JP2005297649A - Operation control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To perform improvement of the control response of a pressure piston cylinder part operated by the pressure of operating oil generated according to a differential rotation between rotating members with simple structure. <P>SOLUTION: The operation control device is equipped with a rotating shaft 11, and a drive pinion shaft 17 at the rotation side performing torque transmission, a pump part 23 generating the pressure of the oil according to the differential rotation between the rotating shaft 11 and the drive pinion shaft 17, the pressure piston cylinder part 24 which is provided at the rotation side and operates according to the pressure of the oil, and a clutch part 21 operating according to the pressure piston cylinder part 24. A control valve 27 is provided at the rotation side, and the operation pressure of the pressure piston cylinder part 24 is controlled by the control of the control valve 27. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an operation control device that changes a torque transmission state of an automobile.

  As an example of a conventional operation control device, for example, there is a torque transmission device shown in a sectional view of FIG.

  As shown in FIG. 7, the torque transmission device 301 includes a friction clutch 307 and a hydraulic pump 309 between the rotation shafts 303 and 305. A drum 311 is fixed on the rotary shaft 10 side, and a piston 313 is supported on the drum 311. A piston chamber 315 is provided between the drum 311 and the piston 313.

  When the rotary shafts 303 and 305 are differentially rotated, the hydraulic pump 309 works to suck oil from the oil reservoir 317 and pump it to the piston chamber 315. The piston 313 is moved by the oil pressure, and the friction clutch 307 is fastened.

  Therefore, the friction clutch 307 can be fastened according to the differential rotation between the rotating shafts 303 and 305.

  However, since the piston 313 and the piston chamber 315, which are fluid actuators, are provided on the rotating shaft 305 in the above structure, there is a problem that it is difficult to perform free control by the pressure control circuit. That is, when performing a free control by the pressure control circuit, since the control valve for pressure control and the controller for electric control are provided on the fixed side, it may be difficult to adjust the pressure of the piston chamber 315 on the rotation side, The structure for oil distribution between the stationary side and the rotating side may be complicated. For this reason, there is a problem that the control function is lowered and it is difficult to improve the control response.

JP-A-63-301130

  The problem to be solved is that it is difficult to improve the control response of the fluid actuator on the rotation side, and the structure becomes complicated.

  The present invention provides a control valve on the rotation side in order to improve the control response of a fluid actuator that operates with the pressure of the working fluid generated according to the differential rotation between the rotating members. The most important feature is to control the operating pressure of the fluid actuator by control.

  In the operation control device of the present invention, a control valve is provided on the rotation side, and the operation pressure of the fluid actuator is controlled by the control valve. Therefore, the flow of the working fluid between the control valve and the fluid actuator is controlled on the rotation side. The control function can be prevented from being lowered and the control response can be improved with a simple structure.

  When the control valve is provided on one of the first and second rotating members, the control function of the fluid actuator provided on the rotating side is reliably suppressed and controlled with a simple structure. Response can be improved reliably.

  When the fluid actuator and the control valve are directly connected by the flow path provided on the rotation side, the control response can be improved reliably.

  When the control valve has a pressure adjustment opening communicating with the fluid actuator and controls the operating pressure of the fluid actuator by changing the area of the pressure adjustment opening, the control valve has a simple structure for changing the area of the pressure adjustment opening. A decrease in the control function can be reliably suppressed, and the control response can be reliably improved.

  The pressure adjustment opening is formed by a plurality of openings communicating with the fluid actuator, and further includes a movable member movable in a direction along a rotation axis on the rotation side, and the movable member includes the opening In the case where the area is changed by selectively opening and closing, the reduction of the control function can be reliably suppressed and the control response can be improved with a simple structure in which the area is changed by moving the movable member.

  The control valve includes a spool valve capable of changing an area of the pressure adjustment opening on the rotation side and a movable member movable in a direction along the rotation axis, and adjusts the spool valve by movement of the movable member. In this case, a simple structure in which the area of the pressure adjustment opening is changed via the spool valve by the movement of the movable member can reliably suppress a decrease in the control function and improve the control response with certainty.

  In the case where a movable member that adjusts the opening area of the pressure adjusting opening is provided and a movement control unit that controls the movement of the movable member is provided, the movable member can be reliably moved.

  When the movement control means controls the movement of the movable member manually or by an actuator, the movable member can be reliably moved.

  The movement control means is provided on the rotation side and moves by the centrifugal force due to the input rotation on the rotation side, and the movement of the movable member is received in the direction along the rotation axis by the movement of the ball. In the case of the cam portion to be performed and the biasing means for returning the movement, the movable member can be reliably moved according to the input rotation without using a special drive source.

  The pump portion is supported on the one side of the first and second rotating members, and is supported by the other side and is in contact with the concavo-convex portion to reciprocate by relative rotation with the concavo-convex portion. A reciprocating body that pumps the working fluid, and the fluid actuator includes a pressure piston that is supported on the other side of the first and second rotating members and forms a pressure chamber between the other side, When the working fluid pumped by the pump unit is supplied to the pressure chamber, the working fluid discharged from the pump unit can be guided to the fluid actuator, and the pressure of the pump unit can be efficiently applied.

  When the operation unit is a clutch unit that changes the torque transmission state between the pair of rotating members, the torque transmission state can be changed according to the differential rotation between the pair of rotating members, and the clutch unit External control can also be easily performed with a simple structure.

  When the operation unit is a switching mechanism unit that switches the transmission state of the transmission gear or a switching mechanism unit that switches the transmission state of the continuously variable transmission using the metal belt, according to the differential rotation between the pair of rotating members. The switching mechanism can be changed, and external control of the switching mechanism can be easily performed with a simple structure.

  When the clutch unit controls the torque transmission state over the two-wheel drive state and the four-wheel drive state of the four-wheel drive vehicle, the drive state over the two-wheel drive state and the four-wheel drive state is determined according to the input rotation. It can be reliably controlled.

  When the clutch part is provided on the input side to the differential device that is the driven side of the four-wheel drive vehicle or on the output side of the transfer, the transmission torque to the rear wheel side is controlled according to the input rotation, The driving state over the driving state and the four-wheel driving state can be reliably controlled.

  When the clutch portion is provided in the differential device of the four-wheel drive vehicle and changes the torque transmission state to the left and right axle shafts, the transmission torque to the left and right wheels can be controlled according to the left and right differential rotation.

  The purpose of changing the operating characteristics while suppressing the deterioration of the function was realized with a simple structure.

  1 and 2 relate to a first embodiment of the present invention, FIG. 1 is a skeleton plan view of a four-wheel drive vehicle showing an arrangement of a torque transmission device as an example of an operation control device, and FIG. 2 is a mounting state of the torque transmission device. FIG.

As shown in FIG. 1, the torque transmission device 1 includes a rear differential device 3 and a propeller of a laterally mounted front engine front drive base (FF base) part-time four-wheel drive vehicle (also referred to as an on-demand four-wheel drive vehicle). It is arranged between the shaft 5. The torque transmission device 1 is disposed in the carrier cover 7. The carrier cover 7 constitutes a carrier together with a differential carrier 9 which is a carrier body, and is detachably attached to the differential carrier 9 with bolts or the like. The rear differential device 3 is a driven-side differential device with respect to a later-described front differential device to which driving force is constantly transmitted. The torque transmission device 1 has a rotary shaft 11 on one end side that supports one end of the carrier cover 7. The drive pinion shaft 17 on the other end side is interlocked with the rear differential device 3 while projecting from the portion 13 and coupled to the constant velocity joint 15. In the present embodiment, the rotating shaft 11 and the drive pinion shaft 17 constitute a pair of first and second rotating members of the torque transmission device 1. The drive pinion shaft 17 includes a drive pinion gear 19.

  In addition to the rotating shaft 11 and the drive pinion shaft 17, the torque transmission device 1 includes a clutch part 21 that is an operation part, a pump part 23, and a pressurizing piston cylinder part 24 that is a fluid actuator. A control valve 27 is provided on the rotating shaft 11 which is the rotating side of the two-rotating member.

  The clutch portion 21 is fastened according to the pressure piston cylinder portion 24 and changes the torque transmission state between the rotating shaft 11 and the drive pinion shaft 17.

  The pump unit 23 generates pressure of the working oil according to the differential rotation between the rotary shaft 11 as the first rotating member and the drive pinion shaft 17 as the second rotating member. The suction port side of the pump unit 23 communicates with the oil reservoir 25 side and sucks the working oil from the oil reservoir 25 according to the input rotation of the rotary shaft 11. The discharge port side of the pump part 23 is connected to the pressurizing piston cylinder part 24 side.

  The control valve 27 adjusts the degree of communication between the pressure piston cylinder portion 24 and the oil reservoir portion 25. Therefore, the control valve 27 adjusts the operating pressure of the pressurizing piston cylinder part 24 by returning a part or all of the working oil discharged from the pump part 23 to the oil reservoir 25 side.

  Control of the control valve 27 is performed by an electromagnetic actuator 31 as movement control means. As the electromagnetic actuator 31, a solenoid or the like is used and is electrically controlled by a controller configured by a microcomputer or the like. The controller inputs detection signals from various sensors. The controller can control the control valve 27 according to the running conditions of the vehicle by signals from various sensors. Various sensors include a vehicle speed sensor, a steering angle sensor, a front and rear wheel rotational speed sensor, an oil temperature sensor, and the like.

  The rear differential device 3 is rotatably supported by the differential carrier 9. The ring gear 35 of the rear differential device 3 meshes with the drive pinion gear 19. The rear differential device 3 is linked to left and right rear wheels 41 and 43 via left and right axle shafts 37 and 39.

  The rotating shaft 11 is linked to an output shaft 47 of the transfer 46 via the constant velocity joint 15, the propeller shaft 5, and the constant velocity joint 45. The output shaft 47 is provided with a bevel gear 49 in the transfer 46. The bevel gear 49 is linked to the bevel gear 51, the transmission shaft 53, and the spur gears 55 and 57, and the spur gear 57 is linked to the differential case 61 of the front differential device 59.

  The output of an engine 65 as an internal combustion engine is input to the ring gear 63 of the front differential device 59 via a transmission 67. The front differential device 59 is linked to left and right front wheels 73 and 75 via left and right axle shafts 69 and 71.

  Therefore, the output torque of the engine 65 is transmitted from the transmission 67 to the ring gear 63 of the front differential device 59, and is transmitted from the front differential device 59 to the left and right front wheels 73 and 75 via the left and right axle shafts 69 and 71. Further, torque is transmitted from the differential case 61 of the front differential device 59 to the propeller shaft 5 through the spur gears 57 and 55, the transmission shaft 53, the bevel gears 51 and 49, and the output shaft 47 of the transfer 46. Torque is transmitted from the propeller shaft to the rotating shaft 11 of the torque transmission device 1.

  In the torque transmission device 1, the pump portion 23 works by differential rotation between the rotating shaft 11 and the drive pinion shaft 17, and the working oil is pumped from the oil reservoir portion 25 to the pressurizing piston cylinder portion 24. The control valve 27 adjusts the operating pressure of the pressurizing piston cylinder part 24 by adjusting the amount of hydraulic oil discharged from the pump part 23 to the oil reservoir 25.

  The clutch part 21 transmits torque from the rotary shaft 11 to the drive pinion shaft 17 and the left and right rear wheels 41 and 43 when the clutch part 21 is fastened by the operation of the pressurizing piston cylinder part 24 and controlled to a torque transmission state. Therefore, the vehicle can travel in the four-wheel drive state by the left and right front wheels 73 and 75 and the left and right rear wheels 41 and 43.

  If the hydraulic oil is not pumped to the pressurizing piston cylinder 24, the clutch 21 is not fastened and the torque transmission device 1 enters a torque cutoff state. At this time, torque transmission from the rotary shaft 11 to the drive pinion shaft 17 is interrupted, and torque is not transmitted to the left and right rear wheels 41 and 43. Therefore, traveling in a two-wheel drive state can be performed by transmitting torque to the left and right front wheels 73 and 75.

  As shown in FIG. 2, the clutch portion 21 of the torque transmission device 1 includes a clutch outer cylinder 77 and a clutch hub 79. The clutch outer cylinder 77 is integrally provided with a vertical wall portion 81 on the inner peripheral side thereof. In the middle part of the vertical wall part 81, a linkage support part 82 is provided in a circular shape. An inner peripheral boss portion 83 is integrally provided on the inner peripheral edge of the vertical wall portion 81. The inner peripheral boss 83 is spline-engaged with the end of the drive pinion shaft 17. Due to this spline engagement, the clutch outer cylinder 77 is engaged with the drive pinion shaft 17 in the rotational direction, and is movable in the direction of the drive pinion shaft 17 (right direction in the figure) along the rotational axis. In order to make the spline engaging portion move smoothly, a ball spline may be used between the spline itself or between the spline and the inner peripheral boss portion 83, or an elastic member or a low friction member may be used. it can.

  The clutch hub 79 is integrally provided at one end of the rotating shaft 11. The front end of the clutch hub 79 is supported and supported by a linkage support portion 82 of the clutch outer cylinder 77 via a needle bearing 84 so as to be relatively rotatable. With this holding support, the clutch outer cylinder 77 and the clutch hub 79 can be reliably supported, and the occurrence of vibrations can be suppressed without rattling.

  A frictional multi-plate clutch 87 is provided between the clutch outer cylinder 77 and the clutch hub 79. In the friction multi-plate clutch 87, an outer plate is spline-engaged with the clutch outer cylinder 77 and an inner plate is spline-engaged with the clutch hub 79. Therefore, torque transmission between the clutch outer cylinder 77 and the clutch hub 79 can be performed by the friction engagement of the friction multi-plate clutch 87.

  A pressure receiving plate 86 is disposed opposite one end between the clutch outer cylinder 77 and the clutch hub 79, and a pressing plate 89 is disposed opposite the other end. Referring also to the enlarged cross-sectional view of the main part of FIG. 3, the pressure receiving plate 86 is fitted and fixed to the stepped portion 94 of the clutch hub 79 and positioned in the direction along the rotational axis. The press plate 89 has an outer spline 88 engaged with an inner spline 90 on the inner periphery of the clutch outer cylinder 77. A snap ring 92 is attached to the clutch outer cylinder 77 to position the pressing plate 89. The pressing plate 89 can be moved in the direction along the rotation axis together with the clutch outer cylinder 77 by the snap ring 92.

  A cam cylinder 91 is integrally provided on the inner peripheral edge of the pressing plate 89. A pump cam 93 of the pump unit 23 is provided on the inner peripheral surface of the cam cylinder 91 as a circumferential uneven portion. Accordingly, the pump cam 93 is formed in a circular shape on the drive pinion shaft 17 side which is one of the first and second rotating members. The profile has a length in the direction along the rotational axis of the pump cam 93. Due to the profile of the pump cam 93, the pump piston 95 is allowed to move on the side of the pressing plate 89 that moves together with the clutch outer cylinder 77.

  The pump unit 23 includes a pump piston 95 which is a reciprocating body in addition to the pump cam 93. The pump piston 95 is supported on the rotating shaft 11 side, which is the other side of the first and second rotating members. The pump piston 95 is in contact with the pump cam 93 and reciprocates in the rotational radial direction of the rotating shaft 11 by relative rotation with the pump cam 93 to generate pressure of working oil as working fluid.

  Specifically, a support wall 97 is integrally provided on the rotating shaft 11 on the base side of the clutch hub 79. The support wall 97 is provided with a pump cylinder 99 penetrating along the radial direction of rotation. A plurality of pump cylinders 99 are provided on the support wall 97 at predetermined intervals in the circumferential direction, and a suction port 101 is provided in each pump cylinder 99. The suction port 101 opens to a suction preliminary chamber 102 in the carrier housing 7.

  The pump pistons 95 are supported by the pump cylinders 99 so as to reciprocate. A pump spring 103 is provided in the pump cylinder 99. The pump spring 103 is interposed between the spring receiver 105 in the pump cylinder 99 and the pump piston 95. The tip of the pump piston 95 is in contact with the pump cam 93 by the urging force of the pump spring 99. The spring receiver 105 is positioned by a snap ring 107.

  A discharge port 109 is provided at the end of the pump cylinder 99. A pump valve 111 is provided at the discharge port 109. The pump valve 111 is opened by a part of the outer peripheral portion being bent inward in the rotational radial direction by the discharge pressure generated by the reciprocating motion of the pump piston 95.

  On the inner peripheral side of the pump portion 23, a flow path 113 is provided in the rotary shaft 11 which is the other side of the first and second rotary members. The flow path 113 guides the working oil discharged by the pump unit 23 to the inside in the rotational radius direction to the control valve 27. The flow path 113 includes a cavity 115 and a shaft hole 116. The hollow portion 115 is provided on the inner peripheral side of the pump portion 23 at the end of the rotary shaft 11 and communicates with the discharge port 109. The shaft hole 116 is provided in the shaft core portion of the rotating shaft 11, and allows the cavity 115 to communicate with the control valve 27.

  The preliminary suction chamber 102 is formed between the rotary shaft 11 and the intermediate wall 117 of the carrier cover 7. That is, a cylindrical portion 119 is provided on the intermediate wall 117. On the support wall 97 of the rotary shaft 11, a seal support portion 121 is formed in a circular shape on the outer peripheral side of the suction port 101. An oil seal 123 is interposed between the inner periphery of the intermediate wall 117 and the seal support part 121. A seal support fitting 125 is attached to the inner periphery of the tip of the cylindrical portion 119. An oil seal 126 is interposed between the seal support fitting 125 and the rotary shaft 11. The cylindrical portion 119 is provided with a suction tube 127 on the lower side. The suction tube 127 has an upper end facing the suction preliminary chamber 102 and a lower end facing the lowest portion 122 side of the oil reservoir 25 in the carrier cover 7. The oil reservoir 25 is filled with working oil at a filling rate of 60 to 70% of its volume. However, the filling rate of the working oil is arbitrary. In the carrier cover 7, transmission oil is sealed for lubrication also in the space on the clutch part 23 side.

  The pressurizing piston cylinder part 24 includes a pressurizing cylinder 128 and a pressurizing piston 129. The pressure cylinder 128 is formed in a circular shape on the inner peripheral surface side of the clutch hub 79. The pressure piston 129 is disposed so as to fit into the pressure cylinder 128. The pressure piston 129 is provided with a seal 130 and is in close contact with the pressure cylinder 128. A pressure chamber 131 is formed between the pressure piston 129 and the pressure cylinder 128. The pressure chamber 131 communicates with the flow path 113. Therefore, the pressurizing piston cylinder portion 24, which is a fluid actuator, and the control valve 27 are directly connected by the flow path 113 provided on the rotation side.

  The pressurizing piston 129 is provided with a convex portion 133. The convex part 133 enters the cavity part 115 on the inner peripheral side of the pump part 23 with a gap. The convex portion 133 reduces the volume of the pressure chamber 131 so that the pressurizing piston 129 operates with good response to the discharge pressure of the pump portion 23. A thrust bearing 135 is interposed between the pressure piston 129 and the linkage support portion 82 of the clutch outer cylinder 77. The thrust bearing 135 reduces the pressure piston 129 from receiving a frictional force from the clutch outer cylinder 77 side, thereby suppressing a rotational difference from the clutch hub 79 and enabling rotation.

  The control valve 27 includes a pressure adjustment opening 137 and adjusts the operating pressure of the pressurizing piston cylinder portion 24 by adjusting the area of the pressure adjustment opening 137. The pressure adjustment opening 137 is formed of a plurality of openings 139, 141, and 143 in this embodiment. The opening 139 is formed relatively large, and the openings 141 and 143 are formed relatively small. The openings 139, 141, and 143 are connected in a direction along the rotation axis of the rotation shaft 11, and a plurality of openings are provided at predetermined intervals in the circumferential direction. The openings 139, 141, and 143 communicate with the shaft hole 116 through radial holes 145, 147, and 149.

  The control valve 27 includes a movable member 151. The movable member 151 is fitted to the rotary shaft 11 at the outer peripheral positions corresponding to the openings 139, 141, and 143, and is movable in the direction along the rotary axis of the rotary shaft 11 on the rotation side. By the movement of the movable member 151 (movement from left to right in FIG. 2), the opening 139, the opening 141, and the opening 143 are selectively opened in this order, and the area of the pressure adjustment opening 137 is adjusted. . By opening the openings 139, 141, 143 in this order, the hydraulic oil is first returned to the oil reservoir 25 by the large opening 139, and then the smaller openings 141, 143 are sequentially opened to the oil reservoir 25. The amount of hydraulic oil to be returned can be finely adjusted. Each of the openings 139, 141, 143 can be adjusted to the opening degree of each intermediate state with the movement of the movable member 151.

  The movable member 151 has an engagement groove 153 formed in a circular shape on the outer peripheral surface. A fork 155 is engaged with the engaging groove 153. The fork 155 is supported by the operation rod 157. One end of the operation rod 157 is movably supported by a support hole 159 provided in the intermediate wall 117 of the carrier cover 7, and the other end of the operation rod 157 passes through the support hole 161 provided in the carrier cover 7 and interlocks with the electromagnetic actuator 31. It is configured. Therefore, when the electromagnetic actuator 31 is driven via the controller by a button operation on the driver's seat, the operation rod 157 is operated to move in the axial direction. By this moving operation, the movable member 151 is interlocked via the fork 155. For this reason, the fork 155 and the operation rod 157 constitute a movement control means together with the electromagnetic actuator 31 and control the movement of the movable member 151. Moreover, the movable member 151 has a configuration in which movement can be arbitrarily controlled by an electromagnetic actuator 31 that is an actuator. However, the movable member 151 can be manually controlled to move by lever operation of the driver's seat without using an actuator.

  The rotating shaft 11 is rotatably supported by a support portion 13 of the carrier cover 7 by a ball bearing 163. A coupling flange 165 is spline-engaged with the outer end of the rotating shaft 11. The coupling flange 165 is fastened to the rotating shaft 11 by a nut 167 and is prevented from coming off. A seal 169 is provided between the coupling flange 165 and the carrier cover 7. The coupling flange 165 is coupled to the constant velocity joint 15.

  The drive pinion shaft 17 is rotatably supported on the bearing housing 173 of the differential carrier 9 by a unit bearing 171 having a pair of tapered rollers. The unit bearing 171 is fastened by a nut 175 that is screwed onto the drive pinion shaft 17. By this fastening, a preload (preload) is applied to the unit bearing 171.

  Next, the operation will be described.

  During normal travel, if there is no differential rotation between the rotary shaft 11 and the drive pinion shaft 17, the pump piston 95 side and the pump cam 93 side of the pump unit 23 rotate integrally, so the pump unit 23 does not work. No hydraulic oil pressure is generated. Therefore, the automobile can travel in a two-wheel drive state with the front wheels 73 and 75 as described above.

  When the front wheels 73 and 75 slip on rough roads or the like, a difference between the rotary shaft 11 and the drive pinion shaft 17 is caused by torque transmitted from the engine 65 to the front differential device 59, the transfer 46, the propeller shaft 5, and the rotary shaft 11. Dynamic rotation occurs. Due to this differential rotation, the pump piston 95 on the rotating shaft 11 side and the pump cam 93 on the drive pinion shaft 17 side relatively rotate. This relative rotation causes the pump piston 95 to reciprocate between the crest and trough of the pump cam 93. By this reciprocating operation, the pump unit 23 sucks the working oil in the suction preliminary chamber 102. The working oil in the oil reservoir 25 is introduced into the suction preliminary chamber 102 from the suction tube 127 when the pump unit 23 is operated. Accordingly, the working oil can be reliably sucked by the pump unit 23.

  The working oil sucked into the pump part 23 is discharged from the discharge port 109 into the cavity part 115 when the pump valve 111 is opened by the pressure in the pump cylinder 99.

  The pressure of the hydraulic oil discharged into the cavity 115 reaches the pressure chamber 131 of the pressurizing piston cylinder 24 and passes through the shaft hole 116 and the radial holes 145, 147, 149 and the openings 139, 141, 141. 143.

  When the movable member 151 does not move and all the openings 139, 141, 143 are closed, the pressure of the discharged hydraulic oil acts on the pressure piston 129. Due to this operating pressure, the pressurizing piston 125 moves, and the linkage support portion 82 of the clutch outer cylinder 77 receives a pressing force via the thrust bearing 135. By this pressing force, the entire clutch outer cylinder 77 moves toward the drive pinion shaft 17 in the direction along the rotation axis with respect to the drive pinion shaft 17. This movement is allowed by the spline engagement between the clutch outer cylinder 77 and the drive pinion shaft 17.

  As the clutch outer cylinder 77 moves, the pressing plate 89 receives a force from the snap ring 92 and moves in the same direction together with the clutch outer cylinder 77. Due to the movement of the pressing plate 89, the friction multi-plate clutch 87 is fastened between the pressing plate 89 and the pressure receiving plate 86.

  The torque transmitted to the rotating shaft 11 by the fastening according to the differential rotation of the friction multi-plate clutch 87 is transmitted from the clutch hub 79 to the clutch outer cylinder 77 via the friction multi-plate clutch 87. Torque is transmitted from the clutch outer cylinder 77 to the drive pinion shaft 17.

  Therefore, as described above, the vehicle is in a four-wheel drive state with the front wheels 73 and 75 and the rear wheels 41 and 43, and the front wheels 73 and 75 are slipped by transmitting torque to the rear wheels 41 and 43. The running ability of can be improved.

  The movable member 151 is controlled to move via the operation rod 157 and the fork 155 by driving the electromagnetic actuator 31 under the control of the controller. When the openings 139, 141, and 143 are sequentially opened by this control, the area of the pressure adjustment opening 137 is adjusted, and the amount of working oil returned from the shaft hole 116 side into the oil reservoir 25 is adjusted. By this adjustment, the pressure of the working oil supplied to the pressure chamber 131 is adjusted. As the opening 139 and the opening 141 are opened from the state in which only the opening 139 is opened, and further the state in which the opening 143 is opened, the pressure in the pressure chamber 131 decreases, and all the openings are opened. When 139, 141, 143 is opened, the pressure hardly acts on the pressure chamber 131. In the present embodiment, the movement control of the movable member 151 is performed according to the traveling state such as the vehicle speed.

  Thus, during high-speed turning, the electromagnetic actuator 31 is controlled to return more hydraulic oil from the pump unit 23 to the oil reservoir 25, the pressure in the pressure chamber 131 decreases, and the engagement force of the friction multi-plate clutch 87 is increased. Becomes smaller or almost zero. Therefore, even if there is a differential rotation between the rotary shaft 11 and the drive pinion shaft 17, little torque is transmitted from the rotary shaft 11 to the drive pinion shaft 17 or almost no two wheels are driven by the front wheels 73 and 75. Thus, stable high-speed turning can be performed.

  Even at an intermediate speed between the low-speed driving and the high-speed driving, the four-wheel drive can be accurately performed according to the driving state by the movement control of the movable member 151 by the electromagnetic actuator 31.

  Even when the friction multi-plate clutch 87 is engaged as described above at low speed, when the front wheels 73 and 75 are turning without slipping, the movable member 151 is detected by signals from the vehicle speed sensor and the steering angle sensor. Is controlled to release the pressure in the pressure chamber 131 to the oil reservoir 25 side, and the engagement of the friction multi-plate clutch 87 is released. By releasing the engagement of the friction multi-plate clutch 87, the so-called tight corner braking phenomenon can be eliminated, and the low-speed turning traveling can be performed smoothly.

  Further, the controller controls the electromagnetic actuator 31 according to the oil temperature based on the signal of the oil temperature sensor that detects the oil temperature of the working oil in the carrier cover 7, and the area of the pressure adjustment opening 137 by the movement of the movable member 151. The pressure feeding state to the pressure chamber 131 can be changed. By this adjustment, the hydraulic oil is pumped according to the oil temperature, and the engagement control of the friction multi-plate clutch 87 according to the rotation speed of the rotating shaft 11 can be more reliably performed.

  As described above, in the first embodiment of the present invention, the control valve 27 is provided on the rotating shaft 11 and the operating pressure of the pressurizing piston cylinder portion 24 is controlled by the control valve 27. The working oil can be circulated with the portion 24 on the rotation side, and the control function can be prevented from being lowered and the control response can be improved with a simple structure.

  Since the control valve 27 is provided on the rotating shaft 11, the control function of the pressurizing piston cylinder portion 24 provided on the rotating side of the rotating shaft 11 and the drive pinion shaft 17 is reliably suppressed with a simple structure. Thus, the control response can be improved with certainty.

  Since the pressurizing piston cylinder portion 24 and the control valve 27 are directly connected by the flow path 113 provided on the rotation side, the control response can be improved reliably.

  The control valve 27 includes a pressure adjustment opening 137 that communicates with the pressurization piston cylinder part 24, and controls the operating pressure of the pressurization piston cylinder part 24 by changing the area of the pressure adjustment opening 137. With a simple structure that changes the area of 137, it is possible to reliably suppress a decrease in the control function and to improve the control response reliably.

  The control valve 27 is formed of a plurality of openings 139, 141, 143 communicating with the pressurizing piston cylinder 24, and a movable member 151 that is movable in the direction along the rotation axis is provided on the rotation side. The movable member 151 selectively opens and closes the opening portions 139, 141, and 143 to change the opening area, so that the control function can be reliably lowered with a simple structure that changes the area by moving the movable member 151. And control response can be improved with certainty.

  One opening may be provided without providing a plurality of openings. In this case, pressure can be controlled by adjusting the opening area of the opening by moving the movable member.

  FIG. 4 is an enlarged cross-sectional view showing the control valve and its periphery according to the second embodiment of the present invention. The components corresponding to those of the first embodiment are denoted by the same reference numerals or symbols A, and the overall configuration of the four-wheel drive vehicle is shown in FIG. 1, and the overall configuration of the torque transmission device is shown in FIGS. I will explain.

  In this embodiment, the movement control means for controlling the movement of the movable member 151A is changed. The movement control means includes a ball 177 and a cam portion 179 and a coil spring 181 as urging means.

  The ball 177 is formed of steel or the like, and moves in the radial direction of rotation by the centrifugal force generated by the rotation of the rotary shaft 11A. The cam portion 179 receives a moving force in the direction along the axis of rotation due to the movement of the ball 177 and moves the movable member 151 </ b> A, and includes a receiving portion 183 and a movable portion 185. The receiving portion 183 and the movable portion 185 are both formed in a circular shape by a plate material such as steel, the outer peripheral portions are formed so as to gradually approach each other, and the opposing surfaces are formed as cam surfaces 187 and 189. The receiving portion 183 is fitted and fixed to the rotating shaft 11. The receiving portion 183 is positioned by engaging with a stopper 191 attached to the rotating shaft 11A. The movable part 185 is in contact with one end surface of the movable member 151A. The coil spring 181 is interposed between a stopper 193 attached to the rotating shaft 11A and the other end surface of the movable member 151A.

  When the automobile is traveling at a low speed, the input rotation to the rotating shaft 11A is low, and the ball 177 is positioned radially inward as shown in FIG. 4, and the movable member 151A has all of the openings 139, 141, and 143. close up.

  Therefore, when differential rotation occurs between the rotary shaft 11A and the drive pinion shaft 17 due to the input rotation, the friction multi-plate clutch 87 is fastened at a high pressure as described above.

  When the vehicle speed increases and the speed of the input rotation to the rotating shaft 11A increases, the centrifugal force acting on the ball 177 gradually increases according to the rotating speed of the rotating shaft 11A. Due to this centrifugal force, the ball 177 moves outward in the radial direction and increases the contact force against the cam surfaces 187 and 189. Due to an increase in the contact force of the ball 177 against the cam surfaces 187 and 189, the movable portion 185 moves to the movable member 151 </ b> A side against the biasing force of the coil spring 181 due to the reaction force from the receiving portion 183. By the movement of the movable member 151A, the openings 139, 141, and 143 are sequentially opened, and the working oil on the shaft hole 116 side is returned to the oil reservoir 25 side as described above. Since the movable member 151A moves in accordance with an increase in the centrifugal force acting on the ball 177 due to an increase in the vehicle speed, the openings 139, 141, and 143 are selectively opened sequentially in accordance with the increase in the vehicle speed. .

  Therefore, also in the present embodiment, the operating pressure of the pressurizing piston cylinder portion 24 is adjusted according to the vehicle speed, and the same effect as that of the first embodiment can be obtained. In the present embodiment, the movable member 151A can be reliably moved according to the input rotation without requiring a special drive source.

  5 and 6 relate to the third embodiment of the present invention, FIG. 5 is an enlarged sectional view showing the control valve and its periphery, and FIG. 6 is an enlarged sectional view of the spool valve. The components corresponding to those of the first embodiment are denoted by the same reference numerals or symbols B, and the overall configuration of the four-wheel drive vehicle is shown in FIG. 1, and the overall configuration of the torque transmission device is shown in FIGS. I will explain.

  In this example, the structure of the control valve was changed. The control valve 27B includes a spool valve 195 and a movable member 151B.

  The spool valve 195 includes a spool 197 and a sleeve 199.

  The spool 197 is movably supported in a spool support hole 201 provided in the rotating shaft 11B. The spool support hole 201 is provided in the radial direction perpendicular to the shaft hole 116 of the rotating shaft 11B. In the spool 197, a spring seat 205 is provided around the small diameter portion 203, and a return spring 207 is interposed between the spring seat 205 and the bottom portion of the spool support hole 201. A front end 209 of the spool 197 is formed in a spherical shape and protrudes out of the spool support hole 201 by the urging force of the return spring 207.

  The sleeve 199 includes the shaft hole 116 and a second shaft hole 211 having a smaller diameter than the shaft hole 116. One end of the second shaft hole 211 is a pressure adjustment opening 137B. The second shaft hole 211 is formed to communicate with the radial hole 213. The radial holes 213 pass through the rotary shaft 11 </ b> B, and both ends are open to the oil reservoir 25.

  The movable member 151 </ b> B is provided corresponding to the spool 197. A slope 215 is provided on the movable member 151B. The tip 209 of the spool 197 is in contact with the slope 215. The movement control means for controlling the movement of the movable member 151B is configured in the same manner as in the first embodiment. Therefore, the movable member 151B is provided with an engagement groove 153B that engages the fork 155.

  Therefore, in the state of FIG. 5 in which the movable member 151B is not moved and the lower end side of the inclined surface 215 is in contact with the tip 209 of the spool 197, the pressure adjustment opening 137B is closed by the spool 197, and the high pressure as described above. Thus, the friction multi-plate clutch 87 is engaged.

  When the movable member 151B is controlled to move according to the increase in the vehicle speed or the like, the slope 215 of the movable member 151B moves relative to the spool 197, and the tip 209 of the spool 197 is in contact with the higher side of the slope 215. Changes. Due to this change, the spool 197 is urged and moved by the return spring 207, and the pressure adjustment opening 137B is opened according to the increase in the vehicle speed or the like, and the area thereof is adjusted. Therefore, the working oil flows from the shaft hole 116 to the second shaft hole 211 according to the opening area of the pressure adjustment opening 137B, and the working oil is returned from the radial hole 213 to the oil reservoir 25.

  Therefore, also in the present embodiment, the operating pressure of the pressurizing piston cylinder portion 24 is adjusted according to the vehicle speed, and the same effect as that of the first embodiment can be obtained. Further, in this embodiment, a simple structure in which the area of the pressure adjustment opening is changed via the spool valve 195 by the movement of the movable member 151B can reliably suppress the deterioration of the control function and improve the control response with certainty. it can.

  In addition, the torque transmission apparatus of each said Example can also be provided in the input side to the front differential apparatus used as the to-be-driven side of a four-wheel drive vehicle. In this case, the torque transmitted to the front wheels can be controlled according to the input rotation, and the driving state over the two-wheel driving state and the four-wheel driving state can be reliably controlled.

  The torque transmission device of each of the embodiments can be provided in a differential device of a four-wheel drive vehicle. In this case, the state of torque transmission to the left and right axle shafts can be changed to control the transmission torque to the left and right wheels according to the left and right differential rotation, and the external control of the clutch part can be easily performed with a simple structure. It can be carried out.

  Further, the torque transmission device of each of the embodiments can be provided as the torque transmission device 1A on the output shaft 47 of the transfer 46 in FIG.

In each of the above-described embodiments, the operation unit of the operation control device is provided as a clutch unit of an automobile. However, for example, a switching mechanism unit that switches a shift state of a transmission gear or a shift state continuously using, for example, a metal belt or toroidal It is also possible to provide a switching mechanism that switches the shift state of the continuously variable transmission that can be changed.

  In each of the above-described embodiments, a radial piston pump having a piston movable in the rotational radius direction with respect to the uneven portion as the pump portion has been described. However, the rotating shaft is formed with respect to the uneven portion formed in the circumferential direction facing the rotational axis direction. An axial piston pump having a piston movable in the direction may be used, and the other pump unit may be an internal or external gear or internal gear pump, a vane pump, or a trochoid pump.

(Example 1) which is a skeleton top view of a four-wheel drive vehicle. (Example 1) which is a longitudinal cross-sectional view which shows the attachment state of a torque transmission apparatus. (Example 1) which is an expanded sectional view of the principal part. (Example 2) which is an expanded sectional view which shows a control valve and its periphery. (Example 3) which is an expanded sectional view which shows a control valve and its periphery. (Example 3) which is an expanded sectional view of a spool valve. It is a longitudinal cross-sectional view which shows the attachment state of a torque transmission apparatus (conventional example).

Explanation of symbols

1,1B Torque transmission device (motion control device)
11, 11A, 11B Rotating shaft (first rotating member)
17 Drive pinion shaft (second rotating member)
21 Clutch part (operation part)
23 Pump part 24 Pressure piston cylinder part (fluid actuator)
27, 27A, 27B Control valve 93 Pump cam (uneven portion)
95 Pump piston (reciprocating body)
129 Pressure piston 131 Pressure chamber 137, 137B Pressure adjustment opening 139, 141, 143 Opening 151, 151A, 151B Movable member

Claims (14)

First and second rotating members on the rotating side for transmitting torque;
A pump unit that generates a pressure of the working fluid in response to differential rotation between the first and second rotating members;
A fluid actuator provided on the rotating side and operating in accordance with the pressure of the working fluid;
An operation unit that operates according to the fluid actuator,
A control valve is provided on the rotation side,
An operation control apparatus for controlling an operation pressure of the fluid actuator by controlling the control valve. The operation control apparatus according to claim 1,
The operation control device, wherein the control valve is provided on one of the first and second rotating members. The operation control device according to claim 1 or 2,
An operation control apparatus, wherein the fluid actuator and the control valve are directly connected by a flow path provided on the rotation side. The operation control device according to claim 1,
The control valve includes a pressure adjustment opening communicating with the fluid actuator,
An operation control apparatus for controlling an operation pressure of the fluid actuator by changing an area of the pressure adjustment opening. The operation control device according to claim 4,
The pressure adjustment opening is formed with a plurality of openings communicating with the fluid actuator, and includes a movable member movable in a direction along a rotation axis on the rotation side,
The operation control device according to claim 1, wherein the movable member selectively opens and closes the opening to change the area. The operation control device according to claim 5,
The control valve includes a spool valve capable of changing an area of the pressure adjustment opening on the rotation side and a movable member movable in a direction along the rotation axis.
An operation control apparatus for adjusting the spool valve by movement of the movable member. The operation control device according to claim 4,
A movable member for adjusting an opening area of the pressure adjustment opening;
An operation control device comprising movement control means for controlling movement of the movable member. The operation control device according to claim 7,
The movement control means controls the movement of the movable member manually or by an actuator. The operation control device according to claim 7,
The movement control means is provided on the rotation side and moves by the centrifugal force due to the input rotation on the rotation side, and receives the movement force in the direction along the rotation axis by the movement of the ball, and moves the movable member. An operation control device comprising a cam portion to be performed and an urging means for returning the movement. The operation control device according to claim 1,
The pump part is supported by the circumferential uneven part formed on one side of the first and second rotating members and the other side, is in contact with the uneven part, and reciprocates by relative rotation with the uneven part. It has a reciprocating body that pumps working fluid,
The fluid actuator includes a pressurizing piston that is supported on the other side of the first and second rotating members and forms a pressure chamber with the other side.
An operation control device, characterized in that the working fluid pumped by the pump unit is supplied to the pressure chamber. The operation control apparatus according to any one of claims 1 to 10,
The operating unit is a clutch unit that changes a torque transmission state between the first and second rotating members, a switching mechanism unit that switches a transmission state of the transmission gear, or a continuously variable gear that can continuously change the transmission state. An operation control device that is a switching mechanism that switches a shift state of a transmission. The operation control device according to claim 11,
The clutch control unit controls a torque transmission state between a two-wheel drive state and a four-wheel drive state of a four-wheel drive vehicle. The operation control device according to claim 11 or 12,
The operation control device according to claim 1, wherein the clutch portion is provided on an input side to a driven differential device of a four-wheel drive vehicle or on an output side of a transfer. The operation control device according to claim 11 or 12,
The clutch control unit is provided in a differential device of a four-wheel drive vehicle, and changes the state of torque transmission to the left and right axle shafts.

Images