectively a compliant foil thrust bearing300and the same providing a view through the plates thereof. Likewise,FIGS.7aand7bshow a compliant foil thrust bearing300but this time with a cutout portion310revealing recessed surface244, supports246, deflection elements134, force transfer elements124and fluid foil elements114. The cutout portions310demonstrate in this example of a compliant foil thrust bearing300the relative interaction between plates of the compliant foil thrust bearing subassembly100and thrust plate200. As is apparent from consideration ofFIGS.6a,6b,7aand7b, the fluid plate110, the force transfer plate120and the spring plate130may be vertically stacked such that the fluid foil elements114, the force transfer elements124, and the deflection elements134are circumferentially aligned with each other in an axially overlapping relationship. Thus the plates of the subassembly100may be stacked such that each fluid foil element114is axially supported by a pair of corresponding and axially overlapping force transfer elements124and deflection elements134. In the example shown inFIG.1, the fluid plate110overlies the force transfer plate120and the force transfer plate120overlies the spring plate130. In the event that the subassembly100and thrust plate200are combined, the spring plate overlies the thrust plate200. The order of stacking anticipated in the example ofFIG.1is that the spring plate130is positioned onto the thrust plate200, the force transfer plate120is positioned onto the spring plate130and finally the fluid plate110is positioned onto the force transfer plate120. During or following stacking, the plates can be oriented such that the fluid foil elements114are axially supported by corresponding pairs of overlapping force transfer elements124and deflection elements134. The plates are orientable such that each fluid foil element114overlies a corresponding force transfer element124, which force transfer element124overlies a corresponding deflection element134. In this way force transmitted from each fluid foil element114may be transmitted through the corresponding force transfer element124to the corresponding deflection element134. The force imparted to the deflection element134may cause the deflection element134to axially displace relative to the spring plate mating ring132. The direction of displacement is axially away from the fluid plate110. Whereas in some prior art implementations corrugated foil is provided to facilitate compliance having a tendency to give rise to plastic deformation in use, according to the examples described herein there is facilitated the possibility to safeguard against such plastic deformation owing to the force transfer mechanism disclosed herein. In the examples disclosed herein, there is provided a compliant foil thrust bearing subassembly100for positioning directly onto a thrust plate200offering a minimal number of plates and thus reduced manufacturing complexity and performance variation as compared to the case when a higher number of plates are employed. Particular attention is directed to the interaction between a force transfer element124and a corresponding deflection element134. In particular, as shown in these figures, the force transfer elements124and/or the deflection elements134may comprise axial through-holes126,136. These axial through-holes may be open and/or closed axial through-holes. The force transfer elements124and/or the deflection elements134may comprise grids comprising axial through-holes. For example, each force transfer element124may comprise a grid defining axial through-holes126. The deflection elements134, or at least portions thereof, may be arranged to be extendable within the axial through-holes126of the force transfer elements124. With reference toFIGS.9aand9b, axial through-holes126provided in the force transfer elements124facilitate axial displacement of the deflection elements134into the through-holes126formed in the force transfer elements124. Each force transfer element124may comprise a force transfer element grid and each corresponding deflection element134may comprise an overlapping and offset deflection element grid. By overlapping and offsetting the force transfer element and deflection element grids in this way, there is facilitated relative displacement therebetween in an axial direction for the purpose of resiliently transferring load and providing compliance in the compliant foil thrust bearing. It will be recognized that whilst the examples provided herein show specific transfer element124and deflection element134geometries, the overall principle is applicable to a wide variation in terms of geometries. Supports246of the thrust plate200may be arranged so as to axially overlap with axial through-holes126of the force transfer plate120and/or axial through-holes136of the spring plate130, as is particularly visible inFIGS.7aand7b. Radial portions of the deflection elements134may be arranged so as to axially overlap with axial through-holes125of the force transfer plate120, as shown inFIGS.7aand7b. Thus supports246of the thrust plate200and/or portions of deflection elements134and portions of force transfer elements124may be axially intermeshed so as to present gaps into which portions of the deflection elements134can extend. Such extension facilitates relative movement between the plates, conferring resilience. In the example shown inFIGS.7aand7b, the force transfer elements124comprise radially extending portions127interconnected by circumferentially extending portions129. The force transfer elements124overlap with underlying deflection elements134. The deflection elements134comprise radially extending portions arranged to extend between the overlying radially extending portions127of the corresponding force transfer elements124. The circumferentially extending portions129of the force transfer elements124contact with the underlying radially extending portions135of the corresponding deflection elements134. The annular supports246of the underlying thrust plate200extend between the circumferential portions129of the force transfer elements124. This form of interconnection facilitates excellent resilience characteristics that are highly configurable to individual applications. FIGS.8aand8bshow tabs138of the spring plate130in extended and folded orientations. Thus the plates can be stacked together, with the tabs138then folded over the remaining plates to retain them in position. The force transfer plate120may be provided with a thickness that is greater than that of the spring plate130, and optionally also greater than that of the fluid plate110, as shown inFIGS.9aand9b. It has been identified that the provision of a force transfer plate with a greater thickness than that of the spring plate safeguards against performance deterioration associated with distortion of the force transfer plate. The increased thickness force transfer plate helps in evenly spreading the forces to be transmitted over a greater working area of the fluid plate. The fluid plate may comprise a thickness between 0.076 and 0.127 mm. The force transfer plate120may comprise a thickness between 0.1 and 0.25 mm, or between 0.127 and 0.25 mm. The spring plate130may comprise a thickness between 0.076 and 0.127 mm. Each of the examples disclosed herein, including the claimed examples, may be provided in a gas turbine system, e.g. a micro turbine system, comprising the compliant foil thrust bearing according to any one example. Employing such a compliant foil thrust bearing in a gas turbine system provides a gas turbine system offering improved performance characteristics owing to improved management of frictional losses and heat, and simplified manufacturing. It will be recognized that the examples disclosed herein are not limiting and are capable of numerous modifications and substitutions. | 20,683 |
11859660 | DETAILED DESCRIPTION Embodiments of the invention relate to bearing assemblies, bearing apparatuses, and methods of use in which one or more or at least a portion of one or more bearing surfaces of the rotor and/or the bearing surfaces of the stator include different materials. For example, the bearing surface(s) of one of the rotor or stator may include diamond (e.g., polycrystalline diamond), while the bearing surface(s) of the other of the rotor or stator do not include diamond, but include another superhard material (e.g., silicon carbide). Another embodiment of the invention relates to bearing apparatuses including both a thrust-bearing assembly and a radial bearing assembly in which the bearing surfaces of the thrust-bearing assembly include diamond, while the bearing surfaces of the radial bearing assembly do not include diamond, but include another superhard material. The diamond bearing surfaces may be in the form of PCD, which may be attached to a substrate to form a PDC. For example, in any of the embodiments disclosed herein the bearing surfaces that employ PCD and/or a PDC may be formed and/or structured as disclosed in U.S. Pat. Nos. 7,516,804; 7,866,418; 8,236,074; and 8,297,382; which are incorporated herein, in their entirety, by this reference. PCD includes a plurality of directly bonded together diamond grains exhibiting diamond-to-diamond bonding (e.g., sp3bonding) therebetween, with a catalyst disposed in at least a portion of the interstitial regions defined by the diamond grains. In some embodiments, the catalyst may comprise a metal-solvent catalyst (e.g., cobalt, iron, nickel, or alloys thereof) or a nonmetallic catalyst such as a carbonate catalyst. Furthermore, in any of the bearing surfaces that use PCD, the catalyst used to form the PCD (e.g., cobalt) may be leached to a selected depth from the bearing surface. The diamond particles that are HPHT sintered to form the PCD used in the bearing elements disclosed herein may include one or more selected sizes that may be determined, for example, by passing the diamond particles through one or more sizing sieves or by any other method. In an embodiment, the plurality of diamond particles may include a relatively larger size and at least one relatively smaller size. As used herein, the phrases “relatively larger” and “relatively smaller” refer to particle sizes determined by any suitable method, which differ by at least a factor of two (e.g., 40 μm and 20 μm). More particularly, in various embodiments, the plurality of diamond particles may include a portion exhibiting a relatively larger size (e.g., 100 μm, 90 μm, 80 μm, 70 μm, 60 μm, 50 μm, 40 μm, 30 μm, 20 μm, 15 μm, 12 μm, 10 μm, 8 μm) and another portion exhibiting at least one relatively smaller size (e.g., 30 μm, 20 μm, 10 μm, 15 μm, 12 μm, 10 μm, 8 μm, 4 μm, 2 μm, 1 μm, 0.5 μm, less than 0.5 μm, 0.1 μm, less than 0.1 μm). In an embodiment, the plurality of diamond particles may include a portion exhibiting a relatively larger size between about 40 μm and about 15 μm and another portion exhibiting a relatively smaller size between about 15 μm and 2 μm. The plurality of diamond particles may also include three or more different sizes (e.g., one relatively larger size and two or more relatively smaller sizes) without limitation. The diamond grain size of the PCD so formed after HPHT sintering may be substantially the same or similar to the diamond particles used to form the PCD or the PCD of a PDC. In an embodiment, other forms of diamond may also be employed, such as natural diamond, other synthetic diamond, a diamond-silicon carbide composite as disclosed in U.S. Pat. No. 7,998,573 that is incorporated herein in its entirety by this reference, diamond deposited by chemical vapor deposition, diamond or diamond-like carbon deposited by physical vapor deposition, or other deposition technique. As used herein, a non-diamond superhard material employed for the non-diamond bearing surface is a non-diamond material exhibiting a hardness that is at least as hard as tungsten carbide. Examples of non-diamond superhard materials include, but are not limited to, polycrystalline cubic boron nitride, silicon carbide, tungsten carbide, tantalum carbide, other carbides exhibiting a hardness at least equal to that of tungsten carbide, or any combination of the foregoing. The disclosed bearing apparatuses may be used in a number of applications, such as downhole motors in subterranean drilling systems, directional drilling systems, pumps, transmissions, gear boxes, and many other applications. FIG.1is an isometric cutaway view of an embodiment of a thrust-bearing apparatus100, which may employ diamond bearing elements (e.g., PCD bearing elements) on one or both of the thrust-bearing assemblies102a,102b. For example, any suitable PDC may be used as bearing elements. A non-diamond superhard material may be employed for at least one of the bearing surfaces of at least one of the thrust-bearing assemblies. For example, one of the thrust-bearing assemblies102a,102bmay include diamond bearing elements, while the other of the thrust-bearing assemblies102a,102bmay include bearing elements using a non-diamond superhard material. Each thrust-bearing assembly102a,102bincludes an annular support ring104a,104bthat may be fabricated from any suitable material, such as carbon steel, stainless steel, a superhard material (e.g., silicon carbide, tantalum carbide, or another carbide), or another suitable material. In an embodiment, each support ring104a,104bmay include a plurality of pockets or recesses105that receives a corresponding bearing element106a,106b. For example, each bearing element106a,106bmay be mounted to a corresponding support ring104a,104bwithin a corresponding recess by brazing, interference-fitting, using fasteners, or another suitable mounting technique. Alternatively, the bearing elements106a,106bmay be mounted onto a surface of support ring104a,104b, respectively, without being received into a corresponding recess. In an embodiment, bearing elements106amounted into or on support ring104amay include a PCD bearing surface, while bearing elements106bmounted into or on support ring104bmay not include diamond, but include bearing surfaces that include a superhard material other than diamond (e.g., silicon carbide or another carbide or other ceramic). For example, bearing elements106amay comprise PDCs including a PCD table108that may be metallurgically bonded to a substrate (e.g., a cemented carbide substrate). In an embodiment, the substrate of bearing elements106ato which PCD table108is bonded may comprise cobalt-cemented tungsten carbide or another suitable carbide material that may include chromium carbide, tantalum carbide, vanadium carbide, or combinations thereof as an alternative to or in addition to tungsten carbide. Each PCD table108may include a bearing surface110a. Bearing elements106bmay include a non-diamond superhard material. For example, elements106bmay be similarly shaped and sized as bearing elements106a, but do not include a PCD table thereon, the bearing surface of bearing elements106bbeing defined rather by a non-diamond superhard material. For example, bearing elements106bmay include a carbide, such as silicon carbide. In use, bearing surfaces110aof thrust-bearing assembly102abear against opposing bearing surfaces110bof the other bearing assembly102b. For example, one of the thrust-bearing assemblies102a,102bmay be operably coupled to a shaft to rotate therewith and may be termed a “rotor.” The other of the thrust-bearing assemblies102a,102bmay be held stationary and may be termed a “stator.” Because bearing surfaces110aand110bmay include different materials, non-diamond bearing surfaces may wear preferentially relative to bearing surfaces includes diamond. Providing such a bearing assembly including different material bearing surfaces may provide for better heat transfer and better maintenance of a fluid film between bearing surfaces110aand110bthan if all bearing surfaces110aand110bincluded the same non-diamond superhard material (e.g., where both include silicon carbide). Diamond has substantially higher thermal conductivity than superhard carbides, such as silicon carbide. Because one of bearing surfaces110a,110b(e.g.,110a) includes diamond, heat generated at non-diamond bearing surfaces may be better dissipated as a result of its proximity or contact with diamond bearing surfaces. Thus, a bearing assembly including differing bearing surface materials, as described, may provide increased wear resistance as compared to a bearing assembly in which all bearing surfaces include a non-diamond superhard material (e.g., silicon carbide), but at significantly lower cost than would be associated with a bearing assembly in which both of the opposed bearing surfaces include only diamond. In an embodiment, the stator may include at least one non-diamond superhard bearing surface, such as only including non-diamond bearing surfaces. The stator within a bearing apparatus often fails before the rotor. In some instances, this may occur because the stator bearing surfaces are often subject to unequal heating and wear. For example, wear on a stator is often unequal as a result of a small number of stator bearing elements being somewhat more “prominent” than the other stator bearing elements. As a result, contact, heating, and wear during use may be preferentially associated with these more prominent stator bearing elements. For example, the bulk of the load and resulting wear may be borne by, for example, the one to three most prominent bearing elements, while the other stator bearing elements may show little wear by comparison. Such wear may result from the difficulty of perfectly aligning the bearing elements of the bearing assembly. Because the stator may typically wear faster than the rotor, in an embodiment the stator bearing elements may not include diamond, but include a non-diamond superhard material, as the stator typically fails first anyway. In such embodiments, the stator may be replaced once failure or a given degree of wear occurs. In another embodiment, the stator may include at least one, one or more, or only diamond bearing surfaces, and the rotor may not include or may only include a small number of diamond bearing surfaces, such as including only non-diamond superhard material for bearing surfaces. It is currently believed that the configuration of thrust-bearing apparatus100facilitates faster breaking in of the bearing surfaces as the less hard bearing surfaces wear/break in relatively faster. FIG.2Ashows a thrust-bearing assembly202baccording to another embodiment. Thrust-bearing assembly202bincludes a single substantially continuous bearing surface210bdefined by a single substantially continuous bearing element206brather than a plurality of bearing elements. Such a configuration may improve wear performance as compared to an assembly in which the overall bearing surface is formed of a plurality of segmented, discontinuous bearing surfaces defined by the individual bearing elements. Wear performance may be improved because alignment of a single, large substantially continuous bearing element may be more readily achieved than alignment of a plurality of discontinuous, spaced apart bearing elements. In addition, the substantial absence of any discontinuities in the overall bearing surface (e.g., substantially planar in the context of the illustrated thrust-bearing assembly) may minimize and/or prevent chipping or cracking of substantially continuous bearing surface210band/or promote fluid film development. FIG.2Bshows a bearing apparatus100′ according to an embodiment, which includes the bearing assembly202bofFIG.2A. Thus, one bearing assembly (e.g., assembly202b) may include a single substantially continuous bearing surface (e.g.,210b), while the generally oppositely disposed bearing assembly (e.g., assembly102a) may include a plurality of bearing elements, each defining a bearing surface (e.g.,110a) so that the overall ring-shaped bearing surface plane includes a plurality of discontinuous, separate bearing surfaces. In an embodiment, bearing surface210bof bearing assembly202bmay not include diamond, but include a non-diamond superhard material while at least one of bearing surfaces110aof bearing assembly102ainclude diamond. As shown, in an embodiment, bearing surface210band bearing element206bmay be provided integral with support ring204b. For example, bearing element206band support ring204bmay be formed of a single piece of the same material (e.g., a carbide, such as tantalum carbide, tungsten carbide, silicon carbide, vanadium carbide, boron nitride, titanium nitride, or combinations thereof). FIG.2Cshows another bearing apparatus100″ in which both bearing assemblies202aand202beach include a single substantially continuous bearing surface210aand210b, respectively. In an embodiment, one of bearing surfaces210aor210b(e.g.,210a) may include diamond (e.g., polycrystalline diamond), while the other bearing surface does not include diamond, but includes a non-diamond superhard material. In an embodiment, at least a portion of bearing surfaces210aor210b(e.g.,210a) may include diamond (e.g., polycrystalline diamond), while the other bearing surface does not include diamond but at least a portion of the bearing surface includes a non-diamond superhard material. FIG.3is an isometric cutaway view of an embodiment of a radial bearing apparatus300, which may employ different materials for at least a portion of the bearing surfaces of one or both of the assemblies in accordance with the principles of any of the disclosed embodiments. Radial bearing apparatus300includes an inner race302positioned generally within an outer race304. Outer race304includes one or more bearing elements306amounted thereto that include respective bearing surfaces310a. For such a radial bearing, bearing surface310aof elements306amounted to outer race304may be concavely curved. Inner race302also includes a plurality of bearing elements306baffixed thereto that have respective bearing surfaces310b. For such a radial bearing, bearing surface310bof elements306bmounted to inner race302may be convexly curved to correspond with the concave curvature of bearing surface310a. The inner race302is positioned generally within the outer race304and, thus, the inner race302and outer race304may be configured so that the bearing surfaces310aand310bmay at least partially contact one another and move relative to each other as the inner race302and/or outer race304rotate relative to each other during use. Either bearing elements306aor bearing elements306bmay include a diamond (e.g., PCD) bearing surface, while one or both sets of bearing elements may include at least one bearing surface that includes a superhard material other than diamond (e.g., silicon carbide). In an embodiment, bearing surfaces310bmay include diamond (e.g., polycrystalline diamond), while bearing surfaces310amay not include diamond, but include a non-diamond superhard material such as silicon carbide or another type of diamond material such as a diamond-silicon carbide composite. In an embodiment, outer race304may be a stator bearing assembly, while inner race302may be a rotor bearing assembly. In another embodiment, inner race302may be the stator, while outer race304may be the rotor. FIG.4Ashows an inner race402for use in a radial bearing apparatus according to another embodiment. Inner race402includes a bearing element406bdefining a single substantially continuous bearing surface410b. As described above, such a configuration may improve wear performance as compared to an assembly in which the overall bearing surface is comprised of a plurality of segmented, discontinuous bearing surfaces of the individual bearing elements and/or may promote fluid film development. FIG.4Bshows an outer race404for use in a radial bearing apparatus according to another embodiment. Outer race404includes a bearing element406adefining a single substantially continuous bearing surface410a. Such a configuration may improve wear performance as compared to an assembly in which the overall bearing surface is comprised of a plurality of segmented, discontinuous bearing surfaces of the individual bearing elements and/or may promote fluid film development. FIG.4Cshows an embodiment of a bearing apparatus400including inner race402ofFIG.4Aand the outer race404ofFIG.4Bso that both bearing elements406aand406bdefine substantially opposed bearing surfaces410aand410bthat are each a single substantially continuous bearing surface, without any discontinuities or segments disposed therein. One of bearing surfaces410a,410bmay include diamond (e.g., PCD), while the other of the bearing surfaces does not include diamond, but includes a non-diamond superhard material (e.g., silicon carbide). In an embodiment, at least a portion of one or both of bearing surfaces410a,410bmay include diamond (e.g., PCD) and a non-diamond superhard material (e.g., silicon carbide). Various combinations of the illustrated inner and outer race configurations may be employed in other embodiments. For example,FIG.4Cshows a configuration in which both races each include a single bearing element defining a substantially continuous bearing surface, which surfaces are oriented substantially opposite to one another during use.FIGS.4D and4Eshow configurations400′ and400″ according to additional embodiments, in which either the inner race or outer race includes a single bearing element defining a substantially continuous bearing surface, while the other of the races includes a plurality of bearing elements, such that the overall bearing surface (e.g., resembling the inner or outer surface of a cylinder) is defined by a plurality of segmented or discontinuous bearing surfaces that are separate from one another. FIG.4Dshows a further embodiment of a radial bearing apparatus. As shown, one bearing assembly (e.g., outer race304) may include a plurality of bearing elements306a, each defining a separate bearing surface310a, while the other bearing assembly (e.g., inner race402) may include a single substantially continuous bearing element that extends around substantially the entire perimeter of inner race402, so as to define a single substantially continuous bearing surface410b. In an embodiment, either bearing elements306aor bearing element406bcomprise diamond (e.g., bearing elements306amay comprise PCD or a PDC) while the other bearing element (e.g., bearing element406b) may not comprise diamond, but comprises a non-diamond superhard material. In an embodiment, at least a portion of the bearing element406band/or the bearing surface410bor the bearing elements306amay include PCD. FIG.4Eshows a configuration similar to, but reversed, as compared toFIG.4D. For example, outer race404includes a single substantially continuous bearing element406aand bearing surface410athat extends along substantially the entire perimeter of outer race404, while inner race302(e.g., similar to that seen inFIG.3) may include a plurality of bearing elements306b, each defining a separate bearing surface310b. Either bearing elements306bor bearing element406ainclude diamond (e.g., bearing elements306bmay include diamond) while the other bearing element (e.g., bearing element406a) may not include diamond, but includes a non-diamond superhard material. Any of the radial bearing apparatuses disclosed herein may be employed in a variety of mechanical applications, such as roller cone bits, downhole motors, and turbines. For example, so-called roller cone rotary drill bits may benefit from a radial bearing apparatus. More specifically, the inner race may be mounted to a spindle of a roller cone and the outer race may be mounted to an inner bore formed within a cone such that the outer race and inner race may be assembled to form a radial bearing apparatus. FIGS.5A and5Bshow a bearing apparatus500that includes both a thrust-bearing assembly and a radial bearing assembly, and which may include one material (e.g., PCD) for the thrust-bearing surfaces, while employing a different material (e.g., a non-diamond superhard material) for at least another bearing surface such as the radial bearing surfaces. In an embodiment, a portion of the thrust-bearing surfaces or radial bearing surfaces may include PCD and a portion of the thrust-bearing surfaces or radial bearing surfaces may include a non-diamond superhard material such as silicon carbide. Bearing apparatus500includes a combination thrust/radial bearing assembly501that may include a thrust-bearing assembly502aand a radial bearing inner race502. In an embodiment, combination thrust/radial bearing assembly501may include a rotor, operatively coupled to a shaft (e.g., received through inner race502). Bearing apparatus500may further include thrust-bearing assembly502band radial bearing outer race504, which may operate as stator thrust and stator radial bearing components, respectively. Each thrust-bearing assembly502aand502bmay include a respective support ring (e.g.,505aand505b, respectively) with one or more bearing elements506aand506bmounted into or on the corresponding bearing ring. Radial bearing inner race502of combination thrust/radial bearing assembly501includes one or more bearing elements506c, while radial bearing outer race504includes one or more bearing elements506dconfigured to be oriented in generally opposed orientation relative to bearing elements506c. Respective bearing surfaces defined by bearing elements506a,506b,506c, and506dmay be selected, as described above, so that oppositely oriented bearing surfaces are different from one another. For example, bearing elements506aor506bmay include diamond, while the other does not include diamond, but includes a non-diamond superhard material. Similarly, bearing elements506cor506dmay include diamond, while the other does not include diamond, but includes a non-diamond superhard material. In another embodiment, both of thrust-bearing elements506aand506band their defined bearing surfaces may include one material (e.g., diamond), while the radial bearing elements506cand506dand their defined bearing surfaces may include the other material (e.g., a non-diamond superhard material). In an embodiment, the thrust-bearing surfaces may comprise diamond (e.g., PCD), while the radial bearing surfaces do not comprise diamond, but include a non-diamond superhard material such as silicon carbide. Such a configuration may be employed where the thrust load is considerably greater than the radial load so that the diamond bearing surfaces employed in the thrust-bearing portion of the apparatus provide high wear resistance and thermal management characteristics associated with the high thrust load. The radial bearing surfaces may be non-diamond, allowing the apparatus to be fabricated at significantly lower cost than an embodiment where all bearing surfaces were diamond, but also providing enhanced operation characteristics (e.g., greater wear resistance, improved heat transfer, or both) as compared to an embodiment where all bearing surfaces were non-diamond. FIGS.6A and6Bshow an apparatus500′ similar to apparatus500ofFIG.5Aaccording to an embodiment, but in which radial bearing outer race504′ includes a single substantially continuous bearing element506d′ rather than a plurality of separate bearing elements. Single substantially continuous bearing element506d′ may extend substantially entirely about the inside perimeter of outer race504′. As described above, where outer race504′ serves as a stator to rotor inner race502, the substantially continuous bearing surface may improve wear resistance and operational life of stator outer race504′. Another embodiment (not shown) may replace one or both thrust-bearing assemblies502aand502bwith configurations including a single substantially continuous bearing element, rather than the illustrated configuration including a plurality of separate bearing elements. Any of the embodiments for bearing apparatuses discussed above may be used in a subterranean drilling system.FIG.7is a schematic isometric cutaway view of a subterranean drilling system700according to an embodiment, which may employ one or more of any of the disclosed bearing apparatus embodiments. The subterranean drilling system700may include a housing760enclosing a downhole drilling motor762(i.e., a motor, turbine, or any other device capable of rotating an output shaft) that may be operably connected to an output shaft756. A thrust-bearing apparatus764may be operably coupled to the downhole drilling motor762. The thrust-bearing apparatus764may be configured as any of the thrust-bearing apparatus embodiments disclosed herein. A rotary drill bit768may be configured to engage a subterranean formation and drill a borehole and may be connected to the output shaft756. The rotary drill bit768is shown comprising a bit body790that includes radially and longitudinally extending blades792with a plurality of PDCs794secured to the blades792. However, other embodiments may utilize different types of rotary drill bits, such as core bits and/or roller-cone bits. As the borehole is drilled, pipe sections may be connected to the subterranean drilling system700to form a drill string capable of progressively drilling the borehole to a greater depth within the earth. The thrust-bearing apparatus764may include a stator772that does not rotate and a rotor774that may be attached to the output shaft756and rotates with the output shaft756. As discussed above, the thrust-bearing apparatus764may be configured as any of the embodiments disclosed herein. In operation, lubricating fluid may be circulated through the downhole drilling motor762to generate torque and rotate the output shaft756and the rotary drill bit768attached thereto so that a borehole may be drilled. A portion of the lubricating fluid may also be used to lubricate opposing bearing surfaces of the stator772and the rotor774. While various aspects and embodiments have been disclosed herein, other aspects and embodiments are contemplated. The various aspects and embodiments disclosed herein are for purposes of illustration and are not intended to be limiting. For example, another embodiment may employ PCD for one bearing surface, while employing a non-PCD superhard material having a hardness lower than PCD for the opposing bearing surface. In an embodiment, the superhard material may include a form of diamond exhibiting lower hardness than PCD (e.g., chemically vapor deposited diamond). Similar preferential wear characteristics may be associated with such a configuration where the non-PCD bearing surfaces wear preferentially relative to the PCD bearing surfaces. Another embodiment may employ the harder PCD material for opposed thrust-bearing surfaces while opposed radial bearing surfaces of a bearing apparatus may not include PCD, but include a non-PCD superhard material having a hardness lower than PCD. Additionally, the words “including,” “having,” and variants thereof (e.g., “includes” and “has”) as used herein, including the claims, shall be open ended and have the same meaning as the word “comprising” and variants thereof (e.g., “comprise” and “comprises”). | 27,382 |
11859661 | DETAILED DESCRIPTION OF THE EMBODIMENT Those of ordinary skill in the art will appreciate from this disclosure that when a range is provided such as (for example) an angle/distance/number/weight/volume/spacing being between one (1 of the appropriate unit) and ten (10 of the appropriate units) that specific support is provided by the specification to identify any number within the range as being disclosed for use with a preferred embodiment. For example, the recitation of a percentage of copper between one percent (1%) and twenty percent (20%) provides specific support for a preferred embodiment having two point three percent (2.3%) copper even if not separately listed herein and thus provides support for claiming a preferred embodiment having two point three percent (2.3%) copper. By way of an additional example, a recitation in the claims and/or in portions of an element moving along an arcuate path by at least twenty (20°) degrees, provides specific literal support for any angle greater than twenty (20°) degrees, such as twenty-three (23°) degrees, thirty (30°) degrees, thirty-three-point five (33.5°) degrees, forty-five (45°) degrees, fifty-two (52°) degrees, or the like and thus provides support for claiming a preferred embodiment with the element moving along the arcuate path thirty-three-point five (33.5°) degrees. In the following description, terms indicating directions, such as “axial”, “radial” and “circumferential direction”, unless otherwise specified or delimited, refer to the axial, radial and circumferential directions of the bearing or its cage. FIG.1shows a schematic cross-sectional view of the deep groove ball bearing according to the present invention. In the illustrated embodiment, the bearing10comprises an inner ring1, an outer ring2, a plurality of rolling elements3arranged between the inner and outer rings, and a cage4that constrains the rolling elements3to maintain a predefined circumferential spacing, where the rolling elements3can be made of a metallic material (e.g., bearing steel) or a ceramic material (e.g., silicon nitride). Ceramic materials have unique advantages in electric motor applications because they have many advantages such as heat resistance, corrosion resistance, electrical insulation, and non-magnetism, and, after they are made into rolling elements, can prevent magnetization and electrocorrosion of the bearings within the magnetic field of the motor. As shown inFIG.1, the bearing10has a radial dimension H1in the sense of thickness, which is numerically equal to half of the difference between the outer diameter D and the inner diameter d of the bearing, i.e. H1=(D−d)/2. To improve the rigidity of the bearing, the invention is designed to use smaller size rolling elements so that the diameter of the rolling element DWdoes not exceed 50% of H1, i.e. DW≤0.5H1. In a further preferred embodiment, the diameter of the rolling elements may be set to DW≤0.45H1, DW≤0.4H1, up to DW≤0.35H1as desired. The smaller size of the rolling elements allows for a further increase in the density of rolling element distribution between the raceways, thus enhancing the rigid support of the bearing while also allowing room to improve the structural strength of the bearing rings, as described in detail later. It is should be noted that the smaller size of the rolling elements also contributes to the increase of the bearing speed. On the one hand, due to the existence of clearance, a deep groove ball bearing in the working condition actually forms an angular contact ball bearing. During the rotation of the bearing, the centrifugal force will prompt the contact angle between the rolling element and the inner ring raceway and the contact angle between the rolling element and the outer ring raceway to be inconsistent. The resulting gyroscopic torque causes a self-spinning motion of the rolling element around its normal to the contact surface of the raceway, and this self-rotating motion is an important cause of frictional heating. The ratio of the angular velocity of self-spin to the angular velocity of rolling of the rolling element is called “spin-roll ratio”. The larger the spin-roll ratio, the more violent the sliding friction, the more heat generated by the friction. Smaller size rolling elements are less subject to centrifugal force, resulting in a weaker self-spinning effect, a lower spin-roll ratio, and a weaker frictional heating effect than larger size rolling elements, and so are especially conducive to high-speed operation of the bearing. On the other hand, the smaller size of the rolling elements also gives way to internal space for the adoption of a cage of reinforced structure. It is well known that the structural strength of a cage can limit the increase in bearing speed. An enlarged space inside the bearing facilitates the adoption of a well-designed and structurally solid cage, which can enhance the upper limit of cage adaptation to bearing speed. Based on the small size rolling elements, the invention can also be designed with a large size wall thickness of the bearing outer ring. Since the rigidity of the outer ring depends mainly on the wall thickness at its thinnest position, the invention uses the radial thickness H2of the outer ring2at the deepest part of the outer ring raceway5as the dimensional reference for describing the thickness of the outer ring (hereinafter referred to as “minimum thickness of the outer ring”). In the present invention, the minimum thickness of the outer ring H2≥0.25H1; In a further preferred embodiment, the minimum thickness of the outer ring H2≥0.27 H1; In a still further preferred embodiment, the minimum thickness of the outer ring H2≥0.28H1. As the shaft and bearing inner ring is generally in a tight fit, after assembly there will be a “compensation” effect on the rigidity of the inner ring, so that the outer ring thickness plays a more significant role than the inner ring in improving the rigidity of the bearing, which thus can significantly reduce the dynamic deformation of the bearing house caused by the contact load between the rolling elements and outer ring raceway. As is well known, due to the limitation of geometry, the diameter of the bearing pitch circle and the size of the rolling elements determine the upper limit of the number of rolling elements that can be filled in between the inner and outer raceways of the bearing. Therefore, under the condition of the same pitch diameter, the smaller the size of the rolling elements, the more the number of rolling elements that can be filled into the bearing, the more rigid the bearing will be. At the same time, a larger number of rolling elements can alleviate to a considerable extent the increase in contact stress (intensity of pressure) between the rolling elements and the raceway due to size reduction, thus ensuring that the fatigue life of the material does not become a bottleneck limiting the bearing life. To ensure the life and rigidity of the bearing, the deep groove ball bearing according to the present invention is designed with a sufficient number of small size rolling elements. Taking the typical application of motor bearings in electric vehicles as an example, bearing life is required to last at least 250,000-300,000 km vehicle mileage and the bearings are also required to have higher rigidity. According to the analysis and tests, in the case of rolling element diameter DW=0.35H1, when the number of rolling elements meet the following empirical relationship equation (1), not only does the bearing life meet the above mileage requirement, but the axial stiffness is also increased by about 15% compared to the conventional rolling element diameter and number: Z≥1+1812arcsin(DWDe-DW)(1)where Z is the number of rolling elements, DWis the diameter of the rolling elements, and Deis the diameter of the outer raceway. As a further preferred embodiment, in the case of rolling element diameter DW=0.35H1, when the number of rolling elements meet the following empirical relationship equation (2), not only does the bearing life meet the above mileage requirement, but the axial stiffness is also increased by about 40% compared to the conventional rolling element diameter and number: Z≥1+1852arcsin(DWDe-DW)(2) While the load is constant, the increase in the number of rolling elements reduces the contact load between the individual rolling elements and the bearing raceways, which in turn reduces the dynamic deformation of the bearing rings caused by this contact load, thus significantly reducing the risk of creep and wear between the bearing outer ring and the bearing housing bore. Starting from the motor applications of deep groove ball bearings, this invention opposes the traditional design concept of fatigue life as the criteria and replaces it with the pursuit of a comprehensive and balanced performance, so as to construct a bearing solution that can meet the needs of most motor applications by adopting relatively smaller size rolling elements, more number of rolling elements and relatively thick outer ring structure. In addition to the significant increase in bearing rigidity (including axial and radial rigidity), the smaller size of the rolling elements also reduces the self-spinning effect and the resulting thermal effect, and leaves room for the use of a cage of a stronger structure to increase the upper speed limit of the bearing. The invention fully meets the comprehensive needs of motor applications for deep groove ball bearings, corrects the technical bias in the industry of unilaterally pursuing fatigue life and designing bearing structures accordingly, and reconstructs a comprehensive and balanced bearing index for motor applications. The invention is widely applicable to rotor support and torque output of various motors including those for electric vehicles, and fully meets the performance requirements of most applications in the motor field. It should be understood by those skilled in the art that the described bearing and its applications are not limited by the specific embodiments and that the more general technical solutions will be subject to the limitations in the accompanying claims. Any modifications and improvements to the present invention are within the scope of protection of the present invention provided that they conform to the limitations of the accompanying claims. | 10,427 |
11859662 | DETAILED DESCRIPTION OF EMBODIMENTS A novel and useful bearing structure has been developed, to improve the dynamic behavior of bearings, such as in particular, but not exclusively, PCD bearings and other bearings characterized by high stiffness. The novel bearings include two components, arranged coaxial to one another. One component rotates integrally with a rotary machine part, such as an impeller of a rotodynamic pump. The other component is stationarily housed in the machine housing. The stationary component includes damping features, which prevent or reduce the propagation of vibrations between the rotary machine component and the stationary structure of the machine. In embodiments disclosed herein, the stationary component of the bearing includes two co-axial substantially cylindrical members, namely an internal one and an external one. The internal and external members form a gap therebetween. In the gap a resilient damping feature is arranged, which is adapted to allow dampened displacements of the external cylindrical member with respect to the internal cylindrical member. Displacements can be in a radial direction and/or in a tangential direction. Displacements can be provoked by vibrations of a rotary machine component, mounted for integral rotation with the external bearing component. The vibrations propagate through bearing pads from the outer component to the inner component and are dampened by the resilient damping feature arranged in the gap formed in the inner component, between the external cylindrical member and the internal cylindrical member thereof. This results in efficient damping of vibrations and reduced propagation of the vibrations generated by the rotary machine component towards the stationary structure of the machine. The novel bearing structure will now be described in combination with a rotodynamic pump, and specifically with a multi-phase rotodynamic pump. Those skilled in the art will nevertheless appreciate that the bearing structure of the present disclosure can be used with advantage also in other applications, for instance whenever a relatively stiff bearing is used to support a rotary machine part subject to vibrations and damping of the vibrations is desired. Referring now toFIG.1, a rotodynamic pump1comprises a casing3and a stationary shaft5arranged therein. The stationary shaft can be formed by a beam extending longitudinally through the pump casing. In other embodiments, the stationary shaft5can be comprised of stacked shaft sections connected to one another by an axial tie rod. The pump can comprise a plurality of stages7. Each pump stage7comprises a respective impeller9, which is supported for rotation on the shaft5and coacts with a statoric part11, i.e. with a non-rotating, stationary component of the pump1. If the stationary shaft5is formed by stacked sections, each impeller9can be supported by a separate section of the stationary shaft5. Referring now toFIG.2, with continuing reference toFIG.1, each impeller9comprises a disc-shaped body12and a plurality of blades13distributed annularly around a rotation axis A-A. A process fluid path15extends across the bladed portion of each impeller9. Mechanical power generated by embedded electric motors, to be described, rotate the impellers9, which transfer the power to the process fluid along the process fluid path15to boost the pressure of the fluid. In the exemplary embodiment ofFIGS.1and2, each impeller9comprises a shroud17. Each impeller9is driven into rotation by a respective electric motor18housed in the casing3. Each electric motor18includes a rotor19, arranged around the shroud17and rotating with the impeller9, as well as a stator21developing around the rotor19and stationarily housed in the casing3. Each impeller9is supported on the stationary shaft5by means of a respective bearing31. In the embodiment ofFIGS.1and2each bearing31comprises a stationary inner bearing component31B and an outer rotary bearing component31A. The two components31A,31B are substantially co-axial. In presently preferred embodiments the bearing31is a PCD (Poly-Crystalline Diamond) bearing comprised of radial bearing pads51A on the rotary outer bearing component31A and radial bearing pads51B on the stationary inner component31B. Each bearing31can further include axial bearing pads53A on the rotary outer bearing component31A and axial bearing pads53B on the stationary inner bearing component31B or on the statoric part11of the pump1. According to embodiments disclosed herein, the inner bearing component31B is configured to provide a vibration damping effect, such that vibrations generated by the rotating impeller9, for instance, are dampened and not propagated, or propagated only in a dampened manner, through the respective bearing31towards the stationary structure11of the pump1. Referring now toFIG.3, with continuing reference toFIG.2, the inner stationary bearing component31B comprises an external cylindrical member61and an internal cylindrical member63. The internal and external cylindrical members61,63are substantially co-axial to one another and to the stationary shaft5, on which the internal cylindrical member63can be mounted. The bearing pads51B are integral with the external cylindrical member61. The external cylindrical member61and the internal cylindrical member63can be coupled to one another by a ferrule65, seeFIG.2, which can be screwed on one end of the internal cylindrical member63. The opposite end of the internal cylindrical member63can form a flange67. The external cylindrical member61can be pressed by screwing the ferrule65, between the flange67and the ferrule65. O-ring or similar seals71,73can be arranged between the internal cylindrical member63and the external cylindrical member61. A cylindrical gap75is formed between the external cylindrical member61and the internal cylindrical member63. The cylindrical gap75extends in an axial direction, i.e. parallel to the rotation axis A-A. In the cylindrical gap75a resilient damping feature is arranged. As used herein, the term “resilient damping feature” can be understood as any mechanical device or combination of devices arranged between the external cylindrical member61and the internal cylindrical member63and coacting therewith, such that the vibration of one said internal and external cylindrical members63,61is not transmitted to the other of said internal and external cylindrical members63,61, or a dampened vibration is transmitted thereto. A lubricant fluid, preferably a lubricant liquid, such as oil or other preferably high-viscosity fluid can fill the gap75. In some embodiments, as shown inFIG.3, the resilient damping feature includes a corrugated tubular sheet77. The corrugated tubular sheet77comprises corrugations77A extending axially, i.e. parallel to the rotation axis A-A of the bearing31. Due to the corrugated tubular sheet77arranged in the gap75, the external cylindrical member61and the internal cylindrical member63can move one with respect to the other to a limited extent in a radial direction, for instance due to oscillations induced by vibrations of the rotary impeller9. The radial displacement of the external cylindrical member61with respect to the internal cylindrical member63is obtained through the compliance of the corrugations77A under a radial load applied thereto. The oscillation in radial direction is dampened by the resilient damping feature, provided by the corrugated tubular sheet77. In addition to a radial displacement, the external cylindrical member61can also move tangentially with respect to the internal cylindrical member63, i.e. the two members61,63can rotate with respect to one another by a limited angle. The tangential displacement (arrow f61,FIG.3) can be limited by tangential displacement limiting devices. For instance said devices can include at least one, and preferably a set of first radial projections81extending radially inwardly from an inner surface of the external cylindrical member61towards the outer surface of the internal cylindrical member63. The tangential displacement limiting devices can further include at least one, and preferably a set of second radial projections83extending radially outwardly from the outer surface of the internal cylindrical member63towards the external cylindrical member61. The first radial projections81and the second radial projections83extend between adjacent corrugations77A, such that the tangential displacement of the internal and external cylindrical members63,61is limited by co-action of the first and second radial projections81,83with the corrugations77A. A tangential displacement provoked by vibrations or oscillations induced by the rotary impeller causes flexural deformation of the corrugations77A of the corrugated tubular sheet77, which therefore dampens the oscillations. The damping effect of the resilient damping feature can be improved by high-viscosity lubrication liquid contained in the gap75and/or by friction between the resilient damping feature77and the surfaces of the external and internal cylindrical members61,63in contact with the corrugations77A of the resilient damping feature77. Referring now toFIGS.4and5, with continuing reference toFIG.2, in other, currently less preferred embodiments, the resilient damping feature can include a set of compressible inserts arranged in the gap between the external cylindrical member61and the internal cylindrical member63. InFIGS.4and5the same or equivalent parts or elements already shown inFIGS.2and3and described above are labeled with the same reference numbers and are not described again. In the embodiment ofFIGS.4and5the resilient damping feature includes a set of O-rings78housed in the gap75. Annular grooves on the inner cylindrical surface61A of the external cylindrical member61and annular grooves in the outer cylindrical surface63A of the internal cylindrical member63can be provided, to retain the O-rings78in the correct position. Referring toFIG.6, with continuing reference toFIG.2, in yet further, currently less preferred embodiments, the resilient damping feature can include a set of longitudinally extending resilient members79. InFIG.6the same or equivalent parts or elements already shown inFIGS.2and3and described above are labeled with the same reference numbers and are not described again. The resilient members79are housed in the gap75and can be retained in position by longitudinal grooves provided in the inner cylindrical surface61A of the external cylindrical member61and longitudinal grooves in the outer cylindrical surface63A of the internal cylindrical member63. While the invention has been described in terms of various specific embodiments, it will be apparent to those of ordinary skill in the art that many modifications, changes, and omissions are possible without departing form the spirit and scope of the claims. In addition, unless specified otherwise herein, the order or sequence of any process or method steps may be varied or re-sequenced according to alternative embodiments. | 11,085 |
11859663 | DETAILED DESCRIPTION OF THE EXEMPLARY EMBODIMENTS The present disclosure is more particularly described in the following examples that are intended as illustrative only since numerous modifications and variations therein will be apparent to those skilled in the art. Like numbers in the drawings indicate like components throughout the views. As used in the description herein and throughout the claims that follow, unless the context clearly dictates otherwise, the meaning of “a”, “an”, and “the” includes plural reference, and the meaning of “in” includes “in” and “on”. Titles or subtitles can be used herein for the convenience of a reader, which shall have no influence on the scope of the present disclosure. The terms used herein generally have their ordinary meanings in the art. In the case of conflict, the present document, including any definitions given herein, will prevail. The same thing can be expressed in more than one way. Alternative language and synonyms can be used for any term(s) discussed herein, and no special significance is to be placed upon whether a term is elaborated or discussed herein. A recital of one or more synonyms does not exclude the use of other synonyms. The use of examples anywhere in this specification including examples of any terms is illustrative only, and in no way limits the scope and meaning of the present disclosure or of any exemplified term. Likewise, the present disclosure is not limited to various embodiments given herein. Numbering terms such as “first”, “second” or “third” can be used to describe various components, signals or the like, which are for distinguishing one component/signal from another one only, and are not intended to, nor should be construed to impose any substantive limitations on the components, signals or the like. Referring toFIG.1toFIG.15, an embodiment of the present disclosure provides a linear guideway100. The linear guideway100in the following description is a standard linear guideway, but the present disclosure is not limited thereto. As shown inFIG.1toFIG.5, the linear guideway100in the present embodiment includes a track10having an elongated shape, a sliding module20slidably disposed on the track10along a sliding direction D, and two end modules30that are respectively assembled to two opposite ends of the sliding module20and that are slidably disposed on the track10. It should be noted that the sliding module20in the present embodiment is described in cooperation with the track10and the two end modules30, but the present disclosure is not limited thereto. For example, in other embodiments of the present disclosure not shown in the drawings, the sliding module20can be independently used (e.g., sold) or can be used in cooperation with other components. As shown inFIG.2,FIG.4, andFIG.5, a longitudinal direction of the track10defines the sliding direction D, and the track10has an upper surface101and two lateral surfaces102that are arranged on two opposite sides thereof. In the present embodiment, the track10has a straight shape, and the upper surface101and the two lateral surfaces102are parallel to the sliding direction D, but the present disclosure is not limited thereto. For example, in other embodiments of the present disclosure not shown in the drawings, the track10can be curved. As shown inFIG.4toFIG.6, the sliding module20in the present embodiment includes a slider1, two circulation seats2assembled to the slider1, a plurality of rollers3(e.g., rolling balls), and a plurality of dustproof members4that are assembled to the slider1and that are abutted against the track10. It should be noted that the two circulation seats2in the present embodiment are described in cooperation with the slider1, the rollers3, and the dustproof members4, but the present disclosure is not limited thereto. For example, in other embodiments of the present disclosure not shown in the drawings, the circulation seat2can be independently used (e.g., sold) or can be used in cooperation with other components. Moreover, the two end modules30are respectively assembled to two end surfaces11of the slider1, so that the sliding module20and the two end modules30can jointly define a plurality of rolling paths P, and the rollers3are respectively movable along the rolling paths P. Each of the rolling paths P is a closed loop, and the rolling paths P respectively correspond in position to the two lateral surfaces102. Furthermore, two ends of each of the dustproof members4are respectively fixed to the two end modules30, and the dustproof members4are respectively abutted against the upper surface101and the two lateral surfaces102of the track10, thereby isolating the rolling paths P from an external environment so as to achieve a dustproof effect. The slider1in the present embodiment has an elongated shape, and the sliding direction D can be defined by a longitudinal direction of the slider1. The slider1includes a base portion12and two lateral wing portions13that respectively extend from the base portion12, and the two end surfaces11of the slider1are perpendicular to the sliding direction D. Moreover, an inner side of the base portion12faces toward the upper surface101of the track10, and inner sides of the two lateral wing portions13respectively face toward the two lateral surfaces102of the track10. Each of the two circulation seats2is limited to having an inherently one-piece structure, so that any circulation seat formed by assembling more than one component is different from the circulation seat2described in the present embodiment. The two circulation seats2are respectively assembled to the two lateral wing portions13of the slider1and respectively correspond in position to the two lateral surfaces102. As the two circulation seats2in the present embodiment are of the substantially same structure or are in a mirror-symmetrical arrangement, the following description discloses the structure of just one of the two circulation seats2for the sake of brevity, but the present disclosure is not limited thereto. For example, in other embodiments of the present disclosure not shown in the drawings, the two circulation seats2can be of different structures. As shown inFIG.6toFIG.9, the circulation seat2in the present embodiment includes two turning portions21, a middle retaining portion22, and two lateral retaining portions23. Each of the middle retaining portion22and the two lateral retaining portions23is connected to and arranged between the two turning portions21. Each of the middle retaining portion22and the two lateral retaining portions23is parallel to the sliding direction D and has a length that is within a range from 20 mm to 175 mm, but the present disclosure is not limited thereto. Specifically, the two turning portions21are respectively disposed on the two end surfaces11of the slider1. In other words, each of the two end surfaces11of the slider1is provided with one of the two turning portions21of each of the two circulation seats2to be disposed thereon, so that each of the two end modules30covers one of the two turning portions21of each of the two circulation seats2(i.e., each of the two end modules30covers two of the turning portions21that are adjacent to each other and that respectively belong to the two circulation seats2). The middle retaining portion22is limited to having a two-stepped structure parallel to the sliding direction D. In other words, a structure of the middle retaining portion22in the present embodiment excludes a structure that is different from the two-stepped structure (e.g., a three-stepped structure), thereby facilitating two ends of the middle retaining portion22to be integrally connected to the two turning portions21, respectively. Accordingly, the circulation seat2integrally formed as the single one-piece structure can be implemented. The middle retaining portion22(or the two-stepped structure) in the present embodiment includes a connection bar221and a limiting bar222that is connected to the connection bar221. The limiting bar222of the middle retaining portion22and any one of the two lateral retaining portions23respectively define two opposite sides of one of the rolling paths P, and can be further cooperated with the two turning portions21so as to enable the one of the rolling paths P to have the closed loop. Moreover, each of the limiting bar222of the middle retaining portion22and the two lateral retaining portions23has an injection groove2222,232formed on a boundary surface2221,231adjacent to the track10. The boundary surfaces2221,231are parallel to each other, the boundary surfaces231of the two lateral retaining portions23are coplanar with each other, and the injection groove2222of the limiting bar222is spaced apart from the injection grooves232of the two lateral retaining portions23by a same distance, thereby enabling the circulation seat2to be integrally formed as the single one-piece structure. Specifically, the connection bar221is connected to and arranged between the two turning portions21, and a distance between two long lateral surfaces2211of the connection bar221gradually increases along a direction away from the limiting bar222. The two long lateral surfaces2211of the connection bar221in the present embodiment have an arrangement angle σ221therebetween that is within a range from 20 degrees to 45 degrees, thereby facilitating connection of two ends of the connection bar221to the two turning portions21, respectively. Moreover, in a cross section of the circulation seat2perpendicular to the sliding direction D (as shown inFIG.9), the connection bar221has a trapezoidal cross section, and a bottom edge of the trapezoidal cross section has a length L221that is within a range from 60% to 80% of a length L222of the boundary surface2221of the limiting bar222, but the present disclosure is not limited thereto. The above description describes the structure of the circulation seat2, and the following description describes the connection relationship of the components of the sliding module20, but the present disclosure is not limited thereto. As shown inFIG.3andFIG.5, in each of the two circulation seats2, the connection bar221and any one of the two turning portions21can jointly define a notch24. Each of the two end modules30includes two mating blocks301each corresponding in shape to any one of the notches24, and the mating blocks301of the two end modules30are respectively inserted into the notches24of the two circulation seats2. Furthermore, ends of the two long lateral surfaces2211of the connection bar221can be coplanar with surfaces of the two turning portions21adjacent thereto and surfaces of the two mating blocks301adjacent thereto. In summary, the circulation seat2provided by the present embodiment is integrally formed as the single one-piece structure, so that the notches24can be precisely manufactured for facilitating each of the notches24and the corresponding mating block301to be precisely cooperated with each other. Accordingly, issues related to assembling tolerances of the conventional middle retainer can be effectively avoided in the circulation seat2of the present embodiment. As shown inFIG.5andFIG.10toFIG.12, each of the dustproof members4in the present embodiment has an inherently one-piece structure (e.g., a rubber member), and two ends of each of the dustproof members4are detachably engaged with the two end modules30, respectively, so that each of the dustproof members4can be assembled to the two end modules30without using any fixing component (e.g., a screw) for achieving rapid assembly. In addition, the cooperation structures of each of the dustproof members4and the two end modules30can be adjusted or changed according to design requirements, and are not limited by the drawings of the present embodiment. Specifically, the dustproof members4include an upper dustproof member41and two lower dustproof members42. The upper dustproof member41has a fixing segment411and two dustproof segments412that are respectively connected to two opposite sides of the fixing segment411. Each of the fixing segment411and the two dustproof segments412is elongated and is parallel to the sliding direction D. Each of the two dustproof segments412includes a carrying bar4121, an inner rib4122, and an outer rib4123, the latter two of which are connected to the carrying bar4121. Moreover, the carrying bar4121, the inner rib4122, and the outer rib4123of each of the two dustproof segments412are elongated and are parallel to the sliding direction D, and the outer ribs4123of the two dustproof segments412are respectively located at two opposite sides of the inner ribs4122of the two dustproof segments412, but the present disclosure is not limited thereto. It should be noted that as the two dustproof segments412in the present embodiment are mirror-symmetrical with respect to the fixing segment411, the following description discloses the structure of just one of the two dustproof segments412for the sake of brevity, but the present disclosure is not limited thereto. For example, in other embodiments of the present disclosure not shown in the drawings, the two dustproof segments412can be of different structures. In the present embodiment, inner side surfaces41221,41231of the inner rib4122and the outer rib4123are arranged adjacent to each other and are parallel to the sliding direction D, and outer side surfaces41222,41232of the inner rib4122and the outer rib4123are arranged away from each other and are parallel to the sliding direction D. Moreover, cross sections of the inner rib4122and the outer rib4123perpendicular to the sliding direction D are substantially the same, but the present disclosure is not limited thereto. For example, in other embodiments of the present disclosure not shown in the drawings, the cross sections of the inner rib4122and the outer rib4123perpendicular to the sliding direction D can be different from each other. Specifically, in a cross section of the dustproof segment412perpendicular to the sliding direction D (as shown inFIG.11), the outer side surface41222of the inner rib4122and the outer side surface41232of the outer rib4123can virtually extend to form an isosceles triangle T1having a top angle σ41that is within a range from 10 degrees to 30 degrees. The top angle641is preferably within a range from 15 degrees to 25 degrees, but the present disclosure is not limited thereto. Accordingly, in the dustproof segment412of the present embodiment, the outer side surface41222of the inner rib4122and the outer side surface41232of the outer rib4123can be designed to have a suitable structural condition through the isosceles triangle T1and the top angle σ41, so that the inner rib4122and the outer rib4123can provide a better supporting force for enabling the inner rib4122and the outer rib4123to need only a relatively low interference with respect to the track10. As shown inFIG.4,FIG.11, andFIG.12, a free end edge41223of the inner rib4122(e.g., a junction of the inner side surface41221and the outer side surface41222) is abutted against the upper surface101of the track10so as to form an inner interference distance within a range from 0 mm to 0.05 mm. Moreover, a free end edge41233of the outer rib4123(e.g., a junction of the inner side surface41231and the outer side surface41232) is abutted against the upper surface101of the track10so as to form an outer interference distance that is greater than the inner interference distance. The outer interference distance is preferably within a range from 0.05 mm to 0.1 mm, but the present disclosure is not limited thereto. In the dustproof segment412of the present embodiment, a deformation of the inner rib4122with respect to the track10can be reduced to approach zero through the above structural design of the inner rib4122and the outer rib4123, thereby preventing dust or particles from slipping into an interface between the inner rib4122and the upper surface101of the track10. Accordingly, the inner rib4122can be maintained to be gaplessly abutted against the upper surface101of the track10for increasing the dustproof effect. As shown inFIG.11, in the cross section of any one of the two dustproof segments412, the inner side surface41221of the inner rib4122and the inner side surface41231of the outer rib4123have an angle σ412therebetween within a range from 10 degrees to 30 degrees, the inner rib4122has an isosceles triangle having a top angle σ4122that is within a range from 10 degrees to 30 degrees, and the outer rib4123has an isosceles triangle having a top angle σ4123that is within a range from 10 degrees to 30 degrees. The above description describes the upper dustproof member41, and the following description describes the two lower dustproof members42. As shown inFIG.4andFIG.13toFIG.15, the two lower dustproof members42are respectively abutted against the two lateral surfaces102of the track10. It should be noted that as the two lower dustproof members42in the present embodiment are in a mirror-symmetrical arrangement, the following description discloses the structure of just one of the two lower dustproof members42for the sake of brevity, but the present disclosure is not limited thereto. For example, in other embodiments of the present disclosure not shown in the drawings, the two lower dustproof members42can be of different structures. Specifically, the lower dustproof member42includes an assembling segment421, an upper rib422connected to the assembling segment421, a lower rib423connected to the assembling segment421, and a reinforced rib424that is connected to the upper rib422and the lower rib423. Each of the assembling segment421, the upper rib422, the lower rib423, and the reinforced rib424is elongated and is parallel to the sliding direction D. In other words, the assembling segment421, the upper rib422, the lower rib423, and the reinforced rib424are parallel to each other. Moreover, each of the upper rib422and the lower rib423has an inner surface4221,4231and an outer surface4222,4232that is opposite to the inner surface4221,4231. The inner surface4221of the upper rib422is spaced apart from and arranged adjacent to the inner surface4231of the lower rib423. The reinforced rib424is integrally connected to the inner surface4221of the upper rib422and the inner surface4231of the lower rib423so as to jointly define a substantially trapezoidal space that is parallel to the sliding direction D. In the present embodiment, cross sections of the upper rib422and the lower rib423perpendicular to the sliding direction D are substantially the same, but the present disclosure is not limited thereto. For example, in other embodiments of the present disclosure not shown in the drawings, the cross sections of the upper rib422and the lower rib423perpendicular to the sliding direction D can be different from each other. Specifically, in a cross section of any one of the lower dustproof members42perpendicular to the sliding direction D (as shown inFIG.14), the outer surface4222of the upper rib422and the outer surface4232of the lower rib423can virtually extend to form an acute angle σ42within a range from 15 degrees to 25 degrees, and an angle σ424between the reinforced rib424and the inner surface4231of the lower rib423is preferably within a range from 110 degrees to 150 degrees. Accordingly, in the lower dustproof member42of the present embodiment, the outer surface4222of the upper rib422and the outer surface4232of the lower rib423can be designed to have a suitable structural condition through the specific range of the acute angle σ42, so that the upper rib422and the lower rib423can provide a better supporting force for enabling the upper rib422and the lower rib423to need only a relatively low interference with respect to the track10. Specifically, in each of the two lower dustproof members42, a free end edge4223of the upper rib422(e.g., a junction of the inner surface4221and the outer surface4222) is abutted against the corresponding lateral surface102of the track10so as to form an upper interference distance within a range from 0 mm to 0.05 mm. Moreover, a free end edge4233of the lower rib423(e.g., a junction of the inner surface4231and the outer surface4232) is abutted against the corresponding lateral surface102of the track10so as to form a lower interference distance within a range from 0 mm to 0.05 mm. In the lower dustproof member42of the present embodiment, a deformation of any one of the upper rib422and the lower rib423with respect to the track10can be reduced to approach zero through the above structural design of the upper rib422and the lower rib423, thereby preventing dust or particle from slipping into an interface between the upper rib422(or the lower rib423) and the corresponding lateral surface102of the track10. Accordingly, the upper rib422(or the lower rib423) can be maintained to be gaplessly abutted against the corresponding lateral surface102of the track10for increasing the dustproof effect. Beneficial Effects of the Embodiments In conclusion, in any one of the linear guideway, the sliding module, and the circulation seat provided by the present embodiment of the present disclosure, the circulation seat can be integrally formed as a single one-piece structure through the structural design of the middle retaining portion (e.g., the middle retaining portion is the two-stepped structure, and a distance between two long lateral surfaces of the connection bar gradually increases along a direction away from the limiting bar), thereby effectively avoiding problems associated with the middle retainer of the conventional linear guideway (e.g., the problems related to alignment accuracy requirements, assembling tolerances, and stress concentration due to rotation). Moreover, in the linear guideway provided by the present embodiment of the present disclosure, the circulation seat is formed with the above specific structural design, e.g., the arrangement angle being within a range from 20 degrees to 45 degrees, the injection groove of the limiting bar being spaced apart from the injection grooves of the two lateral retaining portions by the same distance, and the length of the bottom edge of the trapezoidal cross section of the connection bar being 60% to 80% of the length of the boundary surface of the limiting bar, thereby enabling the circulation seat to be integrally formed as the single one-piece structure in a stable manner. The foregoing description of the exemplary embodiments of the disclosure has been presented only for the purposes of illustration and description and is not intended to be exhaustive or to limit the disclosure to the precise forms disclosed. Many modifications and variations are possible in light of the above teaching. The embodiments were chosen and described in order to explain the principles of the disclosure and their practical application so as to enable others skilled in the art to utilize the disclosure and various embodiments and with various modifications as are suited to the particular use contemplated. Alternative embodiments will become apparent to those skilled in the art to which the present disclosure pertains without departing from its spirit and scope. | 23,270 |
11859664 | DETAILED DESCRIPTION Reference is made toFIGS.1-6for various views of an example embodiment of a multi-piece pinion shaft assembly100according to the teachings of the present disclosure. The pinion shaft assembly100includes a linear tubular member102with a circular bore and first and second pinion gear members104and106that are affixed to the two ends of the tubular member102. The first pinion gear member104includes a pinion gear108and a generally cylindrical-shaped interference fit coupling extension110(FIG.3) that has an outside diameter that corresponds to an inside diameter of the first end112of the tubular member102to achieve a tight fit therebetween. The coupling may be achieved by shrink fitting, press fitting, friction fitting, or another suitable interference fitting technique. The interference coupling extension110of the first end member104further includes an alignment key114that corresponds to a slot defined on the inner wall of the first end112of the tubular member. The alignment key114, when disposed in a seat defined in the interference coupling extension110, protrudes beyond the outside diameter surface of the interference coupling extension110. The use of the alignment key114enables the pinion gear member104to be inserted and received into the first end112of the tubular member102in the correct rotational orientation, and helps to prevent rotation of the first pinion gear member104relative to the tubular member102. The first end112of the tubular member102further includes a bearing interface116proximate to the pinion gear member104for receiving roller bearings502(shown inFIGS.5and6). The second pinion gear member106includes a pinion gear120and a generally cylindrical-shaped interference coupling extension122(FIG.3) that has an outside diameter that corresponds to an inside diameter of the second end124of the tubular member102to achieve a tight friction fit therebetween. The interference coupling extension122of the second pinion gear member106further includes an alignment key126that corresponds to a slot defined on the inner wall of the first end124of the tubular member102. The alignment key126, when disposed in a seat defined in the interference coupling extension122, protrudes beyond the outside diameter surface of the interference coupling extension122. The use of the alignment key126enables the pinion gear member106to be inserted and received into the second end124of the tubular member102in the correct rotational orientation, and helps to prevent rotation of the second pinion gear member106relative to the tubular member102. The second pinion gear member106further includes an extended shaft portion130for coupling with a power source, such as a motor or engine. The extended shaft portion130may include a keyway132such as a longitudinally-oriented groove or slot formed therein, splines or any other mechanism that facilitates coupling to the power source. The second end124of the tubular member102further includes a bearing interface136proximate to the pinion gear member106for receiving roller bearings500(shown inFIGS.5and6). It should be noted that the alignment key114,126may be implemented with alternate suitable mechanisms such as splines, pins, and threaded engagement. As another example, a spring-loaded detent mechanism disposed in the interference coupling extension of the pinion gear member may engage an indentation formed in the inner wall of the tubular member when the pinion gear member is inserted into the tubular member at the correct depth and correct rotational orientation. Further, the shape of the interference coupling extension of the pinion gear members and the tubular member bore may be non-circular, such as square, hexagonal, octagonal, and any suitable shape. It should be noted that assembling the pinion gear members with the tubular member may include cooling the interference coupling extension and/or heating the tubular member so that the parts may be assembled with minimal interference and force. Conventional single-piece pinion shaft implementations suffer from disadvantages of having to correct deformation of the shaft due to heat treatment of the gear teeth. Constructed of separate pieces of materials, the tubular member102, and end members104and106may be fabricated and machined separately and then assembled together. Rather than being fabricated from a single solid piece of material, the tubular member102may be made from a hollow tube with the advantage of a significant reduction in weight. Further, the pinion gear teeth of the pinion gear members104and106may undergo manufacturing steps such as heat treatment without inadvertently damaging or distorting the shaft. The assembly of the pinion gear members104and106onto the tubular member102may be achieved without the use of torque tools as interference coupling is used without the use of fasteners. Being formed of separate pieces, the pinion gear members may be serviced without replacing the entire pinion shaft component. Because the tubular member and the pinion gear members are fabricated separately, they may be constructed from the same or different materials using the same or different manufacturing processes to achieve optimal results. It should be noted that the interference coupling extensions110and122and the ends112and124of the tubular member102may have other corresponding shapes such as, for example, rectangular extensions for insertion into rectangular cavities. FIG.7is a cross-sectional view of a reciprocating pump700that incorporates the multi-piece pinion shaft assembly100described herein. The reciprocating pump700includes a fluid end702and a power end704operably coupled thereto. The fluid end702includes one or more cylinders706, each of which includes a fluid chamber708. The fluid chambers708are in fluid communication with a suction manifold710and a discharge manifold712. The fluid end702further includes plungers714that operate within the fluid chambers708. Each plunger714is adapted to reciprocate within the corresponding fluid chamber708during operation of the reciprocating pump700. The power end704of the reciprocating pump700includes a crankshaft716that includes one or more crank throws, corresponding to the one or more cylinders706of the fluid end702, and a main shaft. The crank throws are connected to the main shaft and are each offset from the rotational axis of the crankshaft. The crankshaft716is mechanically coupled to a power source (not shown) via a bull gear718and a pinion720(e.g., multi-piece pinion shaft assembly100). The bull gear718is attached to the crankshaft716and the pinion720is connected to a power source or motor (not shown). The gear teeth of the bull gear718mesh with the gear teeth of the pinion720, thereby transmitting torque therebetween. The crank throws are each coupled to a respective one of the plungers714via a mechanical linkage722, each of which includes a connecting rod724, a crosshead726, and a pony rod728. Each of the crossheads726is disposed within a corresponding crosshead bore730, within which the crosshead726is adapted to reciprocate. The connecting rods724connect respective ones of the crossheads726to respective ones of the crank throws. Further, the pony rods728connect respective ones of the crossheads726to respective ones of the plungers714. In operation, the power source or motor (not shown) rotates the shaft of the multi-piece pinion assembly100, which rotates the pinion gear teeth of the pinion gear members104and106that engage the bull gear718and the crankshaft716. The crankshaft716rotates the crank throws about the central axis of the main shaft. The crank throws, in turn, are operable to drive the mechanical linkages722, including respective ones of the connecting rods724, the crossheads726, and the pony rods728, causing the crossheads726to reciprocate within the corresponding crosshead bores730. The reciprocating motion of the crossheads726is transferred to respective ones of the plungers714via the pony rods728, causing the plungers714to reciprocate within the corresponding fluid chambers708. As the plungers714reciprocate within the respective fluid chambers708, fluid is allowed into the pressure chambers708from the suction manifold710and, thereafter, discharged from the pressure chambers708into the discharge manifold712. The features of the present disclosure which are believed to be novel are set forth below with particularity in the appended claims. However, modifications, variations, and changes to the exemplary embodiments described above will be apparent to those skilled in the art, and the multi-piece pinion shaft assembly described herein thus encompasses such modifications, variations, and changes and are not limited to the specific embodiments described herein. | 8,787 |
11859665 | DETAILED DESCRIPTION FIG.1shows a drive arrangement20, which drives a component22through a drive input24. A drive shaft26connects the input24to the output22. As one example, component22may be helicopter propellers. The drive shaft26may be formed of composite materials. Drive shafts26coming within the scope of this disclosure may be formed of fiber reinforced polymer matrix composite materials. In particular, the matrix can be a thermoplastic polymer. Different types of reinforcing fibers, such as, for example, carbon fibers, glass fibers, organic fibers, inorganic materials (e.g., ceramic) fibers, or their combinations can be used in different embodiments. In addition, while thermoplastic polymers are preferred, thermoset polymers may benefit from some of the structural details disclosed below. FIG.2Ashows a concern with a known shaft26during operation. Shaft26extends between ends28aand28b. There are “wrinkles”28that may be formed along the length of the shaft26due to local instability (buckling) from the torque moment29transmitted through the drive shaft26. These wrinkles are shown inFIG.2Aas an example of shear stress distribution, calculated by finite element method for a representative thin-walled composite drive shaft. FIG.2Billustrates a diametric cross-section in the center of a composite drive shaft shown inFIG.2Abefore and after the event of local buckling. As shown inFIG.2B, the wrinkles28can move the shaft26from its original cylindrical shape27such that it has cross-sectional deformation at28. FIGS.3-6below show axial cross-sections of designs of composite drive shafts.FIG.3Ashows known shaft26having a uniform outer and inner surfaces. FIG.3Bshows a first embodiment30wherein the drive shaft has a nominal hollow tubular member32with a ring member34adhered to the outer periphery. The member ring34will resist the local buckling deformation under torsional moment, if bending stiffness of the ring member is sufficiently high. The bending stiffness of the ring member in the hoop direction is preferably, at least twice as high as the bending stiffness of a tubular member wall segment with the same width as the ring. FIG.3Cshows an embodiment31, which is similar to embodiment30except the ring member34is between an inner wall, tubular member32and an outer wall36. A ramp or bump38is formed in the outer wall36to enclose the ring member34. FIG.3Dshows yet another embodiment39, similar to embodiment31, but wherein there is an extra wrap40having a bump42at the location of the bump38. The wrap40can minimize risk of debonding between the ring member34and outer wall36. Also, the wraps may help secure the ring34to the underlying tubular member32. Further, the wraps can provide better adherence. In addition, by selecting materials for the wraps, any number of other features or characteristics can be placed into the tubes. FIG.3Eshows an embodiment43similar to the embodiment39, however, additional wraps50and52are placed outwardly of the wrap40.FIG.3Eillustrates a case with three wraps, however, different number of the wraps can be used according to specifics of designs, applications and load conditions. FIG.3Fshows an embodiment54having an underlying tubular member32with ring members60and64. An outer wrap66is placed outwardly of ring members60and64. Another ring member62is placed axially intermediate ring members60and64, and radially intermediate the wrap66and an outer wrap68. Another wrap70is placed outwardly of the wrap68. Similarly toFIG.3E, different number of wraps and unconnected individual rings can be used according to the specifics of requirements. FIG.4Ashows an embodiment70wherein the ring member76is on an inner surface73of the tubular member72. The tube72has an outwardly extending bump74to accommodate ring76. FIG.4Bshows an embodiment80, which is similar to embodiment70, however, an additional wrap82is placed outward of the bump74. FIG.4Cshows an embodiment84. Here, additional wraps86and88are added to the embodiment80. In other embodiments, different number of wraps can also be used. FIG.4Dshows an embodiment90. Here, two ring members94are axially spaced at a radially inner surface of an inner shaft92. Another ring member100is placed axially intermediate ring members94, and radially intermediate inner shaft92and an outer shaft102. Another wrap104is placed radially outward of the wrap102. In other embodiments, different number of wraps and/or individual un-connected rings can also be used. FIG.5Ashows an embodiment110wherein ring members114and116are placed both radially outwardly and radially inwardly of the tube112. FIG.5Bshows an embodiment120similar toFIG.3C, having an outer ring122outward of the ring126and an inner ring124. The rings illustrated so far have been generally rectangular, or close to rectangular, in cross-section. Here “generally rectangular” shapes also include similar shapes with upper and lower surfaces of the ring parallel or almost parallel to each other with curved shapes at other side surfaces (e.g., corners at the left and right atFIGS.3-5). FIG.6Ashows an embodiment130wherein the tube132has an L-shaped (in cross-section) ring member134. L-shaped ring member134is defined as having an axially extending contact portion136, in contact with the outer periphery133of the tube132. Radially outwardly extending ring138extends radially outwardly from the portion136. An optional wrap137has a portion140secured to the outer surface133and a portion142radially outward of the portion136of the ring134. FIG.6Bshows an embodiment150having a pair of L-shaped ring members134having the radially outwardly extending surfaces138facing each other. Both can be provided with optional wraps139. FIG.6Cshows an embodiment wherein the ring member162has an I-shape (in cross-section) with a contacting portion168in contact with the outer periphery133of the inner shaft132. A radially outwardly extending portion164extends to a radially outward thicker portion166. Optional wraps174are secured on each axial end of the portion164and to the contact portion168. L- and I-shaped rings can have advantages in providing higher bending stiffness per weight in comparison, for example, with rings with rectangular cross-sections.FIG.6Dshows a ring182having an outer periphery184that has a part circular or similar curved convex shape in the cross-section. A contact portion183is in contact with an outer surface179of the tube181. An outer optional wrap186is also secured at ends187to the outer surface179and to the ring182. FIG.6Eshows an embodiment190wherein the ring member192has a pair of different material portions193and194. Similarly, rings with more than two materials can be used in other embodiments. Again, a ring member196may be spaced on an opposed side of the tube194from the ring192. The materials may be selected to achieve particular benefits. FIG.6Fshows an embodiment200wherein the tube202receives a ring member204that has a hollow206. The hollow206may also be filled by various materials, or may be left empty. An optional wrap208may also be secured outwardly of the ring204. FIG.7Ashows the embodiments220such as has been illustrated to this point and having a tubular member222with a ring member224extending about the entire circumference. FIG.7Bshows embodiment230wherein the tube222may receive a ring member224extending across the entire circumference, but may also receive isolated ring portions232extending between circumferential ends234extending through an angle A. In this embodiment, angle A may be 90°. Further, the ring portions232may be utilized without the full hoop ring224in some embodiments. FIG.7Cshows an embodiment330wherein the tube322and the full hoop ring member324receive ring portions332extending between circumferential ends334. Here, circumferential ends334extend through an angle B. In one embodiment, angle B is 60°. FIG.7Dshows an embodiment430wherein the tubular member422has the ring member424and the ring portions432. Ring portions432extend between ends434. Ends434extend through a circumferential extent of an angle C. In embodiments, angle C is 45°. FIG.7Eshows an embodiment500wherein a tubular member522does not receive a full hoop ring. Rather, only the circumferentially spaced ring portions524are utilized. While the embodiment500resemblesFIG.7Dand its spacing, it should be understood that the other ring portions ofFIGS.7B and7Ccan be utilized without the underlying full hoop structure. The number and sizes of ring portions can be different in other embodiments and can be defined by design optimization driven, for example, by criteria of weight reduction. FIG.8shows a feature with regard to a tubular member600having a center axis606. The ring member602may be formed to be perpendicular relative to the axis606. On the other hand, a ring604may extend at an angle such that it is not perpendicular to the axis606. The angle α here may be selected to provide various functions to optimize the drive shaft design for specific loading conditions. For example, one may account for bending and axial load components in addition to the torque. Angle α can be either uniform or non-uniform along the ring length. FIG.9Ashows an example700wherein tubular member702receives a plurality of ring members704, which are all perpendicular to the axis708. FIG.9Bshows an embodiment710wherein the tubular member702receives a plurality of ring members712, which are all formed at a slope, such as shown in604inFIG.8. FIG.9Cshows an embodiment730wherein the tubular member732receives ring members740at a slope relative to the axis708and other ring members750extending in an opposed angle relative to the angle α1that the ring members740are sloped relative to axis708. The angle α2that the ring members750are sloped with regard to the axis708may be equal to, but in an opposed direction from the angle E. At least one of the plurality of ring members could be said as having a central axis Zswhich is non-perpendicular to a central axis708of the tubular member732. At least one of the central axis Zoof at least one of the plurality of ring members extends in an opposed direction relative to the central axis Zsof at least another of the plurality of the rings. FIG.9Dshows an embodiment750wherein the underlying tubular member732receives angled ring members740and750, extending in opposed directions, and perpendicularly positioned ring members704. In addition, a ring portion760is formed only at an end761. FIG.9Eshows an embodiment780wherein a tubular member781has ring members782and784extending at a slope, but in opposed directions, similar to theFIG.9CorFIG.9Dembodiments. However, the ring members782and784also intersect at points786. Opposite directions of ring members782and784can be the same or different. Different angles of ring members782and784can be especially helpful in case of dominant torque in one direction. The ring members extending at a single slope, such as shown inFIG.9B, might be especially helpful if torque is primarily applied in one direction. On the other hand, the embodiment ofFIG.9Cmay be helpful if there is rotation passing in both directions through the shaft. With regard to the sloped ring members, it could be said that they extend at an angle relative to a central axis of the tubular member such that the outer peripheral surface of the ring members lies at different axial positions on an outer periphery of the tubular member measured along the central axis708. FIG.10shows a feature of the disclosed shafts. A tubular member810has ring members812spaced along an axial dimension. There will still be deformation at814under torque815, such as the “wrinkle” mentioned with regard toFIG.2A. However, as can be appreciated, by shortening the length LSthrough which the deformation814extends, the magnitude of the deformation will also be reduced. Here, the wrinkles are shown as distributions of shear stresses calculated by the finite element method for a problem similar to one shown atFIG.2but with added rigid rings. FIG.11Ashows a feature900wherein the tubular member902has a plurality of equally spaced ring member904. The ring member904inFIG.11Aare spaced by an axial distance L1. FIG.11Bshows an embodiment910wherein a tubular member912receives ring members914,916, and918. The ring members in the embodiment910are spaced by axial distances L2, L3, and L4. As can be appreciated, L2-L4are not all the same length. The lengths can be selected based upon an understanding that a buckling moment is approximately inversely proportional to the square root of the length L. A formula is shown below which will help select lengths L for a tube having a radius R. MT=˜21.75*(DΘΘ{circumflex over ( )}(5/8))*(Exx{circumflex over ( )}(3/8))*(RA(5/4))/(L{circumflex over ( )}(1/2)) Here DΘΘis the bending stiffness of the drive shaft wall in the hoop direction, and Exxis the axial stiffness of the wall, respectively. A method of attaching ring member using the Automated Fiber Placing (AFP) method is shown at1000inFIG.12A. A tubular member1002is shown receiving a material1004. The material1004comes from a source, with a feed mechanism. A consolidation roller1008is rolling the material1004on an outer peripheral surface1009. A heater1010is providing heat to the material to cause it to deform and adhere to the outer surface1009. A beginning point1012of the material1004is shown. If a full ring is utilized, once the material1006reaches the end1020, a cutter1014cuts the material. Of course, in the embodiments having partial ring portions, the cutting would occur at the appropriate ends. FIG.12Bshows an embodiment1100showing a method similar to that ofFIG.12A. Common features are indicated by reference numerals100larger than those shown inFIG.12A. However, the material1104is placed in an axial direction along an axis A of the tubular member1102or any other directions in addition to the axial and hoop directions. The embodiment shown inFIG.12Bcan be used to fabricate rings in non-circumferential directions (e.g., shown inFIGS.9B-9E) and/or to fabricate bodies of composite shafts with multi-directional laminated layups. The method shown inFIGS.12A and12Bis generally known as automated fiber placement (AFP) or automated tape laying (ATL). A drive shaft according to this disclosure could be said to include a tubular member extending between axial ends and being hollow. The tubular member is formed of a thermoplastic matrix with embedded fibers. There is at least one ring member positioned radially of the tubular member. The “positioned radially” language should be understood to cover on an outer peripheral surface, an inner peripheral surface or at a radially intermediate location within the radial extend of the tubular member. The tubular member extends across 360°, and the ring member may also extend across 360°. Alternatively the tubular member may extend through 360° and the ring member extends through less than 360°. That is, the rings are formed of a plurality of spaced ring portions, such that the ring does not extend across 360°. A wrap may be placed on an opposed side of the ring member relative to the at least one of the inner and outer peripheral surfaces. There may also be a plurality of the ring member, with one ring member placed on the outer peripheral surface and a second of the ring members placed on an inner peripheral surface. There may be a plurality of ring members spaced along an axial length of the tubular member. An axial distance along a central axis of the tubular member is defined between each of the plurality of rings. The axial distance may be uniform across an axial length of the tubular member. Alternatively, an axial distance between adjacent ones of the rings along an axial length of the tubular member may be non-uniform. The ring member may be at least part circular in cross-section. Alternatively, the ring member may be non-circular in cross-section. The ring member may be a part circular cross-section. A method of forming a drive shaft could be said to include the steps of forming a tubular member extending along an axis, and having an inner peripheral surface and an outer peripheral surface. Further, the method includes the steps of forming at least one ring member by placing a material on one of the inner peripheral surface and outer peripheral surface, and heating the material. Radial pressure is applied to the material in a sequentially moved fashion. The material is adhered to the one of inner and outer peripheral surface. A method of forming a drive shaft could also be said as providing the steps of forming a tubular member extending along an axis, and having an inner peripheral surface and an outer peripheral surface. A ring portion in this format on at least one of the inner and outer peripheral surfaces by placing a material on the at least one of the inner and outer peripheral surfaces, applying a roller to the material to adhere the material to the at least one of the inner and outer peripheral surfaces while applying heat to the material. While the automated fiber placement is the preferred method, various other methods may be utilized. As an example, when the tubular member is a composite, the composite tube could be formed as a continuous element or assembly of segments. The rings may be formed separate from the tube, rather than being formed on the tube. The additional wraps may be attached utilizing automated fiber placement about the rings or can be attached by other methods. The ring member and tubular member can be secured together by solidifying when the thermoplastic is utilized for both the tube and the rings. In addition, welding can be utilized if thermoplastic is utilized for both the tube and the rings. If a thermoset is used, the ring can be cured onto the tube. Further, the materials can be pre-cured or partially-cured. In addition, radial fasteners, glue or any combination of the various attachment methods disclosed above may be utilized. It could also be said that this disclosure provides a drive shaft with a tubular member extending between axial ends and being hollow. The tubular member is formed of a thermoplastic matrix with embedded fibers. There is a ring on the tubular member. The ring may be on an outer peripheral portion as shown in some Figures, on an inner peripheral portion, as shown in other Figures, or intermediate the inner and outer peripheral portions, shown in yet other Figures. Further, there may be a plurality of rings. To the extent these teachings extend to a drive shaft with a metallic tubular member, the metallic tubular member could be formed of a continuous element or an assembly of segments. The ring member can be formed separately. The rings can be assembled with the tube and the rings with or without extra wraps. Welding can be utilized if the ring is also metallic. If the rings are thermoplastic, they can be solidified onto the tubular member. If the ring is thermoset, it can be cured, pre-cured, or partially cured and then placed onto the metallic tubular member. Again, radial fasteners, adhesives, or any combination of the above may be utilized. It should be understood across these embodiments that the wraps are optional and the ring may stand alone. The rings can be formed of a composite and the wraps may be formed of a composite. Alternatively, the rings may be metallic or the wraps may be formed of a metallic material. In addition, while composite shaft are the main focus of this disclosure, many of the structural combinations disclosed here would benefit metallic shafts. Any combination of composite and material shafts/rings/wraps may come within the scope of this disclosure. Several embodiments are disclosed above. A worker of ordinary skill in this art would recognize that certain modifications would come within the scope of this disclosure. For that reason, the following claims should be studied to determine the true scope and content of this disclosure. | 20,025 |
11859666 | DETAILED DESCRIPTION A detailed description of one or more embodiments of the disclosed apparatus and method are presented herein by way of exemplification and not limitation with reference to the Figures. The present disclosure incorporates magnetic bearings as one or all of the bearing elements in a rotary separator. The term magnetic bearing includes actively controlled or passive magnetic bearings. The magnetic bearings in these configurations may also be canned, which allows for the ability to hermetically seal the separator. Magnetic bearing rotary phase separators minimize wear, improve external load performance, reduce maintenance, extend life, remove the need for lubricant, accommodate a wide range of running speeds, and allow for easily measured and readily changed dynamic properties. They can also be used in harsh environmental conditions, including extremely low temperatures, zero-gravity, and corrosive environments. Referring to the Figures, a cross-sectional view of an embodiment of a magnetic bearing rotary phase separator10is shown inFIG.1. The rotary phase separator10separates phases of the liquid/gas mixture by using a motor12to drive a shaft14having a plurality of disks16and cylinders18that contact the liquid/gas mixture to spin the liquid such that centrifugal force drives the liquid toward an outer diameter20thereby creating a liquid ring22that displaces gas. The gas then migrates toward the center to create a gas core24. The liquid and gas are then exhausted from the chamber through separate outlet ports. The rotary phase separator10includes a housing26that defines a separator chamber28inside of the housing26. In some embodiments, the separator chamber28is cylindrical with the outer diameter20concentric about a longitudinal axis30of the housing26. The housing26includes an inlet opening32, shown in the end view ofFIG.2, tangential to an outer diameter of a pre-swirl chamber34, also shown inFIG.2. The motor12is mounted to the housing26and drives the shaft14about the longitudinal axis30. In some embodiments, the motor12is a canned electric motor. One skilled in the art will readily appreciate that a canned electric motor12is only one possible means of rotating the shaft14. The shaft14may be driven by alternate methods, such as being driven by a hydraulic pump or other adjacent apparatus. While in the embodiment illustrated inFIG.1, the housing26is stationary and the shaft14rotates about the longitudinal axis30, in other embodiments the configuration is reversed and the shaft14is stationary while the housing26rotates about the longitudinal axis30. Bearing assemblies36support the shaft14for rotation about the longitudinal axis30. The bearing assemblies36are magnetic bearings. Magnetic bearings utilize magnetic levitation to support the shaft14without physical contact. The bearing assemblies36include radial bearings38located at a first shaft end40and at a second shaft end42to maintain a desired radial position of the shaft14relative to the longitudinal axis30. The radial bearings38include a radial bearing rotor44disposed at the shaft14and rotatable with the shaft14, and an electromagnetic bearing stator46disposed at the housing26, such that when the bearing stator46is electrically energized, the shaft14is levitated to its operational radial position, such as shown inFIG.1and in a cross-sectional view of a bearing assembly as shown inFIG.3. In some embodiments, the motor12and the radial bearing rotor44are located inside the housing26, while the radial bearing stator46is located outside of the housing26. While two radial bearings38are illustrated inFIG.1, it is to be appreciated that other quantities of radial bearings38, such as three or more radial bearings38, may be utilized. The bearing assemblies36further include an axial bearing48configured to maintain a desired axial position of the shaft14relative to the housing26. In some embodiments, the axial bearing48is located at the second shaft end42such as shown inFIG.1, but one skilled in the art will readily appreciate that the axial bearing48may be located at other positions along the shaft14. The axial bearing48includes axial bearing rotor elements50located at the shaft14and rotatable with the shaft14. Axial bearing stator elements52are located upstream of the axial bearing rotor elements50and downstream of the axial bearing rotor elements50, relative to the longitudinal axis30. When electrically energized, the shaft14is maintained operational axial position along the longitudinal axis30, such as shown inFIG.1. In some embodiments, the axial bearing rotor elements50are located inside the housing26, while the axial bearing stator elements52are located outside of the housing26. Locating the radial bearing stator46and the axial bearing stator elements52outside of the housing26, while the motor12, the radial bearing rotor44and the axial bearing rotor elements50are located inside the housing26allows for the motor12and the bearing assemblies36to be “canned” or sealed, reducing leakage from the separator10or isolation of hazardous fluids internal to the separator10. In some embodiments, such as shown inFIG.1, the bearing assemblies36are actively controlled and connected to a bearing controller54. The bearing controller54may utilize, for example, position sensor data, to selectably alter the electrical signal to the radial bearing stator46and/or the axial bearing stator elements52to modify a radial and/or axial position of the shaft14during operation of the separator10. In operation, the liquid/gas mixture enters the separator chamber28through the inlet opening32in a tangential manner, best shown inFIG.2. The liquid/gas mixture then enters the separator chamber28and flows past the disks16of the plurality of disks16axially along the separator chamber28. The motor12rotates the shaft14and thereby the disks16about the longitudinal axis30mixture. As the liquid/gas mixture flows around the disks16the gas is displaced by the liquid and thereby moves toward the longitudinal axis30to form the gas core24. The liquid moves toward the outer diameter20of the separator chamber28to form the liquid ring22. The rotation of the disks16and cylinders18maintains the incoming rotation of the liquid portion of the mixture along the outer diameter20of the separator chamber28. Rotation of the disks16and cylinders18generates a centrifugal force that drives the liquid toward the outer diameter20of the separator chamber28away from the longitudinal axis30. The gas core24forms because the heavier liquid displaces the lighter gas to form the gas core24within the liquid ring22. Gas flows through openings58in the disks16and may exit the separator chamber28via, for example, a hollow shaft portion60of the shaft14and out of a gas outlet62. Liquid from the liquid ring exits the separator chamber28via a liquid outlet64(shown inFIG.2). The incorporation of magnetic bearing assemblies36as one or more of the bearing assemblies36of the rotary separator10allows for the separator chamber28to be hermetically sealed. Further, the use of magnetic bearing assemblies36results in minimal friction and wear from the load bearing elements of the bearing assemblies36, and improved performance of the bearing assemblies36while experiencing external loads, such as launch loads. Additionally or alternatively, the use of magnetic bearing assemblies36reduce vibration emissions and maintenance required as well as extends the service life of the rotary separator10and removes the need for lubrication of bearing assemblies. Magnetic bearing assemblies36can be used in harsh environmental conditions, including extremely low temperatures, low pressures, micro gravity conditions, and corrosive environments. A wide range of running speeds may be used, including ultra high speed rotation. The term “about” is intended to include the degree of error associated with measurement of the particular quantity based upon the equipment available at the time of filing the application. The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the present disclosure. As used herein, the singular forms “a”, “an” and “the” are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms “comprises” and/or “comprising,” when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, element components, and/or groups thereof. While the present disclosure has been described with reference to an exemplary embodiment or embodiments, it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted for elements thereof without departing from the scope of the present disclosure. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the present disclosure without departing from the essential scope thereof. Therefore, it is intended that the present disclosure not be limited to the particular embodiment disclosed as the best mode contemplated for carrying out this present disclosure, but that the present disclosure will include all embodiments falling within the scope of the claims. | 9,462 |
11859667 | Corresponding reference characters indicate corresponding parts throughout the drawings. In the figures, the systems are illustrated as schematic drawings. The drawings may not be to scale. DETAILED DESCRIPTION Position sensors described herein, including modular inductive position sensors, are configured to determine sensor information for magnetic bearing systems. For example, one or more positions sensors are formed from a plurality of E-shaped members stacked to surround and provide offset sensing elements as part of the magnetic bearing of the system. The magnetic bearing can be any type of bearing that supports a load using magnetic levitation. In particular, the position sensor in some configurations includes a frame and a plurality of ferromagnetic E-shaped cores and corresponding windings. A position measurement circuit includes an AC voltage source and windings of the ferromagnetic E-shaped cores, connected to bridge connections, and having output voltages that are linearly dependent of the rotor position in x-, y-, and z-directions (i.e., zero voltage(s) correspond to the (0,0,0) position). The configuration provides a low-cost modular inductive position sensor, in part, by forming a stator core of the sensor by placing identical ferromagnetic E-shaped cores partly on top of each other comprising a full circle. Wound coil bobbins are mounted around each stator tooth and an assembly tool is used to tune the air-gap between the stator core and rotor, which results in a high degree of tuning accuracy. The stator core and coil bobbins of the sensor mounted within the frame, and coils, are supplied from the AC voltage source. The output of each coil is connected to a differential bridge connection from which rotor positions in the x-, y- and z-directions can be measured. In some configurations, a low-cost modular inductive x,y,z-direction position sensor is used with a high-speed electric motor or other similar apparatus to detect the position of the rotor or some other type of rotating shaft. This position sensor is suitable to be used with magnetic bearing system in some examples because a stable position control of the rotor requires a position measurement feedback. The present disclosure allows for measuring the position of the rotor of a high-speed electric motor with a rotation speed of several kilohertz using non-mechanical contact configurations, particularly using inductive measurements. However, it should be appreciated that the present disclosure can be applied to different non-contactless measuring principles, such as capacitive, eddy current, or optical measuring principles. The inductive position sensor of various examples is made mechanically rugged and robust, able to thermally sustain high temperatures, and non-volatile to electromagnetic interference (EMI) that can affect position measurements. In operation, the inductive sensor is used in, for example, a magnetic bearing system to provide position feedback measurement signals for a rotor position controller. That is, position feedback measurement signals are output by the herein described configuration of sensing elements formed from ferromagnetic E-shaped cores, sensor coils wound around suitable plastic coil bobbins and connected into a bridge connection, and the ferromagnetic rotor which is the measured object. The coils are supplied from a high frequency AC-voltage source (e.g., greater than kHz range) that creates an alternating magnetic flux. This magnetic flux flows from the ferromagnetic E-shaped cores through an air-gap to the ferromagnetic rotor and back to ferromagnetic core via another air-gap. If the ferromagnetic parts (E-shaped cores and rotor) are working below a magnetic saturation flux density level, then the rotor position is directly proportional to the size of air-gap between the rotor and ferromagnetic E-shaped cores. That is, rotor movement in one direction increases air-gap on one side and decreases the air-gap from the opposite side, which changes the magnetic circuit inductance and can be detected from the altered bridge connection output voltage. Specifically, and with reference toFIG.1, an E-shaped core100is formed by laminated electrical steel sheets or using suitable low loss ferrite grades as a core material, which both reduce the amount of eddy currents caused by the alternating magnetic flux inside the ferromagnetic core. It should be noted that other ferromagnetic materials, such solid iron/steel can be used, but high eddy currents are caused by the high frequency of the AC voltage supply of the windings that results from the fast alternating magnetic flux. These eddy currents can cause high losses and skin effects that makes the magnetic flux flow only on the surfaces of the iron parts. Using a ferrite material or laminated steel sheet structure reduces the eddy currents significantly and results in a lower cost of manufacture. The E-shaped core100includes a middle tooth102between two side teeth104extending from a base106that together generally define the E-shape of the E-shaped core100. In the illustrated example, the middle tooth102is wider than each of the side teeth104, which in one configuration is twice as wide, and each having the same thickness. Additionally, the middle tooth102and each of the side teeth104have the same length in one example. However, different widths, thickness, and/or lengths are contemplated, such as based on the particular application or configuration of a rotor of a magnetic bearing. In one example, the side teeth104are angled inward toward the middle tooth102such that a gap108therebetween decreases from a proximal position at the base106to a distal position at the ends of the side teeth104. The amount of angle can be varied as desired or needed. In some examples, the middle tooth102and side teeth104extend generally perpendicularly from the base108, which has a curved or arcuate shape. That is, the curvature of the base108causes the side teeth104to be angled relative to the middle arm102. The base106further includes slots110that are positioned opposite to corresponding gaps108. The slots110are thereby positioned on an opposite side of the base106to the gaps108and are together define openings to allow selective placement of electromagnetic coil bobbins. That is, bobbins having electromagnetic windings are positioned to allow the flow of electrical current. Additionally the middle tooth102and side teeth104are angled at a proximal end to form angled corners112within the gap108. That is, the corners112formed at (i) the proximal end of the middle tooth102and side teeth104and (ii) the base106are angled inward such that a non-perpendicular configuration results. In one example, a plurality of E-shaped cores100are configured as a sensor and that define a stator core200as illustrated inFIG.2. In the illustrated configuration, the stator core200is formed from eight E-shaped cores100in an alternating or offset stacked arrangement. It should be appreciated that fewer or additional E-shaped cores100can be used, such as based on the size of each of the E-shaped cores100and the overall size (e.g., diameter) of the stator core200. More particularly, each of the E-shaped cores100define core portions (e.g., ferromagnetic core portions of the stator core200) and are positioned partially overlapping or on top of an adjacent E-shaped core100to define a circular opening202therethrough to receive a shaft. The E-shaped cores100are arranged to define a continuous circular shape of the stator core200wherein part of each E-shaped core100(illustrated as an end of each of the E-shaped cores100) overlaps with part of the E-shaped core100on each adjacent side of the E-shaped core100. In this arrangement, an axial thickness (in the Z-direction) and position of the teeth102and104of the E-shaped cores100(that define the teeth of the stator core200) vary. In the illustrated example, the thickness of overlapping teeth causes a thickness to double (i.e., abutting teeth of the E-shaped cores100doubles the thickness of the thereby defined tooth of the stator core200). InFIG.2, the E-shaped cores100are arranged in a partial overlapping arrangement such that every second tooth is in an overlapping arrangement and in the middle (i.e., teeth2,4,6,8,10,12,14, and16inFIG.2), and that are used for radial direction sensing as described in more detail herein. That is, the side teeth104of adjacent ones of the E-shaped cores100overlap, and the middle teeth102do not overlap. In one example, one side tooth104of one E-shaped core100entirely overlaps one side tooth104of the adjacent E-shaped core100. In the illustrated example, the E-shaped cores100are positioned to overlap in a same axial direction, such that four of the E-shaped cores100are positioned along a first x-y plane and the other four of the E-shaped cores100are positioned along a second x-y plane parallel to and in abutting arrangement, such that the E-shaped cores100in each of the first and second parallel planes contact each other at ends thereof. Thus, as illustrated inFIG.2, the end portions of the E-shaped cores100ahaving the teeth104are positioned on top of the end portions of the E-shaped cores100bhaving corresponding teeth104as viewed in this figure. Thus, in the example ofFIG.2none of the E-shaped cores100aare positioned below the E-shaped cores100bas viewed in this figure. As such, all of the middle teeth102of each of the E-shaped cores100aand the E-shaped cores100bare positioned within a corresponding x-y plane. That is, every second tooth104is displaced axially from the center, such that every fourth tooth to the left side marked with numbers1,5,9, and13inFIG.2from the center and every fourth tooth to the right side from the center marked as teeth3,7,11, and15inFIG.2, and are used for axial sensing. FIG.2also illustrates one example of selecting a coordinate system in which the +y-direction is between radial teeth2and16and +x-direction is between radial teeth4and6. It should be appreciated that by modifying the width and/or thickness of the teeth102and104, the magnetic flux density flowing inside the stator teeth through the coils is affected, thereby affecting the voltage induced to the coils and the sensitivity of the sensor. The stator core200is configured to surround a measured object, for example a rotor300, as illustrated inFIG.3, which defines a solid shaft. That is, the rotor300is positioned within the middle opening of the stator core200such that the rotor300and the stator core200are co-axially positioned. That is, the axial Z-direction is aligned with the rotor300and the rotor rotation direction can be either clockwise (CW) or counter-clockwise (CCW) around the z-axis as illustrated by the arrows. It should be noted that in some examples, to facilitate controlling the eddy currents and the problems associated with these current, the rotor300includes a laminated steel sheet outer layer302inside which magnetic flux can flow with practically zero eddy currents. It should be noted that due to mechanical limitations, the inner part of the rotor300is formed of solid material (e.g. a suitable steel). Additionally, inFIG.3, only part of the rotor300that is associated with the position measurement is shown (i.e., the rotor300is longer axially than shown to define a shaft) for ease in illustration. As illustrated inFIG.4, wound coil bobbins400are placed around (to surround) each stator tooth, including the middle tooth102and side teeth104of the E-shaped cores100and within a frame410. The bobbins400include wire402wound around a shaft404, thereby defining electrical coils. Any suitable coil winding technology is used to form electromagnetic coils402from wires surrounding the shafts404of the coil bobbins400. It should be noted that that size and shape of the coil bobbins400can be changed, such as based on the particular application, size of the rotor300, etc. For example, if the cross section of the radial and axial teeth is a square shape (e.g., teeth102and104as shown inFIG.1), only one type of coil bobbins400are used. In other configurations, for example, if the width of the radial tooth matches thickness of the axial tooth and vice versa, the same coil bobbins400are used and rotated 90 degrees as illustrated inFIG.4between radial and axial teeth. In this configuration, the coil bobbins400include two connection pins406on two sides of the coil bobbins400(from which only two connection pins406are used and the other two connection pins406removed (e.g., cut off) depending on the orientation of the coil bobbin400when placed around the teeth102and104of the E-shaped cores102). Using only one type of coil bobbins400reduces sensor costs, but as should be appreciated, two different types of coil bobbins (e.g., bobbins having different configurations) for radial and axial stator teeth can be used. In operation, the electromagnetic coils402are supplied from a power source412(e.g., a high frequency AC voltage source) that generates fast alternating magnetic flux flowing inside the ferromagnetic parts (e.g., E-shaped cores100) and across the air-gaps between the rotor300and stator core200. Magnetic flux paths are selected by setting the polarity of the electromagnetic coils402in a particular way. It should be noted that not all of the electromagnetic coils402are used as a supply coils at the same time, in some examples, if the polarity of the electromagnetic coils402are configured accordingly. Additionally, by selecting the number of turns in each winding of the electromagnetic coils402, a suitable flux density level for the magnetic circuit is set. In one configuration, magnetic flux density levels below the saturation flux density limit of the ferromagnetic parts (stator core200and rotor300) are used so that the sensor operation is linearly dependent on the air-gap length between stator core200and rotor300. In some examples, the outputs of each of the windings of the coil bobbins400are connected to form an output bridge connection from which radial direction x and y, as well as axial direction z, measurements are separately made. For example, if the coordinate system x, y, and z is set as shownFIG.2, the connections as shown inFIGS.5and6are used to obtain differential output voltages from each coordinate axis. That is, the connection arrangement500shown inFIG.5is configured to obtain x-direction and y-direction measurements, and the connection arrangement600shown inFIG.6is configured to obtain z-direction measurements. By connecting the electromagnetic coils402as shown inFIGS.5and6, axial coils are solely measurement coils and magnetic flux flowing therethrough is generated with the radial coils. As such, the bridge output voltage is zero if the rotor300is exactly in the middle of the stator cores200(i.e., all the radial and axial air-gaps are equal to each other). Differential connection improves the resolution of the sensor because, for example, rotor movement in +x direction can be measured as positive voltage in the +x coils and negative voltage in the −x coils. Radial direction movement is compensated from the axial direction measurement in some examples by placing four axial coils (either + coils1,5,9, and13or minus coils3,7,11, and15as shown inFIG.2) to have a 90 degrees angle difference. In some examples, the sensor air-gap is selected to be as small as mechanically possible to reduce the size of the power supply and power consumption of the sensor because most of the magnetic energy is stored in the air-gaps when the ferromagnetic parts are working well below the saturation area. The air-gap in various examples is smaller than 1 millimeter (mm), resulting in the accuracy requirements for the sensor-rotor air-gap to be stringent. For example, a 0.1 mm inaccuracy correspond tens of percent inaccuracy in the air-gap, which is directly proportional to the inductance of the electromagnetic coils402. In one example, accurate machining tools are used to produce the ferromagnetic E-shaped cores100as described herein. In another example, a specific assembly tool inside the sensor is used in the assembly process as described herein. After the sensor cores are assembled to form a continuous circle, the sensor cores are mounted inside a frame (e.g., the frame410formed from aluminum as shown inFIG.4) so that sensor cores are not securely attached to the frame410. In this example, the E-shaped cores100are mounted to the frame410using connection screws704(shown inFIG.7), which is also a cost saving method compared with gluing or shrink fitting. Using connection screws also increases the assembly speed compared to other conventional methods. A sensor700is illustrated inFIG.7, wherein a shaft702(e.g., a precision machined shaft) is positioned (e.g., pushed) inside the sensor700and powered so that the sensor700acts as an electromagnet pulling the E-shaped cores100(formed of a ferrite material) towards the shaft702so that air-gaps around the circular configuration are uniform and as small as possible. Thereafter, the mounting screws704of the E-shaped cores100are tightened and the assembly tool power is powered off and removed from the stator core200. Then, the plastic and wound coil bobbins400are attached to each stator core tooth (i.e., the teeth102and104) and the electromagnetic coils402are connected to form the connection arrangement shown inFIGS.5and6. In one example, this connection arrangement is performed by using a printed circuit board800as shown inFIG.8to reduce the amount of space used and to provide a robust design. The printed circuit board800is connected to a control circuit804via electrical wires802. The control circuit804is configured to control the supply of electrical power to the electromagnetic coils402, via the electrical wires802, to drive rotation of the rotor300about the axis thereof. For example, when electrical power is selectively supplied to one of the electromagnetic coils402(configured as stator winding) via one of the electrical wires802, the resulting current in the stator winding generates a magnetic field that couples to the rotor300. The magnetic field associated with the magnetic material in the rotor300(within the E-shaped cores100) attempts to align with the magnetic field generated by the stator core200, resulting in rotational movement of the rotor300. The control circuit804is some examples sequentially activates the stator windings so that the E-shaped cores100(magnet elements) of the rotor300continuously “chase” the advancing magnetic field generated by the stator windings. The present disclosure provides a position sensor that can provide a signal to the control circuit804that is indicative of a current position of the rotor300(relative to the stator core200) using the E-shaped cores100. The control circuit804is configured to utilize this signal when sequentially activating the stator windings to maintain proper timing of a commutation sequence. Thus, various examples provide a sensor design that is modular. That is, designing position sensors for different sizes of rotors involves only the scaling of the size of the individual parts (E-cores, coil bobbins, frame and optionally the printed circuit board for connections). That is, an inductive position sensor is configured to measure the position of the shaft of a magnetic bearing without the use of a cogged ring. The present disclosure uses E-shaped ferrite cores and the corresponding windings to provide the measurements. That is, the E-shaped ferrite cores are arranged around the shaft as disclosed herein to form an inductive type position sensor. FIG.9illustrates a flow chart of a method900for manufacturing a sensor device, such as an inductive type position sensor for determining the position of the shaft within a magnetic bearing. The method900is easily scalable to different sizes of shafts and magnetic bearings. More particularly, and with reference also toFIGS.1-8, the method900includes at902arranging a plurality of E-shaped ferromagnetic cores (e.g., the E-shaped cores100) in a offset stacked arrangement as described herein. For example, the E-shaped ferromagnetic cores are arranged in a circle to define a shaft opening wherein adjacent E-shaped ferromagnetic cores have one or more overlapping teeth. The method includes coupling the E-shaped ferromagnetic cores to a frame at904. For example, the E-shaped ferromagnetic cores are coupled within a frame (e.g., the frame410) to define a stator core through which a shaft can be inserted. In one example, a shaft (rotor) is interested within the arranged E-shaped ferromagnetic cores, which are then energized. The E-shaped ferromagnetic cores are then coupled to the frame in the energized state. The method900further includes at906configuring the E-shaped ferromagnetic cores to provide measurement signals used to control rotation of the shaft. For example, in operation with the manufactured sensor device, a control circuit (e.g., the control circuit804) receives position signals from the E-shaped ferromagnetic cores and uses the signals to control the energization of electromagnetic coils (e.g., the electromagnetic coils402) of the stator (e.g., the stator core200formed in part by the E-shaped ferromagnetic cores) to control rotation of the shaft. Thus, in various examples, identically shaped ferromagnetic E-shaped cores can be manufactured from laminated electrical steel sheets or suitable ferrite material, which are both inexpensive and easy to manufacture. The herein described design is also modular, such that sensors for measuring different sizes of rotor can be provided by scaling the size of E-shaped cores, as well as the coil bobbins and frame part (i.e., making the E-shaped cores larger or smaller). The position measurement circuit in one example includes an AC voltage source and windings of the ferromagnetic E-shaped cores wound around plastic coil bobbins and connected to bridge connections having output voltages that are linearly dependent of the rotor position in x-, y-, and z-directions. Winding connections between coil-bobbins in one example are implemented with printed circuit boards. Exemplary Operating Environment The present disclosure is operable with any electrical machine having a magnetic bearing. The control of the electrical machine is accomplished in some examples using a computing apparatus. In one example, components of the computing apparatus may be implemented as a part of an electronic device according to one or more embodiments described in this specification. The computing apparatus comprises one or more processors which may be microprocessors, controllers or any other suitable type of processors for processing computer executable instructions to control the operation of the electronic device. Platform software comprising an operating system or any other suitable platform software may be provided on the apparatus to enable application software to be executed on the device. According to an embodiment, anomaly detection may be accomplished by software. Computer executable instructions may be provided using any computer-readable media that are accessible by the computing apparatus. Computer-readable media may include, for example, computer storage media such as a memory and communications media. Computer storage media, such as the memory, include volatile and non-volatile, removable and non-removable media implemented in any method or technology for storage of information such as computer readable instructions, data structures, program modules or the like. Computer storage media include, but are not limited to, RAM, ROM, EPROM, EEPROM, flash memory or other memory technology. CD-ROM, digital versatile disks (DVD) or other optical storage, magnetic cassettes, magnetic tape, magnetic disk storage or other magnetic storage devices, or any other non-transmission medium that can be used to store information for access by a computing apparatus. In contrast, communication media may embody computer readable instructions, data structures, program modules, or the like in a modulated data signal, such as a carrier wave, or other transport mechanism. As defined herein, computer storage media do not include communication media. Therefore, a computer storage medium should not be interpreted to be a propagating signal per se. Propagated signals per se are not examples of computer storage media. Although the computer storage medium (the memory) is shown within the computing apparatus, it will be appreciated by a person skilled in the art, that the storage may be distributed or located remotely and accessed via a network or other communication link (e.g. using a communication interface). The computing apparatus may comprise an input/output controller configured to output information to one or more input devices and output devices, for example a display or a speaker, which may be separate from or integral to the electronic device. The input/output controller may also be configured to receive and process an input from the one or more input devices, for example, a keyboard, a microphone or a touchpad. In one embodiment, the output device may also act as the input device. An example of such a device may be a touch sensitive display. The input/output controller may also output data to devices other than the output device, e.g. a locally connected printing device. In some embodiments, a user may provide input to the input device(s) and/or receive output from the output device(s). The functionality described herein, such as the control functionality, can be performed, at least in part, by one or more hardware logic components. According to an example, the computing apparatus is configured by the program code when executed by the processor(s) to execute the embodiments of the operations and functionality described. Alternatively, or in addition, the functionality described herein can be performed, at least in part, by one or more hardware logic components. For example, and without limitation, illustrative types of hardware logic components that can be used include Field-programmable Gate Arrays (FPGAs), Application-specific Integrated Circuits (ASICs), Program-specific Standard Products (ASSPs), System-on-a-chip systems (SOCs), Complex Programmable Logic Devices (CPLDs), Graphics Processing Units (GPUs). At least a portion of the functionality of the various elements in the figures may be performed by other elements in the figures, or an entity (e.g., processor, web service, server, application program, computing device, etc.) not shown in the figures. Although described in connection with an exemplary system, examples of the disclosure are capable of implementation with numerous other systems, including using general purpose or special purpose computing system environments, configurations, or devices. Examples of well-known computing systems, environments, and/or configurations that may be suitable for use with aspects of the disclosure include, but are not limited to, mobile or portable computing devices (e.g., smartphones), personal computers, server computers, hand-held (e.g., tablet) or laptop devices, multiprocessor systems, gaming consoles or controllers, microprocessor-based systems, set top boxes, programmable consumer electronics, mobile telephones, mobile computing and/or communication devices in wearable or accessory form factors (e.g., watches, glasses, headsets, or earphones), network PCs, minicomputers, mainframe computers, distributed computing environments that include any of the above systems or devices, and the like. In general, the disclosure is operable with any device with processing capability such that it can execute instructions such as those described herein. Such systems or devices may accept input from the user in any way, including from input devices such as a keyboard or pointing device, via gesture input, proximity input (such as by hovering), and/or via voice input. Any range or device value given herein may be extended or altered without losing the effect sought, as will be apparent to the skilled person. Although the subject matter has been described in language specific to structural features and/or methodological acts, it is to be understood that the subject matter defined in the appended claims is not necessarily limited to the specific features or acts described above. Rather, the specific features and acts described above are disclosed as example forms of implementing the claims. It will be understood that the benefits and advantages described above may relate to one embodiment or may relate to several embodiments. The embodiments are not limited to those that solve any or all of the stated problems or those that have any or all of the stated benefits and advantages. It will further be understood that reference to ‘an’ item refers to one or more of those items. The examples and embodiments illustrated and described herein as well as examples and embodiments not specifically described herein but within the scope of aspects of the claims constitute exemplary means for position sensing. The term “comprising” is used in this specification to mean including the feature(s) or act(s) followed thereafter, without excluding the presence of one or more additional features or acts. The order of execution or performance of the operations in examples of the disclosure illustrated and described herein is not essential, unless otherwise specified. That is, the operations may be performed in any order, unless otherwise specified, and examples of the disclosure may include additional or fewer operations than those disclosed herein. For example, it is contemplated that executing or performing a particular operation before, contemporaneously with, or after another operation is within the scope of aspects of the disclosure. When introducing elements of aspects of the disclosure or the examples thereof, the articles “a.” “an,” “the,” and “said” are intended to mean that there are one or more of the elements. The terms “comprising,” “including,” and “having” are intended to be inclusive and mean that there may be additional elements other than the listed elements. The term “exemplary” is intended to mean “an example of” The phrase “one or more of the following: A. B, and C” means “at least one of A and/or at least one of B and/or at least one of C.” Additional Examples Some examples are directed to a position sensor. Such examples specifically include: a plurality of E-shaped ferromagnetic cores arranged to define a circular opening therethrough to receive a shaft, each E-shaped ferromagnetic core having a plurality of teeth, wherein adjacent E-shaped ferromagnetic cores of the arranged plurality of E-shaped ferromagnetic cores have an overlapping tooth; and a frame surrounding the arranged plurality of E-shaped ferromagnetic cores, the E-shaped ferromagnetic cores coupled to the frame. In some examples, the plurality of E-shaped ferromagnetic cores are configured as a stator to receive therein the shaft configured as the rotor. In some examples, each E-shaped ferromagnetic core of the plurality of E-shaped ferromagnetic cores comprises a middle tooth and two side teeth, one each on an opposite side of the middle tooth, the middle tooth and two side teeth extending from a base to form an E-shaped profile. In some examples, the middle tooth had a first width and each of the two side teeth have a second width, wherein the first width is twice the second width. In some examples a side tooth of one E-shaped ferromagnetic core entirely overlaps a side tooth of an adjacent E-shaped ferromagnetic core. In some examples, a first set of the plurality of E-shaped ferromagnetic cores are arranged in a first plane and a second set of the plurality of E-shaped ferromagnetic cores are arranged in a second plane, the first and second planes being parallel. In some examples, coil bobbins have electromagnetic coils arranged relative to the plurality of plurality of E-shaped ferromagnetic cores, and a control circuit is coupled to the electromagnetic coils, the control circuit is configured to receive position signals from the electromagnetic coils and control power supplied to the electromagnetic coils. In some examples, a printed circuit board forms a connection arrangement between the coil bobbins and the control circuit. In some examples, outputs of each of the electromagnetic coils of the coil bobbins are connected to form an output bridge connection, and the control circuit is configured to obtain separate radial direction x and y measurements and axial direction z measurements from the output bridge connection. Other examples are directed to a rotating device. Specifically, the rotating device includes: a plurality of E-shaped ferromagnetic cores arranged to define a circular opening therethrough to receive a shaft, each E-shaped ferromagnetic core having a plurality of teeth including a stator tooth, the plurality of E-shaped ferromagnetic cores stacked to define offset sensing elements; a plurality of wound coil bobbins having electromagnetic coils and positioned around each stator tooth, a frame surrounding the arranged plurality of E-shaped ferromagnetic cores, the E-shaped ferromagnetic cores coupled to the frame; a shaft positioned within the circular opening of the plurality of E-shaped ferromagnetic cores; a power source configured to supply power to the electromagnetic coils; and a control circuit coupled to the electromagnetic coils, the control circuit configured to receive position signals from the electromagnetic coils and control the power supplied to the electromagnetic coils to cause rotation of the shaft. In some examples, the plurality of E-shaped ferromagnetic cores are configured as a stator to receive therein the shaft configured as the rotor and having a laminated steel sheet outer layer. In some examples, each E-shaped ferromagnetic core of the plurality of E-shaped ferromagnetic cores comprises a middle tooth and two side teeth with one of each side tooth on an opposite side of the middle tooth, the middle tooth and two side teeth extending from a base to form an E-shaped profile. In some examples, the middle tooth had a first width and each of the two side teeth have a second width, wherein the first width is twice the second width. In some examples, a side tooth of one E-shaped ferromagnetic core entirely overlaps a side tooth of an adjacent E-shaped ferromagnetic core. In some examples, a first set of the plurality of E-shaped ferromagnetic cores are arranged in a first plane and a second set of the plurality of E-shaped ferromagnetic cores are arranged in a second plane, the first and second planes being parallel to define the offset sensing elements. In some examples, a printed circuit board forms a connection arrangement between the plurality of wound coil bobbins and the control circuit. In some examples, outputs of each of the electromagnetic coils of the plurality of wound coil bobbins are connected to form an output bridge connection, and the control circuit is configured to obtain separate radial direction x and y measurements and axial direction z measurements from the output bridge connection. Other examples are directed to a method for manufacturing an inductive type position sensor. Specifically, the method includes arranging a plurality of E-shaped ferromagnetic cores in an offset stacked arrangement and defining a circular opening therethrough to receive a shaft, each E-shaped ferromagnetic core having a plurality of teeth, wherein adjacent E-shaped ferromagnetic cores of the arranged plurality of E-shaped ferromagnetic cores have an overlapping tooth; coupling the plurality of E-shaped ferromagnetic cores to a frame; and configuring the E-shaped ferromagnetic cores to provide measurement signals used to control rotation of the shaft when inserted within the circular opening of the plurality of E-shaped ferromagnetic cores. In some examples, the method includes configuring a control circuit to obtain separate radial direction x and y measurements and axial direction z measurements from an output bridge connection connected to wound coil bobbins positioned around the plurality of teeth. In some examples, the method includes coupling the plurality of E-shaped ferromagnetic cores to the frame in an energized state of the plurality of E-shaped ferromagnetic cores. Having described aspects of the disclosure in detail, it will be apparent that modifications and variations are possible without departing from the scope of aspects of the disclosure as defined in the appended claims. As various changes could be made in the above constructions, products, and methods without departing from the scope of aspects of the disclosure, it is intended that all matter contained in the above description and shown in the accompanying drawings shall be interpreted as illustrative and not in a limiting sense. | 37,101 |
11859668 | DETAILED DESCRIPTION In the following, identical or functionally equivalent elements are designated by the same reference numbers. FIG.1shows a schematic circuit diagram of a lubricant injector1that is impinged with lubricant from a lubricant pump assembly, wherein the lubricant is provided, pressurized, via a lubricant line4on a lubricant inlet6of the lubricant injector1. The lubricant pump assembly2here is configured such that lubricant is pressurized in the lubricant line4during a pumping cycle, and at the end of the pumping cycle the lubricant line4is switched pressureless. “Pressureless” here means, for example, a pressure of less than 70 bar, while the pressurization falls in a significantly higher pressure range of, for example, more than 100 bar. Such lubricant pumps are known from the prior art and are therefore not further described. As can further be seen fromFIG.1, the inventive lubricant injector furthermore includes a control unit8and a metering unit10. The control unit8includes a metering piston12that is bringable from a first (I) into a second (II) switching state. Here the control piston12is preloaded in the first switching state I using a preload element14, in particular a spring element. The metering element10includes a piston16that includes a first piston workspace18configured as a first metering chamber, and a second piston workspace20configured as a second metering chamber. If a lubricant pressure abuts on the lubricant inlet6, then in the first switching state I lubricant is conducted via the control piston12into the second metering chamber20by a first lubricant channel22. Due to the increasing volume of the lubricant in the metering chamber20the piston16is displaced toward the first metering chamber18so that lubricant is conducted from the first metering chamber18via a second lubricant channel24to a lubricant outlet26and from there out to a lubricant consumer28. If the piston16has reached its maximum stroke towards the first metering chamber18, i.e., a further advancing toward the metering chamber18is not possible, the pressure of the lubricant increases in the second metering chamber20, in the first lubricant channel22, and also at the lubricant inlet6. Furthermore, a lubricant switchover pressure channel30is disposed on the lubricant inlet6, which lubricant switchover pressure channel30conducts lubricant toward a control-piston workspace upon exceeding of a certain lubricant pressure at the lubricant inlet6or the control piston12. The control piston12is thereby transferred into the second switching state II against the preload force of the preload element14. In the second switching state II lubricant is now supplied via the second lubricant channel of the first metering chamber18, which in turn effects an advancing movement of the piston16toward the second metering chamber20. The lubricant present in the second metering chamber20is thereby pumped via the first lubricant channel22toward the lubricant outlet26. If at the end of the lubricant pumping cycle the lubricant line4pumps no further or little lubricant toward the lubricant inlet6, the pressure drops in the lubricant line4and thus at the lubricant inlet6. If the lubricant pressure has fallen below a certain threshold value that is preferably determined via the preload force of the preload element14, the control piston12can be returned via the preload element14into its first switching state I. FIG.2schematically shows a first preferred exemplary embodiment of the inventive lubricant injector1at the end of the first switching state I. As can be seen fromFIG.2, the lubricant injector1includes a housing34wherein the control piston12and the metering piston16are disposed. Here the control piston12and the metering piston16can also each be disposed in their own housings that are connectable to each other. Rearward of the control piston12the lubricant inlet is schematically indicated. In order to be able to provide the first and the second switching state a first control space36, in particular a ring space, and a second control space38that is also preferably configured as a ring space are disposed on the control piston12. As can further be seen fromFIG.2, in the depicted first switching state I the lubricant inlet6is connected via the ring space36to the first lubricant channel22and the second metering chamber20of the piston16. On the other hand the lubricant channel24is connected via the ring space38to a lubricant outlet channel40, via which lubricant is conducted toward the lubricant outlet26disposed on the spring element14. Since a further advancing of the piston16toward the first metering chamber18is no longer possible in the state depicted inFIG.2, the pressure of the lubricant increases in the second metering chamber20, the first lubricant channel22, and at the lubricant inlet6. If the pressure at the lubricant inlet6or at the control piston12exceeds a certain value, then lubricant can be conducted via the switchover pressure channel30not shown here toward the control-piston workspace32so that the control piston12can be moved into its second switching state II against the preload of the preload element14. FIGS.3A to3Fschematically show the movement of control piston and metering piston during exemplarily shown switching states. HereFIG.3Ashows an initial state wherein the lubricant inlet6is connected via the first ring space36to the first lubricant channel22and guides lubricant toward the second metering chamber20of the metering piston16. The piston16is thereby moved toward the first metering chamber18wherein lubricant from the previous cycle is located, whereby the lubricant present in the chamber18is pumped via the lubricant channel24, the second control space38and the lubricant outlet channel40toward lubricant outlet26.FIG.3Bshows an inventive lubricant injector in an intermediate state, while lubricant is pumped from the first metering chamber18toward lubricant outlet26.FIG.3Cshows a state wherein the metering piston16has displaced the lubricant from the first metering chamber18and guided lubricant into the ring space32of the control piston12. Via the pressure built up in the control-piston space the control piston12is displaced toward the lubricant outlet26against the preload of the preload element until the control piston12reaches its second switching state II. In the second switching state, asFIG.3Dshows, the second ring space38is connected to the lubricant inlet6so that lubricant is conducted via the second ring space38and the second lubricant channel24into the first metering chamber18. This in turn effects an advancing of the metering piston toward the second metering chamber20, whereby lubricant is pumped via the first lubricant channel22and the first ring space38toward the lubricant outlet26. For this purpose in particular a lubricant outlet channel42is disposed. In the end state of the second switching state, which is shown inFIG.3e, the metering piston16is in turn maximally displaced toward the first metering chamber20and the first metering chamber is completely filled with lubricant. After reaching this switching state the end of the lubricant pumping cycle is also usually reached so that no further or only little lubricant is pumped from the lubricant pump toward lubricant inlet6. The lubricant pressure thereby drops in the lubricant line4and also in the control-piston space32so that with the aid of the preload element14the control piston12can be pushed back into the initial state12(seeFIG.3F). Furthermore, as can be seen in particular inFIG.2a plurality of adjusting screws44,46,48are provided on the inventive lubricant injector1. Here the stroke of the control piston12can by finely adjusted by the adjusting screw44. Alternatively the adjusting screw44can also be configured as a simple cover element. The adjusting screws46and48advantageously represent so-called metering screws, via which the stroke of the metering piston16and thus the metering volume is adjustable. Accordingly via these adjusting screws46,48a metered quantity of the lubricant can be continuously adjustable externally. Alternatively it is of course also possible to determine the metering via the size of the metering piston16. In order to monitor a function of the lubricant injector1, a sensor, in particular a proximity sensor, can additionally be provided on the end surface of the metering piston16or of the control piston12, which sensor determines whether the lubricant injector1functions as desired. Alternatively or additionally an indicator pin can also be provided on the metering piston16and/or control piston12, which makes possible an optical functional monitoring. As can be seen in particular inFIGS.2and3, in comparison to the prior art the inventive lubricant injector1is assembled from very few elements, so that the entire construction is simplified. Furthermore it is advantageous that lubricant is pumped to the lubricant outlet26both directly from the first metering chamber18and the second metering chamber20during a lubricant pumping cycle, which increases the pumped quantity of lubricant overall. This inventive design that lubricant is pumped directly to a lubricant outlet26both from the first metering chamber18and from the second metering chamber20also makes possible further inventive designs that are described, for example, inFIGS.4to6. In contrast to the exemplary embodiments depicted inFIGS.2and3,FIGS.4to6include not only one lubricant outlet26but a second lubricant outlet50. Here, asFIG.4shows, for example, the first lubricant-outlet channel40may not, as depicted inFIG.2, extend toward the first lubricant outlet26, but can extend to a second lubricant outlet50. As a result lubricant can be provided from the first metering chamber18to the second lubricant outlet50, while the lubricant from the second lubricant chamber20is pumped via the second lubricant-outlet channel42, as discussed inFIG.2, toward the first lubricant outlet26. FIG.4schematically shows yet another preferred design of the lubricant injector1, since the lubricant outlet channel40not only opens directly into the lubricant outlet50, but it is further provided that the lubricant outlet50need not obligatorily be used as lubricant outlet. For this purpose a closure element can be fitted in the lubricant outlet50, which closure element52sealingly closes the lubricant outlet50. However, in order that the lubricant pumped from the first lubricant chamber18can be conducted out of the lubricant-outlet channel40toward a lubricant outlet, a lubricant-outlet connecting channel54is furthermore provided that, with a closed second lubricant outlet50, transports lubricant from the lubricant outlet channel40toward the first lubricant outlet26. On the other hand if the second lubricant outlet50is to be used as a lubricant outlet, a connecting element56can be used in the lubricant outlet50that is preferably configured such that it blocks the access to the lubricant-outlet connecting channel54. In the exemplary embodiment depicted this is achieved via a cone fitting58,60wherein the cone58of the connecting element56can be fitted directly into the conical opening60on the lubricant outlet50and blocks the lubricant-outlet connecting channel54. Instead of a connecting element designed in this manner another device, for example, a vent device, can be used in the lubricant outlet, which device controls the opening or closing of lubricant outlet26;50or lubricant-outlet connecting channel54such that the dispensing location and/or the dispensed amount of lubricant can again be influenced in a targeted manner. In order to correspondingly variably design the second lubricant outlet50, a connecting device62, for example in the form of a thread, can be formed on the lubricant outlet50, which connecting device62ensures an interference-fit receiving, for example, of the closure element52or of the connecting element56. Alternatively, however, such a connection can also be achieved via a plug connection or snap connection. FIG.5shows a further advantageous design of the inventive lubricant injector1, wherein not only the second lubricant outlet50, but also the first lubricant outlet26are variably designed. For this purpose the first lubricant outlet26is no longer, as depicted inFIG.2, made possible via the spring space of the preload element14, but is also, like the second lubricant outlet50itself, disposed in the housing34of the lubricant injector1. For this purpose the second lubricant-outlet channel44is not only configured as a ring space about the control piston but also includes an extension64that opens directly into the first lubricant outlet26. If the lubricant outlet26is closed by the closure element52, lubricant can also be conducted via the lubricant-outlet connecting channel54from the first lubricant outlet26to the second lubricant outlet50. In order to block the lubricant-outlet connecting channel54, a fitting58can in turn, as already described with reference toFIG.4, be disposed on the lubricant-outlet connecting element56, which fitting58interacts with a counter-fitting60and closes the lubricant-outlet connecting channel54. FIG.6schematically shows a further preferred exemplary embodiment, wherein the second lubricant outlet50is disposed parallel to the first lubricant outlet26. Here the first lubricant outlet26is in turn formed via the return element14. Furthermore it is depicted inFIG.6that the connecting element56is fitted with interference fit in the second lubricant outlet50. The connecting element56furthermore includes an inlet opening66that fluidly connects the lubricant-outlet channel40to the lubricant outlet50. Simultaneously a lubricant-outlet connecting channel54is closed by the interference-fit receiving of the connecting element56in the lubricant outlet50so that lubricant can escape from the first metering chamber18only via the second lubricant outlet50. On the other hand, as known, lubricant is supplied from the second metering chamber20to the first lubricant outlet26. The inventive lubricant injectors are advantageous in particular if a plurality of consumers are to be impinged with lubricant. Then with a single lubricant injector not only one consumer but at least two consumers can be supplied with lubricant. This saves costs and reduces the installation space required. Furthermore it is depicted inFIG.7that the lubricant injectors can not only be provided as individual elements but also disposable as a block one-behind-the-other. Here the lubricant injectors can be connected in series in a common housing, as individual elements, or even as a plurality of blocks. FIG.7here shows a schematic plan view from the control-piston side of a lubricant injector block100, which is constructed of a plurality, six are depicted, of lubricant injectors1-1,1-2,1-3,1-4,1-5, and1-6, which are disposed in the common housing34. Of course, however, the lubricant injectors or the control pistons or metering pistons can also be disposed in separate housings, that are connected in a manner corresponding to a block. The lubricant injectors1-1,1-2,1-3,1-4,1-5, and1-6themselves can be configured as depicted inFIG.6and each include a control piston12-1,12-2,12-3,12-4,12-5, and12-6, as well as a metering piston (not depicted) disposed thereunder in the view ofFIG.7. FurthermoreFIG.7shows that a central lubricant inlet68is disposed on the housing34, via which each of the lubricant injectors1-1to1-6is impingeable with lubricant. For this purpose in particular a central channel72is provided in the housing34, which central channel72connects the lubricant inlets of the control pistons12-1to12-6to each other and connects them in series. Furthermore a central lubricant outlet70can be provided on the housing, via which lubricant would be guidable from the central channel72into a further lubricant injector block100. If no further lubricant injector block100is to be provided with lubricant, then the central lubricant outlet70is closed so that the lubricant supplied to all lubricant injectors1connected in series, or lubricant injector blocks100, can only escape via the respective lubricant outlets26,50of the individual lubricant injectors1. Such an arrangement is particularly advantageous since with one element not only one consumer but a plurality of consumers can be supplied with lubricant. Installation space can in turn thereby be saved. In particular with the inventive lubricant injector a lubricant injector can be provided that is easy to manufacture due to the small number of parts. Simultaneously the preload springs need not, as in the prior art, be matched to each other, since only one preload spring is required per lubricant injector. With the aid of the closure screws influence can also be exerted on the metered amount. REFERENCE NUMBER LIST 1Lubricant injector100Lubricant injector block2Lubricant pump assembly4Lubricant line6Lubricant inlet8Control unit10Metering unit12Control piston14Preload element16Metering piston18First metering chamber20Second metering chamber22First lubricant channel24Second lubricant channel26Lubricant outlet28Lubricant consumer30Lubricant switchover pressure channel32Control-piston workspace34Housing36First control space38Second control space40First lubricant outlet channel42Second lubricant outlet channel44,46,48Adjusting screws50Second lubricant outlet52Closure element54Lubricant-outlet connecting channel56Connecting element58Conical fitting60Conical counter-fitting62Thread64Extension of the second lubricant outlet channel66Opening in the connecting element68Central lubricant inlet in the lubricant injector block70Central lubricant outlet from the lubricant injector block72Lubricant central channelI First switching stateII Second switching state | 17,839 |
11859669 | DETAILED DESCRIPTION Before turning to the figures, which illustrate certain exemplary embodiments in detail, it should be understood that the present disclosure is not limited to the details or methodology set forth in the description or illustrated in the figures. It should also be understood that the terminology used herein is for the purpose of description only and should not be regarded as limiting. Large open areas (e.g., airplane hangars, refineries, tank farms, docks, railroad yards, paper mills, chemical processing plants, etc.) commonly having combustible fluid near heated material. The combination of large open areas containing large quantities of combustible fluid and the proximity of heated material can cause fires to occur. Fire suppression systems can be installed in the open areas to suppress such fires. Many these areas have the possibility of widespread and dangerous fires occurring. The fires can be too dangerous (e.g., hot, volatile, etc.) for a person to approach with a smaller fire suppression system (e.g., handheld extinguishers, etc.). Fire suppression systems able to supply large quantities of fire suppressant onto the hazard area in a short period are implemented in such applications. The fire suppression systems generally utilize an oscillating monitor that is configured to facilitate oscillating a nozzle to direct a spray of fire suppressant agent over an arc (e.g., 10°, 50°, 120°, etc.). The oscillating monitor aids in spreading the fire suppressant agent over the hazard such that the fire is prevented from spreading. The oscillating monitor facilitates unaided oscillation by redirecting a small amount of flow from an input water or other fluid source to a mechanical power source (e.g., piston, gear, etc.) to generate movement of an oscillating member. In certain applications, the oscillating monitor utilizes ball bearings (e.g., casted brass bearings, etc.) to facilitate oscillation of the oscillating components. Some oscillating monitors may be assembled in pieces and welded together such that the ball bearings are irremovable. In such cases, the oscillating monitor may have a run life of 1-8 hours before the ball bearings wear and become inoperable, and the oscillating monitor must be replaced before the fire suppression system can be operable again. As such, various embodiments disclosed herein are directed to a bearing assembly that facilitates the servicing of oscillating monitors and the associated bearing assemblies. Referring generally to the figures, a bearing assembly for an oscillating monitor is shown. The bearing assembly in one embodiment includes a connection flange, an outer race, an inner race, one or more ball bearings, one or more annular sealing members, and one or more fasteners. The bearing assembly facilitates replacement of the bearings without need to replace one or more other components of the bearing assembly. The bearing assembly also facilitates replacement of the bearings by means of one direction/side of access to the oscillating monitor. Fire Suppression System Referring toFIG.1, a discharge system10for a fire suppression system is shown according to an exemplary embodiment. In one embodiment, the fire suppression system is a chemical fire suppression system. The fire suppression system is configured to dispense or distribute a fire suppressant agent onto and/or nearby a fire, extinguishing the fire and preventing the fire from spreading. The fire suppression system can be used in a variety of different applications (e.g., aircraft hangers, fueling areas, helipads, refineries, tank farms, docks, railroad yards, mills, etc.). Different applications can require different types of fire suppressant agent and different levels of mobility. The fire suppression system can use a variety of fire suppressant agents, such as powders, liquids, foams, or other fluid or flowable materials. By way of example, the fire suppression system may be in an aircraft hangar (e.g., for fuel fires, hydraulic fluid fires, etc.), at filling stations (e.g., for gasoline or propane fires, etc.), or in other stationary applications. The discharge system10fluidly couples to a source (e.g., a reservoir, a tank, etc.) of fire suppressant agent within the fire suppression system. The discharge system10is configured to facilitate forming and aiming a spray pattern (e.g., a discharge, a flow, etc.) of fire suppressant agent to a desired location. The discharge system10includes a nozzle12(e.g., spray device), which is configured to release and direct the fire suppressant agent towards a desired location, and an oscillating monitor40, configured to oscillate the nozzle12along a specified range of rotation (e.g., 45° clockwise from a neutral position to 45° counter-clockwise from the neutral position and back). The nozzle12includes a body14configured to contain one or more components of the nozzle12and facilitate interaction between the components. The body14includes a nozzle outlet18(e.g., an aperture) located at a first end region16, configured to release fire suppressant agent towards a location (e.g., a fire). The nozzle12includes a nozzle inlet located on a second end region20of the nozzle12. The second end region20and the first end region16of the nozzle12are located opposite each other on the body14. The nozzle inlet is configured to fluidly communicate with the oscillating monitor40to allow fluid flow from the oscillating monitor40to the nozzle12. The nozzle inlet is defined by a nozzle flange24(e.g., a flange member, etc.), located at the second end region20and configured to couple to the oscillating monitor40. The nozzle flange24includes one or more nozzle apertures (e.g., threaded holes, apertures, etc.), located on and extending through the nozzle flange24. The nozzle apertures are configured to receive fasteners (e.g., a bolt, a screw, a rivet, etc.). The fasteners are configured to fixedly couple the nozzle12to the oscillating monitor40such that when the oscillating monitor40rotates, the nozzle12also rotates. The nozzle12further includes a movement arm30that extends from the body14. The movement arm30is configured to facilitate movement of the nozzle12by a user. An elevation lock32(e.g., a locking mechanism) may be included in the nozzle12and configured to prevent the nozzle12from changing elevation during operation. Referring toFIGS.1and2, the discharge system10, as described above, includes the oscillating monitor40. The oscillating monitor40is configured to facilitate oscillation of the nozzle12during operation of the fire suppression system. The oscillating monitor40includes a shell42(e.g., a casing, housing, etc.), configured to contain the components of the oscillating monitor40to facilitate correct operation. The shell42can include one or more walls44(e.g., planar side portions), configured to prevent unwanted material (e.g., dirt, debris, etc.) from entering the oscillating monitor40. Each of the walls44can extend perpendicular and/or parallel to at least one of the other walls44. The walls44define an inner cavity which is configured to contain one or more components of the oscillating monitor40as well as provide space for the components to function correctly. The shell42may include an open side, such that the inner cavity is accessible via the open side. The oscillating monitor40includes a main flow pipe50(e.g., an elongated cylinder, conduit, etc.) extending between a top end region46and a bottom end region48, shown as. The main flow pipe50may be configured to fluidly communicate with a conduit (e.g., a hose, a pipe, a tube, etc.) and/or the nozzle inlet. The main flow pipe50can protrude from the shell42on the top end and/or the bottom end. The shell42is configured to include a shell access port52(e.g., an aperture, an opening, etc.) located and extending through one of the walls44. The shell access port52may allow the main flow pipe50or another component of the oscillating monitor40to extend out of the shell42and be accessible without removing the shell42. The main flow pipe50includes an aperture extending between a first end and a second end of the main flow pipe50configured to facilitate flow through the main flow pipe50from the first end to the second end. The main flow pipe50includes a radial protrusion, shown as first pipe flange54, located on a distal end of the main flow pipe50and external to the shell42. The first pipe flange54can extend radially outward from a surface of the main flow pipe50to form a secondary surface to which components can be coupled. The first pipe flange54includes one or more pipe fastener apertures55(e.g., tapped holes, openings, etc.) spaced along a periphery of the first pipe flange54. The pipe fastener apertures55are configured to accept a fastener (e.g., a bolt, a screw, a rivet, etc.) to fixedly couple one or more components (e.g., a hose, a pipe, etc.) to the first pipe flange54. The first pipe flange54defines a pipe inlet. The pipe inlet is configured to facilitate flow of a fluid into the aperture extending between the first end and the second end. The main flow pipe50includes a second pipe flange58(e.g., a radial protrusion) located on an opposite end of the first pipe flange54. The second pipe flange58is configured to fixedly couple to a bearing assembly102. The second pipe flange58defines a pipe outlet configured to allow flow to exit the main flow pipe50. The oscillating monitor40also includes a side flow pipe60extending from the main flow pipe50. The side flow pipe60can be positioned between the first end and the second end of the main flow pipe50. The side flow pipe60is configured to receive a portion of the fluid flowing through the main flow pipe50. The side flow pipe60includes an aperture (e.g., inlet, outlet, etc.) extending through a wall of the main flow pipe50to facilitate fluid communication between the side flow pipe60and the main flow pipe50. The side flow pipe60can couple to a valve62configured to control flow through the side flow pipe60. The valve62can be located along a region of the side flow pipe60such that the valve62can restrict/allow flow through the side flow pipe60. The valve62can include a lever64and/or a knob66, each configured to facilitate movement of the valve62to prevent or limit the flow within the side flow pipe60. The side flow pipe60is configured to direct the portion of fluid received from the main flow pipe50to a water wheel68(e.g., a rotational device) or other oscillating device. The portion of fluid received from the main flow pipe50is discharged from the side flow pipe60via an outlet, and the discharged fluid impacts the water wheel68, resulting in rotation of the water wheel68due to a force exerted by the fluid impacting the water wheel68. In some embodiments, the water wheel68can be coupled to a gearbox69via a drive shaft71(e.g., a rod, etc.), such that when the water wheel68rotates, the gearbox69rotates with the same rotational velocity as the water wheel68. The water wheel68may also fixedly couple to a first gear and the first gear couples to a second gear fixedly coupled to the gearbox69. The drive shaft71is fixedly coupled to a rotational arm70(e.g., an elongated member, etc.). The rotational arm70includes a first aperture positioned at a first end of the rotational arm70and extending through the rotational arm70. The first aperture is configured to accept the drive shaft71and facilitate fixedly coupling of the rotational arm70to the drive shaft71. As the drive shaft71rotates, the rotational arm70also rotates at the same rotational velocity. The rotational arm70also includes one or more second apertures, located toward a second end of the rotational arm70and extending through the rotational arm70. The second apertures are configured to accept a fastener73that rotationally couples the rotational arm70to curved arm72(e.g., an elongated member). The curved arm72couples to the rotational arm70and to attachment member74. The curved arm72is configured to translate along a defined path as the rotational arm70rotates. The attachment member74couples to the bearing assembly102to facilitate rotation of the bearing assembly102as the curved arm72translates due to the rotation of the rotational arm70from the rotation of the drive shaft71. Therefore, as fluid flows through the main flow pipe50and the valve62is in an open configuration, a portion of the fluid can be received by the side flow pipe60and directed towards the water wheel68, such that the bearing assembly102may rotate automatically (e.g., with no human interaction, etc.). The oscillating monitor40includes an inner shell76(e.g., an inner housing, etc.), which can include the water wheel68, the gearbox69, and/or a portion of the drive shaft71. The inner shell76can further be configured to prevent access to the water wheel68, the gearbox69, and the portion of the drive shaft71within the inner shell76. The inner shell76can include a leak opening78(e.g., an aperture, etc.), on a lower side of the inner shell76. The leak opening78is configured to facilitate egress of the fluid from the inner shell76after discharge from the side flow pipe60. The leak opening78can include a filter80(e.g., a filtering member) configured to prevent material (e.g., contaminants, fire suppression agent particles, etc.) from egressing from the inner shell76along with the fluid. Referring toFIGS.3-6, a rotational coupling100is shown. The rotational coupling100includes a bearing assembly102and the second pipe flange58(e.g., a fluid supply conduit or bottom or lower flange) of the main flow pipe50. The second pipe flange58is configured to couple to the bearing assembly102. The bearing assembly102includes a first bearing race108(e.g., a bearing member, a first, lower, or bottom race or member, an outer race, etc.), a second bearing race116(e.g., a second bearing, a second, upper, or top race or member, an inner race, etc.), and a connection flange144(e.g., a third member, a top or upper flange, etc.). The bearing assembly102can be coupled to the second pipe flange58as described above. The bearing assembly102is configured to facilitate rotation of the nozzle12, which is fixedly coupled to the bearing assembly102. In some embodiments, connection flange144is omitted from bearing assembly102and provided as a a separate component or as part of rotational coupling100. A first side (e.g., bottom side) of the connection flange144is configured to be coupled to the second bearing race116. In one embodiment, the connection flange144is fixedly coupled to the second bearing race116by a plurality of second fasteners142. The second bearing race116is rotatably coupled to the first bearing race108. A plurality of bearings134(e.g., ball bearings, slanted bearings, etc.) provide an interface between the second bearing race116and the first bearing race108. The first bearing race108is fixedly coupled to the second pipe flange58by a plurality of first fasteners104. The bearing assembly102provides relative rotational movement between the oscillating monitor40(coupled to the first bearing race108) and the nozzle12(coupled to the second bearing race116), and a sealed fluid flow path between these components. As discussed in greater detail below, the components of the bearing assembly102can be removed via access from a second side (e.g., a top side, etc.) of the connection flange144, thereby facilitating maintenance of the bearing assembly102. The second pipe flange58can include one or more first apertures84located on and extending through the second pipe flange58. One or more first fasteners104(e.g., bolts, screws, rivets, etc.) are configured to extend through the first apertures84to fixedly couple the bearing assembly102to the second pipe flange58. The second pipe flange58further may include a first groove86(e.g., a cutout, a notch, a divot, etc.) located on a first side (e.g., a top side, an outer side, etc.). The first groove86is configured to accept a first sealing member106(e.g., a deforming member, an O-ring, a seal, etc.). The first sealing member106is configured to form a water tight seal between the second pipe flange58and the first bearing race108of the bearing assembly102. The first bearing race108may be a generally ring shaped member that may be configured to form an outer race for the bearings134. The first bearing race108also includes one or more second apertures110(e.g., tapped hole, opening, etc.), which may extend at least partially from a first side (e.g., a top side) of the first bearing race108to a second side (e.g., a bottom side) of the first bearing race108. The first side and the second side can be located opposite of each other on the first bearing race108. The second apertures110includes a first inner diameter and a second inner diameter. The first inner diameter and the second inner diameter can be equal or different. By way of example the first inner diameter is larger than the second inner diameter and is configured to accept a head112(e.g., a larger diameter region) of the first fasteners104. The second side of the first bearing race108can couple to the first side of the second pipe flange58. The first side of the first bearing race108can include first protrusion114(e.g., an extension) extending upward. The first protrusion114can facilitate alignment of the second bearing race116onto the first bearing race108during assembly of the bearing assembly102. In some embodiments, the first protrusion114is projection such as an an annular projection that is received within a groove such as an an annular groove in the second bearing race116. The second bearing race116couples to the first side of the connection flange144. The second bearing race116can be configured to form an inner race for the bearings134. The second bearing race116includes a race flange118(e.g., a flange member, a protrusion, etc.) extending radially outward from a body120. The race flange118includes one or more third apertures122, extending at least partially between a first side (e.g., a top side) of the race flange118to a second side (e.g., a bottom side) of the race flange118. The third apertures122are configured to each accept a second fastener142. The first side of the race flange118includes second groove119(e.g., a notch, a divot, a cutout, etc.) configured to accept second sealing member126. The second groove119and the second sealing member126are configured to extend along a periphery of the second bearing race116. The second bearing race116includes a flow aperture128(e.g., a hole, an opening, etc.) extending between a first side (e.g., a top side) and a second side (e.g., a bottom side) of the body120. The first side of the body120and the first side of the race flange118may be coincident. The flow aperture128can align with the aperture extending between the top end region46and the bottom end region48of the main flow pipe50. The second bearing race116also may include a third groove121extending around the periphery of the race flange118and located on the second side of the race flange118. The third groove121is configured to accept the first protrusion114of the first bearing race108. The second bearing race116also includes one or more access apertures130configured to facilitate access to and removal of the first fasteners104when the bearing assembly102is coupled to the flange208. The access apertures130are defined within and extending through the second bearing race116. In some embodiments, the second bearing race116includes less than eight access apertures130to facilitate access to a first group of first fasteners104(e.g., to provide access to a first portion of first fasteners104at a first rotational position of second bearing race116). In this embodiment, the second bearing race116can be rotated to facilitate access to a next group of first apertures104(e.g., to provide access to a second portion of first fasteners104at a second rotational position of second bearing race116). The second bearing race116can be rotated a number of times equal to the number of first fasteners104to facilitate removal of the first fasteners104. Removal of the first fasteners104facilitates removal of the bearing assembly102from the pipe flange58. When the first bearing race108and the second bearing race116are coupled, bearing cavity132may be formed between the first bearing race108and the second bearing race116. The bearing cavity132is configured to accept the bearings134. The bearings134are configured to facilitate rotation of the second bearing race116with respect to the first bearing race108. The bearings134may be configured to move (e.g., roll) within the bearing cavity132during oscillation of the oscillating monitor40to prevent the first bearing race108and second bearing race116from contacting and causing damage to each other. One example of a material suitable for the bearings134is stainless steel. In some embodiments, the bearings134can be removed (e.g., change, serviced, etc.) by a technician via removal of the second bearing race116from the first bearing race108. Generally, the bearings134fail in an oscillating monitor40and need to be replaced before other components. Removal of the bearings134can lower the cost of maintenance of the oscillating monitor40, as replacement of the bearings134is less expensive than replacing the entirety of the bearing assembly102. Also when the first bearing race108and the second bearing race116are coupled, sealing member cavity136may be formed between the first bearing race108and the second bearing race116. The sealing member cavity136is configured to accept third sealing member138(e.g., a deforming member, an O-ring, etc.). The third sealing member138interfaces with one or more of the first side of the second pipe flange58, the first bearing race108, and the second bearing race116. The third sealing member138is configured to form a water tight seal between an inside of the bearing assembly102and an outside of the bearing assembly102to prevent egress of fluid into a gap140defined between the first bearing race108and the second bearing race116. The third sealing member138may be located radially inward of, outward of, or aligned with, the first sealing member106. The bearing assembly102also includes the connection flange144. Connection flange144couples to the first side of the second bearing race116. The second sealing member126can be located between first side of the connection flange144and the second bearing race116. The connection flange144is configured to facilitate oscillation of the bearing assembly102via coupling to the attachment member74. The connection flange144may include a coupling shoulder146configured to assist placement of the second race member on the connection flange144when assembling the bearing assembly102. The coupling shoulder146couples to second protrusion148of the second bearing race116and may extend along the periphery of the race flange118. The connection flange144is configured to extend radially outward of the second pipe flange58, the first bearing race108, and the second bearing race116. The connection flange144includes one or more fourth apertures150, and one or more coupling apertures154. The fourth apertures150are configured to extend from a second side (e.g., a top side) to the first side of the connection flange144and can align with the third apertures122of the second bearing race116and to accept the second fasteners142. In some embodiments, the fourth apertures150include a first inner diameter and a second inner diameter. The first inner diameter can be equal or different (e.g., larger, smaller, etc.) than the second inner diameter. By way of example, the first inner diameter is larger than the second inner diameter. The first inner diameter can be configured to accept a head152(e.g., a larger diameter region) of the second fasteners142. The coupling apertures154are configured to accept a fastener that fixedly couples the connection flange144to the attachment member74to facilitate rotation of the bearing assembly102relative to the main flow pipe50. Referring toFIGS.7and8, the rotational coupling200is shown according to one embodiment. The rotational coupling200includes a second bearing assembly202, and the main flow pipe50of the oscillating monitor40. The second bearing assembly202couples to the main flow pipe50of the oscillating monitor40. The second bearing assembly202includes first bearing race204(e.g., inner race, bearing member, etc.), second bearing race206(e.g., outer race, bearing member, etc.), flange208, and body210. The second bearing assembly202may couple (e.g., fixedly, removably, etc.) to the main flow pipe50. The second bearing assembly202is configured to facilitate rotation of the nozzle12relative to the main flow pipe50. A first side (e.g., bottom side) of the flange208is coupled to the body210. The body210is coupled (e.g., fixedly, removably, etc.) to the second bearing race206. The second bearing race206is rotatably coupled to the first bearing race204. A plurality of bearings212(e.g., ball bearings, slanted bearings, bearings, etc.) provide an interface between the second bearing race206and the first bearing race204. The first bearing race204is fixedly coupled to an outer surface of the main flow pipe50. The second bearing assembly202provides relative rotation between the oscillating monitor40and the nozzle12. As discussed in greater detail below, the components of the second bearing assembly202can be accessed via removal of the connection flange144. The second bearing assembly202couples to the outer surface of the main flow pipe50of the oscillating monitor40. The main flow pipe50includes sealing groove214(e.g., indent, cutout, notch, etc.) that extends around a perimeter of the main flow pipe50and is configured to extend below the outer surface. The sealing groove214is configured to accept sealing member216(e.g., deforming member, O-ring, seal, etc.). The sealing member216may be an annular body that can deform (e.g., the cross sectional shape can change) and may be configured to form a water-tight seal between the flange208and the main flow pipe50. The sealing groove214is located towards the top end region46of the main flow pipe50. The main flow pipe50can include fastener groove218(e.g., indent, cutout, notch, etc.). The fastener groove218may extend around the perimeter of the outer surface of the main flow pipe50and may be located further from or closer to the top end region46than the sealing groove214. The fastener groove218is configured to accept a retention member220(e.g., a snap ring, a fastener flange, a removable flange, a rigid member, etc.). The retention member220interfaces with the flange208to reduce downward movement (e.g., translation, rotation, etc.) of the flange208relative to the top end region46of the main flow pipe50. The second bearing assembly202also includes a rigid ring222(e.g., a rigid member, a plastic ring, a washer, etc.). A first side (e.g., a top side) of the rigid ring222interfaces with a second side (e.g., a bottom side) of the retention member220, the outer surface of the main flow pipe50. A second side (e.g., a bottom side) of the rigid ring222interfaces with a first side (e.g., a top side) of the first bearing race204. The second bearing assembly202includes one or more bearings212(e.g., slanted bearing, ball bearings, friction reducing member, etc.). The bearing212interface with the first bearing race204, and the second bearing race206. The bearing212facilitates rotation of the second bearing race206with respect to the first bearing race204. The bearings212may be accessed (e.g., removed, changed, fixed, etc.) via removal of the body210and the flange208. In some embodiments, the bearings212may be oriented parallel to the main flow pipe50. In other embodiments, the bearings212may be oriented angled relative to the main flow pipe50. The first bearing race204interfaces with the bearing212and the outer surface of the main flow pipe50. The outer surface of the main flow pipe50can include a shoulder226(e.g., a protrusion, a flange, etc.) located further from the top end region46than the sealing groove214and the fastener groove218. A lower side of the first bearing race204interfaces with the shoulder226to minimize downward translation of the first bearing race204relative to the rigid ring222. An upper side of the first bearing race204interfaces with the rigid ring222to minimize upward translation of the first bearing race204relative to the shoulder226. When the upper side of the first bearing race204interfaces with the rigid ring222and the lower side of the first bearing race204is coupled to the shoulder226, the first bearing race204is fixedly coupled within the second bearing assembly202. The second bearing assembly202includes the body210. The body210is configured to interfaces with the outer surface of the main flow pipe50, the flange208, and to the second bearing race206. The body210is configured to fixedly couple to the second bearing race206such that the body210and the second bearing race206rotate as a single component with respect to the first bearing race204and the main flow pipe50during rotation of the oscillating monitor40. The body210can be L-shaped and define a cavity that contains the first bearing race204, the second bearing race206, the retention member220, the rigid ring222, and/or the bearing212. The body210can include first apertures228(e.g., tapped holes, threaded holes, etc.) that extend a distance into the body210. The first apertures228can each be configured to accept at least a portion of an assembly fastener230(e.g., a bolt, a screw, a rivet, etc.). The second bearing assembly202also includes the flange208. The flange208may be coupled to the main flow pipe50, the body210, the attachment member74, and the nozzle12. The flange208may be configured to facilitate rotation of the nozzle12during oscillation of the oscillating monitor40. The flange208includes second apertures232extending between the first side and a second side (e.g., a top side) of the flange208. The second apertures232may have a first diameter and a second diameter. The first diameter and the second diameter can equal or unequal. By way of example, the first inner diameter is larger than the second inner diameter. The first inner diameter is configured to receive a head234(e.g., a large diameter region) of the assembly fasteners230. The second apertures232may be configured to align with the first apertures228, such that the assembly fasteners230can extend through the second apertures232into the first apertures228. The body210and the flange208are fixedly coupled when the assembly fasteners230are accepted by the first apertures228and the second apertures232. The assembly fasteners230, when accepted by both the first apertures228of the body210and the second apertures232of the flange208, are configured to fixedly couple the flange208to the body210forming an assembled configuration. In the assembled configuration, the first side of the flange208interfaces with the first side of the retention member220, and an inner surface of the flange208interfaces with the outer surface of the main flow pipe50and the sealing member216. The second side of the retention member220interfaces with the first side of the rigid ring222and a portion of the retention member220couples to the fastener groove218of the main flow pipe50. An inner surface of the rigid ring222interfaces with the outer surface of the main flow pipe50and the second side of the rigid ring222interfaces with the first surface of the first bearing race204. The inner side of the first bearing race204interfaces with the outer surface of the main flow pipe50. The outer surface of the first bearing race204interfaces with the bearings212. The second surface of the first bearing race204interfaces with the shoulder226of the main flow pipe50, fixedly coupling the flange208, the retention member220, the rigid ring222, and the first bearing race204. The second bearing race206interfaces with the bearings212on an inner side. The second side (e.g., an outer side, etc.) of the second bearing race206fixedly couples to an inner side of the body210. CONFIGURATION OF EXEMPLARY EMBODIMENTS As utilized herein, the terms “approximately,” “about,” “substantially,” and similar terms are intended to have a broad meaning in harmony with the common and accepted usage by those of ordinary skill in the art to which the subject matter of this disclosure pertains. It should be understood by those of skill in the art who review this disclosure that these terms are intended to allow a description of certain features described and claimed without restricting the scope of these features to the precise numerical ranges provided. Accordingly, these terms should be interpreted as indicating that insubstantial or inconsequential modifications or alterations of the subject matter described and claimed are considered to be within the scope of the disclosure as recited in the appended claims. It should be noted that the term “exemplary” and variations thereof, as used herein to describe various embodiments, are intended to indicate that such embodiments are possible examples, representations, and/or illustrations of possible embodiments (and such terms are not intended to connote that such embodiments are necessarily extraordinary or superlative examples). The term “coupled,” as used herein, means the joining of two members directly or indirectly to one another. Such joining may be stationary (e.g., permanent or fixed) or moveable (e.g., removable or releasable). Such joining may be achieved with the two members coupled directly to each other, with the two members coupled to each other using a separate intervening member and any additional intermediate members coupled with one another, or with the two members coupled to each other using an intervening member that is integrally formed as a single unitary body with one of the two members. Such members may be coupled mechanically, electrically, and/or fluidly. The term “or,” as used herein, is used in its inclusive sense (and not in its exclusive sense) so that when used to connect a list of elements, the term “or” means one, some, or all of the elements in the list. Conjunctive language such as the phrase “at least one of X, Y, and Z,” unless specifically stated otherwise, is understood to convey that an element may be either X, Y, Z; X and Y; X and Z; Y and Z; or X, Y, and Z (i.e., any combination of X, Y, and Z). Thus, such conjunctive language is not generally intended to imply that certain embodiments require at least one of X, at least one of Y, and at least one of Z to each be present, unless otherwise indicated. References herein to the positions of elements (e.g., “top,” “bottom,” “above,” “below,” etc.) are merely used to describe the orientation of various elements in the FIGURES. It should be noted that the orientation of various elements may differ according to other exemplary embodiments, and that such variations are intended to be encompassed by the present disclosure. It is important to note that the construction and arrangement of the rotational coupling and bearing assembly as shown in the various exemplary embodiments is illustrative only. Although only a few embodiments have been described in detail in this disclosure, many modifications are possible (e.g., variations in sizes, dimensions, structures, shapes and proportions of the various elements, values of parameters, mounting arrangements, use of materials, colors, orientations, etc.). For example, the position of elements may be reversed or otherwise varied and the nature or number of discrete elements or positions may be altered or varied. Accordingly, all such modifications are intended to be included within the scope of the present disclosure. Other substitutions, modifications, changes, and omissions may be made in the design, operating conditions and arrangement of the exemplary embodiments without departing from the scope of the present disclosure. Additionally, any element disclosed in one embodiment may be incorporated or utilized with any other embodiment disclosed herein. For example, the connection flange144may be incorporated in the second bearing race116. Although only one example of an element from one embodiment that can be incorporated or utilized in another embodiment has been described above, it should be appreciated that other elements of the various embodiments may be incorporated or utilized with any of the other embodiments disclosed herein. | 36,631 |
11859670 | Skilled artisans appreciate that elements in the figures are illustrated for simplicity and clarity and have not necessarily been drawn to scale. For example, the dimensions of some of the elements in the figures may be exaggerated relative to other elements to help to improve understanding of embodiments of the invention. DETAILED DESCRIPTION The following description in combination with the figures is provided to assist in understanding the teachings disclosed herein. The following discussion will focus on specific implementations and embodiments of the teachings. This focus is provided to assist in describing the teachings and should not be interpreted as a limitation on the scope or applicability of the teachings. However, other embodiments can be used based on the teachings as disclosed in this application. Reference to ranges The terms “comprises,” “comprising,” “includes,” “including,” “has,” “having” or any other variation thereof, are intended to cover a non-exclusive inclusion. For example, a method, article, or apparatus that comprises a list of features is not necessarily limited only to those features but may include other features not expressly listed or inherent to such method, article, or apparatus. Further, unless expressly stated to the contrary, “or” refers to an inclusive-or and not to an exclusive-or. For example, a condition A or B is satisfied by any one of the following: A is true (or present) and B is false (or not present), A is false (or not present) and B is true (or present), and both A and B are true (or present). Also, the use of “a” or “an” is employed to describe elements and components described herein. This is done merely for convenience and to give a general sense of the scope of the invention. This description should be read to include one, at least one, or the singular as also including the plural, or vice versa, unless it is clear that it is meant otherwise. For example, when a single embodiment is described herein, more than one embodiment may be used in place of a single embodiment. Similarly, where more than one embodiment is described herein, a single embodiment may be substituted for that more than one embodiment. Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The materials, methods, and examples are illustrative only and not intended to be limiting. To the extent not described herein, many details regarding specific materials and processing acts are conventional and may be found in textbooks and other sources within the tolerance ring arts. Referring now toFIGS.1A and1B, a tolerance ring is illustrated and is generally designated2. As depicted inFIG.1A, the tolerance ring2can include a body4having a generally cylindrical undeformed sidewall104. The sidewall104can include a top106located at a first axial end and a bottom108located at a second axial end, opposite to the first axial end. As depicted inFIG.1B, the sidewall104can include an inner side107located at a first radial side and an outer side109located at a second radial side, opposite to the first radial side. Further, in a number of embodiments, the sidewall104can include a first end or edge110and a second end or edge112. Moreover, a gap114can be established between the first end110and the second end112of the sidewall104. The gap114can extend completely through the sidewall104in order to form a split in the sidewall104of the tolerance ring100. As illustrated inFIG.1B, the tolerance ring2may not contain a split and be a closed loop tube or cylinder. As illustrated inFIG.1A-1B, the tolerance ring100can include a center axis116. In a number of embodiments, the tolerance ring2can have a thickness, T, and T can be ≥0.1 mm, such as ≥0.2 mm, ≥0.3 mm, ≥0.4 mm, ≥0.5 mm, or ≥0.6 mm. In another aspect, T can be ≤1.0 mm, ≤0.9 mm, or ≤0.8 mm. In a number of embodiments, the tolerance ring2may have an overall outer diameter, OD, and OD can be ≥1 mm, such as ≥10 mm, ≥20 mm, ≥30 mm, ≥40 mm, or ≥50 mm. The OD can be ≤100 mm, such as ≤50 mm, or ≤25 mm. In a number of embodiments, the tolerance ring can have an overall length, L from first axial end106to the second axial end108, and L can be ≥1 mm, ≥5 mm, ≥10 mm, ≥25 mm, or ≥50 mm. L can be ≤75 mm, such as ≤50 mm, ≤25 mm, ≤10 mm, or ≤5 mm. The sidewall104of the tolerance ring100can include at least one intermediate region119. The sidewall104of the tolerance ring100can include an upper intermediate region120near, or adjacent to, the top106of the sidewall104. The sidewall104can also include at least one lower intermediate region122near, or adjacent to, the bottom108of the sidewall104opposite the at least one upper intermediate region120. Further, central intermediate regions124can extend axially along the length of the sidewall104between, and extending from, the upper and lower intermediate regions120and122. In a number of embodiments, the intermediate region119(including the upper intermediate region120, lower intermediate region122, and/or the central intermediate region124) may include a contoured or sloped shape. In a number of embodiments, the intermediate region119(including the upper intermediate region120, lower intermediate region122, and/or the central intermediate region124) may include an unformed shape. As illustrated inFIGS.1A and1B, the tolerance ring100can include a plurality of wave structure regions130comprising wave structures formed in the sidewall104. The wave structure regions130can protrude radially outward, or inward, from the sidewall104away from, or toward, the central axis116of the tolerance ring100. In a number of embodiments, the wave structure or wave structure region130may have a polygonal, oval, circular, semi-circular, or substantially circular, or pointed, cross-section and may coincide with the shape. In certain embodiments, the wave structure or wave structure region130may have a triangular cross-section shape with a pointed apex131, as shown inFIGS.2-3. In a number of embodiments, the wave structure or wave structure region130can comprise a regular polygon, that is, the wave structure or wave structure region130can be a polygon that may be both equiangular and equilateral. Each wave structure region130may be connected only to the intermediate region124such that the portion near the intermediate bands120and122of wave structures130may be open. In another embodiment, the wave structure region130may be connected to the undeformed region124and the undeformed bands120and122such that they may be closed. As shown inFIG.1B, each intermediate region124may be located between adjacent wave structure regions130and each wave structure region130may be located between adjacent formed regions124so the wave structure regions130and intermediate regions124alternate around a circumference of the sidewall104. As depicted inFIG.1A, the tolerance ring100can include one row, or band, of wave structures. In other embodiments (not shown), the tolerance ring can include two rows, or bands, of wave structures; three rows, or bands, of wave structures; etc. Further, a total number of wave structures or wave structure regions, NWS, in each row can be ≥3, such as ≥4, ≥5, ≥6, ≥7, ≥8, or ≥9. Further, NWS≤30, ≤25, ≤20, or ≤15. NWScan be within a range between and including any of the NWSvalues above. In a particular embodiment, as shown inFIGS.1A and1B, NWScan be 15. Referring now toFIGS.2-3, in a number of embodiments, a tolerance ring2in accordance with one or more of the embodiments described herein can be disposed between an inner member28(such as a shaft) and an outer member30(such as a housing) along the central axis116to form an assembly1with the tolerance ring in an installed state. The inner component28and outer component30may each be formed from a material including a metal, a polymer, or other similar material known in the art. As shown inFIGS.2-3and9-10, in a number of embodiments, at least one of the opposing first and second edges110,112of the tolerance ring2may engage and/or contact the outer member30. In a number of embodiments, at least one of the first or second edges110,112may be engaged with the outer member30so as to prevent or restrict relative movement between the tolerance ring2and the outer member30. The movement may be prevented or restricted in a rotational, axial, or radial direction with respect to the central axis116. According to a particular embodiment, relative radial movement is prevented. As shown inFIGS.2and9-10, in a number of embodiments, at least one of the opposing first and second edges110,112of the tolerance ring2may form an interlock with at least one of the inner member28or the outer member30. In a number of embodiments, the interlock may be a corner111of at least one of the edges110,112contacting at least one of the inner member28or the outer member30. In a number of embodiments, as shown inFIG.3, at least one of the opposing first and second edges110,112of the tolerance ring2may be keyed to at least one of the inner member28or the outer member30through matching or otherwise corresponding grooves113,113′ found in the inner member28or outer member30. In a number of variations, the grooves113,113′ may have a polygonal, oval, circular, semi-circular, or substantially circular cross-section and may coincide with the shape of at least one of the first or second edges110,112to form an interference fit preventing or restricting the relative movement of the tolerance ring2with at least one of the inner member28or outer member30. Referring still toFIGS.2-3, in a number of embodiments, the tolerance ring2may be deformed as installed between the inner member28and the outer member30such that it forms a plurality of sidewall segments6in the sidewall104when installed in the assembly1. In a number of embodiments, these sidewall segments6may include at least one buckled region35which may be deformed as installed in the assembly1due to an interference fit between the inner member28and the outer member30. In an uninstalled state, the buckled region35may be non-planar as shown inFIGS.1A-1B. During assembly or use, a portion of the buckled region35may be generally planar in an installed state. In a number of embodiments, the buckled region may contact at least one of the inner member28or the outer member30. In a number of embodiments, the buckled region may be adapted to form one point of contact with the outer component30and two points of contact with the inner component28. This buckled region35may be absent in the uninstalled state of the tolerance ring2(i.e. before the tolerance ring2may be disposed between the inner member28and the outer member30), as shown inFIGS.1A-1B. The buckled region35may be at least partially elastically formed, such that upon disassembly from the inner member28and the outer member30the buckled region35at least partially collapses. As shown inFIGS.2-3, the buckled region35may have a buckled region height HBR, where upon disassembly, the buckled region height HBRmay be reduced by no greater than 80%, such as no greater than 70%, such as no greater than 60%, such as no greater than 50%, such as no greater than 40%, such as no greater than 30%, such as no greater than 20%, such as no greater than 10%, or such as no greater than 5%. The height HBRof the buckled region35may be the same slope or contour as the intermediate region119. Upon assembly, at least one of the buckled regions35can operate in an elastic zone of deformation, i.e., at least one of the buckled regions35can be capable of deforming upon application of a force and returning to its original shape after removal of the force. It may be possible, by including buckled regions35of different deformation characteristics, to yet further alter the characteristics of the tolerance ring2, e.g., stiffness, sliding capability, or tolerance absorption. In a number of embodiments, as shown inFIGS.2-3, the buckled regions35may be formed from at least one of the intermediate regions119(120,122,124) during assembly and use of the tolerance ring2between the inner member28and outer member30in an installed state. By non-limiting example. A buckled region35may be formed when installed between the inner member28and outer member30, or during application of force (e.g. rotational force, axial force, or radial force) to at least one of the inner member28or outer member30. In a number of embodiments, as installed within the assembly1, sidewall segments6may form or otherwise include the buckled regions25of the tolerance ring1with each buckled region25forming an apex, plateau, or ridge7that contacts the inner member28or outer member30. In a number of embodiments, as installed within the assembly1, sidewall segments6may form or otherwise include the buckled regions25of the tolerance ring1with each buckled region25forming an apex, plateau, or ridge7that does not contact the inner member28or outer member30. In a number of embodiments, the apex7may be rounded. In a number of embodiments, the apex7may be pointed. In a number of embodiments, the buckled regions25buckled during installation or use of the tolerance ring2within the assembly1may form the sidewall segments6. The sidewall segments6may be between the wave structure regions130, or may include at least a part of one wave structure region130. In a number of embodiments, at least 65% of each sidewall segment6can lie along a plane, such as at least 70% of each sidewall segment, at least 75% of each sidewall segment, at least 80% of each sidewall segment, at least 85% of each sidewall segment, at least 90% of each sidewall segment, or even at least 95% of each sidewall segment6can lie along a plane. In a number of embodiments, each sidewall segment6can define a thickness (TSS) and a height (HSS). In certain embodiments, an aspect ratio, as measured by a ratio of the height of the sidewall segment6to the thickness of the sidewall segment6, can be no less than 1.5:1. In a certain embodiment, the buckled regions35can include at least 3 sidewall segments, such as at least 4 sidewall segments, at least 5 sidewall segments, at least 6 sidewall segments, at least 7 sidewall segments, at least 8 sidewall segments, at least 9 sidewall segments, at least 10 sidewall segments, at least 15 sidewall segments, or even at least 20 sidewall segments. In a further embodiment, the tolerance ring can include no greater than 75 sidewall segments, such as no greater than 50 sidewall segments, or even no greater than 25 sidewall segments. In this regard, when viewed from a top view, such as illustrated inFIGS.2-3, the tolerance ring2can define a polygon, such as, for example, a triangle, a quadrilateral, a pentagon, a hexagon, a heptagon, an octagon, a nonagon, a decagon, etc. After reading this specification, a person of ordinary skill in the art will understand that the number of sidewall segments6including the buckled regions35of the tolerance ring2may depend on a thickness of a radial gap105formed between an inner member and an outer member of an assembly. For example, as explained in greater detail below, assemblies1having a large radial gap105may utilize less sidewall segments6as compared to assemblies1having a small radial gap105, where more sidewall segments6may be required. In a number of embodiments, as shown inFIG.4, the tolerance ring2can include a composite material. In a number of embodiments, the tolerance ring2may include a substrate or metal strip1119and a low friction layer1104. The low friction layer1104can be coupled to at least a portion of the metal strip1119. In a particular embodiment, the low friction layer1104can be coupled to a surface of the metal strip1119so as to form a low friction interface with another surface of another component. In a particular embodiment, the low friction layer1104can be coupled to the radially inner surface of the metal strip1119so as to form a low friction interface with another surface of another component. In a particular embodiment, the low friction layer1104can be coupled to the radially outer surface of the metal strip1119so as to form a low friction interface with another surface of another component (such as the inner member28or outer member30). In an embodiment, the metal strip1119can at least partially include a metal. The metal may include aluminum, zinc, copper, magnesium, tin, platinum, titanium, tungsten, lead, iron, bronze, alloys thereof, or may be another type. More particularly, the substrate can at least partially include a steel, such as a stainless steel or spring steel. For example, the substrate can at least partially include a 301 stainless steel. The 301 stainless steel may be annealed, ¼ hard, ½ hard, ¾ hard, or full hard. The metal strip1119may include a woven mesh or an expanded metal grid. Alternatively, the woven mesh can be a woven polymer mesh. In an alternate embodiment, the metal strip1119may not include a mesh or grid. In another alternate embodiment, the metal strip1119, as a solid component, woven mesh or expanded metal grid, may be embedded between at least one adhesive layer1121included between the low friction layer1104and the metal strip1119. In at least one embodiment, the metal strip1119may be any kind of metal alloy which provides an elastic behavior under application load in an arcuate shape. Optionally, the tolerance ring2may include at least one adhesive layer1121that may couple the low friction layer1103to the metal strip1119. The adhesive layer1121may include any known adhesive material common to the ring arts including, but not limited to, fluoropolymers, epoxy resins, polyimide resins, polyether/polyamide copolymers, ethylene vinyl acetates, ethylene tetrafluoroethylene (ETFE), ETFE copolymer, perfluoroalkoxy (PFA), or any combination thereof. Additionally, the adhesive can include at least one functional group selected from —C═O, —C—O—R, —COH, —COOH, —COOR, —CF2═CF—OR, or any combination thereof, where R is a cyclic or linear organic group containing between 1 and 20 carbon atoms. Additionally, the adhesive can include a copolymer. In an embodiment, the hot melt adhesive can have a melting temperature of not greater than 250° C., such as not greater than 220° C. In another embodiment, the adhesive may break down above 200° C., such as above 220° C. In further embodiments, the melting temperature of the hot melt adhesive can be higher than 250° C. or even higher than 300° C. The adhesive layer1121can have a thickness of about 1 to 50 microns, such as about 7 to 15 microns. Optionally, the metal strip1119may be coated with corrosion protection layers1704and1705to prevent corrosion of the tolerance ring2prior to processing. Additionally, a corrosion protection layer1708can be applied over layer1704. Each of layers1704,1705, and1708can have a thickness of about 1 to 50 microns, such as about 7 to 15 microns. Layers1704and1705can include a phosphate of zinc, iron, manganese, or any combination thereof, or a nano-ceramic layer. Further, layers1704and1705can include functional silanes, nano-scaled silane based primers, hydrolyzed silanes, organosilane adhesion promoters, solvent/water based silane primers, chlorinated polyolefins, passivated surfaces, commercially available zinc (mechanical/galvanic) or zinc-nickel coatings, or any combination thereof. Layer1708can include functional silanes, nano-scaled silane based primers, hydrolyzed silanes, organosilane adhesion promoters, solvent/water based silane primers. Corrosion protection layers1704,1706, and1708can be removed or retained during processing. Optionally, the tolerance ring2may further include a corrosion resistant coating1125. The corrosion resistant coating1125can have a thickness of about 1 to 50 microns, such as about 5 to 20 microns, and such as about 7 to 15 microns. The corrosion resistant coating can include an adhesion promoter layer127and an epoxy layer129. The adhesion promoter layer1127can include a phosphate of zinc, iron, manganese, tin, or any combination thereof, or a nano-ceramic layer. The adhesion promoter layer1127can include functional silanes, nano-scaled silane based layers, hydrolyzed silanes, organosilane adhesion promoters, solvent/water based silane primers, chlorinated polyolefins, passivated surfaces, commercially available zinc (mechanical/galvanic) or Zinc-Nickel coatings, or any combination thereof. The epoxy layer1129can be a thermal cured epoxy, a UV cured epoxy, an IR cured epoxy, an electron beam cured epoxy, a radiation cured epoxy, or an air cured epoxy. Further, the epoxy resin can include polyglycidylether, diglycidylether, bisphenol A, bisphenol F, oxirane, oxacyclopropane, ethylenoxide, 1,2-epoxypropane, 2-methyloxirane, 9,10-epoxy-9,10-dihydroanthracene, or any combination thereof. The epoxy resin layer1129can further include a hardening agent. The hardening agent can include amines, acid anhydrides, phenol novolac hardeners such as phenol novolac poly[N-(4-hydroxyphenyl)maleimide] (PHPMI), resole phenol formaldehydes, fatty amine compounds, polycarbonic anhydrides, polyacrylate, isocyanates, encapsulated polyisocyanates, boron trifluoride amine complexes, chromic-based hardeners, polyamides, or any combination thereof. Generally, acid anhydrides can conform to the formula R—C═O—O—C═O—R′ where R can be CXHYXZAUas described above. Amines can include aliphatic amines such as monoethylamine, diethylenetriamine, triethylenetetraamine, and the like, alicyclic amines, aromatic amines such as cyclic aliphatic amines, cyclo aliphatic amines, amidoamines, polyamides, dicyandiamides, imidazole derivatives, and the like, or any combination thereof. In a number of embodiments, the low friction layer1104can comprise materials including, for example, a polymer, such as a polyketone, a polyaramid, a polyimide, a polytherimide, a polyphenylene sulfide, a polyetherslfone, a polysulfone, a polypheylene sulfone, a polyamideimide, ultra high molecular weight polyethylene, a fluoropolymer, a polyamide, a polybenzimidazole, or any combination thereof. In an example, the low friction layer1104includes a polyketone, a polyaramid, a polyimide, a polyetherimide, a polyamideimide, a polyphenylene sulfide, a polyphenylene sulfone, a fluoropolymer, a polybenzimidazole, a derivation thereof, or a combination thereof. In a particular example, the low friction/wear resistant layer includes a polymer, such as a polyketone, a thermoplastic polyimide, a polyetherimide, a polyphenylene sulfide, a polyether sulfone, a polysulfone, a polyamideimide, a derivative thereof, or a combination thereof. In a further example, the low friction/wear resistant layer includes polyketone, such as polyether ether ketone (PEEK), polyether ketone, polyether ketone ketone, polyether ketone ether ketone, a derivative thereof, or a combination thereof. In an additional example, the low friction/wear resistant layer may be an ultra high molecular weight polyethylene. An example fluoropolymer includes fluorinated ethylene propylene (FEP), polytetrafluoroethylene (PTFE), polyvinylidene fluoride (PVDF), perfluoroalkoxy (PFA), a terpolymer of tetrafluoroethylene, hexafluoropropylene, and vinylidene fluoride (THV), polychlorotrifluoroethylene (PCTFE), ethylene tetrafluoroethylene copolymer (ETFE), ethylene chlorotrifluoroethylene copolymer (ECTFE), polyacetal, polybutylene terephthalate (PBT), polyethylene terephthalate (PET), polyimide (PI), polyetherimide, polyetheretherketone (PEEK), polyethylene (PE), polysulfone, polyamide (PA), polyphenylene oxide, polyphenylene sulfide (PPS), polyurethane, polyester, liquid crystal polymers (LCP), or any combination thereof. The low friction layer1104may include a solid based material including lithium soap, graphite, boron nitride, molybdenum disulfide, tungsten disulfide, polytetrafluoroethylene, carbon nitride, tungsten carbide, or diamond like carbon, a metal (such as aluminum, zinc, copper, magnesium, tin, platinum, titanium, tungsten, lead, iron, bronze, steel, spring steel, stainless steel), a metal alloy (including the metals listed), an anodized metal (including the metals listed) or any combination thereof. Fluoropolymers may be used according to particular embodiments. As used herein, a “low friction material” can be a material having a dry static coefficient of friction as measured against steel of less than 0.5, such as less than 0.4, less than 0.3, or even less than 0.2. A “high friction material” can be a material having a dry static coefficient of friction as measured against steel of greater than 0.6, such as greater than 0.7, greater than 0.8, greater than 0.9, or even greater than 1.0. In a number of embodiments, the low friction layer1104may further include fillers, including glass fibers, carbon fibers, silicon, PEEK, aromatic polyester, carbon particles, bronze, fluoropolymers, thermoplastic fillers, aluminum oxide, polyamidimide (PAI), PPS, polyphenylene sulfone (PPSO2), LCP, aromatic polyesters, molybdenum disulfide, tungsten disulfide, graphite, grapheme, expanded graphite, boron nitrade, talc, calcium fluoride, or any combination thereof. Additionally, the filler can include alumina, silica, titanium dioxide, calcium fluoride, boron nitride, mica, Wollastonite, silicon carbide, silicon nitride, zirconia, carbon black, pigments, or any combination thereof. Fillers can be in the form of beads, fibers, powder, mesh, or any combination thereof. In an embodiment, the low friction layer1104can have a thickness TFLin a range of 0.01 mm and 0.4 mm, such as in a range of 0.15 mm and 0.35 mm, or even in a range of 0.2 mm and 0.3 mm. In an embodiment, the thickness of the low friction1104may be uniform, i.e., a thickness at a first location of the low friction layer1104can be equal to a thickness at a second location therealong. In an embodiment, the tolerance ring2may include a metal strip1119, which may be formed with the low friction layer1104at the outer side109of the sidewall104. In an embodiment, the tolerance ring2may include a metal strip1119, may be formed with the low friction layer1104on the inner side107of the sidewall104. In a number of embodiments, the metal strip1119may extend at least partially along a length of the tolerance ring2. The metal strip1119may be at least partially encapsulated by the low friction or low friction layer1104. That is, the low friction or low friction layer1104may cover at least a portion of the metal strip1119. Axial ends of the metal strip1119may or may not be exposed from the low friction or low friction layer1104. In a particular embodiment, the metal strip1119may be fully encapsulated in the low friction or low friction layer1104such that the metal strip1119may not be visibly perceptible. In another embodiment, the metal strip1119may include an aperture extending at least partially into the low friction or low friction layer1104. The aperture can generally reduce stiffness of the tolerance ring2, thereby allowing a specific engineered stiffness profile. In an embodiment, any of the layers on the tolerance ring2, as described above, can each be disposed in a roll and peeled therefrom to join together under pressure, at elevated temperatures (hot or cold pressed or rolled), by an adhesive, or by any combination thereof. In a number of embodiments, any of the layers of the tolerance ring2, as described above, may be laminated together such that they at least partially overlap one another. In a number of embodiments, any of the layers on the tolerance ring2, as described above, may be applied together using coating technique, such as, for example, physical or vapor deposition, spraying, plating, powder coating, or through other chemical or electrochemical techniques. In a particular embodiment, the low friction layer1104may be applied by a roll-to-roll coating process, including for example, extrusion coating. The low friction layer1104may be heated to a molten or semi-molten state and extruded through a slot die onto a major surface of the metal strip1119. In another embodiment, the low friction layer1104may be cast or molded. In other embodiments, any of the layers on the tolerance ring2, as described above, may be applied by a coating technique, such as, for example, physical or vapor deposition, spraying, plating, powder coating, or through other chemical or electrochemical techniques. In a particular embodiment, the low friction layer1104may be applied by a roll-to-roll coating process, including for example, extrusion coating. The low friction layer1104may be heated to a molten or semi-molten state and extruded through a slot die onto a major surface of the substrate or metal strip1119. In another embodiment, the low friction layer1104may be cast or molded. By way of a non-limiting example, the tolerance ring2can be shaped in a jig. As stated above, in this regard, a strip of resilient material can be bent on the jig at desired locations to form bent portions. The strip of resilient material can comprise the substrate1119including a metal (such as aluminum, zinc, copper, magnesium, tin, platinum, titanium, tungsten, lead, iron, bronze, steel, spring steel, stainless steel), a metal alloy (including the metals listed), an anodized metal (including the metals listed) or any combination thereof. In a non-limiting embodiment, the strip of resilient material can additionally, or alternatively, include a low friction layer1104including a polymer, or a polymer coating disposed on the resilient material or substrate. In a number of embodiments, alternative materials can be used along the circumference of the tolerance ring2. In other words, the buckled regions35, the intermediate regions119, and the wave structure regions130may each comprise different materials or compositions of the materials listed above at various locations circumferentially, radially, or axially about the tolerance ring2. In a particular embodiment, as stated above, the tolerance ring2can further define a circumferential gap114disposed between circumferential ends of the tolerance ring2. The circumferential gap114can extend the entire axial length of the tolerance ring2so as to form a split tolerance ring2. In certain applications, the circumferential gap114can be welded together at one or more locations along the circumferential ends of the tolerance ring2. The weld(s) can be permanent or temporary. A temporary weld may be utilized during transportation of the tolerance rings2in order to prevent entanglement of the tolerance rings. Alternatively, the weld can be permanent so as to form a closed tolerance ring. Alternatively, the tolerance ring may have no gap at all either through welding or through forming without one, such as shown inFIG.1B. In a number of embodiments, in an installed state, sidewall segments6of the buckled regions35can meet at angles, A at the apex7of the buckled region35(illustrated inFIGS.2-3at8). In a particular embodiment, each angle8can be no less than 60°, such as no less than 90°, no less than 120°, or even no less than 150°. In a further embodiment, each angle8can be less than 180°, such as no greater than 170°, no greater than 160°, no greater than 150°, no greater than 140°, no greater than 130°, no greater than 120°, or even no greater than 110°. In a particular embodiment, the angles8can all lie along straight lines that extend in a substantially parallel direction. As used herein, “substantially parallel direction” refers to a deviation of no greater than 5° between the measured directions of two lines, such as no greater than 4°, no greater than 3°, or even no greater than 2°. In a more particular embodiment, the angles8can all lie along lines that extend in parallel. As used herein, “extend in parallel” refers to a deviation of no greater than 0.5° between the measured directions of two lines. In this regard, the sidewall segments6can each have parallel circumferential end lines. In a particular embodiment, when viewed from a top view in an installed state, the tolerance ring2can comprise a regular polygon, that is, the tolerance ring2can be a polygon that may be both equiangular and equilateral. Regular polygons generally have n-fold rotational symmetry, having a number of rotationally symmetric orientations equal to the number of sidewalls thereof. For example, regular triangles have three points of rotational symmetry, regular quadrilaterals have four points of rotational symmetry, regular pentagons have five points of rotational symmetry, and so on. In a particular embodiment, a regular polygon may evenly displace loading conditions around the tolerance ring2so as to avoid uneven radial loading conditions and any undesirable eccentric operational effects. In a particular embodiment, each sidewall segment6of buckled regions35can be adapted to deflect upon a loading condition, e.g., application of a radially outward force supplied by an inner member. In this regard, each sidewall segment6can be adapted to act as a beam. As used herein, the term “beam” refers to the load deflection characteristic exhibited by a beam under normal loading conditions. Whereas traditional tolerance rings may permit the absorption of a tolerance between mating components through elastic or plastic deformation of projecting waves extending from an annular body, the sidewall segments, as described herein, can bend to absorb the tolerance between mating components. In such a manner, the sidewall segments6can bend or deflect like a beam under a loading condition. In the installed state, each sidewall segment6of the buckled regions35can define an undeformed thickness, TSS, as measured by a distance between a radially inner surface of the sidewall segment6and a radially outer surface of the sidewall segment6at an undeformed location, e.g., a location of the sidewall104with a sidewall segment6and devoid of a wave structure region130. In a particular embodiment, the undeformed thickness, TSS, of each sidewall segment6can be less than a thickness, TS, of a portion of the sidewall104with a wave structure region130, as measured by a distance between a plane formed by the radially inner surface of the sidewall segment6and a radially outermost apex of each wave structure region130, e.g., the maximum distance the wave structure region130, extends from the surface of the sidewall104as measured in a direction perpendicular to the inner surface of the sidewall segment. In a particular embodiment, TScan be no less than 1.01 TSS, such as no less than 1.05 TSS, no less than 1.1 TSS, no less than 1.15 TSS, no less than 1.2 TSS, no less than 1.25 TSS, no less than 1.3 TSS, no less than 1.35 TSS, no less than 1.4 TSS, or even no less than 1.45 TSS. In another embodiment, TScan be no greater than 6.0 TSS, such as no greater than 5 TSS, no greater than 4 TSS, no greater than 3 TSS, no greater than 2 TSS, no greater than 1 TSS, no greater than 1.75 TSS, no greater than 1.7 TSS, no greater than 1.65 TSS, no greater than 1.6 TSS, no greater than 1.55 TSS, or even no greater than 1.5 TSS. A person of ordinary skill will understand after reading this specification that in particular embodiments, the ratio of TSto TSScan vary as measured between different wave structure regions130or between different sidewall segments6or buckling regions35. As shown above, in particular embodiments as well asFIGS.1A-3, at least one wave structure or wave structure region130can be used to generate a specific bending characteristic of the sidewall104. In a number of embodiments, the wave structure or wave structure region130may be adapted to alter the stiffness profile of the tolerance ring2. This may in turn adjust the stiffness of each sidewall segment6and may allow for use of the tolerance ring2in various different applications. In a certain embodiment, the wave structure or wave structure region130may contain a material that can extend radially from the sidewall104. In another embodiment, at least one the wave structure or wave structure region130can extend from a sidewall segment6. In yet a further embodiment, a plurality of the wave structures or wave structure regions130can extend from each sidewall segment6. It is not necessary that each sidewall segment6or portion of the sidewall104have the same number of wave structures or wave structure regions130, the same wave structures or wave structure regions130, or even that all the sidewall segments6have a wave structure or wave structure region130. However, in a particular embodiment, each sidewall segment6can have a same number of wave structures or wave structure regions130. In yet a further embodiment, each sidewall segment6can have one or more same shape wave structure or wave structure regions130oriented in a same direction relative to the sidewall segment6. In a particular embodiment, the wave structure or wave structure region130can each include a projection extending from the sidewall segment6or portion of the sidewall104. In a more particular embodiment, the wave structure or wave structure region130can be monolithic with the sidewall segment6or portion of the sidewall104, e.g., pressed, punched, or otherwise deformed from a continuous portion of the sidewall segment6. As used herein, monolithic wave structure or wave structure region130are not readily detachable from the sidewall segment6or portion of the sidewall104and may not have a discrete connection point therewith. In another embodiment, at least one of the wave structures or wave structure regions130can be a separate component attached to one or more of the sidewall segments6or sidewall104by a fastening technique, such as, for example, a fastening element, e.g., a threaded or non-threaded fastener; an adhesive; by mechanical deformation, e.g., crimping or bending; by weld; or by any combination thereof. In a particular embodiment, each wave structure or wave structure region130can extend radially inward toward a central axis116of the tolerance ring2. In another embodiment, each wave structure or wave structure region130can extend radially outward away from the central axis116of the tolerance ring2. In yet another embodiment, at least one wave structure or wave structure region130can extend radially inward towards the central axis116of the tolerance ring2and at least one wave structure or wave structure region130can extend radially outward away from the central axis116of the tolerance ring2. In the installed state, the tolerance ring2can further define an effective radial thickness, RTE, as measured by a shortest distance between an innermost radial location on the inner member28and an outermost radial location on the outer member30thereof. In a non-limiting embodiment, such as illustrated inFIG.1, RTEcan be expressed as a smallest circle on a surface of the inner member28that contacts each sidewall segment6or sidewall104at a single location. A second concentric circle or point of contact with the outer member30can contact each sidewall segment6or sidewall104at opposite axial ends thereof. In third regard, RTEcan be defined as a distance between the smallest circle of contact with inner member28and the second concentric circle or point of contact with the outer member30in a direction normal to the location of measurement. In a number of embodiments, as shown inFIG.2, each sidewall segment6of the buckled regions35can define a surface area, SASS, when measured in the uninstalled state, and as bound by a height and a length of the sidewall segment6. The wave structure or wave structure region130disposed on or contacting the sidewall segment6can define a surface area, SAWS, as measured by the total surface area that all of the wave structure or wave structure region130on the measured sidewall segment6occupy when viewed in a direction normal to an undeformed location of the sidewall segment, e.g., a location devoid of wave structure or wave structure region130. SAWScan include any portion of the wave structure or wave structure region130bound by the sidewall segment6that does not lie along a plane formed by the surface of the sidewall segment6. The surface areas, SAWSand SASS, are to be measured when viewed in a direction normal to the sidewall segment6at an undeformed location. It should be understood that for purpose of calculations SASScan include SAWS. In a particular embodiment, SASScan be greater than SAWS. For example, in a further embodiment, SAWScan be no greater than 0.99 SASS, such as no greater than 0.90 SASS, no greater than 0.85 SASS, no greater than 0.80 SASS, no greater than 0.75 SASS, no greater than 0.70 SASS, no greater than 0.65 SASS, no greater than 0.60 SASS, no greater than 0.55 SASS, no greater than 0.50 SASS, no greater than 0.45 SASS, no greater than 0.40 SASS, no greater than 0.35 SASS, no greater than 0.30 SASS, or even no greater than 0.20 SASS. In yet a further embodiment, SAWScan be no less than 0.01 SASS, such as no less than 0.05 SASS, no less than 0.10 SASS, or even no less than 0.15 SASS. In this regard, in a particular embodiment, the wave structure or wave structure region130can take up no less than 1% and no greater than 99% of the normal surface area of each sidewall segment6or sidewall104overall. In a particular embodiment, at least one wave structure or wave structure region130can extend along a line oriented substantially perpendicular to a height, HWS(illustrated inFIG.6at16), of the sidewall segment6or sidewall104or substantially parallel to a length L of the tolerance ring2. As used herein, “substantially perpendicular” or “substantially parallel” refers to a deviation of no greater than 5° between the measured directions of two lines, such as no greater than 4°, no greater than 3°, or even no greater than 2°. In a more particular embodiment, at least one wave structure or wave structure region130can extend along a line oriented perpendicular to the height, HWS, of the sidewall segment6. As used herein, “oriented perpendicular” or “oriented parallel” refers to a deviation of no greater than 0.5° as measured between the two compared lines. As shown inFIGS.5-6, the height of the wave structure or wave structure region130may be at least 80% of the distance of the effective radial thickness, RTE, such as at least 70%, such as at least 60%, such as at least 50%, such as at least 40%, such as at least 30%, such as at least 20%, such as at least 10%, or such as at least 5%. In a number of embodiments, the height HWSmay be the height of the wave structure or wave structure region130. In a number of embodiments, during use, the height HWSmay be reduced as the wave structures or wave structure regions130contact the outer component. As shown inFIGS.2-3, wave structure or wave structure region130may have a wave structure height HWS, where upon assembly, may be reduced by no greater than 80%, such as no greater than 70%, such as no greater than 60%, such as no greater than 50%, such as no greater than 40%, such as no greater than 30%, such as no greater than 20%, such as no greater than 10%, or such as no greater than 5%. As shown inFIGS.2-3, wave structure or wave structure region130may have a wave structure height HWS, where upon assembly, may be reduced by at least 80%, such as at least 70%, such as at least 60%, such as at least 50%, such as at least 40%, such as at least 30%, such as no greater than 20%, such as at least 10%, or such as at least 5%. As shown inFIGS.2-3, during assembly and use, the wave structure height HWSmay be reduced to fit between the inner member28and the outer member30. Further, the formation of buckling of the buckled regions35may increase the height HBR, which may increase the contour of the intermediate regions119as they form the buckled regions35. The height HBRmay be increased by no greater than 80%, such as no greater than 70%, such as no greater than 60%, such as no greater than 50%, such as no greater than 40%, such as no greater than 30%, such as no greater than 20%, such as no greater than 10%, or such as no greater than 5%. The height HBRmay be increased by at least 80%, such as at least 70%, such as at least 60%, such as at least 50%, such as at least 40%, such as at least 30%, such as no greater than 20%, such as at least 10%, or such as at least 5%. As a result, the wave structure region130height HWSmay decrease while the buckled region height HBRmay increase to form an interface of the tolerance ring2between the inner member28and outer member30of the assembly. Referring toFIGS.5-6, each sidewall segment6can define a length, LSS, (illustrated inFIG.5at20), and each wave structure or wave structure region130can define a length, LWS(illustrated inFIG.5at18). In a particular embodiment, LWScan be less than LSS. For example, LWScan be no greater than 0.99 LSS, such as no greater than 0.95 LSS, no greater than 0.90 LSS, no greater than 0.85 LSS, no greater than 0.75 LSS, or even no greater than 0.50 LSS. Moreover, LWScan be no less than 0.1 LSS, such as no less than 0.25 LSS, or even no less than 0.45 LSS. In a particular embodiment, as shown inFIG.5, at least one wave structure or wave structure region130can be positioned on the tolerance ring2so as to contact a first sidewall segment22and terminate prior to contacting a second sidewall segment24. In this regard, the at least one wave structure or wave structure region130can be disposed on only one sidewall segment6. In another embodiment, at least one wave structure or wave structure region130′ can extend between adjacent sidewall segments22and24. In such a manner, the one wave structure or wave structure region130′ can transect a junction formed between adjacent sidewall segments22and24and can extend along at least a portion of each adjacent sidewall segment22and24. In a further embodiment, multiple wave structures or wave structure regions130can transect the junction between adjacent sidewall segments22and24. In yet another embodiment, such as, for example, illustrated inFIG.6, at least one wave structure or wave structure region130′ can extend along a line oriented substantially parallel to a height16of the sidewall segment6or sidewall104or substantially perpendicular to a length L of the tolerance ring2. In a particular embodiment, the length of the wave structure or wave structure region130′, LWS(illustrated inFIG.6at18) can be less than the height of the sidewall segment, HSS(illustrated inFIG.6at16). For example, LWScan be no greater than 0.99 HSS, such as no greater than 0.95 HSS, no greater than 0.90 HSS, no greater than 0.85 HSS, no greater than 0.75 HSS, or even no greater than 0.50 HSS. Moreover, LWScan be no less than 0.1 HSS, such as no less than 0.25 HSS, or even no less than 0.45 HSS. In a particular embodiment, the wave structure or wave structure region130,130′ can all be oriented in different directions relative to each other. For example, as illustrated inFIG.6, a central wave structure region130can extend in a direction perpendicular to the height16of the sidewall segment6, while one or more outer wave structure regions130′ can extend in a direction parallel to the height16of the sidewall segment6. Moreover, it should be understood that the scope of the disclosure is not intended to be limited by this exemplary embodiment. A person of ordinary skill in the art will understand that the wave structures or wave structure regions130′ can be arranged on each sidewall segment6or sidewall104in various arrangements and configurations, having various dimensions, characteristics, orientations, and properties as described herein. Referring now toFIGS.7A and7B, in a particular embodiment, at least a portion of at least one wave structure or wave structure region130can have an arcuate contour when viewed in cross-section (FIG.7A). In another embodiment, at least a portion of at least one wave structure or wave structure region130′ can have a polygonal contour when viewed in cross-section (FIG.7B). The polygonal contour can include, for example, a triangular contour, a quadrilateral contour (as illustrated as the central wave structure or wave structure region130′ inFIG.4B), a pentagonal contour, a hexagonal contour, a heptagonal contour, or even an octagonal contour. As illustrated inFIG.7B, in a particular embodiment, the wave structure or wave structure regions130,130′ disposed on each sidewall segment6can have a different or unique contour when viewed in cross section. Additionally, each wave structure or wave structure region103,130′ can have an arcuate contoured portion and a polygonal contoured portion. In such a manner, the wave structure or wave structure regions130′ can be varied and altered for specific applications. As stated above the wave structure or wave structure region103,130′ may have a pointed apex131. During and after assembly, at least one of the wave structure or wave structure regions130can operate in an elastic zone of deformation, i.e., the at least one wave structure or wave structure region130can be capable of deforming upon application of a force and returning to its original shape after removal of the force. In a further embodiment, at least one of the wave structure or wave structure regions130can operate in a plastic zone of deformation, i.e., the at least one wave structure or wave structure region130can be incapable of fully returning to its original shape after removal the force. It may be possible, by including wave structures130of different deformation characteristics on a single sidewall segment6or sidewall104, to yet further alter the characteristics of the tolerance ring2, e.g., stiffness, sliding capability, or tolerance absorption. A tolerance ring2in accordance with one or more of the embodiments described herein can have a buckled region35with a sidewall segment6stiffness (an indicator of the sidewall segments resistance to deformation under load) which may be at least 1% greater than a same tolerance ring2devoid of a wave structure or wave structure region130, such as at least 5% greater than a same tolerance ring devoid of a wave structure or wave structure region130, at least 10% greater than a same tolerance ring devoid of a wave structure or wave structure region130, or even at least 20% wave structure or wave structure region130as compared to a same tolerance ring devoid of a wave structure or wave structure region130. In this regard, it may be possible for a tolerance ring2in accordance with embodiments herein to span a large radial gap105between an inner and outer member without substantially altering radial strength or slip characteristics of the tolerance ring2. As used herein, “span” refers to contact between the tolerance ring2and both the inner and outer members. More particularly, “span” can refer to a degree of contact that allows for transmission of force between the inner and outer members. In a further embodiment, the tolerance ring2can further define at least one aperture extending through a portion of the sidewall104. The aperture can be disposed along the sidewall104along an undeformed portion119or buckled region35thereof, along one or more of the wave structure or wave structure regions130, or along a combination thereof. In this regard, the sidewall segment stiffness can be further altered and adjusted for particular applications. For example, a sidewall segment6having a central aperture may have a lower stiffness, making the sidewall segment6more likely bend to absorb tolerances and deflect upon loading conditions. In an embodiment, when a diameter of the inner member28may be less than 30 mm, the tolerance ring2can span a radial gap105having a radial distance of at least 1% of the diameter of the inner member, such as at least 5% of the diameter, at least 10% of the diameter, or even at least 25% of the diameter. As used herein, “radial distance” refers to a shortest distance between coaxial inner and outer members. In another embodiment, when the diameter of the inner member28may be at least 30 mm, the tolerance ring2can span a radial gap105having a radial distance of at least 0.5 mm, such as at least 1 mm, at least 1.5 mm, at least 3 mm, at least 4 mm, at least 5 mm, or even at least 10 mm. In a further embodiment, the tolerance ring2can span a radial gap105having a radial distance of no greater than 250 mm, such as no greater than 200 mm, no greater than 100 mm, or even no greater than 50 mm. In accordance with an embodiment described herein, the tolerance ring2can have the plurality of sidewall segments6formed from the buckling of the buckled regions35. Each sidewall segment6can contact an outer surface210of the inner member28so as to form at least one point of contact with the inner member28. In a more particular embodiment, the point of contact between the tolerance ring2and the inner member28can occur at a middle portion214of each sidewall segment6. In a particular embodiment, the point of contact between the inner member28and the middle portion214of each sidewall segment6can be a point or line contact, e.g., contact formed along a single point or along a single line. Alternatively, the point of contact can be an area contact, e.g., contact formed at an area as measured in a direction parallel to both the length and the height of each sidewall segment6. In a further embodiment, each sidewall segment6of the buckled regions35can contact an inner surface212of the outer member30so as to form at least one point of contact with the outer member30. In a more particular embodiment, the point of contact between the tolerance ring2and the outer member30can occur at opposite apexes7,7′ of the buckled regions35at each sidewall segment6. In this regard, it may be possible for each sidewall segment6to form three contact points between the inner and outer members28and30—two supporting contact points at apexes7,7′, and a loaded contact point at the middle portion214. The radial gap105can define an inner radius, IR, as defined by the outer surface210of the inner member28, and an outer radius, OR, as defined by the inner surface212of the outer member30. The radial gap105can have a radial thickness, TAG, as measured by a difference between OR and IR. A radial gap aspect ratio can be defined by a ratio of IR/OR. In a number of embodiments, several design features may be included in the tolerance ring2to enhance buckled of the buckled regions35during installation and use of the assembly1. In a number of embodiments, the wave structures apexes131may be pointed to promote additional interlocking between the tolerance ring2and at least one of the inner component2or outer component30in the assembly. In a number of embodiments, inner radius IRTRof the tolerance ring2may be manufactured to be just larger than the inner radius IR defined by the outer surface210of the inner member28in an uninstalled state. In this way, the buckling of the buckled regions35may be encouraged during installation as the outer member30may be pressed over the tolerance ring2to provide an interference fit during installation of the assembly1. In a number of embodiments, the buckled regions35and the wave structure regions130may be made of different materials or have different material compositions from the materials listed above such that the buckling of the buckled regions35may be encouraged during installation or use within the assembly1. In a number of embodiments, at least one intermediate region119(or buckled region35) may have a radius that may be different than a radius of at least one non-buckled region (wave structure region130) of the tolerance ring2. In a number of embodiments, the inner radius IRTRof the tolerance ring2may be modified along its circumference to promote buckling of the buckled regions35may be encouraged during installation or use within the assembly1. For example, the inner radius of the buckling regions35IRTRBRmay be smaller in size than the radius of the wave structure regions130IRTRWSalong the circumference of the tolerance ring2. Alternatively, the inner radius of the buckling regions35IRTRBRmay be larger in size than the radius of the wave structure regions130IRTRWSalong the circumference of the tolerance ring2. In a number of embodiments, a portion of the tolerance ring2(such as the wave structure region130) may have a different radius of curvature than a different portion of the tolerance ring2(such as the buckled region35). In a number of embodiments, at least one of the waves structure regions130or the buckled regions35can have a radius of curvature that may be similar to inner radius IR defined by the outer surface210of the inner member28. For example, the radius of curvature of at least one of the waves structure regions130or the buckled regions35can be within 10% of the inner radius IR defined by the outer surface210of the inner member28, such as within 5%, within 4%, or even within 3%. In a more specific embodiment, the wave structure regions130may have a smaller radius of curvature than the overall inner radius IRTRof the tolerance ring2. In a number of embodiments, the arc length of the buckling regions35ALBRmay be smaller in size than the arc length of the wave structure regions130ALWSalong the circumference of the tolerance ring2. Alternatively, the arc length of the buckling regions35ALBRmay be larger in size than the arc length of the wave structure regions130ALWSalong the circumference of the tolerance ring2. Any one of the design features may be used to promote buckling of the buckled regions35on the tolerance ring2during installation or use within the assembly1. A person of ordinary skill in the art will understand after reading the entire specification that the number of sidewall segments6necessary to span a radial gap108can vary based on several variables, such as, for example, the radial gap aspect ratio, the thicknesses, TSSand TWS, of the sidewall segments6, and the desired loading forces, e.g., the slip characteristic, the minimum and maximum allowed radial forces, and the acceptable bending condition of each sidewall segment6. In this regard, a first step in determining the number of sidewall segments6for a particular radial gap aspect ratio can include calculating a theoretical number of sidewall segments using the following equation: n=180cos-1(IROR)(Equation1) where n represents a theoretical number of sidewall segments6formed from buckled regions35necessary for the tolerance ring2to perfectly, or nearly perfectly, fit in the radial gap105, and where IR/OR is the radial gap aspect ratio. Using equation 1, it may be possible to determine an appropriate number of sidewall segments6in an unloaded, or unbent, tolerance ring configuration (such as illustrated inFIG.5). For example, using equation 1, an inner member28having a diameter of 8 mm disposed within an outer member30having a bore204with a diameter of 16 mm can perfectly, or nearly perfectly, fit a tolerance ring having 3 sidewall segments6(or buckled regions35) without deforming any portion of the tolerance ring2. Likewise, an inner member28having a diameter of 10 mm disposed within an outer member30having a bore204with a diameter of 14.142 mm can perfectly, or nearly perfectly, fit a tolerance ring having 4 sidewall segments6(or buckled regions35) without deforming any portion of the tolerance ring2. As used herein, “perfectly fit” refers to a size ratio between two objects as 1:1. More specifically, as used herein “perfectly fit” can refer to a 1:1 ratio of the effective radial thickness of a tolerance ring, RTE, to TAG. In other words, a perfectly fit tolerance ring can be disposed between inner and outer members with the tolerance ring exhibiting no deflection or loading forces, while each sidewall segment can simultaneously form three points of contact with the inner and outer members—two points of contact with the outer member and one point of contact with the inner member. As used herein, “nearly perfectly fit” refers to a deviation from a 1:1 ratio between the effective radial thickness and TAGby less than 5%, such as by less than 4%, less than 3%, less than 2%, or even less than 1%. A person of ordinary skill in the art will understand that equation 1 can be adjusted to account for the thickness of the sidewall segments6. In applications where n is not a whole number, e.g., an inner member28having a diameter of 20 mm disposed within an outer member30having a bore204with a diameter of 26 mm requires use of a tolerance ring having 4.533 sidewall segments6, it may be necessary to adjust the tolerance ring2in one of several ways. Because the number of sidewall segments6required in the last example is between 4.0 and 5.0 it may be acceptable, depending on the application, to utilize a tolerance ring2having either 4 or 5 sidewall segments. By rounding to the nearest whole number of sidewall segments, e.g., to4or five equilateral sidewall segments, an unbalanced radial load may be avoided. In a particular embodiment, it may be advantageous to utilize the lower number of sidewall segments, thereby increasing the circumferential size of the axial gap. After the number of sidewall segments6necessary for an unloaded, e.g., undeformed tolerance ring, has been determined using equation 1, radial stiffness, slip characteristics, loading conditions, and other application specific modifications can be made to the tolerance ring2by adjusting the number, shape, and size of the sidewall segments6, the wave structures130, and any other features of the tolerance ring2. For example, in a non-limiting embodiment, a radial gap105having a radial gap aspect ratio of √{square root over (2)} can perfectly fit, without loading characteristics, a tolerance ring2having four sidewall segments6, e.g., a quadrilateral tolerance ring. Disposing a tolerance ring2having three sidewall segments6within said radial gap may permit a radial loading between the inner member, the tolerance ring, and the outer member, thereby altering the characteristics of the assembly. Similarly, in another, non-limiting embodiment, a radial gap105having a radial gap aspect ratio of approximately 1.2361 can nearly perfectly fit, without loading characteristics, a tolerance ring2having five sidewall segments6, e.g., a pentagonal tolerance ring. Disposing a partial sidewall segment120between each of the adjacent sidewall segments6of the pentagonal tolerance ring, can permit a radial loading between the inner member, the tolerance ring, and the outer member, thereby altering the characteristics of the assembly. In an embodiment, the assembly1can be installed or assembled by an assembly force of at least 1 kgf in a longitudinal direction relative to the shaft4or housing8, such as at least 2 kgf, at least 3 kgf, at least 4 kgf, at least 5 kgf, at least 10 kgf, or even at least 15 kgf. In a further embodiment, the torque assembly1can be installed or assembled by an assembly force of no greater than 200 kg in a longitudinal direction to the housing8, such as no greater than 150 kgf, no greater than 100 kgf, no greater than 75 kgf, or even no greater than 25 kgf. In an embodiment, the assembly1may be tightened to provide a required torque value of about 1 N▪m to about 20 N▪m with a nominal +/−10% variation over the lifetime of the tolerance ring1. Use of the tolerance ring2or assembly1may provide increased benefits in several applications such as, but not limited to, vehicle tail gates, door frames, seat assemblies, or other types of applications. Notably, the use of the tolerance ring may provide an overload protection device that will provide a consistent torque of nominal +/−10% variation over the lifetime of the tolerance ring1. This may provide for an appropriate slip within the assembly at predetermined torque values which does not marginally change over time, for the reasons and through the features stated herein. The tolerance ring2may run within an assembly2in a cycle of not more than 10 cycles. Many different aspects and embodiments are possible. Some of those aspects and embodiments are described below. After reading this specification, skilled artisans will appreciate that those aspects and embodiments are only illustrative and do not limit the scope of the present invention. Embodiments may be in accordance with any one or more of the embodiments as listed below. Embodiment 1. A assembly comprising: an outer member; an inner member; and a tolerance ring disposed between the inner member and the outer member, wherein the tolerance ring comprises a split ring having opposing edges, wherein the edges are engaged with one of the inner member or the outer member so as to prevent or restrict relative movement between the tolerance ring and at least one of the inner member or the outer member. Embodiment 2. A assembly comprising: an outer member; an inner member; and a tolerance ring disposed between the inner member and the outer member, wherein the tolerance ring is deformed as installed between the inner member and the outer member and forms at least one buckled region in the tolerance ring due to an interference fit between the inner member and the outer member, wherein in an uninstalled state, the buckled region is absent. Embodiment 3. The assembly of embodiment 1, wherein the edges form an interlock caused by a corner of at least one of the edges contacting at least one of the inner member or the outer member. Embodiment 4. The assembly of any of embodiments 1 and 3, wherein the edges are engaged to the inner member. Embodiment 5. The assembly of any of embodiments 1 and 3-4, wherein the edges are engaged to the outer member. Embodiment 6. The assembly of embodiment 2, wherein the buckled region is at least partially elastically formed, such that upon disassembly the buckled region at least partially collapses. Embodiment 7. The assembly of any of embodiments 2 and 6, wherein the buckled region has a buckled region height HBR, wherein upon disassembly HBRis reduced by at least 50%. Embodiment 8. The assembly of any of embodiments 2 and 6-7, wherein the buckled region contacts the outer member. Embodiment 9. The assembly any of embodiments 2 and 6-8, wherein in an uninstalled state, the tolerance ring comprises a plurality of wave structure regions spaced circumferentially around the tolerance ring, and a plurality of intermediate regions disposed between the wave structure regions, and wherein at least one intermediate region is deformed upon assembly to form the buckled region in an installed state. Embodiment 10. The assembly of any of the preceding embodiments, wherein at least one of the inner member or the outer member is capable of rotational, axial, or radial movement. Embodiment 11. The assembly of embodiment 10, wherein the low friction layer comprises a polymer. Embodiment 12. The assembly of any of the preceding embodiments, wherein at least one of the outer member is capable of rotational, axial, or radial movement. Embodiment 13. The assembly of any of embodiments 9-12, wherein at least one wave structure region has a rounded apex. Embodiment 14. The assembly of any of embodiments 9-13, wherein the wave structure region comprises at least one wave structure oriented substantially perpendicular to the length of the tolerance ring. Embodiment 15. The assembly of any of embodiments 9-14, wherein the wave structure region comprises at least one wave structure oriented substantially parallel to the length of the tolerance ring. Embodiment 16. The assembly of any of embodiments 9-15, wherein a portion of the intermediate region is contoured in an uninstalled state. Embodiment 17. The assembly of any of embodiments 9-16, wherein at least one buckled region deforms outward while at least one wave structure region deforms inward in an installed state. Embodiment 18. The assembly of any of the preceding embodiments, wherein at least one buckled region is adapted to form one point of contact with the outer component. Embodiment 19. The assembly of any of the preceding embodiments, wherein a portion of the tolerance ring has a different radius of curvature than a different portion of the tolerance ring. Embodiment 20. The assembly of any of embodiments 9-19, wherein at least one intermediate region has a radius of curvature that is different than a radius of curvature of at least one wave structure region of the tolerance ring. Note that not all of the features described above are required, that a portion of a specific feature may not be required, and that one or more features may be provided in addition to those described. Still further, the order in which features are described is not necessarily the order in which the features are installed. Certain features are, for clarity, described herein in the context of separate embodiments, may also be provided in combination in a single embodiment. Conversely, various features that are, for brevity, described in the context of a single embodiment, may also be provided separately or in any subcombinations. Benefits, other advantages, and solutions to problems have been described above with regard to specific embodiments, However, the benefits, advantages, solutions to problems, and any feature(s) that may cause any benefit, advantage, or solution to occur or become more pronounced are not to be construed as a critical, required, or essential feature of any or all the claims. The specification and illustrations of the embodiments described herein are intended to provide a general understanding of the structure of the various embodiments. The specification and illustrations are not intended to serve as an exhaustive and comprehensive description of all of the elements and features of apparatus and systems that use the structures or methods described herein. Separate embodiments may also be provided in combination in a single embodiment, and conversely, various features that are, for brevity, described in the context of a single embodiment, may also be provided separately or in any subcombination. Further, reference to values stated in ranges includes each and every value within that range. Many other embodiments may be apparent to skilled artisans only after reading this specification. Other embodiments may be used and derived from the disclosure, such that a structural substitution, logical substitution, or any change may be made without departing from the scope of the disclosure. Accordingly, the disclosure is to be regarded as illustrative rather than restrictive. | 70,662 |
11859671 | BRIEF DESCRIPTION OF THE INVENTION With reference toFIGS.1and2, an exemplary prior art low moment coupling10will initially be described so that the aspects of the present invention can be highlighted. In operation, coupling10may use high pressure friction connections to connect two shafts12a,12bof respective mating machines14a,14bto transfer rotational movement of one shaft to the other shaft. Opposite ends of coupling10include a hub16a,16bthat are connected with shafts12a,12b, respectively, in a manner that will be described in further detail below. Coupling10further includes one or more connectors18a,18b,18cthat operate to connect hubs16a,16btogether using fasteners20. Further, a flex element22a,22bis positioned between respective connectors18a,18cand hubs16a,16bto allow for misalignment and flexibility between these components. Coupling10is referred to as a low moment coupling because it includes a design that places a suspension point24a,24bof the respective connector18a,18bmass as close to the machinery casing26a,26bas possible, with the objective of reducing the inertial moment that the machinery shaft must support. This is done by positioning an articulation center28a,28bof the respective flex element22a,22btoward an inboard end30a,30bof the respective hub16,16bas much as possible. One way to couple hub16a,16bwith its respective shaft12a,12bis through a hydraulic interference fit, which provides a good combination of strength, low weight, inherent balance and low stress concentration. In order to implement such a fit, as seen inFIG.2, for example, the shape of an inner surface32aof hub16aand an outer surface34aof shaft12aare usually conical. With a conical fit, an axial position of hub16aon shaft12arelative to the free-state contact position of these components determines an interference level. To make up such a fit, an assembler must apply a high axial force to drive hub16aup shaft12ain a direction35. When sliding hub16aon shaft12a, hydraulic fluid is introduced through passages36,37defined in shaft12athat direct the hydraulic fluid to the interface between inner surface32aof hub16aand outer surface34aof shaft12a. The addition of hydraulic pressure in the gap at the interface between hub16aand shaft12aapplies a radial force in a direction38that can “float” the hub16a, which reduces friction, installation force and provides for the “hydraulic fit.” The hydraulic pressure is then released and a back-up retainer nut39is disposed on an end of shaft12. The contact surfaces of inner surface32aof hub16aand outer surface34aof shaft12aare dimensioned to fit together with a high pressure interference, in the neighborhood of 0.002-0.003 inch/(inch of outer diameter of shaft). The outer diameter of hub16amay be around 1.25 to 1.75 times the diameter of shaft12ayielding contact pressures of 12,000 to 20,000 psi. This tight fit rigidly binds hub16aand shaft12atogether under normal loading. However, the current state of hydraulic fit technology has a practical interference limit of around 0.003 inch/(inch of outer diameter of hub). This limit is usually dictated by a tendency for the interface surfaces of hub16aand shaft12ato adhere during assembly and/or disassembly leading to stuck parts and surface damage. Repairing damage in the field is expensive and time consuming, particularly damage to a shaft given the high cost of shafts. To avoid damage, designers limit interference, which in turn sacrifices machine capacity and usefulness. Referring now toFIG.3, there is shown one exemplary embodiment of a hub joint assembly100in accordance with the present invention. In general, hub joint100may form a part of a low moment coupling110that uses high pressure friction to connect to a shaft112of a machine114. As will be seen through the description set forth below, hub joint assembly100operates to increase an interference limit between hub joint assembly100and shaft112, and eliminates shaft damage during assembly by eliminating high pressure sliding upon the outer diameter of the shaft, thereby improving both capacity and service reliability. WhileFIG.3only shows one hub joint assembly100connected to shaft112, it should be understood that one or more additional hub joint assemblies may be included in low moment coupling110to allow shaft112of machine114to be mated with the shaft of another machine. Any description set forth herein with respect to hub joint assembly100may also apply to additional hub joint assemblies included in low moment coupling110. As best seen inFIG.3, a low moment coupling110may include hub joint assembly100and at least one connector118. Connector118may directly connect hub joint assembly100to another hub joint assembly (not shown) to connect shaft112to the shaft of a mating machine. Connector118may also be used in conjunction with one or more additional connectors to connect hub joint assembly100to another hub joint assembly. Hub joint assembly100may be fixedly coupled to connector118using one or more fasteners120, and frictionally connected to shaft112as will be described in detail below. Hub joint assembly100is adapted to engage a distal end140of shaft112having any number of different configurations. For example,FIG.3shows a distal end140that is cylindrically-shaped. In another example, distal end140may include a conical shaped end with features that accommodate a traditional hydraulic fit, such as the passages36,37shown inFIG.2, even though such features may not be utilized, thus illustrating that hub joint assembly100may be retrofitted to an existing shaft end. In another examples, distal end140of shaft112may be straight-stepped with hydraulic features, straight keyed, taper keyed, polygonal, and/or splined. It should be understood that hub joint100may accommodate the above-referenced distal end configurations, as well as other configurations, with little to no configuration changes to the invention. Hub joint assembly100comprises a coupling hub142and a clamp ring144. Coupling hub142includes a collar portion146that receives distal end140of shaft112, and extends in a direction that is generally parallel with a longitudinal axis148of shaft112. Coupling hub142may be formed of high strength steel, but it should be understood that it may be formed of other materials. Collar portion146includes a bore having an inner surface150that is configured to be the same or substantially similar shape to an outer surface152of distal end140of shaft112. For example, if outer surface152of distal end140of shaft112is cylindrical shaped, then inner surface150of collar portion146may also be cylindrical shaped. As such, inner surface150of collar portion146is configured to mate and come into contact with outer surface152of distal end140of shaft112. Coupling hub142further includes an outer surface178that may be conically-shaped, wherein a thickness of collar portion146at a first distal end154would be less than a thickness of collar portion146at a second distal end166to form tapered outer surface178. First distal end154of collar portion146may also include a threaded portion156that is adapted to receive matching threads158on a shaft plug160. Shaft plug160may include a stop surface161that serves to prevent coupling hub142from sliding relative to shaft112in a direction162. Threaded portion156may also be adapted to engage and resist axial installation forces imposed by a pusher device163(FIG.4), which will be described in more detail below. Coupling hub142further includes a flange portion164extends radially outwardly from a second distal end166of collar portion146. For example, flange portion164may extend perpendicularly from collar portion146a distance that will allow an inward face168of flange portion164to be positioned adjacent to an outward face170of a flange172of connector118. Further, coupling hub142may be coupled to connector118using at least one fastener120. It should be understood that a gap174may be defined between at least a portion of the interface between flange portion164and flange172of connector118, which provides flexibility between these two components. Hub joint100further comprises clamp ring144that is configured to receive collar portion146of coupling hub142, whereby clamp ring144surrounds at least a portion of collar portion146of coupling hub142. Clamp ring144may be formed of high strength steel, but it should be understood that it may be formed of other materials as well. Clamp ring144includes a bore having an inner surface176that may be conically-shaped to match a conically-shaped outer surface178of collar portion146of coupling hub142. As will be described further below, the conical surfaces176,178and the relative position of coupling hub142relative to clamp ring144will cause clamp ring144to impose an inwardly directed radial squeeze force180on outer surface178of collar portion146, which in turn drives inner surface150of collar portion146into high pressure contact with distal end140of shaft112. The taper in outer surface178of collar portion146may be provided, for example, by configuring collar portion146so that a width at first distal end154is smaller than a width at second distal end166. It should be understood that the diameter of outer surface178of collar portion146may be enlarged by an amount equivalent to the design interference. In one aspect, a protective anti-adhesion coating may be provided on at least a portion of inner surface176to provide for increased capacity of hub joint assembly100by facilitating higher contact pressures between clamp ring144and coupling hub142. Higher contact pressure translates to higher torque capacity. For example, the protective anti-adhesion coating may be a chemical conversion coating formed of a material, such as, but not limited to, manganese phosphate. Clamp ring144further includes at least one hydraulic passage182defined therein that extends from an outer surface184, through the width of clamp ring144, to inner surface176. Hydraulic passage182is configured to allow a hydraulic fluid to be introduced at the interface between inner surface176of clamp ring144and outer surface178of collar portion146to facilitate the movement between these components when hub joint assembly100is being installed. In addition, one or more oil distribution grooves183a,183bmay be formed in at least one of inner surface176of clamp ring144and outer surface178of collar portion146to facilitate distribution of the hydraulic fluid across the interface between inner surface176of clamp ring144and outer surface178of collar portion146. Further, one or more seal grooves (not shown) may be formed in at least one of inner surface176of clamp ring144and outer surface178of collar portion146, and used in conjunction with a gasket to help prevent the hydraulic fluid from escaping the tapered interface. Outer surface184of clamp ring144may be cylindrical shaped, and configured to fit within the confines of connector118. Having described the components of hub joint assembly100, the assembly and operation of this device will now be described with reference toFIGS.3and4. The assembler may first clean debris and coatings off of outer surface152of shaft112and inner surface150of coupling hub142. Coupling hub142is then slid onto shaft112to set a final axial position of coupling hub142relative to shaft112. If the outer surface152of shaft112and inner surface150of coupling hub142include matching conical surfaces, then coupling hub142is slid onto shaft112until the surfaces150,152meet. This would take up all radial clearance of the parts and establish the final axial position of coupling hub142relative to shaft112. The surfaces176,178of coupling hub142and clamp ring144may then be cleaned and slid together to a stop to establish a zero interference point, which is identified as a first relative position between collar portion146of coupling hub142and clamp ring144. With reference toFIG.4, pusher device163is then used to place clamp ring144in a second relative position to coupling hub142to frictionally connect hub joint assembly100to shaft112at a desired or predetermined interference pressure. It should be understood that the second relative position may be a predetermined position. Pusher device163includes a cylinder188having a bore190defined therein, and a piston192positioned within bore190. Cylinder188and piston192are configured to be slidably coupled with one another. Further, a pressure chamber194is defined between an inner surface196of cylinder and an outer surface198of piston188. A hydraulic passage200may be defined in piston192and allow a hydraulic fluid to be inputted into pressure chamber194using a hydraulic pressure supply201(FIG.5) to move cylinder188and piston192relative to one another. Pusher device163may further include one or more seals202that operate to retain the hydraulic fluid in pressure chamber194. In order to place clamp ring144in the second relative position to coupling hub142to frictionally connect hub joint assembly100to shaft112at the desired interference pressure, pusher device163is positioned so that an end surface204of cylinder188is positioned against an end surface206of clamp ring, and an end surface208of piston192is positioned against ends surfaces210,212of shaft112and collar portion146, respectively. In addition, first distal end154of collar portion146may be threadably connect to a distal end213of piston192to prevent movement of coupling hub142relative to piston192. Further, a dilation pressure assembly214including a hydraulic passage216may be used in instances where hub joint assembly100is being used in association with a shaft112having an outer diameter of approximately three inches or less where there is not enough material in clamp ring144to accommodate a traditional hydraulic port. Dilation pressure assembly214may be positioned so that it surrounds at least a portion of clamp ring144and hydraulic passages182,216are in alignment. For example, dilation pressure assembly214may be ring-shaped and include an inner surface217defining an aperture that is configured for receiving clamp ring144. On one aspect, the entire inner surface217, or a substantial portion thereof, may be in contact with outer surface184of clamp ring144. The hydraulic pressure supply201may be connected to pressure port200, and hydraulic passage216(via a pressure input tube220), so that hydraulic fluid may be independently inputted into hydraulic passage200and hydraulic passages182,216, respectively. For example, hydraulic pressure supply201may include a first (medium) pressure pump attached to hydraulic passage200, and a second (high) pump attached to hydraulic passages216,182. At this point, hydraulic fluid may be introduced in an independent, alternating manner between hydraulic passage200and hydraulic passages182,216to incrementally move clamp ring144from the first relative position at the zero interference point to the second relative position so that collar portion146of coupling hub142is frictionally coupled with shaft112. For example, hydraulic fluid is first introduced through hydraulic passages216,182and into the interface between outer surface178of collar portion146and inner surface176of clamp ring144. This provides for dilation at the interface between outer surface178of collar portion146and inner surface176of clamp ring144. Hydraulic fluid is then introduced though hydraulic passage200and into pressure chamber194. The pressure within chamber194causes cylinder188and piston192to separate from one another, whereby cylinder188is moved in a direction218. The contact between the ends surfaces204,206of cylinder188and clamp ring144causes cylinder188to move clamp ring144an incremental distance in direction218. The presence of the hydraulic fluid at the interface between outer surface178of collar portion146and inner surface176of clamp ring144facilitates the movement of clamp ring144up the incline of the taper on outer surface178of collar portion146. As clamp ring144moves in direction218relative to collar portion146, inwardly directed radial force180is generated which causes collar portion146to be squeezed into outer surface152of shaft112. This squeeze creates an interference pressure between collar portion146and shaft112and thus the frictional connectivity therebetween. A current position of the clamp ring144relative to the collar portion146of coupling hub is then measured relative to the first relative position, or otherwise identified, to determine if the current position is the second relative position that will result in the desired interference pressure between collar portion146and clamp ring144. If the current position is not the second relative position, then the above-referenced process repeats in a step-wise manner until clamp ring144reaches the second relative position, and therefore the desired interference pressure between collect portion146and shaft112is reached. For example, hub joint assembly100may create an interference pressure of approximately 0.004-0.005 in/(inch of outer diameter of hub). Once the second relative position is reached, the hydraulic pressure from hydraulic pressure supply201is released from the interface between outer surface178of collar portion146and inner surface176of clamp ring144, and then released from pressure chamber194. The mating outer surface178of collar portion146and inner surface176of clamp ring144thereafter operate as “locking” tapers which naturally prevent sliding and releasing of contact pressures at the interfaces between shaft112, coupling hub142and clamp ring144. Thereafter, hydraulic pressure supply201is disconnected from dilation pressure assembly214and piston192, and distal end213of piston192is disconnected from first distal end154of collar portion146. Dilation pressure assembly214is also removed from clamp ring144. Shaft plug160may then be attached to first distal end154of collar portion146so that end surface212of collar portion146is in contact with shaft plug160to retain coupling hub142in the second relative position. Connector118may then be attached to flange portion164using one or more fasteners120, such that when shaft112is rotating, the frictional connection between shaft112causes coupling hub142to rotate along with shaft112. This rotation is then translated through flange portion164and connector118. Connector118may then be attached to additional connectors and/or another hub joint assembly that is frictionally connected to a corresponding shaft in the same manner that has been described herein to transfer rotational movement of shaft112to the associated shaft. Numerous benefits and advantages are provided by the hub joint assembly described herein relative to the existing art. One benefit of the present hub joint assembly is that the coupling hub is loaded in compression as opposed to tension. This benefits the coupling hub because it no longer has to bear the high tensile stress required from an outer member of an interference pair. This allows the strength of the coupling hub material to be utilized for more useful power transmission functions. Further, a hydraulic hub in the prior art must grow radially a significant amount to generate the needed squeeze force on the shaft. This strains the material of the hub causing it to grow radially and circumferentially by a significant amount, usually about 90% of the design interference at its outer diameter. This growth strains connections with the flex elements causing them to bear additional stress. Accommodating such strain also affects the hub dimensionally in undesirable ways, potentially causing dimensional instability. In addition, variations of hub installation field practice cause additional variability in the interference level and thus stress and strain around connections which effects overall coupling durability. The hub joint assembly in accordance with the present invention does not suffer from this difficulty because the coupling hub is pressed radially against a radially stiff shaft which yields very low radial strain, associated stress and deflection. Moreover, when the hub joint assembly of the present invention is installed and removed, high pressure sliding occurs between the clamp ring and the coupling hub, as opposed to the hub and the shaft in the existing art. This is a benefit of the present invention because sliding damage may occasionally occur in the field. The present invention provides a benefit of robustness by preventing sliding damage to the shaft surface. It is preferred to protect the shaft because the shaft is an expensive component and difficult to repair. In the present invention, sliding only occurs between the clamp ring and coupling hub thereby protecting the shaft from damage. Unlike an existing hydraulically fit hub which must connect to a coupling flex element, a connector, a connecting machine or other, the outer surface of the clamp ring in the present invention does not have to interface with any members other than the coupling hub during operation. On existing hubs, these connections are often configured as a radial flange with bolt circle. Such features placed on an outer surface of the hub yield a non-uniform outer profile (FIG.1), resulting in significant pressure variations along the hub/shaft interface. This pressure variation makes for local high pressure regions at the interface which, when slid at installation, lead to damage of the hub and shaft surfaces. The clamp ring in the present invention has a uniform outer surface. This uniformity removes pressure concentration allowing for greater nominal interference levels to be designed, without local high pressure regions, typically 0.004-0.005 in/(inch of outer diameter of hub), yielding a greater power density of the hub joint assembly. Further, an existing low moment coupling connects the shaft to the flex element at the inboard end of the hub, as seen inFIG.1. One consequence of this is that the connector must extend over any features that make up the hub assembly. Existing shrink disc clamped connections require a large outer diameter to accommodate the connective internal components of the shrink disc forcing the connector to have an unpractically large outer diameter. The hub joint assembly of the present invention utilizes a low profile clamp ring outer diameter which better matches the outer diameter of a traditional hydraulic hub. This makes the hub joint assembly of the present invention better suited to fit within traditional low moment coupling designs. The present invention also provides an improvement to the hydraulic pressure connection between the dilation pressure assembly214and the clamp ring144. As explained with reference toFIG.4, the application of dilation pressure to clamp ring144causes inner surface176to expand, which provides added freedom for clamp ring144to move up the taper on outer surface178of collar portion146. As inner surface176expands during this process, outer surface184of clamp ring144also expands. Given that the entire, or a substantial portion, of inner surface217of dilation pressure assembly214is in contact with outer surface184of clamp ring144, the expansion of outer surface184of clamp ring144results in an increase in contact pressure between a threaded conical interface221between the end of pressure input tube220and hydraulic passage182to a damaging level. To address this issue, there is provided an alternative dilation pressure assembly that is radially less stiff compared to dilation pressure assembly214so that the contact pressure is less affected at the joint as the dilation pressure is increased and clamp ring144expands. There are a number of ways to make dilation pressure assembly radially less stiff, such as, for example, by removing material to reduce its cross-section and bending stiffness. For example, as best seen inFIGS.6-8, an alternative dilation pressure assembly214ais provided. As was described with respect toFIG.4, dilation pressure assembly214amay be used to incrementally place clamp ring144in the second relative position to coupling hub142to frictionally connect hub joint assembly100to shaft112at the desired interference pressure. In one example, the radial stiffness in dilation pressure assembly214amay be reduced by providing at least one recessed cut-out portion222defined in inner surface217, so that inner surface217is not in contact with outer surface184of clamp ring144in the region of the cut-out portion222. As best seen inFIGS.7and8, dilation pressure assembly214amay include, for example, four cut-out portions222(only three cut-outs are shown inFIG.7), which in turn define a corresponding number of extension members224that extend radially inwardly toward clamp ring144. Each of the extension members224may be spaced an equal distance apart from one another. An inner surface226of each extension member224may be configured to contact outer surface184of clamp ring144. One of extension members224includes hydraulic passage216that is configured to receive pressure input tube220and align with hydraulic passage182in clamp ring144to allow hydraulic fluid to be provided between the interface between outer surface178of collar portion146and inner surface176of clamp ring144via threaded interface221. The inclusion of cut-out portions222allow dilation pressure assembly214ato expand only in the location of extension members224, where the rest of the dilation pressure assembly214abows inward toward outer surface184of clamp ring144. This configuration reduces the contact pressure at the interface between pressure input tube220and hydraulic passage182. From the foregoing, it will be seen that this invention is one well adapted to attain all the ends and objects hereinabove set forth together with other advantages which are obvious and which are inherent to the method and apparatus. It will be understood that certain features and sub-combinations are of utility and may be employed without reference to other features and sub-combinations. This aspect is contemplated by and is within the scope of the claims. Since many possible embodiments of the invention may be made without departing from the scope thereof, it is also to be understood that all matters herein set forth or shown in the accompanying drawings are to be interpreted as illustrative and not limiting. The constructions described above and illustrated in the drawings are presented by way of example only and are not intended to limit the concepts and principles of the present invention. As used herein, the terms “having” and/or “including” and other terms of inclusion are terms indicative of inclusion rather than requirement. While the invention has been described with reference to preferred embodiments, it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted for elements thereof to adapt to particular situations without departing from the scope of the invention. Therefore, it is intended that the invention not be limited to the particular embodiments disclosed as the best mode contemplated for carrying out this invention, but that the invention will include all embodiments falling within the scope and spirit of the appended claims. | 27,240 |
11859672 | DETAILED DESCRIPTION OF EMBODIMENTS FIG.1shows a schematic diagram of a typical fracturing operation site arrangement. As shown inFIG.1, at the fracturing site, there is a manifold100with a plurality of manifold interfaces16to receive fracturing fluid, and the manifold100may be disposed on a skid to form a manifold skid. Fracturing equipment200such as a fracturing truck is connected with the interface of the manifold100through a hose6to deliver the fracturing fluid from the fracturing equipment200to the manifold100, and then to deliver the same downhole through the manifold for fracturing operations. AlthoughFIG.1shows that there are 8 fracturing trucks200connected to the manifold, more or fewer fracturing equipment may be connected according to demand. Upon preparation for the fracturing operation, after the fracturing equipment200arrives at the fracturing site, the fracturing equipment200needs to be connected to the manifold100through the hose. The present disclosure is to provide a quick connection device for realizing such an operation. FIG.2shows a hose quick connection device300for fracturing equipment. To deliver the fracturing fluid, one end of the high-pressure hose6may be fixedly or releasably connected to the fracturing equipment in advance. The hose quick connection device300according to the present disclosure realizes automatic quick connection of the free end of the hose and the manifold interface16. The hose quick connection device300shown inFIG.2includes a hose holding and moving mechanism, a controller17and an actuation mechanism20. The hose holding and moving mechanism can hold the hose6and move the free end of the hose6from an initial position to a target position aligned with the manifold interface16. For example,FIG.2shows an initial position in which the fracturing equipment is initially positioned relative to the manifold after the fracturing truck arrives at the site, wherein the free end of the hose6is not aligned with the manifold interface16. In the illustrated embodiment, the hose holding and moving mechanism includes a base1preferably arranged on the fracturing equipment, a fixed rod4extending vertically upward from the base1and horizontally rotatable, a first arm8pivotally connected to the fixed rod4around a joint7, and a second arm13pivotally connected to the first arm8around a joint11. The hose6is releasably held to the first arm8and the second arm13by the hose holding members9and12, respectively. In one embodiment, the hose holding members9and12may be in the form of hose clamps. Other structures capable of releasably holding the hose to the first arm8and the second arm13are also conceivable, such as sleeves. A hydraulic motor2is disposed in the base1to drive the fixed rod4to rotate horizontally by driving a rotating base3. A hydraulic cylinder5is disposed between the fixed rod4and the first arm8. One end of the hydraulic cylinder5is connected to the side of the fixed rod4while the opposite end is connected to the side of the first arm8. A hydraulic cylinder10is provided between the first arm8and the second arm13. One end of the hydraulic cylinder10is connected to the side of the first arm8while the opposite end is connected to the side of the second arm13. The expansion and contraction of the hydraulic cylinders5and10may drive the first arm8and the second arm13to pivot around the joints7and11. The controller17may communicate with a first sensing device15provided on the manifold interface16to receive orientation information indicating the orientation of the manifold interface from the first sensing device15. The controller17may communicate with a second sensing device14provided on the free end of the hose6to receive orientation information indicating the orientation of the free end of the hose from the second sensing device14. In addition, the controller17may compare the orientation information of the manifold interface and the free end of the hose and calculate a desired motion command for moving the free end of the hose to the target position aligned with the manifold interface. Then, the controller17sends the desired motion command to the actuation mechanism20. In response, the actuation mechanism20actuates the hose holding and moving mechanism to move the free end of the hose6to the target position. The controller17may be a processor and preferably integrated in a fracturing equipment controller18of the fracturing equipment, as shown inFIG.3. The first sensing device15and the second sensing device14may be various forms of position sensors, such as laser sensors, smart sensors, and the like. Alternatively, the first sensing device15and the second sensing device14may each be a 3D scanning positioning system to form point cloud data by scanning the surface contour of the manifold interface, thereby obtaining the spatial coordinates of the current interface. In the illustrated embodiment, the actuation mechanism20is a hydraulic mechanism, which, in response to the desired motion command from the controller17, delivers hydraulic oil to the hydraulic motor2, the hydraulic cylinder5and the hydraulic cylinder10to enable the hose holding and moving mechanism to operate the hose6. Specifically, the hydraulic motor2drives the fixed rod4to rotate horizontally by driving the rotating base3. The expansion and contraction of the hydraulic cylinders5and10may drive the first arm8and the second arm13to pivot around the joints7and11, thereby changing the positioning and orientation of the free end of the hose6so that the free end of the hose6may move up, down, left, and right to any position within a certain range, and finally to the target position aligned with the manifold interface16. The operation process of the hose quick connection device is described below. As mentioned above, the base1of the hose quick connection device is mounted on the fracturing equipment, and the hose6is connected with the fracturing equipment to deliver the fracturing fluid. The fracturing equipment arrives at the operation site and is positioned close to the manifold skid so that the free end of the hose6can reach the manifold interface16within its maximum range of movement. By operating the controller17, for example, by a user inputting an instruction, the first sensing device15on the manifold interface16and the second sensing device14on the free end of the high-pressure hose6respectively send the orientation information, e.g., coordinate information of the manifold interface16and the free end of the hose6to the controller17. The controller17calculates a desired motion command for moving the free end of the hose6to the target position aligned with the manifold interface based on the received orientation information of the manifold interface16and the free end of the hose6. Then, the controller17sends the desired motion command to the actuation mechanism20, and the actuation mechanism20delivers hydraulic oil to the hydraulic motor2, the hydraulic cylinder5and the hydraulic cylinder10according to the desired motion command, so that the fixed rod4and the first arm8and the second arm13moves the free end of the hose6toward the manifold interface as desired. For example, the actuation mechanism20may supply oil to the hydraulic motor2in response to the desired motion command from the controller17to drive the fixed rod4to rotate horizontally. According to the desired motion command, after the fixed rod4is rotated to a certain angle as needed, the hydraulic motor2will automatically stop rotating. While stopping the rotation, the controller17may control the actuation mechanism20to supply oil to the hydraulic cylinder5to make the hydraulic cylinder5expand or contract, so as to drive the first arm8to pivot around the joint7, thereby driving the hose holding member9, the hose holding member12, the second arm13and the hose6to pivot vertically around the joint7. According to the requirements of the desired motion command, the actuation mechanism20is controlled to supply oil to the hydraulic cylinder10to control the expansion and contraction thereof, thereby driving the second arm13and the hose6to pivot vertically around the joint11. Through this series of actions, the free end of the hose6may be full-automatically moved to align with the manifold interface16, as shown inFIG.3, thereby achieving the alignment and connection with the manifold interface without requiring workers to manually lift and pull the hose of over 100 kilograms. Once the high-pressure hose6is aligned with the manifold interface16, the high-pressure hose6may be connected to the manifold interface16. The high-pressure hose6may be connected to the manifold interface16in a union form, a quick-plug form or other available forms. Although individual operations of the hydraulic motor2, the hydraulic cylinder5and the hydraulic cylinder10are specifically described above, it is apparent for those skilled in the art that the operations may be parallel, or actuated separately or simultaneously. The actuation mechanism20may include separate hydraulic circuits that control the hydraulic motor2, the hydraulic cylinder5and the hydraulic cylinder10, respectively. The present disclosure is described above in conjunction with the hydraulic actuation mechanism, but those skilled in the art may appreciate that the actuation mechanism of the present disclosure is not limited to the hydraulic mechanism, and may also be an electric actuation mechanism or a combination of the electrical actuation mechanism with the hydraulic actuation mechanism. For example, the hydraulic actuator i.e., the hydraulic motor2may be replaced with an electric motor, the hydraulic cylinder5and the hydraulic cylinder10may be removed, and a servo motor is instead installed at the joint7and the joint11. As such, various embodiments have been shown and described. Certainly, various changes and substitutions may be made without departing from the spirit and scope of the present disclosure. Therefore, in addition to the appended claims and their equivalent scope, the disclosure is not subject to other restrictions. | 10,122 |
11859673 | In the drawings: power shaft1, wheel body2, clutch part3, annular space4, convex tooth5, groove6, rotary driving piece7, spiral sliding groove8, control rotary knob9, annular damping ring10, concave-convex deformation tooth11, concave-convex body12, annular groove13, central supporting shaft14, motor power input structure15, first bearing16, second bearing17, axial sunken groove18, deformation-promoting notch19, sliding protrusion31, sliding strip32, first leading-in inclined surface51, second leading-in inclined surface61. DETAILED DESCRIPTION OF EMBODIMENTS The present invention will be further described in detail in combination with the accompanying drawings and the specific embodiments. as shown inFIG.1, a clutch type driving wheel of an electric scooter includes a wheel body2and a power shaft1penetrating through the center of the wheel body2, wherein a motor power input structure15is arranged at one end of the power shaft1, a central supporting shaft14penetrates through the power shaft1, at least one first bearing16is arranged between the power shaft1and the central supporting shaft14, at least one second bearing17is arranged between the power shaft1and the wheel body2, a controlled clutch structure which enables the wheel body2to be circumferentially positioned relative to the power shaft1or enables the wheel body2to circumferentially rotate relative to the power shaft1when the controlled clutch structure acts is arranged between the power shaft1and the wheel body2, and a clutch state locking structure is arranged on the controlled clutch structure. The driving motor drives the power shaft1through the motor power input structure15to rotate, the central supporting shaft14provides a radial supporting force to the power shaft1through the first bearing16, the power shaft1provides a radial supporting force to the wheel body2through the second bearing17, the power shaft1and the wheel body2may rotate around the central supporting shaft14as a center, the controlled clutch structure is arranged between the power shaft1and the wheel body2, the controlled clutch structure may enable the power shaft1and the wheel body2to be in transmission connection (circumferentially fixed) or be separated mutually (circumferentially separated) through action, and the clutch state locking structure may lock the controlled clutch structure, so that the controlled clutch structure cannot easily act, that is, the controlled clutch structure does not act to change the connection state between the power shaft1and the wheel body2under the influence of the external accidental factors; therefore, the clutch state locking structure is arranged between two rotating pieces to ensure that the state stability can be maintained when the two rotating pieces are in a transmission connection state or a mutual separation state, and switching between the two states caused by some accidental external factors is avoided, thereby ensuring the smooth use of the product with the clutch mechanism and preventing accidents that cause harm to users. Specifically, the controlled clutch structure is arranged on the power shaft1, the controlled clutch structure includes a clutch part3capable of moving axially along the power shaft1so as to enable the wheel body2to be circumferentially positioned relative to the power shaft1or enable the wheel body2to circumferentially rotate relative to the power shaft1, the clutch part3is connected to a driving structure capable of converting rotating motion into axial movement of the clutch part3along the power shaft1, and the clutch state locking structure is arranged between the driving structure and the power shaft1. The power shaft1may drive the clutch part3to rotate circumferentially and synchronously, and the clutch part3may slide axially relative to the power shaft1, which may be realized through cooperation between the sunken grooves18and the sliding strips32. For example, as shown inFIG.3, the circumferential positioning and axial sliding structure includes several axial sunken grooves18arranged on the power shaft1and several sliding strips32arranged on the clutch part3, the sliding strips32and the axial sunken grooves18are arranged in a one-to-one correspondence way, and the sliding strips32are arranged in the axial sunken grooves18, so that the sliding strips32only can slide along the axial sunken grooves18when sliding, and the clutch part3only can slide axially relative to the power shaft1. The clutch part3realizes the transmission connection or mutual separation with the wheel body by sliding along an axis direction of the power shaft1, for example, a concave-convex engagement structure may be arranged between the clutch part3and the wheel body2. When the clutch part is axially forward, the concave-convex engagement structure is engaged so as to circumferentially position the power shaft1and the wheel body2. When the clutch part3is axially backward, the concave-convex engagement structure is separated so as to circumferentially separate the power shaft1and the wheel body2. The clutch part3slides along the axis direction of the power shaft1by rotating the driving structure. According to the present invention, a specific structure of the driving structure capable of converting rotating motion into linear motion is not limited, may adopt a screw rod sliding block structure, or may also adopt a structure as shown inFIG.1andFIG.2. The driving structure includes a rotary driving piece7, the rotary driving piece7is provided with several spiral sliding grooves8distributed at intervals in a circumferential direction, the clutch part3is provided with several sliding protrusions31distributed at intervals in the circumferential direction, the spiral sliding grooves8and the sliding protrusions31are arranged in a one-to-one correspondence way and are in sliding connection, the rotary driving piece7is fixedly connected to a control rotary knob9, the clutch state locking structure is arranged between the control rotary knob9and the power shaft1, the control rotary knob9rotates to enable the rotary driving piece7to rotate synchronously, the spiral sliding grooves8distributed on the surface of the rotary driving piece7at intervals in the circumferential direction rotate, the sliding protrusions31positioned in the spiral sliding grooves8slide along the spiral sliding grooves8, and since the spiral sliding grooves8are spiral along the axial direction of the power shaft1, the sliding protrusions31drive the clutch part3to slide along the axis direction of the power shaft1. The control rotary knob9may be a polygon or may be a circle with an inward concave arc, so that when the control rotary knob rotates, a user has an appropriate point of force application. Preferably, an annular space4is formed between the power shaft1and the wheel2, and the clutch part3is arranged in the annular space4, so that the action of the clutch part3may be limited in the annular space4, which plays a certain limiting guidance role. In combination withFIG.3andFIG.4, the clutch part3is cylindrical and sleeves the power shaft1, a circumferential positioning and axial sliding structure is arranged between the clutch part3and the power shaft1, several convex teeth5distributed uniformly in a circumferential directional are arranged at the front end of the clutch part3, several grooves6distributed uniformly in the circumferential direction are formed in an inner side of the wheel body2, the convex teeth5can be arranged corresponding to the grooves6and can be inserted into each other, and the clutch part3slides along an axis direction of the power shaft1. The power shaft1and the wheel body2are in transmission connection when the convex teeth5are inserted into the grooves6. When the convex teeth5are removed from the grooves6, the power shaft1and the wheel body2are mutually separated, and the convex teeth5and the grooves6are distributed uniformly in the circumferential direction, thereby facilitating the engagement action of the wheel body2and the clutch part3. Meanwhile, when the wheel body2and the clutch part3are engaged, the engagement force can be distributed uniformly and the stability can be enhanced. Preferably, at least one first leading-in inclined surface51is arranged at the front end of each of the convex teeth5; and at least one second leading-in inclined surface61is arranged at a notch of each of the grooves6, the first leading-in inclined surface51and the second leading-in inclined surface61are arranged at the opposite position of the convex teeth5and the grooves6respectively, so that the convex teeth5are conveniently inserted into the grooves6and are engaged with the grooves6. In combination withFIG.1,FIG.2andFIG.5, the clutch state locking structure includes an annular damping ring10, the annular damping ring10is provided with several concave-convex deformation teeth11, several concave-convex bodies are arranged at an outer end of the wheel body2, the annular damping ring10sleeves the periphery of the power shaft1, rotary blockage is realized after the concave-convex deformation teeth11of the annular damping ring10pass over the concave-convex bodies12, the annular damping ring10is fixedly connected to the control rotary knob9, an annular groove13is formed at the periphery of the power shaft1, the concave-convex bodies12are arranged in the annular groove13, the annular damping ring10is embedded in the annular groove13, the annular damping ring10is shaped like a polygonal ring, each side of the annular damping ring is arcuately sunken inward, the concave-convex deformation teeth11are arranged at the middle parts of the sides, and deformation-promoting notches19are formed in two sides of the sides respectively. The control rotary knob9rotates to drive the annular damping ring10to rotate synchronously until the concave-convex deformation teeth11pass over the concave-convex bodies12, so that the annular damping ring10and the concave-convex bodies12are mutually clamped to lock the clutch part3, wherein the annular damping ring10is shaped like a polygonal ring, each side of the annular damping ring is arcuately sunken inward, the concave-convex deformation teeth11are arranged at the middle parts of the sides, and deformation-promoting notches19are formed in two sides of the sides respectively, so that the annular damping ring10may deform by compressing the deformation-promoting notch19, and the concave-convex deformation teeth11may pass over the concave-convex bodies12conveniently. Preferably, the annular damping ring10is provided with a mounting notch for mounting the annular damping ring10into the annular groove13, that is, the annular damping ring10is C-shaped, so that when the annular damping ring10is mounted into the annular groove13, an inner diameter of the annular damping ring10may be shrunk by compressing the mounting notch, thereby facilitating mounting operation. The working principle of the present invention is: during use, the driving motor drives the power shaft1through the motor power input structure15to rotate, the control rotary knob9rotates to drive the rotary driving piece7to rotate synchronously when the wheel body2need to be in transmission connection with the power shaft1, the sliding protrusions31slide along the spiral sliding grooves8so as to drive the clutch part3to slide away from the control rotary knob9, the clutch part3slides axially under the cooperative guide action of the sliding strips32and the axis sunken grooves18, the convex teeth5are embedded into the grooves6, the power shaft1is in transmission connection with the wheel body2, and at this time, the concave-convex deformation teeth11just pass over the concave-convex bodies12, so that the concave-convex bodies and the annular damping ring10are clamped mutually. When the wheel body2rotates by itself, that is, needs to be separated from the power shaft1, a larger force is applied to a direction of rotating the control rotary knob9, so that the concave-convex bodies12are removed from the clamping force of the annular damping ring10and rotate, the sliding protrusions31slide along the spiral sliding grooves8so as to drive the clutch part3to slide close to the control rotary knob9, the clutch part3slides axially under the cooperative guidance action of the sliding strips32and the axis sunken grooves18, the convex teeth5are removed from the grooves6, the power shaft1and the wheel body2are separated from each other, and at this time, the concave-convex deformation teeth11on the other side just pass over the concave-convex bodies12, so that the concave-convex bodies12and the annular damping ring10are mutually clamped; therefore, according to the present invention, the clutch state locking structure is arranged between the power shaft1and the wheel body2, the state stability can be maintained when the power shaft1and the wheel body2are in a transmission connection state or a mutual separation state, and switching between the two states caused by some accidental external factors is avoided, thereby ensuring the smooth use of the electric scooter, preventing accidents that cause harm to users and greatly improving the safety. The specific embodiments described herein are only for illustrating the spirit of the present invention. A person skilled in the art can make various modifications or supplements to the specific examples described or replace them in a similar manner, but it may not depart from the spirit of the present invention or the scope defined by the appended claims. Although terms such as power shaft1, wheel body2, clutch part3, annular space4, convex tooth5, groove6, rotary driving piece7, spiral sliding groove8, control rotary knob9, annular damping ring10, concave-convex deformation tooth11, concave-convex body12, annular groove13, central supporting shaft14, motor power input structure15, first bearing16, second bearing17, axial sunken groove18, deformation-promoting notch19, sliding protrusion31, sliding strip32, first leading-in inclined surface51and second leading-in inclined surface61are widely used in the specification, the possibility of using other terms is not excluded. These terms are used only for more conveniently describing and explaining the essence of the present invention and the interpretation of them as any additional limitation is against the spirit of the present invention. | 14,428 |
11859674 | DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Clutch devices according to preferred embodiments of the present disclosure will be described hereinafter with reference to the drawings. The preferred embodiments described herein are, of course, not intended to particularly limit the present disclosure. Elements and features having the same functions are denoted by the same reference characters, and description for the same elements and features will not be repeated or will be simplified as appropriate. First Preferred Embodiment FIG.1is a cross-sectional view of a clutch device10according to this preferred embodiment. The clutch device10is provided in a vehicle such as a motorcycle, for example. The clutch device10allows or interrupts transfer of a rotation driving force of an input shaft (crankshaft) of an engine of the motorcycle to an output shaft15, for example. The clutch device10allows or interrupts transfer of a rotation driving force of the input shaft to a drive wheel (rear wheel) through the output shaft15. The clutch device10is disposed between the engine and a transmission. In the following description, directions in which a pressure plate70of the clutch device10and the clutch center40are arranged will be referred to as directions D, a direction in which the pressure plate70moves toward the clutch center40will be referred to as a first direction D1, and a direction in which the pressure plate70moves away from the clutch center40will be referred to as a second direction D2. The directions D are examples of movement directions. Circumferential directions of the clutch center40and the pressure plate70will be referred to as circumferential directions S, one of the circumferential direction S from one pressure-side cam portion90to another pressure-side cam portion90will be referred to as a first circumferential direction S1(seeFIG.4), and one of the circumferential direction S from the other pressure-side cam portion90to the one pressure-side cam portion90will be referred to as a second circumferential direction S2(seeFIG.4). In this preferred embodiment, axial directions of the output shaft15, axial directions of a clutch housing30, axial directions of the clutch center40, and axial directions of the pressure plate70are the same as the directions D. The pressure plate70and the clutch center40rotate in the first circumferential direction S1. It should be noted that the directions described above are defined simply for convenience of description, and are not intended to limit the state of installation of the clutch device10and do not limit the present disclosure. The output shaft15is a hollow shaft. As illustrated inFIG.1, one end of the output shaft15rotatably supports an input gear35described later and the clutch housing30through a bearing (not shown). The output shaft15fixedly supports a clutch center40through a nut (not shown). That is, the output shaft15rotates together with the clutch center40. The other end of the output shaft15is coupled to a transmission (not shown) of an automobile, for example. The clutch housing30is made of an aluminum alloy. The clutch housing30has a bottomed cylindrical shape. As illustrated inFIG.1, the clutch housing30includes a bottom wall31having a substantially circular shape, and a side wall33extending from an edge of the bottom wall31in the first direction D1. The clutch housing30holds the plurality of input-side rotating plates20. As illustrated inFIG.1, an input gear35is disposed on the bottom wall31of the clutch housing30. The input gear35is fixed to the bottom wall31by a rivet35B through a torque damper35A. The input gear35meshes with a driving gear (not shown) that rotates by rotational driving of the input shaft of the engine. The input gear35is rotationally driven together with the clutch housing30, independently of the output shaft15. The input-side rotating plates20is rotationally driven by rotational driving of the input shaft. As illustrated inFIG.1, the input-side rotating plates20are held on the inner peripheral surface of the side wall33of the clutch housing30. The input-side rotating plates20are held in the clutch housing30by spline fitting. The input-side rotating plates20are displaceable along the axial direction of the clutch housing30. The input-side rotating plates20are rotatable together with the clutch housing30. The input-side rotating plates20are pushed against the output-side rotating plates22. The input-side rotating plates20are ring-shaped flat plates. Each of the input-side rotating plates20is shaped by punching a thin plate of a steel plate cold commercial (SPCC) material into a ring shape. Friction members (not shown) of a plurality of paper sheets are attached to the front and back surfaces of the input-side rotating plates20. A groove with a depth of several micrometers to several tens of micrometers, for example, is located between the friction members to hold clutch oil. As illustrated inFIG.1, the clutch center40is housed in the clutch housing30. The clutch center40and the clutch housing30are concentrically disposed. The clutch center40includes a cylindrical body42and a flange68extending radially outward from the outer edge of the body42. The clutch center40holds the plurality of output-side rotating plates22arranged alternately with the input-side rotating plates20in the directions D. The clutch center40is rotationally driven together with the output shaft15. As illustrated inFIG.2, the body42includes a ring-shaped base wall43, an outer peripheral wall45located radially outward of the base wall43and extending in the second direction D2, an output shaft holding portion50disposed at the center of the base wall43, a plurality of center-side cam portions60connected to the base wall43and the outer peripheral wall45, and a center-side fitting portion58. As illustrated inFIG.2, the output shaft holding portion50has a cylindrical shape. The output shaft holding portion50projects from a surface43A of the base wall43in the second direction D2. The surface43A of the base wall43is an example of a surface of the body42on the side of the second direction D2. An end of the output shaft holding portion50on the side of the second direction is located ahead, in the second direction D2, of an end of the outer peripheral wall45on the side of the second direction D2. The output shaft holding portion has an insertion hole51which penetrates the output shaft holding portion50and in which the output shaft15is inserted and spline-fitted. An inner peripheral surface50A of the output shaft holding portion50defining the insertion hole51includes a plurality of spline grooves positioned along the axial direction. The output shaft15is coupled to the output shaft holding portion50. As illustrated inFIG.2, the outer peripheral wall45of the clutch center40is disposed radially outward of the output shaft holding portion50. An outer peripheral surface45A of the outer peripheral wall45includes a spline fitting portion46. The spline fitting portion46includes a plurality of center-side fitting teeth47extending in the axial directions of the clutch center40along the outer peripheral surface45A of the outer peripheral wall45, a plurality of spline grooves48each formed between adjacent ones of the center-side fitting teeth47and extending in the axial directions of the clutch center40, and oil flow holes49. The center-side fitting teeth47hold the input-side rotating plates20and the output-side rotating plates22. The plurality of center-side fitting teeth47arranged in the circumferential directions S. The plurality of center-side fitting teeth47are arranged at regular or substantially regular intervals in the circumferential directions S. The plurality of center-side fitting teeth47have the same or substantially the same shape. The center-side fitting teeth47project radially outward from the outer peripheral surface45A of the outer peripheral wall45. The oil flow holes49penetrate the outer peripheral wall45along the radial directions. Each of the oil flow holes49is located between adjacent ones of the center-side fitting teeth47. That is, the oil flow holes49are located in the spline grooves48. The oil flow holes49are located at the sides of the center-side cam portions60. More specifically, the discharge holes49are located at the sides of the center-side assist cam surfaces60A of the center-side cam portions60. The oil flow holes49are located ahead of the center-side assist cam surface60A in the second circumferential direction S2. The oil flow holes49are located ahead of spring housing portions54described later in the first circumferential direction S1. In this preferred embodiment, for example, three oil flow holes49are located in each of three portions of the outer peripheral wall45in the circumferential directions S. The oil flow holes49are arranged at regular or substantially regular intervals in the circumferential directions S. The oil flow holes49cause the inside and outside of the clutch center40to communicate with each other. The oil flow holes49allow clutch oil in the clutch center40to be discharged to the outside of the clutch center40. In this preferred embodiment, the oil flow holes49allow clutch oil flowing at an inner peripheral surface45B of the outer peripheral wall45to be discharged to the outside of the clutch center40. The output-side rotating plates22are held by the spline fitting portion46of the clutch center40and the pressure plate70. A portion of the output-side rotating plates22is held by the center-side fitting teeth47of the clutch center40and the spline grooves48by spline fitting. Another portion of the output-side rotating plates22is held by a pressure-side fitting teeth77(seeFIG.4) described later of the pressure plate70. The output-side rotating plates22are displaceable along the axial directions of the clutch center40. The output-side rotating plates22are rotatable together with the clutch center40. The output-side rotating plates22are pushed against the input-side rotating plates20. The output-side rotating plates22are ring-shaped flat plates. Each of the output-side rotating plates22is shaped by punching a thin plate of an SPCC material into a ring shape. The front and back surfaces of the output-side rotating plates22have grooves with depths of several micrometers to several tens of micrometers, for example, to hold clutch oil. The front and back surfaces of the output-side rotating plates22are subjected to a surface hardening treatment to enhance abrasion resistance. The friction members provided on the input-side rotating plates20may be provided on the output-side rotating plates22instead of the input-side rotating plates20, or may be provided on both the input-side rotating plates20and the output-side rotating plates22. Each of the center-side cam portions60preferably has a trapezoidal shape including a cam surface of a slope defining an assist & slipper (registered trademark) mechanism that generates an assist torque as a force of increasing a pressing force (contact pressure force) between the input-side rotating plates20and the output-side rotating plates22or a slipper torque as a force of separating the input-side rotating plates20and the output-side rotating plates22from each other early and shifting these plates into a half-clutch state. The center-side cam portions60are formed in the body42. More specifically, the center-side cam portions60project from the base wall43in the second direction D2. As illustrated inFIG.3, the center-side cam portions60are arranged at regular or substantially regular intervals in the circumferential directions S of the clutch center40. In this preferred embodiment, the clutch center40includes three center-side cam portions60, but the number of the center-side cam portions60is not limited to three. As illustrated inFIG.2, the center-side cam portions60are located radially outward of the output shaft holding portion50. Each of the center-side cam portions60includes the center-side assist cam surface60A and the center-side slipper cam surface60S. The center-side assist cam surface60A is configured to generate a force in a direction from the pressure plate70toward the clutch center40in order to increase a pressing force (contact pressure force) between the input-side rotating plates20and the output-side rotating plates22in relative rotation to the pressure plate70. In this preferred embodiment, when this force is generated, the position of the pressure plate70to the clutch center40does not change, and the pressure plate70does not need to approach the clutch center40physically. The pressure plate70may be physically displaced with respect to the clutch center40. The center-side slipper cam surface60S is configured to separate the pressure plate70from the clutch center40in order to reduce the pressing force (contact pressure force) between the input-side rotating plates20and the output-side rotating plates22in relative rotation to the pressure plate70. In the center-side cam portions60adjacent to each other in the circumferential directions S, the center-side assist cam surface60A of one center-side cam portion60L and the center-side slipper cam surface60S of the other center-side cam portion60M are opposed to each other in the circumferential directions S. As illustrated inFIGS.2and3, the clutch center40includes spring housing portions54. The spring housing portions54are located in the base wall43. The spring housing portions54are recessed in the second direction D2from a back surface43B of the base wall43. The back surface43B of the base wall43is an example of a surface of the body42on the side of the first direction D1. Each of the spring housing portions54has an oval shape. The spring housing portions54house pressure springs25(seeFIG.1). The spring housing portions54are arranged at regular or substantially regular intervals in the circumferential directions S of the clutch center40. In this preferred embodiment, for example, the clutch center40includes three spring housing portions54, but the number of the spring housing portions54is not limited to three. The spring housing portions54are located ahead of the center-side slipper cam surface60S in the first circumferential direction S1. The spring housing portions54are located ahead of the center-side assist cam surface60A in the second circumferential direction S2. The spring housing portions54include through holes54H which penetrate the spring housing portions54and in which bosses84(seeFIG.4) described later are inserted. The through holes54H penetrate the base wall43. The through holes54H penetrate in the movement directions D. The through holes54H extend in the circumferential directions S. The through holes54H allow movement of the bosses84in the circumferential directions S and in the directions D. Each of the through holes54H of this preferred embodiment has an oval shape. As illustrated inFIG.1, the pressure springs25are housed in the spring housing portions54. The pressure springs25are held by the bosses84described later inserted in the through holes54H (seeFIG.3) of the spring housing portions54. The pressure springs25bias the pressure plate70toward the clutch center40(i.e., in the first direction D1). The pressure springs are, for example, coil springs obtained by radially winding spring steel. As illustrated inFIGS.2and3, the clutch center40includes center-side cam holes43H penetrating a portion of the base wall43. The center-side cam holes43H penetrate the base wall43in the directions D. The center-side cam holes43H extend from portions on the side of the output shaft holding portion50to the outer peripheral wall45. Each of the center-side cam holes43H is located between the center-side assist cam surface60A of the center-side cam portion60and the spring housing portions54. When seen in the axial direction of the clutch center40, the center-side assist cam surface60A overlaps with a portion of the center-side cam hole43H. As illustrated inFIG.3, the clutch center40includes a center-side sliding surface56on which a lifter plate100(seeFIG.1) slides. The center-side sliding surface56is disposed at the inner peripheral surface45B of the outer peripheral wall45. The center-side sliding surface56is located ahead of the back surface43B of the base wall43in the first direction D1. As illustrated inFIG.2, the center-side fitting portion58is disposed at the outer peripheral surface of the output shaft holding portion50. The center-side fitting portion58is slidably fitted in a pressure-side fitting portion88described later (seeFIG.4). A gap is located between the center-side fitting portion58and the pressure-side fitting portion88. In this preferred embodiment, for example, the outer diameter of the center-side fitting portion58is smaller by about 0.1 mm than the inner diameter of the pressure-side fitting portion88. A dimensional tolerance between the outer diameter of the center-side fitting portion58and the inner diameter of the pressure-side fitting portion88is, for example, about 0.1 mm or more and about 0.5 mm or less. The length of the center-side fitting portion58in the directions D is longer than a travel distance (stroke) of the pressure plate70in the directions D. As illustrated inFIG.1, the pressure plate70is housed in the clutch housing30. The pressure plate70is located between the clutch housing30and the clutch center40. As illustrated inFIG.1, the pressure plate70is movable toward or away from the clutch center40and rotatable relative to the clutch center40. The pressure plate70is configured to press the input-side rotating plates20and the output-side rotating plates22. The pressure plate70is disposed coaxially with the clutch center40and the clutch housing30. The pressure plate70includes a body72, and a flange98connected to the outer edge of the body72on the side of the second direction D2and extending radially outward. The body72projects ahead of the flange98in the first direction D1. The pressure plate70holds the plurality of output-side rotating plates22arranged alternately with the input-side rotating plates20. The output-side rotating plates22are displaceable along the axial directions of the pressure plate70. The output-side rotating plates22are rotatable together with pressure plate70. As illustrated inFIG.4, the body72includes a fitting hole80, the plurality of pressure-side cam portions90, and the pressure-side fitting portion88. As illustrated inFIG.4, the flange98extends radially outward from the outer edge of the body72. The flange98and the flange68of the clutch center40sandwich the input-side rotating plates20and the output-side rotating plates22. The flange98applies a pressing force to the input-side rotating plates20and the output-side rotating plates22. As illustrated inFIG.4, the fitting hole80is located at the center of the body72. The fitting hole80penetrates the body72in the directions D. The output shaft holding portion50of the clutch center40is inserted in the fitting hole80. As illustrated inFIG.4, the pressure-side fitting portion88is disposed at the inner peripheral surface of the body72to define the fitting hole80. The pressure-side fitting portion88is slidably fitted onto the center-side fitting portion58(seeFIG.2). Each of the pressure-side cam portions90preferably has a trapezoidal shape including a cam surface of a slope constituting an assist & slipper (registered trademark) mechanism that slides on the center-side cam portions60and generates an assist torque or a slipper torque. The pressure-side cam portions90project from the flange98in the first direction D1. As illustrated inFIG.5, the pressure-side cam portions90are arranged at regular or substantially regular intervals in the circumferential directions S of the pressure plate70. In this preferred embodiment, for example, the pressure plate70includes three pressure-side cam portions90, but the number of the pressure-side cam portions90is not limited to three. As illustrated inFIG.4, the pressure-side cam portion is located radially outward of the fitting hole80. Each of the pressure-side cam portions90includes a pressure-side assist cam surface90A and a pressure-side slipper cam surface90S. The pressure-side assist cam surface90A can be brought into contact with the center-side assist cam surface60A. The pressure-side assist cam surface90A is configured to generate a force in a direction from the pressure plate70toward the clutch center40in order to increase a pressing force (contact pressure force) between the input-side rotating plates20and the output-side rotating plates22in relative rotation to the clutch center40. The pressure-side slipper cam surface90S can be brought into contact with the center-side slipper cam surface60S. The pressure-side slipper cam surface90S is configured to separate the pressure plate70from the clutch center40in order to reduce a pressing force (contact pressure force) between the input-side rotating plates20and the output-side rotating plates22in relative rotation to the clutch center40. In the pressure-side cam portions90adjacent to each other in the circumferential directions S, the pressure-side assist cam surface90A of one pressure-side cam portion90L and the pressure-side slipper cam surface90S of the other pressure-side cam portion90M are opposed to each other in the circumferential directions S. Advantages of the center-side cam portions60and the pressure-side cam portions90will now be described. When the rotation speed of the engine increases so that a rotation driving force input to the input gear35and the clutch housing30is thereby allowed to be transferred to the output shaft15through the clutch center40, a rotation force in the first circumferential direction S1is applied to the pressure plate70, as illustrated inFIG.6A. Thus, with the effects of the center-side assist cam surface60A and the pressure-side assist cam surface90A, a force in first direction D1is generated in the pressure plate70. Accordingly, a contact pressure force between the input-side rotating plates20and the output-side rotating plates22increases. On the other hand, when the rotation speed of the output shaft15exceeds the rotation speed of the input gear35and the clutch housing30and a back torque is generated, a rotation force in the first circumferential direction S1is applied to the clutch center40, as illustrated inFIG.6B. Thus, with the effects of the center-side slipper cam surface60S and the pressure-side slipper cam surface90S, the pressure plate70moves in the second direction D2and releases a contact pressure force between the input-side rotating plates20and the output-side rotating plates22. In this manner, it is possible to avoid problems in the engine and the transmission caused by the back torque. As illustrated inFIG.4, the pressure plate70has pressure-side cam holes73H penetrating the body72and a portion of the flange98. The pressure-side cam holes73H are located radially outward of the fitting hole80. The pressure-side cam holes73H extend from portions on the side of the fitting hole80to the radially outside of the pressure-side cam portion90. Each of the pressure-side cam holes73H is located between adjacent ones of the pressure-side cam portions90. Each of the pressure-side cam holes73H is located between the pressure-side assist cam surface90A and the pressure-side slipper cam surface90S of adjacent ones of the pressure-side cam portions90. When seen in the axial direction of the pressure plate70, the pressure-side assist cam surface90A overlaps with portions of the pressure-side cam holes73H. As illustrated inFIG.4, the pressure plate70includes the plurality of pressure-side fitting teeth77formed on the flange98. The pressure-side fitting teeth77hold the input-side rotating plates20and the output-side rotating plates22. The pressure-side fitting teeth77are located radially outward of the fitting hole80. The pressure-side fitting teeth77are located radially outward of the pressure-side cam portions90. The pressure-side fitting teeth77project in the first direction D1from the flange98. The pressure-side fitting teeth77are arranged in the circumferential directions S. The pressure-side fitting teeth77are arranged at regular or substantially regular intervals in the circumferential directions S. As illustrated in IG.4, the pressure plate70includes a plurality of (for example, three in this preferred embodiment) bosses84. The bosses84support the clutch center40. The bosses84are arranged at regular or substantially regular intervals in the circumferential directions S. Each of the bosses84has a cylindrical shape. The bosses84are located radially outward of the fitting hole80. The bosses84extend in the directions D. The bosses84are disposed on the pressure-side cam portions90. Each of the bosses84is located between the pressure-side assist cam surfaces90A and the pressure-side slipper cam surface90S. The bosses84extend from surfaces90F of the pressure-side cam portions90toward the clutch center40(i.e., in the first direction D1). The bosses84have screw holes84H in which bolts28(seeFIG.1) are inserted. The screw holes84H extend in the axial directions of the pressure plate70. The surfaces90F of the pressure-side cam portions90is an example of surfaces of the pressure-side cam portions90on the side of the first direction D1(toward the clutch center40). FIG.5is a perspective view illustrating a state where the clutch center40and the pressure plate70are combined (hereinafter referred to as a combined state). In the state illustrated inFIG.5, the pressure-side assist cam surface90A and the center-side assist cam surface60A are not in contact with each other, and the pressure-side slipper cam surface90S and the center-side slipper cam surface60S are not in contact with each other. At this time, the pressure plate70is closest to the clutch center40. In the combined state, the pressure-side assist cam surface90A and the center-side assist cam surface60A may be in contact with each other, and the pressure-side slipper cam surface90S and the center-side slipper cam surface60S may not in contact with each other. As illustrated inFIG.7A, in the combined state, distal ends84T of the bosses84projects outward from the through holes54H. The distal ends84T of the bosses84are ends of the bosses84on the side of the first direction D1. As illustrated inFIG.7B, while the surfaces90F of the pressure-side cam portions90and surfaces60F of the center-side cam portions60are in contact (e.g., surface contact) with each other (i.e., in the state where the pressure plate70rides on the clutch center40), the distal ends84T of the bosses84project outward from the through holes54H. More specifically, while the surfaces90F of the pressure-side cam portions90and the surfaces60F of the center-side cam portions60are in contact with each other, the distal ends84T of the bosses84project outward from the back surface43B of the base wall43. While the surfaces90F of the pressure-side cam portions90and the surfaces60F of the center-side cam portions are in contact with each other, the distal ends84T of the bosses84are located ahead of the back surface43B in the first direction D1. Thus, in combining the clutch center40and the pressure plate70with each other, for example, even if the surfaces90F of the pressure-side cam portions90and the surface60F of the center-side cam portions60contact each other, the bosses84projecting outward from the through holes54H can be held. Rotation of the clutch center40in the circumferential directions S with the bosses84held, for example, can cancel the state where the pressure plate70rides on the clutch center40, and the positional relationship among the pressure-side assist cam surface90A, the center-side assist cam surface60A, the pressure-side slipper cam surface90S, and the center-side slipper cam surface60S can be corrected. The surfaces60F of the center-side cam portions60are an example of surfaces of the center-side cam portions60on the side of the second direction D2(toward the pressure plate70). As illustrated inFIG.1, the clutch device10includes the lifter plate100. The lifter plate100is used to displace the pressure plate70in the directions D. The lifter plate100is fixed to the pressure plate70with the bolts28. The lifter plate100rotates together with the pressure plate70. The lifter plate100slides in the directions D along the center-side sliding surface56of the clutch center40. The lifter plate100moves in the directions D relative to the clutch center40and rotates relative to the clutch center40. As illustrated inFIG.8, the lifter plate100includes a body portion102having a substantially cylindrical shape and extension portions104extending radially outward from the body portion102. As illustrated inFIG.1, the body portion102houses a release bearing103. The release bearing103is pressed by a release fork110of a clutch release mechanism (not shown). The clutch release mechanism herein is a mechanical device that presses the release bearing103toward the output shaft (i.e., toward the second direction D2) by driver's operation of a clutch operation lever (not shown) in a vehicle such as a motorcycle on which the clutch device10is mounted. InFIG.1, the release fork110is indicated by the chain double-dashed lines. As illustrated inFIG.1, the extension portions104support the pressure springs25housed in the spring housing portions54of the clutch center40. The extension portions104are portions that slide in the directions D along the center-side sliding surface56of the clutch center40. In this preferred embodiment, for example, the lifter plate100includes three extension portions104. The three extension portions104are arranged at regular or substantially regular intervals in the circumferential directions S. The extension portions104have insertion holes104H in which the bolts28to fix the lifter plate100to the pressure plate70are inserted. The clutch device10is filled with a predetermined amount of clutch oil. Clutch oil passes through the center-side cam holes43H from the sides of the back surface43B of the base wall43of the clutch center40to be distributed in the clutch center40and the pressure plate70. Clutch oil also flows at the outer peripheral surface45A of the outer peripheral wall45through the oil flow holes49from the side of the back surface43B of the base wall43of the clutch center40. Then, clutch oil is supplied to the input-side rotating plates20and the output-side rotating plates22at the outer peripheral surface45A of the outer peripheral wall45. Clutch oil reduces or prevents absorption of heat and abrasion of the friction members. The clutch device10according to this preferred embodiment is a so-called multiplate wet friction clutch device. Operation of the clutch device10according to this preferred embodiment will now be described. As described above, the clutch device10is disposed between the engine and the transmission of the motorcycle, and allows or interrupts transfer of a rotation driving force of the engine to the transmission by driver's operation of a clutch operation lever. In the clutch device10, in a case where the driver of the motorcycle does not operate the clutch operation lever, the release fork110of the clutch release mechanism (not shown) does not press the release bearing103, and thus, the pressure plate70presses the input-side rotating plates20with a biasing force (elastic force) of the pressure springs25. Accordingly, the clutch center40enters a clutch-ON state in which the input-side rotating plates20and the output-side rotating plates22are pushed against each other to be friction coupled, and is rotationally driven. That is, a rotation driving force of the engine is transferred to the clutch center40, and the output shaft15is rotationally driven. In the clutch-ON state, with the effect of the center-side assist cam surface60A and the pressure-side assist cam surface90A, a force in the first direction D1is generated in the pressure plate70. Accordingly, a contact pressure force between the input-side rotating plates20and the output-side rotating plates22increases. In addition, when the rotation speed of the output shaft15exceeds the rotation speed of the input gear35and the clutch housing30to cause a back torque in the clutch-ON state, the pressure plate70moves in the second direction D2to cancel the contact pressure force between the input-side rotating plates20and the output-side rotating plates22with the effect of the center-side slipper cam surface60S and the pressure-side slipper cam surface90S. On the other hand, in the clutch device10, when the driver of the motorcycle operates the clutch operation lever in the clutch-ON state, the release fork110of the clutch release mechanism (not shown) presses the release bearing103, and thus, the pressure plate70is displaced in a direction away from the clutch center40(second direction D2) against a biasing force of the pressure springs25. Accordingly, the clutch center40enters a clutch-OFF state in which friction coupling between the input-side rotating plates20and the output-side rotating plates22is canceled, and thus, rotational driving attenuates or stops. That is, a rotation driving force of the engine is interrupted to the clutch center40. At this time, since the center-side assist cam surface60A and the pressure-side assist cam surface90A are separated from each other and the center-side slipper cam surface60S and the pressure-side slipper cam surface90S are separated from each other, no assist torque and no stopper torque do not occur. Then, when the driver cancels the clutch operation lever in the clutch-OFF state, pressing of the release bearing103by the release fork110of the clutch release mechanism (not shown) through the push member16B is canceled, and thus, the pressure plate70is displaced with a biasing force of the pressure springs25to a direction (first direction D1) of moving toward the clutch center40. As described above, in the clutch device10according to this preferred embodiment, while the surfaces90F of the pressure-side cam portions90and the surfaces60F of the center-side cam portions60are in contact with each other, the distal ends84T of the bosses84project outward from the through holes54H. Thus, in combining the clutch center40and the pressure plate70, for example, even if the surfaces90F of the pressure-side cam portions90and the surfaces60F of the center-side cam portions60contact each other and the pressure plate70rides on the clutch center40, the bosses84projecting outward from the through holes54H can be held. Since the through holes54H extend in the circumferential directions S and allows movement of the bosses84in the circumferential directions S and the directions D, relative rotation of the clutch center40and the pressure plate70with the bosses84held can easily eliminate contact between the surfaces90F of the pressure-side cam portions90and the surfaces60F of the center-side cam portions60. In the clutch device10according to this preferred embodiment, the clutch center40includes the body42including the center-side cam portions60, and the spring housing portions54recessed in the second direction D2from the back surface43B of the base wall43of the body42and housing the pressure springs25that biases the pressure plate70in the first direction D1, the bosses84are formed on the pressure plate70, the through holes54H are formed in the spring housing portions54of the clutch center40, and the distal ends84T of the bosses84are located ahead of the back surface43B of the base wall43of the body42in the first direction D1while the surfaces90F of the pressure-side cam portions90and the surfaces60F of the center-side cam portions60are in contact with each other. In this configuration, even when the pressure plate70rides on the clutch center40, the bosses84on the pressure plate70project outward from the through holes54H in the spring housing portions54. At this time, the distal ends84T of the bosses84are located ahead of the back surface43B of the base wall43of the body42in the first direction D1. Accordingly, the bosses84can be easily held. In the clutch device10according to this preferred embodiment, each of the center-side cam portions60includes the center-side assist cam surface60A and the center-side slipper cam surface60S, and each of the pressure-side cam portions90includes the pressure-side assist cam surface90A and the pressure-side slipper cam surface90S. In this configuration, contact between the surfaces90F of the pressure-side cam portions90and the surfaces60F of the center-side cam portions60can be easily eliminated, and thus, effects of the center-side assist cam surface60A and the pressure-side assist cam surface90A can be appropriately exerted so that a force in the first direction D1is generated in the pressure plate70. In addition, effects of the center-side slipper cam surface60S and the pressure-side slipper cam surface90S are appropriately exerted so that the pressure plate70can thereby move in the second direction D2. Second Preferred Embodiment In the preferred embodiment described above, the bosses84are located on the pressure plate70, and the through holes54H are located in the spring housing portions54of the clutch center40. However, the present disclosure is not limited to this example. For example, as illustrated inFIG.9A, the through holes54H may be located in the spring housing portions54of the pressure plate70with the bosses84located on the clutch center40. In this case, the clutch center40is located between the clutch using30and the pressure plate70. As illustrated inFIG.9A, the pressure plate70includes the spring housing portions54. The spring housing portions54are located in the body72including the pressure-side cam portions90. The spring housing portions54are recessed in the first direction D1from the back surface72R of the body72. The back surface72R of the body72is an example of the surface of the body72on the side of the second direction D2. The spring housing portions54are arranged at regular or substantially regular intervals in the circumferential directions S of the pressure plate70. The spring housing portions54include the through holes54H which penetrate the spring housing portions54and in which the bosses84are inserted. As illustrated inFIG.9A, the clutch center40includes the plurality of (for example, three in this preferred embodiment) bosses84. The bosses84support the pressure plate70. The bosses84are arranged at regular or substantially regular intervals in the circumferential directions S. The bosses84extend in the directions D. The bosses84are disposed on the base wall43of the body42. The bosses84are located between the center-side assist cam surface60A and the center-side slipper cam surface60S with respect to the circumferential directions S. The bosses84extend from the surface43A of the base wall43toward the pressure plate70(i.e., in the second direction D2). As illustrated inFIG.9A, in the combined state, distal ends184T of the bosses84project outward from the through holes54H. The distal ends184T of the bosses84are ends of the bosses84on the side of the second direction D2. As illustrated inFIG.9B, while the surfaces90F of the pressure-side cam portions90and surfaces60F of the center-side cam portions60are in contact (e.g., surface contact) with each other (i.e., in the state where the pressure plate70rides on the clutch center40), the distal ends184T of the bosses84project outward from the through holes54H. More specifically, while the surfaces90F of the pressure-side cam portions90and the surfaces60F of the center-side cam portions60are in contact with each other, the distal ends184T of the bosses84project outward from the back surface72R of the body72of the pressure plate70. While the surfaces90F of the pressure-side cam portions90and the surfaces60F of the center-side cam portions60are in contact with each other, the distal ends184T of the bosses84are located ahead of the back surface72R in the second direction D2. Thus, in combining the clutch center40and the pressure plate70, for example, even if the surfaces90F of the pressure-side cam portions90and the surfaces60F of the center-side cam portions60contact each other, the bosses84projecting outward from the through holes54H can be held. Rotation of the pressure plate70in the circumferential directions S with the bosses84held, for example, can cancel the state where the pressure plate70rides on the clutch center40, and the positional relationship among the pressure-side assist cam surface90A, the center-side assist cam surface60A, the pressure-side slipper cam surface90S, and the center-side slipper cam surface60S can be corrected. In the clutch device10according to this preferred embodiment, the pressure plate70includes the body72including the pressure-side cam portions90, and the spring housing portions54recessed in the first direction D1from the back surface72R of the body72and housing the pressure springs25that bias the pressure plate70in the first direction D1, the bosses84are formed on the clutch center40, the through holes54H are located in the spring housing portions54of the pressure plate70, and the distal ends184T of the bosses84are located ahead of the back surface72R of the body72in the second direction D2while the surfaces90F of the pressure-side cam portions90and the surfaces60F of the center-side cam portions60are in contact with each other. In this configuration, even when the pressure plate70rides on the clutch center40, the bosses84located on the clutch center40project outward from the through holes54H located in the spring housing portions54. At this time, the distal ends184T of the bosses84are located ahead of the back surface72R of the body72in the second direction D2. Accordingly, the bosses84can be easily held. In the preferred embodiments described above, the through holes54H are located in the spring housing portions54. However, the present disclosure is not limited to this example. The through holes54H may penetrate the base wall43of the clutch center40, or may penetrate the pressure-side cam portions90of the pressure plate70. In the preferred embodiments described above, the output shaft holding portion50of the clutch center40and the spline fitting portion46located on the outer peripheral wall45are integrally formed, but may be separate structural members. That is, the clutch center40may include a first clutch member including the output shaft holding portion50and a second clutch member formed as a separate structural member from the first clutch member and including the spline fitting portion46and use the first clutch member and the second clutch member in combination. Third Preferred Embodiment FIG.10is a disassembled perspective view of a clutch center240and a pressure plate270of a clutch device210according to a third preferred embodiment. The clutch center240is housed in a clutch housing30(seeFIG.1). The clutch center240and the clutch housing30are concentrically disposed. As illustrated inFIG.10, the clutch center240includes a body242, and a flange268connected to an outer edge of the body242on the side of a first direction D1and extending radially outward. The body242projects from the flange268in a second direction D2. The clutch center240does not hold output-side rotating plates22. The clutch center240is rotationally driven together with an output shaft15(seeFIG.1). As illustrated inFIG.10, the body242includes an output shaft holding portion250, a plurality of center-side cam portions60, and a center-side fitting portion258. The center-side cam portions60project from the flange268in the second direction D2. The center-side cam portions60are located radially outward of the output shaft holding portion250. The output shaft holding portion250has a cylindrical shape. The output shaft holding portion250has an insertion hole251in which the output shaft15(seeFIG.1) is inserted and spline-fitted. The insertion hole251penetrates the body242. An inner peripheral surface250A of the output shaft holding portion250defining the insertion hole251has a plurality of spline grooves along the axial direction. The output shaft15is coupled to the output shaft holding portion250. As illustrated inFIG.10, the clutch center240includes a plurality of (for example, three in this preferred embodiment) bosses84. The bosses84are located radially outward of the output shaft holding portion250. The bosses84are disposed on the body242. As illustrated inFIG.10, the clutch center240includes center-side cam holes243H penetrating the body242and a portion of the flange268. The center-side cam holes243H penetrate the body242and the flange268in directions D. The center-side cam holes243H extend from portions on the side of the output shaft holding portion250to the flange268. The center-side cam holes243H are located between the center-side assist cam surfaces60A of the center-side cam portions60and the bosses84. When seen in the axial direction of the clutch center240, the center-side assist cam surfaces60A overlap with a portion of the center-side cam holes243H. As illustrated inFIG.10, the center-side fitting portion258is disposed on the body242. The center-side fitting portion258is located radially outward of the center-side cam portions60. The center-side fitting portion258is located ahead of the center-side cam portions60in the first direction D1. The center-side fitting portion258is configured to slidably fit in the pressure-side fitting portion288(seeFIG.11). The pressure plate270is movable toward or away from the clutch center240and rotatable relative to the clutch center240. The pressure plate270is configured to press the input-side rotating plates20and the output-side rotating plates22. The pressure plate270is disposed coaxially with the clutch center240and the clutch housing30. The pressure plate270includes a cylindrical body272, and a flange298extending radially outward from the outer edge of the body272. The pressure plate270holds the plurality of output-side rotating plates22alternately arranged with the input-side rotating plates20in the directions D. As illustrated inFIG.11, the body272includes a ring-shaped base wall273, an outer peripheral wall275located radially outward of the base wall273and extending in the first direction D1, a cylindrical portion280disposed at the center of the base wall273, a plurality of pressure-side cam portions90connected to the base wall273and the outer peripheral wall275, a pressure-side fitting portion288, and spring housing portions54(seeFIG.10). The pressure-side cam portions90project from the body272in the first direction D1. The pressure-side cam portions90are located radially outward of the cylindrical portion280. The pressure-side cam portions90are located radially inward of the outer peripheral wall275. The cylindrical portion280has a cylindrical shape. The cylindrical portion280is formed integrally with the pressure-side cam portions90. The cylindrical portion280receives clutch oil that has flowed out from the distal end15T of the output shaft15. As illustrated inFIG.11, the outer peripheral wall275of the pressure plate270is located radially outward of the cylindrical portion280. The outer peripheral wall275has a ring shape extending in the directions D. An outer peripheral surface275A of the outer peripheral wall275has a spline fitting portion276. The spline fitting portion276includes a plurality of pressure-side fitting teeth277extending in the axial direction of the pressure plate270along the outer peripheral surface275A of the outer peripheral wall275, a plurality of spline grooves278each located between adjacent ones of the pressure-side fitting teeth277and extending in the axial direction of the pressure plate270, and oil flow holes279. The pressure-side fitting teeth277hold the output-side rotating plates22. The plurality of pressure-side fitting teeth277are arranged in the circumferential directions S. The plurality of pressure-side fitting teeth277are arranged at regular or substantially regular intervals in the circumferential directions S. The plurality of pressure-side fitting teeth277have the same or substantially the same shape. The pressure-side fitting teeth277project radially outward from the outer peripheral surface275A of the outer peripheral wall275. The oil flow holes279penetrate the outer peripheral wall275in the radial directions. Each of the oil flow holes279is located between adjacent ones of the pressure-side fitting teeth277. That is, the oil flow holes279are located in the spline grooves278. The oil flow holes279are located at the sides of the pressure-side cam portions90. The oil flow holes279are located at the sides of pressure-side assist cam surfaces90A of the pressure-side cam portions90. The oil flow holes279are located ahead of the pressure-side assist cam surfaces90A in the first circumferential direction S1. The oil flow holes279are located ahead of pressure-side slipper cam surfaces90S in the second circumferential direction S2. In this preferred embodiment, three oil flow holes279are located in each of three portions of the peripheral wall275in the circumferential directions S. The oil flow holes279are arranged at regular or substantially intervals in the circumferential directions S. The oil flow holes279cause the inside and outside of the pressure plate270to communicate with each other. The oil flow holes279allow clutch oil that has flowed out of the output shaft15into the pressure plate270to be discharged to the outside of the pressure plate270. In this preferred embodiment, the oil flow holes279allow clutch oil flowing at an inner peripheral surface275B of the peripheral wall275to be discharged to the outside of the pressure plate270. At least a portion of the oil flow holes279is located at a position facing the center-side fitting portion258(seeFIG.10). The output-side rotating plates22are held by the spline fitting portion276of the pressure plate270. The output-side rotating plates22are held by the pressure-side fitting teeth277and the spline grooves278by spline-fitting. The output-side rotating plates22are displaceable along the axial direction of the pressure plate270. The output-side rotating plates22are rotatable together with the pressure plate270. As illustrated inFIGS.10and11, the pressure plate270includes pressure-side cam holes273H penetrating a portion of the base wall273. The pressure-side cam holes273H penetrate the base wall273in the directions D. The pressure-side cam holes273H are located radially outward of the cylindrical portion80. The pressure-side cam holes273H extend from the sides of the cylindrical portion80to the outer peripheral wall275. Each of the pressure-side cam holes273H penetrates a portion between adjacent ones of the pressure-side cam portions90. Each of the pressure-side cam holes273H penetrates a portion between the pressure-side assist cam surface90A and the pressure-side slipper cam surface90S of adjacent ones of the pressure-side cam portions90. When seen in the axial direction of the pressure plate270, the pressure-side assist cam surfaces90A overlap with a portion of the pressure-side cam holes273H. Clutch oil flows into the pressure-side cam holes273H from the outside of the pressure plate270. As illustrated inFIG.11, the pressure-side fitting portion288is located radially outward of the cylindrical portion280. The pressure-side fitting portion288is located radially outward of the pressure-side cam portions90. The pressure-side fitting portion288is located ahead of the pressure-side cam portions90in the first direction D1. The pressure-side fitting portion288is located on the inner peripheral surface275B of the peripheral wall275. The pressure-side fitting portion288is configured to slidably fit onto the center-side fitting portion258(seeFIG.10). A gap is located between the pressure-side fitting portion288and the center-side fitting portion258. As illustrated inFIG.11, the spring housing portions54are located in the pressure-side cam portions90. The spring housing portions54include the through holes54H which penetrate the spring housing portions54and in which the bosses84(see FIG. are inserted. The through holes54H penetrate the pressure-side cam portions90. In this preferred embodiment, in a manner similar to the example illustrated inFIG.9B, while the surfaces90F of the pressure-side cam portions90(seeFIG.11) and the surfaces60F of the center-side cam portions60(seeFIG.10) are in contact (e.g., surface contact) with each other (i.e., in the state where the pressure plate270rides on the clutch center240), the distal ends184T of the bosses84(seeFIG.10) project outward from the through holes54H. More specifically, while the surfaces90F of the pressure-side cam portions90and the surfaces60F of the center-side cam portions60are in contact with each other, the distal ends184T of the bosses84project outward from the back surface273R of the base wall273of the pressure plate270. In the third preferred embodiment, the bosses84are located on the clutch center240, and the through holes54H are formed in the spring housing portions54of the pressure plate270. However, the present disclosure is not limited to this example. For example, in a manner similar to the first preferred embodiment, the through holes54H may be located in the spring housing portions54of the clutch center240with the bosses84formed on the pressure plate270. The following Clause provides other specific aspects of the technique disclosed herein. Clause 1: A clutch device to allow or interrupt transfer of a rotation driving force of an input shaft to an output shaft, the clutch device including a clutch center housed in a clutch housing holding a plurality of input-side rotating plates rotationally driven by rotational driving of the input shaft, the clutch center holding a plurality of output-side rotating plates and being operable to be rotationally driven together with the output shaft, the input-side rotating plates and the output-side rotating plates being alternately arranged, and a pressure plate movable toward or away from the clutch center and rotatable relative to the clutch center, the pressure plate being operable to press the input-side rotating plates and the output-side rotating plates, wherein the pressure plate includes a pressure-side cam portion including at least one of a pressure-side assist cam surface and a pressure-side slipper cam surface, the pressure-side assist cam surface being operable to generate a force in a direction from the pressure plate toward the clutch center in order to increase a pressing force between the input-side rotating plates and the output-side rotating plates upon rotation relative to the clutch center, the pressure-side slipper cam surface being operable to cause the pressure plate to move away from the clutch center in order to reduce a pressing force between the input-side rotating plates and the output-side rotating plates upon rotation relative to the clutch center, the clutch center includes a center-side cam portion including at least one of a center-side assist cam surface and a center-side slipper cam surface, the center-side assist cam surface being operable to generate a force in a direction from the pressure plate toward the clutch center in order to increase the pressing force between the input-side rotating plates and the output-side rotating plates upon rotation relative to the pressure plate, the center-side slipper cam surface being operable to cause the pressure plate to move away from the clutch center in order to reduce the pressing force between the input-side rotating plates and the output-side rotating plates upon rotation relative to the pressure plate, and assuming directions in which the pressure plate moves are movement directions, a direction in which the pressure plate moves toward the clutch center is a first direction, and a direction in which the pressure plate moves away from the clutch center is a second direction, at least one of the pressure plate and the clutch center includes a boss extending in the movement directions, and the other of the pressure plate and the clutch center includes a through hole which penetrates therethrough along the movement directions and in which the boss is insertable, the through hole extends in circumferential directions and allows movement of the boss along the circumferential directions and the movement directions, and while a surface of the pressure-side cam portion on a side of the first direction and a surface of the center-side cam portion on a side of the second direction are in contact with each other, a distal end of the boss projects outward from the through hole. The foregoing description is directed to the preferred embodiments of the present disclosure. The preferred embodiments described above, however, are merely examples, and the present disclosure can be performed in various modes and through various preferred embodiments. In the preferred embodiments described above, each of the center-side cam portions60includes the center-side assist cam surface60A and the center-side slipper cam surface60S, but only needs to include at least one of the center-side assist cam surface60A or the center-side slipper cam surface60S. In the preferred embodiments described above, each of the pressure-side cam portions90includes the pressure-side assist cam surface90A and the pressure-side slipper cam surface90S, but only needs to include at least one of the pressure-side assist cam surface90A or the pressure-side slipper cam surface90S. In the third preferred embodiment described above, the clutch center240is configured not to hold the output-side rotating plates22, but the present disclosure is not limited to this example. The clutch center240may include center-side fitting teeth having a configuration similar to that of the pressure-side fitting teeth77of the first preferred embodiment capable of holding the output-side rotating plates22. While preferred embodiments of the present invention have been described above, it is to be understood that variations and modifications will be apparent to those skilled in the art without departing from the scope and spirit of the present invention. The scope of the present invention, therefore, is to be determined solely by the following claims. | 58,592 |
11859675 | DETAILED DESCRIPTION OF THE DISCLOSURE Hereinafter, embodiments of the present disclosure will be described with reference to the accompanying drawings. FIG.1is an outline cross-sectional view illustrating a friction engagement device according to one embodiment of the present disclosure. As illustrated inFIG.1, a friction engagement device1according to this embodiment of the present disclosure is constituted as a friction engagement device of an automatic transmission mounted on a vehicle. The friction engagement device1includes a cylindrical drum part2, a cylindrical hub part3which is disposed coaxially inside the drum part2, a plurality of annular friction plates4which are disposed so as to be lined up along an axis21of the drum part2and an axis31of the hub part3, in an inner circumference of the drum part2and an outer circumference of the hub part3, a planetary gear5(illustrated by a broken line) which is disposed inside the hub part3, and a piston6which is disposed inside the drum part2, at a first end side (e.g., left inFIG.1) of the drum part2from the friction plates4and the planetary gear5, and presses the friction plates4with oil pressure by sliding along the axis21of the drum part2and the axis31of the hub part3. The drum part2includes a first drum cylindrical body22awhich is provided around the axis21of the drum part2, a corner part22bwhich is provided at a first end side of the first drum cylindrical body22a,and inclines radially inward as it goes to the first end side of the drum part2, a first drum vertical wall part22cwhich is provided at the first end side of the corner part22b,and extends radially inward, a second drum cylindrical body22dextending on the first end side along the axis21from an inner end part of the first drum vertical wall part22c,an inclined part22ewhich is provided at the first end side of the second drum cylindrical body22d,and inclines radially inward as it goes to the first end side of the drum part2, a second drum vertical wall part22fwhich is provided at the first end side of the inclined part22e,and extends radially inward, and a third drum cylindrical body22gwhich extends on the first end side along the axis21from an inner end part of the second drum vertical wall part22f. The drum part2is provided with a first inner drum cylindrical body23awhich extends towards a second end side (e.g., right inFIG.1) along the axis21of the drum part2, between the inclined part22eand the second drum vertical wall part22f. Further, the drum part2is provided with a second inner drum cylindrical body23bwhich extends toward the second end side along the axis21from a second end side of the third drum cylindrical body22g.A thrust bearing8is disposed at the second end side of the second inner drum cylindrical body23b.The thrust bearing8contacts the second end side of the second inner drum cylindrical body23band a first end side of the planetary gear5to permit a relative rotation between the drum part2and the planetary gear5. In an inner circumference of the first drum cylindrical body22aof the drum part2, a plurality of spline parts25are formed by being depressed radially outward. The spline parts25have serrations24extending along the axis21of the drum part2, and the serrations24are formed at equal intervals in the circumferential direction. Further, in the inner circumference of the first drum cylindrical body22aof the drum part2, a plurality of annular drum-side friction plates41are disposed so as to be lined up along the axis21of the drum part2. In an outer circumference of the drum-side friction plates41, a plurality of drum-side tooth parts42which project radially outward are provided at equal intervals in the circumferential direction. The drum-side tooth parts42spline-fit into the serrations24of the spline parts25formed in the inner circumference of the first drum cylindrical body22aof the drum part2. In the outer circumference of the hub part3, a plurality of spline parts33are provided at equal intervals in the circumferential direction. The spline parts33have serrations32which are depressed radially inward and extend along the axis31of the hub part3. Further, a plurality of annular hub-side friction plates43are provided on the outer circumference of the hub part3, so as to be lined up along the axis31of the hub part3. In an inner circumference of the hub-side friction plate43, a plurality of hub-side tooth parts44are provided. The hub-side tooth parts44which project radially inward are provided at equal intervals in the circumferential direction. The hub-side tooth parts44spline-fit into the serrations32of the spline part33formed in the outer circumference of the hub part3. The cylindrical piston6fits into a space formed between the second drum vertical wall part22f,the first inner drum cylindrical body23aand the second inner drum cylindrical body23bof the drum part2, and the planetary gear5. An axis61of the piston6extends coaxially with the axis21of the drum part2and the axis31of the hub part3. The piston6includes an annular snap ring62attached to an outer circumference of the second inner drum cylindrical body23b,a cylindrical spring retainer63attached to the outer circumference of the second inner drum cylindrical body23bso as to contact a first end side of the snap ring62, a cylindrical piston part64attached to the outer circumference of the second inner drum cylindrical body23bbetween the spring retainer63and the second drum vertical wall part22fso as to be slidable along the axis61, and a return spring65disposed between the spring retainer63and the piston part64so as to bias the piston part64to the first end side along the axis61. The spring retainer63is provided on a first end side of the spring retainer63with a spring retainer recess63awhich is depressed toward the second end side. A centrifugal balance hydraulic chamber66is formed in a space between the spring retainer recess63aand the piston part64. On the second end side of the piston part64, the piston part64includes a piston recess64awhich is depressed toward the first end side, a piston cylindrical body64bprovided in an outer circumference of the piston part64, a piston outer inclined part64cwhich extends in an outer circumference of the piston cylindrical body64bso as to incline radially inward as it goes toward first end side, and a piston pressing part64dwhich extends at the second end of the piston outer inclined part64ctoward the second end side so as to press the drum-side friction plate41of the drum part2along the axis21of the drum part2. Further, the piston part64is slidable along the axis61in a state where the outer circumference of the piston cylindrical body64bfits into an inner circumference of the first inner drum cylindrical body23aof the drum part2, and an inner circumference of the piston cylindrical body64bfits onto an outer circumference of the spring retainer63. The piston part64is provided at the first end side of the piston part64with a piston inner inclined part64ewhich inclines radially inward as it goes toward the second end side. A hydraulic chamber67is formed in a space between the piston inner inclined part64eand the second drum vertical wall part22f. In the second inner drum cylindrical body23b,a centrifugal balance oiling hole66awhich extends radially toward the centrifugal balance hydraulic chamber66, and an oiling hole67awhich extends radially toward the hydraulic chamber67are formed. Between an inner circumference of the piston part64and the outer circumference of the second inner drum cylindrical body23bof the drum part2, between the inner circumference of the piston cylindrical body64band the outer circumference of the spring retainer63, and between the outer circumference of the piston cylindrical body64band the inner circumference of the first inner drum cylindrical body23a,an annular oil seal (inFIG.1, it is illustrated in a rectangular shape) is provided. Into the drum part2, lubricating oil is supplied from radially inward of the second inner drum cylindrical body23b.Further, also to the centrifugal balance hydraulic chamber66and the hydraulic chamber67of the piston6, the lubricating oil is supplied from the centrifugal balance oiling hole66aand the oiling hole67a,respectively. By supplying the lubricating oil from the oiling hole67aformed in the second inner drum cylindrical body23bof the drum part2toward the hydraulic chamber67of the piston6, the piston part64of the piston6compresses the return spring65disposed on the second end side of the piston part64toward the second end side, and slides toward the second end side along the axis61. Therefore, since the piston pressing part64dof the piston part64presses the drum-side friction plates41of the drum part2toward the second end side along the axis21of the drum part2, the drum-side friction plate41and the hub-side friction plate43of the hub part3engage with each other. On the other hand, by discharging the lubricating oil from the hydraulic chamber67of the piston6via the oiling hole67aformed in the second inner drum cylindrical body23bof the drum part2, the return spring65of the compressed piston6expands toward the first end side, and slides the piston part64of the piston6toward the first end side along the axis61. Therefore, since the piston pressing part64dof the piston part64moves toward the first end side along the axis21of the drum part2so as to separate from the drum-side friction plate41of the drum part2, the engagement between the drum-side friction plate41and the hub-side friction plate43of the hub part3is canceled. When the lubricating oil is discharged from the hydraulic chamber67of the piston6via the oiling hole67aformed in the second inner drum cylindrical body23bof the drum part2, part of the lubricating oil may remain inside the hydraulic chamber67. At this time, when the vehicle is operated, the piston6of the friction engagement device1rotates to cause a centrifugal force of the lubricating oil which remains inside the hydraulic chamber67. With this centrifugal force, although the lubricating oil is discharged from the hydraulic chamber67, the piston part64of the piston6may slide toward the second end side along the axis61, and the piston pressing part64dof the piston part64may press the drum-side friction plate41of the drum part2toward the second end side along the axis21of the drum part2. Therefore, the piston6is constructed so that, when the lubricating oil is discharged from the hydraulic chamber67, the lubricating oil is supplied from the centrifugal balance oiling hole66aformed in the second inner drum cylindrical body23bof the drum part2toward the centrifugal balance hydraulic chamber66of the piston6so as to balance the oil pressure of the hydraulic chamber67, the oil pressure of the centrifugal balance hydraulic chamber66, and the restoring force of the return spring65. FIG.2is an outline front view of the drum part2of the friction engagement device1ofFIG.1. A plurality of oil galleries26are formed in the outside of the corner part22bprovided between the first drum cylindrical body22aand the first drum vertical wall part22cof the drum part2. The oil galleries26are depressed radially outward and formed in the inner circumference of the first drum cylindrical body22aat equal intervals so as to correspond to the circumferential positions of the plurality of spline parts25having the serrations24extending along the axis21of the drum part2. Particularly, in this embodiment, the oil galleries26are formed with intervals in the circumferential direction so as to skip every other spline part25. FIG.3is an outline cross-sectional view of the drum part2, taken along a line ofFIG.2. Inside the corner part22bprovided between the first drum cylindrical body22aand the first drum vertical wall part22cof the drum part2, a drum recess27is formed so that it is connected to the serration24of the spline part25formed in the inner circumference of the first drum cylindrical body22a,and is depressed toward the first end side along the axis21of the drum part2. The drum recess27is connected to the oil gallery26formed outside the corner part22b. In the serration24of the spline part25formed in the inner circumference of the first drum cylindrical body22a,serration side surfaces24awhich are depressed radially outward along the serration24and extend along the axis21of the drum part2are formed. The serration side surface24aextends toward the first end side along the axis21so as to be connected to the drum recess27formed inside the corner part22b. Returning toFIG.2, since the oil gallery26is formed along the serration side surface24awhen seen from the axis21of the drum part2, it can be seen in a semicircular shape. Returning toFIG.1, in the piston outer inclined part64cof the piston part64of the piston6disposed inside the first drum cylindrical body22aof the drum part2, a lubricating oil discharge hole68extending along the axis61of the piston6is formed so as to pass through the inside and the outside of the piston outer inclined part64c. By discharging the lubricating oil from the hydraulic chamber67of the piston6via the oiling hole67aformed in the second inner drum cylindrical body23bof the drum part2, when the piston part64of the piston6slides toward the first end side along the axis61to cancel the engagement between the drum-side friction plate41and the hub-side friction plate43of the hub part3which are pressed by the piston pressing part64dof the piston part64, the lubricating oil which remains inside the piston outer inclined part64ccan be discharged outside the piston outer inclined part64cvia the lubricating oil discharge hole68formed in the piston outer inclined part64cof the piston6, and can further be discharged outside from the oil gallery26connected to the drum recess27. Further, by the oil gallery26formed along the serration side surface24aof the serration24of the spline part25formed in the drum part2, the lubricating oil which remains between the serration24and the drum-side friction plate41which spline-fits into the serration24can be smoothly discharged outside from the oil gallery26connected to the serration24via the drum recess27. FIG.4is an outline cross-sectional view of the drum part2, taken along a line IV-IV ofFIG.2. Particularly,FIG.4illustrates a cross section between two adjacent spline parts25formed in the inner circumference of the first drum cylindrical body22a.The thickness radially outward of the first drum cylindrical body22awhere the spline part25is not formed as illustrated inFIG.4, is larger than the thickness thereof where the spline part25is formed as illustrated inFIG.3. FIG.5is an outline cross-sectional view of the drum part2, taken along a line V-V ofFIG.2. Particularly,FIG.5illustrates a cross section of another spline part25awhich is adjacent to the spline part25connected to the oil gallery26formed in the inner circumference of the first drum cylindrical body22a.In another spline part25aofFIG.5, the drum recess connected to the serration side surface24aof serration24of the spline part25illustrated inFIG.3, and the oil gallery connected to the drum recess are not formed. FIG.6is a view illustrating a method of forming the oil gallery26of the corner part22bof the drum part2ofFIG.2. In the forming method illustrated inFIG.6, first, on the outside of the corner part22b, the drum part2is formed by die casting so that a press-out part28which projects outside in a direction perpendicular to the surface of the corner part22bis formed at a position corresponding to the drum recess27of the drum part2. As illustrated, the press-out part28is provided, outside the corner part22b,radially outward of a scheduled cutting line28aillustrated by a broken line. The second end side of the first drum cylindrical body22aof the drum part2is fixed to a fixture102which is rotated by a motor101with respect to the drum part2which is a die-cast article. A cutting tool103for lathe turning which extends in the radial direction of the drum part2is disposed radially outward of the drum part2so that it opposes to the outer surface of the press-out part28. This cutting tool103is connected to a tool moving mechanism104which moves the cutting tool103along the axis21of the drum part2and in the radial direction of the drum part2. The motor101and the tool moving mechanism104are electrically connected to a controller105disposed externally to control the drive of the motor101and the tool moving mechanism104. In the drum part2disposed as described above, when the oil gallery26is fabricated outside the corner part22bof the drum part2, the motor101rotates based on an electric signal transmitted from the controller105. Here, the drum part2fixed to the fixture102via the first drum cylindrical body22arotates on the axis21together with the fixture102which is rotated by the motor101. Next, when the tool moving mechanism104operates based on the electric signal transmitted from the controller105, the cutting tool103moves to the second end side along the axis21of the drum part2, and moves radially inward of the drum part2, toward the press-out part28provided to the corner part22bof the drum part2. The cutting tool103which is moved by the tool moving mechanism104is pressed against the press-out part28provided to the corner part22bof the drum part2which rotates on the axis21. The cutting tool103pressed against the press-out part28cuts by turning the drum part2so that a cut part29connected to the drum recess27is formed in the circumferential direction of the drum part2, by cutting the press-out part28of the drum part2which is die-cast (i.e., a part radially outward of the scheduled cutting line28aillustrated by the broken line). By forming the cut part29connected to the drum recess27, the drum recess27is opened to the outside, and the oil gallery26connected to the drum recess27is formed. Thus, in the friction engagement device1according to this embodiment, outside the corner part22bprovided between the first drum cylindrical body22aand the first drum vertical wall part22c,the cut part29cut in the circumferential direction of the drum part2is provided so as to be connected to the drum recess27which is provided inside the corner part22bso as to be connected to the serration24of the spline part25formed in the drum part2, and is depressed on the first end side along the axis21of the drum part2. According to the cut part29, the drum recess27is opened outside to form the oil gallery26connected to the drum recess27. In the friction engagement device1, the oil gallery26is formed by die-casting the drum part2, and cutting by turning the outside of the corner part22bof the drum part2in the circumferential direction, without adjusting each machining position. Therefore, the friction engagement device1provided with the drum part2in which the oil gallery26is formed is short in the machining time, and its productivity improves. Further, the lubricating oil discharge hole68formed in the piston outer inclined part64cof the piston6disposed between the first drum vertical wall part22cinside the drum part2and the friction plates4extends along the axis21of the drum part2. Thus, when the piston6presses the drum-side friction plates41of the friction plates4, the lubricating oil which remains inside the piston6is discharged outside the piston6through the lubricating oil discharge hole68. Therefore, the centrifugal force due to the lubricating oil can be suppressed from acting on the piston6. Further, since the oil gallery26is formed along the serration side surface24aof the spline part25formed in the drum part2, the opening area becomes larger, thereby smoothly discharging the lubricating oil which remains between the friction plates4and the serrations24. Further, according to the method of forming the friction engagement device1, by die-casting the drum part, and cutting (turning) in the circumferential direction the press-out part28provided outside the corner part22bof the drum part2, the oil gallery26can be formed, without adjusting each machining position. Therefore, since the method of forming the oil gallery26is short in the machining time, the productivity of the friction engagement device1improves. Although in this embodiment the oil gallery26is formed in the semicircular shape along the serration side surface24a,it may be formed in a triangular shape or a trapezoidal shape along the serration side surface24a. FIG.7is a schematic view of a drum part202of a friction engagement device200according to another embodiment. As illustrated inFIG.7, a plurality of oil galleries290which extend in the radial direction may be formed in an outer circumference of a first drum cylindrical body222aof the drum part202so as to be connected to the serrations of the spline parts formed in an inner circumference of the first drum cylindrical body222a. The present disclosure is not limited to the illustrated embodiments, and various improvements and various design changes may be possible without departing from the spirit of the present disclosure. As described above, according to the present disclosure, since it becomes possible to easily form the plurality of oil galleries, it may be utilized suitably for the manufacturing technology field of vehicles which carry the automatic transmission having the friction engagement device. It should be understood that the embodiments herein are illustrative and not restrictive, since the scope of the invention is defined by the appended claims rather than by the description preceding them, and all changes that fall within metes and bounds of the claims, or equivalence of such metes and bounds thereof, are therefore intended to be embraced by the claims. DESCRIPTION OF REFERENCE CHARACTERS 1Friction Engagement Device2Drum Part22aCylindrical Body (First Drum Cylindrical Body)22bCorner Part22cVertical Wall Part (First Drum Vertical Wall Part)24Serration25Spline Part26Oil Gallery27Drum Recess29Cut Part41Friction Plate (Drum-side Friction Plate)42Tooth Part (Drum-side Tooth Part) | 22,102 |
11859676 | DETAILED DESCRIPTION OF EMBODIMENTS 1. Schematic Configuration of Constant-Velocity Joint A schematic configuration of a constant-velocity joint applied to a manufacturing method according to an embodiment of the present disclosure will be described. The constant-velocity joint may be a variety of joints such as a ball-type joint and a tripod-type joint. Examples of the ball-type joint include a fixed ball-type constant-velocity joint (such as BJ and UFJ) and a sliding ball-type constant-velocity joint (such as DOJ and LJ). The constant-velocity joint includes at least an outside joint member, an inside joint member, and rolling elements. Here, the fixed ball-type constant-velocity joint is taken as an example of the constant-velocity joint. Thus, as illustrated inFIG.1, a constant-velocity joint100includes an outside joint member10, an inside joint member20, a cage30, and six balls40that serve as rolling elements. The constant-velocity joint100is a constant-velocity joint of a joint center fixed type and is mounted on a vehicle. The constant-velocity joint100is suitably used as an outboard joint for a drive shaft. The constituent member of the constant-velocity joint100to be applied to the manufacturing method according to the present embodiment is the outside joint member10. Therefore, the inside joint member20, the cage30, and the balls40are indicated by hidden outlines (long dashed short dashed lines) inFIG.1. The outside joint member10has a cup portion11in a bottomed tubular shape that opens on one side (left side inFIG.1) in the direction of a central axis L1, and a coupling shaft portion12formed integrally with the cup portion11to extend toward the other side (right side inFIG.1) in the direction of the central axis L1. The cup portion11is formed with an outside ball groove portion11bformed in an inner peripheral surface11aof the cup portion11. The inner peripheral surface11ahas a concave spherical shape. The outside ball groove portion11bextends in the direction of the central axis L1. The coupling shaft portion12is formed with a spline portion12a, a screw portion12b, and a engagement groove portion12cfor connection to a different power transfer shaft (not illustrated). The inside joint member20is formed in an annular shape, and formed with an inside ball groove portion20bformed in an outer peripheral surface20aof the inside joint member20. The outer peripheral surface20ahas a convex spherical shape. The inside ball groove portion20bextends in the direction of a central axis L2. The cage30is formed with a plurality of window portions30athat can accommodate and hold one ball40each. The cage30is disposed between the inner peripheral surface11aof the outside joint member10and the outer peripheral surface20aof the inside joint member20. The balls40that are held by the cage30are rollably disposed between the outside ball groove portion11band the inside ball groove portion20b. The inside joint member20is relatively rotated about a joint center O with respect to the outside joint member10while rolling the balls40. That is, the inside joint member20can make an angle (joint angle) with respect to the outside joint member10. The cage30is rotated about the joint center O along with rolling of the balls40. The balls40that are held by the cage30transfer torque between the outside joint member10and the inside joint member20. 2. Characteristics of Manufacture of Outside Joint Member As illustrated inFIG.3, a step of manufacturing the outside joint member10includes: a plastic working and hardening heating step (step P1inFIG.3) in which a material (hereinafter a material that has been processed etc. will also be referred to as the “material”) to form the outside joint member10is heated for plastic working and hardening; a plastic working step (step P2inFIG.3) in which the material is subjected to plastic working; and a hardening cooling step (step P3inFIG.3) in which the material is cooled for hardening. The manufacturing step further includes: a scale removal step (step P4inFIG.3) in which scales of the material are removed; a finish turning step (step P5inFIG.3) in which the material is subjected to finish turning; a paint step (step P6inFIG.3) in which a paint is applied to the material; a drying and tempering heating step (step P7inFIG.3) in which the material is heated for paint drying and tempering; and a tempering cooling step (step P8inFIG.3) in which the material is cooled for tempering. As described in the Summary section, the manufacture of an outside joint member of a constant-velocity joint according to the related art requires the material to form the outside joint member to be subjected to a total of four heating and cooling steps, that is, a heating and cooling step for plastic working, a heating and cooling step for hardening, a heating and cooling step for tempering, and a heating and cooling step for paint drying. In the manufacture of the outside joint member10of the constant-velocity joint100according to the present embodiment, hardening of the material is performed by utilizing heat applied to the material for heating to a working temperature range during plastic working as heat for hardening of the material and by cooling the material after plastic working (steps P1and P3inFIG.3). Further, the material is tempered by utilizing heat applied to the material for heating to a drying temperature range during paint drying as heat for tempering of the material and by cooling the material (steps P7and P8inFIG.3). Consequently, it is only necessary that the material should be subjected to a total of two heating and cooling steps, that is, a heating and cooling step for plastic working and hardening and a heating and cooling step for paint drying and tempering, which can significantly suppress the cost of installation of heating equipment and the cost of energy consumed for heating. The characteristics of the manufacturing step will be described in detail below. The outside joint member10according to the present embodiment is formed from a steel material (S55C) containing 0.40% to 0.60% of carbon, and the material after being hardened (after being cooled) is so hard as not to be easily turnable. Thus, main processing is completed in plastic working steps (four sets), specifically warm forging and warm ironing, which performed in a predetermined working temperature range before cooling. That is, in the warm forging, rough processing of the outer periphery of the cup portion11and the outer periphery of the coupling shaft portion12is completed. In the warm ironing, finishing of the inner peripheral surface11aof the cup portion11and the spline portion12aof the coupling shaft portion12and rough processing of the outside ball groove portion11bare completed. While the spline portion12ais formed through rough turning and form rolling in the related art, a rough turning step and a form rolling step can be omitted in the present embodiment. The material is hardened by cooling the material immediately after the plastic working in the predetermined working temperature range described above is completed. If a hardening cooling start temperature (temperature immediately after the plastic working is completed) Te is too low, the hardening temperature may be insufficient. Further, it is necessary to avoid a transformation (a phenomenon in which the crystal structure is varied) of the steel material. From the above, the hardening cooling start temperature (temperature immediately after the plastic working is completed) Te is set to be at least equal to or higher than 727° C., which is the transformation point (A1point) of the steel material (equal to or higher than the transformation point), preferably a temperature that is equal to or higher than the A3line in the Fe—C binary equilibrium diagram. In the present example, the hardening cooling start temperature Te is set to 870° C. The hardening is through hardening in which water or oil is sprayed to the material that has been entirely heated to rapidly cool the material. Since the entire material is hardened, the strength of the material is improved better than the induction hardening process according to the related art in which the surface of the material is hardened. Hence, the functionality is improved when the outside joint members10of the same dimensions are formed, and a weight reduction is achieved when the outside joint members10of the same strength are formed. On the other hand, a plastic working temperature becomes gradually lower in the plastic working step (particularly, heat is generated through deformation during each set, and cooled by air between the sets) from a plastic working start temperature Ts at the start of plastic working that uses heat applied before the plastic working (heat applied for hardening). Hence, it is necessary for the plastic working start temperature Ts that the hardening cooling start temperature Te should be secured after the plastic working time (in the present example, 40 sec.) elapses. It should be noted, however, that the organization may be coarsened if the temperature is too high. From the above, in the present example, the plastic working start temperature Ts is set to 900° C. or higher and 1050° C. or lower, preferably 950° C. or higher and 990° C. or lower. It is occasionally necessary to shorten the plastic working time in order to secure the temperature range in the plastic working step described above, depending on the size of the material etc. If heating before plastic working (heating for hardening) is performed in an air atmosphere, surface decarburization in which carbon is removed from the surface of the material is caused. In the related art, a surface decarburized layer of the material is removed through rough turning after plastic working. In the warm forging according to the present embodiment, however, rough processing of the outer periphery of the cup portion11and the outer periphery of the coupling shaft portion12is performed, and thus no rough turning is necessary. Therefore, there is no chance to remove the surface decarburized layer from the material, and a forged skin due to the warm forging remains, as it is, as the product skin in the outside joint member10. Thus, heating before plastic working is performed in a nitrogen gas atmosphere (inert gas atmosphere) to prevent surface decarburization of the material. Besides the nitrogen gas, an argon gas etc. may also be used as long as an inert gas. In addition, scales adhere to the surface of the material because of oxidation during hardening of the material. Thus, the scales of the material are removed through shot blasting (that uses alumina particles etc.), shot peening, barrel processing, wet blasting, etc. immediately after the hardening. In addition, as described above, the outer periphery of the cup portion11and the outer periphery of the coupling shaft portion12are subjected to rough processing in the warm forging, and the outside ball groove portion11band an inside spherical surface portion11c(seeFIG.1) are subjected to rough processing in the warm ironing. Hence, finish turning is performed on such rough processed portions. Further, the screw portion12band the engagement groove portion12cof the coupling shaft portion12are also processed in the finish turning. While the screw portion12bis formed through form rolling in the related art, a form rolling step can be omitted in the present embodiment. In addition, the hardness of the material after tempering is lowered by about 50 Hv. Therefore, it is necessary that a tempering start temperature (paint drying start temperature) Tss for maintaining a predetermined hardness should be equal to or higher than 100° C. The paint that is used in the present embodiment is a water-soluble, highly rust-proof paint, and contains an epoxy resin material as a paint component. Therefore, the paint is burned to be powdery at a temperature exceeding 200° C. Meanwhile, an unpainted portion is oxidized to turn into a dark reddish-brown metal surface color at a temperature exceeding 200° C. From the above, the tempering start temperature (paint drying start temperature) Tss is set to be equal to or higher than 150° C. and equal to or lower than 200° C. 3. Method of Manufacturing Constituent Member of Constant-Velocity Joint Next, a method of manufacturing the outside joint member10of the constant-velocity joint100according to the embodiment of the present disclosure will be described with reference to the drawings. As described above, the method of manufacturing the outside joint member10includes heating a material for plastic working and hardening, and cooling the material for the hardening. The method further includes heating the material for paint drying and tempering, and cooling the material for the tempering. It should be noted, however, that different manufacturing methods are also conceivable, such as a manufacturing method that includes heating a material for plastic working and hardening but does not include heating the material for paint drying and tempering, and a manufacturing method that includes heating a material for paint drying and tempering but does not include heating the material for plastic working and hardening. With such methods, it is also possible to decrease the number of heating and cooling steps, which can significantly suppress the cost of installation of heating equipment and the cost of energy consumed for heating. Such methods will be sequentially described below. First of all, a first manufacturing method will be described. In the first manufacturing method, first, a material to form the outside joint member10is caused to pass through a forging Billet heater filled with a nitrogen gas, and heated until the temperature of the material reaches the plastic working start temperature (step S1inFIG.2; P1inFIG.3; plastic working and hardening heating step). Then, the material that has been heated is set to a pressing machine to perform rough processing of the outer periphery of the cup portion11and the outer periphery of the coupling shaft portion12through warm forging that is plastic working, and perform finishing of the inner peripheral surface11aof the cup portion and the spline portion12aof the coupling shaft portion12and rough processing of the outside ball groove portion11band the inside spherical surface portion11cthrough warm ironing that is plastic working (step S2inFIG.2; P2inFIG.3; plastic working step). Subsequently, water or oil is sprayed to the material that has been subjected to plastic working to rapidly cool the material to harden the material (step S3inFIG.2; P3inFIG.3; hardening cooling step). When the temperature of the material is lowered to room temperature (step S4inFIG.2; P3inFIG.3; hardening cooling step), scales of the material are removed (step S5inFIG.2; P4inFIG.3; scale removal step). Then, the material, from which scales have been removed, is set to a turning device to be subjected to finish turning of the outer periphery of the cup portion11, the outer periphery of the coupling shaft portion12, the outside ball groove portion11b, and the inside spherical surface portion11cand finish turning of the screw portion12band the engagement groove portion12cof the coupling shaft portion12(step S6inFIG.2; P5inFIG.3; finish turning step). Next, the material that has been subjected to turning is caused to pass through a painting machine to be painted (step S7inFIG.2; P6inFIG.3; paint step). Subsequently, the material is caused to pass through a drying machine to heat the material until the temperature of the material reaches the tempering start temperature and dry the paint of the material (step S8inFIG.2; P7inFIG.3; drying and tempering heating step). Then, when the paint of the material is dried and a predetermined tempering time has elapsed since the temperature of the material reaches the tempering start temperature (step S9inFIG.2; P7inFIG.3; drying and tempering heating step), the material is taken out of the drying machine to be cooled (step S10inFIG.2; P8inFIG.3; tempering cooling step), finishing all the processes. The first manufacturing method includes heating a material for plastic working and hardening, and cooling the material for the hardening. The method further includes heating the material for paint drying and tempering, and cooling the material for the tempering. Consequently, it is only necessary that the material should be subjected to a total of two heating and cooling steps, that is, a heating and cooling step for plastic working and hardening and a heating and cooling step for paint drying and tempering, which can significantly suppress the cost of installation of heating equipment and the cost of energy consumed for heating. Next, a second manufacturing method will be described. The second manufacturing method is the same as the first manufacturing method in the plastic working and hardening heating step, the plastic working step, the hardening cooling step, and the scale removal step (steps S11to S15inFIG.4; P1to P4inFIG.5). Then, the material, from which scales have been removed, is caused to pass through a heating furnace to be heated until the temperature of the material reaches the tempering start temperature (step S16inFIG.4; P71inFIG.5; tempering heating step). Then, when a predetermined tempering time has elapsed since the temperature of the material reaches the tempering start temperature (step S17inFIG.4; P71inFIG.5; tempering heating step), the material is taken out of the heating furnace to be cooled (step S18inFIG.4; P81inFIG.5; tempering cooling step). Then, the material that has been cooled is set to a turning device to be subjected to finish turning of the outer periphery of the cup portion11, the outer periphery of the coupling shaft portion12, the outside ball groove portion11b, and the inside spherical surface portion11cand finish turning of the screw portion12band the engagement groove portion12cof the coupling shaft portion12(step S19inFIG.4; P5inFIG.5; finish turning step). At this time, finish turning can be performed easily since the material has been tempered and the hardness thereof has been lowered. Then, the material that has been subjected to turning is caused to pass through a painting machine to be painted (step S20inFIG.4; P6inFIG.5; paint step). Subsequently, the material is caused to pass through a drying machine to dry the paint (step S21inFIG.4; P72inFIG.5; drying step), and the material is taken out of the drying machine to be cooled (step S22inFIG.4; P82inFIG.5), finishing all the processes. The second manufacturing method includes heating a material for plastic working and hardening, and cooling the material for the hardening. Consequently, it is only necessary that the material should be subjected to a total of three heating and cooling steps, that is, a heating and cooling step for plastic working and hardening, a heating and cooling step for paint drying, and a heating and cooling step for tempering, which can significantly suppress the cost of installation of heating equipment and the cost of energy consumed for heating. Next, a third manufacturing method will be described. The third manufacturing method is the same as the first manufacturing method in the plastic working and hardening heating step, the plastic working step, the hardening cooling step, the scale removal step, the finish turning step, and the paint step (steps S31to S37inFIG.6; P1to P6inFIG.7). Then, the material that has been painted is caused to pass through a drying machine to dry the paint (step S38inFIG.6; P72inFIG.7; drying step), and the material is taken out of the drying machine to be cooled (step S39inFIG.6; P82inFIG.7). Then, the material that has been cooled is caused to pass through a heating furnace to be heated until the temperature of the material reaches the tempering start temperature (step S40inFIG.6; P71inFIG.7; tempering heating step). Then, when a predetermined tempering time has elapsed since the temperature of the material reaches the tempering start temperature (step S41inFIG.6; P71inFIG.7; tempering heating step), the material is taken out of the heating furnace to be cooled (step S42inFIG.6; P81inFIG.7; tempering cooling step), finishing all the processes. The third manufacturing method includes heating a material for plastic working and hardening, and cooling the material for the hardening. Consequently, it is only necessary that the material should be subjected to a total of three heating and cooling steps, that is, a heating and cooling step for plastic working and hardening, a heating and cooling step for paint drying, and a heating and cooling step for tempering, which can significantly suppress the cost of installation of heating equipment and the cost of energy consumed for heating. Next, a fourth manufacturing method will be described. The fourth manufacturing method does not include heating for hardening, but includes heating for plastic working and cooling after the plastic working (steps S51to S53inFIG.8; P11, P21, and P31inFIG.9; plastic working heating step, plastic working step, plastic working cooling step). Then, the material that has been cooled to room temperature is caused to pass through a heating furnace to be heated until the temperature of the material reaches the hardening start temperature (step S54inFIG.8; P12and P22inFIG.9; hardening heating step). When the temperature of the material reaches the hardening start temperature, water or oil is sprayed to the material to rapidly cool the material to harden the material (step S55inFIG.8; P32inFIG.9; hardening cooling step). Then, after the temperature of the material is lowered to room temperature (step S56inFIG.8; P32inFIG.9; hardening cooling step), the scale removal step, the finish turning step, the paint step, the drying and tempering heating step, and the tempering cooling step of the first manufacturing method are performed (steps S57to S62inFIG.8; P4to P8inFIG.9), finishing all the processes. The fourth manufacturing method includes heating a material for paint (e.g. water-soluble paint) drying and tempering, and cooling the material for the tempering. Consequently, it is only necessary that the material should be subjected to a total of three heating and cooling steps, that is, a heating and cooling step for plastic working, a heating and cooling step for hardening, and a heating and cooling step for paint drying and tempering, which can significantly suppress the cost of installation of heating equipment and the cost of energy consumed for heating. 4. Others The method of manufacturing the outside joint member10of the constant-velocity joint100according to the embodiment described above is described as including removing scales of the material and finish turning. However, one or both of the scale removal step and the finish turning step may not be included in the case where no scales adhere to the material during hardening of the material or in the case where a high working precision can be obtained with plastic working. The outside joint member10is described as an example of a constituent member of the constant-velocity joint100. However, the present disclosure is also applicable to other constituent members. In the case where the material is deformed or distorted in the hardening step, hardening may be performed with the material restrained in a die etc. in order to suppress deformation or distortion of the material. In order to remove deformation or distortion of the material due to the hardening step, the material may be corrected by a pressing machine etc. after the hardening step. | 23,760 |
11859677 | DETAILED DESCRIPTION The cage freewheel1which is shown inFIG.1comprises an annular cage2(cage ring) with clamping bodies3which are inserted pivotably therein in a manner known per se. The clamping bodies3have a slot4centrally, into which an annular spring5, for instance a spiral spring, is inserted around the entire circumferential surface of the clamping body row, which annular spring5loads the clamping bodies3in the coupling direction. The cage freewheel serves for installation into the annular gap between a shaft component and a hub component, the inner circumferential surface of the hub component and the outer circumferential surface of the shaft component being configured in each case as cylindrical raceways for the clamping bodies3. Those edge faces of the clamping bodies3which are oriented toward the inner and outer raceways on shaft components and hub components act as clamping wedges which jam the shaft component with respect to the hub component in one rotational direction, that is to say in the blocking direction of the freewheel, and thus block a relative rotation. In the opposite rotational direction, that is to say in the freewheel direction, the shaft component can be rotated freely in the case of a stationary hub component, for example. The cage freewheel1according to the invention can fundamentally also be inserted, instead of directly between a shaft component and a hub component, between a freewheel inner ring and a freewheel outer ring which are then in each case pressed onto the shaft component and pressed into the hub component, and form the cylindrical raceways for the clamping bodies3. In order to center the shaft component with respect to the hub component in the shaft/hub connection, the cage freewheel1has additional bearing rollers6which are inserted in each case in pairs into corresponding pockets7of the freewheel cage2on both sides of the annular spring5and assume the function of a roller bearing. Four clamping bodies3which follow one another are situated in each case between two roller pairs6, with the result that four times as many clamping bodies as roller pairs are arranged distributed over the circumference. The clamping bodies3of a clamping-body freewheel which are frequently also called clamping pieces are of non-round configuration due to their design, that is to say have a long and a short transverse direction of extent. In their long transverse extent, the clamping bodies3are somewhat wider than the diameter of the bearing rollers6, with the result that, during coupling, they jam in the annular gap which is formed by the outer surface of the shaft part and the inner running surface of the hub part. In the short transverse direction of extent, the clamping bodies3are somewhat narrower than the diameter of the bearing rollers6, with the result that, loaded against the running surfaces of the annular gap in the coupling direction, they slide along on them. The cage2is shown in greater detail inFIG.2. It has two annular edge strips9a,9bwhich form the cage side edges and are connected to one another via webs10which run in the axial direction. Receiving pockets8for the clamping bodies3are configured between the webs10. One pocket pair7for bearing rollers6follows after in each case four pockets8for clamping bodies3. The annular spring5runs over the center web11in the case of the finally assembled cage freewheel. The pockets7are configured in such a way that they receive the bearing rollers6in each case in a positively locking manner. To this end, projections or cams13which protrude in each case lying radially on the inside and lying radially on the outside into the interior of the pockets are arranged on the lateral boundary webs12of the pockets7. The spacing a1of two cams13in the circumferential direction is smaller than the external diameter of a bearing roller6. A rounded contour14which is adapted to the circumferential course of the bearing rollers6is configured between the inner and outer projection13of a boundary web12. The spacing a2in the center between two opposite rounded contours14is selected to be somewhat greater here than the diameter of the bearing rollers6. The cage2is produced from a high-quality plastic material such as, for instance, polyamide or polyetheretherketone (PEEK) which has a certain elastic property. As a result, the bearing rollers6can be pressed from the inside or from the outside into the relevant pockets7during assembly. As a result of the pressure on the bearing rollers6, the associated pocket7is widened by way of elastic deformation of the projections13. After the bearing roller6reaches its central radial position, the deformation eases and the bearing roller6is held in the center of the pocket by way of the projections13and the curved contour14. The bearing roller6is positioned in the axial direction in the pocket7by way of inner surfaces of the edge strip9aand the edge strip9band the central web11. The width of the central web11is greater than the external diameter of the annular spring. This ensures that the bearing rollers do not come into contact with the annular spring during assembly and later during operation. In order to assemble the cage freewheel, the cage2can first of all be fitted with clamping pieces3, by the latter being inserted radially from the outside into the pockets8. The spacing between two webs10in the circumferential direction is dimensioned in such a way that it is greater than the width, oriented in the circumferential direction, of the radially inner side of the clamping bodies3. The radially outer width of the clamping bodies3is greater, however, than the spacing between two boundary webs8, with the result that the clamping bodies3cannot fall inward through their pockets8. Subsequently, the annular spring5is placed around the clamping pieces3, and finally the bearing rollers6can be pressed into their associated pockets7. It is likewise possible that the pockets7are first of all fitted with the bearing rollers6and subsequently the clamping bodies3are inserted into the pockets8and the annular spring5is placed around the outer circumference of the clamping body row. In the case of the finally assembled cage freewheel, the clamping bodies3are therefore held by way of the annular spring5, while the bearing rollers6are held in a positively locking and captive manner in their pockets. The finally assembled cage freewheel can therefore be pushed onto a shaft component in order to establish a freewheel, and can be inserted with the latter into an associated hub component or, conversely, can be pushed into a hub component and a shaft component can subsequently be plugged through. Different modifications of the cage freewheel which is shown in the exemplary embodiment are possible and included within the context of the present invention. Thus, for example, instead of five pairs of bearing rollers, more or fewer bearing roller pairs can also be used. For example, a minimum of three bearing roller pairs can be arranged distributed at a 120° angle around the circumference of the freewheel cage, with the result that more space for further clamping bodies remains. The bearing rollers6of one bearing roller pair can also be connected to one another via a common central axle. In this case, the central web11can be dispensed with, or it can be provided with a corresponding cutout for the common axle of the bearing roller pair6. Additional guide surfaces which delimit the pivoting movement of the clamping bodies can be configured on the axially inner end sides of the edge strips9aand9b. Pins can likewise be provided on the axially inner end faces of the edge strips9a,9b, which pins engage into the corresponding end-side recesses of the clamping bodies and, as a result, define a pivoting axle for the clamping bodies. In this case, the assembly of the clamping bodies can also take place by way of slight pressure and associated elastic deformation of the cage2, until the pins latch into the end-side recesses of the clamping bodies. Corresponding pins on the clamping bodies and recesses for the pins can likewise be provided on the inner end faces of the edge strips9a,9b. Furthermore, it would be possible, however, for the cage to be configured in two parts with, for example, two-part rings which are latched to one another via latching connections in the region of the webs10,12, as disclosed, for example, in DE 20 2017 106205 U1. | 8,469 |
11859678 | DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The preferred embodiments will now be described with reference to the accompanying drawings, wherein like reference numerals designate corresponding or identical elements throughout the various drawings. The drawings are to be viewed in an orientation in which the reference numerals are viewed correctly. An embodiment of the present invention will be described below with reference to the drawings. FIG.9is a side view illustrating an embodiment of a working vehicle1. In a case of this embodiment, the working vehicle1is a tractor. However, the working vehicle1is not limited to a tractor and may be an agricultural machine (agricultural vehicle) such as a combine or a transplanter, a construction machine (construction vehicle) such as a loader working machine, and the like. Hereinafter, a direction in which an operator who is seated on an operator's seat10of the working vehicle (tractor)1is oriented (direction of arrow A1inFIG.9) is referred to as “front”, while the opposite direction thereof (direction of arrow A2inFIG.9) is referred to as “back”. In addition, the left of the operator is referred to as “left”, while the right of the operator is referred to as “right”. Furthermore, a horizontal direction orthogonal to the front-back direction of the working vehicle1is referred to as “vehicle-body width direction”. As illustrated inFIG.9, the working vehicle (tractor)1includes a vehicle body3, a prime mover4, and a transmission5. The vehicle body3has a traveling device7and is capable of traveling. The traveling device7is a drive driven by power output from the prime mover4and has front wheels7F and rear wheels7R. The front wheels7F may be of a tire type or a crawler type. The rear wheels7R may also be of a tire type or a crawler type. The prime mover4is a diesel engine, an electric prime mover, or the like and is a machine that outputs power. In this embodiment, the prime mover4is a diesel engine. The transmission5is a transmission mechanism that transmits power output from the prime mover4to the traveling device7(drive). The transmission5can switch a propelling force of the traveling device7by changing gears and can switch the traveling device7between forward travel and reverse travel. The vehicle body3is provided with the operator's seat10. A coupler8is provided in a rear portion of the vehicle body3. A working device2can be attached to and detached from the coupler8. By the working device2being coupled to the coupler8, the vehicle body3can tract the working device2. Examples of the working device2include a cultivator for cultivation, a fertilizer spreader for spreading a fertilizer, an agricultural chemical spreader for spreading an agricultural chemical, a harvester for harvesting, a mower for mowing grass or the like, a tedder for tedding grass or the like, a rake for raking grass or the like, and a baler for baling grass or the like. As illustrated inFIG.2, a steering wheel30for steering the vehicle body3, a brake operation member31, and a clutch switch member32are provided around the operator's seat10. The brake operation member31includes a plurality of operation units, for example, a brake pedal31L provided on the left and a brake pedal31R provided on the right. The brake pedal31L and the brake pedal31R are supported by the vehicle body3in a swingable manner and can be operated by the operator seated on the operator's seat10. The clutch switch member32includes a clutch pedal32A and a clutch lever32B. The clutch pedal32A is supported by the vehicle body3in a swingable manner and can be operated by the operator seated on the operator's seat10, similarly to the brake pedal31L and the brake pedal31R. For example, the clutch lever32B is supported in a swingable manner near the steering wheel30and is switchable among a forward-travel position (F), a reverse-travel position (R), or a neutral position (N). As illustrated inFIG.1, the transmission5includes a main shaft (propeller shaft)5a, a main transmission unit5b, a sub-transmission unit5c, a traveling clutch5d, and a power take-off (PTO) power transmission unit5e. The propeller shaft5ais rotatably supported by a housing case (transmission case) of the transmission5, and power from a crankshaft of the prime mover4is transmitted to the propeller shaft5a. The main transmission unit5bhas a plurality of gears and a gearshift that changes connection of the gears. The main transmission unit5bchanges connection (engagement) of the plurality of gears by using the gearshift as appropriate to change and output rotation input from the propeller shaft5a(change gears). Similarly to the main transmission unit5b, the sub-transmission unit5calso has a plurality of gears and a gearshift that changes connection of the gears. The sub-transmission unit5cchanges connection (engagement) of the plurality of gears by using the gearshift as appropriate to change and output rotation input from the main transmission unit5b(change gears). The traveling clutch5dis a traveling device that is switchable between a connected state in which power is transmitted to the traveling device7(the front wheels7F and the rear wheels7R) and a disconnected state in which transmission of power to the traveling device7is disconnected. In addition, the traveling clutch5dcan be displaced to a half-clutch state in which power is slidably and partly transmitted to the traveling device7in response to the disconnected state being switched to the connected state. The traveling clutch5dhas a shuttle shaft12and a clutch switch unit13. Power output from the prime mover4is transmitted to the shuttle shaft12. The clutch switch unit13is a hydraulic clutch that is switched to a forward-driving clutch state, a reverse-driving clutch state, or a neutral state. The clutch switch unit13is connected to a forward-travel switching valve26and a reverse-travel switching valve27connected via a fluid passage (omitted from illustration) or the like. Each of the forward-travel switching valve26and the reverse-travel switching valve27is a two-position electromagnetic switching valve, for example. If a solenoid of the forward-travel switching valve26is energized, the clutch switch unit13is switched to the forward-driving clutch state. If a solenoid of the reverse-travel switching valve27is energized, the clutch switch unit13is switched to the reverse-driving clutch state. If each of the solenoids of the forward-travel switching valve26and the reverse-travel switching valve27is deenergized, the clutch switch unit13is switched to the neutral state. The clutch switch unit13is switchable by using the clutch switch member32. If the clutch lever32B is in the forward-travel position (F), while the solenoid of the forward-travel switching valve26is energized, the solenoid of the reverse-travel switching valve27remains deenergized, and the clutch switch unit13is switched to the forward-driving clutch state. If the clutch lever32B is in the reverse-travel position (R), while the solenoid of the reverse-travel switching valve27is energized, the solenoid of the forward-travel switching valve26remains deenergized, and the clutch switch unit13is switched to the reverse-driving clutch state. If the clutch lever32B is in the neutral position (N), the solenoids of the forward-travel switching valve26and the reverse-travel switching valve27remain deenergized, and the clutch switch unit13is switched to the neutral state. If the clutch pedal32A is operated in a state where the clutch lever32B is in the forward-travel position (F) and if the clutch pedal32A is operated in a state where the clutch lever32B is in the reverse-travel position (R), either of the solenoids of the forward-travel switching valve26and the reverse-travel switching valve27is energized, and the clutch switch unit13is switched to the neutral state from either of the forward-driving clutch state and the reverse-driving clutch state. The shuttle shaft12is connected to the propeller shaft5a. Power of the propeller shaft5ais transmitted to the main transmission unit5band the sub-transmission unit5c, and power output from the sub-transmission unit5cis transmitted to a rear-wheel differential20R. The rear-wheel differential20R rotatably supports a rear axle21R to which the rear wheels7R are attached. That is, if the clutch switch unit13is switched to either of the forward-driving clutch state and the reverse-driving clutch state and the clutch pedal32A is not operated, the traveling clutch5dis in the connected state and transmits power to the traveling device7(the front wheels7F and the rear wheels7R). If the clutch switch unit13is switched to the neutral state, the traveling clutch5dis in the disconnected state and disconnects transmission of power to the traveling device7. The PTO power transmission unit5ehas a PTO propeller shaft14and a PTO clutch15. The PTO propeller shaft14is rotatably supported and can transmit power from the propeller shaft5a. The PTO propeller shaft14is connected to a PTO shaft16via a gear or the like. The PTO clutch15includes, for example, a hydraulic clutch or the like, and is switched between a state where power of the propeller shaft5ais transmitted to the PTO propeller shaft14and a state where power of the propeller shaft5ais not transmitted to the PTO propeller shaft14by engaging/disengaging of the hydraulic clutch. As illustrated inFIG.1, the working vehicle1includes a brake device46. The brake device46has a left brake device46aand a right brake device46b. Each of the left brake device46aand the right brake device46bis a disc-type brake device and is switchable between a brake state for braking and a release state for releasing the brake. The left brake device46ais provided on the left of the rear axle21R, while the right brake device46bis provided on the right of the rear axle21R. Upon the operator who operates the working vehicle1operating (depressing) the brake pedal31L, a left coupling member47acoupled to the brake pedal31L can be moved in a braking direction, and the left brake device46acan be brought into a brake state. Upon the operator operating (depressing) the brake pedal31R, a right coupling member47bcoupled to the brake pedal31R can be moved in a braking direction, and the right brake device46bcan be brought into a brake state. A left hydraulic actuation unit48athat is actuated by a hydraulic fluid is coupled to the left coupling member47a. A left braking valve49ais connected to the left hydraulic actuation unit48avia a fluid passage. By actuating the left hydraulic actuation unit48aby using the left braking valve49a, the left coupling member47acan be moved in the braking direction. A right hydraulic actuation unit48bthat is actuated by a hydraulic fluid is coupled to the right coupling member47b. A right braking valve49bis connected to the right hydraulic actuation unit48bvia a fluid passage. By actuating the right hydraulic actuation unit48bby using the right braking valve49b, the right coupling member47bcan be moved in the braking direction. In the above manner, by operating the brake pedal31L and the brake pedal31R, the left brake device46aand the right brake device46bcan independently bring the left rear wheel7R and the right rear wheel7R into the braking state. As illustrated inFIG.2, a plurality of display devices50are provided around the operator's seat10. The plurality of display devices50include a first display device50A provided in front of the operator's seat10(the steering wheel30) and a second display device50B provided on a side of the operator's seat10(the steering wheel30). As illustrated inFIG.3, the first display device50A is a meter panel or the like that mainly displays various kinds of driving information and includes a prime mover tachometer51athat displays the rotation speed of the prime mover4, a water temperature gauge51b, and a fuel gauge51c. The first display device50A further has a notifier52including at least one indicator lamp52A that notifies various kinds of information by being turned on/off or the like. The first display device50A illustrated inFIG.3is an example and is not limited to the above configuration. Similarly to the first display device50A, the second display device50B is a device that mainly displays various kinds of driving information and includes a display panel50B1and a touch panel50B2that is disposed on a surface of the display panel50B1. Various menu items are displayed on the second display device50B, and various settings of the working vehicle1can be performed by a predetermined operation. As illustrated inFIG.1, the working vehicle1includes a control device40. The control device40includes a central processing unit (CPU), electrical and electronic circuitry, or the like and controls the working vehicle1in various manners. The control device40includes a change unit40A and a storage unit40B. The storage unit40B is a storage device and stores various control programs and data tables regarding operations of the working vehicle1. To the control device40, an accelerator sensor42a, an ignition switch42b, a raising/lowering switch42c, a vehicle speed detection sensor42d, a brake-operation detection sensor42e, a clutch lever sensor42f, a detector53, and the like are connected. The accelerator sensor42adetects an operation amount of an accelerator41a(FIG.2). The vehicle speed detection sensor42ddetects the vehicle speed (velocity). The brake-operation detection sensor42edetects an operation amount of the brake operation member31(the brake pedal31L and the brake pedal31R). The clutch lever sensor42fdetects the position of the clutch lever32B. The detector53detects an operation position of the clutch pedal32A and outputs a detected value corresponding to the detected operation position. The detector53is, for example, a clutch-operation detection sensor53athat detects an operation amount of the clutch pedal32A. The clutch-operation detection sensor53ais a detection sensor whose detection method is such that a detected value decreases in accordance with the operation amount (depressed amount) of the clutch pedal32A. For example, in a state where the clutch pedal32A is depressed to a maximum depression position PMAX (seeFIG.6Adescribed later), the detected voltage value of the clutch-operation detection sensor53ais “0 volts”. Then, as the clutch pedal32A becomes away from the maximum depression position PMAX, the detected voltage value of the clutch-operation detection sensor53aincreases. Then, in a state where a foot is detached from the clutch pedal32A, that is, in a state where the clutch pedal32A is in an unoperated position P0(seeFIG.6Adescribed later), the detected voltage value of the clutch-operation detection sensor53abecomes a maximum (e.g., “5 volts”). If the operation amount of the accelerator41ais detected by the accelerator sensor42a, the control device40changes the rotation speed of the prime mover4(referred to as “prime mover rotation speed”) in accordance with the operation amount. If the ignition switch42bis operated to be turned on, the control device40starts the prime mover4through a predetermined process; if the ignition switch42bis operated to be turned off, the control device40stops driving the prime mover4. If the raising/lowering switch42cis operated in a raising direction, the control device40controls a control valve to extend a lift cylinder and to raise the working device2. If the raising/lowering switch42cis operated in a lowering direction, the control device40controls the control valve to contract the lift cylinder to lower the working device2. The control device40performs a brake control on the basis of the brake-operation detection sensor42e. During the brake control, upon the brake-operation detection sensor42edetecting an operation on the brake pedal31L, the control device40actuates the left hydraulic actuation unit48ato operate the left brake device46afor braking. In addition, during the brake control, upon the brake-operation detection sensor42edetecting an operation on the brake pedal31R, the control device40actuates the right hydraulic actuation unit48bto operate the right brake device46bfor braking. Furthermore, during the brake control, upon the brake-operation detection sensor42edetecting operations on the brake pedal31L and the brake pedal31R, the control device40actuates the left hydraulic actuation unit48aand the right hydraulic actuation unit48bto operate the left brake device46aand the right brake device46bfor braking. Upon the clutch lever sensor42fdetecting that the clutch lever32B has been switched to the forward-travel position (F), the control device40energizes the solenoid of the forward-travel switching valve26to switch the clutch switch unit13to the forward-driving clutch state. Upon the clutch lever sensor42fdetecting that the clutch lever32B has been switched to the reverse-travel position (R), the control device40energizes the solenoid of the reverse-travel switching valve27to switch the clutch switch unit13to the reverse-driving clutch state. Upon the clutch lever sensor42fdetecting that the clutch lever32B has been switched to the neutral position (N), the control device40deenergizes the solenoids of the forward-travel switching valve26and the reverse-travel switching valve27to switch the clutch switch unit13to the neutral state. If a detected value from the detector53(the clutch-operation detection sensor53a) (e.g., detected voltage value) corresponds with a predetermined threshold (e.g., threshold voltage), the control device40brings the traveling clutch5dinto the half-clutch state. If the detected value is less than the threshold, the control device40brings the traveling clutch5dinto the disconnected state. If the detected value exceeds the threshold, the control device40brings the traveling clutch5dinto the connected state. For example, if the operator depresses the clutch pedal32A to the maximum depression position PMAX, the detected voltage value from the clutch-operation detection sensor53aexceeds the threshold voltage, and thus, the control device40brings the traveling clutch5dinto the disconnected state. Then, if the operator restores the clutch pedal32A from the maximum depression position PMAX to a position denoting the half-clutch state, the detected voltage value from the clutch-operation detection sensor53acorresponds with the threshold voltage, and thus, the control device40brings the traveling clutch5dinto the half-clutch state. Then, if the operator further restores the clutch pedal32A, the detected voltage value from the clutch-operation detection sensor53abecomes less than the threshold voltage, and thus, the control device40brings the traveling clutch5dinto the connected state. In the above manner, the operator performs a series of operations of depressing the clutch pedal32A to the maximum depression position PMAX and then restoring the clutch pedal32A to the position denoting the half-clutch state and further restoring the clutch pedal32A to the unoperated position P0. The working vehicle1according to this embodiment can change a half-clutch stroke length of the clutch pedal32A. Note that the half-clutch stroke length is the length of displacement of the clutch pedal32A from the maximum depression position PMAX, in which the clutch pedal32A is operated so that the traveling clutch5dis brought into the disconnected state, to the operation position of the clutch pedal32A, in which the traveling clutch5dis brought into the half-clutch state. The clutch lever32B (operation lever) includes an operation member45that is operable by the operator or the like. The operation member45is a dial switch45a, for example, provided at the tip of the clutch lever32B and rotatable around the longitudinal direction of the clutch lever32B as an axial center. As illustrated inFIG.2, an armrest18is provided on the right of the operator's seat10. The armrest18extends in the front-back direction of the operator's seat10. The operator can operate the steering wheel30with the right arm rested on the armrest18. On the right side surface of the armrest18, a second operation member54is provided. The second operation member54is different from the operation member45disposed on the clutch lever32B and serving as a first operation member. The second operation member54is a sensitivity setting button54a, for example. The sensitivity setting button54ais a push-button switch, for example. The sensitivity setting button54ais an operation switch that is turned on while the operator or the like is operating it and is turned off while the operator or the like is not performing it. As illustrated inFIG.1, the control device40includes the change unit40A. The control device40functions as the change unit40A by, for example, the CPU executing a control program stored in the storage unit40B. The change unit40A changes the value of the threshold voltage (threshold) to a different value in accordance with an operation on the operation member45. Specifically, if the clutch pedal32A is in the maximum depression position PMAX (i.e., maximum operation position), the detector53outputs a predetermined first detected value (e.g., minimum, which is “0 volts”) as the detected value; if the clutch pedal32A is in the unoperated position P0, where no operation is performed, the detector53outputs a predetermined second detected value (e.g., maximum, which is “5 volts”), which is a value separated from the first detected value by a certain value range, as the detected value. The threshold voltage is a predetermined single value among a plurality of values that are present between the first detected value (0 volts) and the second detected value (5 volts). The threshold voltage is set to, for example, 2.5 volts as a default value (initial value). If the second operation member54and the operation member45are operated (e.g., if the dial switch45ais operated while the sensitivity setting button54ais pressed), in accordance with the operation on the dial switch45a, the change unit40A can change the value of the threshold to a value (e.g., 1 volt) closer to the first detected value (0 volts) than the default value (2.5 volts) is or a value (e.g., 4 volts) closer to the second detected value (5 volts) than the default value (2.5 volts) is. Note that the first detected value, the second detected value, the value of the threshold, and the changed value of the threshold are not limited to the above values and may be values other than the above values. Here, a sensitivity setting process performed by the control device40will be described with reference toFIG.4. Upon determining that the sensitivity setting button54ais operated (Yes in51), the control device40changes a mode of the working vehicle1from a normal mode to a setting changing mode. The setting changing mode is maintained throughout the operation on the sensitivity setting button54aby an operator or the like. Upon the operator or the like stopping the operation on the sensitivity setting button54a, the control device40returns the mode of the working vehicle1from the setting changing mode to the normal mode. On the other hand, as long as the operator or the like does not operate the sensitivity setting button54a(No in S1), the control device40ends this process without changing the mode of the working vehicle1to the setting changing mode. If the mode of the working vehicle1is the setting changing mode, the change unit40A executes sensitivity setting for changing the value of the threshold voltage (threshold) to a different value in accordance with the operation on the operation member45(the dial switch45a) (S2). Specifically, as illustrated inFIG.5A, the control device40causes the second display device50B to display a setting screen M1for setting the sensitivity of the clutch pedal32A. InFIG.5A, it is assumed that the sensitivity “3” (default value) of the clutch pedal32A is indicated. In accordance with the operation on the dial switch45aprovided on the clutch lever32B (operation lever), the change unit40A changes the sensitivity of the clutch pedal32A. In this embodiment, the sensitivity of the clutch pedal32A is changeable within a predetermined range (range of sensitivity from “1” to “5”) in units of one decimal place. If the operator or the like rotates the dial switch45ato the back (i.e., counterclockwise in a left side view of the clutch lever32B), the sensitivity of the clutch pedal32A is increased. The sensitivity of the clutch pedal32A is displayed in an indicator portion102band a numerical value display portion103. On the other hand, if the operator or the like rotates the dial switch45ato the front (i.e., clockwise in a left side view of the clutch lever32B), the sensitivity of the clutch pedal32A is decreased. InFIG.5B, the sensitivity of the clutch pedal32A is set to the maximum “5”. Upon a button104bindicating “OK” being touched in this state, if the mode of the working vehicle1is the setting changing mode, the change unit40A changes the sensitivity from “3” to “5”, changes the value of the threshold voltage from the threshold voltage corresponding to the sensitivity “3” to a threshold voltage corresponding to the sensitivity “5”, and stores the changed sensitivity and the changed value of the threshold voltage in the storage unit40B. Subsequently, the control device40restores the mode of the working vehicle1from the setting changing mode to the normal mode and ends this process. In addition, upon a button104aindicating “CANCEL” being touched in a state where the setting screen M1illustrated inFIG.5Bis displayed, the change unit40A displays the unchanged sensitivity (the sensitivity “3” illustrated inFIG.5Ain this example) without changing the sensitivity to “5”, and the control device40returns the mode of the working vehicle1from the setting changing mode to the normal mode and ends this process. The storage unit40B maintains the unchanged sensitivity and the unchanged value of the threshold voltage. As illustrated inFIG.6AandFIG.6C, the sensitivity “3” and the value of the threshold voltage “2.5 volts” are associated with each other in advance. In this case, the stroke length of the clutch pedal32A is a length L3. This means that the detected voltage value of the clutch-operation detection sensor53awhen the clutch pedal32A is set in a position P3by being restored from the maximum depression position PMAX by the length L3is “2.5 volts”, the detected voltage value corresponds with the threshold voltage, and the traveling clutch5dis brought into the half-clutch state. The position of the clutch pedal32A in which the traveling clutch5dis brought into the half-clutch state is the position of the length L3. That is, the stroke length of the clutch pedal32A is the length L3. In addition, the sensitivity “5” and the value of the threshold voltage “1 volt” are associated with each other in advance. In this case, the stroke length of the clutch pedal32A is a length L5. This means that the detected voltage value of the clutch-operation detection sensor53awhen the clutch pedal32A is set in a position P5by being restored from the maximum depression position PMAX by the length L5is “1 volt”, the detected voltage value corresponds with the threshold voltage, and the traveling clutch5dis brought into the half-clutch state. The position of the clutch pedal32A in which the traveling clutch5dis brought into the half-clutch state is the position of the length L5. That is, the stroke length of the clutch pedal32A is the length L5. Furthermore, the sensitivity “1” and the value of the threshold voltage “4 volts” are associated with each other in advance. In this case, the stroke length of the clutch pedal32A is a length L1. This means that the detected voltage value of the clutch-operation detection sensor53awhen the clutch pedal32A is set in a position P1by being restored from the maximum depression position PMAX by the length L1is “4 volts”, the detected voltage value corresponds with the threshold voltage, and the traveling clutch5dis brought into the half-clutch state. The position of the clutch pedal32A in which the traveling clutch5dis brought into the half-clutch state is the position of the length L1. That is, the stroke length of the clutch pedal32A is the length L1. The above three stroke lengths have the relationship of “L5<L3<L1”. In addition, within the sensitivity range from “1” to “5”, the threshold voltage is also associated with each of the sensitivities other than the sensitivities “1”, “3”, and “5” in advance, and the stroke length of the clutch pedal32A is a corresponding length. That is, the sensitivity, the threshold voltage, and the stroke length have a relationship (proportional relationship) such that the threshold voltage and the stroke length are decreased as the sensitivity is increased. As illustrated inFIG.6B, if the sensitivity is “3” (default value), the threshold voltage is 2.5 volts and the stroke length of the clutch pedal32A is the length L3. However, if the sensitivity is changed to “5”, the threshold voltage becomes 1 volt, and the stroke length of the clutch pedal32A becomes the length L5. Thus, the stroke length is decreased, and the response of the vehicle body3is faster. On the other hand, if the sensitivity is changed to “1”, the threshold voltage becomes 4 volts, and the stroke length of the clutch pedal32A becomes the length L1. Thus, the stroke length is increased, and the response of the vehicle body3is slower. The stroke length of the clutch pedal32A differs depending on the operator's preference. For example, operators with driving skills may prefer a short stroke length. On the other hand, novice operators may prefer a long stroke length. By changing the sensitivity of the clutch pedal32A in the above manner, the stroke length of the clutch pedal32A can be changed in accordance with the operator's preference. The storage unit40B stores the relationship among the sensitivity, the threshold voltage, and the stroke length of the clutch pedal32A illustrated inFIG.6Cin advance. Note that the storage unit40B may store the relationship between the sensitivity and the threshold voltage and does not necessarily store the stroke length of the clutch pedal32A. Since the second display device50B has a touch panel function, the sensitivity of the clutch pedal32A can be set thereon. As illustrated inFIG.5A, the second display device50B displays a sensitivity input portion100on the setting screen M1. The sensitivity input portion100is a portion where the sensitivity of the clutch pedal32A is input and has a button input portion101, a slide input portion102, and the numerical value display portion103. The button input portion101is a portion where the sensitivity of the clutch pedal32A is input by a pressing operation and includes an increase input portion101afor increasing the sensitivity and a decrease input portion101bfor decreasing the sensitivity. The slide input portion102is a portion where the sensitivity is input by a sliding operation and includes a scale portion102aand the indicator portion102b. The scale portion102ais a scale indicating the magnitude of the sensitivity and includes, for example, a plurality of vertical bars (gauges) arranged side by side horizontally. In the scale portion102a, one end of the arranged vertical bars is the minimum, while the other end of the arranged vertical bars is the maximum. For example, the left end is the minimum, while the right end is the maximum. The indicator portion102bis a portion that indicates the sensitivity on the scale portion102aand can move in the arrangement direction of the vertical bars. The indicator portion102bcan move in response to a touch operation or the like along the scale portion102a. In addition, the indicator portion102bmoves along the scale portion102ain conjunction with the sensitivity input in the button input portion101. For example, if the sensitivity is increased in the increase input portion101a, the indicator portion102bmoves in the increasing direction along the scale portion102a. If the sensitivity is decreased in the decrease input portion101b, the indicator portion102bmoves in the decreasing direction along the scale portion102a. The numerical value display portion103displays the sensitivity set in the button input portion101and the slide input portion102as numerical values. Note that a lower limit and an upper limit of the sensitivity are set in advance in the sensitivity input portion100, and it is not possible to set the sensitivity to values lower than the predetermined lower limit and values higher than the predetermined upper limit. For example, the lower limit of the sensitivity is set to “1”, while the upper limit of the sensitivity is set to “5”. Although the control device40causes the second display device50B to display the setting screen M1illustrated inFIG.5AandFIG.5B, that is, a screen for setting the sensitivity of the clutch pedal32A, the control device40may also cause the second display device50B to display the setting screen M1for setting the threshold voltage of the clutch pedal32A as illustrated inFIG.5CandFIG.5D. For example, the default value of the threshold voltage is set to “2.5 volts”, the lower limit of the threshold voltage is set to “1 volt”, and the upper limit of the threshold voltage is set to “4 volts”. Note that the control device40may further cause the stroke length of the clutch pedal32A illustrated inFIG.6Ato be displayed on the setting screen M1illustrated inFIG.5Ain the sensitivity setting (S2) illustrated inFIG.4. That is, the control device40causes the sensitivity setting of the clutch pedal32A and the stroke length of the clutch pedal32A illustrated inFIG.6Ato be displayed in association with each other. For example, if the sensitivity is “3” as illustrated inFIG.5A, as illustrated inFIG.6A, in the range from the unoperated position P0to the maximum depression position PMAX, an image of the clutch pedal32A in a state where the stroke length is the length L3and supplementary information thereof (information indicating the sensitivity “3”, the value of the threshold voltage (2.5 volts), and the position P3) are displayed on the setting screen M1of the second display device50B. Then, in conjunction with the change in the sensitivity setting of the clutch pedal32A, the control device40causes an image of the clutch pedal32A in a state where the stroke length is changed and the supplementary information thereof to be displayed on the setting screen M1. For example, if the sensitivity is changed to “5” as illustrated inFIG.5B, an image of the clutch pedal32A in a state where the stroke length is the length L5illustrated inFIG.6Aand related information (information indicating the sensitivity “5”, the value of the threshold voltage (1 volt), and the position P5) are displayed on the setting screen M1of the second display device50B. In this case, it becomes easier to grasp a correspondence between the sensitivity setting of the clutch pedal32A and the stroke length, and thus, the sensitivity can be set easier. The control device40can perform automatic switch control. The automatic switch control is disconnection control (first process) for switching the traveling clutch5dfrom the connected state to the disconnected state in accordance with an operation on the brake operation member31(the brake pedal31L and the brake pedal31R). That is, in a situation where the traveling clutch5dis switched to the forward-driving clutch state and in a situation where the traveling clutch5dis switched to the reverse-driving clutch state, the automatic switch control can switch the traveling clutch5dto the disconnected state by using the brake operation member31for braking. A switching unit43that selects whether the automatic switch control is valid or invalid is connected to the control device40. The switching unit43includes a switch44. The switch44is provided around the operator's seat10and can be turned on/off. If at least the automatic switch control is invalid, by turning on the switch44from off state, the automatic switch control is switched from invalid to valid. The clutch pedal32A is part of the switching unit43, and if at least the automatic switch control is valid, by operating the switching unit43, the automatic switch control is switched from valid to invalid. Whether the automatic switch control is valid or invalid can be displayed on either of the first display device50A and the second display device50B. As illustrated inFIG.3, for example, among a plurality of indicator lamps52A of the notifier52, a first indicator lamp52A1corresponding to the automatic switch control is turned on while the automatic switch control is valid and is turned off while the automatic switch control is invalid. Alternatively, on the second display device50B, a display portion on a predetermined screen corresponding to the automatic switch control is turned on while the automatic switch control is valid and is turned off while the automatic switch control is invalid. The control device40performs the first process (disconnection control) as the automatic switch control. During the first process, when an operation amount (depressed amount) W1of each of the brake pedal31L and the brake pedal31R is greater than or equal to a predetermined threshold E2, the control device40performs the first process. If the operation amount (depressed amount) W1is less than the threshold E2, the control device40does not perform the first process. The storage unit40B stores the threshold E2of the operation amount (depressed amount) W1of each of the brake pedal31L and the brake pedal31R in advance. If the first process is performed, the notifier52notifies that the first process is performed. For example, among the plurality of indicator lamps52A of the notifier52, a second indicator lamp52A2corresponding to the automatic switch control is turned on when the first process is performed and is turned off when the first process is not performed. Thus, since the first display device50A has the first indicator lamp52A1and the second indicator lamp52A2, whether the automatic switch control is valid or invalid can be displayed and whether the first process is performed can be displayed. FIG.7AtoFIG.7Care flowcharts of the automatic switch control and the like performed by the control device40. As illustrated inFIG.7A, in a situation where the clutch pedal32A is not operated and the clutch lever32B is switched to either of the forward-travel position (F) and the reverse-travel position (R), the control device40determines whether the automatic switch control is valid (S11). If the automatic switch control is valid (Yes in S11), the control device40determines whether the clutch pedal32A is operated (S12). If the clutch pedal32A is operated (Yes in S12), the control device40controls the traveling clutch5d(S13). The control device40determines whether the operation amount W1of the brake pedal (each of the brake pedal31L and the brake pedal31R) is greater than or equal to the threshold E2(S14). If the operation amount W1is greater than or equal to the threshold E2(Yes in S14), the control device40performs the first process for switching the traveling clutch5dfrom the connected state to the disconnected state (S15). If the first process is performed, the control device40temporarily stores the position of the clutch lever32B prior to the first process (position storing process). On the other hand, if the operation amount W1is not greater than or equal to the threshold E2(No in S14), the process returns to S11. After the first process is performed, the control device40advances to a post-disconnection process illustrated inFIG.7BandFIG.7C. As illustrated inFIG.7B, during the post-disconnection process, the control device40determines whether the operation amount W1of the brake pedal becomes less than the threshold E2(S21: brake pedal determination). In S21(brake pedal determination), for example, after the first process (S15) is performed in a state where the brake pedal is depressed, the control device40determines whether depression of the brake pedal is released, that is, whether the brake pedal is released. If the operation amount W1of the brake pedal becomes less than the threshold E2by releasing the brake pedal or the like (Yes in S21), the control device40performs a restore process (S22) for restoring the traveling clutch5dto the state prior to the first process. On the other hand, if the operation amount W1is greater than or equal to the threshold E2(No in S21), the process returns to S21. In S22(restore process), if the clutch lever32B in the forward-travel position (F) is stored in the position storing process, the control device40restores the traveling clutch5dto the forward-driving clutch state; if the clutch lever32B in the reverse-travel position (R) is stored in the position storing process, the control device40restores the traveling clutch5dto the reverse-driving clutch state. Here, in restoring the traveling clutch5dto the forward-driving clutch state or the reverse-driving clutch state, the control device40performs connection control for switching the traveling clutch5dto the connected state through the half-clutch state by using the threshold with the default value (e.g., the threshold voltage is 2.5 volts: the sensitivity “3”) if the threshold is not changed, or by using the threshold whose value is changed by the change unit40A (e.g., the threshold voltage is 1 volt: the sensitivity “5” or the threshold voltage is 4 volts: the sensitivity “1”). Although the series of operations by the operator on the clutch pedal32A are not performed here, the control device40performs control as if the detected voltage value of the clutch-operation detection sensor53acorresponds with and exceeds the threshold with the default value or the changed threshold. As illustrated inFIG.7C, the control device40determines whether the clutch pedal32A is operated (S31: clutch pedal determination). In S31(clutch pedal determination), for example, after the first process is performed (after S15) in a state where the clutch pedal32A is not depressed, the control device40determines whether the clutch pedal32A is depressed. If the clutch pedal32A is changed from a released state to a depressed state (Yes in S31) in S31(clutch pedal determination), the control device40keeps the disconnected state of the traveling clutch5d(S32) and switches the automatic switch control from valid to invalid (S33). On the other hand, if the clutch pedal32A is not operated (No in S31), the process returns to S31. If the automatic switch control is not valid (No in S11) in S11inFIG.7A, the process returns to S11, and thus, the automatic switch control is not performed. If the automatic switch control is not valid (No in S11), the control device40may end this process and may skip S12to S15inFIG.7Aand the processes inFIG.7BandFIG.7C. FIG.8AandFIG.8Bare diagrams illustrating an overall relationship among whether the automatic switch control is valid/invalid, the position of the clutch lever32B, the operation on the clutch pedal32A, the operation on the brake pedals31L and31R, and the like. For the convenience of description, a state where the clutch lever32B is switched to either of the forward-travel position (F) and the reverse-travel position (R) is referred to as “forward-travel/reverse-travel period”. In addition, “OFF” of the clutch pedal32A indicates that the operation amount of the clutch pedal32A is less than a predetermined amount (less than the threshold) and indicates, for example, an unoperated state. “ON” of the clutch pedal32A indicates that the operation amount of the clutch pedal32A is greater than or equal to the predetermined amount (greater than or equal to the threshold) and indicates, for example, a depressed state. “OFF” of the brake pedal indicates that the operation amount W1of the brake pedal is less than the threshold E2and indicates, for example, a released state. “ON” of the brake pedal indicates that the operation amount W1of the brake pedal is greater than or equal to the threshold E2, and indicates, for example, a depressed state. InFIG.8B, a previous state indicates a state when an initial operation is performed, while a subsequent state indicates a state when the clutch pedal32A, the brake pedal, or the like is operated after the previous state. InFIG.8AandFIG.8B, “connected” indicates that the traveling clutch5dis in the connected state, while “disconnected” means that the traveling clutch5dis in the disconnected state. In addition, “keep disconnected” indicates that the disconnected state is kept in the subsequent state if at least the traveling clutch5dis brought into the disconnected state in the previous state. Furthermore, “keep connected” indicates that the connected state is kept in the subsequent state if at least the traveling clutch5dis brought into the connected state in the previous state. “Keep valid” indicates that the automatic switch control is kept valid in the subsequent state if at least the automatic switch control is valid in the previous state. “Switch to invalid” indicates that the automatic switch control is switched from valid to invalid in the subsequent state if at least the automatic switch control is valid in the previous state. As illustrated in No. 1 to No. 4 inFIG.8A, in a state where the automatic switch control is invalid and during the forward-travel/reverse-travel period, upon the clutch pedal32A being operated, the traveling clutch5dis switched to either of the connected state and the disconnected state regardless of the brake pedal. As illustrated in No. 5 to No. 8 inFIG.8A, in a state where the automatic switch control is invalid and the clutch lever32B is in the neutral position (N), the traveling clutch5dis maintained in the disconnected state even if the clutch pedal32A is operated. As illustrated in “previous state” in No. 11 inFIG.8B, in a state where the automatic switch control is valid and during the forward-travel/reverse-travel period, the traveling clutch5dis brought into the connected state unless the clutch pedal32A and the brake pedal are operated. Subsequently, as illustrated in “subsequent state” in No. 11 inFIG.8, upon the clutch pedal32A being operated (ON), although the traveling clutch5dis switched to the disconnected state, the automatic switch control is kept valid (keep valid). In addition, as illustrated in “subsequent state” in No. 11 inFIG.8B, upon the brake pedal being operated, the first process is performed, and the traveling clutch5dcan be brought into the disconnected state. The automatic switch control is kept valid (keep valid). As illustrated in “previous state” in No. 12 inFIG.8B, upon the brake pedal being operated in a state where the clutch pedal32A is not operated, the first process is performed, and the traveling clutch5dcan be brought into the disconnected state. Subsequently, as illustrated in “subsequent state” in No. 12 inFIG.8B, upon the clutch pedal32A being operated (ON), the disconnected state of the traveling clutch5dis kept (keep disconnected), and the automatic switch control is switched to invalid (switch to invalid). In addition, as illustrated in “subsequent state” in No. 12 inFIG.8B, upon the operation on the brake pedal being released, the traveling clutch5dis brought into the connected state, and the automatic switch control is kept valid (keep valid). As illustrated in “previous state” in No. 13 inFIG.8B, in a state where the automatic switch control is valid and during the forward-travel/reverse-travel period, upon the clutch pedal32A being operated without an operation on the brake pedal, the traveling clutch5dis brought into the disconnected state. Subsequently, with the clutch pedal32A being operated in “previous state” in No. 13, upon the brake pedal being operated as illustrated in “subsequent state” in No. 13, that is, upon both the clutch pedal32A and the brake pedal being operated, the automatic switch control is switched from valid to invalid (switch to invalid). In addition, as illustrated in “subsequent state” in No. 13 inFIG.8B, upon the operation on the clutch pedal32A being released, the traveling clutch5dis brought into the connected state, and the automatic switch control is kept valid (keep valid). As illustrated in “previous state” in No. 14 inFIG.8B, in a state where the automatic switch control is valid and during the forward-travel/reverse-travel period, upon the brake pedal and the clutch pedal32A being operated, the traveling clutch5dis brought into the disconnected state. Subsequently, as illustrated in “subsequent state” in No. 14, unless the brake pedal and the clutch pedal32A are operated, the disconnected state of the traveling clutch5dis kept, and the automatic switch control is kept valid (keep valid) In the above manner, the working vehicle1according to the above embodiment includes the prime mover4that outputs power; the traveling device7(drive) driven by the power output from the prime mover4; the transmission5(transmission mechanism) that transmits the power output from the prime mover4to the traveling device7; the traveling clutch5d(clutch) provided in the transmission5and displaceable to a connected state in which the power is transmitted to the traveling device7, a disconnected state in which transmission of the power to the traveling device7is disconnected, and a half-clutch state in which the power is slidably and partly transmitted to the traveling device7; the clutch pedal32A; the detector53that detects an operation position of the clutch pedal32A and outputs a detected value corresponding to the operation position detected; the control device40that brings the traveling clutch5dinto the half-clutch state if the detected value from the detector53corresponds with a predetermined threshold, brings the traveling clutch5dinto the disconnected state if the detected value is either one of a value less than the threshold and a value greater than the threshold, and brings the traveling clutch5dinto the connected state if the detected value is the other of the value less than the threshold and the value greater than the threshold; the operation member45; and the change unit40A that changes a value of the threshold to a different value in accordance with an operation on the operation member45. According to this configuration, by merely changing the value of the threshold to a different value by the operation on the operation member45by the operator, the operation position of the clutch pedal32A corresponding to the half-clutch state can be changed. That is, the operation position of the clutch pedal32A indicating a detected value from the detector53corresponding with the changed threshold becomes the changed operation position corresponding to the half-clutch state. The operation position of the clutch pedal32A corresponding to the half-clutch state can be changed to any given position within the range of the positions P1to P5illustrated inFIG.6A. Thus, the half-clutch stroke length can be adjusted. That is, it is possible to provide the working vehicle1that can improve operability of a clutch operation. In addition, if the clutch pedal32A is in the maximum operation position, the detector53outputs the predetermined first detected value as the detected value, if the clutch pedal32A is in the unoperated position P0, where no operation is performed, the detector53outputs the predetermined second detected value, which is a value separated from the first detected value by a certain value range, as the detected value, the threshold is a predetermined single value among a plurality of values that are present between the first detected value and the second detected value, and in accordance with the operation on the operation member45, the change unit40A changes the value of the threshold to a value closer to the first detected value than a default value is or a value closer to the second detected value than the default value is. According to this configuration, by changing the value of the threshold to the value closer to the first detected value than a default value is by the operation on the operation member45by the operator, the half-clutch stroke length can be made shorter than that before change. In addition, by changing the value of the threshold to the value closer to the second detected value than the default value is by the operation on the operation member45by the operator, the half-clutch stroke length can be made longer than that before change. The working vehicle1further includes the display device50, in which, as illustrated inFIG.5CandFIG.5D, the control device40causes the display device50to display the threshold that is set and causes the display device50to display the threshold to be changed by the change unit40A in accordance with the operation on the operation member45. According to this configuration, the threshold that is set can be checked on the display devices50. In addition, since the threshold to be changed by the change unit40A in accordance with the operation on the operation member45by the operator is displayed on the display devices50, the threshold to be changed can be checked on the display devices50when changing the threshold. The working vehicle1further includes the display device50, in which, as illustrated inFIG.5AandFIG.5B, the control device40causes the display device50to display, as a sensitivity of the clutch pedal32A, the threshold that is set, and causes the display device50to display, as the sensitivity of the clutch pedal32A, the threshold to be changed by the change unit40A in accordance with the operation on the operation member45. According to this configuration, the operator can grasp the sensitivity of the clutch pedal32A by viewing the sensitivity of the clutch pedal32A displayed on the display devices50. In addition, the operator can grasp the sensitivity of the clutch pedal32A to be changed in accordance with the operation on the operation member45by the operator. Thus, the operator can change the sensitivity of the clutch pedal32A intuitively. In addition, the operation member45is the dial switch45aprovided on the clutch lever32B (operation lever), and the change unit40A changes the value of the threshold to a different value in accordance with an operation on the dial switch45a. According to this configuration, the value of the threshold can be changed to a different value with a pitch in accordance with the operation on the dial switch45aby the operation on the dial switch45aby the operator. Thus, the half-clutch stroke length can be adjusted with a pitch in accordance with the operation on the dial switch45aby the operator. In addition, the operation member45is the second display device50B (display device) including the display panel50B1and the touch panel50B2that is disposed on a surface of the display panel50B1, and the change unit40A changes the value of the threshold to a different value in accordance with a touch operation on the touch panel50B2. According to this configuration, the value of the threshold can be changed to a different value in accordance with the touch operation by the operator. Thus, the half-clutch stroke length can be adjusted in accordance with the touch operation by the operator. The working vehicle1further includes: the brake operation member31; the brake device46capable of braking the traveling device7in accordance with an operation on the brake operation member31; and the switching unit43that selects whether the automatic switch control is valid or invalid, the automatic switch control being control for switching the traveling clutch5dfrom the connected state to the disconnected state, in which the control device40, if the automatic switch control is invalid, upon an operation on the brake operation member31, performs brake control for braking the traveling device7in accordance with the operation on the brake operation member31, and, if the automatic switch control is valid, upon an operation on the brake operation member31, performs the brake control and disconnection control for switching the traveling clutch5dfrom the connected state to the disconnected state, and, when the operation on the brake operation member31is released after the disconnection control, performs connection control for switching the traveling clutch5dfrom the disconnected state to the connected state through the half-clutch state by using the threshold whose value is changed by the change unit40A. According to this configuration, if the automatic switch control is valid, by the operation on the brake operation member31, the brake control and the disconnection control are performed, and thus, the traveling clutch5dcan be automatically switched from the connected state to the disconnected state, and the working vehicle1can be smoothly stopped without manually switching the traveling clutch5d. Furthermore, if the operation on the brake operation member31is released, the traveling clutch5dcan be switched from the disconnected state to the connected state through the half-clutch state using the changed threshold, and thus, the working vehicle1can be started at a clutch connection timing changed by the operator, realizing a start familiar with the operator's driving feeling. In addition, if the clutch pedal32A is in the maximum operation position, the detector53outputs the predetermined first detected value as the detected value, if the clutch pedal32A is in the unoperated position P0, where no operation is performed, the detector53outputs the predetermined second detected value, which is a value separated from the first detected value by a certain value range, as the detected value, the threshold is a predetermined single value among a plurality of values that are present between the first detected value and the second detected value, and in accordance with the operation on the operation member45, the change unit40A changes the value of the threshold to a value closer to the first detected value than a default value is. If the automatic switch control is valid, after an operation on the brake operation member31, upon the operation on the brake operation member31being released, the traveling clutch5dcan be switched from the disconnected state to the connected state through the half-clutch state using the changed threshold. Since the changed threshold is a shorter half-clutch stroke length, that is, the clutch connection timing is an earlier timing changed by the operator, the time for the traveling clutch5dto be brought into the half-clutch state from the disconnected state can be shortened, the working vehicle1can be started with the clutch connection timing shortened, and the work efficiency of the working vehicle1can be improved. The working vehicle1further includes the second operation member54that is different from the operation member45, in which if the second operation member54and the operation member45are operated, the change unit40A changes the value of the threshold to a different value in accordance with the operation on the operation member45, and, if the operation member45is operated in a state where the second operation member54is not operated, the change unit40A does not change the value of the threshold to a different value regardless of the operation on the operation member45. According to this configuration, only when the second operation member54and the operation member45are operated, the value of the threshold can be changed to a different value in accordance with the operation on the operation member45. Thus, the threshold can be prevented from being changed by an erroneous operation. The working vehicle1is a tractor including: the vehicle body3; and the coupler8that is provided for the vehicle body3and that couples a working device for working to the vehicle body3. According to this configuration, the tractor having the above special effects can be realized. The drive is the traveling device7that gives a propelling force to the vehicle body3, and the traveling clutch5d(clutch) is provided in the transmission5(transmission mechanism) and is displaceable to a connected state in which the power is transmitted to the traveling device, a disconnected state in which transmission of the power to the traveling device is disconnected, and a half-clutch state in which the power is slidably and partly transmitted to the traveling device. According to this configuration, by merely changing the value of the threshold to a different value by the operation on the operation member45by the operator, the operation position of the clutch pedal32A corresponding to the half-clutch state can be changed, and the tractor with high operability, which can be smoothly started regardless of a physique or experience of the operator, can be realized. Although the detector53employs the detection method such that the detected value decreases in accordance with the operation amount (depressed amount) of the clutch pedal32A in the above embodiment, the present invention is not limited to this. For example, the clutch-operation detection sensor53amay be a detection sensor whose detection method is such that the detected value increases in accordance with the operation amount (depressed amount) of the clutch pedal32A. In this case, if the detected value from the detector53(the clutch-operation detection sensor53a) corresponds with the predetermined threshold, the control device40brings the traveling clutch5dto the half-clutch state; if the detected value exceeds the threshold, the control device40brings the traveling clutch5dinto the disconnected state; if the detected value is less than the threshold, the control device40brings the traveling clutch5dinto the connected state. Although the operation member45(e.g., the dial switch45a) is provided on the clutch lever32B (operation lever) in the above embodiment, the present invention is not limited to this. For example, the operation member45may be provided on any of various operation levers (e.g., gear shift and multi-function operation lever) disposed around the operator's seat10. In addition, if the working vehicle1is a construction machine (construction vehicle) such as a loader working machine, the operation member45may be provided on a loader operation lever for operating a front loader. In addition, the operation member45may also be provided on a member other than the operation lever around the operator's seat10. Although the operation member45is the dial switch45ain the above embodiment, the present invention is not limited to this. For example, the operation member45may also be any of various operation switches such as a rotary switch, a button switch, and a slide switch. Although the half-clutch stroke length of the clutch pedal32A is adjusted in the above embodiment, the present invention is not limited to this. For example, the present invention is also applicable to adjustment of the half-clutch stroke length of a clutch pedal (POT clutch pedal) for operating the PTO clutch15. In addition, the storage unit40B may store names of a plurality of operators and changed sensitivities or changed values of the threshold voltage for each of the plurality of operators in association with one another, and upon the second display device50B receiving input of identification information (e.g., name, operator number, or password) of an operator, the control device40may read, from the storage unit40B, and set the changed sensitivity or changed value of the threshold voltage corresponding to the input identification information the operator. Accordingly, the single working vehicle1(tractor) can be shared by the plurality of operators, clutch operations can be performed by using the half-clutch stroke length corresponding to the changed sensitivity or changed value of the threshold voltage set by each operator, and the highly convenient working vehicle1(tractor) for the plurality of operators can be provided. While preferred embodiments of the present invention have been described above, it is to be understood that variations and modifications will be apparent to those skilled in the art without departing from the scope and spirit of the present invention. The scope of the present invention, therefore, is to be determined solely by the following claims. | 64,578 |
11859679 | DETAILED DESCRIPTION For example, in a control device for an exemplary torque transmission device, when a piston stroke amount of an actuator operated by energization reaches an indicated value, drive of the actuator and a PID control are stopped, and an integral term in the PID control is initialized. After that, the PID control is restarted when the piston stroke amount exceeds a predetermined threshold value or when a predetermined time has passed since the stop of the PID control. As a result, rapid convergence of overshoot and undershoot is attempted. However, in the control device, there is a possibility that a difference occurs between an output duty immediately after the control is restarted and an output duty immediately before the stop after convergence when the PID control is stopped and the integral term is initialized, and there is a possibility that variations in the load immediately after the control, that is, a stroke behavior may occur. For example, in the control device, when the duty of the integral term converges to the target with +10%, the duty immediately after restarting the control is output 10% lower than the original balance point. Further, when the duty of the integral term converges to the target at −10%, the duty immediately after restarting the control is output 10% higher than the original balance point, and the load response immediately after resuming control may deteriorate. The present disclosure provides a control device that stabilizes behavior of a torque transmission device immediately after feedback control is restarted. An exemplary embodiment of the present disclosure provides a control device that controls a torque transmission device. The torque transmission device includes an actuator that operates by being energized and a torque transmission portion that is switched to a transmission state or a non-transmission state by the actuator operating, and transmits a torque between a first transmission portion and a second transmission portion when the torque transmission portion is in the transmission state. The control device includes a target calculation unit, a mode determination unit, and a control unit. The target calculation unit calculates a target transmission torque that is a torque to be transmitted between the first transmission portion and the second transmission portion. The mode determination unit determines that an operating mode is an engagement mode when the target transmission torque increases over time, determine that the operating mode is a release mode when the target transmission torque decreases over time, and determine that the operating mode is a steady mode when the target transmission torque does not change over time. The control unit controls the actuator based on the operating mode determined by the mode determination unit. The control unit includes a feedback control unit, a gain setting unit, a duty calculation unit, a duty output unit, an energization control unit, and a feedback control adjustment unit. The feedback control unit performs feedback-control of the actuator based on the target transmission torque. The gain setting unit sets a gain used for the feedback-control by the feedback control unit. The duty calculation unit calculates a duty based on the gain. The duty output unit outputs the duty calculated by the duty calculation unit as an output duty. The energization control unit controls energization of the actuator based on the output duty output from the duty output unit. The feedback control adjustment unit shifts to a control stop mode that causes the feedback control unit to stop the feedback-control of the actuator when a predetermined stop condition is satisfied in a case where the mode determination unit determines that the operating mode is the steady mode. The feedback control adjustment unit stores an integral calculation value in the feedback-control immediately before the feedback control unit stops the feedback-control of the actuator when shifting to the control stop mode, and then restarts the feedback control unit performing the feedback-control of the actuator by using the integral calculation value stored when a predetermined restart condition is satisfied. In the exemplary embodiment of the present disclosure, it is possible to reduce the difference between the output duty of the torque transmission device immediately before the feedback control is stopped and the output duty immediately after the feedback control is restarted, thereby suppressing variations in the load behavior immediately after the feedback control is restarted. Therefore, the behavior of the torque transmission device immediately after the feedback control is restarted can be stabilized. Hereinafter, torque transmission devices and control devices according to multiple embodiments will be described with reference to the drawings. Elements that are substantially the same in the embodiments are denoted by the same reference signs and will not be described. (First Embodiment) A torque transmission device and a control device according to a first embodiment are illustrated inFIG.1. A torque transmission device1is, for example, a clutch device, is provided between an internal combustion engine and a transmission of a vehicle, and is used to allow or block transmission of a torque between the internal combustion engine and the transmission. A control device100is used to control the torque transmission device1. The torque transmission device1includes an actuator2and a clutch70serving as a “torque transmission portion”. The actuator2includes a housing10, an electric motor20, a speed reducer30, a rotational translation unit60, and a pressing unit81. The torque transmission device1includes an input shaft61as a “first transmission portion” and an output shaft62as a “second transmission portion”. The control device100is, for example, an electronic control unit, that is, an ECU, and is a small computer including a CPU as a calculation unit, a ROM, a RAM, and the like as storage units, and an I/O and the like as input and output units. Based on information such as signals from various sensors provided in parts of the vehicle, the control device100executes a calculation according to a program stored in the ROM or the like and controls operation of various devices and machines of the vehicle. In this way, the control device100executes the program stored in a non-transitory tangible storage medium. By executing the program, a method corresponding to the program is executed. The control device100can control operation of the internal combustion engine and the like based on the information such as the signals from various sensors. The control device100can control operation of the electric motor20, which will be described later. The input shaft61is connected to, for example, a drive shaft (not illustrated) of the internal combustion engine, and is rotatable together with the drive shaft. That is, a torque from the drive shaft is input to the input shaft61. The vehicle equipped with the internal combustion engine is provided with a fixing flange3(seeFIG.1). The fixing flange3is formed in a tubular shape, and is fixed to, for example, an engine compartment of the vehicle. The input shaft61is supported by the fixing flange3via, for example, a bearing. The housing10is provided between an inner peripheral wall of an end portion of the fixing flange3and an outer peripheral wall of the input shaft61. The housing10includes a housing inner cylinder portion11, a housing plate portion12, a housing outer cylinder portion13, and the like. The housing inner cylinder portion11is formed in a substantially cylindrical shape. The housing plate portion12is formed in an annular plate shape in a manner of extending radially outward from an end portion of the housing inner cylinder portion11. The housing outer cylinder portion13is formed in a substantially cylindrical shape in a manner of extending from an outer edge portion of the housing plate portion12to the same side as the housing inner cylinder portion11. Here, the housing inner cylinder portion11, the housing plate portion12, and the housing outer cylinder portion13are integrally formed of, for example, metal. The housing10is fixed to the fixing flange3such that outer walls of the housing plate portion12and the housing outer cylinder portion13are in contact with a wall surface of the fixing flange3(seeFIG.1). The housing10is fixed to the fixing flange3by a bolt or the like (not illustrated). Here, the housing10is provided coaxially with the fixing flange3and the input shaft61. The electric motor20is provided, for example, among the housing inner cylinder portion11, the housing plate portion12, and the housing outer cylinder portion13. The electric motor20includes a stator and a rotor (not illustrated), and can output a torque from the rotor by being energized. The control device100can control the operation of the electric motor20by controlling electric power to be supplied to the electric motor20. In the present embodiment, the torque transmission device1includes a rotation angle sensor5. The rotation angle sensor5is provided, for example, between the electric motor20and the housing plate portion12. The rotation angle sensor5detects a rotation angle of the electric motor20and outputs a signal corresponding to the rotation angle to the control device100. Accordingly, the control device100can detect the rotation angle, a rotation speed, and the like of the electric motor20based on the signal from the rotation angle sensor5. The speed reducer30is provided, for example, on a side opposite to the housing plate portion12with respect to the electric motor20between the housing inner cylinder portion11and the housing outer cylinder portion13. A torque of the electric motor20is input to the speed reducer30. The speed reducer30outputs the torque of the electric motor20at a reduced speed. The rotational translation unit60includes a rotation portion40and a translation portion50. The rotation portion40is formed in, for example, an annular shape, and is provided on a side opposite to the electric motor20with respect to the speed reducer30between the housing inner cylinder portion11and the housing outer cylinder portion13. The torque of the electric motor20decelerated by the speed reducer30is input to the rotation portion40. When the torque is received from the speed reducer30, the rotation portion40rotates relative to the housing10. The translation portion50is formed in, for example, a tubular shape, and is provided on a side opposite to the speed reducer30with respect to the rotation portion40on a radially outer side of the housing inner cylinder portion11. When the rotation portion40rotates relative to the housing10, the translation portion50moves relative to the housing10in an axial direction. In the present embodiment, the torque transmission device1includes a return spring55and a C ring57. The return spring55is provided, for example, on a side opposite to the rotation portion40with respect to the translation portion50on the radially outer side of the housing inner cylinder portion11. The C ring57is provided on, for example, an outer peripheral wall of the housing inner cylinder portion11in a manner of being positioned on a side opposite to the translation portion50with respect to the return spring55. One end of the return spring55is in contact with the translation portion50, and the other end is in contact with the C ring57. The return spring55biases the translation portion50toward the rotation portion40. The output shaft62includes a shaft portion621, a plate portion622, a cylinder portion623, and a friction plate624(seeFIG.1). The shaft portion621is formed in a substantially cylindrical shape. The plate portion622is integrally provided with the shaft portion621to extend radially outward from one end of the shaft portion621in an annular plate shape. The cylinder portion623is integrally provided with the plate portion622to extend in a substantially cylindrical shape from an outer edge portion of the plate portion622toward a side opposite to the shaft portion621. The friction plate624is formed in a substantially annular plate shape, and is provided on an end surface of the plate portion622on the side of the cylinder portion623. The friction plate624is not relatively rotatable with respect to the plate portion622. An end portion of the input shaft61passes through the inside of the housing inner cylinder portion11and is positioned on a side opposite to the rotation portion40with respect to the translation portion50. The output shaft62is provided coaxially with the input shaft61on a side opposite to the fixing flange3with respect to the housing10, that is, on a side opposite to the rotation portion40with respect to the translation portion50. The output shaft62is supported by the input shaft61via, for example, a bearing. The input shaft61and the output shaft62are relatively rotatable with respect to the housing10. The clutch70is provided between the input shaft61and the output shaft62inside the cylinder portion623. The clutch70includes inner friction plates71, outer friction plates72, and a locking portion701. The multiple inner friction plates71are each formed in a substantially annular plate shape, and are aligned in the axial direction between the input shaft61and the cylinder portion623of the output shaft62. The inner friction plates71are provided such that inner edge portions thereof are spline-coupled to the outer peripheral wall of the input shaft61. Therefore, the inner friction plates71are not relatively rotatable with respect to the input shaft61and are capable of relatively moving with respect to the input shaft61in the axial direction. The multiple outer friction plates72are each formed in a substantially annular plate shape, and are aligned in the axial direction between the input shaft61and the cylinder portion623of the output shaft62. Here, the inner friction plates71and the outer friction plates72are alternately arranged in the axial direction of the input shaft61. The outer friction plates72are provided such that outer edge portions thereof are spline-coupled to an inner peripheral wall of the cylinder portion623of the output shaft62. Therefore, the outer friction plates72are not relatively rotatable with respect to the output shaft62and are capable of relatively moving with respect to the output shaft62in the axial direction. Among the multiple outer friction plates72, the outer friction plate72positioned closest to the friction plate624is capable of coming into contact with the friction plate624. The locking portion701is formed in a substantially annular shape, and is provided such that an outer edge portion is fitted into the inner peripheral wall of the cylinder portion623of the output shaft62. The locking portion701can lock an outer edge portion of the outer friction plate72positioned closest to the translation portion50among the multiple outer friction plates72. Therefore, the multiple outer friction plates72and the multiple inner friction plates71are prevented from coming off from the inside of the cylinder portion623. A distance between the locking portion701and the friction plate624is larger than a sum of plate thicknesses of the multiple outer friction plates72and the multiple inner friction plates71. In an engaged state in which the multiple inner friction plates71and the multiple outer friction plates72are in contact with each other, that is, are engaged with each other, a frictional force is generated between the inner friction plates71and the outer friction plates72, and relative rotation between the inner friction plates71and the outer friction plates72is restricted according to a magnitude of the frictional force. On the other hand, in a disengaged state in which the multiple inner friction plates71and the multiple outer friction plates72are separated from each other, that is, are not engaged with each other, no frictional force is generated between the inner friction plates71and the outer friction plates72, and the relative rotation between the inner friction plates71and the outer friction plates72is not restricted. Here, the “engaged state” corresponds to a “transmission state”, and the “disengaged state” corresponds to a “non-transmission state”. When the clutch70is in the engaged state, the torque input to the input shaft61is transmitted to the output shaft62via the clutch70. On the other hand, when the clutch70is in the disengaged state, the torque input to the input shaft61is not transmitted to the output shaft62. In this way, the clutch70serving as the “torque transmission portion” transmits the torque between the input shaft61and the output shaft62. The clutch70allows transmission of the torque between the input shaft61and the output shaft62in the engaged state in which the clutch70is engaged, and cuts off the transmission of the torque between the input shaft61and the output shaft62in the disengaged state in which the clutch70is not engaged. In the present embodiment, the torque transmission device1is a so-called normally open type torque transmission device that is normally in a disengaged state when the electric motor20is not energized. The pressing unit81includes two disk springs. The two disk springs are provided such that inner edge portions thereof are positioned in a step portion501formed on an outer peripheral wall of an end portion of the translation portion50on a clutch70side in a state in which the disk springs overlap each other in the axial direction. The pressing unit81is elastically deformable in the axial direction. When the electric motor20is not energized, a distance between the rotation portion40and the translation portion50is relatively small, and a gap is formed between an outer edge portion of the pressing unit81and the clutch70(seeFIG.1). Therefore, the clutch70is in the disengaged state, and the transmission of torque between the input shaft61and the output shaft62is blocked. Here, when electric power is supplied to the electric motor20under the control of the control device100, the electric motor20rotates, the torque is output from the speed reducer30, and the rotation portion40relatively rotates with respect to the housing10. Accordingly, the translation portion50relatively moves with respect to the housing10in the axial direction, that is, moves toward the clutch70while compressing the return spring55. Accordingly, the pressing unit81moves toward the clutch70. When the pressing unit81moves toward the clutch70due to the movement of the translation portion50in the axial direction, the gap between the pressing unit81and the clutch70becomes small, and the outer edge portion of the pressing unit81comes into contact with the outer friction plate72of the clutch70. When the translation portion50further moves in the axial direction after the pressing unit81comes into contact with the clutch70, the pressing unit81presses the outer friction plate72toward the friction plate624while being elastically deformed in the axial direction. Accordingly, the multiple inner friction plates71and the multiple outer friction plates72are engaged with each other, and the clutch70is brought into the engaged state. Therefore, the transmission of the torque between the input shaft61and the output shaft62is allowed. When a clutch transmission torque reaches a clutch required torque capacity, the control device100stops the rotation of the electric motor20. Accordingly, the clutch70is brought into an engagement maintaining state in which the clutch transmission torque is maintained at the clutch required torque capacity. In this way, by the torque of the electric motor20, the pressing unit81can move in the axial direction and press the clutch70to switch the state of the clutch70to the engaged state or the disengaged state. In the output shaft62, an end portion of the shaft portion621opposite to the plate portion622is connected to an input shaft of the transmission (not illustrated), and the output shaft62is rotatable together with the input shaft. That is, the torque output from the output shaft62is input to the input shaft of the transmission. The torque input to the transmission is changed in speed by the transmission, and is output to driving wheels of the vehicle as a drive torque. Accordingly, the vehicle travels. In the present embodiment, the torque transmission device1includes a temperature sensor6. The temperature sensor6is provided on, for example, the cylinder portion623of the output shaft62. The temperature sensor6detects temperatures of the clutch70and lubricant of the clutch70, and outputs signals corresponding to the temperatures to the control device100. Accordingly, the control device100can detect the temperatures of the clutch70and the lubricant based on the signals from the temperature sensor6. As illustrated inFIG.1, according to the present embodiment, the control device100includes the actuator2that operates by being energized and the clutch70serving as the “torque transmission portion” that is switched to the transmission state or the non-transmission state by the operation of the actuator2, and controls the torque transmission device1that transmits the torque between the input shaft61and the output shaft62when the clutch70is in the transmission state. The control device100includes a target calculation unit111, a mode determination unit112, and a control unit113as conceptual functional units. The target calculation unit111calculates a target transmission torque that is a torque to be transmitted between the input shaft61and the output shaft62. The mode determination unit112determines that an operating mode is an engagement mode when the target transmission torque increases over time, determines that the operating mode is a release mode when the target transmission torque decreases over time, and determines that the operating mode is a steady mode when the target transmission torque does not change over time (seeFIG.2). The control unit113controls the actuator2based on the mode determined by the mode determination unit112. Here, the “engagement mode” is a mode in which the pressing unit81is moved toward the clutch70by the actuator2to bring the clutch70into the engaged state, that is, to engage the clutch70. The “release mode” is a mode in which the pressing unit81is moved to a side opposite to the clutch70by the actuator2to bring the clutch70into the disengaged state, that is, to release the clutch70. The “steady mode” is a mode in which the pressing unit81is held at a predetermined position to maintain the state of the clutch70in the engaged state or the disengaged state. The control unit113includes a feedback control unit121, a gain setting unit122, a duty calculation unit123, a duty output unit124, an energization control unit125, and a feedback control adjustment unit126. The feedback control unit121feedback-controls the actuator2based on the target transmission torque. The gain setting unit122sets a gain used for feedback control by the feedback control unit121. The duty calculation unit123can calculate the duty based on the gain. The duty output unit124outputs the output duty calculated by the duty calculation unit123. The energization control unit125controls energization of the actuator2based on the output duty output from the duty output unit124. In the present specification, the term “duty” means a “duty ratio” obtained by dividing a pulse width of a signal by a pulse period (cycle). As illustrated inFIG.3, a PID controller includes the feedback control unit121, the gain setting unit122, the duty calculation unit123, the duty output unit124, and a feedback control adjustment unit126. In the present embodiment, the feedback control unit121PID-controls the electric motor20of the actuator2based on the target transmission torque and the rotation angle of the electric motor20detected by the rotation angle sensor5. In the present embodiment, a feedback circuit is implemented by software. Specifically, a target clutch transmission load, which is a load to be transmitted by the clutch70, is calculated based on the target transmission torque. A target stroke, which is a target movement amount of the pressing unit81in the axial direction, is calculated based on the target clutch transmission load. A target rotation angle of the electric motor20is calculated based on the target stroke, and a rotation angle deviation which is a deviation between the target rotation angle and the rotation angle of the electric motor20detected by the rotation angle sensor5is input to the feedback control unit121. The duty calculation unit123calculates the duty based on the gain set by the gain setting unit122. The duty output unit124outputs the output duty calculated by the duty calculation unit123to the energization control unit125. The feedback control adjustment unit126shifts to a control stop mode that causes the feedback control unit121to stop feedback-controlling the actuator2when a predetermined stop condition is satisfied in a case where the mode determination unit112determines that the operating mode is the steady mode. Here, the predetermined stop condition may be defined as a case where “a time count starts when a deviation between an actual control value that is an actual control amount of the actuator2and a target value becomes within a threshold value, and then it is determined, by the time count, that a predetermined time has passed.” The feedback control adjustment unit126stores an integral calculation value in feedback-controlling immediately before the feedback control unit121stops feedback-controlling the actuator2when shifting to the control stop mode, and then restarts the feedback control unit121feedback-controlling the actuator2by using the integral calculation value stored when a predetermined restart condition is satisfied. Here, the predetermined restart condition may be defined as a case where “the mode determination unit112, in the control stop mode, determines that the steady mode shifts to the engagement mode or the release mode.” A series of pieces of processing related to the control of the actuator2by the control device100are illustrated inFIG.4. S100of the series of pieces of processing illustrated inFIG.4is started when the mode determination unit112determines that the mode is the steady mode. In S101, the feedback control adjustment unit126determines whether or not “the target rotation angle is the same value and the rotation angle deviation is within the threshold value A1”. Specifically, the feedback control adjustment unit126determines whether or not the target rotation angle is the same value as in the previous processing, and the rotation angle deviation, that is, the absolute value of the difference between the rotation angle θrefnof the electric motor20and the target rotation angle θrefn−1is within the threshold value A1. When the feedback control adjustment unit126determines that “the target rotation angle is the same value and the rotation angle deviation is within the threshold value A1” (S101: YES), the processing proceeds to S102. On the other hand, if the feedback control adjustment unit126determines that “the target rotation angle is not the same value or the rotation angle deviation is not within the threshold value A1” (S101: NO), the processing proceeds to S111. It should be noted that whether or not “the target rotation angle is the same value and the rotation angle deviation is within the threshold value A1” is the same meaning of a part of the predetermined stop condition, that is, whether or not “the deviation between the actual control amount of the actuator2and the target value becomes within a threshold value”. In S102, the feedback control adjustment unit126determines whether or not it has continued for a predetermined time T1 (s) or longer. When the feedback control adjustment unit126determines that it has continued for the predetermined time T1 or longer (S102: YES), the processing proceeds to S103. On the other hand, when the feedback control adjustment unit126determines that it has not continued for the predetermined time T1 or longer (S102: NO), the processing returns to S101. In S103, the feedback control adjustment unit126stores an integral calculation value X at that time, that is, immediately before the PID control stops. After S103, the processing proceeds to S104. In S104, the feedback control unit121stops the feedback control of the actuator2. After S104, the processing proceeds to S105. In S105, the feedback control adjustment unit126determines whether “the target rotation angle has changed or the rotation angle deviation has become greater than the threshold value A1”. Specifically, the feedback control adjustment unit126determines whether or not the target rotation angle has changed from the previous processing or the rotation angle deviation, that is, the absolute value of the difference between the rotation angle θrefnof the electric motor20and the target rotation angle θrefn−1has become greater than the threshold value A1. When the feedback control adjustment unit126determines that “the target rotation angle has changed or the rotation angle deviation has become greater than the threshold value A1” (S105: YES), the processing proceeds to S106. On the other hand, when the feedback control adjustment unit126determines that “the target rotation angle has not changed and the rotation angle deviation has not become greater than the threshold value A1” (S105: NO), the processing returns to S105. It should be noted that whether or not “the target rotation angle has changed or the rotation angle deviation has become greater than the threshold value A1” is the same meaning of a part of the predetermined stop condition, that is, whether or not “the mode determination unit112determines that the steady mode shifts to the engagement mode or the release mode.” In S106, the feedback control unit121restarts the feedback control, that is, the PID control of the actuator2using the integral calculation value immediately before the PID control is stopped, that is, the integral calculation value stored by the feedback control adjustment unit126in S103as an initial value. After that, the processing exits S100of the series of pieces of processing. In S111, the feedback control unit121continues the normal PID control of the actuator2, that is, the feedback control. After that, the processing exits S100of the series of pieces of processing. After exiting S100of the series of pieces of processing, when the mode determination unit112determines that the mode is the steady mode, S100of the series of pieces of processing is restarted. An operation example of the control device100is illustrated inFIG.5. When a target clutch transmission load changes to the increasing side at time t1, the mode determination unit112determines that the mode is the engagement mode, and the feedback control unit121starts the normal PID control of the actuator2, that is, the feedback control. Therefore, after time t1, the duty calculated based on the gain is output from the duty output unit124as the output duty. As a result, the actual load, which is the actual transmission load of the clutch70, changes so as to approach the target clutch transmission load. Since the target clutch transmission load does not change after time t1, the mode determination unit112determines that the mode is the steady mode. As a result, S100of the series of pieces of processing described above is started. At time t2, the rotation angle deviation converges within the threshold value A1, and at time t3 after a predetermined time T1 (s) has elapsed from time t2, the control shifts to the control stop mode. The feedback control adjustment unit126stores the integral calculation value X immediately before shifting to the control stop mode, and stops the power supply to the actuator2, that is, cuts the power supply. As a result, the feedback control of the actuator2by the feedback control unit121is stopped. In the present embodiment, even when the power supply to the actuator2is stopped in the control stop mode, the relative positions of the rotation portion40and the translation portion50with respect to the housing10and the axial relative position, that is, the stroke of the pressing unit81with respect to the housing10are maintained. Therefore, the state of the clutch70is maintained. When the target clutch transmission load changes to the increasing side at time t4, the mode determination unit112determines that the steady mode has shifted to the engagement mode, and the feedback control unit121restarts the feedback control of the actuator2. Here, the feedback control unit121restarts the feedback control of the actuator2using the integral calculation value X immediately before the PID control is stopped, that is, the integral calculation value X stored at time t3 as an initial value. Therefore, after time t4, the duty calculated based on the gain is output from the duty output unit124as the output duty. As a result, the actual load, which is the actual transmission load of the clutch70, changes so as to follow the target clutch transmission load. Since the target clutch transmission load does not change after time t5, the mode determination unit112determines that the mode is the steady mode. As a result, S100of the series of pieces of processing described above is started. At time t6, the rotation angle deviation converges within the threshold value A1, and at time t7 after a predetermined time T1 (s) has elapsed from time t6, the control shifts to the control stop mode. The feedback control adjustment unit126stores the integral calculation value X immediately before shifting to the control stop mode, and stops the power supply to the actuator2. As a result, the feedback control of the actuator2by the feedback control unit121is stopped. When the target clutch transmission load changes to the increasing side at time t8, the mode determination unit112determines that the steady mode has shifted to the engagement mode, and the feedback control unit121restarts the feedback control of the actuator2. Here, the feedback control unit121restarts the feedback control of the actuator2using the integral calculation value X immediately before the PID control is stopped, that is, the integral calculation value X stored at time t7 as an initial value. Therefore, after time t8, the duty calculated based on the gain is output from the duty output unit124as the output duty. As a result, the actual load, which is the actual transmission load of the clutch70, changes so as to approach the target clutch transmission load. Since the target clutch transmission load does not change after time t8, the mode determination unit112determines that the mode is the steady mode. As a result, S100of the series of pieces of processing described above is started. At time t9, the rotation angle deviation converges within the threshold value A1, and at time t10 after a predetermined time T1 (s) has elapsed from time t9, the control shifts to the control stop mode. The feedback control adjustment unit126stores the integral calculation value X immediately before shifting to the control stop mode, and stops the power supply to the actuator2. As a result, the feedback control of the actuator2by the feedback control unit121is stopped. When the target clutch transmission load changes to the decreasing side at time t11, the mode determination unit112determines that the steady mode has shifted to the release mode, and the feedback control unit121restarts the feedback control of the actuator2. Here, the feedback control unit121restarts the feedback control of the actuator2using the integral calculation value X immediately before the PID control is stopped, that is, the integral calculation value X stored at time t10 as an initial value. Therefore, after time t11, the duty calculated based on the gain is output from the duty output unit124as the output duty. As a result, the actual load, which is the actual transmission load of the clutch70, changes so as to approach the target clutch transmission load. Since the target clutch transmission load does not change after time t11, the mode determination unit112determines that the mode is the steady mode. As a result, S100of the series of pieces of processing described above is started. At time t12, the rotation angle deviation converges within the threshold value A1, and at time t13 after a predetermined time T1 (s) has elapsed from time t12, the control shifts to the control stop mode. The feedback control adjustment unit126stores the integral calculation value X immediately before shifting to the control stop mode, and stops the power supply to the actuator2. As a result, the feedback control of the actuator2by the feedback control unit121is stopped. When the target clutch transmission load changes to the decreasing side at time t14, the mode determination unit112determines that the steady mode has shifted to the release mode, and the feedback control unit121restarts the feedback control of the actuator2. Here, the feedback control unit121restarts the feedback control of the actuator2using the integral calculation value X immediately before the PID control is stopped, that is, the integral calculation value X stored at time t13 as an initial value. Therefore, after time t14, the duty calculated based on the gain is output from the duty output unit124as the output duty. As a result, the actual load, which is the actual transmission load of the clutch70, changes so as to follow the target clutch transmission load. Since the target clutch transmission load does not change after time t15, the mode determination unit112determines that the mode is the steady mode. As a result, S100of the series of pieces of processing described above is started. At time t16, the rotation angle deviation converges within the threshold value A1, and at time t17 after a predetermined time T1 (s) has elapsed from time t16, the control shifts to the control stop mode. The feedback control adjustment unit126stores the integral calculation value X immediately before shifting to the control stop mode, and stops the power supply to the actuator2. As a result, the feedback control of the actuator2by the feedback control unit121is stopped. When the target clutch transmission load changes to the decreasing side at time t18, the mode determination unit112determines that the steady mode has shifted to the release mode, and the feedback control unit121restarts the feedback control of the actuator2. Here, the feedback control unit121restarts the feedback control of the actuator2using the integral calculation value X immediately before the PID control is stopped, that is, the integral calculation value X stored at time t17 as an initial value. Therefore, after time t18, the duty calculated based on the gain is output from the duty output unit124as the output duty. As a result, the actual load, which is the actual transmission load of the clutch70, changes so as to approach the target clutch transmission load. Since the target clutch transmission load does not change after time t18, the mode determination unit112determines that the mode is the steady mode. As a result, S100of the series of pieces of processing described above is started. At time t19, the rotation angle deviation converges within the threshold value A1, and at time t20 after a predetermined time T1 (s) has elapsed from time t19, the control shifts to the control stop mode. The feedback control adjustment unit126stores the integral calculation value X immediately before shifting to the control stop mode, and stops the power supply to the actuator2. As a result, the feedback control of the actuator2by the feedback control unit121is stopped. Times t1, t4, t5, t8, t11, t14, t15, and t18 are timings at which the target is updated. Further, times t2, t6, t9, t12, t16, and t19 are timings at which the rotation angle deviation converges within the threshold value A1 in the steady state. Further, times t3, t7, t10, t13, t17, and t20 are timings at which a state in which the rotation angle deviation is within the threshold value A1 in the steady state continues for T1 (s), that is, timings for shifting to the control stop mode. In the control stop mode (time t3 to t4, t7 to t8, t10 to t11, t13 to t14, t17 to t18), the energization control unit125, without stopping stop the power supply to the actuator2, may reduce an amount of the power supply to the actuator2to maintain a predetermined amount of the power supply (see the three-dot chain line inFIG.5). In this case, in the control stop mode, the rotation portion40and the translation portion50with respect to the housing10and the axial relative position, that is, the stroke of the pressing unit81with respect to the housing10can be reliably maintained. Therefore, the state of the clutch70can be reliably maintained. Another operation example of the control device100is illustrated inFIG.6. When a target clutch transmission load changes to the increasing side at time t1, the mode determination unit112determines that the mode is the engagement mode, and the feedback control unit121starts the feedback control of the actuator2. Therefore, after time t1, the duty calculated based on the gain is output from the duty output unit124as the output duty. As a result, the actual load, which is the actual transmission load of the clutch70, changes so as to approach the target clutch transmission load. Since the target clutch transmission load does not change after time t1, the mode determination unit112determines that the mode is the steady mode. As a result, S100of the series of pieces of processing described above is started. At time t2, the rotation angle deviation converges within the threshold value A1, and at time t3 after a predetermined time T1 (s) has elapsed from time t2, the control shifts to the control stop mode. The feedback control adjustment unit126stores the integral calculation value X1 immediately before shifting to the control stop mode, and stops the power supply to the actuator2, that is, cuts the power supply. As a result, the feedback control of the actuator2by the feedback control unit121is stopped. When a disturbance is applied at time t4, and the deviation between the actual control amount (actual load) and target value (target clutch transmission load) of the actuator2exceeds the threshold value A1 at time t5, the feedback control unit121restarts the feedback control of the actuator2. Here, the feedback control unit121restarts the feedback control of the actuator2using the integral calculation value X1 immediately before the feedback control is stopped, that is, the integral calculation value X1 stored at time t3 as an initial value. Therefore, after time t5, the duty calculated based on the gain is output from the duty output unit124as the output duty. As a result, the actual load, which is the actual transmission load of the clutch70, changes so as to follow the target clutch transmission load. Note that the duty output from the duty output unit124as the output duty is calculated based on the integral calculation value X1 at time t3 and the proportional calculation value Ya at time t5. At time t6, the rotation angle deviation converges within the threshold value A1, and at time t7 after a predetermined time T1 (s) has elapsed from time t6, the control shifts to the control stop mode. The feedback control adjustment unit126stores the integral calculation value X2 immediately before shifting to the control stop mode, and stops the power supply to the actuator2. As a result, the feedback control of the actuator2by the feedback control unit121is stopped. When the target clutch transmission load changes to the decreasing side at time t8, the mode determination unit112determines that the steady mode has shifted to the release mode, and the feedback control unit121restarts the feedback control of the actuator2. Here, the feedback control unit121restarts the feedback control of the actuator2using the integral calculation value X2 immediately before the feedback control is stopped, that is, the integral calculation value X2 stored at time t7 as an initial value. Therefore, after time t8, the duty calculated based on the gain is output from the duty output unit124as the output duty. As a result, the actual load, which is the actual transmission load of the clutch70, changes so as to approach the target clutch transmission load. Note that the duty output from the duty output unit124as the output duty is calculated based on the integral calculation value X2 at time t7 and the proportional calculation value Yb at time t8. Since the target clutch transmission load does not change after time t8, the mode determination unit112determines that the mode is the steady mode. As a result, S100of the series of pieces of processing described above is started. At time t9, the rotation angle deviation converges within the threshold value A1, and at time t10 after a predetermined time T1 (s) has elapsed from time t9, the control shifts to the control stop mode. The feedback control adjustment unit126stores the integral calculation value X3 immediately before shifting to the control stop mode, and stops the power supply to the actuator2. As a result, the feedback control of the actuator2by the feedback control unit121is stopped. Note that time t4 indicates the timing when the disturbance is applied, and the target is not changed at this time. Also, times t1 and t8 indicate timings when the target is updated. Further, times t2, t6, and t9 are timings at which the rotation angle deviation converges within the threshold value A1 in the steady state. Further, times t3, t7, and t10 are timings at which a state in which the rotation angle deviation is within the threshold value A1 in the steady state continues for T1 (s), that is, timings for shifting to the control stop mode. In a normal PI(D) control, an integral term, that is, an integral calculation value monotonically increases or decreases due to minute deviation after convergence (times t3 to t4, t7 to t8, and after t10). The feedback control adjustment unit126may change the threshold value A1 based on the target transmission torque or the temperature of the clutch70. Further, the feedback control adjustment unit126may change the predetermined time T1 based on the change width of the target transmission torque or the temperature of the clutch70. Another operation example of the control device100according to the present embodiment is illustrated inFIG.7. In this embodiment (see the solid line inFIG.7), the feedback control is restarted at time t4 using an integral value stored at time t3 immediately before the feedback control was stopped. Therefore, after time t4, the actual load, which is the actual transmission load of the clutch70, changes so as to quickly approach the target clutch transmission load. On the other hand, in a case of a system without a control stop mode (see the dashed-dotted line inFIG.7), after time t3, the integral calculation value accumulates (see the lower part ofFIG.7), after time t4, the movement slows down due to integral saturation (see the upper part ofFIG.7), and the actual load of the clutch70approaches the target clutch transmission load more slowly. In a case of a system that resets the integral calculation value (see the two-dot chain line inFIG.7), after time t4, start of movement fluctuates (see the upper part ofFIG.7) and the actual load of the clutch70converges to the target clutch transmission load more slowly. Times t1 and t4 indicate timings when the target is updated. Further, time t2 is timing at which the rotation angle deviation converges within the threshold value A1 in the steady state. Further, time t3 is timing at which a state in which the rotation angle deviation is within the threshold value A1 in the steady state continues for T1 (s), that is, timings for shifting to the control stop mode. In this way, the present embodiment is particularly advantageous in terms of the stability of the behavior of the actual load after the feedback control is restarted, especially for a system that does not have a control stop mode and a system that resets the integral calculation value. As described above, in the present embodiment, the feedback control adjustment unit126shifts to a control stop mode that causes the feedback control unit121to stop feedback-controlling the actuator2when a predetermined stop condition is satisfied in a case where the mode determination unit112determines that the operating mode is the steady mode. The feedback control adjustment unit126stores an integral calculation value in feedback-controlling immediately before the feedback control unit121stops feedback-controlling the actuator2when shifting to the control stop mode, and then restarts the feedback control unit121feedback-controlling the actuator2by using the integral calculation value stored when a predetermined restart condition is satisfied. Therefore, it is possible to reduce the difference between the output duty of the torque transmission device1immediately before the feedback control is stopped and the output duty immediately after the feedback control is restarted, thereby suppressing variations in the load behavior immediately after the feedback control is restarted. Therefore, the behavior of the torque transmission device1immediately after the feedback control is restarted can be stabilized. In the present embodiment, in the case where the mode determination unit112determines that the operating mode is the steady mode, the feedback control adjustment unit126starts the time count when the deviation between the actual control value that is the actual control amount of the actuator2and the target value becomes within the threshold value. In addition, in the present embodiment, the feedback control adjustment unit126shifts to the control stop mode when determining, by the time count, that a predetermined time has passed. The above shows specific examples of the predetermined stop conditions. Further, in the present embodiment, when the mode determination unit126, in the control stop mode, that is, in a case where the feedback control of the actuator2is stopped, determines that the mode determination unit112shifts the steady mode to the engagement mode or the release mode, the feedback control adjustment unit126restarts the feedback control unit121feedback-controlling the actuator2. The above shows a specific example of the predetermined restart condition. In the present embodiment, the feedback control adjustment unit126restarts the feedback control unit121feedback-controlling the actuator2when a deviation between an actual control value that is an actual control amount of the actuator2and a target value exceeds a threshold value in the control stop mode, that is in a case where the feedback control of the actuator2is stopped, and then shifts to the control stop mode when a state where the deviation is within the threshold value continues for a predetermined time. Therefore, even when the control stop mode is canceled due to a disturbance or the like, it is possible to shift to the control stop mode again when a predetermined restart condition is satisfied. As a result, the power saving state can be continued. In the present embodiment, the duty output is updated at the timing of the cycle of the feedback control. That is, in the present embodiment, the duty output unit124outputs the output duty in the same cycle as the calculation cycle of the feedback control unit121. Therefore, the processing timing for shifting to the control stop mode can be shortened, and the responsiveness can be improved. Further, in this embodiment, the feedback control adjustment unit126can change the threshold value based on the target transmission torque or the temperature of the clutch70. Further, in the present embodiment, the feedback control adjustment unit126can change the predetermined time based on the change width of the target transmission torque or the temperature of the clutch70. Therefore, it is possible to achieve the optimum transmission performance such as the responsiveness and stability according to the load or the temperature. Further, in the present embodiment, the energization control unit125can reduce the amount of the power supply to the actuator2to maintain the predetermined amount of the power supply without stopping the power supply to the actuator2. Therefore, the state of the clutch70can be reliably maintained in the control stop mode. In the present embodiment, the actuator2includes the electric motor20that outputs a torque, and the pressing unit81that can move in the axial direction by the torque of the electric motor20and press the clutch70to switch the state of the clutch70to the transmission state or the non-transmission state. The feedback control unit121feedback-controls the actuator2based on the target transmission torque and the rotation angle of the electric motor20. Therefore, it is possible to cope with various controls regardless of a control target. In the present embodiment, the torque transmission portion is the clutch70that is switched to the engaged state or the disengaged state by a pressing force output from the actuator2. In the present embodiment, the clutch70is of a type that connects and disconnects the input shaft61and the output shaft62, of which one and the other rotate with respect to the fixing flange3or the like serving as “another member”, and that transmits power. Here, the clutch70is of a friction type that can be engaged by friction of the friction plates (the inner friction plates71and the outer friction plates72). In the present embodiment, the clutch70is a wet clutch that can be lubricated by lubricant such as ATF. In the present embodiment, the clutch70is a multi-disc clutch including multiple friction plates (the inner friction plates71and the outer friction plates72). (Second Embodiment) A control device according to a second embodiment will be described with reference toFIG.8. The second embodiment is different from the first embodiment in a method for controlling the actuator2by the control device100. In the present embodiment, the duty switching timing when the operating mode is changed is a timing faster than the cycle of the feedback control. An operation example of the control device100is illustrated inFIG.8. When a target clutch transmission load changes to the increasing side at time t1, the mode determination unit112determines that the mode is the engagement mode, and the feedback control unit121starts the normal PID control of the actuator2, that is, the feedback control. Therefore, after time t1, the duty calculated based on the gain is output from the duty output unit124as the output duty. As a result, in the present embodiment, the actual load, which is the actual transmission load of the clutch70, changes so as to approach the target clutch transmission load (see the one-dot chain line inFIG.8). Since the target clutch transmission load does not change after time t1, the mode determination unit112determines that the mode is the steady mode. As a result, S100of the series of pieces of processing described above is started. At time t4, the rotation angle deviation converges within the threshold value A1, and at time t7, which is after time t6, after a predetermined time T1 (s) has elapsed from time t4, the control shifts to the control stop mode. The feedback control adjustment unit126stores the integral calculation value X immediately before shifting to the control stop mode, and stops the power supply to the actuator2, that is, cuts the power supply. As a result, the feedback control of the actuator2by the feedback control unit121is stopped. Times t2 and t7 are times corresponding to times shorter than the calculation cycle of the feedback control unit121. Times t3 and t9 are times corresponding to the calculation cycle of the feedback control unit121. Next, an operation example in which the duty switching timing at the time of operation mode change is the same timing as the cycle of feedback control will be described. When a target clutch transmission load changes to the increasing side at time t3, the mode determination unit112determines that the mode is the engagement mode, and the feedback control unit121starts the normal PID control of the actuator2, that is, the feedback control. Therefore, after time t3, the duty calculated based on the gain is output from the duty output unit124as the output duty. As a result, in the present embodiment, the actual load, which is the actual transmission load of the clutch70, changes so as to approach the target clutch transmission load (see the two-dot chain line inFIG.8). At time t5, the rotation angle deviation converges within the threshold value A1, and at time t9, which is after time t8, after a predetermined time T1 (s) has elapsed from time t5, the control shifts to the control stop mode. The feedback control adjustment unit126stores the integral calculation value X immediately before shifting to the control stop mode, and stops the power supply to the actuator2, that is, cuts the power supply. As a result, the feedback control of the actuator2by the feedback control unit121is stopped. Time t1 indicates timing when the target is updated. Further, times t4 and t5 are timings at which the rotation angle deviation converges within the threshold value A1 in the steady state. Further, times t6 and t8 indicate timings at which the state in which the rotation angle deviation is within the threshold value A1 in the steady state continued for T1 (s). As described above, in the present embodiment, the actual load of the clutch70can be brought closer to the target value more quickly than when the switching timing of the duty at the time of mode change is the same timing as the cycle of the feedback control, and transition timing to the control stop mode can be hastened. As described above, in the present embodiment, the duty switching timing when the operating mode is changed is a timing faster than the cycle of the feedback control. That is, in the present embodiment, the duty output unit124outputs the output duty in a cycle shorter than the calculation cycle of the feedback control unit121for a predetermined period after the mode is determined by the mode determination unit112. Therefore, it is possible to shorten a dead time when updating the target, that is, when updating the operating mode, and to improve responsiveness. The “cycle shorter than the calculation cycle of the feedback control unit121” corresponds to, for example, an interrupt processing cycle or an AD detection cycle. (Third Embodiment) A control device according to a third embodiment will be described with reference toFIG.9. The third embodiment is different from the first embodiment in a configuration of the control device100, a method for controlling the actuator2by the control device100, and the like. In the present embodiment, the control device100includes a stroke sensor7. The stroke sensor7is provided, for example, in the vicinity of the pressing unit81. The stroke sensor7detects a relative position of the pressing unit81with respect to the housing10in an axial direction, and outputs a signal corresponding to the relative position to the control device100. Accordingly, the control device100can detect the relative position, a movement amount, and the like of the pressing unit81with respect to the housing10in the axial direction based on the signal from the stroke sensor7. In the present embodiment, a target clutch transmission load, which is a load to be transmitted by the clutch70, is calculated based on a target transmission torque. A target stroke, which is a target movement amount of the pressing unit81in the axial direction, is calculated based on the target clutch transmission load, and a stroke deviation, which is a deviation between the target stroke and the movement amount of the pressing unit81in the axial direction detected by the stroke sensor7, that is, the stroke, is input to the feedback control unit121. As described above, in the present embodiment, the feedback control unit121feedback-controls the actuator2based on the target transmission torque and the movement amount of the pressing unit81in the axial direction. Therefore, it is possible to cope with various controls regardless of a control target. (Fourth Embodiment) A control device according to a fourth embodiment will be described with reference toFIG.10. The fourth embodiment is different from the first embodiment in a method for controlling the actuator2by the control device100, and the like. In the present embodiment, a target clutch transmission load, which is a load to be transmitted by the clutch70, is calculated based on a target transmission torque. A target stroke, which is a target movement amount of the pressing unit81in the axial direction, is calculated based on the target clutch transmission load. A target rotation angle of the electric motor20is calculated based on the target stroke. A target rotation speed is calculated based on the target rotation angle, and a rotation speed deviation, which is a deviation between the target rotation speed and a rotation speed of the electric motor20detected by the rotation angle sensor5, is input to the feedback control unit121. As described above, in the present embodiment, the feedback control unit121feedback-controls the actuator2based on the target transmission torque and the rotation speed of the electric motor20. Therefore, it is possible to cope with various controls regardless of a control target. (Fifth Embodiment) A control device according to a fifth embodiment will be described with reference toFIG.11. The fifth embodiment is different from the first embodiment in a configuration of the control device100, a method for controlling the actuator2by the control device100, and the like. In the present embodiment, the control device100includes a load sensor8. The load sensor8is provided, for example, between the plate portion622and the friction plate624of the output shaft62. The load sensor8detects an axial load acting on the clutch70from the pressing unit81, and outputs a signal corresponding to the load to the control device100. Accordingly, the control device100can detect the load acting on the clutch70from the pressing unit81based on the signal from the load sensor8. In the present embodiment, a target clutch transmission load, which is a load to be transmitted by the clutch70, is calculated based on a target transmission torque, and a load deviation, which is a deviation between the target clutch transmission load and the load acting on the clutch70from the pressing unit81detected by the load sensor8, is input to the feedback control unit121. As described above, in the present embodiment, the feedback control unit121feedback-controls the actuator2based on the target transmission torque and the load acting on the clutch70from the pressing unit81. Therefore, it is possible to cope with various controls regardless of a control target. (Sixth Embodiment) A control device according to a sixth embodiment will be described with reference toFIGS.12and13. The sixth embodiment is different from the first embodiment in a configuration of the control device100, a method for controlling the actuator2by the control device100, and the like. In the present embodiment, the control device100includes a current sensor9. The current sensor9detects a current flowing through the electric motor20, and outputs a signal corresponding to the current to the control device100. Accordingly, the control device100can detect the current flowing through the electric motor20based on the signal from the current sensor9. In the present embodiment, a target clutch transmission load, which is a load to be transmitted by the clutch70, is calculated based on a target transmission torque. A target stroke, which is a target movement amount of the pressing unit81in the axial direction, is calculated based on the target clutch transmission load. A target current, which is a current to be supplied to the electric motor20, is calculated based on the target stroke, and a current deviation, which is a deviation between the target current and the current flowing through the electric motor20detected by the current sensor9, is input to the feedback control unit121. As illustrated inFIG.13, the control device100includes an electronic controller150and a driver160. The electronic controller150includes the target calculation unit111, the mode determination unit112, and the control unit113. As described above, the control unit113includes the feedback control unit121, the gain setting unit122, the duty calculation unit123, the duty output unit124, the energization control unit125, and a feedback control adjustment unit126. In the present embodiment, the feedback control unit121is a circuit implemented by software, that is, a soft feedback circuit, and feedback-controls the actuator2based on the target transmission torque and the current flowing through the electric motor20. The driver160includes switching elements171and172and the current sensor9. The switching element171is connected to the electronic controller150, the actuator2, and a positive electrode of a battery of a vehicle. The switching element172is connected to the electronic controller150, the actuator2, and the current sensor9. The current sensor9is connected to the switching element172and a ground of the vehicle. The energization control unit125can control energization of the electric motor20of the actuator2by controlling operation of the switching elements171and172. When a current flows through the electric motor20, a potential difference is generated between one end and the other end of the current sensor9. Accordingly, the feedback control unit121of the control unit113can detect the current flowing through the electric motor20. In the present embodiment, the target transmission torque is calculated by the target calculation unit111of the electronic controller150, and the output duty is calculated by the duty calculation unit123of the control unit113of the electronic controller150and output by the duty output unit124. The feedback control adjustment unit126shifts to a control stop mode that causes the feedback control unit121to stop feedback-controlling the actuator2when a predetermined stop condition is satisfied in a case where the mode determination unit112determines that the operating mode is the steady mode. As described above, in the present embodiment, the feedback control unit121feedback-controls the actuator2based on the target transmission torque and the current flowing through the electric motor20. Therefore, it is possible to cope with various controls regardless of a control target. (Seventh Embodiment) A control device according to a seventh embodiment will be described with reference toFIG.14. The seventh embodiment is different from the sixth embodiment in a configuration of the control device100and the like. In the present embodiment, unlike the sixth embodiment, the electronic controller150does not include the control unit113. The driver160further includes the control unit113. That is, the control unit113is provided in the driver160integrally with the switching elements171and172and the current sensor9. Here, the control unit113is, for example, a circuit implemented by hardware such as an IC. The control unit113includes a feedback control unit121, a gain setting unit122, a duty calculation unit123, a duty output unit124, an energization control unit125, and a feedback control adjustment unit126. In the present embodiment, the feedback control unit121is a circuit implemented by hardware, that is, a hard feedback circuit, and feedback-controls the actuator2based on a target transmission torque and a current flowing through the electric motor20. The control unit113is connected to the electronic controller150, the switching elements171and172, and the current sensor9. The energization control unit125of the control unit113can control energization of the electric motor20of the actuator2by controlling operation of the switching elements171and172. The feedback control unit121of the control unit113can detect the current flowing through the electric motor20. In the present embodiment, the target transmission torque is calculated by the target calculation unit111of the electronic controller150, and an output duty is calculated by the duty calculation unit123of the control unit113and output by the duty output unit124. The feedback control adjustment unit126shifts to a control stop mode that causes the feedback control unit121to stop feedback-controlling the actuator2when a predetermined stop condition is satisfied in a case where the mode determination unit112determines that the operating mode is the steady mode. As described above, in the present embodiment, the feedback control unit121is a circuit implemented by hardware, and feedback-controls the actuator2based on the target transmission torque and the current flowing through the electric motor20. Therefore, an inexpensive driver IC can be selected when implementing the control unit113, and the cost can be reduced. (Eighth Embodiment) A control device according to an eighth embodiment will be described with reference toFIG.15. The eighth embodiment is different from the first embodiment in a method for controlling the actuator2by the control device100and the like. FIG.15illustrates a relation between a relative position of the pressing unit81with respect to the housing10in an axial direction, that is, a stroke of the pressing unit81, and an actual transmission load of the clutch70, that is, a clutch load. In this embodiment, the feedback control adjustment unit126shifts to the control stop mode when the mode determination unit112determines that the mode is the steady mode only in the case where the reaction force from the clutch70to the actuator2is greater than 0. Specifically, as shown inFIG.15, in a looseness elimination period when the pressing unit81approaches the clutch70and the clearance between the pressing unit81and the clutch70becomes smaller, that is, when the reaction force from the clutch70to the actuator2becomes 0 or less, the feedback control adjustment unit126does not shift to the control stop mode even if the mode determination unit112determines that the mode is the steady mode. After the touching point at which the pressing unit81contacts the clutch70, in a thrust control period when the pressing unit81presses the clutch70and the clutch load becomes greater than 0, that is, when the reaction force from the clutch70to the actuator2becomes greater than 0, the feedback control adjustment unit126shifts to the control stop mode if the mode determination unit112determines that the mode is the steady mode. As described above, in this embodiment, the feedback control adjustment unit126can shift to the control stop mode when the mode determination unit112determines that the mode is the steady mode only in the case where the reaction force from the clutch70to the actuator2is greater than 0. Since there is no effect of the load of the clutch70during the looseness elimination period, the processing load can be suppressed without performing the processing for shifting to the control stop mode. In addition, during the thrust control period, when a system that does not have a control stop mode or a system that resets an integral calculation value since the reaction force from the clutch70to the actuator2is large is used, there is a possibility that the load behavior will vary immediately after the feedback control is restarted. However, in this embodiment, it is possible to suppress variations in load behavior immediately after the feedback control is restarted after the control stop mode, which is preferable. (Other Embodiments) In the other embodiments, a torque may be received from a second transmission portion and output from a first transmission portion via a clutch. For example, when one of the first transmission portion and the second transmission portion is non-rotatably fixed, the rotation of the other of the first transmission portion and the second transmission portion can be stopped by bringing the clutch into an engaged state. In this case, the clutch is of a type that connects and disconnects the first transmission portion and the second transmission portion, of which one is fixed and the other relatively rotates with respect to another member, and that weakens or stops the transmitted power. Here, the clutch can function as a brake. In the other embodiments, the clutch may be a dry clutch. In the other embodiments, the clutch may be a single-disc clutch. In the other embodiments, a torque transmission portion is not limited to the clutch and may have any configuration as long as the torque transmission portion is switched to a transmission state or a non-transmission state by operation of an actuator. As described above, the present disclosure is not limited to the above embodiments and can be practiced in various forms without departing from the gist of the present disclosure. The control unit and the technique according to the present disclosure may be achieved by a dedicated computer provided by constituting a processor and a memory programmed to execute one or more functions embodied by a computer program. Alternatively, the control circuit and the method described in the present disclosure may be realized by a dedicated computer configured as a processor with one or more dedicated hardware logic circuits. Alternatively, the control circuit and method described in the present disclosure may be realized by one or more dedicated computer, which is configured as a combination of a processor and a memory, which are programmed to perform one or more functions, and a processor which is configured with one or more hardware logic circuits. The computer program may be stored, as instructions to be executed by a computer, in a tangible non-transitory computer-readable medium. The present disclosure has been described on the basis of embodiments. However, the present disclosure is not limited to such embodiments and structures. The present disclosure also encompasses various modifications and variations within the scope of equivalents. Furthermore, various combination and formation, and other combination and formation including one, more than one or less than one element may be made in the present disclosure. | 75,055 |
11859680 | DESCRIPTION OF PREFERRED EMBODIMENTS The disc brake assembly100according to the invention is illustrated inFIG.1in an isometric view. It comprises a brake disc1001which is engaged across by a brake caliper10which is a carrier of two brake linings103. The brake disc1001is mountable on a shaft or an axle support and can then be used in a vehicle (passenger car, truck, rail vehicle) or in a stationary device. The brake caliper10comprises an outwardly positioned jaw104which extends parallel to the friction surface of the brake disc1001wherein through the jaw104the brake force can be applied to the friction linings103. It has a second inner jaw at an end of the brake caliper10which cannot be seen in the drawing and is axially facing away. For the invention, it is of no consequence which principle the brake caliper employs for generating the brake force. It can be an electrically, hydraulically or pneumatically actuated brake caliper. The outer jaw104and the inner jaw that is not illustrated are connected for force transmission by a caliper bridge102in which a lining inspection opening101is provided by means of which in a servicing situation the wear condition of the friction linings103can be easily and quickly determined, i.e., without demounting. In a conventional disc brake assembly, the lining inspection opening is always open so that a significant proportion of the brake dust which is produced during braking also reaches the environment through this opening; this has been determined by the applicant in experiments. According to the invention, the lining inspection opening101is closed by a brake dust particle filter1which is inserted with precise fit therein. The brake dust particle filter1does not project in radial direction past the outer contour of the brake caliper10so that it does not require additional installation space. Moreover, its installation is possible very quickly and easily by simple insertion so that this can be done even by an end user. The construction of the brake dust particle filter1itself can now be seen inFIGS.2and3. The brake dust particle filter1according to the illustrated embodiment is of a two-part configuration: it has (a) a filter medium support11and (b) a filter medium12which is held by the filter medium support11. The filter medium support11is provided with a plurality of through openings15that enable flow through the filter medium12. The filter medium support11, with regard to its shape and dimensions, is matched to the lining inspection opening101so that it can be inserted with proper fit into it. For fastening the filter medium support11in the lining inspection opening101, it comprises clamping hooks13whose length corresponds to the material thickness of the brake caliper10wherein the clamping hooks13can be locked with their respective angled end section behind the lining inspection opening101. In order for the brake dust particle filter1to not be inserted too far radially (=depth direction) into the lining inspection opening101, at the filter medium support11projecting radial stops14embodied as tongues are provided, respectively, which are in contact with the wall surface105of the brake caliper10in the mounted state (FIG.1). The filter medium12is in the present case a flat material, for example, a metal or ceramic nonwoven, which is tailored to the shape and dimensions of the filter medium support11and, provided with cutouts12′ for the clamping hooks13, connected, for example, welded, to the filter medium support11. In certain embodiments, the filter medium12can also be connected detachably to the filter medium support11, for example, only frictionally clamped. When the brake dust particle filter1is to be exchanged, this can be done quickly and simply in the context of the regular wheel change and/or during other servicing work at the brake assembly. In case of a full metal variant (filter medium of metal and filter medium support of metal), a problem-free and resource-saving recyclability is provided in addition. LIST OF REFERENCE CHARACTERS 10brake caliper101lining inspection opening102caliper bridge103friction linings104outer jaw105wall surface100disc brake assembly1001brake disc1brake dust particle filter11filter medium support12filter medium12′ cutouts of the filter medium for clamping hooks13clamping hook14radial stop15through openings | 4,365 |
11859681 | DESCRIPTION OF THE PREFERRED EMBODIMENT Although the disclosure hereof is detailed and exact to enable those skilled in the art to practice the invention, the physical embodiments herein disclosed merely exemplify the invention which may be embodied in other specific structures. While the preferred embodiment has been described, the details may be changed without departing from the invention, which is defined by the claims. Referring now toFIG.1, a disc brake piston retractor tool10used for compressing a piston into a caliper housing when replacing a set of brake pads installed therein is shown. A male threaded rod12carries a female threaded collar14. The threaded collar14is provided with a spreader plate15which engages a portion of the caliper housing as will be described later. A spring16surrounds pusher socket24. A centering ring18is coupled to the pusher socket24. FIG.2is a partially exploded perspective view of the brake caliper tool10ofFIG.1, andFIG.3is a fully exploded view of the tool10. A threaded rod male end20is coupled through threaded collar14, past spreader plate15, and through pusher socket24. Pusher socket24carries a snap ring26(for coupling about washer groove28) and step washer22. Pusher socket face34ultimately contacts the piston104as will be described later. A plurality of centering rings of increasing radius18′,18″ and18′″ are provided. In use, a user selects between one of centering rings of increasing radius18′,18″ and18′″ for optimal fit about piston104. FIG.4is a cross-sectional view of the tool shown inFIG.3. As can be seen, threaded collar14threadedly receives threaded rod12in engaging fashion. Centering rings of increasing radius18′,18″ and18′″ comprise a centering slope30, along which the centering rings of increasing radius18′,18″ and18′″ can self-center about piston104ofFIG.5. FIG.5is a perspective view of a caliper housing100, caliper frame102, and piston104to be retracted with the brake caliper tool ofFIG.1.FIG.6is a side view of the elements shown inFIG.5. FIGS.7-11shown the brake caliper tool10in use. Referring now toFIG.7, a side in-use view of the brake caliper tool10ofFIG.1is shown, the tool10being positioned within the caliper housing100and proximal to the piston104to be retracted. Spreader plate15is placed between caliper104and caliper frame102. Referring now toFIG.8, a side in-use view of the brake caliper tool10ofFIG.1is shown positioned within the caliper housing and proximal to the piston104to be retracted, with the centering cone18approaching the piston104to be retracted. Centering cone18can be advanced toward piston104by manually turning threaded rod12, or placing a socket or impact wrench40(seeFIG.10) into threaded rod wrench receiver32(seeFIG.4). Alternatively, as shown inFIG.2, instead of a threaded rod wrench receiver32, a hexagonal drive head42can be used. As shown inFIG.9, the centering cone18eventually engages the piston104to be retracted, as shown in close up inFIG.9A. The centering slope30of centering cone18self-centers the centering cone18on the piston104. As shown inFIGS.10and10A, rotation of wrench40advances pusher socket24, and particularly pusher socket face34of pusher socket24into engaging contact with piston104. Continued rotation of wrench40urges spreader plate15against caliper frame102, spreading spreader plate15from pusher socket24. Pusher socket24receives the rotational and pushing forces from wrench40operating on threaded rod12, and pusher socket face34of pusher socket24applies both pushing and rotational forces to piston104to retract piston104into the caliper housing100. Spring16initially urges centering cone18into contact with piston104, but as centering cone18advances toward piston14, spring16allows the centering ring18to yield to pusher socket face34engaging piston104. The application of pushing and rotational forces to piston104to retract piston104into the caliper housing100continues until piston104is fully retracted as shown inFIGS.11and11A. Following full retraction of piston104into caliper housing100as shown inFIG.11, the wrench40can be rotated counterclockwise (not shown) to remove the tool10from engagement with caliper housing100. It will be appreciated that threaded road12could be threaded left handed or right handed. The foregoing is considered as illustrative only of the principles of the invention. Furthermore, since numerous modifications and changes will readily occur to those skilled in the art, it is not desired to limit the invention to the exact construction and operation shown and described. While the preferred embodiment has been described, the details may be changed without departing from the invention, which is defined by the claims. | 4,723 |
11859682 | DESCRIPTION OF EMBODIMENTS Hereinafter, an embodiment of the present invention will be described with reference to the drawings. First Embodiment FIGS.1to5illustrate a brake disc1according to a first embodiment of the present invention. The brake disc1is realized as a brake disc used in a bicycle, a motorcycle, or the like. Although aluminum, stainless steel, or carbon steel, for example, may be used as a material of the brake disc1, the material is not limited to these examples.FIG.1is a view of the brake disc1when seen from a brake front surface17a, andFIG.2is a view of the brake disc1when seen from a brake back surface17b. As is best illustrated inFIGS.1to3, the brake disc1includes an outer circumferential portion2on which a brake pad that is not illustrated is caused to abut and a load acts at the time of braking, a center opening portion3formed on an inner side of the outer circumferential portion2, and a plurality of attachment holes5formed at positions projecting from the outer circumferential portion2toward the inside of the center opening portion3to attach the brake disc1to a rotating element (not illustrated) such as a wheel. A flower petal-shaped waveform portion10composed of repetition of recessed portions10aand projecting portions10bis formed in a radial direction at an outer edge of the outer circumferential portion2, and the outer circumferential portion2forms a pad pressurizing surface to which a brake pad that is not illustrated can be applied. For example, the brake pad can apply a brake force to the brake disc by a pair of pads abutting on the outer circumferential portion2from both surfaces, namely the brake front surface17aand the brake back surface17b. Therefore, a load is applied directly to the outer circumferential portion2in a direction opposite to a rotation direction of the brake disc1when rotation is delivered, that is, when the brake pad abuts on the outer circumferential portion2and a brake force is applied. Also, the pad pressurizing surface includes the projecting portions10bof the waveform portion10, and it is possible to remove a small amount of powder generated due to wear of the brake pad by each of the projecting portions10bsequentially abutting on the brake pad with the recessed portions10ainterposed therebetween. Each recessed portion10ais formed of two side parts20and21, and the shape of the recessed portion10ais formed asymmetrically in the present embodiment. As the asymmetric shape, an angle of a tangential line of the side part20with respect to the radial direction is 45° or less, and an angle of a tangential line of the side part21is more than 45°, for example. Note that the shape of the waveform portion10is not limited to the illustrated example and can be changed in an arbitrary suitable manner in the present invention. For example, various forms such as symmetric recessed portions10a, recessed portions10aentirely formed into arc shapes, and recessed portions10a, each of which is formed of three or more side parts, are included. It is a matter of course that the projecting portions10bare also not limited to the illustrated example. In addition, a plurality of through-holes11are also formed in the outer circumferential portion2for an improvement in heat dissipation through an increase in surface area, a light weight, an improvement in a braking property through reduction of moment of inertia, and an improvement in a wear debris and mud protection property. FIG.6illustrates a partially enlarged view of the waveform portion composed of the recessed portions10aand the projecting portions10b. As illustrated in the drawing, the inner circumferential portion32is formed on the inner side of the outer circumferential portion2in the radial direction. The outer circumferential portion2serves as a sliding portion area of the brake pad, which is not illustrated, that is, a region on which the brake pad abuts while sliding, and the inner circumferential portion32serves as a non-sliding portion area of the brake pad, that is, a region on which the brake pad does not abut. If a boundary line between the outer circumferential portion2and the inner circumferential portion32is represented as30, through-holes36and38are formed across the boundary line30, in addition to the through-holes11formed in the outer circumferential portion2, and an inner edge portion of the brake pad in the radial direction can intersect the through-holes36and38. The through-holes36and38function as cleaning portions that remove a small amount of powder generated due to wear of the brake pad similarly to the recessed portions10aand the projecting portions10bwhich an outer edge portion of the brake pad in the radial direction can intersect. Note that a chamfered portion40is formed at an outer circumferential edge portion at a boundary between the brake front surface17aand an outer circumferential end surface18, and a chamfered portion41is formed at an outer circumferential edge portion at a boundary between the brake back surface17band an outer circumferential end surface18. Next, the inner circumferential portion32of the brake disc1will be described. Note that the inner circumferential portion32described below is an example of the inner circumferential portion according to the present invention in which the outer circumferential portion2mainly has characteristic features, and the inner circumferential portion according to the present invention is not limited to this example. In the examples inFIGS.1to5, six attachment holes5are provided in the inner circumferential portion32. In the illustrated example, the six attachment holes5are distributed in the circumferential direction such that center angles (divided angles), each of which is formed by two adjacent attachment holes5and5with respect to the center of the brake disc, become equal angles that are substantially equal to each other. In the case in which the number of attachment holes5is six, the equal angle is 360°/6=60°. Since arrangement of the attachment holes5is determined in accordance with a specification of the rotation element, such as a wheel, to which the brake disc1is attached, the arrangement is not necessarily limited to the arrangement of equal angle, in which each divided angle is equal. For example, it is possible to apply the present invention even if the divided angles are not uniform, such as divided angles of 50°, 55°, 60°, 65°, . . . (the arrangement may include partially uniform divided angles) in accordance with the specification of the wheel. Also, the attachment holes5are formed at positions at an equal distance from a center O of the brake disc in the radial direction in the example inFIGS.1to5. However, since the arrangement of the attachment holes5is determined in accordance with the specification of the wheel or the like in this regard as well, the distances of the attachment holes5from the center O in the radial direction are not necessarily equal to each other and may be different from each other (the arrangement may include partially uniform radii), and it is possible to apply the present invention to this case as well. Each attachment hole5is formed in a region8in which a first crosspiece portion6extending from the outer circumferential portion2to the inside of the center opening portion3and a second crosspiece portion7extending from the outer circumferential portion2to the inside of the center opening portion3intersect one another. The first crosspiece portion6, the second crosspiece portion7, and the intersecting region8form, along with the outer circumferential portion2, each circumferential opening portion9that serves as a through-hole. Only the first crosspiece portion6and the second crosspiece portion7intersect the intersecting region8, and there are no parts intersecting the intersecting region8except for these crosspiece portions. Note that the first crosspiece portion and the second crosspiece portion may be formed symmetrically in the inner circumferential portion32of the present invention, or alternatively, one crosspiece portion extending on the inner side beyond the outer circumferential portion2in the radial direction may be provided rather than the two crosspiece portions as described above, and the attachment hole5may be formed at the crosspiece portion. Alternatively, three or more crosspiece portions may be provided. In the latter case, the attachment hole may be formed at an intersecting portions thereof, for example. As is obvious from the side view ofFIG.4, the brake disc1is formed into a plate shape such that the outer circumferential portion2, the first crosspiece portion6, the second crosspiece portion7, the intersecting region8, and the waveform portion10fall within a predetermined thickness range. The brake disc1is attached to the wheel by pressing the brake back surface17billustrated inFIG.2against the wheel, causing bolts to pass through the attachment holes5from the brake front surface17aillustrated inFIG.1, and screwing the bolts into screw holes in the wheel. Therefore, the attachment holes5have, in front side surfaces, dish-shaped recessed portions12(FIG.3) such that bolt heads can be seated as illustrated inFIGS.1,2, and5. The attachment holes5are not limited to the example and may be through-holes with a columnar shape or through-holes that have dish-shaped parts with a rectangular section, for example. In the brake disc1according to the first embodiment, the shapes and the sizes of the recessed portions10aand the projecting portions10bof the waveform portion10, the number and the size of the through-holes11, and the size of the circumferential opening portions9are defined to obtain, in the outer circumferential portion2, substantially uniform heat capacity distribution in the circumferential direction and the radial direction. Moreover, the recessed portions10aand the projecting portions10bof the waveform portion10, the through-holes11, and the circumferential opening portions9are formed to increase the surface area of the side surface of the brake disc to thereby achieve desired cooling efficiency. Here, the definition of “substantially uniform heat capacity distribution in the circumferential direction and in the radial direction” described in the present embodiment will be described usingFIG.7. FIGS.7(a) and7(b)illustrate one section (a section corresponding to three projecting portions10band two recessed portions10a) in the outer circumferential portion2. It is a matter of course that the sections as illustrated in the drawings are applied to the entire circumference of the outer circumferential portion2. FIG.7(a)illustrates circumferential sections c1, c2, c3, c4, c5, and c6in the outer circumferential portion2, which are sectioned at an equal angle in the circumferential direction, andFIG.7(b)illustrates radial sections r1, r2, and r3in the outer circumferential portion2, which are sectioned to have an equal length in the radial direction. The circumferential sections c1, c2, c3, c4, c5, and c6are sectioned by virtual circumferential boundary lines b1, b2, b3, b4, b5, b6, and b7drawn from the center O of the brake disc at an equal angle in the radial direction for convenience. Among these circumferential boundary lines, b1, b3, b5, and b7are set to extend in the radial direction through minimum points of the recessed portions10a, and the circumferential boundary lines b2, b4, and b6are set to extend in the radial direction through maximum points of the projecting portions10b. Note that the circumferential boundary lines b1, . . . illustrated inFIG.7(a)are virtual lines only for an illustrative purpose, and other dividing ways are also included in the present embodiment. As the preferable number of divided sections in the circumferential direction is thirty to forty five, and in the aforementioned example, the outer circumferential portion2is divided into thirty six sections at every 10 degrees in the circumferential direction. Since the uniform heat capacity distribution in the circumferential direction means that a difference in heat capacities among the circumferential sections c1, . . . decreases, the “substantially uniform heat capacity distribution in the circumferential direction” can be defined as a ratio of the difference in heat capacities among the circumferential sections with respect to each heat capacity among the circumferential sections c1, . . . being equal to or less than a first predetermined ratio. On the other hand, the radial sections r1, r2, and r3are obtained by equally dividing a part from the outermost edge of the outer circumferential portion2to the boundary line30between the outer circumferential portion2and the inner circumferential portion32into an equal length in the radial direction by two radial boundary lines d1and d2. The radial boundary lines d1and d2illustrated inFIG.7(b)are virtual lines only for an illustrative purpose, and other dividing ways are also included in the present embodiment. Preferably, the radial sections are at least three radial sections, and the radial section r1on the outermost side has a length in the radial direction that includes the waveform portion10as illustrated inFIG.7(b). Since the uniform heat capacity distribution in the radial direction means that a difference in heat capacities among the radial sections r1, r2, and r3decreases, the “substantially uniform heat capacity distribution in the radial direction” can be defined as a ratio of the difference in heat capacities among the circumferential sections relative to the heat capacity of each of the radial sections r1, r2, and r3being equal to or less than a second predetermined ratio. In order to clarify the aforementioned characteristic features of the brake disc1according to the present embodiment, a disc A in the related art will be described usingFIGS.14(a) and14(b). FIGS.14(a) and14(b)illustrate the disc A in the related art for comparison with the brake disc1according to the first embodiment. As illustrated inFIG.14(a), an outer circumferential portion52of the disc A in the related art includes a waveform portion60in which recessed portions60aand projecting portions60bare repeatedly formed over an outer circumference and through-holes61and62. A first crosspiece portion56extending to a center opening portion53at a smaller inclination angle with respect to the radial direction and a second crosspiece portion57extending to the center opening portion53at a larger inclination angle with respect to the radial direction are formed on the inner side of the outer circumferential portion52in the radial direction, and an attachment hole55is formed in each region which the first crosspiece portion56and the second crosspiece portion57intersect. The first crosspiece portion56, the second crosspiece portion57, and the intersecting region form, along with the outer circumferential portion52, a circumferential opening portion59. Also, the outer circumferential portion52of the disc A in the related art serves as a sliding portion area of a brake pad, which is not illustrated, that is, a region on which the brake pad abuts while sliding, and an inner circumferential portion composed of the first crosspiece portion56and the second crosspiece portion57serves as a non-sliding portion area of the brake pad, that is, a region on which the brake pad does not abut as illustrated inFIG.14(b). If a boundary line between the outer circumferential portion52and the inner circumferential portion is represented as63, no through-holes crossing the boundary line63are formed in the disc A in the related art. On the other hand, the brake disc1according to the present embodiment includes the cleaning through-holes36and38across the boundary line30between the outer circumferential portion2and the inner circumferential portion32. FIG.8illustrates comparison between the brake disc1according to the present embodiment and the disc A in the related art. As illustrated inFIG.8(a), the brake disc1is a disc that includes, on the outermost side of the outer circumferential portion2, the waveform portion that functions as a cleaning portion for the brake pad, further includes the cleaning through-holes across the boundary line at the boundary line between the outer circumferential portion and the inner circumferential portion, and does not include any non-cleaning portions. On the other hand, although the disc A in the related art includes, on the outermost side of the outer circumferential portion2, the waveform portion that functions as a cleaning portion for the brake pad, no cleaning portions are formed at the boundary line between the sliding portion area and the non-sliding portion area as described above inFIG.14(b). Therefore, there is a non-cleaning portion (thick line) on the boundary line in the state. Also,FIG.8(b)illustrates an area of each radial section and a maximum area difference among the radial sections in each of the present brake disc1and the disc A in the related art. As illustrated in the drawing, each of the areas of radial sections r1′, r2′, and r3′ in the disc A in the related art is 522 mm2, 750 mm2, and 855 mm2, and the maximum area difference among the radial sections (the area of r3′−the area of r1′) is 333 mm2. On the other hand, each of the areas of the radial sections r1, r2, and r3in the present brake disc1is 680 mm2, 730 mm2, and 725 mm2, and the maximum area difference among the radial sections (the area of r2−the area of r1) is 50 mm2. On the assumption that the plate thicknesses are uniform over the entire regions and are the same and the materials are also uniform and are the same in these two brake discs, the area of each section corresponds to the heat capacity of each section. Therefore, it is possible to state that the ratio of the differences in heat capacities among the radial sections with respect to the heat capacity of each radial section in the present brake disc1is significantly smaller than that in the disc A in the related art, and that the heat capacity distribution in the radial direction is substantially uniform in the present brake disc1. FIG.8(c)illustrates an area of each circumferential section and a maximum area difference among the radial sections in each of the present brake disc1and the disc A in the related art. As illustrated in the drawing, the area of each of circumferential sections c1′ to c6′ in the disc A in the related art is 277 mm2to 356 mm2, and the maximum area difference among the circumferential sections (the area of c5′−the area of c1′) is 137 mm2. On the other hand, the area of each of the radial sections c1to c6in the present brake disc1is 382 mm2to 341 mm2, and the maximum area difference among the circumferential sections (the area of c5−the area of c2) is 64 mm2. Therefore, it is possible to state that the ratio of the difference in heat capacities among the circumferential sections with respect to the heat capacity of each circumferential section in the present brake disc1is significantly smaller than that in the disc A in the related art, and that the heat capacity distribution in the circumferential direction is substantially uniform in the present brake disc1. As described above, it is possible to regard the present brake disc1as having substantially uniform heat capacity distribution in the circumferential direction and the radial direction. In the brake disc1illustrated inFIG.8, the ratio of the difference in heat capacities among the circumferential sections with respect to the heat capacity of each circumferential section is 25% or less. Also, the ratio of the difference in heat capacities among the radial sections with respect to the heat capacity of each radial section is 8% or less in the present brake disc1. Therefore, it is possible to set the first predetermined ratio to 25% and to set the second predetermined ratio to 8%. FIG.9illustrates a comparison diagram similar toFIG.8for discs B, C, and D other than the disc A in the related art. The disc B in the related art is a disc including a waveform portion with a shape different from that in the disc in the related art, the disc C in the related art has a smaller amplitude in a waveform portion, the disc D in the related art is a perfect circle disc. As illustrated inFIG.9(a), all the discs in the related art include non-cleaning portions. Particularly, the disc C in the related art including a smaller waveform portion and the disc D in the related art with no waveform portion include non-cleaning portions even on the outermost sides. As illustrated inFIG.9(b), the maximum area differences among the radial sections in the discs B, C, and D in the related art are larger than that of the present brake disc1, and the ratios of heat capacities among the radial sections with respect to the heat capacity of each radial section are also higher. Although it is possible to significantly reduce the area differences among the circumferential sections in the discs C and D in the related art as illustrated inFIG.9(c), the maximum area difference among the circumferential sections and the ratio thereof with respect to the area of each section in the disc B in the related art including the waveform portion that functions as a cleaning portion are larger than those of the present disc1. As is obvious from the above description, a disc in which a ratio of a difference in heat capacities among circumferential sections relative to a heat capacity of each circumferential section is equal to or less than the first predetermined ratio (25%), a ratio of a difference in heat capacities among radial sections relative to a heat capacity of each radial section is equal to or less than the second predetermined ratio (8%), and the non-cleaning portion is not present is only the brake disc1according to the present embodiment. FIG.10illustrates summary of the aforementioned comparison related to the heat capacities and the surface areas of the side surfaces of the brake disc1according to the present embodiment and the disc A in the related art. In the brake disc1and the disc A in the related art, the heat capacities of the entire outer circumferential portions that are sliding portion areas of the brake pads are substantially the same values (about 166 J/K). However, in regard to the maximum differences in heat capacities in the circumferential direction, the disc A in the related art has a maximum difference of 1.8 J/K while the present brake disc1has a maximum difference of 0.6 J/K and achieves a significantly small difference in heat capacities in the circumferential direction. Also, in regard to the maximum differences in heat capacities in the radial direction, the disc A in the related art has a maximum difference of 4.4 J/K while the present brake disc1has a maximum difference of 0.7 J/K and achieves a significantly small difference in heat capacities in the radial direction. In regard to the surface areas of the side surfaces (the areas of parts when seen from side surfaces other than the brake front surfaces and the brake back surfaces), the disc A in the related art has the surface area of 1487 mm2while the present brake disc1has the surface area of 2469 mm2, which is significantly large. This is because the present brake disc1can increase the surface area of the side surface through adjustment of the shape and the size of the waveform portion and the arrangement, the number, and the size of the through-holes (9,11,36, and38). Therefore, the present brake disc1can have significantly improved cooling efficiency without increasing the heat capacity itself by having substantially uniform heat capacity distribution in the circumferential direction and in the radial direction and increasing the surface area of the side surface. FIG.11illustrates temperature measurement results of the disc A in the related art and the brake disc A according to the present embodiment under the same conditions. As illustrated inFIG.11(a), large temperature irregularity in the circumferential direction is present in the disc A in the related art, and the highest temperature reaches 617° C. On the other hand, temperature irregularity in the circumferential direction is uniform in the brake disc1according to the present embodiment while the weight, that is, the heat capacity of the sliding portion area is maintained to be the same as that of the disc in the related art, and it is also possible to drop the highest temperature to 572° C. In other words, according to the present embodiment, it is possible to reduce the disc weight even with a specification in which the same highest temperature as that of the disc A in the related art is reached. As described above, according to the present embodiment, it is possible to uniformize temperature irregularity and to enhance cooling efficiency even if the heat capacity is equivalent to that of the disc in the related art, and it is thus possible to achieve better brake feeling. Second Embodiment According to the first embodiment, the entire brake disc1is integrally molded. The brake disc according to the present invention is not limited thereto and can be composed of two or more components. This example will be described as a second embodiment usingFIGS.12and13. Note that for constituent requirements in the second embodiment that are similar to those in the first embodiment, b will be applied to the same reference signs as those in the first embodiment, and detailed description will be omitted. As illustrated inFIGS.12and13, a brake disc1baccording to the second embodiment includes an outer circumferential portion2band a crosspiece inner circumferential portion13, and the crosspiece inner circumferential portion13is coupled to the outer circumferential portion2bvia a plurality of bridge portions15extending from the outer circumferential portion2bto a center opening portion3band pins14. All first crosspiece portions6band second crosspiece portions7bof the brake disc1bare integrally formed in the crosspiece inner circumferential portion13, and each attachment hole5bis formed in each region8bin which the first and second crosspiece portions intersect one another. Note that the plurality of attachment holes5binclude attachment holes at different distances from the center O. Note that composite arc parts20to24and recessed stretching portions25to27may be formed in the second embodiment as well. According to the second embodiment, it is possible to provide a brake disc that becomes compatible merely through exchange of the crosspiece inner circumferential portion13in accordance with a specification of a wheel, as well as to achieve advantageous effects similar to those of the first embodiment. Conversely, it is also possible to exchange only the outer circumferential portion2bdue to wear or the like. Although the brake disc according to the embodiments of the present invention has been described hitherto, the present invention is not limited to the above examples and can be changed in an arbitrary suitable manner within the scope of the present invention. REFERENCE SIGNS LIST 1,1bBrake disc2,2bOuter circumferential portion3,3bCenter opening portion5,5bAttachment hole6,6bFirst crosspiece portion7,7bSecond crosspiece portion8,8bIntersecting region9,9bCircumferential opening portion10Waveform portion10aRecessed portion10bProjecting portion11,11bThrough-hole12Dish-shaped recessed portion13Crosspiece inner circumferential portion14Pin15Bridge portion17aBrake front surface17bBrake back surface20Side part of recessed portion10a(side at 45° or less relative to radial direction)21Side of recessed portion10a(side at 45° or more relative to radial direction)30Boundary line between outer circumferential portion2and inner circumferential portion3232Inner circumferential portion36,38Cleaning through-holeb1, b2, b3, b4, b5, b6, b7Circumferential boundary linec1, c2, c3, c4, c5, c6Circumferential sectiond1, d2Radial boundary liner1, r2, r3Radial section | 28,064 |
11859683 | DESCRIPTION OF THE INVENTION The brake disk1, which constitutes a component within the meaning of the invention, has a base body2which is designed in a conventional manner and is cast from a cast iron material known for this purpose with the DIN-EN designation EN-JL1040. The brake disk1has a pot-shaped supporting part3and a friction ring4cast thereon, which is shown here as consisting of solid material, but can also be designed in conventional manner as an internally ventilated friction ring4. The friction ring4has, in an equally usual manner, an annular friction surface5a,5bon each of its front surfaces aligned normal to the rotational axis X-X. In the case of the base body2provided for the coating, friction surfaces5a,5bhave been prepared by chip-removing processing in a manner known per se after casting of the base body2so that they have an average roughness depth Rz of 20 μm on their upper side. A coating B consisting of an intermediate layer Z and a covering layer D is applied to the friction surfaces5a,5bof the base body2processed in this way. The intermediate layer Z has been produced from a commercially available stainless steel material provided in powder form, for example the above-mentioned stainless steel material standardized under the designation 316L. The thickness Dz of the intermediate layer Z was 120-140 μm. For the application of the intermediate layer Z, the brake disk has been positioned in a horizontal position in a clamping device not shown here, which could be driven in a rotating manner about the rotational axis X-X of the brake disk1by means of a rotary drive also not shown here. Subsequently, the intermediate layer Z has been produced by means of laser deposition welding. For this purpose, a laser beam device not shown here (laser head diameter=5 mm) has been positioned in a starting position at the inner diameter of the friction ring4and the brake disk1has been rotated at 60 revolutions per minute. Starting from the starting position, the laser has then been moved radially in the direction of the outer circumference of the friction ring at a speed of 10 m/min. The laser has been ignited upon start-up and switched off upon reaching the outer diameter. With the start of the laser irradiation, the powdery steel material of the intermediate layer Z has been added to the region in each case swept by the laser beam in accordance with the procedure described in DE 10 2011 100 456 B4. By the intermediate layer Z, unevenness present on the friction surfaces5a,5bhas been evened out and pores6have been closed so that, after application of the intermediate layer Z, a flat surface optimally suited for the application of a covering layer D was present on its side facing away from the base body2. In three tests, a covering layer D has been applied to three brake disks1, each covered with the intermediate layer Z in the manner described above, as follows: Hard material particles HP have been provided, which were tungsten carbide particles. The hard material particles HP had an average grain diameter of −25-60 μm. To the brake disk1clamped in a rotationally drivable manner as for the application of the intermediate layer Z, a layer of powder has been applied, that consisted of a stainless steel standardized under the material number 1.4404 according to the steel-iron list. A laser beam has been directed at the powder, which laser beam has impinged on the section of the powder layer located in each case below it in a spot with a diameter of 2.9 mm in tests 1 and 2 and in a spot with a diameter of 1.2 mm in test 3. Thereby, in test 1, the laser intensity was 0.2 KW/mm2, in test 2, the laser had an intensity of 2.20 KW/mm2and in test 3 not being in accordance with the invention, a laser intensity of 3.50 KW/mm2. By rotating the brake disk1about the rotational axis X-X, the powder layer has been moved under the laser beam and, associated therewith, the laser spot has been moved successively over the powder layer until, after a corresponding number of revolutions, the stainless steel powder has melted completely and solidified again under formation of the stainless steel matrix E of the covering layer D. Into the melt bath formed in each case from the stainless steel powder in the spot of the laser beam, a quantity of the provided hard material particles HP has been introduced, which was dimensioned such that in the melt bath there was a steel melt which consisted of 40% of the hard material particles HP and as remainder of the stainless steel melt. The covering layer D produced in this way had a thickness Dd of 250 μm with a surface hardness of 950-1500 HV10. At the brake disks1coated in this way, microsections aligned transversely to the circumferential direction have been produced, which are shown inFIGS.2(test 1),3(test 2) and4(test 3). FIGS.2-4show the cast iron material G of the brake disk1, the intermediate layer Z lying on the cast iron material G and the covering layer D lying on the intermediate layer Z with the hard material particles HP embedded therein. The hard material particles HP each have a clearly visible inner core region K, which is not melted and is accordingly in the state in which the hard material particles HP have been introduced into the melt bath produced by the laser beam from the stainless steel powder during the production of the covering layer D. The core region K of the hard material particles HP is in each case surrounded by a mixing zone M, in which material of the hard material particle HP is mixed with the stainless steel material of the stainless steel matrix E of the covering layer D. Via the mixing zone M, the hard material particles HP with their core region K are materially bonded to the stainless steel matrix E. It can be seen that in the tests carried out according to the invention, i.e. with a laser intensity for which 0.1 laser intensity 2.5, the core regions K of the hard material particles HP in the stainless steel matrix E were present in a clearly defined shape. In contrast, in test 3 not being in accordance with the invention due to the excessively high laser intensity, the hard material particles HP are melted and strongly deformed, so that they did not correspond to the original state in which they have been provided, either in terms of their shape or their properties. Rather, the regions visible as dark dots inFIG.4as a whole consist only of mixing zones in which the completely melted material of the hard phases is mixed with the stainless steel material of the stainless steel matrix E. REFERENCE SIGNS 1Brake disk2Base body of the brake disk13Support part of the brake disk14Friction ring of the brake disk15a,5bFriction surface of the friction ring46PoresB CoatingD Covering layer of the coating BDd Thickness of the covering layer DDz Thickness of the intermediate layer ZE Stainless steel matrix of the covering layer DG Iron casting material of the brake disk1HP Hard material particlesK Core region of the hard material particlesX Rotational axis of the brake disk1Z Intermediate layer of the coating BM Mixing layer surrounding the hard material particles HP | 7,173 |
11859684 | DETAILED DESCRIPTION FIG.1shows a drive unit1only in regions and in the region of a decoupled fastening on a carrier component3.FIG.1shows a section through a rubber-elastic bearing4, the rubber-elastic bearing4being accommodated in the housing8with a first portion5between a first housing part6and a second housing part7. The rubber-elastic bearing4extends from the first portion via a connection element9to a second portion10toward the carrier component3. In this embodiment, the rubber-elastic bearing4is designed as a hollow profile having a recess11. The rubber-elastic bearing4is shown inFIG.1in section and in a side view, the rubber-elastic bearing4in this exemplary embodiment being describable as cylindrical or round. The connection element9forms a stepped hollow-cylindrical profile. A joining aid12extends into the recess12. In this exemplary embodiment, the joining aid12is integral with the second housing part7, but it is also conceivable that the joining aid12can be connected to the second housing part7as a separate component along a dividing line13. In this case, the joining aid12could be connected to the second housing part as a separate component. The joining aid12extends, starting from the first portion5of the rubber-elastic bearing, through the connection element9into the region of the second portion10of the rubber-elastic bearing4. As indicated by the axis of symmetry H, at least the rubber-elastic bearing4and the joining aid12are symmetrical. In any case, the joining aid12extends from the first portion5, in which the bearing4, the electric motor, the first housing part6and the second housing part7and an extension14are integrated or fixed, into the connection element9. The shape of the joining aid12is selected such that the bearing4acts independently of the joining aid12in the context of the decoupling movement between the housing8and the carrier component3. In other words, the rubber-elastic bearing4is not impaired by the joining aid in the context of decoupling the drive unit1from the carrier component3. An axial end15of the joining aid12extends into the second portion10of the bearing4. The second portion10can also be described as a joining region10. In the joining region10, a circumferential annular groove16is formed in the bearing4which circumferentially surrounds a bore17in the carrier component3and in which the circumferential annular groove16is held. The joining region10thus fits interlockingly into the carrier component3. The annular groove16advantageously makes it possible to connect the bearing4to carrier components3of different thicknesses, such that the elastic bearing4can be used in many different regions of the vehicle. As can be clearly seen inFIG.1, a force F can be introduced into the joining region10by means of the joining aid12in order to securely connect the joining region10to the carrier component3. The axial end15has sufficient play S in order, on the one hand, to allow easy joining of the joining region10and, on the other hand, not to impair the elasticity of the bearing4. The joining aid12can thus ensure easy and secure joining of the bearing4to the carrier component3. FIG.2shows an alternative embodiment of a connection between a drive unit18and a carrier component19. The carrier component19has a spherical cut-out20into which a spherical head21can be interlockingly inserted. The spherical head21can be made of plastics material or metal, for example. An advantageous material pairing results when the carrier component19is made of plastics material and the spherical head21is made of a metal material. The spherical head21is, for example, integrally bonded to a rubber-elastic bearing22. The rubber-elastic bearing22has an accordion-like connection element23which connects the second portion24of the rubber-elastic bearing22to the first portion25. A joining aid27is in turn formed integrally on a second housing part26, such that when the drive unit18is installed, it is possible to join the spherical head21and this joining can be assisted by a force from the joining aid27. FIG.3shows an alternative embodiment of a rubber-elastic bearing28. The rubber-elastic bearing28connects a carrier component29to a housing30, the joining aid31being integral with the rubber-elastic bearing28in this exemplary embodiment. In this exemplary embodiment, the rubber-elastic bearing28has two circumferential annular grooves32,33, a first annular groove23being connectable to the housing30and a second annular groove32being connectable to the carrier component29. The rubber-elastic bearing28is usually connected to the housing30of the drive unit and installed on the carrier component29. When joining the elastic bearing28, secure and easy joining of the joining region34of the rubber-elastic bearing28can now be assisted and achieved by means of the joining aid31. LIST OF REFERENCE SIGNS 1,18drive unit2decoupled fastening3,19,29carrier component4,22,28rubber-elastic bearing5,25first portion6first housing part7,26second housing part8,30housing9,23connection element10,24,34second portion, joining region11recess12,27,31joining aid13dividing line14extension15axial end16,32,33annular groove17bore20cut-out21spherical headA axis of symmetryF forceS play | 5,246 |
11859685 | DESCRIPTION OF THE EMBODIMENTS The technical solution of the present invention is further described in detail below in combination with the drawings and specific embodiments. Embodiment 1: as shown inFIG.1andFIG.2, a formation method for liquid rubber composite nodes with middle damping holes includes the following steps. Adding a middle spacer sleeve3between an outer sleeve1and a mandrel2, bonding the middle spacer sleeve3and the mandrel2together through rubber4vulcanization, and assembling the integrated middle spacer sleeve and the mandrel into the outer sleeve1. Forming damping through holes which penetrate through the mandrel2on the mandrel2. Hollowing the middle spacer sleeve3to form a plurality of spaces. After vulcanization, forming a plurality of interdependent liquid cavities5by using rubber4and the plurality of spaces, and arranging liquid (not shown in the figure) in the plurality of liquid cavities5and communicating the plurality of liquid cavities5through the damping through holes6. The liquid rubber composite nodes formed by the above method can provide small radial stiffness and large axial stiffness to realize a large dynamic-static ratio, thereby optimizing the product performance of the liquid rubber composite nodes. The test data of several samples by the applicant are as follows: RadialAxialDynamic-StaticStiffnessStiffnessRatioSample 15.6813.166.5:1Sample 25.5712.627:1Sample 35.5412.386:1Sample 45.3413.026:1Sample 55.2511.685:1 As shown inFIG.1andFIG.2, in the present embodiment, two liquid cavities5are arranged (the upper liquid cavity at the top and the lower liquid cavity at the bottom inFIG.1). During work, the two liquid cavities need to be communicated to ensure that liquid can flow back and forth between the two liquid cavities. In the present embodiment, a perforated damping through hole6is arranged along the radial direction of the mandrel2on the mandrel2, and the upper liquid cavity and the lower liquid cavity are communicated through the damping through hole6. As shown inFIG.1toFIG.4, the formation method for the liquid cavities is as follows: firstly, two spaces (spaces X1and X2inFIG.4) are dug out on the middle spacer sleeve3. The space X1and the space X2are similar to through holes, and the outer ends and the inner ends of the spaces are open. Here, one end of the space adjacent to one side of the mandrel2is regarded as the inner end and one end of the space away from one side of the mandrel2is regarded as the outer end. In order to ensure that the liquid cavities can store the liquid, openings on both ends of each space need to be sealed so that each space is independently formed. In the present embodiment, when the openings at the inner ends of the spaces are sealed, the openings are sealed by the rubber4, i.e., the openings at the inner ends of the spaces are blocked by the vulcanized rubber4after the mandrel2and the middle spacer sleeve3are bonded together through rubber4vulcanization. When the openings at the outer ends of the spaces are sealed, an arc cover plate7is covered on the hollowed middle spacer sleeve3and used for blocking the openings at the outer ends of the spaces so that each space forms an independent liquid cavity. As shown inFIG.5, a step part8is arranged on the middle spacer sleeve3at the periphery of the openings on the outer ends of the spaces, a complete ring of the step part8is arranged along the openings at the outer ends of the spaces, and the arc cover plate7is covered on the step part8. One effect of the step part8is to serve as a positioning structure to facilitate the positioning and assembly of the arc cover plate7. In the present embodiment, the mandrel, the outer sleeve, the middle spacer sleeve and the arc cover plate can be made of metal materials. As shown inFIG.3, a rubber coating at the outer circumferential surface of the mandrel in the liquid cavities is also provided with a first rubber coating through hole411and a second rubber coating through hole. One end of the damping through holes6is communicated with one liquid cavity5through the first rubber coating through hole411, and the other end of the damping through holes6is communicated with another liquid cavity5through the second rubber coating through hole, thereby communicating the two liquid cavities5through the damping through holes6. To ensure that the damping through holes are communicated with the rubber coating through holes, the projections of the damping through holes on the axial projection surface along the mandrel and the projections of the rubber coating through holes on the axial projection surface along the mandrel need to be completely coincident or partially coincident. The diameter of the rubber coating through holes is set as D1and the diameter of the damping through holes is set as D2. Then, in the present embodiment, D1>D2. In this design, firstly, the difficulty of assembly can be reduced and assembly is facilitated. In addition, a damping force can be generated when the liquid flows through the damping through holes. The size of the damping force can be adjusted by adjusting the size of D2. As shown inFIG.5, in order to further ensure the sealing performance of the openings at the outer ends of the spaces, it is also necessary to match rubber coating with pressing mounting. Namely, in the present embodiment, the step part8is a one-level step, and the rubber is coated onto the step part8. Rubber coating thickness here can be set according to actual conditions. During assembly, the mandrel2and the hollowed middle spacer sleeve3are vulcanized into a whole through the rubber4, the rubber is coated on the step part8and then the arc cover plate7is covered on the step part8, so that the arc cover plate7is in contact with the rubber coating on the step part8. Then, the middle spacer sleeve3with the arc cover plate7is in interference assembly into the outer sleeve1, the arc cover plate7is pressed on the step part8by the acting force generated after the assembly, so that the rubber coating on the step part8is deformed to achieve a sealing effect. After the outer sleeve1is assembled, a certain reduction amount can be further designed to further improve the sealing effect. The middle spacer sleeve adopts an integral spacer sleeve or a multi-disc spacer sleeve. In the present embodiment, the multi-disc spacer sleeve is adopted, such as two-disc structure and three-disc structure. Specifically, in the present embodiment, a four-disc structure is adopted. As shown inFIG.4, the middle spacer sleeve3in the present embodiment is a four-disc spacer sleeve comprising a left arc disc body311, a right arc disc body312, an upper arc disc body313and a lower arc disc body314. Four disc bodies are circumferentially enclosed to form a spacer sleeve. As shown inFIG.7, after the middle spacer sleeve is bonded with the mandrel through rubber vulcanization, before interference assembly, a gap E (such as the gap E between one end of the left arc disc body311and one end of the lower arc disc body314inFIG.7) is reserved between the end surfaces of two close ends of adjacent disc bodies. An open gap F is also reserved in the rubber4and at each gap E. However, after the interference assembly of the nodes, as shown inFIG.6, under the influence of the acting force, the gap E and the adjacent open gap F disappear, i.e., the end surfaces of two close ends of adjacent disc bodies come into contact with each other and the open gap F is also filled with the deformed rubber4, so that the performance of the assembled product can be further enhanced. As shown inFIG.7, in the present embodiment, the open gap F is a U-shaped groove. The opening of the U-shaped groove faces the gap E and the radial extension lines of the middle spacer sleeve on the edges of both sides of the U-shaped groove respectively coincide with the end surfaces of two close ends of two disc bodies at the gap E. The depth of the U-shaped groove is designed according to the actual assembling conditions. The open gap F is set to ensure that the end surfaces of two close ends of each disc body come into contact with each other after the assembly, and the rubber may not enter therebetween. In the design of the multi-disc middle spacer sleeve, equal design or non-equal design can be adopted. In the present embodiment, the non-equal design is adopted, i.e., by taking a center point of the middle spacer sleeve as a circle point, circle center angles corresponding to the plurality of arc disc bodies are unequal. As shown inFIG.4, the circle center angles corresponding to the radian of the upper arc disc body313and the lower arc disc body314are set as a, and the circle center angles corresponding to the left arc disc body311and the right arc disc body312are set as β, and α>β. This is because in the present embodiment, the hollowed arc disc bodies are the radian of the upper arc disc body313and the lower arc disc body314. After hollowing, by taking the radian of the upper arc disc body313and the direction of the lower arc disc body314(Y direction in the figure) as a void direction and taking the direction of the left arc disc body311and the right arc disc body312(X direction in the figure) as a solid direction, the radian of the arc disc body in the void direction is maximized to maximize the volume of the liquid cavities, thereby benefiting the improvement of product performance. In addition, the radial stiffness in the void direction can be reduced. In the present embodiment, α is 120 degrees and β is 60 degrees. The hollowed disc bodies may be any disc body in the multi-disc middle spacer sleeve. In the present embodiment, the radian of the upper arc disc body313and the lower arc disc body314, which are symmetrically arranged about the axial direction of the mandrel2, are hollowed to form the liquid cavities. In order to provide nonlinear stiffness properties by liquid rubber, a design solution of a matching structure between the metal cover and the mandrel is adopted. The present invention is described below in embodiment 1, embodiment 2 and embodiment 3. In the present embodiment 1, as shown inFIG.2,FIG.3andFIG.8, the inner circumferential arc surface of the arc cover plate7is provided with a bump711that protrudes towards the mandrel2. During work, when the node is loaded, the bump711comes into contact with the rubber4covered on the outer circumferential surface of the mandrel2to provide nonlinear stiffness properties, and under the further effect of the load, the bump711comes into indirect contact with the mandrel2to form the protection function of hard stop limiting. In the present embodiment, the rubber in contact with the bump711is specifically configured as an externally convex rubber block412. The shape and the size of the rubber block412are matched with the shape and the size of the bump711. The protrusion direction of the rubber block412is in a mutually protruding state with the protrusion direction of the bump711, and the contact surfaces of the rubber block412and the bump711are configured as arc surfaces. Because the rubber block412and the bump711are mutually matched, the contact surface of the bump711is an inwards concave arc surface and the contact surface of the rubber block412is an outwards convex arc surface (as shown inFIG.1). Under the effect of the load, the gap H between the bump711and the rubber block412gradually disappears. After the gap H disappears, the bump711and the rubber block412come into contact with each other, and the node begins to provide nonlinear stiffness properties. At this moment, through the contact between the bump711and the rubber block412, a buffer effect can also be provided through the rubber block412to avoid hard contact. Therefore, a nonlinear stiffness curve can be adjusted by adjusting the size of the gap H. In the present embodiment, bumps711are arranged on the inner circumferential arc surfaces of two arc cover plates7. The corresponding convex rubber blocks412are arranged on the outer circumferential surface of the mandrel2corresponding to the two bumps711. One bump711and one corresponding rubber block412as well as the other bump711and the other corresponding rubber block412are respectively located in two liquid cavities5. It should be noted here that through the above design of the arc cover plates7, the bumps711and the rubber blocks412, the volume size of the liquid cavities is also influenced. The volume of the bumps711and the rubber blocks412can be designed to be smaller, so that the volume of the liquid cavities is larger and more liquid can be accommodated. The liquid cavities in the present embodiment are small-volume liquid cavities, and the nodes of the small-volume liquid cavities can provide larger dynamic stiffness properties under the same stiffness. As shown inFIG.2, the mandrel2is formed as follows: a mandrel is formed by taking a central axis I of the mandrel2as a bus and taking a saddle surface J, which is high at both ends and low in the middle, as a rotating surface. Through this arrangement of the mandrel, the rubber4between the mandrel and the middle spacer sleeve is divided into two parts. One part of the rubber is middle rubber413, and the other part of the rubber is end rubber414located at both ends of the middle rubber413. The thickness of the middle rubber413along the radial direction of the mandrel is set as radial thickness K1, and the thickness of the end rubber414along the axial direction of the mandrel is set as axial thickness K2. During work, the middle rubber413mainly provides the radial stiffness, and the end rubber414mainly provides the axial stiffness. In this way, the radial thickness K1and the axial thickness K2are adjusted to adjust the radial stiffness and the axial stiffness of the nodes. A liquid injection hole9is also arranged on the mandrel2. The liquid injection hole9is communicated with one liquid cavity5. At the beginning, the liquid is injected into the liquid cavity5through the liquid injection hole9, and then sealed. Embodiment 2: as shown inFIG.9, compared with embodiment 1, the differences are that: in order to provide nonlinear stiffness properties by the liquid rubber, the present embodiment adopts the following solution. No bump is arranged on the inner circumferential arc surface of the arc cover plate7in the present embodiment, and a mandrel bump211is arranged on the mandrel2, and the rubber4is covered on the mandrel2and the mandrel bump211to form along them. Under the effect of the load, the arc cover plate7firstly comes into contact with the rubber4located in the liquid cavities and the nodes start to provide nonlinear stiffness characteristics. Under the further effect of the load, the arc cover plate7comes into indirect contact with the mandrel bump211to form the protection function of hard stop limiting. In the present embodiment, corresponding convex mandrel bumps211are arranged at the outer circumferential surfaces of the mandrel2corresponding to the two arc cover plates7. The two mandrel bumps211are respectively located in two liquid cavities5. Embodiment 3: as shown inFIG.10, compared with embodiment 1, the differences are that: in order to provide nonlinear stiffness properties by the liquid rubber, the present embodiment adopts the following solution. No bump is arranged on the arc cover plate7and the mandrel2in the present embodiment, and rubber bumps415that protrude towards the arc cover plate7are only arranged on the rubber4located on the outer circumferential surface of the mandrel2covered in the liquid cavity. When the arc cover plate7comes into contact with the rubber bumps415, the nodes start to provide nonlinear stiffness characteristics, but in the present embodiment, the nodes have no protection function of hard stop limiting. In the present embodiment, the two rubber bumps415are respectively located in two liquid cavities5. Embodiment 4: as shown inFIG.11, compared with embodiment 1, the difference of the present embodiment is that: both ends of the outer sleeve1in the present embodiment adopt flanging buckling design structures. A continuous first step part10and a second step part11are arranged on one end of the middle spacer sleeve3. The first step part10is positioned in a lower position (near the mandrel), and the second step part11is positioned in an upper position (far away from the mandrel). The end surface of one end of the outer sleeve1is vertically flush with the side vertical surface of the second step part11. An end sealing ring12is arranged on the second step part11. When the flanging buckling is not performed, the height of the end sealing ring12is larger than the height of the second step part11, i.e., the end sealing ring12is positioned between the second step part11and the outer sleeve1. An outer sleeve flanging part111is extended on the end surface of one end of the outer sleeve1. During flanging operation, the end sealing ring12is pressed by flanging and bending the outer sleeve flanging part111, and the end sealing ring12is used to seal an end gap P of the contact surface between the outer sleeve1and the middle spacer sleeve3to further enhance the sealing performance of the node. The outer sleeve flanging part111is flanged to the side vertical surface of the first step part10, so as to flange and position the flanging operation by the first step part10. After the flanging operation, a gap T is reserved between the end part of the outer sleeve flanging part111and a horizontal bottom surface of the first step part10. The other end of the middle spacer sleeve3is also provided with a continuous first step part and a second step part, and the end surface of the other end of the overall outer sleeve is also extended with the outer sleeve flanging part. The flanging buckling design structure at the other end of the middle spacer sleeve is the same as the flanging buckling design structure at one end of the above middle spacer sleeve, and will not be repeated here. Embodiment 5: as shown inFIG.12andFIG.13, compared with embodiment 1, the differences are that: the step part8arranged on the middle spacer sleeve3is a two-level step and has a first spacer sleeve step part811and a second spacer sleeve step part812. The first spacer sleeve step part811is located near one side of the outer sleeve1, i.e., the outer side, and the second spacer sleeve step part812is located near one side of the mandrel, i.e., the inner side. The rubber is coated to the second spacer sleeve step part812, and the arc cover plate7at the contact point with the step part is correspondingly arranged into the shape of multi-level steps, including a first cover plate step part712and a second cover plate step part713. During assembly, when the arc cover plate7is covered on the step part8, the first cover plate step part712is connected with the first spacer sleeve step part811in a metal interference fit mode, and the second cover plate step part713is connected with the second spacer sleeve step part812in a rubber-metal over-pressure fit mode, i.e., the rubber4is pressed on the second spacer sleeve step part812by the second cover plate step part713. This arrangement avoids the problem of internal liquid leakage caused by the failure of over-pressure fit between the metal and the rubber due to the relaxation of the rubber after long-term use. After the integral middle spacer sleeve and the mandrel are assembled into the outer sleeve1, the end part of contact between the outer sleeve1and the middle spacer sleeve3is chamfered, and then applied with solid gum13to further increase the sealing effect. Embodiment 6: as shown inFIG.14, compared with embodiment 5, the differences are that: a rubber groove14is arranged on the first spacer sleeve step part811. Before assembly, the solid gum is applied in the rubber groove14. During assembly, when the first cover plate step part712and the first spacer sleeve step part811are connected by the metal interference fit mode, the solid gum is also in contact with the first cover plate step part712to further increase the sealing effect. Embodiment 7: as shown inFIG.15, compared with embodiment 5, the differences are that: a sealing groove15is formed on the first spacer sleeve step part811. Before assembly, a sealing ring16is assembled in the sealing groove15. During assembly, when the first cover plate step part712and the first spacer sleeve step part811are connected in the metal interference fit mode, the sealing ring16is also pressed in the sealing groove15by the first cover plate step part712to further increase the sealing effect. Embodiment 8: as shown inFIG.16, compared with embodiment 5, the differences are that: a cover plate sealing groove17is formed on the second cover plate step part713. When the rubber is coated on the second spacer sleeve step part812, a sealing bulge416is formed on the rubber4. During assembly, when the second cover plate step part713presses the rubber4onto the second spacer sleeve step part812, the sealing bulge416is positioned in the cover plate sealing groove17and is extruded and contacted by the cover plate sealing groove17. Embodiment 9: as shown inFIG.17, compared with embodiment 5, the differences are that: in the present embodiment, the sealing forms in embodiment 8 and embodiment 6 can also be combined to further enhance the sealing effect, i.e., a cover plate sealing groove17is formed on the second cover plate step part713. When the rubber is coated on the second spacer sleeve step part812, a sealing bulge416is formed on the rubber4. During assembly, when the second cover plate step part713presses the rubber4onto the second spacer sleeve step part812, the sealing bulge416is positioned in the cover plate sealing groove17and is extruded and contacted by the cover plate sealing groove17. A rubber groove14is arranged on the first spacer sleeve step part811. Before assembly, the solid gum is applied in the rubber groove14. During assembly, when the first cover plate step part712and the first spacer sleeve step part811are connected by the metal interference fit mode, the solid gum is also in contact with the first cover plate step part712to further increase the sealing effect. Embodiment 10: as shown inFIG.18, compared with embodiment 8, the differences are that: in the present embodiment, the sealing forms in embodiment 8 and embodiment 7 can also be combined to further enhance the sealing effect, i.e., a cover plate sealing groove17is formed on the second cover plate step part713. When the rubber is coated on the second spacer sleeve step part812, a sealing bulge416is formed on the rubber4. During assembly, when the second cover plate step part713presses the rubber4onto the second spacer sleeve step part812, the sealing bulge416is positioned in the cover plate sealing groove17and is extruded and contacted by the cover plate sealing groove17. A sealing groove15is formed on the first spacer sleeve step part811. Before assembly, a sealing ring16is assembled in the sealing groove15. During assembly, when the first cover plate step part712and the first spacer sleeve step part811are connected in the metal interference fit mode, the sealing ring16is also pressed in the sealing groove15by the first cover plate step part712to further increase the sealing effect. In conclusion, the present invention forms a plurality of independent liquid cavities capable of storing liquid by hollowing and vulcanizing the rubber on the middle spacer sleeve, then installs the damping through holes which penetrate through the mandrel on the mandrel, and communicates the plurality of liquid cavities by the damping through holes to form liquid rubber composite nodes, so as to provide small radial stiffness and large axial stiffness to realize a large dynamic-static ratio, thereby optimizing the product performance of the liquid rubber composite nodes. Through the design of the specific formation method of the liquid cavities, the liquid cavities can be formed smoothly and the quality of the product is guaranteed. When the middle spacer sleeve is designed into a multi-disc spacer sleeve, the assembly structure and the process thereof are designed so as to ensure that after the interference assembly is completed, direct contact is made between the end surfaces of the two adjacent ends of the adjacent disc bodies without rubber interference, which can further improve the performance of the assembled product. When the middle spacer sleeve is designed into a multi-disc spacer sleeve, the non-equal design is adopted for the middle spacer sleeve, and the volume space of the liquid cavities is enlarged as much as possible. The rubber in the middle of the middle spacer sleeve is divided into the middle rubber and the end rubber, and the radial thickness of the middle rubber and the axial thickness of the end rubber are adjusted to adjust the radial stiffness and the axial stiffness of the nodes. The sealing effect is further improved by the sealing structure design between the arc cover plate and the middle spacer sleeve. “A plurality of” in the present embodiment means a quantity of “two or more than two”. The above embodiments are merely used for illustration of the present invention, and not intended to limit the present invention. Various changes or transformations can also be made by those skilled in the art without departing from the spirit and the scope of the present invention. Therefore, all equivalent technical solutions shall also belong to the protection scope of the present invention, and the protection scope of the present invention shall be defined by the claims. | 25,703 |
11859686 | DETAILED DESCRIPTION The present disclosure is described in detail below with reference to specific embodiments. Specific Embodiment I As shown inFIG.1toFIG.7, the present disclosure provides an electromagnetic force control method of the magnetic disk type negative stiffness electromagnetic actuator. The electromagnetic force control method of the magnetic disk type negative stiffness electromagnetic actuator includes the following steps:Step 1: according to the static bearing capacity, selecting a mechanical spring for providing positive stiffness of a vibration isolation system, and determining the positive stiffness of the spring.Step 2: establishing an electromagnetic force expression under magnetic unsaturation, and determining an electromagnetic attraction force of an electromagnet. The step 2 is specifically as follows:establishing an electromagnetic force expression under magnetic unsaturation, determining an electromagnetic attraction force of an electromagnet, and representing the electromagnetic attraction force of the electromagnet by the following formulas: Fmag1=12Φ12μ0Sin+12Φ12μ0Sout,Φ1=N1Ic1Rtotal1,Sout=π4(d62-d52),Sin=π4(r42-r32),wherein Fmag1represents an electromagnetic attraction force of an electromagnet1; Rtotal1represents a total reluctance of the electromagnet1; Φ1represents a magnetic flux of the electromagnet1; μ0represents permeability of vacuum; Sinrepresents an equivalent cross-sectional area of an inner magnetic pole; Soutrepresents an equivalent cross-sectional area of an outer magnetic pole; and Ic1represents a current passing into the coil1; anddetermining the total reluctance of the electromagnet1according to an air gap reluctance of an armature1and a reluctance of the armature1, and representing the total reluctance of the electromagnet1by the following formulas: Rtotal1=Rgap11+Rgap12+Rarm+Riron,Riron=lbμ1Sin+lbμ1Sout+laμ1S1,Rarm=l82μ1Sin+l82μ1Sout+ldμ1S2,Rgap11=x1μ0Sin,Rgap12=x1μ0Sout,S1=π16(l1-l2)(l3+l4+l5+l6),S2=π4l8(l3+l4+l5+l6),la=l5+l6-l3-l44,lb=l1+l22,wherein S1represents an equivalent cross-sectional area of a magnetic circuit in a horizontal direction of an iron core1; S2represents an equivalent cross-sectional area of a magnetic circuit in a horizontal direction of the armature1; x1represents an air gap of the electromagnet1; μ1represents a magnetic permeability of materials of the iron core1, an iron core2, the armature1and an armature2; Rgap11represents an air gap reluctance corresponding to an inner magnetic pole of the armature1; Rgap12represents an air gap reluctance corresponding to an outer magnetic pole of the armature1; Rarmrepresents the reluctance of the armature1; Rironrepresents a reluctance of the iron core1; N1represents the number of turns of a coil of the electromagnet1; l1represents a height of the iron core1; l2represents a height of a coil of the electromagnet1; l3represents an inner diameter of the armature1; l4represents an inner diameter of the coil of the electromagnet1; l5represents an outer diameter of the coil of the electromagnet1; l6represents an outer diameter of the iron core1; l7represents an outer diameter of the armature1; and l8represents a height of the armature1.Step 3: enabling a negative stiffness electromagnetic actuator to be symmetrical up and down, establishing an electromagnetic force-displacement expression according to the negative stiffness electromagnetic actuator under a condition of magnetic unsaturation, and determining an electromagnetic attraction force of the negative stiffness electromagnetic actuator under ideal conditions. The step 3 is specifically as follows:according to a structure that the negative stiffness electromagnetic actuator is symmetrical up and down, establishing an electromagnetic force-displacement expression of the negative stiffness electromagnetic actuator under the condition of magnetic unsaturation, determining an electromagnetic attraction force of the negative stiffness electromagnetic actuator under ideal conditions, and representing an electromagnetic attraction force under ideal conditions by the following formulas: Fmag=Fmag1-Fmag2=2N12Ic12μ0SinSout(Sin+Sout)[1(ax+b)2-1(ax-b)2],Fmag2=12Φ22μ0Sin+12Φ22μ0Sout,a=2(Sin+Sout),b=(l8μr+2lbμr+2g)(Sin+Sout)+2laμrSinSout(1S1+1S2),wherein Fmag2represents an electromagnetic attraction force of an electromagnet2; Φ2represents a magnetic flux of the electromagnet2; x represents a displacement of a negative stiffness spring; N2represents the number of turns of a coil of the electromagnet2; I2represents currents passing into a electromagnet2; μrrepresents a magnitude of a relative magnetic conductivity of materials of an iron core1, an iron core2, an armature1and an armature2; a represents an intermediate calculation variable about Sinand Sout; and b represents an intermediate calculation variable about l8, la, lb, Sin, Sout, S1, S2and μr;determining the magnetic flux of the electromagnet2according to the number of turns of the coil and the current of the electromagnet2and the total reluctance of the electromagnet2, and representing the magnetic flux of the electromagnet2by the following formulas: Φ2=N2I2Rtotal2,Rtotal2=Rgap21+Rgap22+Rarm+Riron,Rgap22=x2μ0Sout,wherein Rgap21represents an air gap reluctance corresponding to an inner magnetic pole of the armature2, and Rgap22represents an air gap reluctance corresponding to an outer magnetic pole of the armature2.Step 4: analyzing the electromagnetic force-displacement expression, and determining an expression about currents passing into upper and lower coils about a displacement, a magnitude of ideal constant value negative stiffness and a structural parameter when the negative stiffness electromagnetic actuator takes the current as an input control variable of a system. The step 4 is specifically as follows:Step 4.1: determining an electromagnetic force-displacement expression of the negative stiffness electromagnetic actuator, and making the electromagnetic force-displacement expression of the negative stiffness electromagnetic actuator equal to an electromagnetic force-displacement relationship of the negative stiffness electromagnetic actuator: Fmag=2N12Ic12μ0SinSout(Sin+Sout)[1(ax+b)2-1(ax-b)2]=kmx,Fmag=kmx,wherein kmrepresents the magnitude of the ideal constant value negative stiffness.Step 4.2: analyzing the electromagnetic force-displacement expression, and determining the expression about currents passing into upper and lower coils about the displacement, the magnitude of the ideal constant value negative stiffness and the structural parameter when the negative stiffness electromagnetic actuator takes the current as the input control variable of the system: Ic1=12aN1-kmμ0bSinSout(ax+b)2(ax-b)2,ax+b=(r8μr+2lbμr+2g+2x)(Sin+Sout)+2laμrSinSout(1S1+1S2)>0,b-ax=(r8μr+2lbμr+2(g-x))(Sin+Sout)+2laμrSinSout(1S1+1S2)>0,ax-b<0,Ic1=12aN1-kmμ0bSinSoutb2-a2N1-kmμ0bSinSoutx2=I1-I22,I1=12aN1-kmμ0bSinSoutb2,I2=a2N1-kmμ0bSinSoutx,wherein Ic1(Ic2=Ic1) represents currents passing into the coil1and the coil2at the same time.Step 5: establishing a vibration isolation system dynamic formula, and determining a vibration response according to the electromagnetic attraction force of the negative stiffness electromagnetic actuator under ideal conditions. The step 5 is specifically as follows:Step 5.1: establishing a vibration isolation system dynamic formula, and substituting an ideal electromagnetic force form into a dynamic mathematical model of a vibration isolation system by the following formulas: m{umlaut over (x)}+c({dot over (x)}t−{dot over (x)}e)+km(xt−xe)+k(xt−xe)=0, xe=Xecos(wet), x=xt−xe,wherein m represents a vibration-isolated mass; {umlaut over (x)}trepresents a vibration response acceleration of a vibration-isolated object; {dot over (x)}trepresents a vibration response speed of the vibration-isolated object; xerepresents a system excitation; {dot over (x)}erepresents a system excitation speed; c represents a system damping; xtrepresents a vibration response of the vibration-isolated object; Xerepresents an excitation amplitude; and werepresents an excitation frequency.Step 5.2: under ideal conditions, when a magnitude of an absolute value of negative stiffness is the same as that of positive stiffness and an overall dynamic stiffness of the system is zero, that is, km+k=0, representing a dynamic mathematic model of the vibration isolation system by the following formula: x¨t+cmx.t=-cXewemsin(wet),determining a displacement response, and representing a vibration response by the following formulas: xt=xt11+xt12xt11=C1+C2e-cmt,C1=-Xe,C2=Xem2we2m2we2+c2,xt12=C3cos(wet)+C4sin(wet)=C32+C42sin[wet+arctan(C3C4)],C3=Xec2m2we2+c2,C4=cXemwem2we2+c2,wherein xt11represents a solution corresponding to a free vibration response; xt12represents a particular solution corresponding to a forced vibration response; C1represents a particular solution coefficient 1 corresponding to the free vibration response; C2represents a particular solution coefficient 2 corresponding to the free vibration response; C3represents a particular solution coefficient 1 corresponding to the forced vibration response; and C4represents a particular solution coefficient 2 corresponding to the forced vibration response.Step 5.3: when stiffness of the negative stiffness mechanism is positive stiffness, that is, km+k>0, representing a dynamic mathematic model of the vibration isolation system by the following formula: x¨t+cmx.t+km+kmxt=km+kmXecos(wet)-cmXewesin(wet),determining a displacement response, and representing the displacement response by the following formulas: xt=xt21+xt22,xt21=C7e-c2mtcos(km+kdmt)+C8e-c2mtsin(km+km-c24m2t),C7=-Xe[(km+k)(km+k-mwe2)+c2we2](km+k-mwe2)2+c2we2,C8=-cXe{2m2we4+[(km+k)(km+k-mwe2)+c2we2]}4m(km+k)+c2[(km+k-mwe2)2+c2we2],xt22=C9cos(wet)+C10sin(wet)=C92+C102sin[wet+arctan(C9C10)],C9=Xe[(km+k)(km+k-mwe2)+c2we2](km+k-mwe2)2+c2we2,C10=cmXewe3(km+k-mwe2)2+c2we2,wherein xt21represents a solution corresponding to a free vibration response; xt22represents a particular solution corresponding to a forced vibration response; C7represents a particular solution coefficient 1 corresponding to the free vibration response; C8represents a particular solution coefficient 2 corresponding to the free vibration response; C9represents a particular solution coefficient 1 corresponding to the forced vibration response; and C10represents a particular solution coefficient 2 corresponding to the forced vibration response.Step 6: according to the vibration response and based on the expression about currents about a displacement, a magnitude of ideal constant value negative stiffness and a structural parameter, determining a control current required for meeting a linear electromagnetic force-displacement relationship of a negative stiffness electromagnetic actuator. The step 6 is specifically as follows:under ideal conditions, when a magnitude of a value of negative stiffness is the same as that of positive stiffness, that is, km=−k, representing the control current Ic1(Ic2) by the following formulas: Ic1=I1-(I21+I22+I231-I232)2,I1=12aN1-kmμ0bSinSoutb2,I2=I21+I22+I231-I232=a2N1-kmμ0bSinSout=C0x=C0(xt-xe)=C0xt11+C0xt12-C0xe,=C0C1+C0C2e-cmt+C0C32+C42sin[wet+arctan(C3C4)]-C0Xecos(wet)=Uc1+R1I22+L1dI22dt=0,(cm)2=(R12L1)2=1L1C1′,Uc1(0)=(cm-R1)C0C2,wherein C′1represents a resistance value of a capacitor; R1represents a sum of a resistance value of a circuit and a resistance value of a coil; L1represents an inductance of a circuit1; I1represents a control current1; I2represents a control current2; I21represents a component1of the control current2; I22represents a component2of the control current2; I231represents a component3of the control current2; I232represents a component4of the control current2; C0represents a linear coefficient between the control current I2and a working displacement x; Uc1represents a real-time voltage of a capacitor1; and Uc1(0) represents a voltage before the capacitor1starts to work; andwhen the magnitude of the value of the negative stiffness is less than that of the positive stiffness, that is, km+k>0, representing the control current Ic1(Ic2) by the following formulas: Ic1=I1-I2′2=I1-(I21′+I22′+I231′-I232′)2,I1=12aN1-kmμ0bSinSoutb2,I2′=C0′(xt-xe)=C0′xt21+C0′xt22-C0′xe=C0′C7e-c2mtcos(km+kmt)+C0′C8e-c2mtsin(km+km-c24m2t)+C0′C92+C102sin[wet+arctan(C9C10)]-C0′Xecos(wet)=I21′+I22′+I231′-I232′C0′=a2N1-kmμ0bSinSout,Uc2+R2I22′+L2dI22′dt=0,c2m=R22L2,km+km=1L2C2′-R224L22,Uc2(0)=(L2c2m-R2)C0′C7,Uc3+R3I23′+L3dI23′dt=0,c2m=R32L3,km+km-c24m2=1L3C3′-R324L32,Uc3(0)=-km+kmC0′C8,wherein C′2represents a resistance value of a capacitor2; R2represents a sum of a resistance value of a circuit2and a resistance value of a coil; L2represents an inductance of the circuit2; C′3represents a resistance value of a capacitor3; R3represents a sum of a resistance value of a circuit3and the resistance value of the coil; L3represents an inductance of the circuit3; I1represents a control current1; I′2represents a control current2′; I′21represents a component1of the control current2′; I′22represents a component2of the control current2′; I′231represents a component3of the control current2′; I′232represents a component4of the control current2′; C′0represents a linear coefficient between the control current I′2; and a working displacement x; Uc2represents a real-time voltage of the capacitor2; Uc2(0) represents a voltage before the capacitor2starts to work; Uc3represents a real-time voltage of the capacitor3; and Uc3(0) represents a voltage before the capacitor3starts to work. Specific Embodiment II An electromagnetic force control method of a magnetic disk type negative stiffness electromagnetic actuator includes the following steps:S1: according to the actually required static bearing capacity, reasonably selecting a mechanical spring for providing positive stiffness of a vibration isolation system, and determining a magnitude of the positive stiffness of the mechanical spring as k.S2: establishing a magnetic circuit model of a single electromagnet, as shown inFIG.3, and establishing an electromagnetic force mathematical model under a condition of magnetic unsaturation, as shown in formula (1-1) to formula (1-13): Fmag1=12Φ12μ0Sin+12Φ12μ0Sout,(1‐1)Sin=π4(l42-l32),(1‐2)Sout=π4(l62-l52),(1‐3)S1=π16(l1-l2)(l3+l4+l5+l6),(1‐4)S2=π4l8(l3+l4+l5+l6),(1‐5)la=l5+l6-l3-l44,(1‐6)lb=l1+l22,(1‐7)Rgap11=x1μ0Sin,(1‐8)Rgap12=x1μ0Sout,(1‐9)Rarm=l82μ1Sin+l82μ1Sout+ldμ1S2,(1‐10)Riron=lbμ1Sin+lbμ1Sout+laμ1S1,(1‐11)Rtotal1=Rgap11+Rgap21+Rarm+Riron,(1‐12)Φ1=N1Ic1Rtotal1,(1‐13)wherein Fmag1represents an electromagnetic attraction force of an electromagnet1; Φ1represents a magnetic flux of the electromagnet1; μ0represents permeability of vacuum; μ1represents a magnetic permeability of materials of an iron core1, an iron core2, an armature1and an armature2; Sinrepresents an equivalent cross-sectional area of an inner magnetic pole; Soutrepresents an equivalent cross-sectional area of an outer magnetic pole; S1represents an equivalent cross-sectional area of a magnetic circuit in a horizontal direction of the iron core1; S2represents an equivalent cross-sectional area of a magnetic circuit in a horizontal direction of the armature1; x1represents an air gap of the electromagnet1; Rgap11represents an air gap reluctance corresponding to an inner magnetic pole of the armature1; Rgap12represents an air gap reluctance corresponding to an outer magnetic pole of the armature1; Rarmrepresents a reluctance of the armature1; Rironrepresents a reluctance of the iron core1; Rtotal1represents a total reluctance of the electromagnet1; N1represents the number of turns of a coil of the electromagnet1; Ic1represents the current passing into the electromagnet1, as shown inFIG.3; l1represents a height of the iron core1; l2represents a height of the coil of the electromagnet1; l3represents an inner diameter of the armature1; l4represents an inner diameter of the coil of the electromagnet1; l5represents an outer diameter of the coil of the electromagnet1; l6represents an outer diameter of the iron core1; l7represents an outer diameter of the armature1, and l8represents a height of the armature1.S3: according to a structural characteristic that the negative stiffness electromagnetic actuator is symmetrical up and down as shown inFIG.4, establishing an “electromagnetic force-displacement” mathematical model of the negative stiffness electromagnetic actuator under the condition of magnetic unsaturation on the basis of step S2, as shown in formula (2-1). Fmag=Fmag1-Fmag2=2N12Ic12μ0SinSout(Sin+Sout)[1(ax+b)2-1(ax-b)2],(2‐1)Fmag2=12Φ22μ0Sin+12Φ22μ0Sout,(2‐2)Rgap21=x2μ0Sin,(2‐3)Rgap22=x2μ0Sout,(2‐4)Rtotal2=Rgap21+Rgap22+Rarm+Riron,(2‐5)Φ2=N2Ic2Rtotal2,(2‐6)a=2(Sin+Sout),(2‐7)b=(l8μr+2lbμr+2g)(Sin+Sout)+2laμrSinSout(1S1+1S2),(2‐8)wherein Fmag2represents an electromagnetic attraction force of an electromagnet2; Φ2represents a magnetic flux of the electromagnet2; Rgap21represents an air gap reluctance corresponding to an inner magnetic pole of an armature2; Rgap22represents an air gap reluctance corresponding to an outer magnetic pole of the armature2; Rtotal2represents a total reluctance of the electromagnet2; x1represents an air gap of the electromagnet1; x2represents an air gap of the electromagnet2; x represents a displacement of a negative stiffness spring; g represents a maximum value of a unilateral air gap; x1=x+g, x2=2g−x1=g−x; S1represents an equivalent cross-sectional area of a magnetic circuit in a horizontal direction of an iron core1; S2represents an equivalent cross-sectional area of a magnetic circuit in a horizontal direction of the armature1; μrrepresents a magnitude of a relative magnetic conductivity of materials of the iron core1, the iron core2, the armature1and the armature2; a represents an intermediate calculation variable about Sinand Sout; b represents an intermediate calculation variable about l8, la, lb, Sin, Sout, S1, S2and μr; N2represents the number of turns of a coil of the electromagnet2; in this embodiment, N2=N1; Ic2represents the current passing into the electromagnet2; in this embodiment, Ic2=Ic1; and when the negative stiffness spring is in a static balance position after being energized, the distribution of magnetic lines is as shown inFIG.4.S4: in order to enable a vibration-isolated object to have linear dynamic characteristics, making the “electromagnetic force-displacement” relationship of the negative stiffness electromagnetic actuator as shown in formula (3-1) equal to the “electromagnetic force-displacement” mathematical model of the negative stiffness electromagnetic actuator as shown in the above-mentioned formula (2-1), as shown in formula (3-2), analyzing the “electromagnetic force-displacement” mathematical model of the negative stiffness electromagnetic actuator under a condition of magnetic unsaturation, and determining an expression about currents passing into upper and lower coils about a displacement, a magnitude of ideal constant value negative stiffness and a related structural parameter when the currents are taken as an input control variable of a system, as shown in formulas (3-3), (3-4) and (3-5), wherein when the magnitude of the ideal constant value negative stiffness and the related structural parameter are determined, the current is a function about the displacement, that is, a function about the time, as shown in formulas (3-6) and (3-7). Fmag=2N12Ic12μ0SinSout(Sin+Sout)[1(ax+b)2-1(ax-b)2]=kmx,(3‐1)Fmag=kmx,(3‐2)Ic1=12aN1-kmμ0bSinSout(ax+b)2(ax-b)2,(3‐3)ax+b=(l8μr+2lbμr+2g+2x)(Sin+Sout)+2laμrSinSout(1S1+1S2)>0,(3‐4)b-ax=(l8μr+2lbμr+2(g-x))(Sin+Sout)+2laμrSinSout(1S1+1S2)>0,(3‐5)lc1=12aN1-kmμ0bSinSoutb2-a2N1-kmμ0bSinSoutx2,(3‐6)I1=12aN1-kmμ0bSinSoutb2,I2=a2N1-kmμ0bSinSoutx,(3‐7)wherein kmrepresents a magnitude of an ideal constant value negative stiffness.S5: establishing a vibration isolation system model as shown inFIG.5, and substituting an ideal electromagnetic force form as shown in formula (3-1) into the dynamic mathematical model of the vibration isolation system, as shown in formula (4-1), wherein when the excitation xeis determined, a solution of a vibration response is obtained by taking xt(0)=0 and {umlaut over (x)}t(0)=0 as equation conditions. m{umlaut over (x)}t+c({dot over (x)}t−{dot over (x)}e)+km(xt−xe)+k(xt−xe)=0 (4-1),wherein m represents a vibration-isolated mass; k represents positive stiffness of the system; c represents a system damping; xtrepresents a vibration response of a vibration-isolated object; {umlaut over (x)}trepresents a vibration response acceleration of the vibration-isolated object; {dot over (x)}trepresents a vibration response speed of the vibration-isolated object; xerepresents a system excitation; {dot over (x)}erepresents a system excitation speed; Xerepresents an excitation amplitude; werepresents an excitation frequency; xe=Xecos(wet), x=xt−xe. Under ideal conditions, when the magnitude of the absolute value of the negative stiffness is the same as that of the positive stiffness and the overall dynamic stiffness of the system is zero, that is, km+k=0, a dynamic mathematical model of the vibration isolation system is shown in formula (4-2), and the vibration response of the system is solved as shown in formulas (4-3) to (4-7): x¨t+cmx.t=-cXewemsin(wet),(4‐2)xt=xt11+xt12,(4‐3)xt11=C1+C2e-cmt,(4‐4)C1=-Xe,C2=Xem2we2m2we2+c2,(4‐5)xt12=C3cos(wet)+C4sin(wet)=C32+C43sin[wet+arctan(C3C4)],(4‐6)C3=Xec2m2we2+c2,C4=cXemwem2we2+c2,(4‐7)wherein xt11represents a solution of formula (4-2) corresponding to a free vibration response; xt12represents a particular solution of formula (4-2) corresponding to a forced vibration response; C1represents a particular solution coefficient 1 of formula (4-2) corresponding to the free vibration response; C2represents a particular solution coefficient 2 of formula (4-2) corresponding to the free vibration response; C3represents a particular solution coefficient 1 of formula (4-2) corresponding to the forced vibration response; and C4represents a particular solution coefficient 2 of formula (4-2) corresponding to the forced vibration response. Due to the processing design of the negative stiffness mechanism and the matching problem of the quasi-zero stiffness vibration isolator during installation, the overall dynamic stiffness of the system may still be positive stiffness, that is km+k>0. Then a dynamic mathematical model of the vibration isolation system is shown in formula (4-8). When c2−4m(km+k)<0, the vibration response of the system is solved as shown in formulas (4-9) to (4-13). x¨t+cmx.t+km+kmxt=km+kmXecos(wet)-cmXewesin(wet),(4‐8)xt=xt21+xt22,(4‐9)xt21=C7e-c2mtcos(km+kmt)+C8e-c2mtsin(km+km-c24m2t),(4‐10)C7=-Xe[(km+k)(km+k-mwe2)+c2we2](km+k-mwe2)2+c2we2,C8=-cXe{2m2we4+[(km+k)(km+k-mwe2)+c2we2]}4m(km+k)+c2[(km+k-mwe2)2+c2we2],(4‐11)xt22=C9cos(wet)+C10sin(wet)=C92+C102sin[wet+arctan(C9C10)],(4‐12)C9=Xe[(km+k)(km+k-mwe2)+c2we2](km+k-mwe2)2+c2we2,C10=cmXewe3(km+k-nwe2)2+c2we2,(4‐13)wherein xt21represents a solution of formula (4-8) corresponding to a free vibration response; xt22represents a particular solution of formula (4-8) corresponding to a forced vibration response; C7represents a particular solution coefficient 1 of formula (4-8) corresponding to the free vibration response; C8represents a particular solution coefficient 2 of formula (4-8) corresponding to the free vibration response; C9represents a particular solution coefficient 1 of formula (4-8) corresponding to the forced vibration response; and C10represents a particular solution coefficient 2 of formula (4-8) corresponding to the forced vibration response.S6: re-substituting the solution of the vibration response into the expression about the currents about the displacement, the magnitude of the ideal constant value negative stiffness and the related structural parameter, so as to obtain the input current required for meeting the linear “electromagnetic force-displacement” relationship of the negative stiffness electromagnetic actuator. According to formulas (3-6) and (3-7) in combination with the above-mentioned formulas (4-3) to (4-7) and formulas (4-9) to (4-13), under ideal conditions, when the magnitude of the value of the negative stiffness is the same as that of the positive stiffness, that is, km=−k, the formulas of the control current Ic1are shown in formulas (5-1) to (5-4), and the schematic circuit diagram is shown inFIG.6. When the vibration isolator is not working, there is no current input in other circuits, but a switch S1in an RLC circuit is closed, and a switch S2is switched off. Before working, a capacitor is charged to Uc1(0). During working, the switch S1is switched off; the switch S2is closed; and the capacitor starts to discharge. C′1represents a resistance value of a capacitor; R1represents a sum of a resistance value of a circuit and a resistance value of a coil; L1represents a sum of an inductance of the circuit and an inductance of the coil. Ic1=I1-I22=I1-(I21+I22+I231-I232)2,(5‐1)I1=12aN1-kmμ0bSinSoutb2,(5‐2)I2=a2N1-kmμ0bSinSout=C0x=C0(xt-xe)=C0xt11+C0xt12-C0xe=C0C1+C0C2e-cmt+C0C32+C42sin[wet+arctan(C3C4)]-C0Xecos(wet)=I21+I22+I231-I232,(5‐3)Uc1+R1I22+L1dI22dt=0,(cm)2=(R12L1)2=1L1C1′,Uc1(0)=(cm-R1)C0C2,(5‐4)wherein I1represents a control current1; I2represents a control current2; I21represents a component1of the control current2; I22represents a component2of the control current2; I231represents a component3of the control current2; I232represents a component4of the control current2; C0represents a linear coefficient between the control current I2and a working displacement x; Uc1represents a real-time voltage of a capacitor1; and Uc1(0) represents a voltage before the capacitor1starts to work. When the magnitude of the value of the negative stiffness is less than that of the positive stiffness, that is, km+k>0, the formulas of the control current I are shown in formulas (5-5) to (5-10), and the schematic circuit diagram is shown inFIG.7. When the vibration isolator is not working, there is no current input in other circuits, but switches S3and S5in2RLC circuits are closed, and switches S4and S6are switched off. Before working, the2capacitors are respectively charged to Uc2(0) and Uc3(0). During working, the switches S3and S5are switched off; the switches S4and S6are closed; and the capacitors start to discharge. C′2represents a resistance value of a capacitor2; R2represents a sum of a resistance value of a circuit2and a resistance value of a coil; L2represents a sum of an inductance of the circuit2and an inductance of the coil; C′3represents a resistance value of a capacitor3; R3represents a sum of a resistance value of a circuit3and the resistance value of the coil; and L3represents a sum of an inductance of the circuit3and the inductance of the coil. Ic1=I1-I2′2=I1-(I21′+I22′+I231′-I232′)2,(5‐5)I1=12aN1-kmμ0bSinSoutb2,(5‐6)I2′=C0′(xt-xe)=C0′xt21+C0′xt22-C0′xe=C0′C7e-c2mtcos(km+kmt)+C0′C8e-c2mtsin(km+km-c24m2t)+C0′C92+C102sin[wet+arctan(C9C10)]-C0′Xecos(wet)=I21′+I22′+I231′-I232′,(5‐7)C0′=a2N1-kmμ0SinSout,(5‐8)Uc2+R2I22′+L2dI22′dt=0,c2m=R22L2,km+km=1L2C2′-R224L22,Uc2(0)=(L2c2m-R2)C0′C7,(5‐9)Uc3+R3I23′+L3dI23′dt=0,c2m=R32L3,km+km-c24m2=1L3C3′-R324L32,Uc3(0)=-km+kmC0′C8,(5‐10)wherein I1represents a control current1; I′2represents a control current2′; I′21represents a component1of the control current2′; I′22represents a component2of the control current2′; I′231represents a component3of the control current2′; I′232represents a component4of the control current2′; C′0represents a linear coefficient between the control current I′2and a working displacement x; Uc2represents a real-time voltage of the capacitor2; Uc2(0) represents a voltage before the capacitor2starts to work; Uc3represents a real-time voltage of the capacitor3; and Uc3(0) represents a voltage before the capacitor3starts to work. The specific principle of the electromagnetic force control method of the magnetic disk type negative stiffness electromagnetic actuator according to the present disclosure is as follows: in the magnetic disk type quasi-zero stiffness vibration isolator as shown inFIG.2toFIG.5, the negative stiffness electromagnetic actuator is composed of two electromagnets which are symmetrical up and down and have the same size. During working, when upper and lower coils are simultaneously energized with direct currents having the same direction and the equal magnitude, and are in a static balance, upper and lower air gaps are equal, and the electromagnetic attraction force of an upper stator to a rotor component is equal to the electromagnetic attraction force of a lower stator to the rotor component. After an excitation is applied, if the rotor component has an upward movement trend, the upper air gap is greater than the lower air gap, and the electromagnetic attraction force of the upper stator to the rotor component is greater than the electromagnetic attraction force of the lower stator to the rotor component, thereby intensifying the upward movement trend of the rotor component. If the rotor component has a downward movement trend, the lower air gap is less than the upper air gap, and the electromagnetic attraction force of the lower stator to the rotor component is greater than the electromagnetic attraction force of the upper stator to the rotor component, thereby intensifying the downward movement trend of the rotor component. Therefore, negative stiffness characteristics are achieved. In this process, the currents passing into the upper and lower coils are direct currents having the equal magnitude and the same direction, as shown in formula (2-1); the “electromagnetic force-displacement” relationship of the negative stiffness electromagnetic actuator has serious non-linear characteristics, and the nature of the non-linear system thereof enables the dynamic characteristics of the vibration-isolated object to also present non-linearity, which may cause the multi-stable phenomenon, resulting in complex dynamic behaviors such as jumping during working. Therefore, the present disclosure controls the currents input into the upper and lower coils to enable the “electromagnetic force-displacement” relationship of the negative stiffness mechanism to have good linearity, and enable the magnitude of the negative stiffness to be a constant value km. By analyzing the established “electromagnetic force-displacement” mathematical model of the negative stiffness electromagnetic actuator, the expression about the currents about the displacement, the magnitude of the ideal constant value negative stiffness and the related structural parameter is determined when the currents are taken as the input control variable of the system; the ideal electromagnetic force in a linear form is substituted into a dynamic equation of the vibration-isolated object to obtain a solution of a vibration response; and the solution of the vibration response is then substituted into the expression about the currents about the displacement, the magnitude of the ideal constant value negative stiffness and the related structural parameter, so as to obtain the input current of the negative stiffness electromagnetic actuator required for realizing the linear “electromagnetic force-displacement” relationship. Specific implementation steps are as follows:A1: according to the actually required static bearing capacity, determining positive stiffness k of a mechanical spring required for a magnetic disk type quasi-zero stiffness vibration isolator.A2: establishing an electromagnetic force mathematical model of a single electromagnet under a condition of magnetic unsaturation.A3: establishing an “electromagnetic force-displacement” relationship mathematical model of the negative stiffness electromagnetic actuator on the basis of the electromagnetic force mathematical model of a single electromagnet.A4: analyzing the “electromagnetic force-displacement” mathematical model, and determining the expression about the currents about the displacement response, the magnitude of the ideal constant value negative stiffness and the related structural parameter when the currents are taken as the input control variable of the system.A5: establishing a dynamic mathematical model of a vibration isolation system with a linear electromagnetic force form as shown below, and determining a solution of the vibration response. When the magnitude of the value of the negative stiffness is the same as that of the positive stiffness, the overall dynamic stiffness of the system is zero, that is, km+k=0, and the vibration response of the system is solved as shown below. Due to the processing design of the negative stiffness mechanism and the matching problem of the quasi-zero stiffness vibration isolator during installation, the overall dynamic stiffness of the system may still be positive stiffness, that is, km+k>0. When c2−4m(km+k)<0, the vibration response of the system is shown below.A6: re-substituting the solution of the vibration response into the expression about the currents about the displacement, the magnitude of the ideal constant value negative stiffness and the related structural parameter, so as to obtain the input current required for meeting the linear “electromagnetic force-displacement” relationship of the negative stiffness electromagnetic actuator. When the magnitude of the absolute value of the negative stiffness is equal to that of the positive stiffness, that is, km=−k, the formulas of the control current Ic1(Ic2) are shown below (specifically shown in formulas (5-1) to (5-4)), and the schematic circuit diagram is shown inFIG.6. When the magnitude of the absolute value of the negative stiffness is less than that of the positive stiffness, that is, km+k>0, the formulas of the control current Ic1(Ic2) are shown in formulas (5-5) to (5-8), and the schematic circuit diagram is shown inFIG.7. In the present disclosure, according to the actually required static bearing capacity, the positive stiffness k of a mechanical spring required for a magnetic disk type quasi-zero stiffness vibration isolator is determined; an electromagnetic force mathematical model of a single electromagnet under the condition of magnetic unsaturation is established; an “electromagnetic force-displacement” relationship mathematical model of the negative stiffness electromagnetic actuator is established on the basis of the electromagnetic force mathematical model of a single electromagnet; the “electromagnetic force-displacement” mathematical model is analyzed; and the expression about the currents about the displacement response, the magnitude of the ideal constant value negative stiffness and the related structural parameter is determined when the currents are taken as the input variable of the system; a dynamic mathematical model of a vibration isolation system with a linear electromagnetic force form is established, and a solution of displacement response is determined; and the solution of the vibration response is substituted into the expression about the currents about the displacement, the magnitude of the ideal constant value negative stiffness and the related structural parameter, so as to obtain the input current required for meeting the linear “electromagnetic force-displacement” relationship of the negative stiffness electromagnetic actuator. The present disclosure aims at the magnetic disk type quasi-zero stiffness vibration isolator and takes the coil current as the input control variable, so that the electromagnetic force and displacement of the negative stiffness electromagnetic actuator have a linear relationship, thereby changing the non-linear nature of the vibration isolation system, avoiding the multi-stable phenomenon caused by non-linear electromagnetic force during working, and eliminating complex dynamic behaviors such as jumping when the whole vibration isolator works. Complex sensors and control systems are not needed, and implementation manners are simple and convenient. The above are only the preferred implementation manners of an electromagnetic force control method of a magnetic disk type negative stiffness electromagnetic actuator. The protection scope of the electromagnetic force control method of the magnetic disk type negative stiffness electromagnetic actuator is not limited to the above embodiments, and all technical solutions under this idea belong to the protection scope of the present disclosure. It should be noted that those skilled in the art can make several improvements and changes without departing from the principle of the disclosure, and these improvements and changes should also be regarded as the protection scope of the present disclosure. | 37,816 |
11859687 | DETAILED DESCRIPTION OF THE INVENTION In the context of the present description “personal care” shall mean the nurture (or care) of the skin and of its adnexa (i.e. hairs and nails) and of the teeth and the oral cavity (including the tongue, the gums etc.), where the aim is on the one hand the prevention of illnesses and the maintenance and strengthening of health (“care”) and on the other hand the cosmetic treatment and improvement of the appearance of the skin and its adnexa. It shall include the maintenance and strengthening of wellbeing. This includes skin care, hair care, and oral care as well as nail care. This further includes other grooming activities such as beard care, shaving, and depilation. A “personal care device” thus means any device for performing such nurturing or grooming activity, e.g. (cosmetic) skin treatment devices such as skin massage devices or skin brushes; wet razors; electric shavers or trimmers; electric epilators; and oral care devices such as manual or electric toothbrushes, (electric) flossers, (electric) irrigators, (electric) tongue cleaners, or (electric) gum massagers. This shall not exclude that the proposed personal hygiene system may have a more pronounced benefit in one or several of these nurturing or device areas than in one or several other of these areas. In the below description with reference to the figures, an epilation device was chosen to present details of the proposed personal care device. To the extent in which the details are not particular to an epilation device, the proposed technology can be used in any other personal care device. In accordance with the present disclosure, a moving motor part of a motor is coupled with a motor carrier by means of at least one spring element. The motor carrier is at least partially made from a sheet metal material and in particular the motor carrier may comprise a portion that is made from stamped and bent sheet metal. A sheet metal material used for the purpose of providing a mounting structure for a motor of a personal care device has a certain thickness that may be in a range of between 0.05 mm to 2.0 mm, in particular in a range of between 0.1 mm and 1.0 mm. In order to provide a structure for a connection of the spring element with the motor carrier, the sheet metal material has at least one connection area where the sheet metal material is folded such that two layers of sheet metal material are arranged vis-à-vis. A slot is provided in each of the layers such that the two slots are aligned (i.e. are at least partially congruent or overlapping in position and/or shape), and a connection extension of the spring element can be slid into the aligned slots in order to connect the spring element with the motor carrier. The spring element may comprise a motor connection portion by which the spring element is mounted at the movable motor part. The movable motor part may be connected at the motor carrier by means of at least two spring elements. The movable motor part may be mounted for linear vibratory motion, in particular for linear vibratory motion along an axis perpendicular to the extension plane of the spring element at rest. The motor may comprise more than one movable motor part. The spring element may in particular be realized by a flat spring made from spring sheet metal, which shall not exclude that two or more layers of spring sheet metal are connected with each other to form the spring element. One of the two layers of the connection area of the sheet metal material of the motor carrier may be closer (i.e. proximal) to the spring element and the other layer may then be farther away from (i.e. distal to) the spring element. In such embodiments, it is referred to the proximal layer and the distal layer of the folded connection area formed from the sheet metal material. It is contemplated that the slot in the proximal layer may at least in one region be smaller in width than the slot in the distal layer, in particular where the slot in the proximal layer may be smaller in width than the slot in the distal layer along its complete clamping length, i.e. the length that will get into contact with the connection extension of the spring element. In some embodiments, the slots each have a constant width and the width of the slot of the proximal layer is smaller than the width of the slot in the distal layer. In particular, the width of the slot in the proximal layer may be dimensioned so that a press fit between the connection extension of the spring element and the slot is established. And the slot in the distal layer may have a width dimensioned so that a transition fit is established between the connection extension of the spring element and the slot. The aligned slots may have a common opening at the folding edge, where the common opening may allow to slide an extension portion of the spring element into the pair of aligned slots. In some embodiments the common opening at the folding edge may comprise a chamfer that widens towards the folding edge to support sliding-in of the connection extension of the spring element into the aligned slots (e.g. in an automated process). The slot in the proximal layer may also have an opening in an edge opposite to the folding edge. A gap may extend between the two vis-à-vis arranged layers of sheet metal material of the connection area, which gap may have a width in the range of between 0.005 mm to 5.0 mm, in particular in the range of between 0.01 mm to 2.0 mm and further in particular in the range of between 0.05 mm and 1.0 mm. This shall not exclude that in some embodiments the two layers abut against each other without any intentional gap. The connection extension of the spring element may be held by clamping forces (i.e. friction forces) in the aligned slots. But the connection extension may in particular be fixedly secured at the sheet metal material, e.g. by means of welding or other connection technologies such as gluing, even though welding may be preferred for some motor applications. The fixation may be provided at the distal layer or at both layers. While it is contemplated that a gap may extend between the two layers of sheet metal material of the connection area, in some embodiments the two layers abut against each other and no intentional gap extends between the two layers. In particular in the latter case, the depth of the fixation (e.g. the welding depth) may extend from the distal layer through to the proximal layer. The motor as proposed herein may be used in a personal care device, e.g. in an electric toothbrush, where the motor may be used for driving a drive shaft of the electric toothbrush. FIG.1is an example depiction of a personal care device1that is here realized as an electrical toothbrush. The personal care device1has a head section10and a handle section20. In the shown example, the head section10is detachably attached to the handle section20so that the head section10can essentially not move with respect to the handle section20. The head section10comprises a treatment head11, here realized as a brush head. The treatment head11is arranged for driven oscillatory rotational motion around an axis A as indicated by double arrow R. The oscillatory rotational motion may be driven by a motor in accordance with the present description. The personal care device1extends along a longitudinal direction L. FIG.2is a depiction of an example motor100in accordance with the present description. The motor100as shown has two movable motor parts, namely an armature120and a counter-oscillating mass140. The first movable motor part120is mounted at a motor carrier110by means of two spring elements121and122. The second movable motor part140is mounted at the motor carrier110by means of two spring elements141and142. It shall be understood that a motor as proposed only needs to have a single movable motor part and that a movable motor part can also be mounted at the motor carrier by means of a single spring element. It shall also be understood that the counter-oscillating mass140, even so not actively driven into motion, but passively excited into a motion by the vibrations of the motor carrier110, is a movable motor part within the meaning of the present application. It is here noted that the terms “first” and “second” with respect to the movable motor parts shall not convey any particular meaning other than to say that the shown example has two movable motor parts. In some embodiments, the armature may not be mounted as proposed herein, but only the counter-oscillating mass may be respectively mounted. Then the counter-oscillating mass would the first (or only) movable motor part that is mounted in a manner as described herein. This may also be true the other way around. The motor carrier110is made from a sheet metal material1100that may have been stamped and bent (laser cutting or similar techniques may be used as well instead of stamping).FIG.3shows an example motor carrier110A made from stamped (or laser cut) and bent sheet metal material. Two stabilization elements111and112are fixedly secured at two opposing longitudinal ends of the motor carrier110. A drive shaft150is attached to the armature or first movable motor part120. A stator130comprises a coil131at which an alternating current is applied in operation so that the armature120that carries here two permanent magnets128and129is driven into a linear vibratory motion as indicated by double arrow M. The concept of a driven spring-mass type of motor that is excited at a drive frequency close to or at the resonance frequency of the spring-mass component is widely known by a person skilled in the art and is not further elaborated here. In the shown example motor100, the second movable motor part140is mounted at the motor carrier by means of the two spring elements141and142, where the spring elements141and142each have a connection extension1411and1421, respectively. The connection extension1411of spring element141extends into aligned slots1151of a folded connection area115of the sheet metal material1100of the motor carrier110. The connection extension1421of spring element142extends into aligned slots1152of the folded connection area115. In the folded connection area115, two layers of the sheet metal material1100are arranged vis-à-vis so that a strong and good coupling between spring element and motor carrier is enabled as will be explained in more detail further below. FIG.3is a depiction of an example motor carrier110A made from stamped and bent sheet metal material1100A. The motor carrier110A has two oppositely arranged connection areas111A and112A, where the sheet metal material1100A is folded so that two layers of sheet metal material are arranged vis-à-vis and in close juxtaposition to one another. The connection areas111A and112A are geometrically identical but are mirrored and a folded portion of the sheet metal material1100A is in both cases folded inwards of the motor carrier110A. Similar toFIG.2, a spring element will in an assembled state extend in between the two coupling areas111A and112A. Each of the coupling areas111A and112A has a layer of sheet metal material that faces inwards and thus will be proximate to the spring element, which are proximal layers113A and115A. Similarly, each coupling area111A and112A has also an outer layer of sheet metal material1100A, which will be distal to the spring element and are thus the distal layers114A and116A. The proximal and distal layers113A and114A are connected by folding edge1123A and the proximal and distal layers115A and116A are connected by folding edge1113A. Each of the folding edges1113A and1123A extends in a direction substantially parallel to the direction of the linear oscillatory motion “M” (FIG.2) of the movable motor part120. The proximal and distal layers of the sheet metal material extend from the corresponding folding edge and are mutually juxtaposed in close proximity to one another. The connection area111A comprises two pairs of aligned slots1111A and1112A and the connection area112A comprises two pairs of aligned slots1121A and1122A. The mutually aligned slots are aligned with one another in a direction substantially perpendicular to the direction of the linear oscillatory motion (“M”) of the movable motor part120. Each of the aligned pairs of slots1121A and1122A have a joint or common opening at the respective folding edge as is visible fromFIG.3. FIG.4Ais a front view onto a first example embodiment of a motor100B as proposed herein, the motor100B having a movable motor part140B that is mounted at a motor carrier110B by means of a spring element141B. A second spring element may be connected at the opposite end of movable motor part140B. Like what was explained for the motor carrier110A shown inFIG.3, the motor carrier110B has two connection areas111B and112B. Each connection area111B and112B comprises two layers of sheet metal material1100B. The sheet metal material1100B has here a thickness d that may lie in the previously mentioned ranges, in particular the thickness may be d=0.15 mm. The connection area111B comprises a proximal layer115B and a distal layer115B that are connected by a folding edge1113B. The two layers115B and116B are arranged at a distance that has a width g, which may be in the previously mentioned ranges, in particular the width may be g=0.5 mm. The same holds for the opposite connection area112B having two layers113B and114B that are connected by a folding edge1123B of the sheet metal material1100B. Again, the gap between the proximal layer113B and the distal layer114B may be g=0.5 mm, but this shall not exclude that the two gaps have different values. The spring element141B, which is here realized as a flat spring at rest, has two spring arms1421B and1422B that extend from a central connection portion145B at which the movable motor part140B is connected with the spring element141B. Each of the spring arms1421B and1422B turn around the center connection portion145B by an amount of about 270 degrees. Each of the spring arms1421B and1422B ends in a connection extension1411B and1412B, respectively, which are arranged in aligned slots in the connection areas111B and112B, respectively. The connection extension of the spring element extends through its respective aligned slots in the direction substantially perpendicular to the direction of the linear oscillatory motion (“M”) of the movable motor part120. The motor carrier110B may have the form and shape of the motor carrier110A as shown inFIG.3. FIG.4Bis a perspective view onto the first example motor100B. In this view another spring element142B is used to connect the moving motor part140B at the motor carrier110B. Each of the connection areas111B and112B comprises here two pairs of aligned slots of which aligned slots1112B,1121B, and1122B are visible. The aligned pair of slots1112B in connection area111B comprises slots11121B and11122B that are arranged in the distal and the proximal layer of the connection area111B, respectively. The aligned pair of slots1122B in connection area112B comprises slots11221B and11222B that are arranged in the distal and the proximal layer of the connection area112B, respectively. Connection extension1411B of the spring element141B is disposed in the aligned pair of slots1112B and connection extension1412B of the spring element141B is disposed in aligned pair of slots1122B. It can also be seen that a connection extension1422B of the other spring element142B is disposed in the aligned pair of slots1121B. FIGS.5A and5Bare a perspective of and a front view onto a second example embodiment of a motor100C in accordance with the present disclosure. A movable motor part120C is mounted at a motor carrier110C by means of spring elements121C and122C. Only spring element121C will be further discussed in detail. Spring element122C is mounted in a similar manner. In some embodiments, the first example embodiment and the second example embodiment have a joint motor carrier, i.e. the carriers110B and110C are joined to a single carrier so that a motor similar with the motor100shown inFIG.2results. Spring element121C has a single spring arm128C that has a central connection portion125C where the spring element121C is fixed at the movable motor part120C by means of splayed extensions1201C and1202C. The spring arms128C turns around the center connection portion by about 360 degrees. A first connection extension1211C connects the spring arm128C at about 270 degree at a connection area114C of the motor carrier110C. A second connection extension1212C of the spring arm is arranged at about 360 degrees and connects the spring arm121C with a bottom layer117C of the motor carrier110C. The connection extension1212C may by welded into a slot119C provided in the bottom layer117C. The connection area114C comprises two layers of sheet metal material1100C, namely a distal layer111C and a proximal layer112C, where the two layers111C and112C are arranged to abut against each other so that no gap extends between the two layers111C and112C. The two layers comprise a pair of aligned slots116C. The structure of the connection area114C is in a more general manner explained with reference toFIG.6further below and it is referred to this part of the description. One difference between the first example embodiment ofFIGS.4A and4Band the second example embodiment shown inFIGS.5A and5Bis that in the second example embodiment the two layers111C and112C of sheet metal material1100C are arranged without a gap. In such an embodiment, the fixation of the connection extension1211C at the distal layer111C by, e.g., welding may lead to a fixation depth that extends beyond the thickness of the distal layer111C. As indicated inFIG.5B, the fixation depth dfmay extend through to the proximal layer and is then thicker than the thickness d of the sheet metal material1100C (where the thickness d is defined with reference toFIG.4A). It is a common aspect of the shown embodiments and of the proposed motor in general that the fixation (e.g. welding) of the connection extension of the spring element at the motor carrier is done at the distal layer, where the width of the slot is somewhat wider than the width of the slot in the proximal layer. Independent from the precise realization, such a design tends to improve the fatigue limit of the fixation, i.e. the amplitude of cyclic stress that be applied to the connection without causing fatigue failure. The clamping at two layers leads to essentially a 2-point suspension, where the proximal clamping tends to suppress torsion stress on the welding seam at the distal layer. The folded connection area overall increases the stiffness of the motor carrier and thus tends to suppress vibrations and associated noise. Also, as becomes obvious, the number of needed components is low. No additional rivets are needed. In a motor as shown, the amplitude of movement in the longitudinal direction may be in the order of ±1.0 mm at a frequency of about 150 Hz. The chosen design also assures a relatively stiff fixation, which tends to ensure that the effective spring length (i.e. the spring constant) is relative precisely defined. As was already mentioned, the chamfered joint opening of the aligned slots facilitates the sliding of the connection extension into the aligned slots, hence it facilitates automatic assembly. FIG.6is a detail depiction of a portion of a motor carrier110D made from sheet metal material1100D that comprises an example connection area114D. The connection area114D comprises two layers111D and112D of sheet metal material1100D. For sake of continuity, the layer111D is here referred as the distal layer and the layer112D is referred to as the proximal layer. A folding edge115D of the motor carrier110D connects the distal and proximal layers111D and112D. An aligned pair of slots116D is provided in the connection area114D. The aligned pair of slots116D comprises a slot1161D in the distal layer111D and a slot1162D in the proximate layer112D. The aligned pair of slots116D has a joint opening at the folding edge115D. At the level of the folding edge115D, the joint opening1163D is larger in width than each of the slots1161D and1162D. The joint opening1163D comprises a chamfer1165D so that sliding of a connection extension of a spring element into the pair of aligned slots116D is facilitated. The slot1161D in the distal layer111D has a width w2that is larger than the width w1of the slot1162D in the proximal layer112D. The effective clamping length of the pair of aligned slots116D is s. The slot1162D in the proximal layer112D has also an opening11621D at a free edge118D of the proximate layer112D, which free layer118D lies opposite the folding edge115D. As was mentioned proximal before, the width w2of the slot1162D may be dimensioned so that a press fit with a connection extension of a spring element is established. In the shown design, the slot1162D has a somewhat larger elasticity to deform under applied forces than a shaft/bore pair for which a press fit is usually defined—this shall not limit the definition of a press fit under the given circumstances, i.e. the mentioned dimensions are treated as if they relate to a shaft and a bore that shall establish a press fit. The width w1of the slot1161D is dimensioned so that a transition fit is realized with respect to the connection extension of the spring element. By the given design the proximal layer112D separates into two wings1121D and1122D that are arranged at the sides of the slot1162D. The width of the wings1121D and1122D may be identical and may be given by b, where b may be in a range of between 1.0 mm and 50.0 mm. The height of the wings between folding edge115D and free edge118D is given by 1, where 1 may be in a range of between 1.0 mm and 30.0 mm. The given ranges shall not be understood as limiting. Other dimensions may be chosen as well in accordance with the needs of the individual case. As best shown inFIGS.2-4B, an embodiment of the motor carrier110for the linear motor100of the present disclosure comprises at least two spring elements121,122that couple the movable motor part120with the motor carrier110, each of the at least two spring elements121,122having at least two connection extensions1411B,1412B. In the embodiment illustrated, the at least two connection extensions1411B,1412B are disposed opposite one another (FIG.4A). In another embodiment, illustrated inFIGS.5A and5B, the at least two connection extensions1211C,1212C, are disposed otherwise. The sheet metal material1100B comprises at least two coupling areas111A,112A. Each of the at least two coupling areas111A,112A, which may be disposed opposite one another and at opposite sides of the movable motor part120, comprises the sheet metal material1100folded to form a folding edge1113B,1123B extending in a direction substantially parallel to a direction of the linear oscillatory motion “M” (FIG.2) of the movable motor part120and the two layers of the sheet metal material are folded to extend from the folding edge1113B,1123B to face each other in a close parallel juxtaposition with one another. The at least two layers comprise a proximal layer113B,115B that is proximate to the spring element121,122and a distal layer114B,116B that is distant to the spring element121,122(FIG.4A). The proximal layer113B,115B includes a proximal slot and the distal layer includes a distal slot, the proximal and distal slots being aligned with one another in a direction substantially perpendicular to the direction of the linear oscillatory motion “M” of the movable motor part120. Each of the connection extensions1411B,1412B of each of the at least two spring elements121,122extends through the aligned proximal and distal slots in the direction substantially perpendicular to the direction of the linear oscillatory motion “M” of the movable motor part120. As best shown inFIG.4A, the embodiment of the motor carrier110comprises a bottom portion180and two mutually opposite side walls190A,190B. Each of the side walls190A,190B extends from the bottom portion180up and terminates with the respective folding edge1113B,1123B. As is best shown inFIGS.3and4A, the proximal layers113A,115A (FIG.3) and113B,115B (FIG.4A) may extends from the respective folding edge1123A,1113A (FIG.3) and1123B,1113B (FIG.4A) towards the bottom portion180and terminate before reaching the bottom portion180. The aligned proximal and distal slots may extend from the folding edge1113A,1123A,1113B,1123B so that the aligned slots have a common opening at the respective folding edge. The dimensions and values disclosed herein are not to be understood as being strictly limited to the exact numerical values recited. Instead, unless otherwise specified, each such dimension is intended to mean both the recited value and a functionally equivalent range surrounding that value. For example, a dimension disclosed as “40 mm” is intended to mean “about 40 mm.” Every document cited herein, including any cross referenced or related patent or application and any patent application or patent to which this application claims priority or benefit thereof, is hereby incorporated herein by reference in its entirety unless expressly excluded or otherwise limited. The citation of any document is not an admission that it is prior art with respect to any invention disclosed or claimed herein or that it alone, or in any combination with any other reference or references, teaches, suggests or discloses any such invention. Further, to the extent that any meaning or definition of a term in this document conflicts with any meaning or definition of the same term in a document incorporated by reference, the meaning or definition assigned to that term in this document shall govern. While particular embodiments of the present invention have been illustrated and described, it would be obvious to those skilled in the art that various other changes and modifications can be made without departing from the spirit and scope of the invention. It is therefore intended to cover in the appended claims all such changes and modifications that are within the scope of this invention. | 26,258 |
11859688 | DETAILED DESCRIPTION Turning now to the drawings, it is to be understood that the showings are for purposes of illustrating examples of the subject matter of the present disclosure and that such examples are not intended to be limiting. Additionally, it will be appreciated that the drawings are not to scale and that portions of certain features and/or elements may be exaggerated for purposes of clarity and/or ease of understanding. FIG.1illustrates one example of a suspension system100operatively disposed between a sprung mass, such as an associated vehicle body BDY, for example, and an unsprung mass, such as an associated wheel WHL or an associated suspension component SCP, for example, of an associated vehicle VHC. It will be appreciated that any one or more of the components of the suspension system can be operatively connected between the sprung and unsprung masses of the associated vehicle in any suitable manner. For example, in the arrangement shown, suspension system100can include a plurality of gas spring and damper assemblies102that are operatively connected between the sprung and unsprung masses of the vehicle. Depending on desired performance characteristics and/or other factors, the suspension system can include any suitable number of gas spring and damper assemblies. For example, in the arrangement shown inFIG.1, suspension system100includes four gas spring and damper assemblies102, one of which is disposed toward each corner of the associated vehicle adjacent a corresponding wheel WHL. It will be appreciated, however, that any other suitable number of gas spring and damper assemblies could alternately be used in any other configuration and/or arrangement. As shown inFIG.1, gas spring and damper assemblies102are supported between suspension components SCP and body BDY of associated vehicle VHC, and include a gas spring (or gas spring assembly)104and a damper (or damper assembly)106. It will be recognized that gas springs104are shown and described herein as being of a rolling lobe-type construction. It is to be understood, however, that gas spring assemblies of other types, kinds and/or constructions could alternately be used without departing from the subject matter of the present disclosure. Suspension system100also includes a pressurized gas system108operatively associated with the gas spring and damper assemblies for selectively supplying pressurized gas (e.g., air) thereto and selectively transferring pressurized gas therefrom. In the exemplary arrangement shown inFIG.1, pressurized gas system108includes a pressurized gas source, such as a compressor110, for example, for generating pressurized air or other gases. A control device, such as a valve assembly112, for example, is shown as being in communication with compressor110and can be of any suitable configuration or arrangement. In the exemplary embodiment shown, valve assembly112includes a valve block114with a plurality of valves116supported thereon. Valve assembly112can also, optionally, include a suitable exhaust, such as a muffler118, for example, for venting pressurized gas from the system. Optionally, pressurized gas system108can also include a reservoir120in fluid communication with the compressor and/or valve assembly112and suitable for storing pressurized gas for an extended period of time (e.g., seconds, minutes, hours, weeks, days, months). Valve assembly112is in communication with gas springs104and/or dampers106of assemblies102through suitable gas transfer lines122. As such, pressurized gas can be selectively transferred into and/or out of the gas springs and/or the dampers through valve assembly112by selectively operating valves116, such as to alter or maintain vehicle height at one or more corners of the vehicle, for example. Suspension system100can also include a control system124that is capable of communication with any one or more systems and/or components of vehicle VHC and/or suspension system100, such as for selective operation and/or control thereof. Control system124can include a controller or electronic control unit (ECU)126communicatively coupled with compressor110and/or valve assembly112, such as through a conductor or lead128, for example, for selective operation and control thereof, which can include supplying and exhausting pressurized gas to and/or from gas spring and damper assemblies102. Controller126can be of any suitable type, kind and/or configuration. Control system124can also, optionally, include one or more sensing devices130, such as, for example, may be operatively associated with the gas spring and damper assemblies and capable of outputting or otherwise generating data, signals and/or other communications having a relation to one or more of: a height of the gas spring and damper assemblies; a distance between other components of the vehicle; a pressure or temperature having a relation to the gas spring and damper assembly and/or a wheel or tire or other component associated with the gas spring and damper assembly; and/or an acceleration, load or other input acting on the gas spring and damper assembly. Sensing devices130can be in communication with ECU126, which can receive the data, signals and/or other communications therefrom. The sensing devices can be in communication with ECU126in any suitable manner, such as through conductors or leads132, for example. Additionally, it will be appreciated that the sensing devices can be of any suitable type, kind and/or construction and can operate using any suitable combination of one or more operating principles and/or techniques. Having described an example of a suspension system (e.g., suspension system100) that can include gas spring and damper assemblies in accordance with the subject matter of the present disclosure, an example of such a gas spring and damper assembly will now be described in connection withFIGS.2-9. As shown therein, a gas spring and damper assembly AS1, such as may be suitable for use as one or more of gas spring and damper assemblies102inFIG.1, is shown as including a gas spring (or gas spring assembly) GS1, such as may correspond to one of gas springs104inFIG.1, for example, and a damper (or damper assembly) DP1such as may correspond to one of dampers106inFIG.1, for example. Gas spring assembly GS1and damper assembly DP1can be disposed in a coextensive arrangement with one another, and can be operatively secured to one another in any suitable manner, such as is described hereinafter, for example. A longitudinal axis AX extends lengthwise along assembly AS1, as shown inFIG.7. Damper assembly DP1can include a damper housing200and a damper rod assembly202that is at least partially received in the damper housing. Damper housing200extends axially between housing ends204and206, and includes a housing wall208that at least partially defines a damping chamber210. Damper rod assembly202extends lengthwise between opposing ends212and214and includes an elongated damper rod216and a damper piston218disposed along end214of damper rod assembly202. Damper piston218is received within damping chamber210of damper housing200for reciprocal movement along the housing wall in a conventional manner. A quantity of damping fluid220can be disposed within damping chamber210, and damper piston218can be displaced through the damping fluid to dissipate kinetic energy acting on gas spring and damper assembly AS1. Though damper assembly DP1is shown and described herein as having a conventional construction in which a hydraulic fluid is contained within at least a portion of damping chamber210, it will be recognized and appreciated that dampers of other types, kinds and/or constructions, such as pressurized gas or “air” dampers, for example, could be used without departing from the subject matter of the present disclosure. That is, it will be appreciated that a gas spring and damper assembly in accordance with the subject matter of the present disclosure can, in some cases, include a damper of an otherwise conventional construction that utilizes hydraulic oil or other liquid as a working medium of the damper. In other cases, the damper can be of a type and kind that utilizes pressurized gas as a working medium. In such cases, such a gas damper can include one or more elongated gas damping passages through which pressurized gas can flow to generate pressurized gas damping to dissipate kinetic energy acting on the gas spring and damper assembly. It will be appreciated that such one or more elongated gas damping passages can be of any suitable size, shape, configuration and/or arrangement. Additionally, it will be appreciated that any number of one or more features and/or components can be used, either alone or in combination with one another, to form or otherwise establish such one or more elongated gas damping passages. Housing wall208can form an opening (not numbered) along housing end204. A damper end wall222can extend across the opening and can be secured on or along housing wall218such that a substantially fluid-tight connection is formed therebetween. Damper end wall222can include an opening (not numbered) and elongated damper rod216can extend axially outward from damping chamber210through the opening in a direction opposite housing end206. Additionally, a damper end wall (not numbered) can be connected across end206of damper housing200such that a substantially fluid-tight connection is formed therebetween. In some cases, an end cap224(which is sometimes referred to in the art as a striker cap) that includes an outer side surface portion226can be supported on or along end204of damper housing200. In other cases, an outside surface portion228of housing wall208can be exposed on or along end204of the damper housing. Elongated damper rod216can project outwardly from damper end wall222such that end212of the damper rod assembly is outwardly exposed from the damper housing and is externally accessible with respect to the damper housing. A connection structure230, such as a plurality of threads, for example, can be provided on or along the elongated rod for use in operatively connecting gas spring and damper assembly200, either directly or indirectly, to an associated vehicle structure, a component of gas spring assembly GS1or another component of gas spring and damper assembly AS1. It will be appreciated that gas spring and damper assembly AS1can be operatively connected between associated sprung and unsprung masses of an associated vehicle (or other construction) in any suitable manner. For example, one end of the assembly can be operatively connected to an associated sprung mass with the other end of the assembly disposed toward and operatively connected to an associated unsprung mass. As shown inFIG.3, for example, end212of damper rod assembly202can be operatively engaged (either directly or indirectly) with a first or upper structural component USC, such as associated vehicle body BDY inFIG.1, for example, and can be secured thereon in any suitable manner. As one non-limiting example, gas spring and damper assembly AS1can include an end member assembly EM1that can be secured to upper structural component USC and to which one or more components of gas spring assembly GS1and/or one or more components of damper assembly DS1can be operatively connected. Additionally, or in the alternative, damper assembly DP1can include a mounting bracket232disposed along end206of damper housing200, which can be secured on or along a second or lower structural component LSC (FIG.3), such as associated suspension component SCP inFIG.1, for example, and can be secured thereon in any suitable manner. Gas spring assembly GS1can include a flexible spring member300that can extend peripherally around axis AX and can be secured between opposing end members (or end member assemblies) in a substantially fluid-tight manner such that a spring chamber302is at least partially defined therebetween. As a non-limiting example, end member assembly EM1can include an end member400to which one end of flexible spring member300can be secured and an end member500to which end212of damper rod assembly202can be operatively connected. Additionally, or in the alternative, gas spring assembly GS1can include an end member assembly600that is supported on or along damper housing200. The end of flexible spring member300that is opposite end member400can be secured on or along end member assembly600in any suitable manner. Additionally, it will be appreciated that end member600can be operatively supported on or along damper housing200in a suitable manner. As a non-limiting example, damper assembly DP1can include a support wall or support wall portion234that extends radially outward from along the damper housing toward an outer peripheral edge236. Support wall portion234can include a surface portion238facing toward end204of damper housing200and a surface portion240facing toward end206of the damper housing. Support wall portion234can be supported on or along the damper housing in any suitable manner, such as by way of one or more flowed-material joints242, for example. If included, end cap224can include a cap wall244with an end wall portion246oriented transverse to longitudinal axis AX and a side wall portion248extending axially about the longitudinal axis. Side wall portion248can include outer side surface portion226that faces radially outward and forms an outermost peripheral extent of damper assembly DP1along end204of the damper housing. It will be appreciated that flexible spring member300can be of any suitable size, shape, construction and/or configuration. Additionally, the flexible spring member can be of any type and/or kind, such as a rolling lobe-type or convoluted bellows-type construction, for example. Flexible spring member300is shown inFIGS.2-9as including a flexible wall304that can be formed in any suitable manner and from any suitable material or combination of materials. For example, the flexible wall can include one or more fabric-reinforced, elastomeric plies or layers and/or one or more un-reinforced, elastomeric plies or layers. Typically, one or more fabric-reinforced, elastomeric plies and one or more un-reinforced, elastomeric plies will be used together and formed from a common elastomeric material, such as a synthetic rubber, a natural rubber or a thermoplastic elastomer. In other cases, however, a combination of two or more different materials, two or more compounds of similar materials, or two or more grades of the same material could be used. Flexible wall304can extend in a generally longitudinal direction between opposing ends306and308. Additionally, flexible wall304can include an outer surface310and an inner surface312. The inner surface can at least partially define spring chamber302of gas spring assembly GS1. Flexible wall304can include an outer or cover ply (not identified) that at least partially forms outer surface310. Flexible wall304can also include an inner or liner ply (not identified) that at least partially forms inner surface312. In some cases, flexible wall304can further include one or more reinforcing plies (not shown) disposed between outer and inner surfaces310and312. The one or more reinforcing plies can be of any suitable construction and/or configuration. For example, the one or more reinforcing plies can include one or more lengths of filament material that are at least partially embedded therein. Additionally, it will be appreciated that the one or more lengths of filament material, if provided, can be oriented in any suitable manner. As one example, the flexible wall can include at least one layer or ply with lengths of filament material oriented at one bias angle and at least one layer or ply with lengths of filament material oriented at an equal but opposite bias angle. Flexible spring member300can include any feature or combination of features suitable for forming a substantially fluid-tight connection with end member400of end member assembly EM1and/or suitable for forming a substantially fluid-tight connection with end member assembly600. As one example, flexible spring member300can include open ends that are secured on or along the corresponding end members by way of one or more crimp rings314and316. Alternately, a mounting bead (not shown) can be disposed along either or both of the ends of the flexible wall. In some cases, the mounting bead, if provided, can, optionally, include a reinforcing element, such as an endless, annular bead wire, for example. In some cases, a restraining cylinder318and/or other components can be disposed radially outward along flexible wall304. In some cases, such components can be secured on or along the flexible wall in a suitable manner, such as by way or one or more backing rings320, for example. As mentioned above, gas spring and damper assembly AS1can be disposed between associated sprung and unsprung masses of an associated vehicle in any suitable manner. For example, one component can be operatively connected to the associated sprung mass with another component disposed toward and operatively connected to the associated unsprung mass. As shown inFIGS.2-5, for example, end member500can include one or more fasteners502operable to secure end member assembly EM1on or along upper structural component USC, such as associated vehicle body BDY inFIG.1, for example. Damper assembly DP1can be operatively connected to the upper structural component by way of end member assembly EM1, and can be operatively engaged with the end member assembly in any suitable manner. For example, damper assembly DP1can include a bushing250supported on or along end member500and to which damper rod assembly202is secured, such as by way of a connector252engaging connection structure230along end212of elongated damper rod216, for example. Bushing250can be supported on or along end member500and can be operatively secured thereto in any suitable manner. As a non-limiting example, bushing250could be captured between end member500and an end cap254that can be secured on or along the end member in a suitable manner, such as by way of a retaining ring256, for example. In some cases, a connector fitting258can extend through or otherwise be disposed on or along end cap254, such as may provide communicative coupling of electrical and/or pressurized gas systems and/or devices with gas spring and damper assembly AS1. It will be appreciated that gas spring and damper assembly AS1is displaceable, during use in normal operation, between extended and compressed conditions. In some cases, one or more jounce bumpers can be included to inhibit contact between one or more features and/or components of assembly AS1. For example, damper assembly DP1can include a jounce bumper260positioned on or along elongated damper rod216within spring chamber302. It will be appreciated that the jounce bumper, if provided, can be supported in any suitable manner. As a non-limiting example, jounce bumper260can be supported on end member assembly500to substantially inhibit contact between a component of damper assembly DP1and end member assembly500during a full jounce condition of assembly AS1. It will be appreciated, however, that other configurations and/or arrangements could alternately be used. Additionally, as discussed above, gas spring and damper assembly AS1can experience or otherwise relative rotation during displacement between extended and compressed conditions. It will be appreciated that such relative rotation can be disadvantageous to flexible spring member300, and that gas spring and damper assemblies commonly include on or more features, components and/or constructions operable to isolate such relative rotation from the flexible spring member. For example, in some cases, the operative connection to upper structural component USC can include one or more rotatable or twistable components. In such cases, end member assembly600can be directly supported in a substantially-fixed rotational position on or along the support wall of the damper assembly. In other cases, however, end member assembly EM1can be secured on or along upper structural component USC in a substantially-fixed rotational orientation. In such cases, gas spring and damper assembly AS1can include a torsional isolator700that can be supported on or along support wall portion234of damper assembly DP1. Torsional isolator700can include an elastomeric or otherwise compliant body702supported between a (comparatively) rigid body704and a (comparatively) rigid body706. It will be appreciated that compliant body702can be permanently secured (i.e., inseparable without damage, destruction or material alteration of at least one of the component parts) to and/or between rigid bodies704and706, such as by way of a cured joint (e.g., vulcanized) and/or a flowed-material joint. It will be appreciated that torsional isolator700can be supported between support wall portion234and end member assembly600in any suitable manner. As a non-limiting example, rigid body706can include a surface portion708disposed in facing relation to surface portion238of support wall portion234. Rigid body706can also include one or more mounting studs710or other securement devices that can extend through corresponding holes262in support wall portion234. In such an arrangement, rigid body706can be supported on damper assembly DP1in a substantially-fixed position in at least one axial direction and in a substantially-fixed rotational orientation. A seal712can be sealingly disposed between rigid body706and damper housing200such that a substantially fluid-tight arrangement is formed therebetween. In some cases, rigid body706can include an annular recess714extending into the rigid body from along surface portion708, and seal712can be disposed within the annular recess together with a base ring716that supports the seal in axially-spaced relation to support wall portion234. Rigid body704can include a rigid body wall718with a flange wall portion720oriented transverse to longitudinal axis AX and a pilot wall portion722that extends axially from along flange wall portion720in a direction away from rigid body706. Flange wall portion720can extend radially outward to an outer peripheral edge724, and can include a surface portion726facing opposite surface portion708. Pilot wall portion722extends axially toward a distal end surface portion728facing opposite surface portion708, and includes an outer side surface portion730facing radially outward. Rigid body704can be operatively connected with end member assembly600such that a substantially-fixed rotational position is maintained therebetween. As such, rigid body704can include one or more projections732extending outward from along surface portion726that are received within corresponding passages602in the end member assembly, such as to transmit rotational forces and/or loads to, from and/or between rigid body704and the end member assembly. In some cases, one or more projections734can extend from along rigid body704in a direction transverse to longitudinal axis AX, such as from along outer peripheral edge724, for example. A seal736can be sealingly disposed between rigid body704and end member assembly600such that a substantially fluid-tight arrangement is formed therebetween. In some cases, rigid body704can include an annular groove738extending into the rigid body, such as from along outer side surface portion730, and seal732can be at least partially received within the annular groove. It will be appreciated, however, that other configurations and/or arrangements can alternately be used. During use, rigid body706is maintained in a substantially-fixed rotational position relative to damper assembly DP1, and rigid body704is maintained in a substantially-fixed rotational position relative to end member assembly600. As such, seal712and seal734each form a substantially-static seal arrangement between the corresponding components rather than forming a dynamic seal arrangement, such as may be used in known constructions. Accordingly, rotational displacement that may occur during use between one or more components of damper assembly DP1and one or more components of gas spring assembly GS1is isolated (or at least substantially reduced) from flexible spring member300by deflection of compliant body702, which permits rigid bodies704and706to rotate relative to one another about longitudinal axis AX. End member assembly600is of a type and kind commonly referred to as a roll-off piston or piston assembly. It will be appreciated that end member assembly600can include any suitable number of one or more components and/or elements. For example, in the arrangement shown and described herein, end member assembly600includes an end member core604that is disposed along and supported on damper housing200, such as by way of torsional isolator700, as described above. An end member shell (or shell section)606is supported on the end member core and can include an outer surface608along which a rolling lobe322of flexible spring member300can be displaced as gas spring and damper assembly AS1is displaced between compressed and extended conditions. It will be appreciated that end member core604can be configured to receive and support one or more end member shells and/or shell sections, such as may have any one of a wide variety of different sizes, shapes and/or configurations (e.g., outer profiles with different combinations of contours and/or shapes). Additionally, it will be appreciated that end member assembly600and the one or more components and/or elements thereof can be formed from any suitable material or combination of materials, and can include any suitable number or combination of one or more walls and/or wall portions. For example, end member core604and/or end member shell sections606can be formed from a suitable polymeric material or combination of polymeric materials, such as a fiber-reinforced polypropylene, a fiber-reinforced polyamide, or an unreinforced (i.e., relatively high-strength) thermoplastic (e.g., polyester, polyethylene, polyamide, polyether or any combination thereof), for example. End member core604is shown as extending peripherally about axis AX and longitudinally between opposing ends610and612. End member core604can include a first or upper mounting section614toward end610and on or along which end308of flexible spring member300can be operatively connected in a suitable manner. For example, retaining ring316can be crimped radially-inward or otherwise deformed to form a substantially fluid-tight connection between end308of flexible spring member300and mounting section614of end member core604. In this manner, spring chamber302can be at least partially defined by flexible spring member300between end member400and end member assembly600, such as has been described above. End member core604can include a core wall616that extends peripherally about axis AX and longitudinally between ends610and612. Core wall616can include a first or outer wall portion618disposed along end610that terminates at a distal edge620. In some cases, outer wall portion618can at least partially define an outermost periphery along a longitudinal section of end member core616, such as along mounting section614, for example. Outer wall portion618can, optionally, include one or more engagement features disposed along an outer surface portion622thereof that may be suitable for engaging an end or other surface portion of flexible spring member300to thereby enhance retention of the flexible spring member and end member assembly in an assembled condition. As a non-limiting example, the one or more engagement features disposed on or along the outer surface of outer wall portion618can include a plurality of axially-spaced, endless, annular grooves624. It will be appreciated, however, that other configurations and/or arrangements could alternately be used. A backing ring626, such as may be formed as an endless, annular ring of metal or other rigid material, for example, can be disposed radially inward of outer wall portion618to provide increased rigidity and/or strength to the crimped connection between the flexible spring member and the end member core that is formed by retaining ring324. In some cases, outer wall portion618can take the form of an endless, annular wall that extends circumferentially about end member assembly600. Core wall616can also include a second or inner wall portion628that is spaced radially-inward from outer wall portion618such that an annular channel630is formed therebetween. Inner wall portion628can extend peripherally about axis AX, and can extend axially toward a distal edge632that can, in some cases, be disposed in approximate alignment with distal edge620of outer wall portion618. In such cases, the distal edge of inner wall portion628can, optionally, be disposed in a common plane with distal edge620of outer wall portion618. Additionally, at least a portion of inner wall portion628can be co-extensive (i.e., extending in axially-overlapping relation with one another) with outer wall portion618. Core wall616of end member core604can also include a second or intermediate section634that extends from along upper mounting section614in a direction toward end612of the end member core. Intermediate section634can include an outer surface portion636dimensioned to receivingly engage one or more of end member shells or sections, which can be secured therealong in any suitable manner. As one example, the end member shell can include a shell wall638that can be split or, alternately, formed into two or more shell wall sections606that can be assembled together around intermediate section634. It will be appreciated, however, that other configurations and/or arrangements could alternately be used. Additionally, shell wall638can include a contoured outer surface portion (not numbered) that at least partially forms outer surface608of end member assembly600along which rolling lobe322is displaced during use. Core wall616of end member core604can also include a third or lower mounting section640disposed at or along end612that can be dimensioned or otherwise configured to at least partially support end member assembly600in an axial direction on or along damper assembly DP1. Core wall616can also include an inner surface portion642that can at least partially define a passage644through end member core604. Core wall616can, optionally, include one or more elongated ribs646that can be disposed in peripherally-spaced relation to one another about axis AX and can extend longitudinally along inner surface portion642. If included, elongated ribs646can be dimensioned to form a sliding or clearance fit along outer surface228of damper housing200. Additionally, a wear-reducing and/or friction-reducing band648can be disposed along mounting section614, such as may be dimensioned for operative engagement with outer side surface portion226of end cap224and/or outside surface portion228of housing wall208. Band648can include an inner surface portion650and an outer surface portion652. Band648can extend axially between edges654and656, and can take the form of an endless annular ring or a split ring. In the latter case, band648can include ends658and660. It will be appreciated that band648can be secured on or along end member core604in any suitable manner such that band648can rotate with end member core604, as end member assembly600is rotationally displaced relative to damper assembly DP1, such as has been described above in connection with the operation of torsional isolator700. As one non-limiting example, inner wall portion628of mounting section614can include an inner surface portion662facing radially inward. Additionally, inner wall portion628can include a plurality of first projections664that are peripherally-spaced apart from one another about longitudinal axis AX. Plurality of first projections664can include a shoulder surface portion666disposed in facing relation to end612of end member core604. Shoulder surface portions666can extend radially inward from along inner surface portion662toward radially-inward edges668of the first projections. Additionally, inner wall portion628can include a plurality of second projections670disposed in peripherally-spaced relation to one another about the longitudinal axis. Plurality of second projections670can include a shoulder surface portion672facing toward end610of the end member core. Shoulder surface portions672can extend radially inward from along inner surface portion662toward radially-inward edges674. Plurality of second projections670can be disposed in axially-spaced relation to plurality of first projections664in a direction toward end612such that a groove676facing radially inward and bounded by inner surface portion662and shoulder surface portions666and672is formed along end member core604. Groove676can be dimensioned to at least partially receive band648with at least inner surface portion650projecting radially inward beyond projections664and670. Inner wall portion628can include a plurality of slots678extending axially into the inner wall portion from along distal edge632in a direction toward end612. In such case, inner surface portion662can be separated into a plurality of inner surface portions or segments. In such an arrangement, first projections664and/or the first shoulder portions thereof can extend peripherally between projection edges680and682. Additionally, or in the alternative, second projections670and/or the second shoulder portions thereof can extend peripherally between projection edges684and686. End member core604can be configured such that radially-inward edges668of first projections664form the radially innermost extents of core wall616from shoulder surface portions666to end612of the end member core. Additionally, or in the alternative, the end member core can be configured such that radially-inward edges674of second projections670form the radially innermost extends of core wall616from shoulder surface portions672to end610of the end member core. In such a configuration, first projections664and second projections670can form interleaved annular sectors extending around longitudinal axis AX, which are represented inFIGS.15and16by reference dimensions SC1and SC2. As used herein with reference to certain features, elements, components and/or structures, numerical ordinals (e.g., first, second, third, fourth, etc.) may be used to denote different singles of a plurality or otherwise identify certain features, elements, components and/or structures, and do not imply any order or sequence unless specifically defined by the claim language. Additionally, the terms “transverse,” and the like, are to be broadly interpreted. As such, the terms “transverse,” and the like, can include a wide range of relative angular orientations that include, but are not limited to, an approximately perpendicular angular orientation. Also, the terms “circumferential,” “circumferentially,” and the like, are to be broadly interpreted and can include, but are not limited to circular shapes and/or configurations. In this regard, the terms “circumferential,” “circumferentially,” and the like, can be synonymous with terms such as “peripheral,” “peripherally,” and the like. Furthermore, the phrase “flowed-material joint” and the like, if used herein, are to be interpreted to include any joint or connection in which a liquid or otherwise flowable material (e.g., a melted metal or combination of melted metals) is deposited or otherwise presented between adjacent component parts and operative to form a fixed and substantially fluid-tight connection therebetween. Examples of processes that can be used to form such a flowed-material joint include, without limitation, welding processes, brazing processes and soldering processes. In such cases, one or more metal materials and/or alloys can be used to form such a flowed-material joint, in addition to any material from the component parts themselves. Another example of a process that can be used to form a flowed-material joint includes applying, depositing or otherwise presenting an adhesive between adjacent component parts that is operative to form a fixed and substantially fluid-tight connection therebetween. In such case, it will be appreciated that any suitable adhesive material or combination of materials can be used, such as one-part and/or two-part epoxies, for example. Further still, the term “gas” is used herein to broadly refer to any gaseous or vaporous fluid. Most commonly, air is used as the working medium of gas spring devices, such as those described herein, as well as suspension systems and other components thereof. However, it will be understood that any suitable gaseous fluid could alternately be used. It will be recognized that numerous different features and/or components are presented in the embodiments shown and described herein, and that no one embodiment may be specifically shown and described as including all such features and components. As such, it is to be understood that the subject matter of the present disclosure is intended to encompass any and all combinations of the different features and components that are shown and described herein, and, without limitation, that any suitable arrangement of features and components, in any combination, can be used. Thus it is to be distinctly understood claims directed to any such combination of features and/or components, whether or not specifically embodied herein, are intended to find support in the present disclosure. To aid the Patent Office and any readers of this application and any resulting patent in interpreting the claims appended hereto, Applicant does not intend any of the appended claims or any claim elements to invoke 35 U.S.C. 112(f) unless the words “means for” or “step for” are explicitly used in the particular claim. Thus, while the subject matter of the present disclosure has been described with reference to the foregoing embodiments and considerable emphasis has been placed herein on the structures and structural interrelationships between the component parts of the embodiments disclosed, it will be appreciated that other embodiments can be made and that many changes can be made in the embodiments illustrated and described without departing from the principles hereof. Obviously, modifications and alterations will occur to others upon reading and understanding the preceding detailed description. Accordingly, it is to be distinctly understood that the foregoing descriptive matter is to be interpreted merely as illustrative of the subject matter of the present disclosure and not as a limitation. As such, it is intended that the subject matter of the present disclosure be construed as including all such modifications and alterations. | 38,870 |
11859689 | 100: active control anti-yaw damper1: hydraulic cylinder;2: piston;3: controller;4: cut-off relay;PA: first cylinder block; PB: second cylinder block;C2: first interface; C2: second interface; C3: third interface;N1: first node; N2: second node;B1: first branch; PV1: first adjustable solenoid valve; CV1: first one-way throttle valve;B2: second branch; PV2: second adjustable solenoid valve; CV2: second one-way throttle valve;B3: emergency oil line; SV: solenoid switch valve; TV1: emergency throttle valve;PA1: accumulator; PV3: reversing valve; S1: first working position; S2: second working position;CV3: third throttle valve; CV4: fourth throttle valve; CV5: fifth throttle valve;PRV1, PRV2, PRV3, PRV4: relief valve;PP1: displacement sensor; P11, P12, P13: pressure sensor;FP10: oil inlet; BP10: oil outlet; RP1: oil reservoir port. DETAILED DESCRIPTION The specific embodiments of the present application are further described in detail below in conjunction with the drawings and embodiments. The following embodiments are intended to illustrate the present application, but are not intended to limit the scope of the present application. In the following description, the orientation or positional relationships indicated by terms such as “upper”, “lower”, “left”, “right”, “inside”, “outside”, “front”, “rear”, “head”, “tail”, etc. are based on the orientation or positional relationship shown in the drawings, and are merely for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or component stated must have a particular orientation, is constructed and operated in a particular orientation, and thus is not to be construed as limiting the present application. Moreover, the terms “first”, “second”, “third”, and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. The present embodiment provides an active control anti-yaw damper100, a damping system, and a vehicle. An oil line control structure of the active control anti-yaw damper100is shown inFIGS.2to6. The damping system includes the active control anti-yaw damper100, and a control structure of the damping system is shown inFIG.1. The vehicle includes the damping system. As shown inFIG.1, the active control anti-yaw damper100according to the embodiment includes a hydraulic cylinder1and a piston2. When the piston2reciprocates in the hydraulic cylinder1, the interior of the hydraulic cylinder1is divided into two cylinder blocks. The hydraulic cylinder1shown inFIG.1is in a horizontally arranged state. As shown inFIG.1, the piston2reciprocates leftwards and rightwards inside the hydraulic cylinder1. A cylinder block on the left side of the piston2shown inFIG.1is a first cylinder block PA and the cylinder block on the right side of the piston2is a second cylinder block PB. In the present embodiment, the cylinder blocks on the left and right sides of the piston2have equal volume, and oil line through which oil in two groups of branches flows are the same when the piston2reciprocates in the hydraulic cylinder1such that the damping system is more stable when the damping force of the damper is adjusted. Preferably, the hydraulic cylinder1is respectively connected with an oil inlet FP10and an oil outlet BP10, so that the oil inlet FP10is used to deliver oil and supply oil to the inside of the damper from the outside, and the oil outlet BP10is used to guide excess oil out of the damper to ensure the balance of the oil system inside the damper. As shown inFIG.2, the active control anti-yaw damper100further includes a reversing valve and an oil reservoir. The two cylinder blocks PA and PB of the hydraulic cylinder1communicate with the oil reservoir through two main oil lines, respectively, thereby forming a primary loop between the hydraulic cylinder1and the oil reservoir. When the oil inside in the oil reservoir is pumped into the hydraulic cylinder1through any of main oil lines, the piston2may be driven to reciprocate in the hydraulic cylinder1. In the present embodiment, a reversing valve is installed between the two main oil lines and the oil reservoir and is configured to change a flow direction of the primary loop when the damper is operating normally and in an active mode and thus the piston2is driven to reciprocate based on the change in the flow direction of the primary loop. Also, the reversing valve may be configured to adjust displacement of the piston within the hydraulic cylinder in real time as needed, so as to adjust various performance parameters in real time according to the operation requirements of the vehicle, and keep a suspension system of the train to be always in the best matching status. The active control anti-yaw damper100according to the embodiment of the present embodiment has an active mode, which may be activated when the vehicle is moving in a curve. When the vehicle is running in a curve, the active control anti-yaw damper100automatically enters the active mode, so that the displacement of the piston2may be accurately adjusted by the primary loop, and thus the bogie is in a radial position relative to the vehicle body, so as to increase the curve negotiation speed of the train, reduce the wheel-rail wear, and prolong the service life of the vehicle. In the present embodiment, in order to adjust the flow direction of oil in the primary loop accurately, on one hand, the two cylinder blocks PA and PB are connected to the reversing valve PV3through two main oil lines; on the other hand, the reversing valve PV3communicates with the oil reservoir through two drive oil lines respectively. The reversing valve PV3has at least two switchable working positions S1and S2, so that synchronously reversing of the oil in each main oil line can be achieved based on the switching between respective working positions. Synchronously reversing the two main oil lines indicates that when the reversing valve PV3is in one working position, the flow direction of oil in the two main oil lines is set to be positive, then when the reversing valve PV3is switched to the next working position, the flow direction of oil in the two main oil lines instantly becomes reversed. In the present embodiment, the reversing valve PV3includes a first working position S1and a second working position S2. The first working position and the second working position are each provided with two diversion ports configured to connect the two main oil lines. The two diversion ports at the first working position S1have positions opposite to that of the two diversion ports at the second working position S2. This arrangement may enable one diversion port originally connected to one of the main oil lines to be immediately switched to connect with the other main oil line and the other diversion port to be changed in the same way when the reversing valve PV3switches the working position, so that the diversion port originally used as a liquid inlet may be immediately switched to a liquid outlet to drive the flow direction of the two main oil lines to be changed simultaneously. Preferably, the reversing valve PV3is a three-position four-way solenoid valve. In addition to two working positions, the solenoid valve further includes a closed station. When the reversing valve PV3is switched to the closed station, the reversing valve PV3enables two main oil lines and the two drive oil lines to be disconnected, and the primary loop does not work, and the active control anti-yaw damper100is automatically switched to other modes. In the present embodiment, the active control anti-yaw damper100further includes a drive mechanism connected in series with any of the drive oil lines, so as to provide driving force for flowing oil in the primary loop. The drive mechanism includes a drive motor and a drive pump, and the drive pump is connected in series with the drive oil line and connected with the drive motor. The drive motor is configured to drive the drive pump to apply a pumping force to the drive oil line, so that the drive oil line where the drive mechanism is located keep supplying oil to the reversing valve PV3, and drives the flow direction of oil in the primary loop to be changed according to the state of the reversing valve PV3, which in turn drives the piston2to reciprocate. In an alternative embodiment, as shown inFIG.3, when the reversing valve PV3is in the first working position S1, the drive pump on a drive oil line on the right side produces a driving effect to pump the oil inside the oil reservoir into the reversing valve PV3, then the oil flows into the main oil line on the right after passing through a flow path inside the first working position S1of the reversing valve PV3, and enters the second cylinder PB of the hydraulic cylinder1, and then drives the piston2to move to the left; when the piston2moves to the left, the oil inside the first cylinder PA is pumped into the main oil line on the left, and then enters the other flow path inside the first working position S1of the reversing valve PV3, and then the oil automatically flow into the drive oil line on the left from the reversing valve PV3and finally returns to the oil reservoir. The two flow paths in the first working position S1of the reversing valve PV3are arranged in parallel. As shown inFIG.4, when the reversing valve PV3is in the second working position S2, the drive pump on a drive oil line on the right produces a driving effect to pump the oil inside the oil reservoir into the reversing valve PV3, then the oil flows into the main oil line on the left after passing through a flow path inside the second working position S2of the reversing valve PV3, and enters the first cylinder PA of the hydraulic cylinder1, and then drives the piston2to move to the right; when the piston2moves to the right, the oil inside the second cylinder PB is pumped into the main oil line on the right, and then enters the other flow path inside the second working position S2of the reversing valve PV3, and then the oil automatically flow into the drive oil line on the left from the reversing valve PV3and finally returns to the oil reservoir. The two flow paths in the second working position S2of the reversing valve PV3are arranged crosswise, but these two flow paths are not communicated with each other. The above embodiment gives an internal structure arrangement and reversing mode of the reversing valve PV3. It should be understood that other structures may be used, as long as it plays a reversing role in the main oil line, so as to drive the piston2to reciprocate inside the hydraulic cylinder1. In the present embodiment, the damper further includes an accumulation branch. The accumulation branch has one end communicating with the drive oil line and located between the reversing valve PV3and the drive mechanism and other end communicating with the oil reservoir, so that the accumulation branch is connected in parallel to both ends of the drive mechanism. The accumulator PA1is connected in series on the accumulation branch, so that the accumulator PA1is connected in parallel at both ends of the drive mechanism. When the reversing valve PV3is in the closed station (that is, the reversing valve PV3does not work), oil is accumulated in advance inside the accumulator PA1based on a circuit formed between the drive mechanism and the accumulator PV1, so that the pre-accumulated oil may be input into the drive oil line as supplementary power when the power of the drive pump cannot meet the dynamic requirements of the vehicle curve operation, so as to supplement the kinetic energy to flowing of oil inside the primary loop. In the present embodiment, in order to reasonably use the accumulator PA1to supplement power in the primary loop, it is preferable to connect pressure sensors P13in series with the accumulation branch. The pressure sensors P13may perform necessary pressure monitoring on the accumulator PA1. Using the controller3, a pressure peak value F0may be preset for the accumulator PA1. When the real-time pressure value of the accumulator PA1is lower than the set pressure peak value F0, the drive mechanism starts to run and drives the oil to flow into the accumulation branch from the drive oil line, and then into the accumulator PA1until the hydraulic pressure accumulated in the accumulator PA1reaches or exceeds the peak pressure F0. In order to reasonably control the hydraulic pressure in the accumulator PA1and prevent the occurrence of danger due to too high pressure, it is preferable that a relief valve PRV4is also connected in series on the accumulation branch. The relief valve PRV4is configured to limit the maximum pressure value of the accumulator PA1and the accumulation branch. In order to meet the requirement of real-time adjustment of various performance parameters according to operating requirements when the vehicle is normally traveling in a straight line, as shown inFIG.2, the damper100in the embodiment further includes at least two parallel branches. Both ends of each branch communicate with the two main oil lines, respectively. Each branch is equipped with an adjustable solenoid valve PV configured to adjust the damping force of the oil passing through the branch when the damper100is in normal operation and in the semi-active mode, thereby adjusting the damping coefficient of the damper, and then further adjusting various performance parameters of the damper in normal operation in real time so as to semi-actively control the damper. When the active control anti-yaw damper100is in normal operation and in the semi-active mode, the piston2reciprocates inside the hydraulic cylinder1, so that an oil pressure difference is generated between the two cylinder blocks in the hydraulic cylinder1. The oil flows and switches between various branches according to the change of the oil pressure difference. The damping force of oil is adjusted using adjustable solenoid valves PV1and PV2on the corresponding branches through which oil passes and thus the damper100is ensured to have a controllable damping force and damping coefficient in the semi-active mode. In order to facilitate oil line control, two parallel branches are provided on the damper100. An inlet of one branch communicates with the first cylinder PA, and the outlet of one branch communicates with the second cylinder PB; an inlet of the other branch communicates with the second cylinder PB, and an outlet of the other branch communicates with the first cylinder PA. In other words, oil in the two parallel branches flows in opposite directions. In order to reasonably control the flow direction of each branch, each branch described in the present embodiment respectively includes one-way throttle valves CV1, CV2and adjustable solenoid valves PV1, PV2connected in series. According to the preset flow direction of each branch, the one-way throttle valves CV1, CV2and the adjustable solenoid valve PV1, PV2are connected in series on the same branch so that oil flowing in the reverse direction may be blocked in time and the flow direction of oil inside the branch is limited reasonably. Preferably, the adjustable solenoid valves PV1and PV2are solenoid proportional valves, so that the damping force of the oil flowing through the branch may be adjusted more accurately. It is understandable that three or more parallel branches may be provided in the damper, as long as all the branches are connected in parallel, all the branches are divided into two groups and oil in the two groups of branches has an opposite flow direction such that semi-actively controlling for the damper can be achieved. In the present embodiment, as shown inFIG.2, the branch includes a first branch B1and a second branch B2. One end of the first branch B1and one end of the second branch B2are connected in parallel to a first node N1and the other end of the first branch B1and the other end of the second branch B2are connected in parallel with the second node N2, and the first node N1and the second node N2are connected with the two cylinder blocks of the hydraulic cylinder1, respectively. In the present embodiment, the first branch B1has an opposite flow direction to the second branch B2. Specifically, the first branch B1includes a first one-way throttle valve CV1and a first adjustable solenoid valve PV1connected in series. Base on the controlling of the first one-way throttle valve CV1, the oil in the first branch B1can have a flow direction as follows: after flowing out of the first cylinder PA, oil flows through the first branch B1and then flows back into the second cylinder PB. The second branch B2includes a second one-way throttle valve CV2and a second adjustable solenoid valve PV2. Based on the controlling of the second one-way throttle valve CV2, the oil in the second branch B2can have a flow direction as follows: after flowing out of the second cylinder PB, oil flows through the second branch B2and then flows back into the first cylinder PA. When the damper is in the semi-active mode, as shown inFIG.5, when the oil pressure inside the first cylinder PA of the hydraulic cylinder1is greater than that inside the second cylinder PB, after flowing out of the first cylinder PA, oil flows through the first node N1via the left main oil line and then enters the first branch B1. The oil out of the first branch B1flows through the second node N2and then flows back to the right main oil line and finally flows back to the second cylinder PB, so that an oil control circuit is formed between the first branch B1and the hydraulic cylinder1. The second throttle valve in the second branch B2has the oil kept between the first node N1and the second throttle valve, so that the oil fails to flow through the second branch B2to form a control circuit. In this case, the first adjustable solenoid valve PV1may accurately adjust the damping force of the oil in the first branch B1, i.e., may adjust the system damping coefficient of the damper, so as to adjust performance parameters of the damper in real time and reliably. Similarly, as shown inFIG.6, when the damper is in the semi-active mode, as the oil pressure inside the second cylinder PB of the hydraulic cylinder1is greater than that inside the first cylinder PA, after flowing out of the second cylinder PB, oil flows through the second node N2and then enters the second branch B2, and the oil out of the second branch B2flows through the first node N1and then flows back to the first cylinder PA, so that another oil control circuit is formed between the second branch B2and the hydraulic cylinder1. The first throttle valve in the first branch B1has the oil kept between the second node N2and the first throttle valve, so that the oil fails to flow through the first branch B1to form a control circuit. In this case, the second adjustable solenoid valve PV2may accurately adjust the damping force of the oil in the second branch B2, i.e., may adjust the system damping coefficient of the damper, so as to adjust performance parameters of the damper in real time and reliably. In order to ensure that the damper can operate normally in the event of a fault or power off, the damper of the present embodiment further includes an emergency oil line B3. Both ends of the emergency oil line B3are connected to the two main oil lines, respectively. As shown inFIG.5, preferably one end of the emergency oil line B3is connected to the first node N1, and the other end of the emergency oil line B3is connected to the second node N2, so as to ensure that the emergency oil line B3is connected in parallel with all other branches. In order to ensure that the emergency oil line B3may normally provide an oil closed-loop circuit for the hydraulic cylinder1in a power off state, the emergency oil line B3is provided with a non-adjustable solenoid switch valve SV. The non-adjustable solenoid switch valve SV is configured to enable the emergency oil line B3when the damper is in a passive mode so that the damper may use the emergency oil line B3in the event of a fault or power off, thereby being switched to the passive mode. In the present embodiment, as shown inFIG.7, the emergency oil line B3includes an emergency throttle valve TV1and a solenoid switch valve SV connected in series. In the passive mode, the remaining branches except emergency oil line B3are interrupted due to power off of the one-way throttle valve and adjustable solenoid valve PV on each branch, which blocks the flowing of oil along the corresponding branch. While the solenoid switch valve SV in the emergency oil line B3may be turned on manually, or automatically turn into the turn-on state after power off, so as to ensure that the oil flowing out of the hydraulic cylinder1may flow through the emergency oil line B3and then flow back into the hydraulic cylinder1so that an oil emergency control circuit is ensured to be formed between the emergency oil line B3and the hydraulic cylinder1. In the present embodiment, the emergency throttle valve TV1of the emergency oil line B3is a non-adjustable limit orifice, and the solenoid switch valve SV fails to adjust a flow rate and a damping force of oil inside the emergency oil line B3. Therefore, when oil flows through the emergency oil line B3, all other branches are blocked and the damper is in the passive mode. It is understandable that the damper of the present embodiment also has a small damping mode in addition to the above-mentioned semi-active mode and passive mode. When the train is running in a straight line, as shown inFIGS.5and6, the damper is in the semi-active mode. In this case, the solenoid switch valve SV of the emergency oil line B3is in a charged normally closed state, and the adjustable solenoid valves PV1and PV2of each branch are in a charged state. In this case, the system damping force of the damper is generated by the hydraulic oil flowing through the adjustable solenoid valve PV, and the magnitude of the damping coefficient is determined by a control voltage of corresponding adjustable solenoid valve PV. In order to stably control the oil line, the first adjustable solenoid valve PV1in the first branch B1has equal control voltage to the second adjustable solenoid valve PV2in the second branch B2. When the train is running in a curve, as shown inFIGS.3and4, the damper is in the active mode. In this case, the solenoid switch valve SV of the emergency oil line B3and the adjustable solenoid valves PV1and PV2of all branches are in a power-off state. The drive motor and drive pump are activated to start the primary loop and act as a driving source for the reciprocating movement of the piston2. The working positions are continuously switched through the reversing valve PV3so that the oil flow direction of the primary loop is repeatedly changed at a preset frequency, thereby driving the piston2to reciprocate inside the hydraulic cylinder1. In this case, the damper is in a displacement control state, and the displacement of the piston2may be adjusted in real time through the reversing valve PV3as required. When the damper is in the passive mode, as shown inFIG.7, the damper is in a fault or power-off state, and the adjustable solenoid valve PV and one-way throttle valve of each branch stop working, so that the circulation state of each branch is completely blocked, and the oil is in a non-circulation state in the branch. In this case, the non-adjustable solenoid switch valve SV of the emergency oil line B3is activated, so that the oil flows through the emergency oil line B3to form a control circuit. The damping force of the damper is generated by the hydraulic oil flows through the non-adjustable emergency throttle valve TV1. When the damper is in the small damping mode, the solenoid switch valve SV of the emergency oil line B3is turned on, and the adjustable solenoid valves PV of all branches are turned on in charged state, then all branches are not in the blocking state. The damping coefficient of the adjustable solenoid valve PV on the corresponding branch can be adjusted to be the minimum by controlling the control voltage of the adjustable solenoid valve PV on the remaining branches. In this case, the oil may flow through all branches including the emergency oil line B3and generate a damping force. In this case, the damping force generated by the damper is very small, and the damper is regarded as being a small damping mode, which is suitable for use in small damping conditions such as entry and exit easement curves. Easement curve refers to a curve whose curvature is continuously changed between a straight line and a circular curve or between circular curves in a plane linear shape. Easement curve is one of the linear elements of the road plane and is a curve whose curvature is continuously changed and provided between a straight line and a circular curve or between two circular curves having the same turning and a large difference in radius. When the vehicle follows the easement curve, the working conditions when entering the easement curve and exiting the easement curve are small damping conditions. In the present embodiment, in order to prevent the oil pressure of the damper from being too high, and to improve the safety of the damper when adjusting parameters such as unloading force, unloading speed, and damping coefficient, it is preferable that the first node N1and the second node N2each is connected to the two cylinder blocks of the hydraulic cylinder1through a main oil line, at least one relief branch is connected between the two main oil lines, and all the relief branches are connected to each other in parallel. A relief valve is connected in series on the relief branch. In the present embodiment, two relief branches are connected in parallel between the two main oil lines, and each of the two relief branches is connected with a relief valve PRV1and a relief valve PRV2in series. The relief valve PRV1and the relief valve PRV2separately and cooperatively limit a maximum damping force of the damper, and may cooperate with the adjustable solenoid valve PV in each branch to safely and accurately adjust the unloading force, unloading speed and damping coefficient of the damper. In the damper of the present embodiment, the two main oil lines communicate with the oil reservoir through the oil reservoir lines, respectively. Specifically, the first node N1and the second node N2communicate with the oil reservoir through an oil reservoir lines, respectively. Throttle valves, namely the third throttle valve CV3and the fourth throttle valve CV4are respectively connected in series on the two oil reservoir lines. The third throttle valve CV3and the fourth throttle valve CV4are preferably spring-loaded check valves. When the pressure in any cylinder block of the hydraulic cylinder1is lower than the atmospheric pressure, oil may be directly sucked into the cylinder block from the oil reservoir through the movement of the piston2using the third throttle valve CV3and/or the fourth throttle valve CV4, which may compensate possible leakage problems and prevent cavitation in the hydraulic cylinder. In the present embodiments, a relief oil line communicates between the first node N1and the oil reservoir, the relief oil line is connected in parallel with each of the oil reservoir lines, and a relief valve PRV3is installed in series on the relief oil line. The relief valve PRV3may limit the maximum pressure inside the oil reservoir. The relief valve PRV3is preset with a maximum safety pressure value P0. Once the pressure inside the oil reservoir is greater than the safety pressure value P0, the relief valve PRV3is opened immediately, and the oil in the main oil line of the damper flows directly back into the oil reservoir. A reservoir port RP10is provided on the oil reservoir to increase or decrease the amount of oil inside the oil reservoir and control an oil level and oil pressure as required. As shown inFIG.1, a damping system according to an embodiment of the present application includes a controller3and at least one active control anti-yaw damper100as described above installed on a bogie. A signal input end and a signal output end of the controller3are connected with each of the dampers100, respectively. The controller3is configured to calculate currently required performance parameters of the damper according to the actual state of the vehicle operation. The performance parameters include but are not limited to a damping force, a damping coefficient and a piston displacement. The controller3transmits the control signal with the current performance parameters to the damper, so as to ensure that the damper may adjust various performance parameters in real time according to operation requirements of the vehicle. In order to ensure that the controller3has a reliable data source during calculation, and a good and stable signal control circuit is formed between the controller3and the damper. Preferably, the system also includes a data acquisition mechanism. The data acquisition mechanism is installed on the damper and connected to the signal input end of the controller3. The data acquisition mechanism is configured to transmit the real-time working parameters of the damper to the controller3, so that the controller3may calculate performance parameters required by the damper based on the real-time working parameters and feed control signals containing the preset performance parameter values back to the damper100. In the present embodiment, at least two data interfaces are provided on the controller3. The controller3in the present embodiment mainly includes a first interface C1, a second interface C2, and a third interface C3. Among them, the first interface C1is a signal output end, the second interface C2is a signal input end, and the third interface C3is a power supply and external device access end. The first interface C1is connected to the adjustable solenoid valves PV1, PV2of each branch on the damper, and is configured to adjust control voltages of the adjustable solenoid valves PV1, PV2and other parameters in real time according to the calculation result of the controller3so as to adjust the performance parameters of the damper100. The data acquisition mechanism of the present embodiment includes pressure sensors P11, P12, P13and displacement sensor PP1. The two cylinder blocks of the hydraulic cylinder1are respectively provided with pressure sensors PP1. The pressure sensors P11, P12, P13and the displacement sensor PP1are respectively connected to the second interface C2as a signal input end on the controller3. The pressure sensors P11and P12are installed on the first cylinder PA and the second cylinder PB, respectively to sense the oil pressure values inside the two cylinder blocks on both sides of the piston2inside the hydraulic cylinder1in real time. The pressure sensor P13is connected in series with the accumulation branch to sense the pressure value of the accumulator PA1. The displacement sensor PP1is installed on the piston2or a piston rod, so as to sense the displacement of the piston2or the piston rod inside the damper100with respect to the entire hydraulic cylinder1in real time. The data acquisition mechanism of the present embodiment also includes an acceleration sensor. The acceleration sensor is connected to the second interface C2as a signal input end on the controller3. The acceleration sensor is installed on the vehicle and is configured to provide the controller3with acceleration data during the vehicle is running, so as to be used as reference data when the controller3calculates the required parameters of the damper. The controller3of the present embodiment is also provided with an external interface, and the external interface is connected to a vehicle general control system. A cut-off relay4is installed between the controller3and the vehicle general control system. The cut-off relay4is linked with the on-board instability monitoring system. Once the bogie instability monitoring system gives an alarm, the cut-off relay4may work and cut off the power supply of the semi-active anti-yaw damper such that the whole damper system is powered off, and the damper is forcibly switched to the passive mode. In this case, the damper has the same performance as the traditional passive damper, which is sufficient to ensure that the vehicle continues to operate normally. When the piston2of the active control anti-yaw damper100according to embodiments of the present application reciprocates inside a hydraulic cylinder, an interior of the hydraulic cylinder1is divided into two cylinder blocks PA, PB which communicate with an oil reservoir through two main oil lines respectively to form a primary loop between the hydraulic cylinder1and the oil reservoir; a reversing valve PA3is installed between the two main oil lines and the oil reservoir and is configured to change the flow direction of the primary loop when the active control anti-yaw damper100is in an active mode and adjust the displacement of the piston2within the hydraulic cylinder1. When the damper100is switched to the active mode, the displacement of the piston is changed by the oil pressure difference between the two cylinder blocks PA, PB inside the hydraulic cylinder1, thereby solving various defects due to failure of adjustment for the performance parameters of the traditional anti-yaw dampers100in the prior art, especially that the bogie is in a radial position relative to the vehicle body when the vehicle runs in a curve, so as to increase the curve negotiation speed of the train, reduce the wheel-rail wear, and prolong the service life of the vehicle. The damping system according to embodiments of the present application includes a controller3and at least one above-mentioned active control anti-yaw damper100installed on the bogie, and the signal input end and the signal output end of the controller3are connected to each damper100, respectively. The required performance parameters of the damper are calculated according to the actual operation state of the vehicle using the controller3, the controller3then transmits control signals with the current performance parameters to the damper100, so as to ensure that the damper100may adjust various performance parameters in real time according to the operation requirements of the vehicle so that a suspension system of the train keeps being in the best matching state, and may be compatible with different geographic environments, operation demands of vehicles required by different lines, and the repair cycle of vehicles may be effectively extended, the service life of the vehicle is prolonged and the operating costs are decreased. The embodiments of the present disclosure have been presented for purposes of illustration and description, and are not intended to be exhaustive or to limit the application to the form disclosed. Many modifications and variations are apparent to those skilled in the art. The embodiments are selected and described in order to best explain the principles and embodiments of the present disclosure, and can be understood by those skilled in the art to design various embodiments with various modifications suitable for the particular application. | 35,408 |
11859690 | The drawings referred to in this description should not be understood as being drawn to scale unless specifically noted. DESCRIPTION OF EMBODIMENTS Reference will now be made in detail to embodiments of the present technology, examples of which are illustrated in the accompanying drawings. While the technology will be described in conjunction with various embodiment(s), it will be understood that they are not intended to limit the present technology to these embodiments. On the contrary, the present technology is intended to cover alternatives, modifications and equivalents, which may be included within the spirit and scope of the various embodiments as defined by the appended claims. Furthermore, in the following detailed description, numerous specific details are set forth in order to provide a thorough understanding of the present technology. However, the present technology may be practiced without these specific details. In other instances, well known methods, procedures, components, and circuits have not been described in detail as not to unnecessarily obscure aspects of the present embodiments. The discussion will begin with a brief overview of a vehicle wheel suspension. The discussion will then focus on embodiments of the present technology for a self-regulating suspension that provides for damping assemblies arranged in parallel within the vehicle suspension, thereby providing a greater traveling area for piston movement. In general, vehicle wheel suspensions includes a damping mechanism for dissipating energy (inertial wheel movement induced by disparities in the terrain over which the vehicle travels) and a spring mechanism for storing energy to rebound a compressed suspension to an uncompressed state and to provide additional resistance to compression. Damping assemblies convert wheel movement into heat primarily by means of fluid friction in a dashpot type device. Spring mechanisms may take many forms including, coiled springs, elastomer bumpers, compressible fluid (e.g. gas, silicone oil), suitable combinations thereof or other suitable energy storage mechanisms. Vehicles having a single front wheel, such as for example motorcycles and bicycles, often have front suspension assemblies in the form of a “fork”100as shown inFIG.1.FIG.1is a perspective view of a type of fork100. The fork100includes lower leg tubes104and118having upper leg tubes108and114telescopically engaged respectively therewith. The crown110holds the telescopic fork legs in spaced relation to the steering tube112. The drop outs102accommodate the axle of a front bicycle wheel. The fork100shown includes right leg106and left leg116, The fork100is similar to suspension disclosed in U.S. Pat. No. 7,163,222 which Patent is incorporated herein, in its entirety, by reference. FIGS.2and3show a cross-sectional view of an exemplary fork damping cartridge,200and300, respectively, that includes the internal workings of at least one leg of a bicycle fork (or motorcycle fork). Although the damping cartridge200and300may function inside a single legged fork or shock absorber, the damping cartridge200and300may also be installed inside one or more telescoping legs of the fork400ofFIG.4(a two-legged fork402). The top cap206includes male threads and an outer diameter o-ring seal. The top cap206is threaded into sealing engagement with an inner diameter of an upper leg tube (that extends through a crown, both not shown). The top cap206anchors the upper end of the cartridge axially to the upper end of the upper leg tube. The lower end of the cartridge includes a shaft310and a nut assembly312threaded onto the shaft310. The shaft310extends through a hole in the bottom of a lower leg tube that the cartridge is substantially inside a combination of the lower leg tube and an upper leg tube telescopically engaged therewith. The nut assembly312is threaded onto the shaft310from outside the lower leg tube and the cartridge is thereby anchored axially to the bottom of the lower leg tube. Referring still toFIGS.2and3, the top cap206is connected to the piston rod212, which in turn is connected to the piston assembly202. The top cap206has an adjuster knob208, which is connected to an adjuster plug210. The adjuster plug210axially abuts an adjustment shaft214which in turn axially abuts a needle body216. The needle body216includes the needle218which is disposed in variable axial relation within the orifice220of the piston assembly202. The nut assembly312is connected to the shaft310, which, through the lower damper308internal parts, is connected to the lower damper body304, which is in turn connected to the damper body306. Although the adjuster knob208, adjuster plug210, adjustment shaft214, needle body216and needle218are axially movable relative to the top cap206, the piston rod212, the piston assembly202and the orifice220, all of these move together axially in telescopic relation to the damper body306. During operation, the damper leg of the fork is subject to compression and rebound loads. The compression is induced by disparities in the terrain being traversed by a vehicle equipped with the fork. The rebound is induced by a spring (e.g., gas spring, mechanical spring, coil [not shown]), preferably located in another leg of the fork, which stores energy during compression of the fork and then releases that energy when the disparity is passed. The energy is released in urging the suspension unit to elongate axially following the axial compression during which the energy is stored. The top cap206and its connected parts (as disclosed herein) move with the upper leg tube during compression and rebound and the nut assembly312and its connected parts (as disclosed herein) move with the lower leg tube. Movement of the upper leg tube relative to the lower leg tube causes the piston assembly202to move axially within the damper body306. During a compression stroke, the piston assembly202moves downward in the damper body306and thereby reduces the volume of the compression chamber. As fluid is displaced from the compression chamber, some of it flows through passages and deflects from the one way shim stack valve to enter the rebound chamber204. Some of the displaced fluid flows through the orifice220and into the lower damper308. The resistance to movement of the fluid from the compression chamber, through the passages (and shim valve on piston) and the orifice220provide compression damping for the suspension unit in which the damper cartridge is included. Referring still toFIGS.2and3, during a rebound stroke, the piston assembly202moves upward in the damper body306and thereby increases the volume of the compression chamber. As fluid is displaced from the rebound chamber204, it flows through apertures and into an annular volume. It then flows past the needle218, through channels and the orifice220to enter the compression chamber. Also, the previously displaced fluid flows through the orifice220from the lower damper308and back into the compression chamber. The resistance to movement of the fluid from the rebound chamber204, through the channels and the orifice220provide rebound damping for the suspension unit in which the damper cartridge is included. Referring again toFIGS.2and3, an alternative to the internal floating piston is an outer flexible tubing that is located within the lower damper body304and provides a compensation chamber for the volume of the shaft310as it enters the fluid reservoir222during compression. Another term used for the fluid reservoir is a “compressible chamber”. The outer flexible tube302includes an elastic material or structure, for example an elastomeric toroid or semi-toroid or a metallic or plastic bellows or any other suitable structure or material. An interior of the outer flexible tube302is charged with a compressible fluid at an initial pressure. As the shaft310enters the compression chamber during compression, fluid flows from the compression chamber into the lower damper body304and the volume of the outer flexible tube302is reduced correspondingly as the gas within the outer flexible tube302is compressed. Such gas compression correspondingly raises the ambient pressure within the compression chamber and rebound chamber204. FIGS.5and6show embodiments of a suspension that may be adapted for use with the systems and mechanisms described herein.FIGS.5and6illustrate a coil-sprung embodiment of the two legged fork100ofFIG.1, indicated generally by reference characters500and600respectively. The forks,500and600, coil-sprung fork embodiments, utilize a pair of positive coil springs to provide an expansion force on the fork. A first spring504is located in the right fork leg, while a second spring532is located in the left leg534. An air spring arrangement may be used in lieu of or in conjunction with a coiled spring. With a coil spring, first spring504, second spring532located in each of the fork legs, right leg502, left leg534, respectively, the expansion force on the fork500,600is substantially balanced between the fork legs, right leg502, left leg534. This enhances the coaxial telescopic motion of the upper legs, upper leg tube552and upper leg tube560relative to the lower leg tubes548, lower leg tube548and562during compression and rebound for smooth motion with reduced binding. The first spring504is positioned in the right leg502between the damper cap assembly510and the cartridge tube cap546. A pair of spacers, including a first spacer508and a second spacer506, are interposed between the damper cap assembly510and the first spring504. In one embodiment the spacers, first spacer508and second spacer506are substantially C-shaped so that they may be easily removed from the damper shaft550in a radial direction. Optionally, the spacers, first spacer508and second spacer506, are configured to engage the damper shaft550in a snap fit attachment. An upper spring guide554is positioned between the first spring504and the spacer immediately adjacent the first spring504(second spacer506in the illustrated embodiment) to assist in keeping the first spring504concentric with the damper shaft550. The cartridge tube cap546functions as an upper spring guide554for the lower end of the first spring504. However, a separate spring guide554member may also be provided. A second spring532is positioned in the left leg534between the spring cap assembly522and the upper spring stop542. A first spacer508and a second spacer506are positioned between the spring cap assembly522and the second spring532. In one embodiment, the first and second spacers508and506, respectively, are substantially identical to the spacers described above in relation to the first spring504. A preload adjuster assembly516is provided to allow adjustment of the preload on the second spring532. The preload adjuster assembly516generally comprises an adjuster cap512, an adjuster shaft558, a barrel556and an adjuster knob518. The adjuster cap512is sealingly engaged with upper open end of the upper leg tube560. The adjuster cap512includes a central aperture which allows the adjuster shaft558to pass through while in a sealed arrangement. The adjuster knob518is fixed to the adjuster shaft558by a fastener526such that rotation of the adjuster knob518results in the rotation of the adjuster shaft558. A ball detent assembly514, substantially similar to those described above, may be provided between the adjuster cap512and the adjuster knob518to define a plurality of preload adjustment positions. The barrel556is threadably engaged with the adjuster shaft558and engages the second spacer. In addition, the barrel556includes a ball pocket for holding a ball bearing520, which rides within an axial groove524defined by the adjuster cap512. This arrangement prevents the barrel556from rotating relative to the adjuster cap512. Accordingly, rotation of the adjuster shaft558, via the adjuster knob518, results in translation of the barrel556relative to the adjuster cap512. A change in the axial position of the barrel556alters the preload force on the second spring532. The upper spring stop542is attached (e.g. roll-crimped) to a plunger rod544which extends upward from the closed end of the lower leg tubes548and562. The upper spring stop542includes an O-ring536which serves as an upper spring guide554for the lower end of the second spring532. The O-ring536is preferred because it's compressibility allows a single size of O-ring to accommodate a number of different spring inner diameters. The inner diameter of a spring may vary with different spring rates, therefore, the O-ring536allows a number of first and second springs504and532, respectively, having varying spring rates to be used with fork. A negative spring chamber564is defined between the upper spring stop542and the lower spring stop542. In one embodiment a single negative spring540is provided, rather than the dual negative coil spring arrangement of previous embodiments. The forks500and600ofFIGS.5and6, respectively, are capable of being adjusted for varying amounts of travel, or total distance between it's fully compressed and fully extended positions. With reference toFIG.4, the fork therein has been configured to have less travel than the fork as configured inFIG.3. To accomplish this, the first and second spacers508and506, respectively, of the left leg534were moved from their position between the upper end of the second spring532and the spring cap assembly522to a position below the plunger rod544. Specifically, the upper spring guide is slid downward on the plunger rod544and the first and second spacers508and506, respectively, are positioned between the upper spring guide and the upper spring stop542. This lowers the upper leg tubes552and560, relative to the lower leg tubes548and562, and shortens the travel of the fork by the combined length of the first and second spacers508and506, respectively. In order to accommodate the shorter travel configuration without altering the preload on the first spring504, the spacers, (FIG.5) are removed from the right leg502. In one embodiment, the first spacer508is approximately 20 mm in length and the second spacer506is approximately 25 mm in length. The travel for the fork as configured inFIG.5is approximately 125 mm. As configured inFIG.4, the travel is reduced to 80 mm. Optionally, only one of the first and second spacers508and506, respectively, may be positioned below the upper spring stop542while the other spacer remains positioned above the upper stop. With this configuration, the fork travel would be shortened by the length of the spacer positioned below the upper spring stop542, either 20 mm or 25 mm. The corresponding first and second spacers508and506, respectively, may be removed from the right leg502, to maintain the desired preload on the first spring504, as described above. Additionally, varying spacer configurations may be used. For example, the first and second spacers508and506, respectively, may be replaced by a single spacer. Also, spacers of other lengths may be used. FIGS.7and8show cross-sectional views of one leg of a fork700and a damping assembly800, respectively, in embodiments of the present technology. In relevant detail, as shown inFIG.8, are lower left and right leg tubes802and812, respectively, having upper left and right leg tubes808and810, respectively, telescopically engaged respectively therewith. In the asymmetric fork embodiment ofFIG.8, right leg806comprises a damping assembly while left leg comprises a spring assembly. Optionally, one or each (both) legs may comprise both a damping and spring assembly. FIG.8shows other components of a fork800that are not described in detail, but are depicted nonetheless for contextual purposes. These components are damper cap assembly818, and damper assembly804of right leg. Each for leg comprises a seal and wiper assembly, located at the entrance or upper opening of each lower left and right leg tube,802and812, respectively, to seal the telescopic leg and to keep debris out of the telescopic leg. The seal assembly seals against an outer surface of the upper left and right leg tubes808and810, respectively, as it moves telescopically relative to the opening. In the shown embodiment, the seal assembly comprises wiper seal816and foam ring814. FIG.7shows a damper interoperable with a piston rod702within a leg of a suspension fork, according to one embodiment of the present technology. Referring toFIGS.7and8, the upper left leg tube808telescopes in and out of the lower left leg tube802in response to bumps or depressions that are encountered by a wheel attached to the drop out (fromFIG.1) of the lower left leg tube802. Such forces are transmitted to the piston rod702and lower cartridge704since the piston rod702is fixed relative to the upper left leg tube and the lower cartridge704is fixed relative to the lower left leg tube802that results in a compression force (telescopes in) or tensile force (telescopes out) respectively between the piston rod702and the lower cartridge704. Currently, damping assemblies are arranged linearly, and therefore utilize space within a fork leg that would otherwise be used to accommodate a piston traveling within a compression chamber. Embodiments of the present technology arrange damping assemblies in parallel with each other, thereby opening up space with a fluid reservoir for receiving a piston traveling there through. In one embodiment, the isolated suspension location is positioned along the outer edge of a cylinder (comprising a compression chamber) within a fork leg, and includes an outer wall made of flexible tubing that is designed to expand outward in response to an entry of damping fluid into the isolated suspension location. Thus, for example, when a lower leg telescopically receives an upper leg during compression, the piston of the upper leg moves into a compression chamber (hereinafter, “fluid reservoir”) of the lower leg that is filled with damping fluid. The movement of this piston therein causes the damping fluid to move along a fluid flow circuit from the fluid reservoir and through an inertia valve. If the pressure on the damping fluid caused by the compression exceeds a predetermined threshold, the inertia valve is caused to open such that the damping fluid is able to travel to an isolated suspension location positioned along the outer edge of the cylinder. Once in the isolated suspension location, the damping fluid accumulates and causes the flexible tubing enclosing a portion of the isolated suspension location to expand outwards while at the same time providing resistance and thus a damping effect. A flow regulator (e.g., a one-way shim stack valve is located between the inertia valve and the fluid reservoir). This flow regulator applies another damping influence on the damping fluid flowing through the fluid flow circuit towards the isolated suspension location. Further, this flow regulator is adjustable, thereby enabling the adjustment of a damping rate applied by the flow regulator onto the damping fluid. In one embodiment, when the inertia valve is in a “lock-out” state, telescopically engaging movement between the two fork legs is inhibited. However, a blow-off valve that is positioned in series with the inertia valve and with the flow regulator operates to displace the damping fluid to the isolated suspension location when a predetermined threshold is reached or exceeded. For example, when the damping fluid pressure in the fluid reservoir is above a predetermined threshold, a piston is forced away from a piston seat and allows damping fluid to flow through an inertia valve opening and through radial ports in the inertia valve body and into the isolated suspension location, thus lowering the pressure within the compression chamber. However, when the inertia valve is in a lock-out state, the cylinder of the lower fork leg is at a closed position, and the flow of hydraulic fluid is prevented through the low, mid and high-speed compression circuits. Thus, the fork is also in a lock-out state, where substantially no relative motion is permitted between the upper leg tubes and the lower leg tubes and. This prevents rider pedal energy from being absorbed by the fork, thereby allowing such energy to instead promote forward motion of the bicycle. If a large bump is encountered, such that the pressure within the fluid reservoir rises above the threshold necessary to open the blow-off valve, the blow-off valve operates to allow fluid flow from the fluid reservoir to the isolated suspension location. This prevents damage to the various seals of the fork and prevents the entire force of the bump from being transferred to the rider. Thus, embodiments of the present technology provide a self-regulating suspension system that includes an inertia valve and blow-off valve positioned in parallel with each other and a flow regulator positioned in series with each of the inertia valve and the blow-off valve (and the fluid flow associated with the valves). This unique design enables more travel room in the compression chambers for movement of a piston, thereby providing a more consistent damping rate response to movement of an upper leg tube in relation to the lower leg tube. The following discussion will begin with a description of the structure of the components of the present technology. This discussion will then be followed by a description of the components in operation. Structure FIG.9Ashows a cross-sectional view of a fork900A, in accordance with embodiments of the present technology.FIG.9Ashows the right leg903, including the upper leg tube905telescopically engaged with the lower leg tube901. In embodiments, movable within the lower leg tube901is the damping piston assembly or “damping cartridge”917. The lower leg tube901, in embodiments, includes the cylinder915enclosing the fluid reservoir911and positioned above the damping valve assembly or “lower cartridge”913. Further, the inertia valve assembly909and the blow-off valve assembly907are positioned below the lower cartridge913. FIG.9Bis a block diagram of a self-regulating suspension900B in accordance with embodiments of the present technology. In one embodiment, a self-regulating suspension includes a first suspension member (e.g., upper leg tube905), a second suspension member (e.g., lower leg tube901), a fluid reservoir (e.g., compression chamber)911and a fluid flow circuit922. In one embodiment, the first suspension member902is axially movable relative to the second suspension member914. In another embodiment, the fluid reservoir (e.g., compression chamber)911has a volume that is variable in response to a relative movement between the first and the second suspension members. In one embodiment, the fluid flow circuit922has a first end906in fluidic communication with the fluid reservoir911and a second end916in fluidic communication with an isolated suspension location (e.g., defined by the interior of the annular elastic bladder [e.g., flexible tubing928ofFIG.9C] and the exterior of the compression chamber tube [e.g., cylinder915ofFIG.9A])918. In one embodiment, the fluid flow circuit922comprises a first valve (e.g., inertia valve)910, a second valve (e.g., damping valve [flow regulator])908and a third valve912, wherein the first valve910and third valve912are in parallel and the second valve908is in series with each of the first and third valves910and912, respectively. Of note, in one embodiment, the first valve910is part of the inertia valve assembly909, as shown inFIG.9A. In one embodiment, the second valve908is a flow regulator956(shown inFIG.9D). In one embodiment, a portion of the flow regulator956includes a one way shim stack valve. Moreover, in another embodiment, the third valve912is part of the blow off valve assembly907, as shown inFIG.9A. In one embodiment, the isolated suspension location918includes an inlet924in fluidic communication with the second end (e.g., the outlet of the second valve [damping valve])916of the fluid flow circuit922, an end barrier932and an annular enclosing wall930that defines an isolated suspension location918between the inlet924and the end barrier932. In one embodiment, the annular enclosing wall930includes an outer surface926of a cylinder915, a flexible tubing928, a first compression region934and a second compression region935, the compression regions934and935including hardware fro sealing and retaining each respective end of the flexible tubing928. In one embodiment, the first compression region934is configured for sealingly compressing a first end of the flexible tubing928against a first end of the of the cylinder915. In another embodiment, the second compression region935includes the inlet924and is configured for retainably compressing a second end of the flexible tubing928against a second end of the outer surface926of the cylinder915. FIG.9Dis a cross-sectional view of a portion of the right leg903, in accordance with embodiments of the present technology. More specifically,FIG.9Dshows embodiments of the previously schematically describedFIGS.9B and9C, including a portion of the cylinder, the lower cartridge, the inertia valve and the blow-off valve, according to embodiments. In one embodiment, the first compression region934includes a portion982of the first end of the flexible tubing928, and a first seal ring980configured for sealingly compressing the portion982of the first end of the flexible tubing928against the first end of the outer surface of the cylinder926, such that the first end of the flexible tubing928and the first end of the outer surface926of the cylinder915are sealingly squeezed shut. Further, in one embodiment, the portion982of the first end of the flexible tubing928includes an upset. In one embodiment, both ends of the flexible tubing928are constant wall with the flexible tubing928(i.e., no upsets). In one embodiment, the second compression region935includes a portion952of the second end of the flexible tubing928and a second seal ring950configured for retainably compressing the portion952of the second end of the flexible tubing928against the second end of the outer surface926of the cylinder926, such that the second end of the flexible tubing928and the second end of the outer surface of the cylinder926are squeezed partially together to retain a first915while remaining open to damping fluid flowing between the fluid flow circuit922and the isolated suspension location918. In one embodiment, the portion952of the flexible tubing928includes an upset. FIG.9Eis a cross-sectional view of a portion of the right leg903, in accordance with embodiments of the present technology.FIG.9Eshows a portion of the cylinder915and damping cartridge917. In one embodiment, the flexible tubing928is configured for creating a fluid tight seal at each end of the flexible tubing928. The outer flexible tube is upset and the upset end is captured by a seal ring (first and second seal rings980and950, respectively). During installation, the seal ring is pressed into the inner diameter at an end of the outer flexible tubing928such that it straddles the upset. The end of the outer flexible tubing928, with the seal ring installed is then slid axially into an inner diameter of a solid cylindrical housing, such as for example, the inner diameter of the annular partition1602(ofFIG.16). The annular partition1602and the seal ring are dimensioned such that the annular space formed between them is radially thinner than the thickness of the upset, thereby placing the elastic upset in a sealing squeeze (such as an o-ring mechanism would function). In one embodiment, the bladder stock may be extruded from a suitable elastic material and then cut to an appropriate length. The length may then be upset by a secondary upsetting process (e.g. using heat and pressure). Optionally, the upsetting is not necessary and the seal ring and inner diameter of the annular partition1602are designed to squeeze, in sealing engagement, the mere thickness of the bladder stock where such squeeze is also sufficient to resist axially loading and “shrinkage” forces that may occur when the bladder is internally pressurized (to expand radially). In one embodiment, the flexible tubing928includes extruded tube stock. In another embodiment, the flexible tubing928includes pulltruded tube stock. In one embodiment, the flexible tubing928may be designed, manufactured, and constructed as described herein and may include any suitable material. The outer flexible tubing928exhibits elastic characteristics. In the embodiments ofFIGS.9A-9E, the substantially tubular outer flexible tubing is sealingly captured at each end by a support structure1002and a pinch cap1004. Each mechanism is described further herein. Some embodiments may include other features for further definition as disclosed in U.S. patent application Ser. No. 12/509,258, which application is incorporated herein, in its entirety by reference. In one embodiment, the extruded or pulltruded tube stock is cut in segments to suitable length. Such manufacturing option may reduce costs per bladder and increase the bladder material and property options available. In one embodiment, one of the first and second suspension members,902and914, respectively, is an upper leg tube905, and the other of the one of the first and second suspension members,902and914, respectively, is a lower leg tube901. The lower leg tube901is configured for telescopically receiving the upper leg tube905and is axially slidable relative thereto. In one embodiment, the first valve910is an inertia valve including a movable inertia mass962and a shaft964. In one embodiment, the shaft964comprises an interior hollow portion and an outer surface. The interior hollow portion is in fluidic communication with at least one flow passage intermediate a first and second end of the shaft964. The at least one flow passage is selectively and at least partially obstructed by the movable inertia mass962to control a degree of fluid flow restriction from the fluid reservoir911to the isolated suspension location918depending on a position of the inertia mass. For example, and referring now to embodiments ofFIGS.1-9E, when a bump is encountered by a wheel carried by the suspension and damper ofFIG.7, the suspension generally is moved upwardly (as indicated inFIG.7). The inertia (i.e. tendency to remain at rest) of the inertia valve (of the inertia valve assembly909) causes that inertia valve, due to its designed mass, to remain in space while a suspension member902/914generally moves in response to the impulse caused by the wheel impacting the bump. The result is that the inertia valve “moves” down relative to the shaft964(in fact the shaft964moves up), thereby fluid communicates through fluidic ports948with the axial flow paths1202. With the inertia valve so open in response to the wheel encountering the bump therefore, fluid may flow from the fluid reservoir911and extension (hereinafter, “compression chamber966”), through the fluidic ports948, through axial flow paths1202, and may exert fluid reservoir911and compression chamber pressure on the one way shim stack valve956. FIG.10shows a cross-sectional view of the damping cartridge917, the cylinder915and the lower cartridge913, in accordance with embodiments of the present technology. Referring now toFIG.10, it is noted that the one way valve1002may include any suitable damping fluid control mechanism described herein or any suitable combination thereof. After the damping fluid has passed through the one way valve1002, it flows through the path and annulus1006and into the isolated suspension location918(which may be viewed as a sort of annulus). The isolated suspension location918is formed as a volume between flexible tubing298(or “bladder”) and an inner tube, or compression chamber wall926(or outer surface926of cylinder915). The inner tube includes the tubular wall of the fluid reservoir911. Of note, the fluid reservoir911is within a cylinder915. In one embodiment, the isolated suspension location918and the fluid reservoir911wall are substantially concentric. The isolated suspension location918acts to accumulate displaced fluid reservoir911and compression chamber966fluids during compression of the suspension, and to supply refill fluid, to the fluid reservoir911and the compression chamber966during rebound. FIG.11shows a cross-sectional view of the damping cartridge917, the cylinder915and the lower cartridge913, in accordance with embodiments of the present technology. The return or “rebound” flow sequence includes fluid flowing from the isolated suspension location918, to the path and annulus1006, where it then exerts a pressure against one way valve1002. The one way shim stack valve956is biased closed by a spring1104. When return flow pressure is sufficient, the one way valve1002is opened and the damping fluid flows through passage(s)1008and into the fluid reservoir911and the compression chamber966. In such an embodiment, the inertia valve is bypassed during rebound. Of note, in one embodiment, the one way valve1002includes any of the mechanisms described herein in references to the one way shim stack valve956or combination thereof. In one embodiment, the movable inertia mass962is configured for moving along the outer surface of the shaft964between a first position970and a second position972. The first position970includes a location along the outer surface of the shaft964that at least partially restricts fluid flow through a flow passage. In one embodiment, a portion of the fluid bypasses flowing through a flow passage to flow from the fluid reservoir911to the isolated suspension location918as a piston rod986moves further into a second suspension member914. The second position972includes a location along the outer surface of the shaft964that is providing less restriction to fluid flow through a flow passage, wherein less fluid bypasses flowing through a flow passage to flow from fluid reservoir911to the isolated suspension location918as the piston rod986moves further into a suspension member. In one embodiment, the movable inertia mass962moves from the first position970towards the second position972when an upward acceleration imparted to at least a portion of the self-regulating suspension exceeds a predetermined acceleration threshold. In one embodiment, the inertia valve includes a first plurality of protrusions958located on a first end960of the movable inertia mass962. The first plurality of protrusions958is configured for impacting a first absorber when the inertia valve is opened. In another embodiment, the inertia valve further includes a second plurality of protrusions942located on a second end944of the movable inertia mass962. The second plurality of protrusions942is configured for impacting a second absorber1204when the inertia valve is closed. FIG.12shows a cross-sectional view of portion of a lower cartridge913, an inertia valve and a portion of a blow-off valve, in accordance with embodiments of the present technology. In one embodiment, inertia valve comprises extension “feet” (that are not continuous circumferentially, thereby allowing free fluid flow there around) for impacting an elastomer or other suitably compliant absorber when the inertia valve is opened forcefully. In one embodiment, the extension feet include a first plurality of protrusions958, as is described herein. In another embodiment, the extension feet include a second plurality of protrusions942, as is described herein. In one embodiment, the self-regulating suspension includes an adjustable time delay mechanism configured for delaying the inertia valve from returning to a closed position. In one embodiment, the adjustable time delay mechanism includes a fluid recess940, a one-way delay valve washer946and an inertia valve delay neck968. In one embodiment, the fluid recess940is configured for holding damping fluid. In one embodiment, the fluid recess940is in fluidic communication with the fluid flow circuit922. For example and referring toFIG.12, the time delay functions to hold the inertia valve open against spring1220for a predetermined period of time. Various inertia valve and delay mechanisms are disclosed in U.S. Pat. Nos. 7,520,372, 7,506,884, 7,273,137, 7,128,102, 6,604,751, and 6,581,948, each of which is incorporated, in its entirety, herein by reference. Various inertia valve and delay mechanisms are disclosed in U.S. Published Patent Application No. 2008/007017 A1, 2008/0053767 A1, and 2008/0053768 A1, each of which is incorporated, in its entirety, herein by reference. Another variety of inertia valve fork is disclosed in U.S. Pat. No. 6,105,987 which is incorporated, in its entirety, herein by reference. In another embodiment, the one way delay valve washer946is configured for opening when a fluid pressure differential between the compression chamber966and the fluid recess940is below a predetermined threshold. In one embodiment, the inertia valve delay neck968is positioned at the second end944of the movable inertia mass962. The inertia valve delay neck968is configured for being biased open by a spring1220for a predetermined period of time. The period of time is that which is chosen by a user or that which is preset by someone other than the user. In one embodiment, the predetermined period of time is translated to the adjustable time delay mechanism via rotation of a delay adjustment knob. For example, a delay mechanism knob may be turned, which turn changes the time in which the spring1220is being biased open. In one embodiment, the self-regulating suspension further includes a knob assembly that is selectively rotatable. The knob assembly includes, in one embodiment, a damping valve adjustment knob936and a damping valve adjustment shaft938. The damping valve adjustment knob936is configured for being rotated. The damping valve adjustment shaft938is configured for responding to rotational movement of the damping adjustment knob. In one embodiment, the responding includes moving axially in proportion to a thread helix and pushing or pulling on an adjustment shaft that is coupled with a needle valve1304, thereby adjusting an interference of the needle valve1304within a damping orifice976that extends through a center of a damping piston974. In one embodiment, during compression or extension of the self-regulating suspension, the damping piston974controls a flow of the damping fluid. FIG.13shows a cross-sectional view of a leg of a fork1300, in accordance with embodiments of the present technology. For example, in one embodiment, as shown inFIG.13, the boost valve pair is mounted in a control assembly1302of a fork1300. The control assembly1302is shown in greater detail inFIGS.14and15. Referring toFIG.13, the fork1300includes an upper leg tube905telescopically received within a lower leg tube901and axially slidable relative thereto. The lower leg tube901includes a piston rod986having a damping valve adjustment shaft938disposed coaxially therein and axially and rotationally movable relative thereto. The damping valve adjustment shaft938moves axially in response to rotation of the blow off valve adjustment knob and thereby adjusts the interference of needle valve1304within a damping orifice976that extends through the center of the damping piston974. The damping valve adjustment knob936is accessible from an exterior of the fork and in one embodiment is suited for manipulation by hand, thereby allowing manual adjustment of the needle valve1304. The damping valve adjustment knob936is threaded through the lower end of the lower leg tube901. When the damping valve adjustment knob936is selectively rotated by a user, damping valve adjustment shaft938moves axially in proportion to the thread helix and the shaft pushes or pulls on the damping valve adjustment shaft938. The damping piston974(e.g. orifices there through) controls the flow of fluid from the compression side of the damping fluid chamber to the rebound side1310of the damping fluid chamber during a compression of the fork and vice versa during an extension of the fork, thereby providing a selectable damping resistance. Optionally, a spring (not shown) is included between the damping valve adjustment shaft938and the needle valve1304so that during compression of the fork, a threshold pressure in the compression chamber966can overcome the preset or selected spring force (based on adjustment of the damping valve adjustment knob936), thereby allowing the fork to “blow off” or allow damping fluid to flow through (rebound side1310) an otherwise substantially closed piston orifice. The damping piston974may also include a boost valve piston such as that shown and described herein, for example, inFIG.12. In one embodiment, the third valve912is a blow-off valve of the blow-off valve assembly907. The blow-off valve is configured for allowing the first and second suspension members to move closer together in response to a pressure imparted on the blow-off valve during a compression of a suspension member within the other suspension member. In one embodiment, the pressure is equal to or greater than a threshold pressure when a lock-out valve of the inertia valve is in a substantially inhibiting movement position. FIG.14is a cross-sectional view of a blow-off valve, in accordance with embodiments of the present technology. As shown inFIG.14, the blow off threshold is user adjustable by means of a damping valve adjustment knob936. The damping valve adjustment knob936is rotationally fixed to the damping valve adjustment shaft938which is held incremental rotational positions relative to the lower cartridge704(ofFIG.7) by spring loaded ball detent mechanism1402. Rotation of the damping valve adjustment shaft938causes the damping valve adjustment shaft938to translate axially relative to cartridge extension and correspondingly relative to spring1404. Rotation of the damping valve adjustment knob936therefore, decreases or increases the preload compression in spring1404and therefore the seating force of the blow-off valve. When fluid pressure in the fluid reservoir911and compression chamber966, multiplied times the effective seated area of the blow-off valve, exceeds the seating force of the blow-off valve, compression fluid will flow past the blow-off valve, through flow path1408, and into recess1410, around an exterior of the inertia valve and into the isolated suspension location918as previously described (e.g. via the one way shim stack valve956). In one embodiment, the “blow-off” valve (second valve912) of the blow-off valve assembly907is replaced with, or located in parallel with (or actually co-functional in that a bleed valve includes an overpressure pop off or blow off feature), an adjustable bleed valve or other suitable inertia valve bypass valve. It is noteworthy that, in one embodiment, all compression flow passes through the same one way shim stack valve956regardless of whether it is by normal function or blow off. If a bump is encountered and the inertia valve does not open in a timely manner, then the blow-off valve will serve to allow the suspension damper to compress by allowing compression fluid flow to bypass the inertia valve. Lock and blow-off valve features are disclosed in U.S. Pat. No. 7,163,222, which patent is incorporated, in its entirety, herein by reference. For example, and with reference toFIGS.7-9E, in one embodiment, the damper assembly700ofFIG.7is resistant to compression force (e.g. “locked out”) until a bump is encountered, by a wheel connected to the damper assembly, that is sufficient to move the inertia valve (shown inFIG.12) downward relative to the damper shaft. The inertia valve is biased closed over the fluidic ports948by the spring335. When the fluidic ports948are closed, damping fluid is “locked” within fluid reservoir911and compression chamber966and cannot evacuate, thereby preventing the piston rod986from further entering the fluid reservoir. Since damping fluid cannot evacuate from the fluid reservoir911and the compression chamber966to compensate for the incursion of the volume of rod into the fluid reservoir911, the damper (and associated suspension) is “locked out”. In one embodiment, the threshold pressure is operator-selectable. In another embodiment, the threshold pressure is adjustable from a location external to the first and second suspension members. Referring now toFIG.9D, in one embodiment, the second valve908includes a flow regulator956(such as, for example, one or more orifices optionally covered by flexible plates or “shims”). In one embodiment, the flow regulator956includes a one-way shim stack valve configured for controlling a damping rate by providing resistance to damping fluid flowing there through. In one embodiment, the resistance that is provided by the one-way shim stack valve against the damping fluid is adjustable. In one embodiment, the damping rate is controlled during a flow of the damping fluid towards the isolated suspension location918. In another embodiment, the damping rate is controlled during a rebound flow of the damping fluid away from the isolated suspension location918. In one embodiment, for example, the one way shim stack valve956may be set to a predetermined resistance to control damping rate. In one embodiment, the resistance of the one way shim stack valve956is adjustable so that compression damping may be varied. In one embodiment (not shown), the one way shim stack valve956includes a one way stack allowing flow upward toward the fluid reservoir911and a separate one way flow path stack allowing one way flow downward from the fluid reservoir911to control rebound damping. FIG.15shows an inertia valve including a boost valve pair, in accordance with embodiments of the present technology. Referring now toFIGS.9A-9E and15, in one embodiment, the one way shim stack956includes a valve inner1526and a valve outer1504. Thus, while the inertia valve is open, the damper becomes more resistant to compression as the piston rod986progresses deeper into the fluid reservoir911and the compression chamber966. In such a “boost valve” embodiment, a volume954exterior the isolated suspension location918and the outer flexible tubing928may be pressurized with gas above atmospheric pressure to enhance the function of the boost valve pair, the valve inner1526and the valve outer1504. Alternatively, a low pressure option as described herein may be used. In one embodiment, the third valve912is a boost valve configured for providing increasing resistance to compression as a piston rod986progresses deeper into the fluid reservoir911. In one embodiment, a volume954exterior to the isolated suspension location918is pressurized with gas above atmospheric pressure for increasing an ability of the boost valve to resist the compression. In one embodiment of the present technology, a damping suspension includes a first tube, a second tube telescopically receiving at least a portion of the first tube, a cylinder915, a flexible tubing928coupled with the cylinder915and an isolated suspension location918. In one embodiment, the cylinder915has an inner and outer surface926, wherein the inner surface at least partially bounds a fluid reservoir911. In another embodiment, the flexible tubing928is coupled with the first end984of the cylinder915, wherein a first end of the flexible tubing928is sealingly compressed with a first end984of the cylinder915. In one embodiment, a ring seal, as is described herein, presses the first end of the flexible tubing928against the outer surface926of the cylinder915, such that the flexible tubing928becomes immobile and a seal is formed. In one embodiment, the second end of the flexible tubing928is retainably compressed towards a second end of the outer surface926of the cylinder915. The second end of the outer surface926of the cylinder915may include the cylinder915itself, or parts extending from the cylinder915. For example, in one embodiment a ring seal presses the second end of the flexible tubing928towards the outer surface926of the cylinder926such that the second end becomes immobile, while damping fluid is able to flow between the flexible tubing928and the outer surface926of the cylinder926. In one embodiment, the isolated suspension location918includes a fluid flow circuit922, a first valve910and a second valve908. In one embodiment, the isolated suspension location918is defined by the outer surface926of the cylinder915and an inner surface of the flexible tubing928. In one embodiment, the isolated suspension location918has a fluid pressure cavity port (inlet924) that is in fluidic communication with a damping suspension valve assembly. The flexible tubing928is configured for expanding as damping fluid enters the isolated suspension location918and is configured for compressing as the damping fluid leaves the isolated suspension location918. In one embodiment, the damping suspension valve assembly includes a fluid flow circuit922comprising a first end906in fluidic communication with the fluid reservoir911and a second end916in fluidic communication with the isolated suspension location918. In one embodiment of the present technology, a damping suspension valve assembly includes a fluid flow circuit922, a first valve910, a second valve908and a third valve912. In one embodiment, the fluid flow circuit922includes a first end906in fluidic communication with the fluid reservoir911and a second end916in fluidic communication with the isolated suspension location918. The fluid reservoir911receives therein a variable volume, and the isolated suspension location918receives a damping fluid from the fluid flow circuit922in response to the variable volume. In one embodiment, the first valve910is positioned along the fluid flow circuit922. The first valve910includes a compression chamber966there within and is configured for opening and closing in response to a variable pressure imparted on the first valve910by the damping fluid. In one embodiment, the compression chamber966is in fluidic communication with both the isolated suspension location918and the fluid reservoir911when the first valve910is open, and the compression chamber966is in fluidic communication with the fluid reservoir911when the first valve910is closed. In one embodiment, the first valve910is an inertia valve. In one embodiment, of the damping suspension valve assembly, the second valve908includes an upper surface coupled with the isolated suspension location918and a lower surface coupled with the first valve910via the fluid flow circuit922. The second valve908is configured for providing resistance to the damping fluid flowing along the fluid flow circuit922. In one embodiment, the second valve908is a flow regulator956(including, in one embodiment, a one-way shim stack valve), wherein a first portion of the fluid flow circuit922moving there through is in series with a second portion of the fluid flow circuit922moving through the first valve910. In one embodiment, the third valve912is in fluidic communication with the first and second valve. The third valve912is configured for pushing the damping fluid towards the isolated suspension location918in response to a pressure imparted on the second valve908during compression of the damping suspension that is equal to or greater than an operator-selectable threshold pressure when the first valve910is in a substantially inhibiting movement position. In one embodiment, the third valve912is a blow-off valve. In one embodiment, the outer flexible tube928acts as the floating piston assembly202. In one embodiment, the outer flexible tube928may be pressurized form a source outside of the fork. Additionally, in one embodiment of the vehicle suspension damper in a leg of a fork, a variable damper is coupled with the piston assembly202. In another embodiment, the variable damper is coupled with a ported bulkhead. Referring again toFIG.4, in which a two legged fork (of a vehicle, e.g., bicycle) with a suspension damper is shown in accordance with embodiments of the present technology. As described herein, the cartridge ofFIG.3may be installed in one leg of the fork. In one embodiment and as described herein, one leg may include the vehicle suspension damper400ofFIG.4and the other leg of the fork may include a spring (e.g., gas spring, mechanical spring, coil) which stores energy during compression of the fork and then releases that energy when a disparity is passed. In one embodiment, the spring is adjustable. In one embodiment, the legs include boost valves. In another embodiment, forks include pressurized boost valves. For example, areas within the legs of the fork ofFIG.4are capable of holding matter and may be “pressurized” from an outside source with air, gas, and/or liquid. In one embodiment, the suspension damper includes a compression chamber, a first flow path and a second flow path. In one embodiment, the compression chamber includes a piston and rod movable therein. In one embodiment, the first flow path extends from a first compression chamber portion to a second compression chamber portion, wherein the first compression chamber portion and the second compression chamber portion is separated by the piston. In one embodiment, the second flow path extends from the compression chamber to an isolated suspension location. The second flow path traverses at least one of a terrain sensitive valve and a bypass valve. The second flow path further traverses a flow regulator, wherein at least one of the flow regulator and the terrain sensitive valve and the bypass valve is axially overlapping at least a portion of the isolated suspension location. Referring now toFIG.16, a cross-sectional view of a vehicle suspension damper1600and related components with a leg of a two legged fork is shown in accordance with embodiments of the present technology. The outer flexible tube928within the lower damper can be clearly seen. Operation FIG.17is a flow chart of a method for unlocking a suspension is shown, in accordance with embodiments of the present technology. Referring now toFIGS.9A-9E and17, a suspension may be described as being loaded in compression. At1704, at least one of a blow-off valve and a terrain sensitive damper valve is opened. In one embodiment, at least one of the blow-off valve and a damping valve is opened when a predetermined threshold damping fluid pressure is exceeded. In one embodiment, this predetermined threshold damping fluid pressure imparted upon the at least one of a blow-off valve and a terrain sensitive damper valve is adjusted by a pressure threshold adjustment knob. At1706, a damping fluid flows through the at least one of the blow-off valve and the terrain sensitive damping valve. At1708, the damping fluid is delivered, via the flow regulator956, to a predetermined location of the suspension, the predetermined location being fluidly isolated from gas. At1710, the terrain sensitive damping valve is delayed from returning to a closed position for a predetermined period of time. In one embodiment, this predetermined period of time is set via a delay adjustment knob. In one embodiment, during compression of the fork, the piston shaft1306progresses into the fluid reservoir911and rebound side1310. As it does so, it must, because the fluid reservoir911and rebound side1310is of fixed volume, displace a volume of fluid (typically “incompressible” damping liquid such as hydraulic oil) corresponding to the volume of the piston shaft1306as it enters the fluid reservoir911. The displacement of the damping fluid from the fluid reservoir911and rebound side1310affords an additional damping feature. Referring again toFIGS.15and16, the displaced fluid flows from the fluid reservoir911and into the compression chamber966. From there, it continues into the throat, and then to the orifice1538. When the damping fluid pressure at the orifice1538is sufficient to overcome the preload spring1516, the damping fluid flows through the orifice1538and along flow paths (through a plurality of apertures1508disposed circumferentially about the throat body1540) into a plurality of orifices1520. The plurality of orifices1520are obstructed at a lower end by a valve outer. The valve outer1504is “nested” with the valve inner1526and an annular fluid chamber1506is formed between the valve outer1504and the valve inner1526. In one embodiment, the annular fluid chamber1506is filled by gas at atmospheric pressure. When the static or “ambient” pressure of the damping fluid is greater than atmospheric, it acts to force the valve outer1504upwardly and the valve inner1526downwardly. In other words, the valve outer1504and the valve inner1526tend to become more tightly “nested”. That in turn forces the valve outer1504against the plurality of orifices1520. The greater the differential pressure between the damping fluid and the annular fluid chamber1506, the greater the force will be that is exerted by the valve outer1504against the plurality of orifices1520. That in turn will increase resistance to damping fluid flow through the plurality of orifices1520toward the flow path1534and will thereby increase the compressive damping force of the fork. Damping fluid flowing through the flow paths1534then flows into the annular fluid chamber1506where its pressure may be affected by gas pressure in chamber. Referring now toFIGS.13-16, in one embodiment, the annular fluid chamber1506is filled with substantially nothing and therefore contains a vacuum. That may be accomplished by engaging or “nesting” the parts, valve inner and valve outer, in a vacuum, or by pumping the annular fluid chamber1506down (e.g. vacuum pump) through an orifice1538(not shown) and then plugging the orifice1538. When the annular fluid chamber1506is at vacuum, mere atmospheric pressure will be higher. In one embodiment, pressurization of the shock absorber or fork leg (e.g. through gas induction valve1518to chamber) may be atmospheric or slightly above atmospheric. In one low pressure embodiment, the annular bladder or floating piston is used in order to isolate a minimized volume of gas for facilitating pressure increases during a compression stroke of the suspension. In one embodiment, the annular fluid chamber1506serves to isolate the gas compensation chamber from the damping fluid, thereby avoiding any intermingling of the gas and the fluid (e.g. liquid oil) which would result in a reduced damping performance (due to the damping fluid becoming emulsified). In one embodiment, the annular fluid chamber1506is filled with gas at above atmospheric pressure, whereby such gas pressure is specified to be greater than an initial (corresponding to an extended state of the suspension) static damping fluid pressure and corresponding gas pressure within the chamber. In such an embodiment, the gas in the annular fluid chamber1506biases the outer and inner valve portions away from one another (e.g. increasing the gap) until the suspension is stroked sufficiently in compression to revise the static damping fluid pressure to a value higher than that annular fluid chamber1506gas pressure. In one embodiment, the boost valve damping mechanism is held open until a predetermined point in the compression stroke is reached. In such an embodiment, the suspension exhibits very compliant damping characteristics until later in the compression stroke, at which point the suspension becomes more rigid (and in that way suspension “bottom out” may be mitigated). In one embodiment, a mechanical spring is placed within the annular fluid chamber1506such that it is in compression between the outer and inner valve halves and biases them to move apart in a manner, and with a result, similar to the foregoing description except that the spring rate may be more linear than an initial gas pressure charge “spring”). In one embodiment, the volume of the annular fluid chamber1506is configured in proportion to the diameter of the piston shaft1306and the length of the suspension stroke or the length of the piston shaft1306that will, at most, enter into the fluid reservoir911and the rebound side1310. Such a consideration may be referred to as the “damper compression ratio”. In one embodiment, the volume of the annular fluid chamber1506is twice the volume of the piston shaft1306that may enter the fluid reservoir911and rebound side1310at maximum compression stroke of the suspension or in other words the damper compression ratio is two (volume of the compensating chamber divided by the shaft volume maximum minus shaft volume [in the damping chamber] initial). In some boost valve suspension embodiments, useful compression ratios range from 1.5 to 4. In some embodiment, more particular useful compression ratios range from 2 to 3. In some fork embodiments, compression ratios may be relatively lower in a range because a fork typically operates within a vehicle system on a one to one basis (i.e. the wheel moves an inch and the fork moves an inch, whereas a shock may move ½ inch per 2 inches of wheel travel, thereby increasing the inch per inch resistance required of an effective shock. There is no levering linkage usually associated with a fork. There is often linkage associated with a rear shock.) The ambient pressure of the damping fluid may be altered by pressurizing (in one embodiment with a compressible fluid such as a gas) the compensation chamber. In one embodiment, the isolated suspension location918is pressurized by adding gas, at a desired damping fluid ambient pressure, through gas induction valve1518. The gas induction valve1518may be a rubber plug under a set screw, a Schrader type gas valve, a Presta type gas valve or any valve suitable for gas introduction and sealing at pressure. When the gas is introduced into the gas induction valve1518, it flows through the plurality of orifices1520and into the isolated suspension location918. In one embodiment, the isolated suspension location918is sealed at a lower end by an annular partition1602and seal in order to limit the volume of pressurized gas, consistent with a desired damping compression ratio, influencing the dimension of the upper tube (and if the upper tube is completely pressurized dimensional changes and possible binding between fork legs may occur). In one embodiment, the isolated suspension location918may be pressurized to 100 or 200 psi and may function at pressures from 200 to 600 psi. Referring now toFIGS.10and15, the ambient pressure of the damping fluid may be altered by pressurizing (in one embodiment with a compressible fluid such as a gas) the fluid reservoir. In one embodiment, the fluid reservoir911is pressurized by adding gas, at a desired damping fluid ambient pressure, through the gas induction valve1518. The gas induction valve1518may be a rubber plug under a set screw, a Schrader type gas valve, a Presta type gas valve or any valve suitable for gas induction and sealing at pressure. When the gas is introduced into the gas induction valve1518, it flows through the orifices1520and into the isolated suspension location918. In one embodiment, the fluid reservoir911is sealed at a lower end by an annular partition1602and is sealed in order to limit the volume of pressurized gas influencing the dimension of the upper tube (seeFIG.13) (if the upper tube is completely pressurized dimensional changes and possible binding between fork legs may occur). Referring now toFIG.18, a cross sectional view of a vehicle suspension damper and related components within a fork1800that is configured for a motorcycle is shown in accordance with embodiments of the present technology. Shown in the fork1800are the following components: piston assembly1802, variable damper1818, movable outer valve1808, reverse bend shim1806, main stack of shims1804, the first big diameter shim1820furthest from the piston assembly1802, IFP chamber1810(similar in function to the damping fluid chamber of previous figures), compression bleed adjuster (not labeled), spring pre-load adjuster (not labeled) and IFP spring1812. In operation, the variable damper1818acts against a reverse bend shim1806arrangement. As the pressure in the IFP chamber1812increases due to compression of the fork1800, the movable outer valve1808pushes against the first big diameter shim1820furthest from the piston assembly1802. The first big diameter shim1820bends against the main stack of shims1804, effectively increasing the stiffness of the main stack of shims1804as the fork1800is compressed. At the beginning of travel, when the pressure of the IFP chamber1812is at a minimum, the variable damper1818is not influencing the damping force. At some point into the travel, when the reverse bend shim1806assembly starts to engage the main stack of shims1804, is when the variable damper1818starts acting. This gives initial free movement of the fork1800and then produces the position-sensitive effect to the compression damping deeper in travel. Of note, external adjustments may be made to the components of the fork1800. For example, a compression bleed adjuster is coupled in parallel with the variable damper1818. The compression bleed adjuster is configurable to be adjusted externally. In addition, in one embodiment, there is a spring pre-load adjuster which acts to change the pre-load on the IFP spring1812. In one embodiment, turning the spring pre-load adjuster clockwise will increase the pre-load on the IFP spring1812and make the variable damper1818react closer to the initial part of its travel. Turning the spring pre-load adjuster will control the dive or pitch of the fork1800(most notable in the corners). Another external adjustment that may be made in accordance with embodiments of the present technology is to alter the height of the external oil bath. Raising the oil height will increase the damping of the air volume in the fork1800, thus increasing the apparent pressure of the IFP chamber1810. Most likely, this adjustment will affect the last few inches of travel. Referring now toFIG.15, in one embodiment, the fork includes an adjustable damping mechanism including a metering valve1536. The metering valve1536can be adjusted by rotation of the top cap1510, which correspondingly rotates the adjuster1512. The adjuster1512is non round and engages a similarly non round hole through a nut1514. When the adjuster1512is rotated, the nut1514is rotated and also traverses its threaded housing axially. As the nut1514moves axially, the preload on the preload spring1516is correspondingly altered. Because the preloaded spring exerts an axial load on the metering valve1536body, the damping characteristic, or resistance to flow through the orifice is selectively and manually adjusted by turning the top cap1510. The pressurized gas acts almost without resistance on the damping fluid through the outer flexible tube928. In one embodiment, the outer flexible tube928is made from an elastomer (or other suitable flexible material) and acts as a pressure transmitting diaphragm (annular) between the gas in the isolated suspension location918and the damping fluid in the isolated suspension location918. Because the damping fluid in the annulus is in pressure communication with the entire damping fluid system including the fluid reservoir911and rebound side1310, the communication of gas pressure in the fluid reservoir911to the fluid pressure in the isolated suspension location918(through the outer flexible tube928) increases the ambient damping fluid pressure tot hat of the gas pressure of the isolated suspension location918. As described herein, the ambient pressure influences the damping force exerted by the boost valve or valves included within the fork (valve outer and valve inner). As the fork compresses during a compression stroke, the volume of damping fluid displaced by the piston rod (ofFIG.7) acts to further increase the ambient damping fluid pressure in the system by compressing the gas in the isolated suspension location918by an amount corresponding to the piston rod986introduced into the compression chamber966and rebound side1310. Referring now toFIGS.10and15, during compression of the fork, the piston shaft1306progresses into the fluid reservoir911and the compression chamber966. As it does so, it must, because the fluid reservoir911and the compression chamber966is of a fixed volume, displace a volume of fluid (typically “incompressible” damping liquid such as hydraulic oil corresponding to the volume of the shaft as it enters the chamber). The displacement of damping fluid from the fluid reservoir911and rebound side1310affords an additional damping feature. The displaced fluid flows from the fluid reservoir911into compression chamber966. From there, it continues into the throat body1540to the orifice. When the damping fluid pressure at the orifice1538is sufficient to overcome the meter valve preload spring1516, the damping fluid flows through the orifice1538and along the flow paths1528(through a plurality of apertures1508disposed circumferentially about the throat body1540) into a plurality of orifices1520. The plurality of orifices1520are obstructed by the valve outer. The valve outer is nested with the valve inner and an annular fluid chamber1506is formed between the valve outer and the valve inner. In one embodiment, the annular fluid chamber1506is filled by gas at atmospheric pressure. When the “ambient” pressure of the damping fluid is greater than atmospheric, it acts to force the outer valve upwardly and the inner valve downwardly. In other words, the outer valve and the inner valve tend to become more tightly “nested”. That in turn forces the outer valve against the plurality of orifices1520. The greater the differential pressure between the damping fluid and the annular fluid chamber1506, the greater the force will be that is exerted by the valve outer against the plurality of orifices1520. That in turn will increase resistance to the damping fluid flow through the plurality of orifices1520toward the flow path1534and will thereby increase the compressive damping force of the fork. Damping fluid flowing through the flow paths1534then flows into the annular bladder interior1532where its pressure may be affect by gas pressure in the chamber. While the foregoing is directed to embodiments of the present technology, other and further embodiments of the present technology may be implemented without departing from the scope of the invention, and the scope thereof is determined by the claims that follow. | 70,678 |
11859691 | DESCRIPTION OF THE PART REFERENCES 100. Upper part110. Upper section111. Clip retainer112. Nail120. Middle section121. Hole130. Lower section131. Clip slot132. Nail space200. Lower part201. Hole210. Slide211. Slide roof220. Inlet slot opening230. Inlet slot end240. Mounting hole10. Pleated or honeycomb curtain system11. Upper profile12. Curtain13. Lower profile14. Rope15. Rope fixing apparatus DETAILED DESCRIPTION OF THE INVENTION In this detailed description, the preferred alternatives of the rope fixing apparatus (A5) of the invention is described only for a better understanding of the subject without any limiting effects. InFIG.1, the pleated or honeycomb curtain system (10) is seen. Said pleated or honeycomb curtain system (10) basically comprises the upper profile (11) forming the upper edge of the pleated or honeycomb curtain system (10) and enabling the pleated or honeycomb curtain system (10) to open and close up and down, the curtain (12) connected under the upper profile (11), the lower profile (13) forming the lower edge of the pleated or honeycomb curtain system (10) by being connected under the curtain (12) and enabling the pleated or honeycomb curtain system (10) to open and close up and down, the rope (14) attaching the upper profile (11) and lower profile (13) each other by passing through the curtain (12), the rope fixing apparatus (15) enabling the rope (14) to be fixed to the upper profile (11) and lower profile (13) and also the application area of the pleated or honeycomb curtain system (10) in the required tension adjustment. InFIG.2, a demounted view of the rope fixing apparatus (15) of the invention is given. Accordingly, the rope fixing apparatus (15) basically comprises an upper part (100) that can open and close as a clip enabling the rope (14) to be fixed in the required tension adjustment, the lower part (200) locking the upper part (100) by passing it through and connecting the upper part (100) to the area where the pleated or honeycomb curtain system (10) will be used and also enabling the rope (14) to be fixed in a way that it does not come out of the upper part (100). The upper part (100) that can open and close as a clip inFIG.3basically consists of an upper section (110) with V-shaped protruding nails (112) on its inner surface, a lower section (130) with V-shaped recessed nail space (132) in accordance with the form of said nails (112) on its inner surface and a middle section (120) in the perforated (121) structure between said upper section (110) and lower section (130). The middle section (120) is made of a material that is less rigid than the upper section (110) and the lower section (130). Therefore, the upper part (110) and the lower part (130) can be folded two from the middle section (120) and closed on each other to make the rope (14) to be fixed in the required tension adjustment. The upper section (110) has the ability of moving back and forth on the lower section (130). When the upper part (110) and the lower part (130) can be folded two from the middle section (120) and closed on each other, the V-shaped protruding nails (112) are closed on the V-shaped recessed nail spaces (132). Said nails (112) and nail spaces (132) closed on the nails (112) enable the rope (14) passed through the hole (121) in the middle section (120) to be fixed by tightening and enable the rope to be brought to the desired tension adjustment by means of moving the upper section (110) back and front on the lower section (130). The hole (121) located on the middle section (120) and enabling the rope (14) to enter into the upper part (100) may be in a circle, triangle or different geometric shape. When the upper part (110) and the lower part (130) can be folded two from the middle section (120) and closed on each other, there is a clip slot (131) in the form of recess mutually on both sides on the lower section (130) to fix the upper section (110) and lower section (130) and a clip retainer (111) in the form of protrusion fixed by passing to said clip slot (131) mutually on both sides on the upper section (110). When the upper part (110) and the lower part (130) can be folded two from the middle section (120) and closed on each other, the clip retainers (111) on the upper section (110) as seen inFIG.4are fixed by passing to the clip slots (131) on the lower section (130). The lower part (200) enabling the upper part (100) to be connected to the area where the pleated or honeycomb curtain system (10) will be used and enabling the rope (14) to be fixed in a way that it does not come out of the upper part (100) has a slide (210) in height of the upper part (100) mutually on both sides as seen inFIG.5. The inlet slot opening (220) forming one end of said slide (210) is open in order to make the upper part (100) enter the lower part (200). The inlet slot end (230) forming the other end of said slide (210) is close in order to make the upper part (100) to be fixed to the lower part (200). The slide roof (211) on the slide (210) is in an inward curved structure as seen inFIG.5bin order to lock the upper part (100) into the lower part (200) and to fix the rope (14) into the upper part (100) with said locking. Therefore, it is provided that the upper part (100) passed into the slide (210) is locked by tightening into the slide (210) by means of the inward curved slide roof (211) and the rope (14) is fixed in a way that it does not come out of the upper part (100). There is at least one mounting hole (240) on the lower part (200) to provide that the pleated or honeycomb curtain system (10) is fixed to the application area. The working principle of the rope fixing apparatus (15) of the invention is as follows. The rope (14) of the pleated or honeycomb curtain system (10) is passed through the hole (121) in the middle section (120) when the upper part (100) is open and the upper section (110) and the lower section (130) is folded two from the middle section (120) and closed on each other. In the meantime, the clip retainers (111) on the upper section (110) pass to the clip slots (131) on the lower section (130). When the upper part (110) and the lower part (130) are folded two from the middle section (120) and closed on each other, the rope (14) passed through the hole (121) stands stable by tightening between the nails (112) and the nail spaces (132) closed on the nails (112). The upper section (110) is moved back and front on the lower section (130) in order to adjust the tension of the rope (14) when necessary and it is provided that the rope is brought to the desired tension adjustment. After the adjustment, the upper part (100) is passed to the slide (210) on the lower part (200) connected to the sills by means of the mounting holes (240) in the application area of the pleated or honeycomb curtain system (100) by means of the inlet slot opening (220). The upper part (100) is moved by being pushed along the slide (210) and the upper part (100) bears to the inlet slot end (230). In the meantime, it is provided that the upper part (100) is locked by tightening into the slide (210) by means of the inward curved slide roof (211) and is fixed in a way that it does not come out of the upper part (100). In the pleated or honeycomb curtain system (10), it is provided that the curtain (12) opens and closes on the ropes (14) by moving the upper profile (11) and/or the lower profile (13) up and down. | 7,457 |
11859692 | DETAILED DESCRIPTION OF THE INVENTION A hook assembly according to the present invention will now be described in detail with reference toFIGS.1to7of the accompanying drawings. The hook assembly10includes a hook body11with a shank portion12and a free end portion13disposed in a common plane and defining a hook opening14. The hook opening14can be used for receiving an item to be engaged by the hook assembly10, such as a chain link, cable, or other similar item. The shank portion12has a base15configured to be weldable to allow the hook assembly10to be used as a weld-on attachment point. The base15has at least one weldable chamfer edge16on a side opposite from the hook opening14to facilitate welding the hook body11to another structure S, such as a trailer frame, loader bucket or other piece of equipment. The free end portion13of the hook body11has a tip end portion17that extends further from the hook opening14than the shank portion12. The tip end portion17has a through passage18that extends generally perpendicular to the free end portion13of the hook body11. The through passage18includes a key slot19along one side thereof. In the illustrated embodiment, the key slot19is formed on a side of the through passage18nearest to a closed end20of the hook body11. This allows the key slot19to be formed without creating a weak spot in the structure of the tip end portion17surrounding the through passage18. A removable pin assembly21has a pin member22and a spring retainer23. The pin member22in the illustrated embodiment is a lynch pin. The lynch pin22has a head24, and the spring retainer23is a generally circular spring with offset ends25,26received in respective openings27,28in opposite sides of the head24. The lynch pin22has an elongate shaft29with a protrusion30on one side thereof. The elongate shaft29can be a cylindrical shaft, or a substantially cylindrical shaft with a flat side31, as illustrated. The protrusion30protrudes generally perpendicular to a longitudinal axis of the lynch pin22. The diameter of the shaft29of the pin member22and the size of the protrusion30are such that the lynch pin22can be inserted into the through passage18with the protrusion30mated with the key slot19. The lynch pin22must be rotated to a first position of rotation with the protrusion30aligned with the key slot19(as depicted inFIGS.3to6) to allow the lynch pin22to be received in and removed from the through passage18. The lynch pin22is received in the through passage18and extends through the passage18generally perpendicular to the shank portion12with an end portion32of the pin member22adjacent to an end face33of the shank portion12. The lynch pin22substantially closes or blocks an open side34of the hook opening14when fully inserted into the through passage18to retain items within the hook opening14. The protrusion30is arranged to abut a periphery35of the through passage18and serve as a locking structure that prevents the lynch pin22from being removed from the through passage18when the lynch pin22is rotated away from the first position. The spring retainer23of the pin assembly21has a first released position (i.e., spring retainer23extending away from the shaft29of the lynch pin22, as depicted inFIGS.3to6) in which the lynch pin22can be rotated freely within the through passage18when the lynch pin22is fully inserted (i.e., with the protrusion30past the key slot19). The spring retainer23has a second closed position, as depicted inFIGS.1and2, in which the spring retainer23is held by spring force against an outer surface of the shaft29of the lynch pin22. In the second closed position, the spring retainer23has abutting portions36,37arranged to abut respective sides38,39of the free end portion13of the hook body11to prevent rotational movement of the lynch pin22to its first position with the protrusion30aligned with the key slot19. The spring retainer23in its second closed position is arranged to bias the lynch pin22to a rotational position away from the first position to prevent the lynch pin22from being removed from the through passage18. The spring retainer23prevents the lynch pin22from being rotated to the first position, and thereby prevents the protrusion30on the lynch pin22from being aligned with the key slot19in the through passage18. The protrusion30extends generally perpendicular to a plane containing the spring retainer23when the spring retainer23is in its second closed position. The protrusion30on the lynch pin22and the key slot19in the through passage18provide a means for locking the pin assembly21in a position with the lynch pin22received in the through passage18substantially closes the open side34of the hook opening14. Other means for locking the pin assembly21in such a position could also be used, including the use of a spring retainer without a separate mating locking structure, or the use of a spring biased detent protruding from the shaft of the lynch pin. In each case, the pin assembly21extends through the passage18to close the open side34of the hook assembly10and is reliably held in the closed position by a locking structure, a spring retainer, and/or a spring biased detent. The hook assembly10of the present invention is illustrated inFIGS.1to7as a grab hook. The shank portion12and free end portion13of the hook body11in this embodiment define a hook opening14in the form of an elongate receiving slot having a narrow, straight-sided throat. Grab hooks are typically used to receive a single chain link in the hook opening14, and the hook opening14is sufficiently narrow to prevent additional chain links from sliding through the opening14. The chain links on either side of the engaged link of chain in the hook opening14prevent the chain from moving freely in the throat of the grab hook. The hook assembly10of the present invention can also be used with various other types of hooks, such as slip hooks. In a slip hook, the shank portion and free end portion of the hook body define a hook opening with a wide throat that allows items retained in the hook opening to slide freely through the hook. A slip hook assembly having a tip end structure with a through passage and a removable pin assembly according to the present invention can be used to retain items within the hook opening of the slip hook assembly. While the hook body11shown inFIGS.1to7is a weld-on type hook, it will be appreciated that features of the present invention can also be used with other types of hooks, such as clevis type hooks and eye type hooks. The structure of the hook assembly10according to the present invention has been described above. A method of using the hook assembly10will now be described. With the lynch pin22completely removed from the through passage18of the hook body11, or partially withdrawn so that the end portion32of the lynch pin22does not extend into the hook opening14, a chain, cable or other item to be retained can be inserted into the hook opening14. Variations of this starting position can be used, including a position in which only the end portion32of the lynch pin is inserted into the through passage18, and the spring retainer23is in its first closed position to hold the lynch pin22in place, as depicted inFIG.2. Once the item to be retained is inserted into the hook opening14, the spring retainer23is moved into its first released position so that the lynch pin22can be rotated freely relative to the through passage18. The lynch pin22is then rotated to its first position to align the protrusion30on the pin22with the key slot19in the through passage18. The lynch pin22is then inserted into the through passage18until the end portion32of the lynch pin22is adjacent to the end face33of the shank portion12to substantially close the hook opening14. Once the lynch pin22is inserted far enough so that the protrusion30on the pin22is all the way through the key slot19in the through passage18, the lynch pin22can then be rotated (e.g., approximately ¼ to ½ turn) in either direction, and then the spring retainer23moved to its second closed position (FIG.1). In the second closed position, the spring retainer23allows only limited rotational movement of the lynch pin22(e.g., approximately 150 to 170 degrees) and prevents rotational movement of the lynch pin22back to its first position in which the protrusion30and key slot19would be aligned. The lynch pin22is thus held within the through passage18by a combination of the spring retainer23being spring tensioned into its second closed position, and the locking structure of the protrusion30and key slot19not being aligned. The hook assembly10of the present invention allows a weld-on grab hook to be positioned with its hook opening14facing downwardly, and a chain link, cable or other item held within the hook opening14by the lynch pin22until the load above the grab hook is tied down. The lynch pin22in its fully inserted position (FIG.1) prevents accidental dislodging of the chain from the hook opening14of the grab hook body11before the load is secured by chain binders or the like. The lynch pin can22be removed easily from the hook body11by moving the spring retainer23to its first released position, rotating the lynch pin22until the protrusion30and key slot19are aligned, and sliding the lynch pin22out of the through passage18. The present invention can also be used with things other than hook assemblies. For example, elements of the present invention can be used to provide a closure system for door latches, tool boxes, and a variety of other items that use pin members to close, secure or retain the item. In this case, the closure system includes a first element having a through passage with a key slot, and a removable lynch pin received in the through passage. The lynch pin has a protrusion that mates with the key slot when the lynch pin is rotated to a first position to allow the lynch pin to be received in and removed from the through passage. The protrusion serves as a locking structure to prevent the lynch pin from being removed from the through passage when the lynch pin is rotated away from the first position. A spring retainer is connected to the lynch pin and arranged to bias the lynch pin to a rotational position away from the first position to prevent the lynch pin from being removed from the through passage. As in the other embodiments described above, the lynch pin has a head, and the spring retainer is a generally circular spring having offset ends received in respective openings in the head. The spring retainer has a first released position in which the lynch pin can be rotated freely within the through passage, and a second closed position in which an intermediate portion of the spring retainer is held by spring force against an outer surface of the lynch pin. The spring retainer also has abutting side portions arranged to abut respective sides of the first element to prevent rotational movement of the lynch pin to the first position. While the invention has been described in connection with specific embodiments thereof, it is to be understood that this is by way of illustration and not of limitation, and the scope of the appended claims should be construed as broadly as the prior art will permit. | 11,234 |
11859693 | DETAILED DESCRIPTION Reference will now be made to the drawings wherein like reference numerals identify similar structural features or aspects of the subject invention. For purposes of explanation and illustration, and not limitation, a partial view of an exemplary embodiment of a gear assembly in accordance with the disclosure is shown inFIG.1and is designated generally by reference character100. Other embodiments of the gear assembly in accordance with the invention, or aspects thereof, are provided inFIG.2as will be described. The methods and systems of the invention can be used to simplify gear retention and precision between different systems. FIG.1shows a gear assembly100including a first gear wheel102, which includes a shaft bore104which defines a primary axis106. The first gear wheel102further includes a first gear108wherein teeth110of the first gear108are oriented parallel to the primary axis106and a second gear112wherein teeth114of the second gear112are oriented not-parallel to the primary axis106. The gear assembly100also includes a second gear wheel116meant to mate the second gear112of the first gear wheel102. The second gear wheel116includes an outer gear118wherein teeth120of the outer gear118are oriented parallel to the primary axis106and an inner gear122wherein teeth124of the inner gear122are oriented parallel to teeth114of the second gear112of the first gear wheel102. The second gear112of the first gear wheel102and the inner gear122of the second gear wheel116mate and can form, for example, helical splines. FIG.1further shows a set of shims126configured to appropriately locate the second gear wheel116along the shaft bore104and a retention member128, such as a retaining ring, a locknut, or a pressed on bearing, to secure the second gear wheel116and the set of shims126. The second gear wheel116has to be positioned on the first gear wheel102such that the second gear wheel lines up appropriately with other outer systems (not shown) and such that the teeth110of the first gear are aligned with the teeth120of the second gear wheel116. This alignment is important for timing and torque transfer purposes of the assembly100. When the assembly100is pressed together, when the first gear wheel102is held in place, and the second gear wheel116slides along the teeth114of the second gear112, the second gear wheel116will rotate, allowing a user to locate and align the teeth114of the second gear and the teeth120of the outer gear118of the second gear wheel116. Once the appropriate location of the second gear wheel116along the second gear112is identified, the second gear wheel can be secured with the shim126. The ability to rotate the second gear wheel116circumferentially by changing its axial position along the spline of the second gear112saves machinists and assembly personnel a lot of time when assembling cluster gears. The shims of the shim pack126can be arranged as required in order to secure the second gear wheel116. For instance inFIG.1, two shims of differing thicknesses are placed on each side of the second gear wheel116. The shims of the shim pack126can consist of varying thicknesses, it is also considered that shim packs126can include shims of the same thickness. For example in a non-limiting configuration, in order to move the second gear wheel116closer to the first gear wheel108by 0.004 inches, a user would remove one 0.054 shim from one side of the second gear wheel116and swap it with a 0.050 shim from the second side of the second gear wheel. This allows an angular rotation between the gear teeth110and the gear teeth120to adjust timing following the angle of the helical spline. Further shown inFIG.1, a flange130on the first gear wheel102in order to help secure the retaining member128. The first gear wheel can include a second flange132configured to define a maximum position of the second gear wheel116along the second gear112of the first gear wheel102. FIG.2shows the gear assembly100in an assembled manner. The first gear108is shown having a larger primary diameter (D1) than the outer diameter (D2) of the second gear112, also first gear108of the first gear wheel102includes a larger primary diameter (D1) than the diameter (D3) outer gear118of the second gear wheel116. Although alternate embodiments wherein D3is larger than D1and D2is larger than D1are also possible. The second gear112of the first gear wheel102is wider along the primary axis106than the second gear wheel116. This feature further allows the second gear wheel116to be positioned in multiple locations along the second gear112of the first gear wheel102, and be adaptable to multiple configurations and applications. Further, arrangement of the splined gears provides an axial thrust load. When torque is applied from either the first gear wheel102or from the second gear wheel116that gear pushes axially into the shoulder of the other gear. If the torque is reversed the force goes into the retention member128. Reversing the orientation of the spline of the gears allows the loads to be reversed as well. For example, as long as the torque is always the same way for an application a user is able to select which component takes the thrust load, a gear or retaining member, locking in the timing consistently for each load application. The gear assembly100allows for a simple method of assembly without needing to welding and grinding. The assembly process allows for simply threading the second gear wheel116onto the first gear wheel102, measuring the timing of the system without the shims126, and if necessary removing the second gear wheel116and adding the appropriate number or thicknesses of shims126to appropriately position the second gear wheel116along axis106, and installing remaining shims on the opposite side of the second gear wheel116to minimize the space between retention member128and the second gear wheel116. The methods and systems of the present disclosure, as described above and shown in the drawings, provide for a gear assembly with superior properties including increased reliability and stability, and complexity, and/or cost. While the apparatus and methods of the subject disclosure have been shown and described with reference to certain exemplary embodiments, those skilled in the art will readily appreciate that changes and/or modifications may be made thereto without departing from the spirit and score of the subject disclosure. | 6,426 |
11859694 | DETAILED DESCRIPTION It will be understood that when an element (or mechanism or module) is referred to as being “disposed on”, “connected to” or “coupled to” another element, it can be directly disposed on, connected or coupled to another element, or it can be indirectly disposed on, connected or coupled to another element, that is, intervening elements may be present. In contrast, when an element is referred to as being “directly disposed on”, “directly connected to” or “directly coupled to” another element, there are no intervening elements present. In addition, the terms first, second, third, etc. are used herein to describe various elements or components, these elements or components should not be limited by these terms. Consequently, a first element or component discussed below could be termed a second element or component. FIG.1shows a three-dimensional schematic view of a linear actuator10according to one embodiment of the present disclosure.FIG.2shows one partial exploded view of the linear actuator10of the embodiment ofFIG.1.FIG.3shows another partial exploded view of the linear actuator10of the embodiment ofFIG.1. Please refer toFIGS.1,2and3, the linear actuator10includes a semi-finished product100and a threaded shaft200. The semi-finished product100includes a case110, a driving module120, and a transmission module130. The case110defines an inner space, and the driving module120is disposed within the inner space and includes a motor121. The transmission module130is disposed within the inner space and includes a main gear131driven by the motor121and a main gear bearing132sleeved on the main gear131. One end of the threaded shaft200is inserted into and restricted by the main gear131. A bushing180can be sleeved on one side of the main gear131. When assembling the semi-finished product100and the threaded shaft200, the threaded shaft200can be inserted from the abovementioned side of the main gear131into the main gear131and then can be restricted thereby. The main gear bearing132is in association with the bushing180to allow the main gear131to rotate stably about one axis. In addition, the main gear131can further include an engaging hole1311having an inner thread (not shown) configured for the threaded shaft200to screw therewith, thereby linking the threaded shaft200and the main gear131. Hence, because the semi-finished product100can be manufactured in advance, the threaded shaft200that is suitable for the demands can then be chosen and assembled, and the assembling efficiency and convenience of the linear actuator10can be increased. FIG.4shows a three-dimensional schematic view of an alignment of a distance adjusting module140of the linear actuator10of the embodiment ofFIG.1. Please refer toFIG.4with reference toFIG.3, the semi-finished product100can further include a distance adjusting module140configured to defect the elevating distance of the threaded shaft200. The distance adjusting module140is detachably disposed at the case110and includes a module housing141and a circuit board142. The circuit board142is received within the module housing141. When the distance adjusting module140is assembled with the case110, the circuit board142is electrically connected to the driving module120. The circuit board142can include micro switches (not shown), and the distance adjusting module140can further include a slave wheel (not labeled) to be engaged with the gear of the driving module120. As shown inFIGS.3and4, the driving module120can further include a connecting portion122electrically connected to the motor121, and the connecting portion122exposes from the case110. The distance adjusting module140can further include an inserting portion143electrically connected to the circuit board142and corresponding to the connecting portion122. The inserting portion143can include a plurality of pins, and the connecting portion122can include a plurality of pin holes corresponding to a plurality of wires of the motor121, respectively. As the inserting portion143is inserted into the connecting portion122, the circuit board142can be electrically connected to the motor121via the inserting portion143and the connecting portion122, and can detect the elevating distance of the threaded shaft200in real-time. The distance adjusting module140can further include another inserting portion (not shown) configured to connect to an outer controller (not shown). The outer controller can receive the elevating distance of the threaded shaft200detected by the distance adjusting module140to stop the motor121according to a predetermined distance setting. Precisely, the case110can further include an engaging groove1101, the module housing141can further include an engaging tab1141, and the shape of the engaging groove1101fits the shape of the engaging tab1141. When the engaging tab1141is engaged with the engaging groove1101, the distance adjusting module140is secured at the case110, and the inserting portion143is inserted into the connecting portion122of the driving module120to complete the electric connection between the driving module120and the distance adjusting module140. Finally, the module housing141can be secured at the case110by screws. If the user would like to remove the distance adjusting module140, the screws can be unscrewed and the distance adjusting module140can be pulled out along the engaging groove1101to allow the inserting portion143to disengage from the connecting portion122, thereby removing the distance adjusting module140. FIG.5shows a partial three-dimensional schematic view of the linear actuator10of the embodiment ofFIG.1. As shown inFIGS.3to5, the semi-finished product100can further include a reinforcing seat150and an end cap160. The reinforcing seat150is disposed within the case110and connected to the main gear131. The reinforcing seat150includes a reinforcing seat body151and at least one installed hole152disposed on the reinforcing seat body151. The reinforcing seat150can share the loads on the case110during an operation of the linear actuator10. The end cap160is detachably connected to the reinforcing seat150and includes an end cap body161and at least one through hole162corresponding to the at least one installed hole152and configured for at least one fastening screw to screw therewith. The at least one fastening screw passes the at least one through hole162to screw with the at least one installed hole152so as to allow the end cap160to be secured at the reinforcing seat150. In other embodiments, the case and the reinforcing seat can be combined in other methods, and the present disclosure is not limited thereto. FIG.6shows a block diagram of a linear actuator assembling method S1according to another embodiment of the present disclosure. Please refer toFIG.6with references toFIGS.1to5, the linear actuator assembling method S1includes a semi-finished product assembling step S2and a threaded shaft assembling step S3. The semi-finished product assembling step S2is to form a semi-finished product100, and the semi-finished product100includes a case110, a main gear131, and a main gear bearing132. The main gear131and the main gear bearing132are surrounded and restricted by the case110, and the main gear bearing132is sleeved on the main gear131. In the threaded shaft assembling step S3, a threaded shaft200is reversely assembled, and one end of the threaded shaft200is inserted into the main gear131to allow the end of the threaded shaft200to be restricted by the main gear131. To be more specific, in the semi-finished product assembling step S2, a distance adjusting module140is allowed to be engaged with the case110and to be electrically connected to a driving module120of the semi-finished product100, and therefore the distance adjusting module140is favorable for the user to quickly remove from or install into the case110for checking or changing purpose. In the threaded shaft assembling step S3, the end of the threaded shaft200is allowed to expose from the main gear131, a spacer170is sleeved on the end of the threaded shaft200, and then a punch riveting process is used to restrict the threaded shaft200. In other embodiments, the threaded shaft can be restricted by the main gear via pins or key grooves to quickly assembled, and the present disclosure is not limited thereto. The other end of the threaded shaft200is configured to combine an elevating mechanism300. The elevating mechanism300linked with the threaded shaft200can move linearly relative to the linear actuator10. In other embodiments, the elevating mechanism can be modified to apply in other fields based on the demands, and the present disclosure is not limited thereto. The semi-finished product100can further include a reinforcing seat150disposed within the case110and sleeved on the main gear bearing132. The reinforcing seat150can further include at least one installed hole152corresponding to at least one opening133of the main gear131. In the semi-finished product assembling step S2, a fixture (not shown) can be used to pass the at least one installed hole152and the at least one opening133to restrict a rotation of the main gear131, and then the threaded shaft200is fastened therewith. Therefore, the installed hole152can be configured for the fixture to pass therethrough for restricting the main gear131, and, in the later process, the installed hole152can be configured for an end cap160to fasten therewith. Moreover, the opening133on the main gear131is favorable for losing weight and decreasing cost, and the structure can have lots of functions. Additionally, the linear actuator assembling method S1can further include an end cap assembling step S4, and the end cap160is allowed to connect to the semi-finished product100. Hence, the protection effect and the anti-dust effect can be achieved. As described above, the present disclosure is to assemble the components other than the threaded shaft200into a semi-finished product100, the threaded shaft200that is suitable for the demands can then be chosen and assembled by the user, and the assembling efficiency and convenience of the linear actuator10can be increased. Although the present disclosure has been described in considerable detail with reference to certain embodiments thereof, other embodiments are possible. Therefore, the spirit and scope of the appended claims should not be limited to the description of the embodiments contained herein. It will be apparent to those skilled in the art that various modifications and variations can be made to the structure of the present disclosure without departing from the scope or spirit of the disclosure. In view of the foregoing, it is intended that the present disclosure covers modifications and variations of this disclosure provided they fall within the scope of the following claims. | 10,826 |
11859695 | DETAILED DESCRIPTION OF THE INVENTION When describing the invention, the terms used are to be construed in accordance with the following definitions, unless a context dictates otherwise. Reference throughout this specification to “one embodiment” or “an embodiment” means that a particular feature, structure or characteristic described in connection with the embodiment is included in at least one embodiment of the present invention. Thus, appearances of the phrases “in one embodiment” or “in an embodiment” in various places throughout this specification are not necessarily all referring to the same embodiment, but may. Furthermore, the particular features, structures or characteristics may be combined in any suitable manner, as would be apparent to a person skilled in the art from this disclosure, in one or more embodiments. Furthermore, while some embodiments described herein include some but not other features included in other embodiments, combinations of features of different embodiments are meant to be within the scope of the invention, and form different embodiments, as would be understood by those in the art. As used in the specification and the appended claims, the singular forms “a”, “an,” and “the” include plural referents unless the context clearly dictates otherwise. By way of example, “a gear” means one gear or more than one gear. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as is commonly understood by one of skill in the art. All publications referenced herein are incorporated by reference thereto. Throughout this application, the term ‘about’ is used to indicate that a value includes the standard deviation of error for the device or method being employed to determine the value. The recitation of numerical ranges by endpoints includes all integer numbers and, where appropriate, fractions subsumed within that range (e.g. 1 to 5 can include 1, 2, 3, 4 when referring to, for example, a number of elements, and can also include 1.5, 2, 2.75 and 3.80, when referring to, for example, measurements). The recitation of end points also includes the end point values themselves (e.g. from 1.0 to 5.0 includes both 1.0 and 5.0). Any numerical range recited herein is intended to include all sub-ranges subsumed therein. In the present description of the invention, reference is made to the accompanying drawings that form a part hereof, and in which are shown by way of illustration only of specific embodiments in which the invention may be practiced. Parenthesized or emboldened reference numerals affixed to respective elements merely exemplify the elements by way of example, with which it is not intended to limit the respective elements. It is to be understood that other embodiments may be utilised and structural or logical changes may be made without departing from the scope of the present invention. The following detailed description, therefore, is not to be taken in a limiting sense, and the scope of the present invention is defined by the appended claims. As used herein, the term “integral gear” is a gear which is monolithic with the axle or shaft. The integral gear and the shaft or axle may be tooled from the same single object. As used herein, the term “cluster gears” refers to at least two gears which are rigidly connected to each other, preferably the two gears are monolithic. The at least two gears may be tooled from the same single object. In some embodiments, the two gears forming a cluster gear may be spaced apart from each other by a connecting section. The term “rotationally fixed” refers to an attachment in which rotation between the parts is locked. The term “permanently rotationally fixed” refers to an attachment in which rotation between the parts is locked at least for a duration of the lifetime of the gearbox but may optionally be detached for the purpose of repair and/or servicing. The term “axially fixed” refers to an attachment in which an axial position of a part is locked with respect to a shaft (e.g. a gear on a shaft). The term “permanently axially fixed” refers to an attachment in which an axial position of a part is locked with respect to a shaft at least for a duration of the lifetime of the gearbox but may optionally be detached for the purpose of repair and/or servicing. The term “revolutely attached” refers to an attachment in which rotation between the parts is not locked (e.g. free-spinning gear on a shaft). Described here is a gearbox (100) for use in a vehicular transmission (see e.g.FIGS.1to3), comprising:an inner input drive shaft (10) and an outer input drive shaft (40) both transmitting torque from a dual-clutch (250) (to the gearbox),a counter-shaft (70) for output of torque and adapted for operable connection to wheels (308,310) of the vehicle (via one or more gears and a differential (300)), whereinthe outer input drive shaft (40) supports gears (42,44,46,48,49) for 4 forward even-number gear speeds and 1 reverse gear direction, and the inner input drive shaft supports gears (11,13,15,17) for 4 forward odd-number gear speeds, each gear meshed with a corresponding gear pair (79,72,74,76,78,79,71,73,75,77) on the counter-shaft (70), wherein a gear speed is selected by an axial movement of an axially adjacent synchroniser sleeve of a corresponding synchroniser (22,52,54,92,94), said synchroniser sleeve being rotationally fixed and axially slidable relative to one of the shafts (10,40,70) and the selected gear (15,17,44,46,48,71,72,73,79) being revolutely attached to the same shaft (10,40,70), wherein the axial movement of the adjacent synchroniser sleeve engages the selected gear (15,17,44,46,48,71,72,73,79) and rotationally fixes it with respect to the same shaft (10,40,70) as the synchroniser (22,52,54,92,94), the selected gear being meshed with a gear pair (75,77,74,76,78,11,42,13,49) permanently rotationally fixed to the other shaft. The forward gear pairs may each be directly meshed. The reverse gear pair (49,79) are not directly meshed; in order to reverse direction of rotation, an intervening idler gear (59) engages with both reverse gear pairs (49,79). Typically, the gears (15,17,44,46,48,71,72,73,79) that are revolutely attached to their shaft (10,40,70) are free-spinning and have a fixed axial (non-slidable) position on the shaft. The adjacent synchroniser engages the selected gear so rotation of the shaft and free-spinning gear become locked or synchronised. A synchroniser (22,52,54,92,94) refers to any assembly that reproducibly brings a gear wheel normally revolutely attached to a shaft, into locked rotation with the shaft. A synchroniser typically comprises a hub permanently rotationally fixed and permanently axially fixed to the shaft. The synchroniser typically further comprises a sleeve, rotationally fixed to the hub that is slidable relative to the hub. The movement of the sleeve towards the free-spinning gear engages the sleeve with locking toothing on the free-spinning gear, so that the rotation of the shaft and free-spinning gear become locked or synchronised. The locking toothing on the gear is separate from the gear teeth that mesh with the other gear of the gear pair. A synchroniser may contain other elements such as a friction cone on the selected gear, synchroniser ring having a conical surface that engages with the friction cone on the selected gear. Other variations of a synchroniser exist as is understood in the art. More particularly, the invention relates to a gearbox (100) for use in a vehicular transmission, comprising:an inner input drive shaft (10) and an outer input drive shaft (40) both transmitting torque from a dual-clutch (250) (to the gearbox),a counter-shaft (70) for output of torque and adapted for operable connection to wheels (308,310) of the vehicle (via one or more gears and a differential (300)), whereinthe outer input drive shaft (40) supports gears (42,44,46,48,49) for 4 forward even-number gear speeds and 1 reverse gear direction, and the inner input drive shaft supports gears (11,13,15,17) for 4 forward odd-number gear speeds, each forward gear meshed with a corresponding gear pair (72,74,76,78,79,71,73,75,77) on the counter-shaft (70), the reverse gear (49) meshed via an idler gear (59) with the corresponding gear pair (79) on the counter-shaft (70),a gear speed is selected by an axial movement of an axially adjacent synchroniser sleeve of a corresponding synchroniser (22,52,54,92,94), said synchroniser sleeve being rotationally fixed and axially slidable relative to one of the shafts (10,40,70) and the selected gear (15,17,44,46,48,71,72,73,79) being revolutely attached to the same shaft (10,40,70), wherein the axial movement of the adjacent synchroniser sleeve engages the selected gear (15,17,44,46,48,71,72,73,79) and rotationally fixes it with respect to the same shaft (10,40,70) as the synchroniser (22,52,54,92,94), the selected forward gear or selected reverse gear (79) via the idler gear (59) being meshed with a gear pair (75,77,74,76,78,11,42,13,49) permanently rotationally fixed to the other shaft;and,the permanently rotationally fixed gear (75,77,74,76,78,11,42,13,49) is the smaller of the gear pair. The smaller gear preferably referring to the radially smaller gear. This may allow providing at least one or more of the small gears as integral gear on a shaft without having to have a too large diameter on the shaft shape. The larger gear (79,72,44,46,48,17,15,73,71) of the gear pair, is revolutely attached (freely spinning) to the same shaft as the synchroniser (94,54,22,92); the synchroniser sleeve thus engages with the larger gear (79,72,44,46,48,17,15,73,71) of the gear pair. Due to the larger diameter, the larger gear may be axially thinned under the gear teeth creating axial space, into which at least part of the synchroniser can reside, preferably the synchroniser ring can be fitted. Hence, the total axial length of the gearbox may be reduced. The larger gear (79,72,44,46,48,17,15,73,71) of at least one gear set may comprise at least one annular recess that axially reduces the width of the gear body (below the meshing teeth). At least a part of the adjacent synchroniser may be positioned in said annular recess. This may result in a shorter axial length of the gearbox. The larger gear (79,72,44,46,48,17,15,73,71) of the gear pair is a revolutely loose gear wheel having a fixed axial position. Preferably, the larger gear (79,72,44,46,48,17,15,73,71) is mounted on a bearing, said bearing being mounted on a shaft (10,40,70), preferably the outer input shaft (40), the inner input shaft (10) and/or the counter shaft (70). In some embodiments, the gearbox is a 2-shaft design. As used herein the term “2-shaft design” refers to the number of shaft centerlines, i.e. input and countershaft, and not the total number of shafts. Likewise, a “3-shaft design” has 3 main shaft centerlines, i.e. input and two countershafts. The reverse idler shaft (60) is not considered a separate centerline. In some embodiments, the gearbox is suitable to be coupled to a dual clutch. In some embodiments, a double-sided synchroniser (94) is configured to engage alternatively with one gear of the reverse gear pair, one gear of the 2ndgear pair, or with no gear at all, preferably by engaging with the larger gear (79,72) of each gear pair. In some embodiments, a double-sided synchroniser (54) is configured to engage alternatively with one gear of the 4thgear pair, one gear of the 6thgear pair, or with no gear at all, preferably by engaging with the larger gear (44,46) of each gear pair. In some embodiments, a double-sided synchroniser (52) is configured to engage alternatively with one gear of the 8thgear pair, or with no gear at all, preferably by engaging with the larger gear (48) of the 8thgear set. In some embodiments, a double-sided synchroniser (22) is configured to engage alternatively with one gear of the 7thgear pair, one gear of the 5thgear pair, or with no gear at all, preferably by engaging with the larger gear (17,15) of each gear set. In some embodiments, a double-sided synchroniser (92) is configured to engage alternatively with one gear of the 3rdgear pair, one gear of the 1stgear pair, or with no gear at all, preferably by engaging with the larger gear (13,11) of each gear set. In some embodiments, one gear of the gear pair corresponding to gear speeds 4th(74) 6th(76), 5th(75), 7th(77) and 8th(79) is each permanently rotationally and permanently axially fixed to the counter-shaft (70). In some embodiments, one gear of the gear pair corresponding to gear speeds 1st(71) and 3rd(73) is each attached in revolute relation to the counter-shaft (70), each gear configured to engage alternately with the same synchroniser sleeve rotationally fixed to the counter-shaft (70) by sliding the synchroniser sleeve axially, and both gears flank the synchroniser (92); and, the other gear of the gear pair corresponding to gear speeds 1st(11) and 3rd(13) is each permanently rotationally and permanently axially fixed to the inner input drive shaft (10). In some embodiments, one gear of the gear pair corresponding to gear speeds 5th(15) and 7th(17) is each attached in revolute relation to the inner input drive shaft (10), each gear configured to engage alternately with the same synchroniser sleeve rotationally fixed to the inner input drive shaft (10) by sliding the synchroniser sleeve axially, and both gears flank the synchroniser (22); and, the other gear of the gear pair corresponding to gear speeds 5th(75) and 7th(77) is each permanently rotationally and permanently axially fixed to the counter-shaft (70). In some embodiments, one gear of the gear pair corresponding to gear direction reverse (79) and to gear speed 2nd(72) is each attached in revolute relation to the counter-shaft (70), each gear configures to engage alternately with the same synchroniser sleeve rotationally fixed to the counter-shaft (70) by sliding the synchroniser sleeve axially, and both gears flank the synchroniser (94); and, the other gear of the gear pair corresponding to gear direction reverse (49) and to gear speed 2nd(42) is each permanently rotationally and permanently axially fixed to the outer input drive shaft (40). In some prior art designs, the reverse gear on an input drive shaft supports odd-numbered gears, i.e. the same shaft as the 1stgear. In the present configuration, the reverse gear is provided on the outer input drive shaft (40) supporting even numbered gears. The configuration allows a 1st-reverse-1stgear shift to be purely a clutch to clutch shift since the 1stand reverse gears remain preselected in the gear box. With the prior art design where the reverse gear on the input drive shaft support odd-numbered gears, the same sequence requires a gear to gear shift: clutch opens, gear selection changes 1st-reverse-1st, clutch closed. A clutch to clutch shift is much faster, and also leads to less mechanical wear because the synchroniser is not called into action. Transmissions with reverse and 1stgear on same shaft are known to suffer from delays in changing vehicle direction leading to more difficult parking manoeuvres. In some embodiments, one gear of the gear pair corresponding to gear speeds 4th(44) and 6th(46) is each attached in revolute relation to the outer input drive shaft (40), each gear configured to engage alternately with the same synchroniser sleeve rotationally fixed to the outer input drive shaft (40) by sliding the synchroniser sleeve axially, and both gears flank the synchroniser (54); and, the other gear of the gear pair corresponding to gear speeds 4th(74) and 6th(76) is each permanently rotationally and permanently axially fixed to the counter-shaft (70). In some embodiments, one gear of the gear pair corresponding to gear speed 8th(48) is attached in revolute relation to the outer input drive shaft (40), said gear configured to engage with the synchroniser sleeve rotationally fixed to the outer input drive shaft (40) by sliding the synchroniser sleeve axially; and, the other gear of the gear pair corresponding to gear speed 8th(78) is permanently rotationally fixed and permanently axially to the counter-shaft (70). In some embodiments, the outer input drive shaft (40) is supported by a housing on two separate bearings (56,58) that flank the collection of gears (42,44,46,48,49) thereon, and the inner input drive shaft is supported by a housing on two separate bearings (24,26) that flank the collection of gears (11,13,15,17) thereon. Preferably bearings are radial bearings. This may have the advantage that the outer input shaft does not need to be provided with a collar to fit over a bearing between the outer and inner input shaft. Hence the diameter of outer input shaft does not need to be enlarged. This may also has the advantage that the bearing may have a higher load capacity, as the load may be split over more bearings. In some embodiments, one gear of the gear pair corresponding to gear speeds 1st(11) and 3rd(13) is each integral with the inner drive shaft (10). In some embodiments, one gear of the gear pair corresponding to the reverse gear (49) and the 2ndgear speed (42) is each integral with the outer drive shaft (40). In some embodiments, the gears on the counter-shaft (70) are arranged in two axially-separated groups (79,72,74,76,78and71,73,75,77) corresponding to the even and odd-numbered gear speeds, and within each group in ascending order of gear speed (from the outer ends) towards middle of the counter-shaft (70). As the diameter of the smallest gear limits the maximum diameter of the shaft, it is advantageous to provide a shaft with the largest diameter in the middle, and then thinning the diameter towards the ends, so that gears can be slid on the shaft from both ends. Such a lay out provides for the smallest possible small gear, thereby enlarging the ratio spread. In some embodiments, the counter-shaft (70) comprises an output gear (80) rotationally fixed disposed towards the middle of the counter-shaft. As the output gear does not mesh with a gear on one of the input shafts, axial space is available at the axial height of the output gear on the input shafts. This space may be used for bearing the inner input shaft10and the outer input shaft40by separate radial bearings, instead of one radial bearing, plus a needle bearing between the shafts. This may allow for higher capacity and does not require modification or enlargement of the diameter of the outer input shaft to accommodate for a bearing between the two input shafts. In some embodiments, the output gear (80) is rotationally fixed by a spline connection. Especially for the high torque applications, a shrink fit with requires more axial length than the axial length of the required gear teeth, a spline connection does not require extra axial space, shortening the overall axial length of the gearbox. In some embodiments, one gear of the gear pair corresponding to gear speeds 4th(74) and 6th(76) is each combined as a cluster gear rotationally fixed by shrink fit to the counter-shaft (70). The connecting section of the cluster gear provides enough surface for a robust shrink fit, strong enough so that the area underneath the smallest gear of the cluster gear does not have to participate in the shrink fit. This way, even the small gear can be fixed by a shrink fit, although their small diameter would not allow it to be shrink fitted on its own. This allows for small “small gears”, allowing a large ratio spread. Especially for the high torque application, the shaft must have quite a large minimum diameter, to be able to handle such high torque. The shrink fit of the cluster gears does not require a reduction in diameter of the countershaft. Even more, such cluster gear can be placed right next to an integral gear. This has the advantage that the axial length can be optimally used, what is not possible for two integral gears, as they cannot be tooled when they are right next to each other or touching each other on a shaft. In some embodiments, one gear of the gear pair corresponding to gear speeds 5th(75) and 7th(77) is each combined as a cluster gear rotationally fixed by shrink fit to the counter-shaft (70). In some embodiment, the small gears (74and76;77and75) of gear sets (4thand 6th; 7thand 5th) which are actuated by the same synchroniser (54,22) are combined as a cluster gear on the countershaft (70). In some embodiments, one gear of the gear pair corresponding to the 8thgear (78) is integral with the counter-shaft (70). In some embodiments, the small gear (74) of the 4thgear set and the small gear76of the 6thgear set cluster gear is placed less than 10 mm, preferably less than 8 mm, more preferably less than 6 mm, even more preferably less than 4 mm, yet more preferably less than 2 mm, and most preferably less than 1 mm axial distance away from the small gear (78) of the 8thgear set on the countershaft (70). In some embodiments, the small gear (74) of the 4thgear set and the small gear (76) of the 6thgear set cluster gear is touching the small gear (78) of the 8thgear set on the countershaft (70), preferably the small gear (76) of the 6thgear set is touching the small gear (78) of the 8thgear set. In some embodiments, the counter-shaft (70) is supported by a housing on three separate bearings (86,88,90), two (86,90) that flank the collection of gears thereon, and one (88) disposed towards the middle of the counter-shaft preferably between the collection of odd and even-numbered gears. This has the advantage of improving shaft strength and reducing deformations. Preferably, said bearings are radial bearings. In some embodiments, the gearbox comprises a pinion shaft (84), whereon a pinion (83) is rotationally fixed for meshing with the ring gear (302) on a differential (300) and whereon a gear (82) is rotationally fixed for meshing with the output gear (80). In some embodiments, the gearbox comprises an idler gear (59), mounted on an idler shaft (60), for meshing with both the larger gear (79) of the reverse gear set and the smaller gear (49) of the reverse gear set. In another aspect, the invention provides in a transaxle transmission comprising the gearbox according to an embodiment of the invention. The invention will be more readily understood by reference to the following examples, which are included merely for purpose of illustration of certain aspects and embodiments of the present invention and are not intended to limit the invention. EXAMPLES FIG.1depicts a schematic representation of a gear box according to an embodiment of the invention. Power is fed from the engine (200) to the dual clutch (250), the output of the dual clutch are the power input of the gear box (100), i.e. the inner input drive shaft (10) and the outer input drive shaft (40), these two input shafts (10), (40) being at least partially concentrically arranged. Parallel to these input shafts (10,40), a single countershaft (70) is arranged; hence, the gear box (100) is as known in the art a 2-shaft design. The countershaft supports an output gear (80), which meshes with a gear (82) on the pinion shaft (84), said pinion shaft transferring power to the differential (300), preferably a limited slip differential by meshing of the pinion (83) with the ring gear (302) of the differential, said differential splitting the torque over the two output shafts (304) and (306), respectively connected to the wheels (308and310). The outer input shaft (40), provides the even gear sets, i.e. 2nd, 4th, 6th, 8thgear sets, and the reverser gear set, and this by starting from the engine side:the smallest gear (49) of the reverse gear pair being rotationally fixed to the outer input shaft (40), by being an integral gear;the smallest gear (42) of the 2ndgear pair being rotationally fixed to the outer input shaft (40); by being an integral gear;the largest gear (44) of the 4thgear set being rotationally supported by the outer input shaft (40) via a bearing;the 4th/6thgear synchroniser (54being rotationally fixed to the outer input shaft (40), via a spline connection;the largest gear (46) of the 6thgear set being rotationally supported by the outer input shaft (40) via a bearing;the largest gear (48) of the 8thgear set being rotationally supported by the outer input shaft (40) via a bearing;the 8thgear synchroniser (52) being rotationally fixed to the outer input shaft (40); Wherein the 4th/6thgear synchroniser is a double sided synchroniser, configured to either engage with the 4thgear, the 6thgear or no gear at all. The 8thgear synchroniser (52) is a single sided synchroniser configured to either engage with the 8thgear or no gear at all. FIG.2shows the bearings used to support the different shafts in the housing. The outer input shaft (40) is borne by two bearings (56and58). The inner input shaft (10) is borne by two bearings (26and24). The countershaft is borne by three bearings one at each end (86and90), and a bearing (88) between the output gear (80) and the smallest gear (77) of the 7thgear set. The pinion shaft (84) is borne by bearings (92and94). The differential (300) is borne by bearings (314and318). Wheel bearings (312and316) bear the output shafts (304and306). FIG.3shows a cross-section view of an exemplary gearbox described herein.FIG.3shows that the largest gear (46) of the 6thgear pair comprises an annular recess at the engine side, wherein at least part of the synchroniser ring of the 6thgear is placed in, said recess thereby reducing the axial length of the gear box. FIG.3further shows that the largest gear (48) of the 8thgear pair comprises an annular recess at the opposing engine side, wherein at least part of the synchroniser ring of the 8thgear is placed in, said recess thereby reducing the axial length of the gear box. The inner input shaft (10), provides the odd gear sets, i.e. 1th, 3th, 5th, 7thgear sets, and this by starting from the engine side:the largest gear (17) of the 7thgear set being rotationally supported by the inner input shaft (10) via a bearing;the 7th/5thgear synchroniser (22) being rotationally fixed to the inner input shaft (10, via a spline connection;the largest gear (15) of the 5thgear set being rotationally supported by the inner input shaft (10) via a bearing;the smallest gear (13) of the 3thgear pair being rotationally fixed to the inner input shaft (10), by being an integral gear;the smallest gear (11) of the 1stgear pair being rotationally fixed to the inner input shaft (10), by being an integral gear; Wherein the 7th/5thgear synchroniser is a double sided synchroniser, configured to either engage with the 7thgear, the 5thgear or no gear at all. FIG.3further shows that the largest gear (17) of the 7thgear pair comprises an annular recess at the opposing engine side, wherein at least part of the synchroniser ring of the 7thgear is placed in, said recess thereby reducing the axial length of the gear box. The countershaft provides starting from the engine side:the largest gear (79) of the reverse gear set being rotationally supported by the countershaft (70) via a bearing;the reverse/2thgear synchroniser (94) being rotationally fixed to the countershaft (70), via a spline connection;the largest gear (72) of the 2ndgear set being rotationally supported by the countershaft (70) via a bearing;the smallest gear (74) of the 4thgear pair being rotationally fixed to the counter shaft (70), via a shrink fit, thereby not requiring a reduction in diameter of the countershaft for said rotational fix;the smallest gear (76) of the 6thgear pair being rotationally fixed to the counter shaft (70), via being connected to the smallest gear (74) of the 4thgear pair by being a cluster gear, hence this rotational fix does not require a reduction in diameter of the countershaft;the smallest gear (78) of the 8thgear pair being rotationally fixed to the counter shaft (70, by being an integral gear;the output gear (80) being rotationally fixed to the counter shaft (70), via a spline connection;the smallest gear (77) of the 7thgear pair being rotationally fixed to the counter shaft (70), via being connected to the smallest gear (75of the 5thgear pair by being a cluster gear, hence this rotational fix does not require a reduction in diameter of the countershaft.the smallest gear (75) of the 5thgear pair being rotationally fixed to the counter shaft (70), via a shrink fit, thereby not requiring a reduction in diameter of the countershaft for said rotational fix;the largest gear (73) of the 3thgear set being rotationally supported by the countershaft (70) via a bearing;the 3th/1stgear synchroniser (92) being rotationally fixed to the countershaft (70), via a spline connection;the largest gear (71) of the 1stgear set being rotationally supported by the countershaft (70) via a bearing. InFIG.3the largest gear (79) of the reverse gear pair comprises an annular recess at the opposing engine side, wherein at least part of the synchroniser ring of the reverse gear is placed in, said recess thereby reducing the axial length of the gear box. InFIG.3the largest gear (72) of the 2ndgear pair comprises an annular recess at the engine side, wherein at least part of the synchroniser ring of the 2ndgear is placed in, said recess thereby reducing the axial length of the gear box. InFIG.3the largest gear (71) of the 1stgear pair comprises an annular recess at the engine side, wherein at least part of the synchroniser ring of the 1stgear is placed in, said recess thereby reducing the axial length of the gear box. FIG.3also shows bearings used to support the different shafts in the housing. The outer input shaft (40) is borne by two bearings (56and58) (only part of the bearing58is drawn). The inner input shaft (10) is borne by two bearings (26and24) (only part of the bearing26is drawn). The countershaft is borne by three bearings one at each end (86and90), and a bearing (88) (only part of the bearing88is drawn) between the output gear (80) and the smallest gear (77) of the 7thgear set. The pinion shaft (84) is borne by bearings (92and94). It is to be understood that although preferred embodiments and/or materials have been discussed for providing embodiments according to the present invention, various modifications or changes may be made without departing from the scope and spirit of this invention. | 30,505 |
11859696 | DESCRIPTION OF THE EMBODIMENTS FIG.1depicts a drivetrain1of a vehicle which comprises a main engine2, for example a combustion engine, a transmission gearbox3and a system4for driving and synchronizing a countershaft5of the transmission gearbox3. The main engine2is connected to a primary shaft6of the transmission gearbox3by means of a clutch device8of any appropriate type, for example a slip clutch. The clutch device8has an engaged state in which it is able to transmit torque between the main engine2and the primary shaft6of the transmission gearbox3, and a disengaged state in which the main engine2and the primary shaft6of the transmission gearbox3are uncoupled. The transmission gearbox3is housed inside a transmission casing7. The transmission gearbox3comprises a primary shaft6, a countershaft5and a secondary shaft9which is intended to be connected to the driven wheels of the vehicle via a differential, not depicted. The transmission gearbox3comprises countershaft gear wheels10,11,12,13,14which rotate as one with the countershaft5. The transmission gearbox3also comprises two primary gear wheels15,16which are coaxial with the primary shaft6and each form a gearset with one of the countershaft gear wheels10,11. A three-position dual synchronizer17allows one or other of the primary gear wheels15,16to be coupled to the primary shaft6, and has a neutral position in which neither one of the primary gear wheels15,16is coupled to the primary shaft6. The transmission gearbox3also comprises secondary gear wheels18,19,20, which are coaxial with the secondary shaft9. The secondary gear wheels18,19,20each form, with one of the countershaft gear wheels12,13,14, a gearset. The gearsets formed by the secondary gear wheels18,19,20and the corresponding countershaft gear wheels12,13,14are in permanent mesh. One of the gearsets has an additional gearwheel21between one of the secondary gear wheels20and one of the countershaft gear wheels14in order to create a reverse gear ratio able to reverse the direction of rotation of the secondary shaft9. A three-position dog coupling22without synchronizer, positioned between two of the secondary gear wheels19,20, makes it possible to either couple one or other of the two associated secondary gear wheels19,20to the secondary shaft9, or, in a neutral position, to keep the secondary gear wheels19,20uncoupled from the secondary shaft9. In the embodiment depicted, the axis of revolution of the primary shaft6is aligned with the axis of revolution of the secondary shaft9. Furthermore, the primary gear wheel16is positioned so that it straddles one end of the primary shaft6and one end of the secondary shaft9. Thus, said primary gear wheel16can also be used as a secondary gear wheel by being rotationally coupled to the secondary shaft9. To this end, a three-position dog coupling23, positioned between said primary gear wheel16and the secondary gear wheel18, makes it possible to couple either the primary gear wheel16or the secondary gear wheel18to the secondary shaft9, and also makes it possible, in a neutral position, to keep the primary gear wheel16and the secondary gear wheel18uncoupled from the secondary shaft9. A transmission gearbox3such as this thus has six forward gears and two reverse gears that can, if applicable, be coupled at the output of the secondary shaft9to a planetary gearset (not illustrated) in order to obtain a 12-speed transmission gearbox. The drive and synchronization system4is associated with the countershaft5of the transmission gearbox3in order to drive or brake same. The drive and synchronization system4comprises a reversible electric machine24powered by a battery43, a reduction gearset25and a coupling device26. The reversible electric machine24comprises a stator and a rotor which is connected to the coupling device26via the reduction gearset25. The coupling device26has a coupled state in which it is able to transmit torque between the reversible electric machine24and the countershaft5, and an uncoupled state in which the transmission of torque between the reversible electric machine24and the countershaft5is interrupted. The drive and synchronization system4is notably intended to be used during the transient phases in the change in gear ratio of the transmission gearbox3. Specifically, during these transient phases, the reversible electric machine24may be used as an electric motor to increase the rotational speed of the countershaft5or as an electrodynamic brake to decrease the rotational speed of the countershaft5. This adapting of the rotational speed of the countershaft5thus makes it possible to reduce the length of the transient phases in the change in gear ratio. Outside of the transient phases, the reversible electric machine24may also be used in a motor mode, in which the reversible electric machine24supplies a driving torque to the wheels. The reversible electric machine24is capable of being used jointly with the main engine2to supply additional power for the traction of the vehicle. In that case, the clutch device8is in the engaged configuration. According to one embodiment, the reversible electric machine24may also be used in a mode in which the vehicle traction is purely electric. In such a mode of operation, the clutch device8is then in the disengaged configuration. Moreover, the reversible electric machine24may also be used, in a current generator mode, to recharge the battery43. Outside of the transient phases and when the reversible electric machine24is being used neither in a current generator mode nor in a motor mode, the coupling device26is positioned in the uncoupled state so as to limit the drag torque liable to be generated by the reversible electric machine24, thereby making it possible to reduce the fuel consumption of the main engine2. In connection with the first embodiment ofFIGS.2to4, there may be seen a module48according to a first embodiment comprising a bearing part33mounted without the ability to rotate on the chassis of the vehicle, and a coupling device26of the drive and synchronization system4. The coupling device26comprises an input element27which is coupled to the reversible electric machine24and an output element28(indicated schematically inFIG.1only and not depicted inFIGS.2to4) which is coupled to the intermediate shaft5. In the coupled state, the coupling device26is able to transmit torque between the input element27and the output element28. By contrast, in the uncoupled state, the transmission of torque between the input element27and the output element28is interrupted. The input element27comprises an input hub29. The input hub29comprises internal splines30and is intended to accept a splined end of a shaft, not depicted, which is coupled to the reversible electric machine24via the reduction gearset25. The input hub29is supported and guided in rotation inside a bearing part33which is fixed to a casing of the drivetrain1(the casing is not depicted), and which is intended to be fixed to the chassis of the vehicle. According to a variant of the invention, the bearing part33can be a plain bearing. According to another variant of the invention, a needle or ball bearing can be inserted radially between the bearing part33and the input hub29. In the embodiment depicted, the coupling device26is a multidisc wet coupling device. The input element27comprises two half-casings31,32fixed together and together defining an internal space housing a multidisc assembly intended to transmit torque between the input element27and the output element28when said coupling device26is in the coupled state, an actuating piston34, and a hydraulic fluid such as oil. The multidisc assembly comprises a plurality of annular plates35, for example made of steel, which rotate as one with the input element27and are mounted with the ability to slide axially with respect to the latter. To do that, each plate35on its external periphery has an external toothset which is in mesh with the internal toothset formed on the inside of a cylindrical skirt of one of the half-casings31,32of the input element27. The multidisc assembly further comprises a plurality of friction discs36which are interposed between the plates35. The friction discs36rotate as one with the output element28with the freedom to move in axial translation. For that purpose, the output element28comprises an external toothset and each friction disc36comprises, on its internal periphery, and internal toothset which is in mesh with the external toothset of the output element28. Each friction disc36comprises friction linings arranged on each of its front and rear faces. Moreover, the actuating piston34is mounted with the ability to move axially inside the internal space of the input element27. The actuating piston34comprises, on its external periphery, a seal37which collaborates sealingly with the cylindrical skirt of the half-casing31so as to define a variable-volume sealed chamber38between the actuating piston34and the end wall39of the half-casing31. Moreover, the end wall39of the half-casing31has a duct40, visible inFIG.3, which is connected to a hydraulic circuit fitted with a pump, not depicted, by means of a duct41formed in the bearing part33. When the variable-volume sealed chamber38is supplied with pressurized fluid to move the coupling device26toward a coupled state, the actuating piston34moves towards the multidisc assembly so that the friction discs36are squeezed between the plates35and torque is thus transmitted between the input element27and the output element28. Conversely, when the hydraulic fluid is expelled from the variable-volume sealed chamber38, the actuating piston34slides away from the multidisc assembly so that the friction disc36and the plates35return to an uncoupled position in which they are spaced axially away from one another. Moreover, the module48further comprises a lock-up device42, notably visible inFIGS.2and4, which has a lock-up state in which it blocks the rotation of the input element27with respect to the bearing part33and a released state in which it allows the input element27to rotate with respect to said bearing part33. Thus, when the lock-up device42is in the lock-up state, the coupling device26can, during the transient phases in the change in gear ratio of the transmission gearbox3, be made to brake the countershaft5. The coupling device26then acts as a gearbox brake without placing demands on the reversible electric machine24. Such a lock-up state is notably used in the event of failure of the reversible electric machine24or when the battery43associated with the reversible electric machine24has reached its maximum charge such that use of the reversible electric machine24to brake the countershaft5would carry the risk of damaging the battery43. The make-up of the module48is not restricted to that of the first embodiment described in connection withFIGS.2to4. For example, the module48may also comprise all or part of the reduction gearset25, it being possible for the lock-up device42to be positioned anywhere on the path along which torque is transmitted between the rotor of the reversible electric machine24and the input element27of the coupling device26. Thus, the lock-up device42may notably be associated with one of the gears of the reduction gearset25, with the shaft transmitting torque between the reduction gearset25and the input element27of the clutch, or directly associated with the input element27of the clutch device, as is the case in the embodiment depicted. This last arrangement is particularly advantageous in that it avoids angular lash between the point of application of the rotation blocking force applied by the lock-up device42and the input element27of the clutch device, such angular lash being liable to reduce the performance of the coupling device26when it is acting as a gearbox brake, to generate uncomfortable noise and to cause the drive and synchronization system4to deteriorate. In the embodiment depicted, the lock-up device42comprises a plurality of orifices44, visible inFIG.2, uniformly distributed on the external periphery of the input hub29of the clutch device and a mobile pin45able to be inserted into one of said orifices44. The pin45is mounted with the ability to slide in a bore46formed in the bearing part33between, on the one hand, a lock-up position in which the end of the pin45is inserted in one of the orifices44and thus blocks the rotation of the input element27and, on the other hand, a released position in which the end of the pin45is out of the orifices44, allowing the input element27to rotate. In the embodiment depicted, in order to make it easier for the pin45to be inserted into the orifices44in the lock-up position, the orifices44have chamfered entrances and the pin45has a chamfered end, the chamfered entrances and the chamfered end being configured to facilitate insertion of the pin45into the orifices44. The lock-up device42further comprises a return member47, such as a helical spring, which is positioned between a shoulder of the bore46and a shoulder of the pin45and thus allows the pin45to be returned towards the released position. Moreover, the board46of the bearing part33communicates with a hydraulic or pneumatic circuit, not depicted, equipped with a pump allowing pressure to be applied to the pin45so as to move it into, and keep it in, the lock-up position. Note that the lock-up device42is described hereinabove by way of example, and that the invention is not in any way restricted to the lock-up device42exhibiting such a structure. Thus, according to embodiment variants, the movement of the pin45between the lock-up position and the released position is brought about by an electric actuator. Furthermore, according to another embodiment, the lock-up device42is a dog-clutch coupling device. Such a dog-clutch coupling device comprises, for example, a sliding sleeve which comprises a set of teeth and is fixed in terms of rotation. The sliding sleeve is able to move axially between, on the one hand, a lock-up position in which the toothset of the sliding sleeve meshes with a complementary toothset that rotates as one with the input hub29in order to block the rotation of the latter and, on the other hand, a released position in which the toothsets are parted from one another in order to allow the input hub29to rotate. FIG.5describes a second embodiment of the invention in which the lock-up device42comprises a plurality of teeth54uniformly distributed around the external perimeter of the input hub29of the clutch device and a lever55able to be inserted between two teeth54. The lever55is articulated about an axis Y parallel to and distant from the axis of rotation X of the countershaft5between, on the one hand, a lock-up position in which the end of the lever55is inserted between two teeth54and thus blocks the rotation of the input element27and, on the other hand, a released position in which the end of the lever55is out of the teeth44, allowing the input element27to rotate. In this second embodiment depicted, the lever55has an end56which is inserted between two teeth54when the lever is in the lock-up position. To facilitate the insertion of the lever55between two teeth54in the lock-up position, the teeth54have chamfered entrances and the lever55has chamfers on its end. The lock-up device42further comprises a return member47, such as a torsion spring, which is positioned between an end stop58formed on the lock-up device42and an orifice in the lever55and thus allows the lever55to be returned towards the released position. Moreover, the lever55is made to move by a pushrod59able to apply pressure on the lever55so as to move it into, and keep it in, the lock-up position. A method for operating a drive and synchronization system4as described hereinabove, during the transient phases of a change in gear ratio, is described hereinbelow. During the transient phases of a change in gear ratio, the drive and synchronization system4offers two alternative modes of operation respectively referred to hereinafter as the standard mode and the downgraded mode. The drive and synchronization system4operates in standard mode when no critical event indicative of a state of operation of the reversible electric machine24or of the battery43that powers it has been detected. By contrast, it operates in downgraded mode when such a critical event has been detected. The critical event corresponds, for example, to the detection of a malfunctioning of the reversible electric machine24or to the detection of a state of charge of the battery43associated with the reversible electric machine24which is above a maximum threshold charge. The critical event may also correspond to the detection of a temperature lower than a minimum temperature of use of the battery or of a temperature higher than a maximum temperature of use of the battery. In standard mode, the lock-up device42is in its released state, the coupling device26is operated in such a way that it remains in a coupled position if it already was in that position, or moves from the uncoupled position into a coupled position. The reversible electric machine24is controlled according to a signal representative of a setpoint rotational speed of the countershaft5. In response to the detection of a critical event, the drive and synchronization system4switches over into downgraded mode. The lock-up device42is then moved from its released state into its lock-up state. The coupling device26is then controlled according to a signal representative of a setpoint rotational speed of the countershaft5so that the coupling device26applies a resistive torque that allows the countershaft5to attain the setpoint rotational speed of the countershaft5. The coupling device26thus acts as a gearbox brake. Although the invention has been described in connection with a plurality of particular embodiments, it is obvious that it is in no way limited thereto and that it comprises all technical equivalents of the means described and combinations thereof where these fall within the scope of the invention as defined by the claims. In the claims, any reference sign between parentheses cannot be interpreted as limiting the claim. | 18,247 |
11859697 | DETAILED DESCRIPTION As required, detailed embodiments of the present invention are disclosed herein; however, it is to be understood that the disclosed embodiments are merely exemplary of the invention that may be embodied in various and alternative forms. The figures are not necessarily to scale; some features may be exaggerated or minimized to show details of particular components. Therefore, specific structural and functional details disclosed herein are not to be interpreted as limiting, but merely as a representative basis for teaching one skilled in the art to variously employ the present invention. Referring toFIG.1, an example of an axle assembly10is shown. The axle assembly10may be provided with a motor vehicle like a car, truck, bus, farm equipment, mining equipment, military transport or weaponry vehicle, or cargo loading equipment for land, air, or marine vessels. The motor vehicle may include a trailer for transporting cargo in one or more embodiments. The axle assembly10may provide torque to one or more traction wheel assemblies that may include a tire12mounted on a wheel14. One or more axle assemblies may be provided with the vehicle. In at least one configuration, the axle assembly10may include a housing assembly20, an electric motor22, a rotor shaft24, a drive pinion26, a countershaft transmission28, a drop gear set30, a differential assembly32, at least one axle shaft34, and a control system36. The housing assembly20may facilitate mounting of the axle assembly10to the vehicle. In addition, the housing assembly20may receive various components of the axle assembly10. For example, the housing assembly20may receive and support the electric motor22, the rotor shaft24, the drive pinion26, the countershaft transmission28, the drop gear set30, the differential assembly32, the axle shafts34, or combinations thereof. In at least one configuration, the housing assembly20may include an axle housing40that may have a center portion42and one or more arm portions44. The center portion42may be disposed proximate the center of the housing assembly20. The center portion42may at least partially define a cavity that may receive the differential assembly32. The center portion42may be made of one or more components and may facilitate mounting of a differential carrier that supports the differential assembly32. A lower region of the center portion42may at least partially define a sump portion that may contain lubricant that may be splashed to lubricate internal components of the axle assembly10, such as the differential assembly32and associated bearings. The center portion42may also facilitate mounting of various external components. For instance, the center portion42may facilitate mounting of the electric motor22and the countershaft transmission28to the housing assembly20. One or more arm portions44may extend from the center portion42. For example, two arm portions44may extend in opposite directions from the center portion42and away from the differential assembly32. The arm portions44may have substantially similar configurations. For example, the arm portions44may each have a hollow configuration or tubular configuration that may extend around a corresponding axle shaft34and may help separate or isolate the axle shaft34from the surrounding environment. An arm portion44or a portion thereof may be integrally formed with the center portion42. Alternatively, an arm portion44may be separate from the center portion42. In such a configuration, each arm portion44may be attached to the center portion42in any suitable manner, such as by welding or with one or more fasteners. Each arm portion44may define an arm cavity that may receive a corresponding axle shaft34. It is also contemplated that the arm portions44may be omitted. The electric motor22may provide torque to the differential assembly32via the rotor shaft24, the drop gear set30, the countershaft transmission28, and the drive pinion26. In addition, the electric motor22may be electrically connected to an electrical power source50, such as a battery, capacitor, or the like. An inverter may electrically connect the electric motor22and the electrical power source50. The electric motor22may have any suitable configuration. In at least one configuration, the electric motor22may include a stator52and a rotor54. The stator52may be fixedly positioned with respect to the housing assembly20. For example, the stator52may extend around a first axis60and may not rotate about the first axis60. The stator52may include windings that may be electrically connected to the electrical power source50. The rotor54may extend around the first axis60and may be received inside the stator52. The rotor54may be rotatable about the first axis60with respect to the stator52. For example, the rotor54may be spaced apart from the stator52and may include magnets or ferromagnetic material that may facilitate the generation of electrical current. The rotor54may be operatively connected to the countershaft transmission28via the rotor shaft24and the drop gear set30as will be discussed in more detail below. The rotor shaft24may operatively connect the electric motor22to the drop gear set30. For example, the rotor shaft24may extend from the rotor54or may be operatively connected to the rotor54such that the rotor54and the rotor shaft24may be rotatable together about a first axis60. The rotor shaft24may be fixedly coupled to the rotor54at or proximate a first end of the rotor shaft24and may be fixedly coupled to a gear of the drop gear set30proximate a second end that may be disposed opposite the first end. The rotor shaft24may have a shorter length than the drive pinion26. The rotor shaft24may be rotatable about the first axis60. For instance, the rotor shaft24may be rotatably supported on the housing assembly20by one or more roller bearing assemblies. As an example, a roller bearing assembly may be located near opposing first and second ends the rotor shaft24. The roller bearing assembly may have any suitable configuration. For instance, the roller bearing assembly may include a plurality of rolling elements that may be disposed between an inner race and an outer race. The inner race may be mounted to the rotor shaft24and may extend around and may receive the rotor shaft24. The outer race may extend around the inner race and may be mounted to the housing assembly20. The drive pinion26may be at least partially received in the housing assembly20. The drive pinion26may be selectively connected to the electric motor22via the rotor shaft24, the drop gear set30, and the countershaft transmission28. As such, the drive pinion26may help operatively connect the electric motor22to components of the axle assembly10like the differential assembly32. The drive pinion26may extend along and may be rotatable about a drive pinion axis70. The drive pinion axis70may be disposed parallel or substantially parallel to the first axis60, may be spaced apart from the first axis60, may not be coaxially disposed with the first axis60, or combinations thereof. In at least one configuration, the drive pinion26may include a gear portion72and a shaft portion74. The gear portion72may be disposed at or near an end of the drive pinion26. The gear portion72may have a plurality of teeth that may mate or mesh with corresponding teeth on a ring gear of the differential assembly32as will be discussed in more detail below. As such, the drive pinion26may provide torque from the electric motor22to the ring gear. The shaft portion74may extend along and may be rotatable about the drive pinion axis70with the gear portion72. The shaft portion74may be operatively connected to the countershaft transmission28and may extend from the gear portion72in a direction that may extend away from the electric motor22and that may extend toward the countershaft transmission28. The shaft portion74may be integrally formed with the gear portion72or may be provided as a separate component that may be fixedly coupled to the gear portion72. The countershaft transmission28may operatively connect the electric motor22to the drive pinion26. The countershaft transmission28may be spaced apart from the electric motor22such that the differential assembly32may be positioned between the countershaft transmission28and the electric motor22. For instance, the differential assembly32may be positioned between the drop gear set30and the drive pinion26or between the drop gear set30and the countershaft transmission28. In at least one configuration, the countershaft transmission28may include a set of drive pinion gears80, a countershaft82, and a set of countershaft gears84. The set of drive pinion gears80may include a plurality of gears. In the configuration shown, the set of drive pinion gears80includes a first gear90, a second gear92, and a third gear94; however, it is to be understood that a greater or lesser number of gears may be provided. The members of the set of drive pinion gears80may be selectively coupled to the drive pinion26as shown inFIG.1, fixedly coupled to the drive pinion26as shown inFIG.5, or at least one drive pinion gear may be selectively coupled to the drive pinion26and at least one drive pinion gear may be fixedly coupled to the drive pinion26as shown inFIG.9. A member of the set of drive pinion gears80may be rotatable about the drive pinion axis70with the drive pinion26when that gear is coupled to the drive pinion26. Conversely, the drive pinion26may be rotatable about the drive pinion axis70with respect to a member of the set of drive pinion gears80that is decoupled from or not coupled to the drive pinion26. In the configurations shown inFIGS.1and9, a member of the set of drive pinion gears80may be selectively coupled to the drive pinion26in any suitable manner, such as with a clutch as will be discussed in more detail below. In configurations like that shown inFIG.1where all members of the set of drive pinion gears are selectively couplable to the drive pinion26, no more than one gear of the set of drive pinion gears80may be coupled to the drive pinion26at the same time when the drive pinion26rotates about the drive pinion axis70. Referring toFIG.1, the first gear90may receive the shaft portion74of the drive pinion26. For example, the first gear90may have a through hole through which the shaft portion74may extend. The first gear90may extend around the drive pinion axis70and the shaft portion74and may have a plurality of teeth that may be arranged around and may face away from the drive pinion axis70. The teeth of the first gear90may contact and may mate or mesh with teeth of a first countershaft gear that may be provided with the set of countershaft gears84as will be discussed in more detail below. In at least one configuration, the first gear90may be axially positioned along the drive pinion axis70such that the first gear90is positioned closer to the electric motor22and the differential assembly32than some or all of the other members of the set of drive pinion gears80. The second gear92may receive the shaft portion74of the drive pinion26. For example, the second gear92may have a through hole through which the shaft portion74may extend. The second gear92may extend around the drive pinion axis70and the shaft portion74and may have a plurality of teeth that may be arranged around and may face away from the drive pinion axis70. The teeth of the second gear92may contact and may mate or mesh with teeth of a second countershaft gear that may be provided with the set of countershaft gears84as will be discussed in more detail below. The second gear92may have a different diameter than the first gear90and the third gear94. For example, the second gear92may have a larger diameter than the first gear90and a smaller diameter than the third gear94. In at least one configuration, the second gear92may be axially positioned along the drive pinion axis70between the first gear90and the third gear94. The third gear94may receive the shaft portion74of the drive pinion26. For example, the third gear94may have a through hole through which the shaft portion74may extend. The third gear94may extend around the drive pinion axis70and the shaft portion74and may have a plurality of teeth that may be arranged around and may face away from the drive pinion axis70. The teeth of the third gear94may contact and may mate or mesh with teeth of a third countershaft gear that may be provided with the set of countershaft gears84as will be discussed in more detail below. The third gear94may have a different diameter than the first gear90and the second gear92. For example, the third gear94may have a larger diameter than the first gear90and the second gear92. In at least one configuration, the third gear94may be axially positioned along the drive pinion axis70further from the electric motor22and the differential assembly32than the first gear90and the second gear92. In the configuration shown inFIG.1, a bearing such as a roller bearing may optionally be provided that may receive the shaft portion74and may rotatably support a corresponding gear. For instance, a bearing may be received between the first gear90and the shaft portion74, between the second gear92and the shaft portion74, between the third gear94and the shaft portion74, or combinations thereof to facilitate rotation of the drive pinion26with respect to a gear when the gear is not coupled to the drive pinion26. The countershaft82may be rotatable about a countershaft axis100. The countershaft axis100may be disposed parallel or substantially parallel to the first axis60, the drive pinion axis70, or both. The countershaft axis100may be offset from and may not be coaxially disposed with the first axis60, the drive pinion axis70, or both. The countershaft82may be rotatably supported on the housing assembly20by one or more roller bearing assemblies. As an example, a roller bearing assembly may be located near opposing first and second ends the countershaft82. The countershaft82may support the set of countershaft gears84. The set of countershaft gears84may be at least partially received in the housing assembly20. The set of countershaft gears84may include a plurality of gears. In the configurations shown inFIGS.1,5and9, the set of countershaft gears84may include a first countershaft gear110or110′, a second countershaft gear112or112′, and a third countershaft gear114or114′; however, it is contemplated that a greater number of gears or a lesser number of countershaft gears may be provided. The set of countershaft gears84may be the only countershaft gears provided and thus a second countershaft or second countershaft subassembly may not be provided with the axle assembly. Members of the set of countershaft gears84may be rotatable about the countershaft axis100with the countershaft82. The configuration shown inFIG.1will be described first below and the configurations shown inFIGS.5and9will be described later in the text. Referring toFIG.1, the first countershaft gear110may be fixedly disposed on the countershaft82or fixedly mounted to the countershaft82. As such, the first countershaft gear110may rotate about the countershaft axis100with the countershaft82. For example, the first countershaft gear110may have a hole that may receive the countershaft82and may be fixedly coupled to the countershaft82. The first countershaft gear110may extend around the countershaft axis100and may have a plurality of teeth that may be arranged around and may face away from the countershaft axis100. The teeth of the first countershaft gear110may contact and may mate or mesh with the teeth of the first gear90. In at least one configuration, the first countershaft gear110may be axially positioned along the countershaft axis100closer to the electric motor22and the differential assembly32than the second countershaft gear112and the third countershaft gear114. The second countershaft gear112inFIG.1may be fixedly disposed on the countershaft82or fixedly mounted to the countershaft82. As such, the second countershaft gear112may rotate about the countershaft axis100with the countershaft82. For example, the second countershaft gear112may have a hole that may receive the countershaft82and may be fixedly coupled to the countershaft82. The second countershaft gear112may extend around the countershaft axis100and may have a plurality of teeth that may be arranged around and may face away from the countershaft axis100. The teeth of the second countershaft gear112may contact and may mate or mesh with the teeth of the second gear92. The second countershaft gear112may have a different diameter than the first countershaft gear110and the third countershaft gear114. In at least one configuration, the second countershaft gear112may be axially positioned along the countershaft axis100between the first countershaft gear110and the third countershaft gear114. The third countershaft gear114inFIG.1may be fixedly disposed on the countershaft82or fixedly mounted to the countershaft82. As such, the third countershaft gear114may rotate about the countershaft axis100with the countershaft82. For example, the third countershaft gear114may have a hole that may receive the countershaft82and may be fixedly coupled to the countershaft82. The third countershaft gear114may extend around the countershaft axis100and may have a plurality of teeth that may be arranged around and may face away from the countershaft axis100. The teeth of the third countershaft gear114may contact and may mate or mesh with the teeth of the third gear94. The third countershaft gear114may have a different diameter than the first countershaft gear110and the second countershaft gear112. In at least one configuration, the third countershaft gear114may be axially positioned along the countershaft axis100further away from the electric motor22and the differential assembly32than the first countershaft gear110and the second countershaft gear112. The first gear90and the first countershaft gear110may provide a different gear ratio than the second gear92and the second countershaft gear112and may provide a different gear ratio than the third gear94and the third countershaft gear114. As a non-limiting example, the first gear90and the first countershaft gear110may provide a gear ratio of 1:1 or less, the second gear92and the second countershaft gear112may provide a gear ratio from 1:1 to 2:1, and the third gear94and the third countershaft gear114may provide a gear ratio of 2:1 or more. For instance, the first countershaft gear110may have a larger diameter than the first gear90, the second countershaft gear112, and the third countershaft gear114. The second countershaft gear112may have a larger diameter than the third countershaft gear114and a smaller diameter or the same diameter as the second gear92. The third countershaft gear114may have a smaller diameter than the third gear94. It is also contemplated that other gear configurations may be provided. As one example, the first gear90may have a larger diameter than the second gear92and the third gear94. As another example, gears or gear pairings may be arranged in different sequences along their respective axes. As another example, multiple meshing gear pairings or no gear pairings may provide “overdrive” gear ratios of less than 1:1. As another example, multiple meshing gear pairings may provide gear ratios of greater than 1:1. As such, gear ratios may be provided that are greater than 1:1, less than 1:1, equal (i.e., 1:1), or combinations thereof. The teeth of the countershaft gears may be of any suitable type. As a non-limiting example, the meshing teeth of the members of the set of drive pinion gears80and the members of the set of countershaft gears84may have a helical configuration. The drop gear set30may be at least partially received in the housing assembly20. In addition, the drop gear set may be disposed on the same side of the differential assembly32as the electric motor22. For instance, the drop gear set30may be positioned between the differential assembly32and the electric motor22. The drop gear set30may include a plurality of gears. In the configurations shown inFIGS.1,5and9, the drop gear set30may include a first drop gear120and a second drop gear122; however, it is contemplated that a greater number of gears may be provided. Members of the drop gear set30may be rotatable about different axes and may have the same diameters or different diameters. The first drop gear120may be fixedly disposed on the rotor shaft24or fixedly mounted to the rotor shaft24. As such, the first drop gear120may rotate about the first axis60with the rotor shaft24. For example, the first drop gear120may have a hole that may receive the rotor shaft24and may be fixedly coupled to the rotor shaft24. The first drop gear120may extend around the first axis60and may have a plurality of teeth that may be arranged around and may face away from the first axis60. The second drop gear122may be fixedly disposed on the countershaft82or fixedly mounted to the countershaft82. As such, the second drop gear122may rotate about the countershaft axis100with the countershaft82. For example, the second drop gear122may have a hole that may receive the countershaft82and may be fixedly coupled to the countershaft82. The second drop gear122may extend around the countershaft axis100and may have a plurality of teeth that may be arranged around and may face away from the countershaft axis100. The teeth of the first drop gear120may contact and may mate or mesh with the teeth of the second drop gear122. The first drop gear120and the second drop gear122may provide gear reduction when provided with different diameters. For example, the first drop gear120may have a smaller diameter than the second drop gear122and may provide a gear reduction ratio greater than 1:1. As a nonlimiting example, the first drop gear120and the second drop gear122may cooperate to provide a 2:1 gear reduction ratio. Such gear reduction may decrease the rotational speed of the countershaft82with respect to the rotational speed of the rotor shaft24and may increase the torque provided from the electric motor22to the countershaft transmission28. The differential assembly32may be at least partially received in the center portion42of the housing assembly20. The differential assembly32may transmit torque to the vehicle traction wheel assemblies and permit the traction wheel assemblies to rotate at different velocities. For example, the differential assembly32may be operatively connected to the axle shafts34and may permit the axle shafts34to rotate at different rotational speeds about a second axis130. The second axis130may be disposed perpendicular or substantially perpendicular to the first axis60, the drive pinion axis70, the countershaft axis100, or combinations thereof. Moreover, the electric motor22may be positioned on an opposite side of the second axis130from the drive pinion26, the countershaft transmission28, or both. In at least one configuration, the differential assembly32may include a differential case140, a ring gear142, a first differential gear144, a second differential gear146, and at least one pinion gear148. The differential case140may be configured to receive components of the differential assembly32. In addition, the differential case140may be rotatable about the second axis130. For example, the differential case140may be rotatably supported by a pair of roller bearing assemblies, which in turn may be mounted to a portion of the housing assembly20, such as a differential carrier. The differential case140may at least partially define a cavity that may at least partially receive the first differential gear144, second differential gear146, and pinion gear(s)148. The ring gear142may be fixedly disposed on the differential case140or fixedly mounted to the differential case140. As such, the ring gear142may rotate about the second axis130with the differential case140. The ring gear142may extend around the second axis130and may have a set of ring gear teeth that may contact and mate or mesh with teeth of the gear portion72of the drive pinion26. As such, torque may be transmitted between the countershaft transmission28and the differential assembly32via the meshing teeth of the drive pinion26and the ring gear142. The first differential gear144may be disposed in the differential case140. In addition, the first differential gear144may be coupled to an axle shaft34such that the axle shaft34and the first differential gear144are rotatable together about the second axis130. The first differential gear144may be coupled to the axle shaft34in any suitable manner. For instance, the first differential gear144may have a hole that may receive the axle shaft34and the axle shaft34and first differential gear144may be coupled with mating splines, a weld, fastener, or the like. The first differential gear144may also have gear portion that may have a set of teeth that may be arranged around the second axis130and that may mate or mesh with teeth on one or more pinion gears148. The second differential gear146may be disposed in the differential case140. The second differential gear146may be spaced apart from the first differential gear144and may have a similar or identical configuration as the first differential gear144. As such, the second differential gear146may be coupled to another axle shaft34in any suitable manner such that the axle shaft34and the second differential gear146are rotatable together about the second axis130. The second differential gear146may also have gear portion that may have a set of teeth that may be arranged around the second axis130and that may mate or mesh with teeth on one or more pinion gears148. At least one pinion gear148may be received in the differential case140. A pinion gear148may include a set of teeth that mate or mesh with teeth on the first differential gear144and teeth on the second differential gear146. In addition, a pinion gear148may be rotatable with respect to the differential case140or rotatably mounted on the differential case140. For instance, a pinion gear148may receive and may be rotatable about a shaft or a spider that may extend from or may be mounted to the differential case140such that the shaft or spider is rotatable about the second axis130with the differential case140. The axle shafts34may transmit torque from the differential assembly32to corresponding traction wheel assemblies. For example, two axle shafts34may be provided such that each axle shaft34extends into or through a different arm portion44of housing assembly20. The axle shafts34may extend along and may be rotatable about the second axis130. Each axle shaft34may have a first end and a second end. The first end may be operatively connected to the differential assembly32. The second end may be disposed opposite the first end and may be operatively connected to a corresponding wheel end assembly that may have a wheel hub that may support a wheel14. Optionally, gear reduction may be provided between an axle shaft34and a wheel14, such as with a gear reduction unit150having any suitable configuration. For instance, the gear reduction unit150may be configured with bevel gears or a planetary gear set in a manner known by those skilled in the art. The control system36may control operation of the axle assembly10. The control system36may include one or more electronic controllers, such as a microprocessor-based controller, that may monitor and/or control operation of various components of the axle assembly10, such as the electric motor22and the electrical power source50. In addition, the control system36may control coupling and decoupling of the gears. InFIG.1, the control system36may control coupling and decoupling of the set of drive pinion gears80to and from the drive pinion26. InFIG.5, the control system36may control coupling and decoupling of the set of countershaft gears84to and from the countershaft82. InFIG.9, the control system36may control coupling and decoupling of at least one member of the set of drive pinion gears80to and from the drive pinion26and coupling and decoupling of at least one member of the set of countershaft gears84to and from the countershaft82. For instance, the control system36may control operation of one or more clutches that may couple/decouple at least one gear from a corresponding shaft. A clutch may have any suitable configuration. The clutch may be configured as a disc clutch that may include friction discs that may be selectively engaged to couple a gear to a corresponding shaft. Alternatively, the clutch may be configured as a dog clutch or clutch collar that may receive, rotate with, and slide along a corresponding shaft to selectively couple and decouple one or more members of the set of drive pinion gears80to and from the drive pinion26, one or more members of the set of countershaft gears84to and from the countershaft82, or combinations thereof. For example, a clutch that is configured as a dog clutch or a clutch collar may have a through hole that may receive the shaft portion74of the drive pinion26and may rotate about the drive pinion axis70with the shaft portion74, or may have a through hole that may receive the countershaft82and may rotate about the countershaft axis100with the countershaft82. For instance, the clutch and the shaft it receives may have mating splines that inhibit rotation of the clutch with respect to the shaft while allowing the clutch to slide in an axial direction along an axis (e.g., the drive pinion axis70or the countershaft axis100) with respect to the shaft to engage or disengage a gear, such as member of the set of drive pinion gears80or a member of the set of countershaft gears84. Such a clutch may have a tooth or teeth that may be configured to selectively mate or mesh with corresponding teeth on a member of the set of drive pinion gears80or a member of the set of countershaft gears84to couple the gear to the drive pinion26or the countershaft82, respectively, such that the gear is rotatable about the drive pinion axis70with the drive pinion26or is rotatable about the countershaft axis100with the countershaft82. The tooth or teeth of the clutch may be configured as a face gear that may be disposed along a lateral side of the clutch or may be configured like a spline and may be received inside a hole of a member of the set of drive pinion gears80or a member of the set of countershaft gears84. Clutches will primarily be described below as having a dog clutch or clutch collar configuration; however, it is to be understood that a clutch may have a different configuration and may not be configured as a dog clutch or a clutch collar, that a different number of clutches may be provided, and that clutches may be associated with a single member of the set of drive pinion gears80or a single member of the set of countershaft gears84rather than multiple gears or vice versa. In at least one configuration, a first clutch160and a second clutch162may be provided. InFIG.1, the first clutch160may be axially positioned along the drive pinion axis70between the first gear90and the second gear92while the second clutch162may be axially positioned along the drive pinion axis70between the second gear92and the third gear94. InFIG.5, the first clutch160may be axially positioned along the countershaft axis100between the first countershaft gear110′ and the second countershaft gear112′ while the second clutch162may be axially positioned along the countershaft axis100between the second countershaft gear112′ and the third countershaft gear114′. InFIG.9, the first clutch160may be axially positioned along the countershaft axis100between the first countershaft gear110′ and the second countershaft gear112′ while the second clutch162may be axially positioned along the drive pinion axis70between the second gear92and the third gear94. The first clutch160and the second clutch162may be configured to selectively couple a single gear or multiple gears to the drive pinion26as will be discussed in more detail below. It is contemplated that a single actuator may be provided to actuate multiple clutches, like the first clutch140and the second clutch142or that different actuators may actuate different clutches. The first clutch160may be operatively connected to a first actuator170that may be configured to move the first clutch160along an axis. For example, a linkage172, such as a shift fork, may operatively connect the first clutch160to the first actuator170. The first actuator170may be of any suitable type. For example, the first actuator170may be an electrical, electromechanical, pneumatic, or hydraulic actuator. In at least one configuration, such as when the first clutch160is a clutch collar or dog clutch, the first actuator170may move the first clutch160along an axis and may execute a shift when the rotational speed of the first clutch160and a corresponding gear are sufficiently synchronized to complete a shift so that the teeth of the first clutch160may mesh with teeth on a gear or so that the teeth of the first clutch160gear may disengage from teeth on a gear. The control system36may monitor and/or control operation of the first actuator170. The second clutch162may be operatively connected to a second actuator180that may be configured to move the second clutch162along an axis. It is also contemplated that a single actuator may be provided to actuate multiple clutches, like the first clutch140and the second clutch142. For example, a linkage182, such as a shift fork, may operatively connect the second clutch162to the second actuator180. The second actuator180may be of any suitable type. For example, the second actuator180may be an electrical, electromechanical, pneumatic, or hydraulic actuator. In at least one configuration, such as when the second clutch162is a clutch collar or dog clutch, the second actuator180may move the second clutch162along an axis and may execute a shift when the rotational speed of the second clutch162and a corresponding gear are sufficiently synchronized to complete a shift so that the teeth of the second clutch162may mesh with teeth on a gear or so that the teeth of the second clutch162gear may disengage from teeth on a gear. The control system36may monitor and/or control operation of the second actuator180. Sufficient synchronization to permit shifting or movement of a clutch, like the first clutch160or the second clutch162, may be attained using a gear synchronizer, by controlling the rotational speed of the rotor54, or combinations thereof. Such synchronization components or control actions may be omitted with different clutch configurations, such as a clutch that is a disc clutch. Referring toFIGS.1-4, examples of different clutch positions are shown. The control system36may actuate the first clutch160and the second clutch162to a desired position based on an operator input or an automated shift control routine. The rotor shaft24may rotate about the first axis60and the countershaft82and set of countershaft gears84may rotate about the countershaft axis100when the rotor54rotates about the first axis60in the clutch positions shown in these figures. Referring toFIG.1, the first clutch160and the second clutch162are shown in neutral positions. The first clutch160may not couple a gear of the set of drive pinion gears80to the drive pinion26when the first clutch160is in the neutral position. For instance, the first clutch160may not couple the first gear90or the second gear92to the drive pinion26when the first clutch160is in the neutral position. Likewise, the second clutch162may not couple a gear of the set of drive pinion gears80to the drive pinion26when the second clutch162is in the neutral position. For instance, the second clutch162may not couple the second gear92or the third gear94to the drive pinion26when the second clutch162is in the neutral position. The drive pinion26may be free to rotate about the drive pinion axis70with respect to at least one member of the set of drive pinion gears80when a clutch is in the neutral position and may be free to rotate about the drive pinion axis70with respect to all members of the set of drive pinion gears80when all clutches are in their respective neutral positions. Thus, torque is not transmitted between the electric motor22and the drive pinion26when the first clutch160and the second clutch162are in their respective neutral positions. As an overview of the configurations shown inFIGS.2-4, torque may be transmitted between the electric motor22and the drive pinion26when one member of the set of drive pinion gears80is coupled to the drive pinion26by a corresponding clutch and the other members of the set of drive pinion gears80are decoupled from the drive pinion26such that the drive pinion26is free to rotate about the drive pinion axis70with respect to a decoupled drive pinion gear. The straight arrowed lines inFIGS.2-4that are not shown inFIG.1depict the torque transmission path from the electric motor22to the drive pinion26, and hence to the differential assembly32; however, it is to be understood that the torque transmission path may be reversed in each of these figures and torque may be transmitted from the differential assembly32to the drive pinion26and then to the electric motor22via the countershaft transmission28, the drop gear set30, and the rotor shaft24. Referring toFIG.2, the first clutch160is shown in a first position and the second clutch162is shown in the neutral position. The first clutch160may be moved to the first position by the first actuator170. In the first position, the first clutch160may couple the first gear90to the drive pinion26such that the first gear90is rotatable about the drive pinion axis70with the drive pinion26. Accordingly, torque may be transmitted to or from the drive pinion26via the first countershaft gear110, the first clutch160, and the first gear90. The second gear92and the third gear94are not coupled to the drive pinion26by a clutch. Thus, the second countershaft gear112and the third countershaft gear114may rotate the second gear92and the third gear94, respectively, about the drive pinion axis70, but torque may not be transmitted to or from the drive pinion26via the second gear92or the third gear94since these gears are decoupled from the drive pinion26. Therefore, torque may be transmitted between the electric motor22and the drive pinion26via the first gear90when the first clutch160couples the first gear90to the drive pinion26such that the first gear90is rotatable about the drive pinion axis70with the drive pinion26. A first gear ratio is provided when the first gear90is coupled to the drive pinion26. Referring toFIGS.3A and3B, two different examples are shown that illustrate the transmission of torque via the second gear92. InFIGS.3A and3B, a second gear ratio is provided when the second gear92is coupled to the drive pinion26. The second gear ratio may differ from the first gear ratio. InFIG.3A, the first clutch160is shown in a second position and the second clutch162is shown in the neutral position. The first clutch160may be moved to the second position by the first actuator170. In the second position, the first clutch160couples the second gear92to the drive pinion26such that the second gear92is rotatable about the drive pinion axis70with the drive pinion26. Accordingly, torque may be transmitted to or from the drive pinion26via the second countershaft gear112, the first clutch160, and the second gear92. The first gear90and the third gear94are not coupled to the drive pinion26via the first clutch160or the second clutch162. Thus, the first countershaft gear110and the third countershaft gear114may rotate the first gear90and the third gear94, respectively, about the drive pinion axis70, but torque may not be transmitted to or from the drive pinion26via the first gear90or the third gear94since these gears are decoupled from the drive pinion26. Therefore, torque is transmitted between the electric motor22and the drive pinion26via the second gear92when the first clutch160does not couple the first gear90to the drive pinion26and the first clutch160couples the second gear92to the drive pinion26such that the second gear92is rotatable about the drive pinion axis70with the drive pinion26. InFIG.3B, the second clutch162is shown in a first position and the first clutch160is shown in the neutral position. The second clutch162may be moved to the first position by the second actuator180. In the first position, the second clutch162couples the second gear92to the drive pinion26such that the second gear92is rotatable about the drive pinion axis70with the drive pinion26. Accordingly, torque may be transmitted to or from the drive pinion26via the second countershaft gear112, the second clutch162, and the second gear92. The first gear90and the third gear94are not coupled to the drive pinion26via the first clutch160or the second clutch162. Thus, the first countershaft gear110and the third countershaft gear114may rotate the first gear90and the third gear94, respectively, about the drive pinion axis70, but torque may not be transmitted to or from the drive pinion26via the first gear90or the third gear94since these gears are decoupled from the drive pinion26. Therefore, torque is transmitted between the electric motor22and the drive pinion26via the second gear92when the first clutch160does not couple the first gear90to the drive pinion26and the second clutch162couples the second gear92to the drive pinion26such that the second gear92is rotatable about the drive pinion axis70with the drive pinion26. InFIG.4, the second clutch162is shown in a second position and the first clutch160is shown in the neutral position. The second clutch162may be moved to the second position by the second actuator180. In the second position, the second clutch162couples the third gear94to the drive pinion26such that the third gear94is rotatable about the drive pinion axis70with the drive pinion26. Accordingly, torque may be transmitted to or from the drive pinion26via the third countershaft gear114, the second clutch162, and the third gear94. The first gear90and the second gear92are not coupled to the drive pinion26via the first clutch160or the second clutch162. Thus, the first countershaft gear110and the second countershaft gear112may rotate the first gear90and the second gear92, respectively, about the drive pinion axis70, but torque may not be transmitted to or from the drive pinion26via the first gear90or the second gear92since these gears are decoupled from the drive pinion26. Therefore, torque is transmitted between the electric motor22and the drive pinion26via the third gear94when the first clutch160does not couple the first gear90or the second gear92to the drive pinion26and the second clutch162couples the third gear94to the drive pinion26such that the third gear94is rotatable about the drive pinion axis70with the drive pinion26. A third gear ratio is provided when the third gear94is coupled to the drive pinion26. The third gear ratio may differ from the first gear ratio and the second gear ratio. Referring toFIG.5, an axle assembly10′ is shown that is similar to the configuration shown inFIG.1. The configuration inFIG.5differs from the configuration shown inFIG.1in that the members of the set of drive pinion gears80are fixedly coupled to the drive pinion26and the members of the set of countershaft gears84are selectively couplable to the countershaft82rather than being fixedly coupled to the countershaft82. The set of drive pinion gears80is illustrated with a first gear90′, a second gear92′, and a third gear94′. The first gear90′, second gear92′, and the third gear94′ may be the same as the first gear90, the second gear92, and the third gear94, respectively, except that the first gear90′, second gear92′, and third gear94′ may be fixed to the drive pinion26and may not be configured with features that facilitate direct coupling with a clutch. Conversely, the first countershaft gear110′, the second countershaft gear112′, and the third countershaft gear114′ may each have a through hole that may receive the countershaft82. The first clutch160and the second clutch162may receive the countershaft82and may be configured to selectively couple at least one of the first countershaft gear110′, the second countershaft gear112′, and the third countershaft gear114′ to the countershaft82such that a coupled gear may rotate about the countershaft axis100with the countershaft82as previously discussed. The first countershaft gear110′ may extend around the countershaft axis100and may have a plurality of teeth that may be arranged around and may face away from the countershaft axis100. The teeth of the first countershaft gear110′ may contact and may mate or mesh with the teeth of the first gear90′. In at least one configuration, the first countershaft gear110′ may be axially positioned along the countershaft axis100closer to the electric motor22and the differential assembly32than the second countershaft gear112′ and the third countershaft gear114′. The second countershaft gear112′ may extend around the countershaft axis100and may have a plurality of teeth that may be arranged around and may face away from the countershaft axis100. The teeth of the second countershaft gear112′ may contact and may mate or mesh with the teeth of the second gear92′. The second countershaft gear112′ may have a different diameter than the first countershaft gear110′ and the third countershaft gear114′. In at least one configuration, the second countershaft gear112′ may be axially positioned along the countershaft axis100between the first countershaft gear110′ and the third countershaft gear114′. The third countershaft gear114′ may extend around the countershaft axis100and may have a plurality of teeth that may be arranged around and may face away from the countershaft axis100. The teeth of the third countershaft gear114′ may contact and may mate or mesh with the teeth of the third gear94′. The third countershaft gear114′ may have a different diameter than the first countershaft gear110′ and the second countershaft gear112′. In at least one configuration, the third countershaft gear114′ may be axially positioned along the countershaft axis100further away from the electric motor22and the differential assembly32than the first countershaft gear110′ and the second countershaft gear112′. InFIG.5, the first clutch160and the second clutch162are shown in neutral positions. The first clutch160may not couple a gear of the set of countershaft gears84to the countershaft82when the first clutch160is in the neutral position. For instance, the first clutch160may not couple the first countershaft gear110′ or the second countershaft gear112′ to the countershaft82when the first clutch160is in the neutral position. Likewise, the second clutch162may not couple a gear of the set of countershaft gears84to the countershaft82when the second clutch162is in the neutral position. For instance, the second clutch162may not couple the second countershaft gear112′ or the third countershaft gear114′ to the countershaft82when the second clutch162is in the neutral position. The countershaft82may be free to rotate about the countershaft axis100with respect to at least one member of the set of countershaft gears84when a clutch is in the neutral position and may be free to rotate about the countershaft axis100with respect to all members of the set of countershaft gears84when all clutches are in their respective neutral positions. Thus, torque is not transmitted between the electric motor22and the drive pinion26when the first clutch160and the second clutch162are in their respective neutral positions. Referring toFIG.6, the first clutch160is shown in a first position and the second clutch162is shown in the neutral position. The first clutch160may be moved to the first position by the first actuator170. In the first position, the first clutch160may couple the first countershaft gear110′ to the countershaft82such that the first countershaft gear110′ is rotatable about the countershaft axis100with the countershaft82. Accordingly, torque may be transmitted to or from the countershaft82via the first countershaft gear110′, the first clutch160, and the first gear90′. The second countershaft gear112′ and the third countershaft gear114′ are not coupled to the countershaft82by a clutch. Thus, the countershaft82may be free to rotate about the countershaft axis100with respect to the second countershaft gear112′ and the third countershaft gear114′, but torque may not be transmitted to or from the drive pinion26via the second countershaft gear112′ or the third countershaft gear114′ since these gears are decoupled from the countershaft82. A first gear ratio is provided when the first countershaft gear110′ is coupled to the drive pinion26. Referring toFIGS.7A and7B, two different examples are shown that illustrate the transmission of torque via the second countershaft gear112′. InFIGS.7A and7B, a second gear ratio is provided when the second countershaft gear112′ is coupled to the countershaft82. The second gear ratio may differ from the first gear ratio. InFIG.7A, the first clutch160is shown in a second position and the second clutch162is shown in the neutral position. The first clutch160may be moved to the second position by the first actuator170. In the second position, the first clutch160couples the second countershaft gear112′ to the countershaft82such that the second countershaft gear112′ is rotatable about the countershaft axis100with the countershaft82. Accordingly, torque may be transmitted to or from the countershaft82via the second countershaft gear112′, the first clutch160, and the second gear92′. The first countershaft gear110′ and the third countershaft gear114′ are not coupled to the countershaft82via the first clutch160or the second clutch162. Thus, the countershaft82may be free to rotate about the countershaft axis100with respect to the first countershaft gear110′ and the third countershaft gear114′, but torque may not be transmitted to or from the drive pinion26via the first countershaft gear110′ or the third countershaft gear112′ since these gears are decoupled from the countershaft82. InFIG.7B, the second clutch162is shown in a first position and the first clutch160is shown in the neutral position. The second clutch162may be moved to the first position by the second actuator180. In the first position, the second clutch162couples the second countershaft gear112′ to the countershaft82such that the second countershaft gear112′ is rotatable about the countershaft axis100with the countershaft82. Accordingly, torque may be transmitted to or from the countershaft82via the second countershaft gear112′, the second clutch162, and the second gear92′. The first countershaft gear110′ and the third countershaft gear114′ are not coupled to the countershaft82via the first clutch160or the second clutch162. Thus, the countershaft82may be free to rotate about the countershaft axis100with respect to the first countershaft gear110′ and the third countershaft gear114′, but torque may not be transmitted to or from the drive pinion26via the first countershaft gear110′ or the third countershaft gear112′ since these gears are decoupled from the countershaft82. InFIG.8, the second clutch162is shown in a second position and the first clutch160is shown in the neutral position. The second clutch162may be moved to the second position by the second actuator180. In the second position, the second clutch162couples the third countershaft gear114′ to the countershaft82such that the third countershaft gear114′ is rotatable about the countershaft axis100with the countershaft82. Accordingly, torque may be transmitted to or from the countershaft82via the third countershaft gear114′, the second clutch162, and the third gear94′. The first countershaft gear110′ and the second countershaft gear112′ are not coupled to the countershaft82via the first clutch160or the second clutch162. Thus, the countershaft82may be free to rotate about the countershaft axis100with respect to the first countershaft gear110′ and the second countershaft gear112′, but torque may not be transmitted to or from the drive pinion26via the first countershaft gear110′ or the second countershaft gear112′ since these gears are decoupled from the countershaft82. A third gear ratio is provided when the third countershaft gear114′ is coupled to the drive pinion26. The third gear ratio may differ from the first gear ratio and the second gear ratio. Referring toFIG.9, an axle assembly10″ is shown that is a combination of the configurations shown inFIGS.1and5. InFIG.9, at least one member of the set of drive pinion gears80may be fixedly coupled to the drive pinion26and at least one member of the set of drive pinion gears80may be selectively coupled to the drive pinion26. Similarly, at least one member of the set of countershaft gears84may be fixedly coupled to the countershaft82and at least one member of the set of countershaft gears84may be selectively coupled to the countershaft82. In the configuration shown, the first gear90′ and the second gear92′ are fixedly coupled to the drive pinion26and the first countershaft gear110′ and the second countershaft gear112′ are selectively couplable to the countershaft82like the configuration shown inFIG.5while the third gear94is selectively couplable to the drive pinion26and the third countershaft gear114is fixedly coupled to the countershaft82like the configuration shown inFIG.1. InFIG.9, the first clutch160and the second clutch162are shown in neutral positions. The first clutch160may not couple a gear of the set of countershaft gears84to the countershaft82when the first clutch160is in the neutral position. For instance, the first clutch160may not couple the first countershaft gear110′ or the second countershaft gear112′ to the countershaft82when the first clutch160is in the neutral position. Likewise, the second clutch162may not couple a gear of the set of drive pinion gears80to the drive pinion26when the second clutch162is in the neutral position. For instance, the second clutch162may not couple the third gear94to the drive pinion26when the second clutch162is in the neutral position. The countershaft82may be free to rotate about the countershaft axis100with respect to the first countershaft gear110′ and the second countershaft gear112′ when the first clutch160is in the neutral position but the third gear94may be rotatable with the countershaft82about the countershaft axis100. The drive pinion26may be free to rotate about the drive pinion axis70with respect to the third gear94when the second clutch162is in the neutral position but the first gear90′ and the second gear92′ may be rotatable with the drive pinion26about the drive pinion axis70. Thus, torque is not transmitted between the electric motor22and the drive pinion26when the first clutch160and the second clutch162are in their respective neutral positions. Referring toFIG.10, the first clutch160is shown in a first position and the second clutch162is shown in the neutral position. The first clutch160may be moved to the first position by the first actuator170. In the first position, the first clutch160may couple the first countershaft gear110′ to the countershaft82such that the first countershaft gear110′ is rotatable about the countershaft axis100with the countershaft82. Accordingly, torque may be transmitted to or from the countershaft82via the first countershaft gear110′, the first clutch160, and the first gear90′. The second countershaft gear112′ and the third gear94are not coupled to the countershaft82or the drive pinion26by a clutch. Thus, the countershaft82may be free to rotate about the countershaft axis100with respect to the second countershaft gear112′ and the drive pinion26may be free to rotate about the drive pinion axis70with respect to the third gear94, but torque may not be transmitted to or from the drive pinion26via the second countershaft gear112′ or the third gear94since these gears are decoupled from the countershaft82and the drive pinion26, respectively. A first gear ratio is provided when the first countershaft gear110′ is coupled to the countershaft82. InFIG.11, the first clutch160is shown in a second position and the second clutch162is shown in the neutral position. The first clutch160may be moved to the second position by the first actuator170. In the second position, the first clutch160couples the second countershaft gear112′ to the countershaft82such that the second countershaft gear112′ is rotatable about the countershaft axis100with the countershaft82. Accordingly, torque may be transmitted to or from the countershaft82via the second countershaft gear112′, the first clutch160, and the second gear92′. The first countershaft gear110′ and the third gear94are not coupled to the countershaft82or the drive pinion26via a clutch. Thus, the countershaft82may be free to rotate about the countershaft axis100with respect to the first countershaft gear110′ and the drive pinion26may be free to rotate about the drive pinion axis70with respect to the third gear94, but torque may not be transmitted to or from the drive pinion26via the first countershaft gear110′ or the third gear94since these gears are decoupled from the countershaft82and the drive pinion26, respectively. InFIG.12, the second clutch162is shown in a second position and the first clutch160is shown in the neutral position. The second clutch162may be moved to the second position by the second actuator180. In the second position, the second clutch162couples the third gear94to the drive pinion26such that the third gear94is rotatable about the drive pinion axis70with the drive pinion26. Accordingly, torque may be transmitted to or from the countershaft82via the third countershaft gear114, the second clutch162, and the third gear94. The first countershaft gear110′ and the second countershaft gear112′ are not coupled to the countershaft82via a clutch. Thus, the countershaft82may be free to rotate about the countershaft axis100with respect to the first countershaft gear110′ and the second countershaft gear112′, but torque may not be transmitted to the drive pinion26via the first countershaft gear110′ or the second countershaft gear112′ since these gears are decoupled from the countershaft82. A third gear ratio is provided when the third gear94is coupled to the drive pinion26. The third gear ratio may differ from the first gear ratio and the second gear ratio. The configuration shown inFIGS.9-12may allow one or more gears of the countershaft transmission28to rotate at lower speeds than the configuration shown inFIGS.5-10for a given rotor rotational speed, which may help reduce bearing wear, bearing lubrication requirements, heat generated by a bearing, or combinations thereof. For instance, the configuration shown inFIGS.9-12may reduce the rotational speed of the third countershaft gear114as compared to the rotational speed of the third countershaft gear114′ inFIGS.5-7. InFIGS.9-12, the third countershaft gear114rotates at the same speed as the countershaft82. InFIGS.5-8the third countershaft gear114′ may be driven at a higher rotational speed than the countershaft82when the third countershaft gear114′ is decoupled from the countershaft82and either the first countershaft gear110′ or the second countershaft gear112′ is coupled to the countershaft82. For example, the third gear94′ may backdrive the third countershaft gear114′ at a higher rotational speed than the countershaft82when the third gear94′ has a larger diameter than the third countershaft gear114′. As a nonlimiting example, the third countershaft gear114′ inFIG.6may rotate at 11,000 rpm while the third countershaft gear114inFIG.10may rotate at 5,500 rpm when the rotor54rotates at a given speed. The axle assembly configurations discussed above may provide an axle assembly configuration in which the electric motor and countershaft transmission are arranged on opposite sides of a differential assembly and a center portion of an axle housing. Such a configuration may help thermally separate the electric motor and heat generated by the fast-spinning rotor roller bearings (which may rotate at speeds greater than 50,000 rpm) from other components of the axle assembly, such as the countershaft transmission and lubricant of the axle assembly. This thermal separation may improve thermal management of the axle assembly and may reduce lubricant heating, which may help improve lubricant life. In addition, such an arrangement may provide better weight distribution by locating the center of mass of the axle assembly closer to the axle shafts as compared to a configuration in which the electric motor and countershaft transmission extend from the same side of the housing assembly. As a result, the “standout” or distance the housing assembly extends from the axle shafts may be reduced and housing structural integrity may be improved as compared to a configuration in which the electric motor and countershaft transmission extend from the same side of the housing assembly. The axle assembly may provide multiple gear ratios with a single set of countershaft gears, which may provide gear reduction with fewer gears as compared to a dual countershaft arrangement having two sets of countershaft gears arranged on separate countershafts, which may reduce cost and weight and may help reduce the size of the axle assembly. The configurations described above may also allow a modular countershaft transmission to be provided with multiple gears mounted to a corresponding countershaft without independent bearings for associated gears. While exemplary embodiments are described above, it is not intended that these embodiments describe all possible forms of the invention. Rather, the words used in the specification are words of description rather than limitation, and it is understood that various changes may be made without departing from the spirit and scope of the invention. Additionally, the features of various implementing embodiments may be combined to form further embodiments of the invention. | 62,293 |
11859698 | Corresponding reference characters indicate corresponding parts throughout the several views. The exemplification set out herein illustrates an exemplary embodiment of the invention and such exemplification is not to be construed as limiting the scope of the invention in any manner. DETAILED DESCRIPTION For the purposes of promoting an understanding of the principles of the present disclosure, reference is now made to the embodiment illustrated in the drawings, which is described below. The embodiment disclosed below is not intended to be exhaustive or limit the present disclosure to the precise form disclosed in the following detailed description. Rather, the embodiment is chosen and described so that others skilled in the art may utilize its teachings. Therefore, no limitation of the scope of the present disclosure is thereby intended. Corresponding reference characters indicate corresponding parts throughout the several views. In the disclosed transmission embodiment, selective couplers are disclosed. A selective coupler is a device which may be actuated to fixedly couple two or more components together. A selective coupler fixedly couples two or more components to rotate together as a unit when the selective coupler is in an engaged configuration. Further, the two or more components may be rotatable relative to each other when the selective coupler is in a disengaged configuration. The terms “couples”, “coupled”, “coupler” and variations thereof are used to include both arrangements wherein the two or more components are in direct physical contact and arrangements wherein the two or more components are not in direct contact with each other (e. g., the components are “coupled” via at least a third component), but yet still cooperate or interact with each other. A first exemplary selective coupler is a clutch. A clutch couples two or more rotating components to one another so that the two or more rotating components rotate together as a unit in an engaged configuration and permits relative rotation between the two or more rotating components in the disengaged position. Exemplary clutches may be shiftable friction-locked multi-disk clutches, shiftable form-locking claw or conical clutches, wet clutches, or any other known form of a clutch. A second exemplary selective coupler is a brake. A brake couples one or more rotatable components to a stationary component to hold the one or more rotatable components stationary relative to the stationary component in the engaged configuration and permits rotation of the one or more components relative to the stationary component in the disengaged configuration. Exemplary brakes may be configured as shiftable-friction-locked disk brakes, shiftable friction-locked band brakes, shiftable form-locking claw or conical brakes, or any other known form of a brake. Selective couplers may be actively controlled devices or passive devices. Exemplary actively controlled devices include hydraulically actuated clutch or brake elements and electrically actuated clutch or brake elements. Additional details regarding systems and methods for controlling selective couplers are disclosed in the above-incorporated U.S. Pat. No. 9,625,007. In addition to coupling through selective couplers, various components of the disclosed transmission embodiments may be fixedly coupled together continuously throughout the operation of the disclosed transmissions. Components may be fixedly coupled together either permanently or removably. Components may be fixedly coupled together through spline connections, press fitting, fasteners, welding, machined or formed functional portions of a unitary piece, or other suitable methods of connecting components. The disclosed transmission embodiments include a plurality of planetary gearsets. Each planetary gearset includes at least four components: a sun gear; a ring gear; a plurality of planet gears; and a carrier that is rotatably coupled to and carries the planet gears. In the case of a simple planetary gearset, the teeth of the sun gear are intermeshed with the teeth of the planet gears which are in turn intermeshed with the teeth of the ring gear. Each of these components may also be referred to as a gearset component. It will be apparent to one of skill in the art that some planetary gearsets may include further components than those explicitly identified. For example, one or more of the planetary gearsets may include two sets of planet gears. A first set of planet gears may intermesh with the sun gear while the second set of planet gears intermesh with the first set of planet gears and the ring gear. Both sets of planet gears are carried by the planet carrier. One or more rotating components, such as shafts, drums, and other components, may be collectively referred to as an interconnector when the one or more components are fixedly coupled together. Interconnectors may further be fixedly coupled to one or more gearset components and/or one or more selective couplers. An input member of the disclosed transmission embodiments is rotated by a prime mover. Exemplary prime movers include internal combustion engines, electric motors, hybrid power systems, and other suitable power systems. In one embodiment, the prime mover indirectly rotates the input member through a clutch and/or a torque converter. An output member of the disclosed transmission embodiments provides rotational power to one or more working components. Exemplary working components include one or more drive wheels of a motor vehicle, a power take-off shaft, a pump, and other suitable devices. The output member is rotated based on the interconnections of the gearset components and the selective couplers of the transmission. By changing the interconnections of the gearset components and the selective couplers, a rotation speed of the output member may be varied from a rotation speed of the input member. The disclosed transmission embodiment is capable of transferring torque from the input member to the output member and rotating the output member in at least nine forward gear or speed ratios relative to the input member, illustratively nine forward gear or speed ratios, and in at least nine reverse gear or speed ratios relative to the input member, illustratively nine reverse gear or speed ratios. The architecture disclosed herein may be utilized to achieve various gear ratios based on the characteristics of the gearsets utilized. Exemplary characteristics include respective gear diameters, the number of gear teeth, and the configurations of the various gears. FIG.1is a diagrammatic representation of a multi-speed transmission100. Multi-speed transmission100includes an input member102and an output member104. Each of input member102and output member104is rotatable relative to at least one stationary member106. An exemplary input member102is an input shaft or other suitable rotatable component. An exemplary output member104is an output shaft or other suitable rotatable component. An exemplary stationary member106is a housing of multi-speed transmission100. The housing may include several components coupled together. Multi-speed transmission100includes a plurality of planetary gearsets, illustratively a first planetary gearset108, a second planetary gearset110, a third planetary gearset112, a fourth planetary gearset114, and a fifth planetary gearset216. In one embodiment, additional planetary gearsets may be included. Further, although first planetary gearset108, second planetary gearset110, third planetary gearset112, fourth planetary gearset114, and fifth planetary gearset216are illustrated as simple planetary gearsets, it is contemplated that compound planetary gearsets may be included in some embodiments. In one embodiment, multi-speed transmission100is arranged as illustrated inFIG.1, with first planetary gearset108positioned between a first location or end116at which input member102enters stationary member106and second planetary gearset110, second planetary gearset110is positioned between first planetary gearset108and third planetary gearset112, third planetary gearset112is positioned between second planetary gearset110and fourth planetary gearset114, fourth planetary gearset114is positioned between third planetary gearset112and fifth planetary gearset216, and fifth planetary gearset216is positioned between fourth planetary gearset114and a second location or end118at which output member104exits stationary member106. In alternative embodiments, first planetary gearset108, second planetary gearset110, third planetary gearset112, fourth planetary gearset114, and fifth planetary gearset216are arranged in any order relative to location116and location118. In embodiments, each of first planetary gearset108, second planetary gearset110, third planetary gearset112, fourth planetary gearset114, and fifth planetary gearset216are axially aligned. In one example, input member102and output member104are also axially aligned with first planetary gearset108, second planetary gearset110, third planetary gearset112, fourth planetary gearset114, and fifth planetary gearset216. In alternative embodiments, one or more of input member102, output member104, first planetary gearset108, second planetary gearset110, third planetary gearset112, fourth planetary gearset114, and fifth planetary gearset216are offset and not axially aligned with the remainder. First planetary gearset108includes a sun gear120, a planet carrier122supporting a plurality of planet gears124, and a ring gear126. Second planetary gearset110includes a sun gear130, a planet carrier132supporting a plurality of planet gears134, and a ring gear136. Third planetary gearset112includes a sun gear140, a planet carrier142supporting a plurality of planet gears144, and a ring gear146. Fourth planetary gearset114includes a sun gear150, a planet carrier152supporting a plurality of planet gears154, and a ring gear156. Fifth planetary gearset216includes a sun gear220, a planet carrier222supporting a plurality of planet gears224, and a ring gear226. Multi-speed transmission100further includes a plurality of selective couplers, illustratively a first selective coupler158, a second selective coupler160, a third selective coupler162, a fourth selective coupler164, a fifth selective coupler166, a sixth selective coupler168, a seventh selective coupler170, and an eighth selective coupler172. In the illustrated embodiment, first selective coupler158, second selective coupler160, and eighth selective coupler172are clutches third selective coupler162, fourth selective coupler164, fifth selective coupler166, sixth selective coupler168, and seventh selective coupler170are brakes. The axial locations of the clutches and brakes relative to the plurality of planetary gearsets may be altered from the illustrated axial locations. Multi-speed transmission100includes several components that are illustratively shown as being fixedly coupled together. Input member102is fixedly coupled to sun gear120of first planetary gearset108, first selective coupler158, and second selective coupler160. Output member104is fixedly coupled to ring gear226of fifth planetary gearset216and eighth selective coupler172. Planet carrier122of first planetary gearset108is fixedly coupled to planet carrier132of second planetary gearset110and ring gear146of third planetary gearset112. Ring gear126of first planetary gearset108is fixedly coupled to sun gear130of second planetary gearset110and third selective coupler162. Ring gear136of second planetary gearset110is fixedly coupled to sixth selective coupler168. Sun gear140of third planetary gearset112is fixedly coupled to sun gear150of fourth planetary gearset114and first selective coupler158. Planet carrier142of third planetary gearset112is fixedly coupled to ring gear156of fourth planetary gearset114and second selective coupler160. Ring gear146of third planetary gearset112is fixedly coupled to fourth selective coupler164. Planet carrier152of fourth planetary gearset114is fixedly coupled to sun gear220of fifth planetary gearset216and eighth selective coupler172. Ring gear156of fourth planetary gearset114is fixedly coupled to fifth selective coupler166. Planet carrier222of fifth planetary gearset216is fixedly coupled to seventh selective coupler170. In alternative embodiments, one or more of the components fixedly coupled together are selectively coupled together through one or more selective couplers. Multi-speed transmission100may be described as having seven interconnectors. Input member102is a first interconnector that both provides input torque to multi-speed transmission100and fixedly couples sun gear120of first planetary gearset108, first selective coupler158, and second selective coupler160. Output member104is a second interconnector that both provides output torque from multi-speed transmission100and fixedly ring gear226of fifth planetary gearset216and eighth selective coupler172. A third interconnector180fixedly couples planet carrier122of first planetary gearset108to planet carrier132of second planetary gearset110and ring gear146of third planetary gearset112. A fourth interconnector182fixedly couples ring gear126of first planetary gearset108to sun gear130of second planetary gearset110. A fifth interconnector184fixedly couples ring gear156of fourth planetary gearset114, planet carrier142of third planetary gearset112, and second selective coupler160. A sixth interconnector186fixedly couples sun gear140of third planetary gearset112, sun gear150of fourth planetary gearset114, and first selective coupler158. A seventh interconnector188fixedly couples planet carrier152of fourth planetary gearset114to sun gear220of fifth planetary gearset216and eighth selective coupler172. Multi-speed transmission100further includes several components that are illustratively shown as being selectively coupled together through selective couplers. First selective coupler158, when engaged, fixedly couples a plurality of sun gears of first planetary gearset108, second planetary gearset110, third planetary gearset112, fourth planetary gearset114, and fifth planetary gearset216to input member102. More specifically, first selective coupler158, when engaged, fixedly couples input member102and sun gear120of first planetary gearset108to sun gear140of third planetary gearset112and sun gear150of fourth planetary gearset114. When first selective coupler158is disengaged, input member102and sun gear120of first planetary gearset108may rotate relative to sun gear140of third planetary gearset112and sun gear150of fourth planetary gearset114. Second selective coupler160, when engaged, fixedly couples input member102and sun gear120of first planetary gearset108to planet carrier142of third planetary gearset112and ring gear156of fourth planetary gearset114. When second selective coupler160is disengaged, input member102and sun gear120of first planetary gearset108may rotate relative to planet carrier142of third planetary gearset112and ring gear156of fourth planetary gearset114. Third selective coupler162, when engaged, fixedly couples ring gear126of first planetary gearset108and sun gear130of second planetary gearset110to stationary member106. When third selective coupler162is disengaged, ring gear126of first planetary gearset108and sun gear130of second planetary gearset110may rotate relative to stationary member106. Fourth selective coupler164, when engaged, fixedly couples ring gear146of third planetary gearset112, planet carrier132of second planetary gearset110, and planet carrier122of first planetary gearset108to stationary member106. When fourth selective coupler164is disengaged, ring gear146of third planetary gearset112, planet carrier132of second planetary gearset110, and planet carrier122of first planetary gearset108may rotate relative to stationary member106. Fifth selective coupler166, when engaged, fixedly couples ring gear156of fourth planetary gearset114and planet carrier142of third planetary gearset112to stationary member106. When fifth selective coupler166is disengaged, ring gear156of fourth planetary gearset114and planet carrier142of third planetary gearset112may rotate relative to stationary member106. Sixth selective coupler168, when engaged, fixedly couples ring gear136of second planetary gearset110to stationary member106. When sixth selective coupler168is disengaged, ring gear136of second planetary gearset110may rotate relative to stationary member106. Seventh selective coupler170, when engaged, fixedly couples planet carrier222of fifth planetary gearset216to stationary member106. When seventh selective coupler170is disengaged, planet carrier222of fifth planetary gearset216may rotate relative to stationary member106. Eighth selective coupler172, when engaged, fixedly couples planet carrier152of fourth planetary gearset114and sun gear220of fifth planetary gearset216to ring gear226of fifth planetary gearset216and output member104. When eighth selective coupler172is engaged, ring gear226and sun gear220of fifth planetary gearset216are locked together. Therefore, sun gear220, planet carrier222, and ring gear226all rotate together as a single unit. The same effect may be realized by coupling any two of sun gear220, planet carrier222, and ring gear226together. When eighth selective coupler172is disengaged, planet carrier152of fourth planetary gearset114and sun gear220of fifth planetary gearset216may rotate relative to ring gear226of fifth planetary gearset216and output member104. By engaging various combinations of first selective coupler158, second selective coupler160, third selective coupler162, fourth selective coupler164, fifth selective coupler166, sixth selective coupler168, seventh selective coupler170, and eighth selective coupler172, additional components of multi-speed transmission100may be fixedly coupled together. The plurality of planetary gearsets and the plurality of selective couplers of multi-speed transmission100may be interconnected in various arrangements to provide torque from input member102to output member104in at least nine forward gear or speed ratios and at least nine reverse gear or speed ratios. In the exemplary embodiment shown, selective couplers158-168are selectively engageable to establish the at least nine forward gear or speed ratios and the at least nine reverse gear or speed ratio. Selective couplers170,172may be selectively engaged to reverse the rotational direction of output member104relative to input member102and convert each of the at least nine forward gear or speed ratios to a complementary reverse gear or speed ratio. Referring toFIG.2, an exemplary truth table200is shown that provides the state of each of first selective coupler158, second selective coupler160, third selective coupler162, fourth selective coupler164, fifth selective coupler166, sixth selective coupler168, seventh selective coupler170, and eighth selective coupler172for nine different forward gear or speed ratios and nine reverse gear or speed ratios. Each row corresponds to a given interconnection arrangement for transmission100. The first column provides the gear range. The remaining columns illustrate which ones of the selective couplers158-172are engaged (“X” indicates engaged) and which ones of selective couplers158-172are disengaged (“(blank)” indicates disengaged).FIG.2is only one example of any number of truth tables possible for achieving at least nine forward speed or gear ratios and at least nine reverse speed or gear ratios. In the example ofFIG.2, to place multi-speed transmission in neutral (N), all of first selective coupler158, second selective coupler160, third selective coupler162, fourth selective coupler164, fifth selective coupler166, sixth selective coupler168, seventh selective coupler170, and eighth selective coupler172are in the disengaged configuration. One or more of first selective coupler158, second selective coupler160, third selective coupler162, fourth selective coupler164, fifth selective coupler166, sixth selective coupler168, seventh selective coupler170, and eighth selective coupler172may remain engaged in neutral (N) as long as the combination of first selective coupler158, second selective coupler160, third selective coupler162, third selective coupler162, fifth selective coupler166, sixth selective coupler168, seventh selective coupler170, and eighth selective coupler172does not transmit torque from input member102to output member104. For example, selective couplers166and168may be engaged in a neutral setting and then only one selective coupler needs to be engaged to place transmission in one of 1stforward gear (selective coupler172) or 1streverse gear (selective coupler170). A first forward gear or speed ratio (shown as 1st) in exemplary truth table200ofFIG.2is achieved by having fifth selective coupler166, sixth selective coupler168, and eighth selective coupler172in an engaged configuration and first selective coupler158, second selective coupler160, third selective coupler162, fourth selective coupler164, and seventh selective coupler170in a disengaged configuration. A second or subsequent forward gear or speed ratio (shown as 2nd) in exemplary truth table200ofFIG.2is achieved by having first selective coupler158, fifth selective coupler166, and eighth selective coupler172in an engaged configuration and second selective coupler160, third selective coupler162, fourth selective coupler164, sixth selective coupler168, and seventh selective coupler170in a disengaged configuration. Therefore, when transitioning between the first forward gear or speed ratio and the second forward gear or speed ratio, sixth selective coupler168is placed in the disengaged configuration and first selective coupler158is placed in the engaged configuration. A third or subsequent forward gear or speed ratio (shown as 3rd) in exemplary truth table200ofFIG.2is achieved by having first selective coupler158, sixth selective coupler168, and eighth selective coupler172in an engaged configuration and second selective coupler160, third selective coupler162, fourth selective coupler164, fifth selective coupler166, and seventh selective coupler170in a disengaged configuration. Therefore, when transitioning between the second forward gear or speed ratio and the third forward gear or speed ratio, fifth selective coupler166is placed in the disengaged configuration and sixth selective coupler168is placed in the engaged configuration. A fourth or subsequent forward gear or speed ratio (shown as 4th) in exemplary truth table200ofFIG.2is achieved by having first selective coupler158, fourth selective coupler164, and eighth selective coupler172in an engaged configuration and second selective coupler160, third selective coupler162, fifth selective coupler166, sixth selective coupler168, and seventh selective coupler170in a disengaged configuration. Therefore, when transitioning between the third forward gear or speed ratio and the fourth forward gear or speed ratio, sixth selective coupler168is placed in the disengaged configuration and fourth selective coupler164is placed in the engaged configuration. A fifth or subsequent forward gear or speed ratio (shown as 5th) in exemplary truth table200ofFIG.2is achieved by having first selective coupler158, third selective coupler162, and eighth selective coupler172in an engaged configuration and second selective coupler160, fourth selective coupler164, fifth selective coupler166, sixth selective coupler168, and seventh selective coupler170in a disengaged configuration. Therefore, when transitioning between the fourth forward gear or speed ratio and the fifth forward gear or speed ratio, fourth selective coupler164is placed in the disengaged configuration and third selective coupler162is placed in the engaged configuration. A sixth or subsequent forward gear or speed ratio (shown as 6th) in exemplary truth table200ofFIG.2is achieved by having first selective coupler158, second selective coupler160, and eighth selective coupler172in an engaged configuration and third selective coupler162, fourth selective coupler164, fifth selective coupler166, sixth selective coupler168, and seventh selective coupler170in a disengaged configuration. Therefore, when transitioning between the fifth forward gear or speed ratio and the sixth forward gear or speed ratio, third selective coupler162is placed in the disengaged configuration and second selective coupler160is placed in the engaged configuration. A seventh or subsequent forward gear or speed ratio (shown as 7th) in exemplary truth table200ofFIG.2is achieved by having second selective coupler160, third selective coupler162, and eighth selective coupler172in an engaged configuration and first selective coupler158, fourth selective coupler164, fifth selective coupler166, sixth selective coupler168, and seventh selective coupler170in a disengaged configuration. Therefore, when transitioning between the sixth forward gear or speed ratio and the seventh forward gear or speed ratio, first selective coupler158is placed in the disengaged configuration and third selective coupler162is placed in the engaged configuration. An eighth or subsequent forward gear or speed ratio (shown as 8th) in exemplary truth table200ofFIG.2is achieved by having second selective coupler160, fourth selective coupler164, and eighth selective coupler172in an engaged configuration and first selective coupler158, third selective coupler162, fifth selective coupler166, sixth selective coupler168, and seventh selective coupler170in a disengaged configuration. Therefore, when transitioning between the seventh forward gear or speed ratio and the eighth forward gear or speed ratio, third selective coupler162is placed in the disengaged configuration and fourth selective coupler164is placed in the engaged configuration. A ninth or subsequent forward gear or speed ratio (shown as 9th) in exemplary truth table200ofFIG.2is achieved by having second selective coupler160, sixth selective coupler168, and eighth selective coupler172in an engaged configuration and first selective coupler158, third selective coupler162, fourth selective coupler164, fifth selective coupler166, and seventh selective coupler170in a disengaged configuration. Therefore, when transitioning between the eighth forward gear or speed ratio and the ninth forward gear or speed ratio, fourth selective coupler164is placed in the disengaged configuration and sixth selective coupler168is placed in the engaged configuration. In each of the 1stthrough 9thforward gear or speed ratios, at least three of selective couplers158-172are in an engaged configuration. More specifically, eighth selective coupler172is in an engaged configuration and seventh selective coupler170is in a disengaged configuration in each of the 1stthrough 9thforward gear or speed ratios. Accordingly, output member104rotates in the same direction as input member102. In order to reverse the direction of output member104relative to input member102for each of the 1stthrough 9thforward gear or speed ratios, eighth selective coupler172is placed in the disengaged configuration and seventh selective coupler170is placed in the engaged configuration. Placing eighth selective coupler172in the disengaged configuration and seventh selective coupler170in the engaged configuration and maintaining the selective engagement and disengagement configuration of selective couplers158-168for each of the 1stthrough 9thforward gear or speed ratios reverses the direction of output member104relative to input member102and establishes a complementary reverse gear or speed ratio. In the exemplary embodiment shown, fifth planetary gearset216is positioned between output member104and the group of first planetary gearset108, second planetary gearset110, third planetary gearset112, and fourth planetary gearset114and6may be referred to as an output reversing planetary gearset. A first reverse gear or speed ratio (shown as 1st Rev), complementary to the first forward gear or speed ratio, in exemplary truth table200ofFIG.2is achieved by having fifth selective coupler166, sixth selective coupler168, and seventh selective coupler170in an engaged configuration and first selective coupler158, second selective coupler160, third selective coupler162, fourth selective coupler164, and eighth selective coupler172in a disengaged configuration. A second or subsequent reverse gear or speed ratio (shown as 2nd Rev), complementary to the second forward gear or speed ratio, in exemplary truth table200ofFIG.2is achieved by having first selective coupler158, fifth selective coupler166, and seventh selective coupler170in an engaged configuration and second selective coupler160, third selective coupler162, fourth selective coupler164, sixth selective coupler168, and eighth selective coupler172in a disengaged configuration. Therefore, when transitioning between the first reverse gear or speed ratio and the second reverse gear or speed ratio, sixth selective coupler168is placed in the disengaged configuration and first selective coupler158is placed in the engaged configuration. A third or subsequent reverse gear or speed ratio (shown as 3rd Rev), complementary to the third forward gear or speed ratio, in exemplary truth table200ofFIG.2is achieved by having first selective coupler158, sixth selective coupler168, and seventh selective coupler170in an engaged configuration and second selective coupler160, third selective coupler162, fourth selective coupler164, fifth selective coupler166, and eighth selective coupler172in a disengaged configuration. Therefore, when transitioning between the second reverse gear or speed ratio and the third reverse gear or speed ratio, fifth selective coupler166is placed in the disengaged configuration and sixth selective coupler168is placed in the engaged configuration. A fourth or subsequent reverse gear or speed ratio (shown as 4th Rev), complementary to fourth forward gear or speed ratio, in exemplary truth table200ofFIG.2is achieved by having first selective coupler158, fourth selective coupler164, and seventh selective coupler170in an engaged configuration and second selective coupler160, third selective coupler162, fifth selective coupler166, sixth selective coupler168, and eighth selective coupler172in a disengaged configuration. Therefore, when transitioning between the third reverse gear or speed ratio and the fourth reverse gear or speed ratio, sixth selective coupler168is placed in the disengaged configuration and fourth selective coupler164is placed in the engaged configuration. A fifth or subsequent reverse gear or speed ratio (shown as 5th Rev), complementary to the fifth forward gear or speed ratio, in exemplary truth table200ofFIG.2is achieved by having first selective coupler158, third selective coupler162, and seventh selective coupler170in an engaged configuration and second selective coupler160, fourth selective coupler164, fifth selective coupler166, sixth selective coupler168, and eighth selective coupler172in a disengaged configuration. Therefore, when transitioning between the fourth reverse gear or speed ratio and the fifth reverse gear or speed ratio, fourth selective coupler164is placed in the disengaged configuration and third selective coupler162is placed in the engaged configuration. A sixth or subsequent reverse gear or speed ratio (shown as 6th Rev), complementary to the sixth forward gear or speed ratio, in exemplary truth table200ofFIG.2is achieved by having first selective coupler158, second selective coupler160, and seventh selective coupler170in an engaged configuration and third selective coupler162, fourth selective coupler164, fifth selective coupler166, sixth selective coupler168, and eighth selective coupler172in a disengaged configuration. Therefore, when transitioning between the fifth reverse gear or speed ratio and the sixth reverse gear or speed ratio, third selective coupler162is placed in the disengaged configuration and second selective coupler160is placed in the engaged configuration. A seventh or subsequent reverse gear or speed ratio (shown as 7th Rev), complementary to the seventh forward gear or speed ratio, in exemplary truth table200ofFIG.2is achieved by having second selective coupler160, third selective coupler162, and seventh selective coupler170in an engaged configuration and first selective coupler158, fourth selective coupler164, fifth selective coupler166, sixth selective coupler168, and eighth selective coupler172in a disengaged configuration. Therefore, when transitioning between the sixth reverse gear or speed ratio and the seventh reverse gear or speed ratio, first selective coupler158is placed in the disengaged configuration and third selective coupler162is placed in the engaged configuration. An eighth or subsequent reverse gear or speed ratio (shown as 8th Rev), complementary to the eight forward gear or speed ratio, in exemplary truth table200ofFIG.2is achieved by having second selective coupler160, fourth selective coupler164, and seventh selective coupler170in an engaged configuration and first selective coupler158, third selective coupler162, fifth selective coupler166, sixth selective coupler168, and eighth selective coupler172in a disengaged configuration. Therefore, when transitioning between the seventh reverse gear or speed ratio and the eighth reverse gear or speed ratio, third selective coupler162is placed in the disengaged configuration and fourth selective coupler164is placed in the engaged configuration. A ninth or subsequent reverse gear or speed ratio (shown as 9th Rev), complementary to the ninth forward gear or speed ratio, in exemplary truth table200ofFIG.2is achieved by having second selective coupler160, sixth selective coupler168, and seventh selective coupler170in an engaged configuration and first selective coupler158, third selective coupler162, fourth selective coupler164, fifth selective coupler166, and eighth selective coupler172in a disengaged configuration. Therefore, when transitioning between the eighth reverse gear or speed ratio and the ninth reverse gear or speed ratio, fourth selective coupler164is placed in the disengaged configuration and sixth selective coupler168is placed in the engaged configuration. The present disclosure contemplates that downshifts follow the reverse sequence of the corresponding upshift (as described above). Further, several power-on skip-shifts that are single-transition are possible (e. g. from 1stup to 3rd, from 3rddown to 1st, from 3rdup to 5th, and from 5thdown to 3rd). In the illustrated embodiment, various combinations of three of the available selective couplers are engaged for each of the illustrated forward and reverse gear or speed ratios. Additional forward gear or speed ratios and reverse gear or speed ratios are possible based on other combinations of engaged selective couplers. Although in the illustrated embodiment, each forward gear or speed ratio and reverse gear or speed ratio has three of the available selective couplers engaged, it is contemplated that less than three and more than three selective couplers may be engaged at the same time. While this invention has been described as having exemplary designs, the present invention can be further modified within the spirit and scope of this disclosure. This application is therefore intended to cover any variations, uses, or adaptations of the invention using its general principles. Further, this application is intended to cover such departures from the present disclosure as come within known or customary practice in the art to which this invention pertains and which fall within the limits of the appended claims. | 35,814 |
11859699 | DETAILED DESCRIPTION Described herein is a system and method for an over travel stop mechanism that prevents a gear system from travelling past its design limits. A schematic of an over travel stop mechanism for a first gear20and a second gear30is shown inFIG.1. The first gear20and the second gear30are concentric spur gears of differing sizes which are rotatable on shaft1. Each of the first gear20and the second gear30is run from an input gear10which is a single two-output spur gear. The first output12of the input gear10meshes with the first gear20and the second output14of the input gear10meshes with the second gear30. The first output12and the second output14of the input gear10are each fixed on shaft2and therefore they rotate at the same speed. The first gear20rotates independently to the second gear30. Optionally, one of either the first gear20or the second gear30can be configured to drive shaft1as a system output. When the single two-output spur gear10is turned, the first gear20and the second gear30will turn at a differential speed because the first gear20and the second gear30have differing sizes. The first gear20will turn in a first direction and the second gear30will also turn in the same, first direction. A first end stop25is provided on the first gear20and a second end stop35is provided on the second gear30. When the input gear10is turned, the first end stop25will move either towards or away from the second end stop35, depending on the direction of input rotation. The first end stop25and the second end stop35are configured such that engagement between the first end stop25and the second end stop35will prevent further motion of the first gear20and the second gear30in the first direction. This prevents travel of the first gear20and the second gear30past their design limits. The system stalls upon engagement of the first end stop25with the second end stop35because the first gear20and the second gear30are driven by the same input gear10. The example shown inFIG.2is in accordance with the example shown inFIG.1.FIG.2shows that the first gear20has a larger circumference than the second gear30. The first end stop25of the first gear20extends radially inwards from the circumferential edge of the first gear20. The second end stop35extends radially outwards form the circumferential edge of the second gear30. The first end stop25and the second end stop35are therefore shaped and sized so as to be configured to interlock when they engage each other. Other configurations of end stops are also envisaged. For example, any arrangement of end stops that are fixed to the gears and can engage each other directly through rotary engagement is envisaged. Other systems are also envisaged wherein alongside the end stops, an additional member is provided. This additional member could be fixed to the gearing or translated via a frictional device (i.e. a clutch). Frictional devices are useful for high speed and high inertia systems because the dissipation of speed that results from engagement of the end stops can be controlled through an additional frictional device integrated into the end stops. In addition to, or as an alternative the above, a pin or roller70can be provided that is configured to sit between end stops, as shown inFIG.3.FIG.3shows the system in accordance with the embodiment ofFIG.2with the addition of two rollers70positioned on either side of the first end stop25. When the first end stop25approaches the second end stop35, the first end stop25and the second end stop will impact one of the rollers70. The result of this is that the load distribution between the end stops will be altered and susceptibility to geometric tolerances will be removed. The system described in accordance withFIGS.1and2can be adapted for different gear systems and is scalable for many load and stroke applications. In one example in accordance withFIGS.1and2, the distance between the central rotational shaft1and the centre of the input gear10is 100 mm. The first gear20has a diameter of 52 mm and the second gear30has a diameter of 50 mm. The first end stop25and the second end stop35will move either together or apart by 27.7° per turn of the input gear10, depending on the direction of the input turn. If the first end stop25and the second end stop35are initially set to be 180° apart, the total travel permitted would be 6.5 input turns before the first end stop25and the second end stop35engage each other. In this same example, if the first end stop25and the second end stop35are set to be initially 300° apart, the total travel permitted would be 10.83 input turns. In another example, the distance between the central rotational shaft1and the centre of the single two-output spur gear10is again 100 mm. The first gear20has a diameter of 82 mm and second gear30has a diameter of 80 mm. The first end stop25and the second end stop35will move either together or apart by 10.9° per input turn, depending on the direction of the input turn. If the first end stop25and the second end stop35are initially set to be 300° apart, the total travel permitted would be 27.5 turns. Systems having other dimensions may also be envisaged. In addition to, or as an alternative the above, other configurations are envisaged wherein more than one pair of stops are used for redundancy. In these configurations, the gears will comprise a plurality of end stops which are equally spaced around the gears. FIG.4shows how the over travel stop mechanism can be provided for gears that are stacked in various configurations in order to create a higher load carrying capability.FIG.4shows a first gear120meshed with an input spur gear110, a second gear130meshed with an input spur gear112and a third gear140meshed with an input spur gear114. The first gear120comprises a first end stop115and a second end stop125. The second gear130comprises a third end stop135. The third gear140comprises a fourth end stop145. The input spur gears110,112and114are fixed to the same shaft102so that they rotate at the same speed. The first gear120, the second gear130and the third gear140can rotate independently of each other on shaft101and any one of the first gear, the second gear130, or the third gear140can drive shaft101as a system output. Alternatively, the second gear130and the third gear140can be fixed to the shaft101and the first gear120can rotate independently of the second gear130and the third gear140. The gear system inFIG.4is configured such that the first gear120rotates at a differential speed to both the second gear130and the third gear140. The second gear130and the third gear140rotate at the same speed. The gear system is further configured such that, when the first gear120has rotated in a first direction up to its design limit, the first end stop115engages the third end stop135, and the second end stop125engages the fourth end stop145in order to stop further rotation of the first gear120. The system stalls upon engagement of the end stops because the first gear120, the second gear130and the third gear140are respectively driven by input gears110,112and114that are all fixed to shaft102. The load carrying capability of the over travel stop mechanism can be further increased by reducing the gear tooth load. The load carrying capability can also be increased by reducing the load induced in the end stops. The over stop travel system can be incorporated into existing gear boxes as shown inFIG.5. The left panel ofFIG.5shows a first gear220which is meshed with an input gear212and an output gear214. The first gear220is rotatable on shaft201, the input212gear is fixed to shaft202and the output gear214is rotatable on shaft203. The input gear212rotates independently to the output gear214. The right panel ofFIG.5shows the system of the left panel ofFIG.5with the incorporation of an over travel stop system. All of the elements in the right panel of theFIG.5are identical to the left panel ofFIG.5with the additional features of a first end stop225provided on the first gear220, a second gear230provided on shaft201and second input gear216fixed to shaft202. The second gear230is rotatable on shaft201and is provided with a second end stop235. The first gear220rotates independently from the second gear230. The second input gear216meshes with the second gear230. The system in the right panel ofFIG.5can be configured such that, when the first gear220has rotated up to its design limit, the first end stop225engages the second end stop235in order to stop the motion of the first gear220. The system stalls upon engagement of the end stops because the first gear220and the second gear230are respectively driven by the first input gear212and the second input gear216that are both fixed to shaft202. In all of the examples described herein, the stopping mechanism does not rely on an axially moving element. The stopping elements described herein are configured so that rotational movement of the stopping elements results in engagement of the end stops to prevent over travel of the gears. The design is therefore not affected by axial vibration characteristics which would be an issue for designs that rely of axially moving stopping elements. The benefits of the above described over travel stop systems are that they are scalable for many load and stroke applications. In comparison to other over travel stop systems, the examples described herein are of low complexity which enables the cost and weight of the system to be reduced. Furthermore, a minimal space envelope is required because of the compact design. The over travel stop system can be incorporated into many gear mechanisms such as down drive gear boxes by installing a second pair of gears onto one set of existing gears. The over travel stop system is a low drag alternative to using other conventional mechanisms to create differential movement due to the low number of sliding surfaces. Although this disclosure has been described in terms of preferred examples, it should be understood that these examples are illustrative only and that the claims are not limited to those examples. Those skilled in the art will be able to make modifications and alternatives in view of the disclosure which are contemplated as falling within the scope of the appended claims. | 10,290 |
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