JP4496855B2 - Power transmission device - Google Patents

Description

  The present invention relates to a power transmission device disposed on the output side of a driving force source, and particularly to a power transmission device having an oil pump.

  Conventionally, a hydraulic control device has been used as an actuator for controlling a power transmission device of a vehicle, and a configuration is adopted in which hydraulic oil supplied to a hydraulic circuit of the hydraulic control device is circulated by an oil pump. On the other hand, a technique for using an oil pump for applications other than hydraulic oil transportation equipment is also known, and an example of the technique is described in Patent Document 1. This patent document 1 relates to a continuously variable transmission having a planetary gear device. The planetary gear device includes a sun gear that rotates integrally with an input shaft, a ring gear, and a carrier that holds a pinion gear that meshes with the sun gear and the ring gear. Have. The carrier is configured to rotate integrally with the output shaft, and a plurality of blades are attached to the outer periphery of the ring gear at predetermined intervals. The ring gear is rotatably held in the transmission cover, and an oil pump discharge port and suction port are formed in the transmission cover. Also, a hydraulic circuit that connects the discharge port and the suction port is formed, and an oil tank is disposed in the middle of the hydraulic circuit. In the hydraulic circuit, an adjustment valve is provided between the discharge port and the oil tank.

In the above configuration, when torque is transmitted to the input shaft, the sun gear rotates and the ring gear serves as a reaction force element, and torque is output from the carrier. Further, oil is sucked from the suction port by the rotation of the ring gear, and the oil is discharged from the discharge port. Here, by adjusting the adjustment valve and controlling the hydraulic pressure between the discharge port and the adjustment valve in the hydraulic circuit, the reaction torque and the rotational speed of the ring gear are adjusted, and the pressure between the input shaft and the output shaft is adjusted. The gear ratio is controlled steplessly. Further, the oil discharged from the discharge port is returned to the oil pan via the adjustment valve, and the oil in the oil pan is again sucked into the suction port. In this way, the oil circulates in the hydraulic circuit. Note that Patent Document 2 describes an example of a vehicle having an oil pump that is driven by the power of the driving force source in a path from the driving force source to the wheels.
JP-A-4-88241 JP 2001-323978 A

  The continuously variable transmission described in Patent Document 1 has a configuration in which oil circulates through a hydraulic circuit and a configuration in which reaction force torque is controlled by the hydraulic pressure of the hydraulic circuit. In other words, although it is possible to perform torque amplification according to the gear ratio of the continuously variable transmission, there is room for improvement in that the torque of the output shaft is amplified using oil discharged from the oil pump. was there.

  The present invention was made against the background of the above circumstances, and an object of the present invention is to provide a power transmission device capable of increasing torque transmitted to wheels using oil discharged from an oil pump. Yes.

In order to achieve the above object, the invention of claim 1 has a first rotating member and a second rotating member which are connected so as to be capable of transmitting power, and the relative relationship between the first rotating member and the second rotating member is the same. An oil pump having a configuration for sucking oil from the first oil passage by rotation and discharging the sucked oil to the second oil passage is provided, and between the driving force source and the wheel, In a power transmission device configured to transmit power via the first rotating member and the second rotating member, mechanical energy of oil discharged from the oil pump is transmitted to a wheel. A conversion device for converting into mechanical energy is provided. The conversion device includes an oil motor, and the oil in the second oil passage reaches the third oil passage via the oil motor. With configuration In addition, the oil motor has a third rotating member that rotates due to the oil pressure of the oil, and the torque of the third rotating member is transmitted to the wheels, and mechanical energy generated by the repulsive running of the vehicle is obtained. Is transmitted to the second rotating member, and when the mechanical energy is transmitted to the driving force source via the first rotating member, a braking force is generated by the driving force source. And when the mechanical energy generated by the repulsive running of the vehicle is transmitted to the second rotating member, the oil sucked from the second oil passage is discharged to the first oil passage. The oil pump further includes a configuration, and the power transmitted from the second rotating member to the first rotating member is controlled by controlling the flow rate of oil in the first oil passage. The flow control device It has been kicked and is characterized in Rukoto.

According to a second aspect of the present invention, the first rotating member and the second rotating member are connected so as to be capable of transmitting power, and the first rotating member and the second rotating member are rotated relative to each other. An oil pump having a configuration for sucking oil from the oil passage and discharging the sucked oil to the second oil passage is provided, and the first rotating member is provided between the driving force source and the wheel. In the power transmission device configured to transmit power via the second rotating member, the mechanical energy of oil discharged from the oil pump is converted into mechanical energy transmitted to the wheels. A conversion device is provided, the conversion device includes an oil motor, and the oil in the second oil passage reaches the third oil passage through the oil motor. Along with the oil of the oil The third rotation member and the oil motor has the a configuration in which the torque of the third rotary member is transmitted to the wheels, before Symbol pressure and the second oil path of the first oil passage that is rotated by of a pressure control valve that controls the hydraulic pressure the same, the a to connect flow amount control device in one of the oil motor second oil passage or the oil holding portion, the wheels from the second rotational member And the oil holding portion and the oil when the oil pressure of the first oil passage and the oil pressure of the second oil passage are controlled to be the same. It is further characterized by having a configuration in which the oil of the oil holding part is supplied to the oil required part via the oil motor by connecting to a motor.

According to a third aspect of the present invention, the first rotating member and the second rotating member are connected so as to be capable of transmitting power, and the first rotating member and the second rotating member are rotated relative to each other. An oil pump having a configuration for sucking oil from the oil passage and discharging the sucked oil to the second oil passage is provided, and the first rotating member is provided between the driving force source and the wheel. In the power transmission device configured to transmit power via the second rotating member, the mechanical energy of oil discharged from the oil pump is converted into mechanical energy transmitted to the wheels. A conversion device is provided, the conversion device includes an oil motor, and the oil in the second oil passage reaches the third oil passage through the oil motor. Along with the oil of the oil The oil motor has a third rotary member rotated by a configuration in which the torque of the third rotary member is transmitted to the wheels, leading from the front Stories second oil passage to the third oil passage Between the hydraulic chamber formed in the path and the third rotating member according to the engagement force when reciprocating according to the hydraulic pressure of the hydraulic chamber and contacting the third rotating member The oil motor further includes an operating member for transmitting power, and the torque transmitted between the operating member and the third rotating member increases as the hydraulic pressure in the hydraulic chamber increases. a configuration in which, with has the oil motor further by reducing the amount of oil supplied to the hydraulic chamber from the second oil passage, flow amount you suppress hydraulic pressure rise of the hydraulic chamber A control device is further provided. Is shall.

  The power train of the vehicle targeted by the invention of each claim has the same wheels as the wheels to which power is transmitted from the driving force source and the wheels to which the mechanical energy of oil is converted into torque and the torque is transmitted. A power train having a certain configuration, a wheel to which power is transmitted from a driving force source, and a power train having a configuration in which the mechanical energy of oil is converted into torque and the wheel to which the torque is transmitted are different are included.

  According to the first aspect of the present invention, power is transmitted between the first rotating member and the second rotating member via the oil pump. Further, when the first rotating member and the second rotating member rotate relative to each other and oil is discharged to the second oil passage, the mechanical energy of the oil is transmitted to the wheels. Is converted to Therefore, the torque transmitted to the wheels can be increased as much as possible, and the driving force of the vehicle is increased. Moreover, it becomes possible to reduce the target torque borne by the driving force source among the target torque corresponding to the required driving force of the vehicle, and the degree of freedom of the driving state of the driving force source is expanded.

Further, according to the invention of claim 1, the oil pressure of the OIL is converted to a torque of the third rotary member, the torque of the third rotary member is transmitted to the wheels.

Furthermore, according to the first aspect of the present invention, the mechanical energy due to the repulsive running of the vehicle is transmitted to the driving force source via the second rotating member and the first rotating member, and is controlled by the driving force source. Power is generated. Further, when mechanical energy due to repulsive running of the vehicle is transmitted to the second rotating member, the flow rate of oil discharged from the second passage to the first oil passage is controlled. The power transmitted from the second rotating member to the first rotating member is controlled. Therefore, it is possible to control the braking force generated by the driving force source.

According to the invention of claim 2, power is transmitted between the first rotating member and the second rotating member via the oil pump. Further, when the first rotating member and the second rotating member rotate relative to each other and oil is discharged to the second oil passage, the mechanical energy of the oil is transmitted to the wheels. Is converted to Therefore, the torque transmitted to the wheels can be increased as much as possible, and the driving force of the vehicle is increased. Moreover, it becomes possible to reduce the target torque borne by the driving force source among the target torque corresponding to the required driving force of the vehicle, and the degree of freedom of the driving state of the driving force source is expanded.
According to the invention of claim 2, the oil pressure of the oil is converted into the torque of the third rotating member, and the torque of the third rotating member is transmitted to the wheel. Furthermore, according to the invention of claim 2 , the first rotating member and the second rotating member are integrally rotated by controlling the oil pressures of the first oil passage and the second oil passage to be the same. Oil suction and discharge by the oil pump is stopped. Further, since the oil in the oil holding portion is supplied to the oil required portion via the oil motor, it is possible to suppress a decrease in the amount of oil supplied to the oil required portion.

According to the invention of claim 3, between the first rotary member and second rotary member, the power transmission is performed via the oil pump. Further, when the first rotating member and the second rotating member rotate relative to each other and oil is discharged to the second oil passage, the mechanical energy of the oil is transmitted to the wheels. Is converted to Therefore, the torque transmitted to the wheels can be increased as much as possible, and the driving force of the vehicle is increased. Moreover, it becomes possible to reduce the target torque borne by the driving force source among the target torque corresponding to the required driving force of the vehicle, and the degree of freedom of the driving state of the driving force source is expanded.
According to the invention of claim 3, the oil pressure of the oil is converted into the torque of the third rotating member, and the torque of the third rotating member is transmitted to the wheel. Further, according to the invention of claim 3, the operating member reciprocates according to the hydraulic pressure of the hydraulic chamber and is transmitted to the third rotating member according to the engagement force between the operating member and the third rotating member. Torque to be changed. When there is no need to convert the mechanical energy of the oil into the torque transmitted to the wheels, the amount of oil supplied from the second oil passage to the hydraulic chamber is reduced to suppress an increase in hydraulic pressure in the hydraulic chamber. Is possible. For this reason, when the vehicle runs with the power of the driving force source, the engagement force between the operating member and the third rotating member is reduced, and an increase in power loss due to the rotation of the oil motor can be suppressed.

  Next, the present invention will be described based on specific examples. The present invention is a power transmission device in which an oil pump has both an oil transportation function and a power transmission function, and embodiments of the power transmission device will be sequentially described.

The first embodiment will be described with reference to FIG. FIG. 1 schematically shows an example of a power train of a vehicle Ve having the power transmission device of the present invention. FIG. 2 shows a specific configuration and control of the power train of the vehicle Ve shown in FIG. The system is shown. First, the power train of the vehicle Ve will be described. The engine 1 is provided as a driving force source. The engine 1 is a power device that converts thermal energy generated by fuel combustion into kinetic energy.

  As the engine 1, for example, an internal combustion engine, specifically, a gasoline engine, a diesel engine, an LPG engine, or the like can be used. The engine 1 has an intake / exhaust device, a fuel injection device, an ignition timing control device, and the like, and can electronically control the engine output. The engine torque is transmitted to the front wheels 5 as the first drive shaft via the input shaft 6, the intermediate shaft 2, the forward / reverse switching device 37, the belt type continuously variable transmission 3 and the differential 4. It has become. The intermediate shaft 2, the forward / reverse switching device 37, the belt type continuously variable transmission 3, the differential 4, and the like are provided in a casing 60.

  The crankshaft (not shown), the input shaft 6 and the intermediate shaft 2 of the engine 1 are disposed so as to be rotatable about the rotation axis A1 and transmit power from the input shaft 6 to the intermediate shaft 2. An oil pump 7 is provided in the path. In this embodiment, a radial piston pump which is a kind of constant discharge type pump is used as the oil pump 7. The configuration of the oil pump 7 will be described with reference to FIGS. 3 is a cross-sectional view in a plane including the rotation axis A1, and FIG. 4 is a cross-sectional view in a plane orthogonal to the rotation axis A1. The oil pump 7 has an inner race 8 provided on the input shaft 6 and an outer race 9 provided on the intermediate shaft 2.

  First, the inner race 8 has a disc shape centered on the rotation axis A1, and the inner race 8 is formed with a plurality of cylinders 10 at predetermined intervals in the circumferential direction. Each cylinder 10 is a substantially cylindrical recess opened in the outer peripheral surface of the inner race 8, and as shown in FIG. 3, the axis B1 of each cylinder 10 and the rotation axis A1 are substantially orthogonal to each other. Yes. Furthermore, as shown in FIG. 4, the rotation axis A1 is located on the extension of the axis B1.

  A piston 11 is disposed in each cylinder 10, and each piston 11 is configured to reciprocate in the direction of the axis B1. That is, the piston 11 is movable in the radial direction of the inner race 8. A recess 12 is formed on the outer end face of each piston 11. The recess 12 is formed in a hemispherical shape, and the ball 13 is held by the recess 12. The ball 13 can roll in the recess 12. On the other hand, an oil chamber 14 is formed between the back end face 10 </ b> A of the cylinder 10 and the piston 11. The oil chamber 14 is provided with an elastic member 15, and a force that pushes the piston 11 out of the cylinder 10 is applied from the elastic member 15 to the piston 11.

  The outer race 9 has an outward flange 35 formed on the intermediate shaft 2 and a cylindrical portion 35 </ b> A continuous with the outward flange 35. The cylindrical portion 35A is disposed so as to surround the outer side of the inner race 8, and a cam surface 36 is formed on the inner periphery of the cylindrical portion 35A. The cam surface 36 is formed in an annular shape with the rotation axis A1 as the center, and has a substantially waveform. In other words, convex portions curved so as to project outward in the radial direction and concave portions curved so as to project inward in the radial direction are alternately and continuously arranged in the circumferential direction. ing. The cam surface 36 is in contact with the ball 13 attached to the inner race 8, and the ball 13 can roll along the cam surface 36.

  On the other hand, the input shaft 6 is provided with a suction oil passage 16 and a discharge oil passage 17 in the rotation axis direction, and two annular grooves 16 </ b> A and 17 </ b> A are formed on the outer peripheral surface of the input shaft 6. The annular grooves 16A and 17A are arranged at different positions in the rotation axis direction. The suction oil passage 16 and the annular groove 16A are connected, and the discharge oil passage 17 and the annular groove 17A are connected. Incidentally, a partition wall 61 extending in the radial direction of the rotation axis A <b> 1 is provided in the casing 60, and the shaft hole 20 is formed in the partition wall 61. The partition wall 61 is disposed between the engine 1 and the oil pump 7 in the rotation axis direction. The partition wall 61 is provided with an intake oil passage 18 and a discharge oil passage 19. The partition wall 61 extends in a direction intersecting the rotation axis A <b> 1, and the input shaft 6 is rotatably disposed in the shaft hole 20 of the partition wall 61. The suction oil passage 18 and the discharge oil passage 19 are opened to the shaft hole 20, and the suction oil passage 18 and the annular groove 16A are connected, and the discharge oil passage 19 and the annular groove 17A are connected.

  In this way, the intake oil passage 16 and the intake oil passage 18 are connected to each other when the input shaft 6 is rotating or stopped, and the discharge oil passage 17 and the discharge oil passage 19 are connected. It is configured to be connected. Further, a sealing device 20 </ b> A for preventing oil in the suction oil passage 18, the discharge oil passage 19 and the annular grooves 16 </ b> A and 17 </ b> A from leaking from the shaft hole 20 is provided. Further, the casing 60 is provided with an oil pan 21, and the suction oil passage 18 is connected to the oil pan 21. The oil pan 21 stores the oil that has been supplied to the belt type continuously variable transmission 3 and the forward / reverse switching device 37.

  Further, an oil passage 22 that connects the suction oil passage 16 and the oil chamber 14 is provided, and an oil passage 23 that connects the discharge oil passage 17 and the oil chamber 14 is provided. 24 is provided, and a check valve 25 is provided in the oil passage 23. The check valve 24 is configured to allow the oil in the suction oil passage 16 to be sucked into the oil chamber 14 and prevent the oil in the oil chamber 14 from flowing back into the suction oil passage 16. In contrast, the check valve 25 allows the oil in the oil chamber 14 to be discharged into the discharge oil passage 17 and prevents the oil in the discharge oil passage 17 from flowing back into the oil chamber 14. is doing.

  On the other hand, as shown in FIG. 1, the discharge oil passage 19 is branched in two directions, one branched is connected to the hydraulic control device 26, and the other branched is hydraulically controlled via the oil motor 27. It is connected to the device 26. In FIG. 1, as an example of the oil motor 27, a circumscribed gear motor that is a kind of a constant discharge amount type motor is shown. That is, the oil motor 27 has a pair of meshed gears 70 and 71, a suction port 72 and a discharge port 73. The suction port 72 is connected to the discharge oil passage 19, and the discharge port 73 is connected to the hydraulic control device 26 via the oil passage 34.

  The hydraulic control device 26 has a function of controlling the forward / reverse switching device 37 and the belt-type continuously variable transmission 3, and a function of lubricating and cooling the heat generating portions of the forward / backward switching device 37 and the belt-type continuously variable transmission 3. Have. The hydraulic control device 26 includes a hydraulic circuit (not shown), a solenoid valve (not shown), and the like, and oil is transferred from the hydraulic control device 26 to the forward / reverse switching device 37 and the belt-type continuously variable transmission 3. An oil passage 74 for supplying the oil is provided. Further, as shown in FIG. 2, a transmission 77 that connects at least one of the gears 70 and 71 of the oil motor 27 and the rear wheel 76 that is the second drive shaft so as to be able to transmit power is provided. .

  A forward / reverse switching device 37 is provided on a path from the intermediate shaft 2 to the belt type continuously variable transmission 3. The forward / reverse switching device 37 is a mechanism that is employed when the rotational direction of the engine 1 is limited to one direction, and is configured to switch the rotational direction of the primary shaft 38 relative to the rotational direction of the intermediate shaft 2. It has. In the example shown in FIG. 2, a double pinion type planetary gear mechanism is employed as the forward / reverse switching device 37. That is, a sun gear 39 that rotates integrally with the intermediate shaft 2, a ring gear 40 that is arranged concentrically with the sun gear 39, a pinion gear 41 that meshes with the sun gear 39, and another pinion gear 42 that meshes with the pinion gear 41 and the ring gear 40. The pinion gears 41 and 42 are held by the carrier 43 so as to rotate and revolve freely. The carrier 43 and the primary shaft 38 are connected to rotate integrally.

  Further, a forward clutch 44 for selectively connecting / releasing the intermediate shaft 2 and the carrier 43 is provided. Further, a reverse brake 45 that reverses the rotation direction of the primary shaft 38 with respect to the rotation direction of the intermediate shaft 2 by selectively fixing the ring gear 40 is provided. Engagement / release of the forward clutch 44 and the reverse brake 45 is controlled by the hydraulic control device 26.

  The belt-type continuously variable transmission 3 includes a primary pulley 46 and a secondary pulley 47 arranged in parallel to each other, and a belt 48 is wound around the primary pulley 46 and the secondary pulley 47. Further, a hydraulic servo mechanism 49 that controls the clamping pressure applied from the primary pulley 46 to the belt 48 and a hydraulic servo mechanism 50 that controls the clamping pressure applied from the secondary pulley 47 to the belt 48 are provided. The hydraulic pressure in the hydraulic chambers (not shown) of the hydraulic servo mechanisms 49 and 50 is controlled by the hydraulic control device 26.

  The primary pulley 46 is configured to rotate integrally with the primary shaft 38, and the secondary pulley 47 is configured to rotate integrally with the secondary shaft 51. The primary shaft 38 and the secondary shaft 51 are arranged in parallel with each other, and the torque of the secondary shaft 51 is transmitted to the front wheel 5 via the transmission mechanism 52 and the differential 4.

  Next, the control system of the vehicle Ve shown in FIG. 2 will be described. An electronic control unit 53 is provided as a controller for controlling the entire vehicle Ve. The electronic control unit 53 receives signals such as acceleration request, braking request, engine speed, throttle opening, intermediate shaft 2 speed, primary shaft 38 speed, secondary shaft 51 speed, and shift position. Is done. In contrast, the electronic control device 53 outputs a signal for controlling the hydraulic control device 26, a signal for controlling the engine 1, and the like.

  The operation of the vehicle Ve configured as described above will be described. When the engine torque is transmitted to the input shaft 6, the torque of the input shaft 6 is transmitted to the intermediate shaft 2 via the oil pump 7. The principle of torque transmission in the oil pump 7 will be described later. Here, when the forward position is selected as the shift position, the forward / reverse switching device 37 engages the forward clutch 44 and releases the reverse brake 45. As a result, the intermediate shaft 2 and the carrier 43 are coupled so as to be integrally rotatable, and the torque of the intermediate shaft 2 is transmitted to the primary shaft 38. In this case, the rotation direction of the intermediate shaft 2 and the rotation direction of the primary shaft 38 are the same.

  On the other hand, when the reverse position is selected as the shift position, the reverse brake 45 is engaged and the forward clutch 44 is released. As a result, the ring gear 40 becomes a reaction force element, and the torque of the intermediate shaft 2 is transmitted to the primary shaft 38. In this case, the rotation direction of the primary shaft 38 is opposite to the rotation direction of the intermediate shaft 2.

  On the other hand, in the belt type continuously variable transmission 3, the supply state of pressure oil in the hydraulic servo mechanisms 49 and 50 is controlled by the hydraulic control device 26. Specifically, the flow rate of the pressure oil supplied to the hydraulic servo mechanism 49 is controlled, and the winding radius of the belt 48 in the primary pulley 46 and the winding radius of the belt 48 in the secondary pulley 47 are controlled. The gear ratio of the continuously variable transmission 3, that is, the ratio between the rotational speed of the primary shaft 38 and the rotational speed of the secondary shaft 51 can be controlled steplessly (continuously). In addition to this shift control, the clamping force applied from the secondary pulley 47 to the belt 48 is adjusted, and the torque capacity of the belt type continuously variable transmission 3 is controlled.

  For example, the target driving force in the vehicle Ve is determined based on the vehicle speed and acceleration request (for example, accelerator opening), and the target engine output is determined based on the determination result. A target engine speed that achieves the target engine output with optimum fuel efficiency is obtained, and the gear ratio of the belt-type continuously variable transmission 3 is controlled so that the actual engine speed approaches the target engine speed. In parallel with these controls, the opening of the electronic throttle valve and the like are controlled so that the actual engine torque approaches the target engine torque. As described above, the torque of the intermediate shaft 2 is transmitted to the transmission mechanism 52 via the forward / reverse switching device 37 and the belt-type continuously variable transmission 3, and the torque of the transmission mechanism 52 is transmitted via the differential 4. Then, it is transmitted to the front wheel 5.

  Next, the principle of torque transmission between the intermediate shaft 2 and the input shaft 6 will be described. When the engine 1 is operated, torque is generated in a direction that rotates the inner race 8 in a predetermined direction of FIG. 4, for example, clockwise. In the first embodiment, the torque transmitted between the input shaft 6 and the intermediate shaft 2 and the oil discharge amount from the oil pump 7 are controlled as follows. First, the ball 13 attached to the inner race 8 is urged toward the outside of the cylinder 10 by the urging force of the elastic member 15, and when the pressing inner race 8 rotates, the ball 13 is moved to the outer race 9. The ball 13 and the piston 11 reciprocate in the direction of the axis B <b> 1 in the cylinder 10 due to the rolling irregularities in the radial direction of the cam surface 36.

  As the piston 11 reciprocates in the cylinder 10, the volume of the oil chamber 14 changes. That is, when the piston 11 moves outward along the axis B1, the volume of the oil chamber 14 is expanded, and when the piston 11 moves inward along the axis B1, the volume of the oil chamber 14 is reduced. When the volume of the oil chamber 14 is enlarged, the oil chamber 14 becomes negative pressure. Then, the check valve 24 is opened, and the oil in the oil pan 21 is sucked into the oil chamber 14 via the suction oil passage 18 and the suction oil passage 16. In this case, since the check valve 25 is closed, the oil in the discharge oil passage 17 does not flow back into the oil chamber 14.

  Next, when the piston 11 moves inward with the relative rotation of the inner race 8 and the outer race 9, the volume of the oil chamber 14 is reduced, and the internal hydraulic pressure rises. When the hydraulic pressure in the oil chamber 14 becomes higher than the hydraulic pressure in the suction oil passage 16, the check valve 24 is closed. As a result, the oil in the suction oil passage 16 is not sucked into the oil chamber 14 and the oil in the oil chamber 14 is prevented from flowing back into the suction oil passage 16. On the other hand, the check valve 25 is opened when the oil pressure in the oil chamber 14 becomes higher than the oil pressure in the discharge oil passage 17 due to the reduction in volume of the oil chamber 14. As a result, the oil in the oil chamber 14 is supplied to the oil motor 27 via the discharge oil passage 17 and the discharge oil passage 19. Thereafter, the oil is discharged from the oil pump 7 by the piston 11 repeating the reciprocating motion.

  On the other hand, part of the oil discharged to the discharge oil passage 19 is supplied to the suction port 72 of the oil motor 27, and the gear 70 is changed according to the difference between the oil pressure of the discharge oil passage 19 and the oil pressure of the oil passage 34. , 71 changes the amount of oil passing through. Here, when the oil passes between the gear 70 and the gear 71, the mechanical energy of the oil is converted into the mechanical energy of the gears 70 and 71, and the gears 70 and 71 rotate. Here, the mechanical energy of the oil can be expressed by pressure × flow rate, and the mechanical energy of the gears 70 and 71 can be expressed by torque which is power × rotational speed. Then, the torque of at least one of the gears 70 and 71 is transmitted to the rear wheel 76 via the transmission 77. As described above, the vehicle Ve shown in FIG. 2 is a four-wheel drive vehicle capable of transmitting torque to the front wheels 5 and the rear wheels 76.

  As described above, the oil in the discharge oil passage 19 is supplied to the hydraulic control device 26 via the oil motor 27. On the other hand, part of the oil in the discharge oil passage 19 bypasses the oil motor 27 and is supplied to the hydraulic control device 26. In this way, when oil is supplied to the hydraulic control device 26, the solenoid valve of the hydraulic control device 26 is controlled according to the required flow rate of oil in the forward / reverse switching device 37 and the belt-type continuously variable transmission 3, and discharged. The amount of oil discharged from the oil passage 19 and the oil passage 34 to the oil passage 74 is controlled. In this way, the oil pressure in the oil passages 19 and 34 is regulated. The oil supplied to the forward / reverse switching device 37 and the belt type continuously variable transmission 3 thereafter flows into the oil pan 21 and is then sucked into the oil pump 7 via the suction oil passage 18.

  By the way, the oil pressure in the discharge oil passage 19 affects the operating characteristics of the piston 11 in the cylinder 10. That is, when the force that presses the piston 11 inward is the same, and the piston 11 operates inward to reduce the volume of the oil chamber 14, the higher the oil pressure in the discharge oil passage 19, the higher the discharge from the oil chamber 14. The amount of oil discharged per unit time to the oil passage 17 decreases. On the other hand, the lower the oil pressure in the discharge oil passage 19, the greater the amount of oil per unit time discharged from the oil chamber 14 to the discharge oil passage 17.

  Further, the higher the oil pressure in the discharge oil passage 19, the more difficult the oil pressure in the oil chamber 14 decreases, and the load necessary to operate the piston 11 inward increases. On the other hand, the lower the oil pressure in the discharge oil passage 19, the more easily the oil pressure in the oil chamber 14 decreases, and the load necessary to operate the piston 11 inward decreases. In the first embodiment, the inner race 8 and the outer race 9 rotate relative to each other, whereby the ball 13 rolls on the cam surface 36 and a load that presses the piston 11 inward from the outer race 9 is applied. It has become. Therefore, the higher the load required to move the piston 11 inward, the higher the circumferential load required to rotate the inner race 8 and the outer race 9 relative to each other. In other words, the torque transmitted via the oil pump 7 can be increased.

  As described above, in the first embodiment, the mechanical energy of the oil discharged from the oil pump 7 is converted into the mechanical energy (power) of the gears 70 and 71, and the torque of at least one of the gears 70 and 71 is converted. Can be transmitted to the rear wheel 76, the driving force of the vehicle Ve is increased, and the starting performance and power performance of the vehicle Ve are improved. That is, part of the required torque corresponding to the required driving force can be covered by the torque transmitted from the oil motor 27 to the rear wheel 76, and the degree of freedom of control of the operating state of the engine 1 is expanded. It becomes easier to bring the driving state closer to the optimum fuel consumption line.

  Therefore, the fuel consumption of the engine 1 is further improved. Furthermore, the belt-type continuously variable transmission 3 and the forward / reverse switching device 37 can be lubricated and cooled by the oil discharged from the oil motor 27, and the lubricating performance and cooling performance are further improved. Further, the oil discharged from the oil motor 27 can increase the engagement hydraulic pressure of the forward clutch 44 and the reverse brake 45 of the forward / reverse switching device 37, and the power transmission efficiency of the forward / reverse switching device 37 is reduced. Can be suppressed.

  The correspondence between the configuration described in the first embodiment and the configuration of the present invention will be described. The input shaft 6 and the inner race 8 correspond to the first rotating member of the present invention. The race 9 corresponds to the second rotating member of the present invention, the suction oil passage 18 corresponds to the first oil passage of the present invention, and the discharge oil passage 19 corresponds to the second oil passage of the present invention. The engine 1 corresponds to the driving force source of the present invention, the front wheel 5 corresponds to “a wheel to which the power of the driving force source is transmitted” in the present invention, and the rear wheel 76 corresponds to “the wheel transmitted to the wheel” of the present invention. The oil motor 27 corresponds to the conversion device of the present invention, and at least one of the gears 70 and 71 corresponds to the third rotating member of the present invention. That is, in the power train shown in FIG. 1 and FIG. 2, “wheels to which the power of the driving force source is transmitted (front wheel 5)” and “mechanical energy of oil are converted into torque, and the torque is transmitted. Wheel (rear wheel 76) ".

Will now be described with reference to FIG. 5 the configuration of the second embodiment of the present invention. In the configuration of Example 2 of this, the same configuration as the configuration of Embodiment 1, the description thereof is omitted given the same reference numerals as the configuration of the first embodiment. The configuration of the hydraulic control device 26 in the second embodiment will be specifically described. First, a pressure control valve 80 is provided. The pressure control valve 80 controls the oil pressure in the discharge oil passage 19. The pressure control valve 80 includes a spool 81 operable in a linear direction and an elastic member 82 that urges the spool 81 in a predetermined direction.

  The pressure control valve 80 has an input port 83 and a drain port 84, the input port 83 and the discharge oil passage 19 are connected, and the drain port 84 and the oil passage 94 are connected. The oil passage 94 is connected to the oil passages 34 and 74. Further, a feedback port 85 and a signal pressure port 86 are provided, and the feedback port 85 and the discharge oil passage 19 are connected. Then, an urging force in the same direction as the urging force of the elastic member 82 is applied to the spool 81 according to the signal pressure of the signal pressure port 86, and is opposite to the urging force of the elastic member 82 according to the hydraulic pressure of the feedback port 85. A biasing force in the direction is applied to the spool 81.

  Further, a pressure control valve 87 connected to the oil passage 94 is provided. This pressure control valve 87 controls the oil pressure of the oil passage 94. The pressure control valve 87 includes a spool 88 operable in a linear direction, and an elastic member 89 that urges the spool 88 in a predetermined direction. The pressure control valve 87 has an input port 90 and a drain port 91, and the input port 90 and the oil passage 94 are connected to each other. Further, a feedback port 92 and a signal pressure port 93 are provided, and the feedback port 92 and the oil passage 94 are connected. Then, an urging force in the same direction as the urging force of the elastic member 89 is applied to the spool 88 according to the signal pressure of the signal pressure port 93, and the direction opposite to the urging force of the elastic member 89 according to the oil pressure of the feedback port 92. The urging force is applied to the spool 88.

  Next, the operation of the second embodiment will be described. First, when engine torque is transmitted to the intermediate shaft 2 via the input shaft 6, the oil in the suction oil passage 18 is supplied to the discharge oil passage 19 according to the same principle as in the first embodiment.

  When the oil pressure in the discharge oil passage 19 is equal to or less than a predetermined value, the input port 83 and the drain port 84 are shut off, and the oil in the discharge oil passage 19 is not discharged to the oil passage 94. Therefore, a decrease in the oil pressure of the discharge oil passage 19 is suppressed, or the oil pressure of the discharge oil passage 19 increases. On the other hand, when the hydraulic pressure in the discharge oil passage 19 exceeds a predetermined value, the spool 81 operates to connect the input port 83 and the drain port 84 and is discharged from the discharge oil passage 19 to the oil passage 94. Oil flow increases.

  Accordingly, an increase in the oil pressure of the discharge oil passage 19 is suppressed, or the oil pressure of the discharge oil passage 19 is reduced. In this way, the hydraulic pressure of the discharge oil passage 19 is regulated by the pressure control valve 80. More specifically, by controlling the signal pressure input to the signal pressure port 86 of the pressure control valve 80, the oil pressure PL1 of the discharge oil passage 19 can be controlled. In this way, the differential pressure ΔPL1 between the hydraulic pressure PLO in the suction oil passage 18 and the hydraulic pressure PL1 in the discharge oil passage 19 can be controlled. Here, the torque Tout1 transmitted to the intermediate shaft 2 is obtained by the equation (1).

Tout1≈ΔPL1 · q1 / 2π (1)
In the above formula (1), q1 is the oil discharge volume [cc / rev] of the oil pump 7 per one rotation of the input shaft 6. Therefore, the torque transmitted by the oil pump 7 can be controlled by controlling the signal pressure input to the signal pressure port 86 of the pressure control valve 80. In other words, the transmission torque can be controlled without using a variable displacement pump as the oil pump 7.

  Next, hydraulic control of the oil passage 94 will be described. When the oil pressure in the oil passage 94 is equal to or less than a predetermined value, the input port 90 and the drain port 91 in the pressure control valve 87 are blocked, and the oil in the oil passage 94 is not discharged to the drain port 91. Therefore, a decrease in the oil pressure of the oil passage 94 is suppressed, or the oil pressure of the oil passage 94 increases. On the other hand, when the oil pressure in the oil passage 94 exceeds a predetermined value, the input port 90 and the drain port 91 are communicated with each other by the operation of the spool 88 and the oil discharged from the oil passage 94 to the drain port 91 is discharged. The flow rate increases.

  Accordingly, an increase in the oil pressure of the oil passage 94 is suppressed, or the oil pressure of the oil passage 94 decreases. In this way, the oil pressure in the oil passage 94 is regulated by the pressure control valve 87. More specifically, by controlling the signal pressure input to the signal pressure port 93 of the pressure control valve 87, the oil pressure PL2 of the oil passage 94 can be controlled. In this way, the differential pressure ΔPL2 between the oil pressure PL2 in the oil passage 94 and the oil pressure PL1 in the discharge oil passage 19 can be controlled. Here, the torque Tout2 transmitted from the oil motor 27 to the rear wheel 76 is obtained by Expression (2).

Tout2≈ΔPL2 · q2 / 2π (2)
In the above equation (2), q2 is the oil discharge volume [cc / rev] of the oil motor 27 per one rotation of the gears 70 and 71. Therefore, the torque transmitted from the oil motor 27 to the rear wheel 76 can be controlled by controlling the signal pressure input to the signal pressure port 93 of the pressure control valve 87. In other words, the transmission torque can be controlled without using a variable displacement oil motor as the oil motor 27.

Explaining the correspondence between the configuration described in the second embodiment and the configuration of the present invention, the oil passage 94 corresponds to the third oil passage of the present invention, and the pressure control valve 80 and the pressure control valve 87. but it corresponds to the pressure control valve of the present invention. The correspondence between the other configurations in the second embodiment and the configuration of the present invention is the same as the corresponding relationship between the configuration of the first embodiment and the configuration of the present invention.

Next, the configuration of Embodiment 3 of the present invention will be described with reference to FIG . In the configuration of the real施例3, the same components as in Example 1 and Example 2, the description thereof is omitted denoted by the same reference numerals as the configuration of Example 1 and Example 2.

  In the third embodiment, the configuration of the oil pump 100 is different from the first and second embodiments. This oil pump 100 can be used in place of the oil pump 7 shown in FIG. First, as the oil pump 100, an inscribed oil pump which is a kind of constant discharge amount type oil pump is shown. That is, the oil pump 100 has an inner gear 101 that rotates integrally with the input shaft 6 and an outer gear 102 that rotates integrally with the intermediate shaft 2, and the inner gear 101 and the outer gear 102 are engaged with each other. Yes.

  Further, the intermediate shaft 2 and the input shaft 6 are arranged eccentrically. Further, a crescent (not shown) is formed between the inner gear 101 and the outer gear 102. The oil pump 100 is formed with a suction port 103 and a discharge port 104, the suction port 103 and the suction oil passage 18 are connected, and the discharge port 104 and the discharge oil passage 19 are connected. Further, a clutch 105 is provided on a path from the engine 1 to the input shaft 6. The clutch 105 is controlled by the electronic control unit 53 and controls the torque transmitted between the engine 1 and the input shaft 6.

  Next, a configuration different from that of the second embodiment in the configuration of the hydraulic control device 26 will be described. First, an oil passage 75 branched from the discharge oil passage 19 is provided, and the oil passage 75 and the oil pan 77 are connected. A check valve 78 is provided in the oil passage 75. The check valve 78 has a configuration that allows the oil in the oil pan 77 to flow into the discharge oil passage 19 and prevents the oil in the discharge oil passage 19 from flowing back into the oil pan 77.

  The hydraulic control device 26 has a cut valve (switching valve) 79. The cut valve 79 has ports 79A, 79B, 79C and a spool 79D. The port 79A is connected to the suction port 72 of the oil motor 27 via the oil passage 113, and the port 79B is connected to the discharge oil passage 19. The port 79C is connected to the oil pan 77. The operation of the spool 79D is configured to be controlled by the electronic control unit 53, and control for selectively connecting the port 79A to either the discharge oil passage 19 or the oil pan 77 by the operation of the spool 79D. Alternatively, control for blocking the port 79A can be executed.

  In the third embodiment, the same functions and effects as those of the first and second embodiments can be obtained for the same components as those of the first and second embodiments. In the third embodiment, when the engine torque is transmitted to the front wheels 5, the inner gear 101 and the outer gear 102 are rotated by the rotation of the input shaft 6, and the oil in the suction oil passage 18 is transferred to the oil pump 100. While being sucked into the suction port 103, oil is discharged from the discharge port 104 to the discharge oil passage 19.

  Further, when the engine torque is transmitted to the front wheel 5, the control of the cut valve 79 connects the port 79A and the port 79B and shuts off the port 79C. By such control of the cut valve 79, the oil in the discharge oil passage 19 is supplied to the oil motor 27, and the same effect as in the first and second embodiments is produced. Even when the oil in the suction oil passage 18 is discharged into the discharge oil passage 19 and the oil in the discharge oil passage 19 flows into the oil passage 75, the check valve 78 is closed, so the oil in the discharge oil passage 19 is oil. In addition to being discharged to the pan 77, the oil in the oil pan 77 is not sucked into the discharge oil passage 19.

  On the other hand, when the vehicle Ve travels by repulsion and torque corresponding to the mechanical energy is transmitted from the front wheels 5 to the intermediate shaft 2, the port 78B is shut off by the control of the cut valve 79. . Then, the oil in the discharge oil passage 19 is sucked into the oil pump 100 through the discharge port 104, and the oil is discharged into the suction oil passage 18 through the suction port 103. Thus, when the discharge oil passage 19 becomes negative pressure, the check valve 78 is opened, the oil in the oil pan 77 is sucked, and the oil is sucked through the discharge oil passage 19 and the oil pump 100. It is discharged into the oil passage 18. Then, the check valve 95 is closed, the hydraulic pressure in the suction oil passage 18 is increased, and the torque transmitted from the intermediate shaft 2 to the input shaft 6 is increased. In this way, the braking force due to the rotational resistance of the engine 1, that is, the engine braking force is increased.

  Further, when the vehicle Ve travels by repulsion, the port 79A and the port 79C are connected by the control of the cut valve 79, and the gears 70 and 71 are rotated by the power transmitted from the rear wheel 76, whereby the oil motor 27 is driven. Functions as an oil pump. As a result, the oil in the oil pan 77 is supplied to the oil passages 34 and 94 via the cut valve 79 and the oil motor 27.

In addition, when the vehicle Ve is repulsive,
Tout1 <ΔPL1 · q1 / 2π (3)
By controlling the hydraulic pressure PL1 of the discharge oil passage 19 so that the vehicle oil Ve is switched from the coasting state to the traveling state in which the engine torque is transmitted to the front wheels 5, the discharge amount of the oil pump 100 is substantially reduced. It is possible to cover the necessary oil in the belt type continuously variable transmission 3 and the forward / reverse switching device 37 with the oil supplied to the oil passage 94 from the oil motor 27.

Here, will be described the correspondence between the configuration of the third embodiment and the configuration of the present invention, the check valve 95 is equivalent to put that flow amount control device according to the present invention, the pressure control valve 80, of the present invention corresponds to the pressure control valve, the cut valve 79 is equivalent to the flow amount control device of the present invention, a belt type continuously variable transmission 3 and the forward-reverse switching device 37 is equivalent to the oil necessary part of the present invention, oil The pan 77 corresponds to the oil holding part of the present invention. The correspondence relationship between the other configurations in the third embodiment and the configuration of the present invention is the same as the corresponding relationship between the configurations of the first and second embodiments and the configuration of the present invention.

Next, the configuration of Embodiment 4 of the present invention will be described with reference to FIG . In the configuration of the actual施例4, the same components as in Example 1 and Example 2 and Example 3, the description thereof denoted by the same reference numerals as the configuration of Example 1 and Example 2 and Example 3 Omitted.

  The difference between the fourth embodiment and the third embodiment is that a pressure control valve 106 is provided instead of the check valve 95. The pressure control valve 106 includes a spool 107 that can reciprocate linearly, an elastic member 108 that urges the spool 107 in a predetermined direction, an input port 109 and an output port 110, a signal pressure port 111, and a feedback port. 112. The feedback port 112 is connected to the suction oil passage 18, and an urging force in the same direction as the urging force of the elastic member 108 is applied to the spool 107 according to the hydraulic pressure of the feedback port 112. On the other hand, the signal pressure of the signal pressure port 111 is controlled by the electronic control unit 53, and an urging force opposite to the urging force of the elastic member 108 is applied according to the signal pressure of the signal pressure port 111. Added to the spool 107. The pressure control valve 106 has a configuration in which the input port 109 and the output port 110 are connected when the hydraulic pressure of the signal pressure port 111 is low.

  In the fourth embodiment, when the vehicle Ve travels by transmitting the engine torque to the front wheels 5, the signal pressure of the signal pressure port 111 in the pressure control valve 106 is controlled to a low pressure. The output port 110 is connected, the oil in the oil pan 21 is sucked into the oil pump 100, and the oil is discharged from the oil pump 100 to the discharge oil passage 19. And about the same component as the structure of Example 1 thru | or Example 3, the same effect as Example 1 thru | or Example 3 can be obtained.

  On the other hand, in the fourth embodiment, when the vehicle Ve travels by repulsive force, oil is discharged to the suction oil passage 18 via the discharge oil passage 19 and the oil pump 100 according to the same principle as described in the third embodiment. Is done. In the third embodiment, when the vehicle Ve travels by repulsive force, the signal pressure input to the signal pressure port 111 is increased and the spool 107 is operated to be discharged from the suction oil passage 18 to the oil pan 21. Reduced oil flow. When the oil pressure in the suction oil passage 18 rises, the oil pressure in the feedback port 112 rises and the spool 107 operates against the signal pressure in the signal pressure port 111 and is discharged from the suction oil passage 18 to the oil pan 21. The oil flow increases.

As described above, in the fourth embodiment, the amount of oil discharged from the discharge oil passage 19 to the suction oil passage 18 can be controlled by controlling the signal pressure input to the signal pressure port 111. Therefore, the torque transmitted by the oil pump 100 can be controlled, and the engine braking force can be controlled. Here, the configuration described in Example 4, to describe the correspondence between the configuration of the present invention, the pressure control valve 106 corresponds to put that flow amount control device according to the present invention. The correspondence relationship between the other configurations in the fourth embodiment and the configuration of the present invention is the same as the corresponding relationship between the configurations of the first to third embodiments and the configuration of the present invention.

  Next, a fifth embodiment of the present invention will be described with reference to FIGS. The basic configuration in FIG. 8 is the same as the configuration in FIG. 6 corresponding to the third embodiment. The configuration of the oil motor 200 in FIG. 8 is different from the configuration of the oil motor 27 in FIG. This oil motor 200 can be used in place of the oil motor 27 of FIG. The oil motor 200 is a radial piston type oil motor, and the configuration of the oil motor 200 is the same as the configuration of the oil pump 7 shown in FIGS. 3 and 4. The oil motor 200 has an inner race 208 and an outer race 209, and the inner race 208 is fixed so as not to rotate. The outer race 209 is rotatably arranged, and the outer race 209 and the rear wheel 76 are coupled so as to be able to transmit power. FIG. 9 is a cross-sectional view in a plane perpendicular to the rotation axis of the outer race 209. A plurality of cylinders 210 are formed in the inner race 208 at predetermined intervals in the circumferential direction. Each cylinder 210 is a substantially cylindrical recess opened in the outer peripheral surface of the inner race 208, and as shown in FIG. 9, the axis B2 of each cylinder 210 and the rotation axis of the outer race 209 are substantially orthogonal to each other. It has become.

  A piston 211 is disposed in each cylinder 210, and each piston 211 is configured to be reciprocally movable in the direction of the axis B2. That is, the piston 211 can move in the radial direction of the inner race 208. A concave portion 212 is formed on the outer end face of each piston 211. The recess 212 is formed in a hemispherical shape, and the ball 213 is held by the recess 212. The ball 213 can roll in the recess 212. On the other hand, an oil chamber 214 is formed between the back end surface 210 </ b> A of the cylinder 210 and the piston 211. The oil chamber 214 is provided with an elastic member 215, and a force that pushes the piston 211 out of the cylinder 210 is applied from the elastic member 215 to the piston 211.

  The outer race 209 has a cylindrical portion 235A, and the cylindrical portion 235A is disposed so as to surround the outer side of the inner race 208. A cam surface 236 is formed on the inner periphery of the cylindrical portion 235A. The cam surface 236 is formed in an annular shape centering on the rotation axis, and has a substantially waveform. That is, the convex portions 236A that are curved so as to project toward the inner side in the radial direction and the concave portions 236B that are curved so as to project toward the outer side in the radial direction are alternately and continuously in the circumferential direction. Has been placed. The cam surface 236 and the ball 213 attached to the inner race 208 are in contact with each other, and the ball 213 can roll along the cam surface 236.

  On the other hand, the inner race 208 is provided with a suction oil passage 216 and a discharge oil passage 217 in the axial direction. The suction oil passage 216 and the oil passage 113 are connected, and the discharge oil passage 217 and the oil passage 34 are connected. Further, an oil passage 222 that connects the suction oil passage 216 and the oil chamber 214 is provided, and an oil passage 223 that connects the discharge oil passage 217 and the oil chamber 214 is provided. The oil passage 222 is provided with a check valve 224, and the oil passage 223 is provided with a check valve 225. The check valve 224 has a configuration that allows the oil in the suction oil passage 216 to be sucked into the oil chamber 214 and prevents the oil in the oil chamber 214 from flowing back into the suction oil passage 216. In contrast, the check valve 225 allows the oil in the oil chamber 214 to be discharged into the discharge oil passage 217 and prevents the oil in the discharge oil passage 217 from flowing back into the oil chamber 214. is doing.

  In the fifth embodiment, the same operational effects as those of the first to third embodiments can be obtained with respect to the same components as those of the first to third embodiments. Next, the operation of the oil motor 200 will be described. First, the case where the engine torque is transmitted to the front wheels 5 and the vehicle Ve travels, the port 79A and the port 79B of the cut valve 79 are connected, and the port 79C is shut off will be described. When the rear wheel 76 rotates due to the mechanical energy of the vehicle Ve, the torque is transmitted to the outer race 209, and the outer race 209 and the inner race 208 rotate relative to each other. Then, as the outer race 209 and the inner race 208 rotate relative to each other, the ball 213 rolls along the cam surface 236, and the piston 211 reciprocates in the radial direction of the inner race 208. The action that occurs when the piston 211 moves in the radial direction will be specifically described.

  First, when the ball 213 rolls from the apex of the convex portion 236A toward the concave portion 236B, the piston 211 moves outward in the radial direction. In this case, the oil pressure in the oil chamber 214 is lower than the oil pressure in the suction oil passage 216, the oil in the suction oil passage 216 is supplied to the oil chamber 214 via the oil passage 222, and the check valve 225 is closed. As a result, the oil pressure in the oil chamber 214 increases. For this reason, the pressing force that urges the piston 211 outward along the direction of the axis B2 increases, and the component force in the rotational direction corresponding to the pressing force increases at the contact portion between the ball 213 and the cam surface 236. In this way, the torque in the direction that promotes the rotation of the outer race 209 increases.

  Next, when the ball 213 reaches the deepest portion of the concave portion 236B and the ball 213 reaches the convex portion 236A from the concave portion 236B as the inner race 208 and the outer race 209 rotate relative to each other, the piston 211 moves radially inward. Operates towards. Then, the check valve 225 is opened, the check valve 224 is closed, and the oil in the oil chamber 214 is discharged to the oil passage 34 via the oil passage 217. As described above, along with the relative rotation of the inner race 208 and the outer race 209, the oil in the oil passage 113 is supplied to the oil passage 34 via the oil motor 200, and the mechanical energy of the oil is changed to the piston 211. And a part of the operation force in the radial direction of the piston 211 is converted into a component force in a direction that promotes the rotation of the outer race 209, that is, torque. Therefore, also in the fifth embodiment, the same effect as that of the first embodiment can be obtained.

  On the other hand, when the vehicle Ve travels with the power of the engine 1 without transmitting torque to the rear wheel 76, the port 79A of the cut valve 79 is shut off. Further, the rotational torque of the rear wheel 76 is transmitted to the outer race 209, and the piston 211 operates in the radial direction. Thus, when the piston 211 operates radially outward, no oil is supplied to the oil chamber 214 even if the check valve 24 is opened. Further, when the piston 211 operates inward in the radial direction, the oil chamber 214 becomes high pressure, the check valve 225 is opened, and the oil in the oil chamber 214 is discharged. For this reason, even if the relative rotation between the inner race 208 and the outer race 209 is continued, the oil is not sucked into the oil chamber 214 and the oil pressure in the oil chamber 214 does not increase. That is, the piston 211 stops at the innermost operating position, and the frictional force between the ball 213 and the cam surface 236 is reduced. Therefore, it is possible to avoid a part of the power of the engine 1 being wasted by the oil motor 200.

The oil motor 200 shown in the fifth embodiment can be used in place of the oil motor 27 in the fourth embodiment. Here, the correspondence between the configuration described in the fifth embodiment and the configuration of the present invention will be described. The oil motor 200 corresponds to the conversion device of the present invention, and the oil chamber 214 corresponds to the hydraulic chamber of the present invention. and, outer race 209 is equivalent to the third rotating member in the present invention, the piston 211 and the ball 213 corresponds to the operation member in the present invention, the cut valve 79 corresponds to the flow amount control device of the present invention . The correspondence relationship between the other configurations in the fifth embodiment and the configuration of the present invention is the same as the corresponding relationship between the configurations of the first to fourth embodiments and the configuration of the present invention.

  Next, an example of control that can be executed in the third to fifth embodiments having the cut valve 79 will be described based on the flowchart of FIG. First, the target torque transmitted to the front wheels 5 and the target torque transmitted to the rear wheels 76 are calculated based on signals such as the vehicle speed and acceleration request and data stored in the electronic control unit 53 (step S301). Following this step S301, it is determined whether or not the target torque to be transmitted to the rear wheel 76 is "zero Newton meter" (step S302). If the determination in step S302 is affirmative, control for blocking the port 79B of the cut valve 79 is executed (step S303), and the process proceeds to step S304.

  On the other hand, if a negative determination is made in step S302, the target oil pressure change rate ΔPL2 of the oil passage 94 is calculated (step S305), and the process proceeds to step S304. In step S305, the above-described equation (2) is used. In step S304, the target input torque transmitted from the engine 1 to the forward / reverse switching device 37 and the belt type continuously variable transmission 3 is calculated. Subsequent to step S304, the target oil pressure change rate ΔPL1 in the discharge oil passage 19 is calculated (step S306). In step S306, the above-described equation (1) is used. Subsequent to step S306, the target hydraulic pressure PL1 and the target hydraulic pressure PL2 are calculated (step S307). Following this step S307, the pressure control valve 80 is controlled so that the actual oil pressure in the discharge oil passage 19 approaches the target oil pressure PL1, and the pressure control valve 87 is adjusted so that the actual oil pressure in the oil passage 94 approaches the target oil pressure PL2. Control is performed (step S308), and the control routine shown in FIG. 10 is terminated.

  In the embodiments corresponding to FIGS. 1, 5, 6, and 7, although not particularly shown, the power of the configuration that transmits the power of at least one of the gears 70 and 71 to the front wheel 5. It is also possible to adopt a train. When this power train is employed, the “wheel to which the power of the driving force source is transmitted” and the “wheel to which the mechanical energy of oil is converted into torque and the torque is transmitted” are the same.

  Although not particularly shown in the examples corresponding to FIGS. 8 and 9, it is also possible to employ a power train configured to transmit the power of the outer race 209 to the front wheels 5. When this power train is employed, the “wheel to which the power of the driving force source is transmitted” and the “wheel to which the mechanical energy of oil is converted into torque and the torque is transmitted” are the same.

  Further, although not shown in any of the embodiments, it is also possible to employ a power train configured to transmit engine torque power to the rear wheels and transmit oil motor gear power to the front wheels. . Furthermore, in each embodiment, a motor / generator may be used as the driving force source instead of the engine, or an engine and a motor / generator may be used as the driving force source.

It is a conceptual diagram which shows Example 1 of the power transmission device of this invention. It is a conceptual diagram which shows the power train corresponding to Example 1 of the power transmission device of this invention, and its control system. It is sectional drawing which shows the structural example of the oil pump shown by FIG. It is sectional drawing which shows the structural example of the oil pump shown by FIG. It is a conceptual diagram which shows Example 2 of the power transmission device of this invention. It is a conceptual diagram which shows Example 3 of the power transmission device of this invention. It is a conceptual diagram which shows Example 4 of the power transmission device of this invention. It is a conceptual diagram which shows Example 5 of the power transmission device of this invention. It is a fragmentary sectional view of the oil motor corresponding to Example 5 of this invention. 10 is a flowchart illustrating an example of control that can be executed in the third to fifth embodiments.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Engine, 2 ... Intermediate shaft, 5 ... Front wheel, 6 ... Input shaft, 7 ... Oil pump, 8 ... Inner race, 9,209 ... Outer race, 18 ... Intake oil passage, 19 ... Discharge oil passage, 27, DESCRIPTION OF SYMBOLS 200 ... Oil motor, 70, 71 ... Gear, 76 ... Rear wheel, 79 ... Cut valve, 80, 87, 106 ... Pressure control valve, 95 ... Check valve, 211 ... Piston, 213 ... Ball, 214 ... Oil chamber.

Claims (3)

The first rotating member and the second rotating member are connected so as to be capable of transmitting power, and the relative rotation between the first rotating member and the second rotating member sucks oil from the first oil passage. And an oil pump having a configuration for discharging the sucked oil to the second oil passage, and the first rotating member and the second rotating member between the driving force source and the wheels. In the power transmission device configured to transmit power via,
A conversion device is provided for converting mechanical energy of oil discharged from the oil pump into mechanical energy transmitted to the wheels ;
The conversion device includes an oil motor, and the oil in the second oil passage has a configuration reaching the third oil passage via the oil motor,
The oil motor has a third rotating member that is rotated by the oil pressure, and the torque of the third rotating member is transmitted to the wheels.
When the mechanical energy due to the repulsive running of the vehicle is transmitted to the second rotating member and the mechanical energy is transmitted to the driving force source via the first rotating member, the driving It has a configuration in which braking force is generated by a force source,
When mechanical energy due to repulsive running of the vehicle is transmitted to the second rotating member, the oil pump is configured to discharge oil sucked from the second oil passage to the first oil passage. Has more,
By controlling the flow rate of the oil in the first oil passage, a flow control device for controlling the power transmitted to the first rotary member from said second rotary member is characterized that you have provided Power transmission device. The first rotating member and the second rotating member are connected so as to be capable of transmitting power, and the relative rotation between the first rotating member and the second rotating member sucks oil from the first oil passage. And an oil pump having a configuration for discharging the sucked oil to the second oil passage, and the first rotating member and the second rotating member between the driving force source and the wheels. In the power transmission device configured to transmit power via,
A conversion device is provided for converting mechanical energy of oil discharged from the oil pump into mechanical energy transmitted to the wheels;
Before Symbol converter includes an oil motor, together with the second oil passage of the oil has a structure that leads to a third oil passage via said oil motor,
The oil motor has a third rotating member that is rotated by the oil pressure, and the torque of the third rotating member is transmitted to the wheels .
A pressure control valve that controls the oil pressure of the first oil passage and the oil pressure of the second oil passage in the same manner, and a flow rate control that connects the oil motor to either the second oil passage or the oil holding portion. A device and an oil required portion provided in a power transmission path from the second rotating member to the wheel,
When the oil pressure of the first oil passage and the oil pressure of the second oil passage are controlled to be the same, by connecting the oil holding portion and the oil motor, the oil of the oil holding portion is moving force transmission device, characterized in that the structure to be supplied to the oil required portion by way of the oil motor has more. The first rotating member and the second rotating member are connected so as to be capable of transmitting power, and the relative rotation between the first rotating member and the second rotating member sucks oil from the first oil passage. And an oil pump having a configuration for discharging the sucked oil to the second oil passage, and the first rotating member and the second rotating member between the driving force source and the wheels. In the power transmission device configured to transmit power via,
A conversion device is provided for converting mechanical energy of oil discharged from the oil pump into mechanical energy transmitted to the wheels;
The conversion device includes an oil motor, and the oil in the second oil passage has a configuration reaching the third oil passage via the oil motor,
The oil motor has a third rotating member that is rotated by the oil pressure, and the torque of the third rotating member is transmitted to the wheels.
A hydraulic chamber formed in a path from the second oil passage to the third oil passage, and a reciprocal movement according to the hydraulic pressure of the hydraulic chamber and a contact with the third rotating member The oil motor further includes an operating member that transmits power to the third rotating member in accordance with a resultant force, and the operating member and the hydraulic member are increased as the hydraulic pressure in the hydraulic chamber increases. The oil motor further includes a configuration for increasing torque transmitted to and from the third rotating member,
By reducing the amount of oil supplied to the hydraulic chamber from the second oil passage, the hydraulic chamber pressure suppresses the flow control device to increase of further dynamic power transmission, characterized in that provided apparatus.

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