JP5012667B2 - Power transmission device - Google Patents

Power transmission device Download PDF

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Publication number
JP5012667B2
JP5012667B2 JP2008141355A JP2008141355A JP5012667B2 JP 5012667 B2 JP5012667 B2 JP 5012667B2 JP 2008141355 A JP2008141355 A JP 2008141355A JP 2008141355 A JP2008141355 A JP 2008141355A JP 5012667 B2 JP5012667 B2 JP 5012667B2
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oil
oil pump
passage
pump
discharge
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JP2009287688A (en
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広行 塩入
信也 桑原
直志 藤吉
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トヨタ自動車株式会社
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Description

  The present invention relates to a power transmission device that performs power transmission between a first rotating member and a second rotating member, and discharges oil by the relative rotation of the first rotating member and the second rotating member. It is.

  Conventionally, a power source is mounted on a vehicle, and a power transmission device is disposed on the output side of the power source. As this power transmission device, a hydraulic control type power transmission device and an electromagnetic control type power transmission device are known. As a hydraulic control type power transmission device, for example, it is necessary to suck and discharge a working fluid. There is a radial piston pump to be supplied to the part, which is described in Patent Document 1 below.

  The power transmission device described in Patent Document 1 is driven by an input member and an output member where power transmission is performed, power transmitted between the input member and the output member, and the first rotating member. An oil pump that discharges oil by rotating relative to the second rotating member, and connects the input member and the first rotating member so as to be able to transmit power, and enables transmission of power between the output member and the second rotating member. A transmission member that connects the first rotation member and the second rotation member so as to be able to transmit power is provided and connected between the first rotation member and the second rotation member by controlling the oil discharge amount of the oil pump. And a flow rate control valve for controlling the rotational speed difference.

JP 2005-256960 A

  In the above-described conventional power transmission device, the first rotary member of the oil pump is connected to the crankshaft of the engine, the input shaft is connected to the second rotary member, and the oil discharge amount of the oil pump is controlled by the control valve. Thus, the relative rotational speed difference between the first rotating member and the second rotating member is controlled. That is, the oil pump can discharge a predetermined amount of oil according to the relative rotational speed difference between the crankshaft of the engine and the input shaft.

  By the way, when the vehicle starts, since the relative rotational speed difference between the first rotating member and the second rotating member is large, the oil pump sucks and discharges a large amount of oil. It becomes difficult to inhale. Therefore, it is difficult for the piston to follow the cam, and there is a possibility that a collision sound between the piston and the cam may be generated or pulsation may be generated in the oil. In addition, since the oil pump generates hydraulic pressure in accordance with the engine load, it is difficult to secure an excessive hydraulic pressure when the engine load is small.

  An object of the present invention is to provide a power transmission device that improves pump performance by ensuring a necessary hydraulic pressure regardless of the rotational speed difference between the first rotating member and the second rotating member.

In order to solve the above-described problems and achieve the object, a power transmission device of the present invention includes an input member and an output member to which power transmission is performed, a first rotating member connected to the input member and the output member, and And a first oil pump that discharges oil by relative rotation of the second rotating member. The first oil pump is connected to the second oil pump on the suction side, and on the discharge side is high-pressure oil. A supply unit is connected; the second oil pump is connected to a low-pressure oil supply unit on a discharge side; a first oil circulation passage is provided to connect a discharge side and a suction side of the first oil pump; The discharge state of the first oil pump is controlled by controlling the amount of oil circulation from the discharge side of the first oil pump to the suction side based on the operating state of the vehicle in the first oil circulation passage. The first control valve is provided which, it is characterized in.

  In the power transmission device of the present invention, a second oil circulation passage that connects the discharge side and the suction side of the second oil pump is provided, and the second oil circulation passage is controlled based on the operating state of the vehicle. A second control valve for controlling the discharge state of the second oil pump is provided.

  In the power transmission device of the present invention, a switching valve for switching the connection destination of the first oil pump between the second oil pump and the oil reservoir is provided, and the switching valve is controlled according to a driving state of the vehicle. Thus, the connection destination of the first oil pump is switched.

  In the power transmission device of the present invention, the second oil pump is an electric pump, and the switching valve is controlled according to the operating state of the vehicle and the rotation speed of the electric pump is controlled.

  In the power transmission device of the present invention, an oil communication path that connects the discharge side of the first oil pump and the discharge side of the second oil pump is provided, and the oil communication path is controlled based on the operating state of the vehicle. Thus, a third control valve for controlling the oil supply state to the low-pressure oil supply unit is provided.

  In the power transmission device of the present invention, the third control valve has a switching valve that switches a communication cut-off state of the oil communication passage according to a discharge pressure of the second oil pump.

  In the power transmission device of the present invention, the input member and the first rotating member are connected so as to be able to transmit power, the output member and the second rotating member are connected so as to be able to transmit power, and the first rotating member is connected to the first rotating member. While the cam is provided, the second rotating member is provided with a piston that is movable in the radial direction so as to face the cam, and the piston is pressed by the pressing member so as to contact the cam, The two-rotating member is provided with a fluid chamber whose volume is enlarged or reduced as the piston moves, and the fluid chamber is provided with an oil suction passage through which oil is sucked and an oil discharge passage through which oil is discharged. The second oil pump is connected to the first oil pump, and the first control valve controls the oil discharge state from the oil discharge passage in the first oil pump, so that the first rotation is performed. Controlling the power transmission state between the said and the wood second rotating member.

According to the power transmission device of the present invention, the first oil pump that discharges oil by the relative rotation of the first rotating member and the second rotating member connected to the input member and the output member, and the second oil pump on the suction side. On the other hand, a high pressure oil supply unit is connected to the discharge side, a low pressure oil supply unit is connected to the discharge side by a second oil pump, and a first oil is connected to the discharge side and the suction side of the first oil pump. A circulation passage is provided, and a discharge state of the first oil pump is controlled by controlling an oil circulation amount from the discharge side of the first oil pump to the suction side based on the operation state of the vehicle in the first oil circulation passage. One control valve is provided . Therefore, since the first oil pump sucks and discharges the oil discharged from the second oil pump and supplies the oil to the high pressure oil supply unit, the first oil pump is concerned with the difference in rotational speed between the first rotating member and the second rotating member. In addition, it is possible to improve the pump performance by ensuring the necessary hydraulic pressure.

  Embodiments of a power transmission device according to the present invention will be described below in detail with reference to the drawings. In addition, this invention is not limited by this Example.

  1 is a schematic configuration diagram illustrating a power transmission device according to a first embodiment of the present invention, FIG. 2 is a schematic configuration diagram illustrating a vehicle drive transmission system to which the power transmission device according to the first embodiment is applied, and FIG. FIG. 4 is a schematic cross-sectional view of an oil pump in the power transmission device according to the first embodiment, FIG. 4 is a cross-sectional view along IV-IV in FIG. 3, and FIG. 5 is a schematic diagram illustrating discharge hydraulic pressure by the power transmission device according to the first embodiment.

  In the vehicle drive transmission system to which the power transmission device of the first embodiment is applied, as shown in FIG. 2, an engine 11 as a prime mover is provided, and a damper device 13 is provided on a crankshaft 12 of the engine 11. The input shaft 14 is connected via the engine shaft, and the engine torque is transmitted to the input shaft 14.

  As for the input shaft 14, the primary shaft 15 is supported by the outer peripheral side via several bearing 16a, 16b, 16c, 16d so that relative rotation is possible. The input shaft 14 and the primary shaft 15 are disposed in the casing 17. The casing 17 is configured by a front case 18, a center case 19, and a rear case 20 being coupled and fixed by a connecting bolt (not shown). The front case 18, the center case 19, and the rear case 20 are provided with partition walls 18a, 19a, 20a, and 20b continuous on the inner surface, and bearings 21a, 21b, and 21c are provided on the partition walls 18a, 19a, 20a, and 20b. The primary shaft 15 is rotatably supported through the intermediate shaft 15.

  A first storage chamber A1 is formed in the space surrounded by the partition walls 20a and 20b of the rear case 20 inside the casing 17. The power transmission device 22 of the present embodiment is disposed in the first storage chamber A1. The power transmission device 22 includes a first oil pump 101 configured by a radial piston pump and a second oil pump 102 configured by a gear pump. In this embodiment, the second oil pump 102 is a pump that is driven in synchronization with the engine 11, and the oil discharge capacity of the second oil pump 102 is set to be smaller than the oil discharge capacity of the first oil pump 101. ing. A second oil pump 102 is connected in series to the suction side of the first oil pump 101.

  As shown in FIGS. 3 and 4, the second oil pump 102 has a pump cover 92 fixed to the pump body 91 to form a housing case, and gears 93 and 94 are rotatably housed therein. A pump cover 92 of the second oil pump 102 is fixed to the partition wall 20b of the rear case 20, and a cylindrical sleeve 23 is rotatably supported on the pump body 91 via a bearing 16d. In the sleeve 23, a circular rotating plate 24 is fixed to the flange portion 23a, and a cylindrical first rotating member 25 is fixed to the rotating plate 24. A cam 26 is provided on the inner peripheral surface of the first rotating member 25. The cam 26 is formed so that the first cam surfaces 26a and 26c and the second cam surfaces 26b and 26d opposed to each other in the radial direction are alternately arranged in the circumferential direction so as to be smoothly continuous. In this case, the distance from the central axis O of the first rotating member 25 to the first cam surfaces 26b, 26d is longer than the distance from the central axis O of the first rotating member 25 to the second cam surfaces 26a, 26c. Is set to

  A rotary valve 27 is coupled to the rotary plate 24, and an end plate 28 formed integrally with the end portion of the input shaft 14 is fitted to the outer peripheral surface of the rotary valve 27 and integrally coupled. Yes.

  The rotary valve 27 is formed with a first communication hole 29 in the center from one end face, and two second communication holes 30 a and 30 b on the outer peripheral side of the first communication hole 29. The cylindrical holder 31 is inserted through the sleeve 23, and one end is fitted and fixed to the first communication hole 29, so that the oil is discharged from the holder 31 to the first communication hole 29. An oil passage (oil discharge passage) 32 is formed, and an oil suction oil passage (oil suction passage) 33 that communicates between the sleeve 23 and the holder 31 to the second communication holes 30 a and 30 b is formed. The pump cover 92 is formed with an oil suction port 95, and the pump body 91 is formed with a discharge port 96 communicating with the suction oil passage 33.

  The rotary valve 27 has four connecting grooves 34a, 34b, 34c, 34d formed on the outer peripheral surface along the circumferential direction. The first communication hole 29 and the connecting grooves 34a, 34c are connected to the connecting holes 35a, 35c. On the other hand, the second communication holes 30a and 30b and the connection grooves 34b and 34d communicate with each other through the connection holes 35b and 35d.

  The rotary valve 27 is rotatably fitted with a cylindrical second rotating member 36 on its outer peripheral surface. The second rotating member 36 is formed with eight cylinders 37 a to 37 h opened outward at equal intervals in the circumferential direction on the outer peripheral portion, and pistons 38 a to 38 h are formed in the cylinders 37 a to 37 h with the diameter of the rotary valve 27. It is supported movably along the direction. Rollers 39a to 39h are attached to the tip portions of the pistons 38a to 38h, and the rollers 39a to 39h are rotatably supported around an axis parallel to the axial direction of the rotary valve 27. In addition, compression coil springs 40a to 40h as pressing portions are interposed in the cylinders 37a to 37h, and the compression coil springs 40a to 40h are urged by the rollers 39a to 37h of the cylinders 37a to 37h. 39h is pressed to come into contact with the cam surfaces 26a, 26b, 26c, and 26d of the cam 26.

  That is, the pistons 38a to 38h are arranged to face the cam 26 of the first rotating member 25 in the radial direction, and the rollers 39a to 39h are driven by the urging forces of the compression coil springs 40a to 40h. 26b, 26c, and 26d are in contact. And between each piston 38a-38h and each cylinder 37a-37h, the sealed oil chamber 41a-41h is formed, and when the 1st rotation member 25 and the 2nd rotation member 36 rotate relatively, The pistons 38a to 38h are reciprocated by the cam surfaces 26a, 26b, 26c, and 26d via the rollers 39a to 39h, so that the volumes of the oil chambers 41a to 41h are enlarged or reduced. The oil chambers 41a to 41h can communicate with the connection grooves 34a to 34d through the connection holes 42a to 42h.

  A cylindrical connecting tube 43 is fixed to one flat surface portion of the second rotating member 36. On the other hand, a disc-shaped support plate 44 is rotatably supported on the partition wall 20a of the rear case 20 via a bearing 21c, and an end portion of a cylindrical output shaft 45 is formed in the through hole 44a of the support plate 44. They are fitted and joined together by a joining member 46. And the outer peripheral part of the flange part 44b integrally formed in the support plate 44 is fitted by the spline 47 with respect to the inner peripheral part of the connection cylinder 43, and the connection cylinder 43 and the support plate 44, that is, the second rotating member. 36 and the output shaft 45 are connected so as to be integrally rotatable. A bearing 48 is interposed between the other flat portion of the second rotating member 36 and the rotating plate 24, and a bearing 49 is interposed between the connecting cylinder 43 and the support plate 44, and the input shaft 14. And an output shaft 45 is provided with a bearing 16c.

  As shown in FIG. 2, the second storage chamber A <b> 2 is formed in the space surrounded by the partition wall 19 a of the center case 19 and the partition wall 20 a of the rear case 20, inside the casing 17. A forward / reverse switching device 51 is disposed in the second storage chamber A2. The forward / reverse switching device 51 switches the rotation direction of the primary shaft 15 between the normal rotation direction and the reverse rotation direction with respect to the rotation direction of the output shaft 45, and between the engine 11 and the power transmission device 22. Is arranged.

  The forward / reverse switching device 51 has a planetary gear mechanism, specifically, a single pinion type planetary gear mechanism. That is, the planetary gear mechanism includes a sun gear 52, a ring gear 53 coaxially arranged with the sun gear 52, a plurality of pinion gears 54 meshing with the sun gear 52 and the ring gear 53, and the pinion gear 54 can rotate and revolve. It comprises a carrier 55 that supports it. The sun gear 52 is drivingly connected to the primary shaft 15, and the ring gear 53 is drivingly connected to the output shaft 45. In addition, a forward clutch 56 for controlling the connection and release of the rotating elements constituting the forward / reverse switching device 51 is provided, and a reverse brake 57 for controlling the rotation and stop of the rotating elements is provided. The forward clutch 56 can control the connection and release of the sun gear 52 and the ring gear 53, and the reverse brake 57 can control the rotation and stop of the carrier 55.

  In addition, a friction clutch, an electromagnetic clutch, a meshing clutch, or the like can be applied as the forward clutch 56, and a friction brake, an electromagnetic brake, a meshing brake, or the like can be applied as the reverse brake 57. When applying a friction clutch, a mesh clutch, a friction brake or a mesh brake, a hydraulically controlled actuator is used, and when applying an electromagnetic clutch or an electromagnetic brake, an electromagnetically controlled actuator is used. In this embodiment, a friction clutch (meshing clutch) and a friction brake (meshing brake) are controlled using a hydraulically controlled actuator.

  Further, a third storage chamber A3 is formed in the space inside the casing 17 and surrounded by the partition wall 18a of the front case 18 and the partition wall 19a of the center case 19. A continuously variable transmission 58 is disposed in the third storage chamber A3. The continuously variable transmission 58 is used to change the rotational speed of the primary shaft 15 continuously and transmit it to the secondary shaft 59, and is disposed between the engine 11 and the forward / reverse switching device 51.

  The continuously variable transmission 58 is a belt-type continuously variable transmission, and includes the primary shaft 15 and the secondary shaft 59 described above. The primary shaft 15 and the secondary shaft 59 are separated from each other by the partition walls 18a and 19a. Is supported rotatably. A primary pulley 60 is provided on the primary shaft 15 so as to be integrally rotatable, and a secondary pulley 61 is provided on the secondary shaft 59 so as to be integrally rotatable. An endless belt 62 is wound around the primary pulley 60 and the secondary pulley 61.

  The primary pulley 60 has a fixed sheave 60a that is integral with the primary shaft 15 and a movable sheave 60b that is movable in the axial direction of the primary shaft 15, and an endless belt 62 is wound around the sheave. A first hydraulic servo mechanism 63 that moves the movable sheave 60b in the axial direction of the primary shaft 15 to approach and separate from the fixed sheave 60a is provided. On the other hand, the secondary pulley 61 has a fixed sheave 61a that is integral with the secondary shaft 59 and a movable sheave 61b that is movable in the axial direction of the secondary shaft 59, and an endless belt 62 is wound around this. A second hydraulic servo mechanism 64 that moves the movable sheave 61b in the axial direction of the secondary shaft 59 to approach and separate from the fixed sheave 61a is provided. By changing the engagement positions of the primary pulley 60 and the secondary pulley 61 with respect to the belt 62 by the hydraulic servo mechanisms 63 and 64, the transmission gear ratio can be changed continuously.

  Further, a gear transmission 65 for transmitting the torque of the secondary shaft 59 and a differential 66 are provided inside the casing 17, and wheels 68 are connected to the differential 66 via a drive shaft 67. .

  By the way, as shown in FIGS. 1 and 2, the vehicle is provided with an electronic control unit (ECU) 71 for overall control of the vehicle. That is, an ignition switch 72, an accelerator opening sensor 73, a brake stroke sensor 74, an engine speed sensor 75, a throttle opening sensor 76, an input shaft 14 speed sensor 77, a primary shaft 15 speed sensor 78, and a secondary shaft 59 The rotation speed sensor 79 and the shift position sensor 80 are provided, and this detection signal is input to the ECU 71.

  Further, the vehicle is provided with a hydraulic control device 81 that controls the first oil pump 101, the second oil pump 102, the forward / reverse switching device 51, the continuously variable transmission 58, and the like, which can be controlled by the ECU 71. It has become. That is, as shown in FIGS. 1 to 4, the oil reservoir (for example, oil pan) 82 is connected to the suction port 96 of the second oil pump 102 via the oil suction passage 83. The discharge port 96 of the second oil pump 102 is connected to the oil suction oil passage 33 of the first oil pump 101 via the oil connection passage 84. The oil discharge oil passage 32 of the first oil pump 101 is connected to a hydraulic control device 81 via an oil discharge passage 85, and an oil supply unit (for example, a forward / reverse switching device 51) is connected to the hydraulic control device 81. And an oil supply passage 87 that is connected to the hydraulic control unit 86 of the continuously variable transmission unit 58 and the like.

  The hydraulic control device 81 has a first control valve (flow rate adjusting valve) 88 that controls the first oil pump 101. That is, a first oil circulation passage 89 that connects an oil discharge passage 85 connected to the discharge side of the first oil pump 101 and an oil connection passage 84 connected to the suction side of the first oil pump 101 is provided. A first control valve 88 is provided in the first oil circulation passage 89. The hydraulic control device 81 controls the oil discharge amount of the first oil pump 101 by controlling the first control valve 88 based on the driving state of the vehicle.

  That is, when the first and second oil pumps 101 and 102 are operated by driving the engine 11, the second oil pump 102 sucks the oil in the oil reservoir 82 through the oil suction passage 83 and pressurizes the oil inside. Low pressure oil is discharged into the oil connecting passage 84. Then, the first oil pump 101 sucks the low-pressure oil in the oil connection passage 84, pressurizes the oil into the high-pressure oil, and discharges it to the oil discharge passage 85. At this time, the hydraulic control device 81 controls the first control valve 88 according to the driving state of the vehicle, that is, the required amount of oil. That is, when the first control valve 88 is closed, the entire amount of oil discharged Q1 by the first oil pump 101 is supplied to the oil supply unit 86 via the oil discharge passage 85 and the oil supply passage 87. On the other hand, when the first control valve 88 is opened, an amount Q1-Q2 corresponding to the opening degree of the first control valve 88 is connected to the oil discharge amount Q1 by the first oil pump 101 through the first oil circulation passage 89. The remaining amount Q2 is returned to the passage 84 and supplied to the oil supply portion 86 via the oil discharge passage 85 and the oil supply passage 87.

  Here, the operation of the power transmission device 22 of the above-described embodiment will be described in detail.

  In the power transmission device 22 of the present embodiment, when the torque of the engine 11 is transmitted from the crankshaft 12 to the input shaft 14 via the damper device 13, as shown in FIGS. Is transmitted from the rotary valve 27 of the first oil pump 101 to the first rotating member 25 via the rotating plate 24. At this time, in the cylinders 37a to 37h that communicate with the discharge side, the torque of the first rotating member 25 is transmitted from the cam 26 to the second rotating member 36 via the pistons 38a to 38h by the internal high-pressure oil. It can be transmitted from the second rotating member 36 to the output shaft 45 via the support plate 44.

That is, in the first oil pump 101, the first rotating member 25 and the second rotating member 36 rotate clockwise in FIG. 4 (the direction indicated by the arrow in FIG. 4), and the rotation speed V of the first rotating member 25 is increased. When 1 is larger than the rotation speed V 2 of the second rotation member 36, the second rotation member 36 rotates relative to the first rotation member 25 in the counterclockwise direction. Therefore, for example, from the state shown in FIG. 4, in the piston 38f, the roller 39f rolls from the cam surface 26d toward the cam surface 26a, moves outward from the cylinder 37f, and the oil chamber 41f expands. At this time, the oil chamber 41f communicates with the coupling hole 42f, the coupling groove 34b, the coupling hole 35b, the second communication hole 30a, and the oil suction oil passage 33. On the other hand, from the state shown in FIG. 4, for example, since the roller 39h rolls from the cam surface 26a toward the cam surface 26b, the piston 38h moves inward of the cylinder 37h and the oil chamber 41h contracts. At this time, the oil chamber 41h communicates with the coupling hole 42h, the coupling groove 34a, the coupling hole 35a, the first communication hole 29, and the oil discharge oil passage 32.

  In this case, when the oil chamber 41f is enlarged, a suction force acts from the oil chamber 41f to the oil suction oil passage 33, while the oil chamber 41h contracts, so that the oil chamber 41h is changed to the oil discharge oil passage 32. A compression force acts. Therefore, the low pressure oil discharged from the second oil pump 102 to the oil connection passage 84 flows into the oil suction oil passage 33 of the first oil pump 101 and is sucked into the oil chamber 41f. On the other hand, the oil in the oil chamber 41 h flows from the oil discharge oil passage 32 to the oil discharge passage 85, flows to the oil supply portion 86 through the oil supply passage 87 by the hydraulic control device 81, and part flows to the first oil circulation passage 89. .

  At this time, when the first control valve 88 is fully opened, the flow rate of the oil flowing through the first oil circulation passage 89 is not limited, the flow resistance is small, and the oil discharged from the oil chamber 41h to the oil discharge passage 85 The flow resistance is small. Therefore, when the roller 39h of the piston 38h rolls from the cam surface 26a toward the cam surface 26b, the resistance when the piston 38h moves inward of the cylinder 37h is small, and the first rotating member 25 and the second rotating member 36, that is, the rotational speed difference between the input shaft 14 and the output shaft 45 increases.

  On the other hand, when the opening degree of the first control valve 88 is gradually reduced, the flow resistance of oil flowing through the first oil circulation passage 89 increases, and the flow of oil discharged from the oil chamber 41h to the oil discharge passage 85 is increased. The resistance also increases, the resistance when the piston 38h moves inward of the cylinder 37h increases, and the rotational speed difference between the input shaft 14 and the output shaft 45 decreases. That is, the first oil pump 101 can also function as a starting device by adjusting the opening of the first control valve 88.

  Further, when the first control valve 88 is fully closed, the flow rate of oil flowing through the first oil circulation passage 89 becomes 0, and all the oil discharged from the first oil pump 101 is supplied to the oil supply unit 86.

  In the above description of the operation of the first oil pump 101, only the operations of the piston 38f, the roller 39f, the cylinder 37f, the oil chamber 41f, the piston 38h, the roller 39h, the cylinder 37h, and the oil chamber 41h have been described. The pistons 38a to 38h, rollers 39a to 39h, cylinders 37a to 37h, and oil chambers 41a to 41h are operated in the same manner by the cam 26.

  In the present embodiment, the second oil pump 102 pressurizes the oil into low-pressure oil, and the first oil pump 101 sucks in the low-pressure oil, pressurizes it, and supplies it to the oil supply unit 86 as the high-pressure oil. Yes. Therefore, as shown in FIG. 5, when only one oil pump has been conventionally used, the upper limit value of the discharge pressure is p1, but as in this embodiment, the first and second oil pumps 101, 102 are used. Is used, the upper limit value of the discharge pressure can be increased to p3 (p1 + p2). Therefore, the first oil pump 101 can supply high-pressure oil to the oil supply unit 86.

  Thereafter, when the torque of the input shaft 14 is transmitted to the output shaft 45 through the first oil pump 101, the torque of the output shaft 45 is transmitted to the continuously variable transmission 58 via the forward / reverse switching device 51, and is set here. The vehicle is decelerated or accelerated at a predetermined gear ratio. The torque decelerated or increased by the continuously variable transmission 58 is transmitted to the differential 66 through the gear transmission 65 and is transmitted to the wheels 68 through the drive shaft 67.

  As described above, in the power transmission device according to the first embodiment, the input shaft 14 and the output shaft 45 that perform power transmission are provided, and are driven by the power transmitted between the input shaft 14 and the output shaft 45. A first oil pump 101 that discharges oil by providing relative rotation between the first rotating member 25 and the second rotating member 36 is provided, and the second oil pump 102 is connected to the suction side of the first oil pump 101 while discharging. An oil supply unit 86 is connected to the side.

  Therefore, since the first oil pump 101 sucks the low-pressure oil discharged from the second oil pump 102, discharges it as high-pressure oil, and supplies it to the oil supply unit 86, the first rotation member regardless of the driving state of the vehicle. Even if the rotational speed difference between the second rotating member 25 and the second rotating member 36 is large, the oil pressure necessary for the oil supply unit 86 can be secured, and the pump performance can be improved.

  That is, since the discharge pressure of the second oil pump 102 acts as the suction pressure of the first oil pump 101, the oil suction input of the first oil pump 101 increases, and a sufficient amount of oil is sucked into each of the oil chambers 41a to 41h. The rollers 39a to 39h can appropriately follow the cam 26 and operate. Therefore, noise, vibration, and hydraulic pressure fluctuation due to the collision between the cam 26 and the rollers 39a to 39h can be prevented. In addition, since the discharge pressure of the first oil pump 101 increases by the discharge pressure of the second oil pump 102, it is possible to ensure a higher oil discharge pressure regardless of the input torque of the crankshaft 12 in the engine 11. it can. Accordingly, it is possible to ensure a relative rotational speed difference between the first rotating member 25 and the second rotating member 36 at the time of starting, and to secure a necessary oil pressure when the engine 11 is under a low load.

  In the power transmission device according to the first embodiment, the first oil circulation passage 89 that connects the discharge side and the suction side of the first oil pump 101 is provided, and the first oil circulation passage 89 is provided based on the operating state of the vehicle. The 1st control valve 88 which controls the discharge state of the 1st oil pump 101 by controlling is provided. Therefore, the oil discharge dormitory from the first oil pump 101 can be easily adjusted by controlling the opening degree of the first control valve 88 based on the driving state of the vehicle.

  In the power transmission device according to the first embodiment, the input shaft 14 is connected to the first rotating member 25, the output shaft 45 is connected to the second rotating member 36, and the first rotating member 25 and the second rotating member 36 are connected to each other. The pistons 38a to 38h reciprocate due to the difference in rotational speed, and the pressure of the fluid chambers 41a to 41h varies, so that oil is sucked and discharged. Therefore, it is possible to ensure an appropriate oil discharge amount based on the rotational speed difference between the first rotating member 25 and the second rotating member 36.

  FIG. 6 is a schematic configuration diagram illustrating a power transmission device according to a second embodiment of the present invention. In addition, the same code | symbol is attached | subjected to the member which has the same function as what was demonstrated in the Example mentioned above, and the overlapping description is abbreviate | omitted.

  As shown in FIG. 6, the power transmission device of the second embodiment includes a first oil pump 101 and a second oil pump 102, and the second oil pump 102 is a pump that is driven in synchronization with the engine. The oil discharge capacity of the second oil pump 102 is set smaller than the oil discharge capacity of the first oil pump 101. The second oil pump 102 is connected in series to the suction side of the first oil pump 101, and the oil supply device, supply amount, and supply oil pressure can be set by the hydraulic control device 81.

  That is, the oil reservoir 82 is connected to the suction side of the second oil pump 102 via the oil suction passage 83, and the discharge side of the second oil pump 102 is suctioned to the first oil pump 101 via the oil connection passage 84. It is connected to the side. The discharge side of the first oil pump 101 is connected to the hydraulic control device 81 via the oil discharge passage 85 and is connected to the oil supply portion 86 via the oil supply passage 87.

  The hydraulic control device 81 includes a first control valve 88 that controls the first oil pump 101 and a second control valve (flow rate adjusting valve) 111 that controls the second oil pump 102. That is, a first oil circulation passage 89 is provided to connect an oil discharge passage 85 connected to the discharge side of the first oil pump 101 and an oil connection passage 84 connected to the suction side of the first oil pump 101. A first control valve 88 is provided in the first oil circulation passage 89. Further, a second oil circulation passage 112 is provided for connecting an oil connection passage 84 connected to the discharge side of the second oil pump 102 and an oil suction passage 83 connected to the suction side of the second oil pump 102. A second control valve 111 is provided in the second oil circulation passage 112. The hydraulic control device 81 controls the discharge state of the first and second oil pumps 101 and 102 by controlling the first control valve 88 and the second control valve 111 based on the driving state of the vehicle.

  Therefore, when the first and second oil pumps 101 and 102 are operated by driving the engine, the second oil pump 102 sucks the oil in the oil reservoir 82 through the oil suction passage 83 and pressurizes the oil inside to reduce the pressure. Oil is discharged into the oil connecting passage 84. Then, the first oil pump 101 sucks the low-pressure oil in the oil connection passage 84, pressurizes the oil into the high-pressure oil, and discharges it to the oil discharge passage 85. At this time, the first control valve 88 and the second control valve 111 are controlled according to the driving state of the vehicle, that is, the required amount of oil in the oil supply unit 86. Specifically, control is performed so that the opening degree of the second control valve 111 is increased according to the engine speed.

  That is, when the first control valve 88 and the second control valve 111 are closed, the entire amount of oil discharged Q2 by the second oil pump 102 is supplied to the first oil pump 101 via the oil connection passage 84. Then, the entire amount of oil discharged Q1 by the first oil pump 101 is supplied to the oil supply unit 86 via the oil discharge passage 85 and the oil supply passage 87. On the other hand, when the second control valve 111 is opened, an amount Q2-Q3 corresponding to the opening degree of the second control valve 111 with respect to the oil discharge amount Q3 by the second oil pump 102 is sucked through the second oil circulation passage 112. The remaining amount Q3 is returned to the passage 83 and supplied to the first oil pump 101 via the oil connection passage 84. When the first control valve 88 is opened, the amount Q1-Q3 corresponding to the opening of the first control valve 88 is connected to the oil through the first oil circulation passage 89 with respect to the oil discharge amount Q1 by the first oil pump 101. The remaining amount Q3 is returned to the passage 84 and supplied to the oil supply portion 86 via the oil discharge passage 85 and the oil supply passage 87.

  As described above, in the power transmission device according to the second embodiment, the first and second oil pumps 101 and 102 driven by the engine are provided, and the second oil pump 102 is connected in series to the suction side of the first oil pump 101. The oil supply unit 86 is connected to the discharge side, and a first oil circulation passage 89 is provided to connect the discharge side and the suction side of the first oil pump 101, and the first control valve 88 is provided in the first oil circulation passage 89. And a second oil circulation passage 112 that connects the discharge side and the suction side of the second oil pump 102, a second control valve 111 is provided in the second oil circulation passage 112, and the hydraulic control device 81 The discharge states of the oil pumps 101 and 102 are controlled by controlling the control valves 88 and 111 according to the driving state of the vehicle.

  Therefore, since the first oil pump 101 sucks the low-pressure oil discharged from the second oil pump 102, discharges it as high-pressure oil, and supplies it to the oil supply unit 86, the oil supply unit 86 regardless of the operating state of the vehicle. The required hydraulic pressure can be ensured, and the pump performance can be improved. Moreover, the oil discharge amount from each oil pump 101,102 can be easily adjusted by controlling the opening degree of each control valve 88,111 based on the driving | running state of a vehicle. That is, an appropriate amount of oil can be supplied to the oil supply unit 86 by adjusting the opening of the first control valve 88 according to the amount of oil required by the oil supply unit 86. Further, by adjusting the opening of the second control valve 111 according to the amount of oil required by the oil supply unit 86, the amount of oil that the first oil pump 101 sucks and discharges is adjusted, and the first oil pump 101 Power consumption can be reduced.

  FIG. 7 is a schematic configuration diagram illustrating a power transmission device according to a third embodiment of the present invention, and FIG. 8 is a schematic configuration diagram illustrating a vehicle drive transmission system to which the power transmission device according to the third embodiment is applied. In addition, the same code | symbol is attached | subjected to the member which has the same function as what was demonstrated in the Example mentioned above, and the overlapping description is abbreviate | omitted.

  As shown in FIGS. 7 and 8, the power transmission device according to the third embodiment includes a first oil pump 101 and a second oil pump 102, and the second oil pump 102 is driven in synchronization with the engine. The oil discharge capacity of the second oil pump 102 is set to be smaller than the oil discharge capacity of the first oil pump 101. In the first oil pump 101, the second oil pump 102 is connected to the suction side, while the high-pressure oil supply unit 86a is connected to the discharge side, and the second oil pump 102 is connected to the low-pressure oil supply unit 86b on the discharge side. Are connected to each other, and the oil supply amount and supply oil pressure to each of the oil supply portions 86a and 86b can be set by the hydraulic control device 81.

  That is, the oil reservoir 82 is connected to the suction side of the second oil pump 102 via the oil suction passage 83, and the discharge side of the second oil pump 102 is suctioned to the first oil pump 101 via the oil connection passage 84. It is connected to the side. The hydraulic control device 81 includes a high pressure control device 81a and a low pressure control device 81b, and the oil supply unit 86 includes a high pressure oil supply unit 86a and a low pressure oil supply unit 86b. In this case, the high pressure oil supply unit 86a is, for example, a hydraulic control system for the forward / reverse switching device 51 and the continuously variable transmission unit 58, and the low pressure oil supply unit 86b is a lubrication system for each device. The discharge side of the first oil pump 101 is connected to the high pressure control device 81a of the hydraulic control device 81 via the oil discharge passage 85, and is connected to the high pressure oil supply portion 86a via the oil supply passage 87a.

  The hydraulic control device 81 has a first control valve 88 that controls the first oil pump 101. That is, a first oil circulation passage 89 is provided to connect an oil discharge passage 85 connected to the discharge side of the first oil pump 101 and an oil connection passage 84 connected to the suction side of the first oil pump 101. A first control valve 88 is provided in the first oil circulation passage 89. The hydraulic control device 81 controls the discharge state of the first oil pump 101 by controlling the first control valve 88 based on the driving state of the vehicle. Further, the discharge side of the second oil pump 102 is connected to the low pressure control device 81b of the hydraulic control device 81 via the oil discharge passage 121 branched from the oil connection passage 84, and connected to the low pressure oil supply portion 86b via the oil supply passage 87b. It is connected.

  Therefore, when the first and second oil pumps 101 and 102 are operated by driving the engine, the second oil pump 102 sucks the oil in the oil reservoir 82 through the oil suction passage 83 and pressurizes the oil inside to reduce the pressure. Oil is discharged into the oil connecting passage 84. Then, the first oil pump 101 sucks the low-pressure oil in the oil connection passage 84, pressurizes the oil into the high-pressure oil, and discharges it to the oil discharge passage 85. At this time, the hydraulic control device 81 controls the first control valve 88 according to the driving state of the vehicle, that is, the required amount of oil.

  That is, when the first control valve 88 is closed, a predetermined amount Q3 of the oil discharge amount Q2 by the second oil pump 102 is supplied to the first oil pump 101 via the oil connection passage 84. The total amount of oil discharged Q1 by the first oil pump 101 is supplied to the high-pressure oil supply part 86a through the oil discharge passage 85 and the oil supply passage 87a. Further, a predetermined amount Q4 (Q2-Q3) of the oil discharge amount Q2 by the second oil pump 102 is supplied to the low pressure oil supply unit 86b through the oil discharge passage 121 and the oil supply passage 87b. On the other hand, when the first control valve 88 is opened, the amount Q1-Q3 corresponding to the opening of the first control valve 88 is connected to the oil through the first oil circulation passage 89 with respect to the oil discharge amount Q1 by the first oil pump 101. The remaining amount Q3 is returned to the passage 84 and supplied to the high-pressure oil supply portion 86a through the oil discharge passage 85 and the oil supply passage 87a.

  Thus, in the power transmission device of the third embodiment, the first and second oil pumps 101 and 102 driven by the engine are provided, and the second oil pump 102 is connected to the suction side of the first oil pump 101, A high pressure oil supply unit 86a is connected to the discharge side, a low pressure oil supply unit 86b is connected to the discharge side of the second oil pump 102, and a first oil circulation that connects the discharge side and the suction side of the first oil pump 101 is connected. A first control valve 88 is provided in the passage 89, and the hydraulic control device 81 controls the discharge state of the first oil pump 101 by controlling the first control valve 88 according to the driving state of the vehicle.

  Accordingly, the first oil pump 101 sucks the low-pressure oil discharged from the second oil pump 102, discharges it as high-pressure oil, and supplies it to the high-pressure oil supply part 86a, while the second oil pump 102 supplies the low-pressure oil to the low pressure oil. Since the oil is supplied to the oil supply unit 86b, the oil pressure necessary for each of the oil supply units 86a and 86b can be ensured regardless of the driving state of the vehicle, and the pump performance can be improved.

  In this case, since the hydraulic pressure supply to the high pressure oil supply unit 86a is p1 × Q3 and the hydraulic pressure supply to the low pressure oil supply unit 86b is p2 × Q4, the first oil pump 101 sets the discharge amount to Q4. It is possible to reduce the power consumption by reducing the amount only.

  FIG. 9 is a schematic configuration diagram illustrating a power transmission device according to a fourth embodiment of the present invention. In addition, the same code | symbol is attached | subjected to the member which has the same function as what was demonstrated in the Example mentioned above, and the overlapping description is abbreviate | omitted.

  As shown in FIG. 9, the power transmission device according to the fourth embodiment includes a first oil pump 101 and a second oil pump 102, and the second oil pump 102 is a pump that is driven in synchronization with the engine. The oil discharge capacity of the second oil pump 102 is set smaller than the oil discharge capacity of the first oil pump 101. In the first oil pump 101, the second oil pump 102 is connected to the suction side, while the high-pressure oil supply unit 86a is connected to the discharge side, and the second oil pump 102 is connected to the low-pressure oil supply unit 86b on the discharge side. Are connected to each other, and the oil supply amount and supply oil pressure to each of the oil supply portions 86a and 86b can be set by the hydraulic control device 81. In addition, a switching valve 133 that switches the connection destination of the first oil pump 101 between the second oil pump 102 and the oil reservoir 82 is provided, and the hydraulic control device 81 sets the switching valve 133 according to the driving state of the vehicle. Control is possible.

  That is, the oil reservoir 82 is connected to the suction side of the second oil pump 102 via the oil suction passage 83, and the discharge side of the second oil pump 102 is connected to the switching valve 133 via the oil connection passage 84. Yes. The oil reservoir 82 is connected to the switching valve 133 via the oil suction passage 131. In the first oil pump 101, an oil connection passage 132 connected to the suction side is connected to the switching valve 133. The discharge side of the first oil pump 101 is connected to the high pressure control device 81a of the hydraulic control device 81 via the oil discharge passage 85, and is connected to the high pressure oil supply portion 86a via the oil supply passage 87a.

  The hydraulic control device 81 has a first control valve 88 that controls the first oil pump 101. That is, the first oil circulation passage 89 is provided to connect the oil discharge passage 85 connected to the discharge side of the first oil pump 101 and the oil connection passage 132 connected to the suction side of the first oil pump 101. A first control valve 88 is provided in the first oil circulation passage 89. The hydraulic control device 81 controls the discharge state of the first oil pump 101 by controlling the first control valve 88 based on the driving state of the vehicle. Further, the discharge side of the second oil pump 102 is connected to the low pressure control device 81b of the hydraulic control device 81 via the oil discharge passage 121 branched from the oil connection passage 84, and connected to the low pressure oil supply portion 86b via the oil supply passage 87b. It is connected.

  Therefore, when the first and second oil pumps 101 and 102 are operated by driving the engine, the second oil pump 102 sucks the oil in the oil reservoir 82 through the oil suction passage 83 and pressurizes the oil inside to reduce the pressure. Oil is discharged into the oil connecting passage 84. Then, the first oil pump 101 sucks the low-pressure oil in the oil connection passage 84, pressurizes the oil into the high-pressure oil, and discharges it to the oil discharge passage 85. At this time, the hydraulic control device 81 controls the first control valve 88 according to the driving state of the vehicle, that is, the required amount of oil.

  That is, when the first control valve 88 is closed when the oil connection passages 84 and 132 are in communication with the switching valve 133 and the oil suction passage 131 and the oil connection passage 132 are shut off, the second oil pump 102 A predetermined amount Q3 of the oil discharge amount Q2 is supplied to the first oil pump 101 via the oil connecting passages 84 and 132. The total amount of oil discharged Q1 by the first oil pump 101 is supplied to the high-pressure oil supply part 86a through the oil discharge passage 85 and the oil supply passage 87a. Further, a predetermined amount Q4 (Q2-Q3) of the oil discharge amount Q2 by the second oil pump 102 is supplied to the low pressure oil supply unit 86b through the oil discharge passage 121 and the oil supply passage 87b. On the other hand, when the first control valve 88 is opened, the amount Q1-Q3 corresponding to the opening of the first control valve 88 is connected to the oil through the first oil circulation passage 89 with respect to the oil discharge amount Q1 by the first oil pump 101. The remaining amount Q3 is returned to the passage 84 and supplied to the high-pressure oil supply portion 86a through the oil discharge passage 85 and the oil supply passage 87a.

  On the other hand, when the first control valve 88 is closed when the oil connection passages 84 and 132 are shut off by the switching valve 133 and the oil suction passage 131 and the oil connection passage 132 are in communication, the first oil pump 101 is Then, the oil amount Q3 in the oil reservoir 82 is directly sucked, and the entire oil discharge amount Q1 is supplied to the high pressure oil supply portion 86a via the oil discharge passage 85 and the oil supply passage 87a. Further, in the second oil pump 102, the entire amount of the oil discharge amount Q2 is supplied to the low pressure oil supply unit 86b through the oil discharge passage 121 and the oil supply passage 87b. On the other hand, when the first control valve 88 is opened, the amount Q1-Q3 corresponding to the opening of the first control valve 88 is connected to the oil through the first oil circulation passage 89 with respect to the oil discharge amount Q1 by the first oil pump 101. The remaining amount Q3 is returned to the passage 132 and supplied to the high pressure oil supply portion 86a through the oil discharge passage 85 and the oil supply passage 87a.

  As described above, in the power transmission device according to the fourth embodiment, the first and second oil pumps 101 and 102 driven by the engine are provided, and the second oil pump 102 is connected to the suction side of the first oil pump 101, A high pressure oil supply unit 86a is connected to the discharge side, a low pressure oil supply unit 86b is connected to the discharge side of the second oil pump 102, and a first oil circulation that connects the discharge side and the suction side of the first oil pump 101 is connected. A first control valve 88 is provided in the passage 89, and a switching valve 133 for switching the connection destination of the first oil pump 101 between the second oil pump 102 and the oil reservoir 82 is provided. The discharge state of the first oil pump 101 is controlled by controlling the first control valve 88 and the switching valve 133 according to the operating state.

  Accordingly, the first oil pump 101 sucks the low-pressure oil discharged from the second oil pump 102, discharges it as high-pressure oil, and supplies it to the high-pressure oil supply part 86a, while the second oil pump 102 supplies the low-pressure oil to the low pressure oil. Since the oil is supplied to the oil supply unit 86b, the oil amount and the hydraulic pressure necessary for the oil supply units 86a and 86b can be ensured regardless of the driving state of the vehicle, and the pump performance can be improved.

  That is, since the discharge pressure by the first oil pump 101 becomes low when the vehicle starts or when the engine is operated at a low load, the oil connection passages 84 and 132 are brought into a communication state by the switching valve 133, and the first oil pump 101 The low-pressure oil from the second oil pump 102 is pressurized and supplied to the high-pressure oil supply unit 86a. On the other hand, the high-pressure oil supply unit 86a does not require high-pressure oil when the vehicle is running or the engine is running. Therefore, the oil intake passage 131 and the oil connection passage 132 are brought into communication with each other by the switching valve 133. The oil pump 101 sucks oil directly from the oil reservoir 82, pressurizes it, and supplies it to the high-pressure oil supply part 86a. Therefore, the pump load can be reduced by suppressing the pressure increase of the first oil pump 101 more than necessary, and the second oil pump 102 supplies the entire amount to be discharged to the low-pressure oil supply unit 86b, resulting in insufficient lubricating oil. Can be prevented.

  FIG. 10 is a schematic configuration diagram illustrating a power transmission device according to a fifth embodiment of the present invention, and FIG. 11 is a schematic diagram of a third control valve. In addition, the same code | symbol is attached | subjected to the member which has the same function as what was demonstrated in the Example mentioned above, and the overlapping description is abbreviate | omitted.

  As shown in FIG. 10, the power transmission apparatus of the fifth embodiment includes a first oil pump 101 and a second oil pump 102, and the second oil pump 102 is a pump that is driven in synchronization with the engine. The oil discharge capacity of the second oil pump 102 is set smaller than the oil discharge capacity of the first oil pump 101. In the first oil pump 101, the second oil pump 102 is connected to the suction side, while the high-pressure oil supply unit 86a is connected to the discharge side, and the second oil pump 102 is connected to the low-pressure oil supply unit 86b on the discharge side. Are connected to each other, and the oil supply amount and supply oil pressure to each of the oil supply portions 86a and 86b can be set by the hydraulic control device 81. In addition, the oil supply state to the low-pressure oil supply unit 86b is controlled by controlling the oil communication path 142 that connects the discharge side of the first oil pump 101 and the discharge side of the second oil pump 102 based on the driving state of the vehicle. A third control valve 141 that controls the above is provided.

  That is, the oil reservoir 82 is connected to the suction side of the second oil pump 102 via the oil suction passage 83, and the discharge side of the second oil pump 102 is connected to the switching valve 133 via the oil connection passage 84. Yes. The oil reservoir 82 is connected to the switching valve 133 via the oil suction passage 131. In the first oil pump 101, an oil connection passage 132 connected to the suction side is connected to the switching valve 133. The discharge side of the first oil pump 101 is connected to the high pressure control device 81a of the hydraulic control device 81 via the oil discharge passage 85, and is connected to the high pressure oil supply portion 86a via the oil supply passage 87a.

  The hydraulic control device 81 includes a first control valve 88 and a third control valve 141 that control the first oil pump 101. That is, the first oil circulation passage 89 is provided to connect the oil discharge passage 85 connected to the discharge side of the first oil pump 101 and the oil connection passage 132 connected to the suction side of the first oil pump 101. A first control valve 88 is provided in the first oil circulation passage 89. On the other hand, the discharge side of the second oil pump 102 is connected to the low pressure control device 81b through an oil discharge passage 121 branched from the oil connection passage 84, and is connected to the low pressure oil supply unit 86b through an oil supply passage 87b. An oil discharge passage 85 connected to the discharge side of the first oil pump 101 and an oil discharge passage 121 connected to the discharge side of the second oil pump 102 are connected to the oil communication passage 142, and this oil communication passage 142 is provided with a third control valve 141. The hydraulic control device 81 controls the discharge state of the first oil pump 101 by controlling the first control valve 88 and the third control valve 141 based on the driving state of the vehicle.

  The third control valve 141 has a switching valve 143 that switches the communication cut-off state of the oil communication passage 142 in accordance with the discharge pressure of the second oil pump 102. That is, as shown in FIG. 11, a switching valve 143 is supported in the case 144 so as to be reciprocally movable, and is compressed in one direction by a compression spring 145 as an urging member provided at one end (left in FIG. 11). Direction). The switching valve 143 is movable in both directions (left and right in FIG. 11) by a solenoid coil 146 provided around the switching valve 143. The case 144 is formed with a communication port 147 a communicating with the passage 142 a on the high pressure oil supply part 86 a side in the oil communication path 142 and a drain port 147 b communicating with the drain path 148 to the oil storage unit 82. The case 144 has a communication port 147c that communicates with the passage 142b on the low-pressure oil supply part 86b side, and a branch port 147d that branches from the communication port 147c and communicates with the other end side of the switching valve 143. Is formed. And the communication groove 143a which connects the communication port 147a and the drain channel | path 147b, and the communication port 147c is formed in the outer peripheral part of the switching valve 143 by the movement position.

  Therefore, as shown in FIG. 10, when the first and second oil pumps 101 and 102 are operated by driving the engine, the second oil pump 102 sucks the oil in the oil reservoir 82 through the oil suction passage 83. Then, the inside is pressurized to form low pressure oil and discharged to the oil connecting passage 84. Then, the first oil pump 101 sucks the low-pressure oil in the oil connection passage 84, pressurizes the oil into the high-pressure oil, and discharges it to the oil discharge passage 85. At this time, the hydraulic control device 81 controls the first control valve 88 according to the driving state of the vehicle, that is, the required amount of oil.

  That is, when the first control valve 88 is closed when the oil connection passages 84 and 132 are in communication with the switching valve 133 and the oil suction passage 131 and the oil connection passage 132 are shut off, the second oil pump 102 A predetermined amount Q3 of the oil discharge amount Q2 is supplied to the first oil pump 101 via the oil connecting passages 84 and 132. The total amount of oil discharged Q1 by the first oil pump 101 is supplied to the high-pressure oil supply part 86a through the oil discharge passage 85 and the oil supply passage 87a. Further, a predetermined amount Q4 (Q2-Q3) of the oil discharge amount Q2 by the second oil pump 102 is supplied to the low pressure oil supply unit 86b through the oil discharge passage 121 and the oil supply passage 87b. On the other hand, when the first control valve 88 is opened, the amount Q1-Q3 corresponding to the opening of the first control valve 88 is connected to the oil through the first oil circulation passage 89 with respect to the oil discharge amount Q1 by the first oil pump 101. The remaining amount Q3 is returned to the passage 132 and supplied to the high pressure oil supply portion 86a through the oil discharge passage 85 and the oil supply passage 87a.

  At this time, as shown in FIG. 11, when the hydraulic pressure p <b> 2 supplied to the low pressure oil supply part 86 b through the oil discharge passage 121 is low and the oil amount Q <b> 4 is small, the switching valve 143 is driven by the urging force of the compression spring 145. One side (leftward in FIG. 11) is urged, and the communication port 147a and the communication port 147c communicate with each other through the communication groove 143a. Therefore, the high-pressure oil in the oil discharge passage 85 flows to the oil discharge passage 121 through the passage 142a, the communication port 147a, the communication groove 143a, the communication port 147c, and the passage 142b, and oil shortage in the low-pressure oil supply unit 86b is prevented.

  On the other hand, as shown in FIG. 10, when the first control valve 88 is closed when the oil connection passages 84 and 132 are shut off by the switching valve 133 and the oil suction passage 131 and the oil connection passage 132 are in communication. The first oil pump 101 directly sucks the oil amount Q3 of the oil reservoir 82, and the entire amount of the oil discharge amount Q1 is supplied to the high pressure oil supply portion 86a via the oil discharge passage 85 and the oil supply passage 87a. Further, in the second oil pump 102, the entire amount of the oil discharge amount Q2 is supplied to the low pressure oil supply unit 86b through the oil discharge passage 121 and the oil supply passage 87b. On the other hand, when the first control valve 88 is opened, the amount Q1-Q3 corresponding to the opening of the first control valve 88 is connected to the oil through the first oil circulation passage 89 with respect to the oil discharge amount Q1 by the first oil pump 101. The remaining amount Q3 is returned to the passage 132 and supplied to the high pressure oil supply portion 86a through the oil discharge passage 85 and the oil supply passage 87a.

  At this time, as shown in FIG. 11, when the hydraulic pressure p2 supplied to the low pressure oil supply unit 86b through the oil discharge passage 121 is high and the oil amount Q4 is too large, the switching valve 143 is connected to the low pressure oil supply unit 86b. The other side (right side in FIG. 11) is pressed by the supplied hydraulic pressure p2, and the drain port 147b and the communication port 147c communicate with each other through the communication groove 143a. Therefore, the low pressure oil in the oil discharge passage 121 flows to the drain passage 148 through the passage 142b, the communication port 147c, the communication groove 143a, and the drain port 147b, thereby preventing excessive supply of oil to the low pressure oil supply unit 86b.

  In the above description, the third control valve 141 is moved according to the hydraulic pressure supplied to the low pressure oil supply part 86b through the oil discharge passage 121. However, when the solenoid coil 146 is energized, The third control valve 141 may be moved by a suction force.

  Thus, in the power transmission device of the fifth embodiment, the first and second oil pumps 101 and 102 driven by the engine are provided, and the second oil pump 102 is connected to the suction side of the first oil pump 101, A high-pressure oil supply unit 86 a is connected to the discharge side, and a low-pressure oil supply unit 86 b is connected to the discharge side of the second oil pump 102, and a first oil circulation passage 89 between the discharge side and the suction side of the first oil pump 101. The first control valve 88 is provided, and the third control valve 141 is provided in the oil communication path 142 that connects the discharge side of the first oil pump 101 and the discharge side of the second oil pump 102. The discharge state of the first oil pump 101 is controlled by controlling the first control valve 88, the switching valve 133, and the third control valve 141 according to the driving state of the vehicle.

  Accordingly, the first oil pump 101 sucks the low-pressure oil discharged from the second oil pump 102, discharges it as high-pressure oil, and supplies it to the high-pressure oil supply part 86a, while the second oil pump 102 supplies the low-pressure oil to the low pressure oil. Since the oil is supplied to the oil supply unit 86b, the oil amount and the hydraulic pressure necessary for the oil supply units 86a and 86b can be ensured regardless of the driving state of the vehicle, and the pump performance can be improved.

  That is, when the hydraulic pressure p2 supplied to the low-pressure oil supply part 86b is low, the switching valve 143 moves to one side and the communication groove 143a connects the communication port 147a and the communication port 147c. Can flow to the oil discharge passage 121 side through the oil communication passage 142 by the third control valve 141, and oil shortage in the low-pressure oil supply portion 86b can be prevented. On the other hand, when the hydraulic pressure p2 supplied to the low-pressure oil supply unit 86b is high, the switching valve 143 moves to the other side, and the drain port 147b and the communication port 147c communicate with each other through the communication groove 143a. Flows to the drain passage 148 through the oil communication passage 142 by the third control valve 141, and excessive supply of oil to the low pressure oil supply portion 86b can be prevented.

  FIG. 12 is a schematic configuration diagram illustrating a power transmission device according to a sixth embodiment of the present invention, and FIG. 13 is a flowchart illustrating operation control of the second oil pump. In addition, the same code | symbol is attached | subjected to the member which has the same function as what was demonstrated in the Example mentioned above, and the overlapping description is abbreviate | omitted.

  As shown in FIG. 12, the power transmission apparatus according to the sixth embodiment includes a first oil pump 101 and a second oil pump 150. The second oil pump 150 is an electric pump driven by an electric motor (not shown). Yes, the oil discharge capacity of the second oil pump 150 is set smaller than the oil discharge capacity of the first oil pump 101. The second oil pump 150 is connected in series to the suction side of the first oil pump 101, and the connection destination of the first oil pump 101 can be switched between the second oil pump 150 and the oil reservoir 82. The hydraulic control device 81 can control the rotation speed of the second oil pump 150 in accordance with the driving state of the vehicle.

  That is, the oil reservoir 82 is connected to the suction side of the second oil pump 150 via the oil suction passage 83, and the discharge side of the second oil pump 150 is suctioned to the first oil pump 101 via the oil connection passage 84. It is connected to the side. The oil reservoir 82 is connected to the oil connection passage 84 via the oil suction passage 151, and a check valve 152 is provided in the oil suction passage 151. In this case, the check valve 152 may be a switching valve that permits or prohibits the flow of oil from the oil reservoir 82 to the oil connection passage 84 in the oil suction passage 151. The discharge side of the first oil pump 101 is connected to the hydraulic control device 81 via the oil discharge passage 85 and is connected to the oil supply portion 86 via the oil supply passage 87.

  The hydraulic control device 81 has a first control valve 88 that controls the first oil pump 101. That is, a first oil circulation passage 89 is provided to connect an oil discharge passage 85 connected to the discharge side of the first oil pump 101 and an oil connection passage 84 connected to the suction side of the first oil pump 101. A first control valve 88 is provided in the first oil circulation passage 89. The hydraulic control device 81 controls the discharge state of the first oil pump 101 by controlling the first control valve 88 based on the driving state of the vehicle.

  Accordingly, when the first oil pump 101 is operated by driving the engine and the second oil pump 102 is operated by the electric motor, the second oil pump 150 sucks the oil in the oil reservoir 82 through the oil suction passage 83. Then, it is pressurized inside to form low-pressure oil and discharged to the oil connecting passage 84. Then, the first oil pump 101 sucks the low-pressure oil in the oil connection passage 84, pressurizes the oil into the high-pressure oil, and discharges it to the oil discharge passage 85. At this time, the hydraulic control device 81 controls the first control valve 88 and the second oil pump 150 in accordance with the driving state of the vehicle, that is, the required amount of oil.

  That is, when the oil supply unit 86 requires high-pressure oil, the hydraulic control device 81 drives the second oil pump 150. At this time, when the first control valve 88 is closed, the entire amount of oil discharged by the second oil pump 150 is supplied to the first oil pump 101 via the oil connection passage 84. The total amount of oil discharged by the first oil pump 101 is supplied to the oil supply unit 86 through the oil discharge passage 85 and the oil supply passage 87. On the other hand, when the first control valve 88 is opened, the amount corresponding to the opening of the first control valve 88 returns to the oil connection passage 84 through the first oil circulation passage 89 with respect to the oil discharge amount by the first oil pump 101. The remaining amount is supplied to the oil supply unit 86 through the oil discharge passage 85 and the oil supply passage 87.

  On the other hand, when the oil supply unit 86 does not require high-pressure oil, the hydraulic control device 81 stops driving the second oil pump 150. At this time, the first oil pump 101 sucks the oil in the oil reservoir 82 directly from the oil suction passage 151 and discharges it to the oil discharge passage 85. The amount of oil corresponding to the opening of the first control valve 88 is supplied to the oil supply unit 86 through the oil discharge passage 85 and the oil supply passage 87.

  Here, the operation control of the second oil pump 150 by the hydraulic control device 81 will be described in detail based on the flowchart of FIG.

In the operation control of the second oil pump 150 by the hydraulic control device 81, as shown in FIG. 13, in step S11, the hydraulic control device 81 causes the input / output rotational speed difference (first rotary member and It is determined whether or not the difference in rotation speed (ΔN with the second rotation member) ΔN is smaller than the suction limit rotation speed N MAX of the first oil pump 101. Here, if it is determined that the input / output rotational speed difference ΔN in the first oil pump 101 is smaller than the suction limit rotational speed N MAX , the process proceeds to step S12.

In step S <b> 12, the hydraulic control device 81 determines whether or not the oil discharge pressure P L in the first oil pump 101 is greater than the minimum line pressure P L0 in the oil supply unit 86. Here, if it is determined that the oil discharge pressure P L in the first oil pump 101 is greater than the minimum line pressure P L0 in the oil supply unit 86, the process proceeds to step S13, and the second oil pump 150 is stopped.

On the other hand, in step S11, it is determined that the input / output rotational speed difference ΔN in the first oil pump 101 is not smaller than the suction limit rotational speed N MAX , or in step S12, the oil discharge pressure P L in the first oil pump 101 is determined. Is determined not to be larger than the minimum line pressure PLO in the oil supply unit 86, the process proceeds to step S14, and the second oil pump 150 is driven.

  Thus, in the power transmission device of the sixth embodiment, the first oil pump 101 driven by the engine and the second oil pump 150 driven by the electric motor are provided, and the second oil pump is provided on the suction side of the first oil pump 101. The pump 150 is connected in series, the oil supply unit 86 is connected to the discharge side, the second oil pump 150 is an electric pump, and the first oil pump 101 is connected to the second oil pump 150 and the oil storage unit 82. The hydraulic control device 81 can control the rotation speed of the second oil pump 150 in accordance with the driving state of the vehicle.

  Therefore, since the first oil pump 101 sucks the low-pressure oil discharged from the second oil pump 150, discharges it as high-pressure oil, and supplies it to the oil supply unit 86, the oil supply unit 86 regardless of the driving state of the vehicle. Therefore, it is possible to secure the necessary oil amount and hydraulic pressure and to improve the pump performance. Further, by controlling the rotation speed of the second oil pump 150 based on the driving state of the vehicle, the oil discharge amount and discharge pressure from the first oil pump 101 can be easily adjusted.

  That is, since the discharge pressure by the first oil pump 101 becomes a low pressure when the vehicle starts or when the engine is under a low load operation, the first oil pump 101 causes the low pressure oil to be discharged by driving the second oil pump 150. Pressurized and supplied to the oil supply unit 86. On the other hand, the oil supply unit 86 does not require high-pressure oil when the vehicle is running or the engine is running. Therefore, the first oil pump 101 can be used as the oil storage unit by stopping the second oil pump 150. The oil 82 is pressurized and supplied to the oil supply unit 86. Therefore, the pump load can be reduced by suppressing the pressure increase of the first oil pump 101 more than necessary, and the power consumption can be reduced by stopping the second oil pump 150.

In the sixth embodiment, the suction limit rotation speed N MAX of the first oil pump 101 is used to determine the operation stop of the second oil pump 150. The suction limit rotation speed N MAX is a drop in oil temperature. Accordingly, the suction limit rotational speed N MAX may be variable according to the oil temperature. At this time, the oil discharge pressure by the second oil pump 150 becomes higher as the oil temperature is lower and the input / output rotational speed difference ΔN in the first oil pump 101 is larger. The difference ΔN may be variable according to the oil temperature.

  In each of the above-described embodiments, the first rotation member 25 is provided with the cam 26, while the second rotation member 36 is provided with the pistons 38a to 38h that face the cam 26 and are movable along the radial direction. It is not limited to this configuration. In other words, the second rotating member may be provided with a cam, while the first rotating member may be provided with a piston that is movable in the radial direction so as to face the cam.

  In each of the above-described embodiments, the first oil pump has been described as a radial piston pump. However, the present invention is not limited to this, and any pump that can perform differential rotation, such as a vane pump or an axial pump, may be used.

  As described above, in the hydraulic device according to the present invention, power is transmitted between the first rotating member and the second rotating member, and the first rotating member and the second rotating member rotate relative to each other. In a power transmission device that discharges oil, the pump performance is improved by ensuring the necessary hydraulic pressure regardless of the rotational speed difference between the first rotating member and the second rotating member. It is also suitable for use in an apparatus.

It is a schematic block diagram showing the power transmission device which concerns on Example 1 of this invention. It is a schematic block diagram showing the drive transmission system of the vehicle to which the power transmission device of Example 1 was applied. It is a schematic sectional drawing of the oil pump in the power transmission device of Example 1. FIG. It is IV-IV sectional drawing of FIG. It is the schematic showing the discharge hydraulic pressure by the power transmission device of Example 1. FIG. It is a schematic block diagram showing the power transmission device which concerns on Example 2 of this invention. It is a schematic block diagram showing the power transmission device which concerns on Example 3 of this invention. It is a schematic block diagram showing the drive transmission system of the vehicle to which the power transmission device of Example 3 was applied. It is a schematic block diagram showing the power transmission device which concerns on Example 4 of this invention. It is a schematic block diagram showing the power transmission device which concerns on Example 5 of this invention. It is the schematic of a 3rd control valve. It is a schematic block diagram showing the power transmission device which concerns on Example 6 of this invention. It is a flowchart showing the operation control of a 2nd oil pump.

Explanation of symbols

11 Engine 12 Crankshaft 14 Input shaft (input member)
DESCRIPTION OF SYMBOLS 15 Primary shaft 17 Casing 22 Power transmission device 25 1st rotation member 26 Cam 27 Rotary valve 29 1st communicating hole 30a, 30b 2nd communicating hole 32 Oil discharge | emission oil passage 33 Second oil passage 34a-34d, 113a-113d Connection Grooves 35a to 35d, 114a to 114d Connecting hole 36 Second rotating member 37a to 37h Cylinder 38a to 38h Piston 39a to 39h Roller 40a to 40h Compression coil spring (pressing member)
41a-41h Oil chamber 42a-42h Connecting hole 45 Output shaft (output member)
51 Forward / reverse switching device 58 continuously variable transmission 71 electronic control unit, ECU
DESCRIPTION OF SYMBOLS 81 Hydraulic control apparatus 82 Oil storage part 83,131,151 Oil suction path 84,132 Oil connection path 85,121 Oil discharge path 86 Oil supply part 87 Oil supply path 88 First control valve 89 First oil circulation path 95 Suction port 96 Discharge port 101 1st oil pump 102,150 2nd oil pump 111 2nd control valve 112 2nd oil circulation path 133 Switching valve 141 3rd control valve 142 Oil communication path 152 Check valve (switching valve)

Claims (7)

  1. An input member and an output member for transmitting power;
    A first oil pump that discharges oil by relative rotation of the first rotating member and the second rotating member connected to the input member and the output member;
    In a power transmission device comprising:
    The first oil pump has a second oil pump connected to the suction side and a high-pressure oil supply unit connected to the discharge side.
    The second oil pump has a low pressure oil supply unit connected to the discharge side ,
    A first oil circulation passage connecting the discharge side and the suction side of the first oil pump is provided, and the first oil pump passage is connected to the suction side from the discharge side of the first oil pump based on the operating state of the vehicle. A first control valve for controlling a discharge state of the first oil pump by controlling an oil circulation amount to
    A power transmission device characterized by that.
  2. A second oil circulation passage that connects the discharge side and the suction side of the second oil pump is provided, and the second oil pump discharge is controlled by controlling the second oil circulation passage based on the operating state of the vehicle. The power transmission device according to claim 1 , wherein a second control valve for controlling a state is provided.
  3. A switching valve for switching the connection destination of the first oil pump between the second oil pump and the oil reservoir is provided, and the switching valve is controlled according to the driving state of the vehicle to control the switching of the first oil pump. The power transmission device according to claim 1 , wherein the connection destination is switched.
  4. 4. The power transmission device according to claim 3 , wherein the second oil pump is an electric pump, and the switching valve is controlled according to a driving state of the vehicle and the number of revolutions of the electric pump is controlled. 5.
  5. An oil communication path that communicates the discharge side of the first oil pump and the discharge side of the second oil pump is provided, and the oil communication path is controlled based on a driving state of the vehicle to control the low-pressure oil supply unit. The power transmission device according to any one of claims 1 to 4 , further comprising a third control valve for controlling an oil supply state to the vehicle.
  6. The power transmission device according to claim 5 , wherein the third control valve has a switching valve that switches a communication cut-off state of the oil communication passage according to a discharge pressure of the second oil pump.
  7. The input member and the first rotating member are connected to transmit power, the output member and the second rotating member are connected to transmit power, and a cam is provided on the first rotating member, A piston that is movable in the radial direction facing the cam is provided on the two-rotating member, and the piston is pressed by the pressing member so as to contact the cam,
    The second rotating member is provided with a fluid chamber whose volume is enlarged or reduced as the piston moves, and the fluid chamber is provided with an oil suction passage through which oil is sucked and an oil discharge passage through which oil is discharged. The second oil pump is connected to the suction passage;
    The first control valve controls a power transmission state between the first rotating member and the second rotating member by controlling an oil discharge state from the oil discharge passage in the first oil pump. The power transmission device according to any one of claims 1 to 6 .
JP2008141355A 2008-05-29 2008-05-29 Power transmission device Expired - Fee Related JP5012667B2 (en)

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KR101199091B1 (en) * 2010-08-31 2012-11-08 기아자동차주식회사 Control system for oil hydraulic and flow of engine and the control method thereof
KR20120037623A (en) * 2010-10-12 2012-04-20 현대자동차주식회사 Oil supply system of automatic transmission
KR101339232B1 (en) * 2011-11-29 2013-12-09 현대자동차 주식회사 Hydraulic control system for transmission and control method thereof
KR101339230B1 (en) * 2011-11-29 2013-12-09 현대자동차 주식회사 Hydraulic control system for transmission
KR101338455B1 (en) * 2012-09-03 2013-12-10 현대자동차주식회사 Oil pressure supply system of automatic transmission
KR101394040B1 (en) * 2012-09-03 2014-05-12 현대자동차 주식회사 Oil pressure supply system of automatic transmission
KR101338454B1 (en) 2012-09-03 2013-12-10 현대자동차주식회사 Oil pressure supply system of automatic transmission
KR101394038B1 (en) * 2012-09-03 2014-05-12 현대자동차 주식회사 Oil pressure supply system of automatic transmission
KR101438607B1 (en) * 2012-12-12 2014-09-05 현대자동차 주식회사 Oil pressure supply system of automatic transmission
JP6130860B2 (en) * 2012-12-17 2017-05-17 株式会社Tbk Oil supply device
KR101461876B1 (en) * 2013-04-02 2014-11-13 현대자동차 주식회사 Hydraulic pressure supply system of automatic transmission
KR101484194B1 (en) * 2013-04-02 2015-01-16 현대자동차 주식회사 Hydraulic pressure supply system of automatic transmission
KR101534697B1 (en) * 2013-05-09 2015-07-07 현대자동차 주식회사 Oil suppply system
KR101490915B1 (en) * 2013-07-29 2015-02-06 현대자동차 주식회사 Oil pressure supply system of automatic transmission
KR101566728B1 (en) * 2013-12-18 2015-11-06 현대자동차 주식회사 Oil pressure supply system of automatic transmission
KR101601105B1 (en) * 2014-07-01 2016-03-08 현대자동차 주식회사 Oil pressure supply system of automatic transmission

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AT298054T (en) * 2002-03-29 2005-07-15 Doornes Transmissie Bv wrap-around
JP4228945B2 (en) * 2004-03-11 2009-02-25 トヨタ自動車株式会社 Power transmission device

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