JP2015148321A - Vehicle driving device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vehicle driving device that can drive an oil pump when an engine is stopped, and that restrains upsizing of the device.SOLUTION: A vehicle driving device comprises: a clutch 11 that arbitrarily transmits or interrupts power between an engine 2 and a speed change mechanism 20; a one-way clutch 12 that interrupts the transmission of power from the clutch to the engine; an oil pump 13 that is connected to a rotating shaft 7 connecting the clutch and the one-way clutch and driven by the rotation of the rotating shaft; and a torque converter 5 that is arranged between the engine and the clutch. The one-way clutch is arranged between the torque converter and the clutch.

Description

  The present invention relates to a vehicle drive device.

  Conventionally, there is a vehicle drive device that can drive an oil pump when the engine is stopped. For example, Patent Document 1 discloses a vehicle drive device having an engine output system that outputs power from an engine and a power transmission system that transmits power from the engine output system to drive wheels. An oil pump that supplies hydraulic oil to the speed change mechanism; a first power transmission path that is provided between the engine output system and the oil pump and connects the engine output system and the oil pump at a predetermined speed ratio; A first one-way clutch, which is incorporated in the transmission path and transmits power from the engine output system to the oil pump while interrupting power from the oil pump to the engine output system, is provided between the power transmission system and the oil pump. , A second power transmission path for connecting the power transmission system and the oil pump at a predetermined gear ratio, and a power transmission system that is incorporated in the second power transmission path and transmits power from the power transmission system to the oil pump. On the other hand, the vehicle drive device has a second one-way clutch that cuts off the power from the oil pump to the power transmission system, and the power is transmitted to the oil pump via the first power transmission path or the second power transmission path. Technology is disclosed.

JP 2012-71752 A

  It is desirable to be able to suppress an increase in the size of the apparatus by adding a configuration that can drive the oil pump when the engine is stopped. For example, if one-way clutches are arranged on both sides in the axial direction with respect to the oil pump, the axial length may be extended, and it may be difficult to reduce the size of the vehicle drive device.

  An object of the present invention is to provide a vehicle drive device that can drive an oil pump while the engine is stopped and that can suppress the increase in size of the device.

  The vehicle drive device of the present invention includes a clutch that arbitrarily transmits or cuts power between an engine and a speed change mechanism, a one-way clutch that cuts off transmission of power from the clutch toward the engine, the clutch, An oil pump connected to a rotating shaft that connects to the one-way clutch and driven by rotation of the rotating shaft; and a torque converter disposed between the engine and the clutch, wherein the one-way clutch includes the torque It is arranged between the converter and the clutch.

  In the vehicle drive device, further, a second one-way clutch provided between the rotating shaft and the oil pump, a transmission path for transmitting the power of the engine to the oil pump without passing through the one-way clutch, It is preferable to include a third one-way clutch provided in the transmission path and blocking transmission of power from the oil pump toward the engine.

  In the vehicle drive device, it is preferable that the torque converter includes a lock-up clutch, and the one-way clutch is disposed between the turbine runner and the lock-up clutch of the torque converter and the rotation shaft. .

  Preferably, the vehicle drive device further includes a control unit that automatically stops and restarts the engine, and the control unit automatically stops the engine while the clutch is engaged.

  The vehicle drive device further includes a control unit that automatically stops and restarts the engine, the torque converter includes a lock-up clutch, and the control unit slips the lock-up clutch. It is preferable to restart the engine.

  The vehicle drive apparatus further includes a control unit that automatically stops and restarts the engine, the torque converter includes a lock-up clutch, and the control unit is configured to start the engine from a state where the engine is stopped. When restarting the vehicle and starting the vehicle, it is preferable to slip the lock-up clutch while the vehicle speed is equal to or lower than the predetermined vehicle speed.

  In the vehicle drive device, the torque converter includes a lockup clutch, and further includes an elastic member that suppresses release of the lockup clutch by applying a force in an engagement direction to the lockup clutch. Is preferred.

  A vehicle drive device according to the present invention includes a clutch that arbitrarily transmits or interrupts power between an engine and a transmission mechanism, a one-way clutch that interrupts transmission of power from the clutch to the engine, and a clutch and a one-way clutch. The oil pump is connected to a rotating shaft that is connected and is driven by rotation of the rotating shaft, and a torque converter disposed between the engine and the clutch. The one-way clutch is disposed between the torque converter and the clutch. Has been. According to the vehicle drive device of the present invention, there is an effect that the oil pump can be driven while the engine is stopped, and that the enlargement of the device can be suppressed.

FIG. 1 is a schematic configuration diagram of a vehicle according to the first embodiment. FIG. 2 is a cross-sectional view of a main part of the vehicle drive device according to the first embodiment. FIG. 3 is a diagram illustrating a connection mode of the oil pump and the auxiliary machine of the vehicle according to the first embodiment. FIG. 4 is an operation explanatory diagram of the vehicle drive device according to the first embodiment. FIG. 5 is a diagram illustrating an engine start time of the vehicle drive device according to the first embodiment. FIG. 6 is a time chart relating to engine start of the vehicle drive device of the first embodiment. FIG. 7 is a diagram illustrating the vehicle drive device according to the first embodiment when starting. FIG. 8 is a time chart relating to the start of the vehicle drive device of the first embodiment. FIG. 9 is a diagram illustrating the vehicle drive device according to the first embodiment when traveling at a constant speed. FIG. 10 is a time chart according to the free run of the vehicle drive device of the first embodiment. FIG. 11 is a schematic configuration diagram of a vehicle according to the second embodiment. FIG. 12 is a cross-sectional view of a main part of the vehicle drive device according to the second embodiment. FIG. 13 is a cross-sectional view of a main part of the vehicle drive device according to the third embodiment.

  Hereinafter, a vehicle drive device according to an embodiment of the present invention will be described in detail with reference to the drawings. In addition, this invention is not limited by this embodiment. In addition, constituent elements in the following embodiments include those that can be easily assumed by those skilled in the art or those that are substantially the same.

[First Embodiment]
The first embodiment will be described with reference to FIGS. 1 to 10. The present embodiment relates to a vehicle drive device. FIG. 1 is a schematic configuration diagram of a vehicle according to a first embodiment of the present invention, FIG. 2 is a cross-sectional view of a main part of a vehicle drive device according to the first embodiment, and FIG. The figure which shows the connection aspect of an oil pump and an auxiliary machine, FIG. 4 is operation | movement explanatory drawing of the vehicle drive device which concerns on 1st Embodiment, FIG. 5 is a figure which shows the engine start time of the vehicle drive device which concerns on 1st Embodiment. FIG. 6 is a time chart relating to the engine start of the vehicle drive device of the first embodiment, FIG. 7 is a diagram showing a start time of the vehicle drive device according to the first embodiment, and FIG. 8 is a diagram of the first embodiment. FIG. 9 is a diagram illustrating a time when the vehicle drive device according to the first embodiment travels at a constant speed, and FIG. 10 is a time according to a free run of the vehicle drive device according to the first embodiment. It is a chart.

  The vehicle drive device 1 according to the present embodiment has a structure that can selectively drive a mechanical pump (see reference numeral 13 in FIG. 1) and accessories of the transmission from the engine shaft or the tire shaft side. A differential rotation device (see reference numeral 12 in FIG. 1) that transmits only the driving force from the engine 2 to the engine 2 side of the driving force take-out mechanism of a mechanical pump or auxiliary equipment, and the driving force from either the engine 2 or the tire on the tire side. Due to the structure provided with a differential transmission device (see reference numeral 11 in FIG. 1), when the torque converter 5 or the engine 2 is in a driven state or in an engine stopped state, power from the tire side is not transmitted to the engine 2 side. It has a structure.

  According to the vehicle drive device 1 according to the present embodiment, the oil pump 13 can be driven by power from the tire side when the engine 2 is stopped by adding the second clutch 12 as a differential rotation device. It becomes. In addition, the configuration of the present embodiment in which the second clutch 12 is added is advantageous in that the vehicle drive device 1 is not increased in size as compared with the conventional configuration in which two one-way clutches are arranged on both sides of the oil pump. It is. Therefore, according to the vehicle drive device 1 of the present embodiment, both the ability to drive the oil pump while the engine is stopped and the suppression of the enlargement of the device can be achieved.

  As shown in FIG. 1, a vehicle 100 according to the first embodiment includes an engine 2, a transmission mechanism 20, drive wheels 30, a hydraulic control unit 40, an electric oil pump 9, and a vehicle drive device 1. It consists of The vehicle drive device 1 includes a first clutch 11, a second clutch 12, an oil pump 13, a torque converter 5, and a control unit 50. On the same axis as the engine 2, a damper 4, a torque converter 5, a first clutch 11, and a speed change mechanism 20 are arranged in order from the engine 2.

  The engine 2 converts the combustion energy of the fuel into a rotational motion and outputs it to the output shaft 2a. A damper 4 is provided on the output shaft 2a. The damper 4 absorbs rotational fluctuations and torque fluctuations of the output shaft 2a. The output shaft 2a is connected to the torque converter 5. The torque converter 5 is disposed between the engine 2 and the first clutch 11. The torque converter 5 includes a pump impeller 5a, a turbine runner 5b, a stator 5c, a one-way clutch 5d, a cover 5e, and a lock-up clutch 6.

  The output shaft 2a is connected to the pump impeller 5a via the cover 5e. The pump impeller 5a and the turbine runner 5b transmit torque via the working fluid. The stator 5c amplifies the torque transmitted from the pump impeller 5a to the turbine runner 5b. The one-way clutch 5d restricts the rotation direction of the stator 5c to one direction. The turbine runner 5 b is connected to the rotary shaft 7. The lockup clutch 6 transmits power directly from the cover 5e to the rotary shaft 7 by being engaged.

  The rotating shaft 7 is connected to the automatic transmission 60. The automatic transmission 60 includes the first clutch 11 and the transmission mechanism 20. The first clutch 11 is a clutch that arbitrarily transmits or cuts power between the engine 2 and the speed change mechanism 20. In the present embodiment, the first clutch 11 is interposed between the rotary shaft 7 and the input shaft 26 of the speed change mechanism 20. The output shaft 27 of the speed change mechanism 20 is connected to the drive wheels 30.

  An oil pump 13 and an auxiliary machine 14 are connected to the rotary shaft 7. The oil pump 13 and the auxiliary machine 14 are driven by the rotation of the rotary shaft 7. The oil pump 13 is a mechanical oil pump (MOP) that sucks and discharges oil by being rotationally driven by transmitted power. The vehicle 100 is provided with an electric oil pump (EOP) 9. The electric oil pump 9 sucks and discharges oil by power generated by consuming electric power. The electric oil pump 9 of the present embodiment is configured to include a motor, and is operated by electric power supplied from a battery (not shown).

  As shown in FIG. 2, the automatic transmission 60 includes a planetary gear mechanism 16 and a reverse brake 15 in addition to the transmission mechanism 20 and the first clutch 11. The planetary gear mechanism 16, the first clutch 11, and the reverse brake 15 function as the forward / reverse switching mechanism 10 of the automatic transmission 60. One of the first clutch 11 and the reverse brake 15 is engaged and the other is released to connect the rotary shaft 7 and the input shaft 26. Further, when both the first clutch 11 and the reverse brake 15 are released, the rotary shaft 7 and the input shaft 26 are disconnected.

  The planetary gear mechanism 16 is of a double planetary type and includes a sun gear 16s, a pinion gear 16p, a ring gear 16r, and a carrier 16c. The sun gear 16 s is connected to the rotating shaft 7 and rotates integrally with the rotating shaft 7. The carrier 16 c is connected to the input shaft 26 of the speed change mechanism 20 and rotates integrally with the input shaft 26. One of the pair of pinion gears 16p that mesh with each other further meshes with the sun gear 16s, and the other meshes with the ring gear 16r.

  The first clutch 11 connects or disconnects the sun gear 16s and the carrier 16c. The first clutch 11 of the present embodiment is a friction engagement type, and is, for example, a wet multi-plate clutch. The first clutch 11 connects the sun gear 16s and the carrier 16c by engaging. When the first clutch 11 is engaged, the rotary shaft 7 and the input shaft 26 are connected so that power can be transmitted. When the first clutch 11 is engaged and the reverse brake 15 is released, the torque of the rotating shaft 7 is transmitted to the input shaft 26 as torque in the same direction via the planetary gear mechanism 16. The torque transmitted from the engine 2 to the input shaft 26 with the first clutch 11 engaged causes the drive wheels 30 to generate a driving force in the forward direction. When the control unit 50 causes the vehicle 100 to travel forward, the control unit 50 engages the first clutch 11 and releases the reverse brake 15.

  The reverse brake 15 regulates the rotation of the ring gear 16r. The reverse brake 15 of the present embodiment is a friction engagement type, and is, for example, a wet multi-plate clutch. When engaged, the reverse brake 15 connects the ring gear 16r and the case 28 to restrict the rotation of the ring gear 16r. When the reverse brake 15 is engaged, the ring gear 16r functions as a reaction force receiver and enables transmission of power through the sun gear 16s and the carrier 16c. When the reverse brake 15 is engaged, the rotation input from the engine 2 to the sun gear 16 s is reversed by the planetary gear mechanism 16 and output to the input shaft 26. The torque transmitted from the engine 2 to the input shaft 26 with the reverse brake 15 engaged causes the drive wheels 30 to generate a drive force in the reverse direction. When the vehicle 100 travels backward, the control unit 50 engages the reverse brake 15 and opens the first clutch 11.

  The speed change mechanism 20 includes a primary pulley 21, a secondary pulley 22, a belt 23, an input shaft 26, an output shaft 27, and an output gear 24. The primary pulley 21 is connected to the input shaft 26 and rotates integrally with the input shaft 26. The secondary pulley 22 is connected to the output shaft 27 and rotates integrally with the output shaft 27. An endless belt 23 is stretched between the primary pulley 21 and the secondary pulley 22. The primary pulley 21 and the secondary pulley 22 pinch the belt 23 with the supplied hydraulic pressure. The output gear 24 is disposed on the output shaft 27. The output gear 24 is connected to the left and right drive wheels 30 via a differential gear or the like.

  As shown in FIG. 1, the vehicle 100 is provided with a hydraulic control unit 40. The hydraulic pressure generated by the oil pump 13 and the electric oil pump 9 is sent to the hydraulic control unit 40. The hydraulic control unit 40 regulates the hydraulic pressure sent from the oil pump 13 and the electric oil pump 9 and supplies it to each unit. The hydraulic control unit 40 of this embodiment supplies hydraulic pressure to the torque converter 5, the first clutch 11, and the transmission mechanism 20. For example, the hydraulic control unit 40 controls the hydraulic pressure supplied to the lockup clutch 6 of the torque converter 5. The hydraulic control unit 40 engages or releases the lockup clutch 6 by adjusting the magnitude of the hydraulic pressure supplied to the lockup clutch 6. Further, the hydraulic control unit 40 controls the engagement pressure of the lockup clutch 6 by adjusting the magnitude of the hydraulic pressure to be supplied, so that the lockup clutch 6 is not only fully engaged but also is in a half-engaged state. Can be slipped.

  The hydraulic control unit 40 controls the hydraulic pressure supplied to the first clutch 11 and the reverse brake 15. The hydraulic control unit 40 engages the first clutch 11 and the reverse brake 15 with the supplied hydraulic pressure. Further, the hydraulic control unit 40 can control the first clutch 11 and the reverse brake 15 to be in a half-engaged state or a fully-engaged state, respectively, by adjusting the engagement pressure of the first clutch 11 and the reverse brake 15. it can.

  The hydraulic control unit 40 controls the hydraulic pressure supplied to the primary pulley 21 and the secondary pulley 22. The transmission mechanism 20 continuously changes the transmission ratio according to the hydraulic pressure supplied to the primary pulley 21. Further, the transmission mechanism 20 changes the clamping pressure for clamping the belt 23 in accordance with the hydraulic pressure supplied to the secondary pulley 22.

  The engine 2 is provided with a starter 3. The starter 3 of the present embodiment is a starter motor, and consumes power supplied from a battery to rotate the engine 2.

  The control unit 50 controls each unit of the vehicle 100. The control unit 50 of this embodiment is an electronic control unit having a computer. The control unit 50 is electrically connected to the engine 2, the starter 3, and the hydraulic control unit 40, and controls the engine 2, the starter 3, and the hydraulic control unit 40. The control unit 50 is connected to various sensors 51. The various sensors 51 include a vehicle speed sensor, an engine speed sensor, a turbine speed sensor, an input speed sensor, an accelerator operation amount sensor, a brake operation amount sensor, a shift position sensor, and the like.

  The control unit 50 automatically stops and restarts the engine 2 while traveling or stopping. For example, the control unit 50 automatically stops the engine 2 when an accelerator-off state and a brake-off state are detected during traveling. The control unit 50 restarts the engine 2 when, for example, accelerator-on is detected while the engine 2 is stopped or running while the engine 2 is stopped.

  The vehicle drive device 1 of the present embodiment includes a second clutch 12 that interrupts transmission of power from the first clutch 11 to the engine 2. Thereby, as will be described below, the running resistance when running with the engine 2 stopped is reduced. As shown in FIG. 1, the second clutch 12 of this embodiment is disposed between the first clutch 11 and the engine 2, and interrupts transmission of power from the first clutch 11 to the engine 2. It is a one-way clutch. As the second clutch 12, for example, a sprag type one-way clutch can be used. The second clutch 12 is released when the engine 2 side rotation speed is lower than the first clutch 11 side rotation speed. That is, when the rotation direction of the engine 2 is the forward direction, the second clutch 12 transmits the torque in the forward rotation direction from the engine 2 side to the first clutch 11 side, and interrupts the transmission of the torque in the reverse rotation direction. . Thereby, when the engine 2 is stopped, the second clutch 12 is released, and the transmission of power between the engine 2 and the first clutch 11 is cut off. Therefore, according to the vehicle drive device 1 of the present embodiment, the running resistance when running with the engine 2 stopped is reduced.

  The second clutch 12 of the present embodiment is disposed between the torque converter 5 and the first clutch 11. Thereby, when the engine 2 is stopped, the stirring resistance in the torque converter 5 is reduced. When the engine 2 is stopped, the second clutch 12 is released, and the engine 2 and the torque converter 5 are disconnected from the drive wheels 30. Therefore, there is an advantage that the stirring resistance in the torque converter 5 when traveling with the engine 2 stopped is reduced.

  In the present embodiment, the second clutch 12 is disposed between the turbine runner 5 b and the lockup clutch 6 of the torque converter 5 and the rotating shaft 7. As shown in FIG. 2, the lock-up clutch 6 includes a piston 6a, damper springs 6b and 6c, and a plate 6d. A cover 5e, a piston 6a, a plate 6d, a turbine runner 5b, a stator 5c, and a pump impeller 5a are arranged in this order from the side close to the engine 2 on the same axis as the rotating shaft 7.

  The piston 6 a moves in the axial direction according to the hydraulic pressure adjusted by the hydraulic control unit 40. The piston 6a engages with the cover 5e by moving toward the engine 2 in the axial direction according to the hydraulic pressure. The piston 6a has a friction material 6e, and is frictionally engaged with the cover 5e via the friction material 6e. The piston 6a and the plate 6d are connected via damper springs 6b and 6c.

  The outer ring of the second clutch 12 is connected to the turbine runner 5 b and the plate 6 d, and the inner ring (inner peripheral surface) is connected to the hub 8. The hub 8 is connected to the rotating shaft 7 so as not to rotate relative to the rotating shaft 7. That is, the inner ring of the second clutch 12 rotates integrally with the rotating shaft 7. On the other hand, the outer ring (outer peripheral surface) of the second clutch 12 rotates integrally with the turbine runner 5 b and the plate 6 d of the lockup clutch 6. Therefore, when the second clutch 12 is released, the turbine runner 5 b and the plate 6 d are disconnected from the rotating shaft 7. Thereby, when the engine 2 is stopped, the turbine runner 5b and the plate 6d stop rotating, so that the stirring resistance in the torque converter 5 is reduced.

  As shown in FIG. 2, the second clutch 12 connects the turbine runner 5b, the inner peripheral end of the plate 6d, and the outer peripheral end of the hub 8 in the radial direction. Thereby, the turbine runner 5b and the plate 6d, the second clutch 12, and the hub 8 overlap each other when viewed from the radial direction. For example, the hub 8 can be the same as a hub that connects a plate of a conventional turbine runner or lockup clutch to the rotary shaft 7. In other words, it can be considered that the second clutch 12 is inserted between the blade portion of the turbine runner 5 b and between the plate 6 d and the hub 8. Therefore, an increase in the axial length of the vehicle drive device 1 due to the addition of the second clutch 12 is suppressed.

  The vehicle drive device 1 of the present embodiment can drive the oil pump 13 even when the vehicle 2 travels with the engine 2 stopped, as will be described below. As shown in FIGS. 1 and 2, the oil pump 13 is a pump that is connected to the rotary shaft 7 that connects the first clutch 11 and the second clutch 12 and is driven by the rotation of the rotary shaft 7. The oil pump 13 of the present embodiment is disposed on a shaft different from the rotation shaft 7. As shown in FIG. 2, the oil pump 13 is connected to the rotary shaft 7 via a chain 17. A sprocket 13 b is provided on the rotating shaft 13 a of the oil pump 13. On the other hand, a sprocket 11 b is connected to the drum 11 a of the first clutch 11. The drum 11 a is connected to the rotation shaft 7 and rotates integrally with the rotation shaft 7. The sprocket 11b is arranged coaxially with the rotary shaft 7. An endless chain 17 is spanned between the sprocket 13 b of the oil pump 13 and the sprocket 11 b of the first clutch 11. Therefore, when the rotating shaft 7 rotates, the rotation is transmitted to the oil pump 13 through the chain 17 to drive the oil pump 13 to rotate.

  Further, in the vehicle 100 of this embodiment, as shown in FIG. 1, not only the oil pump 13 but also the auxiliary machine 14 is driven by the rotation transmitted through the chain 17. Specifically, as shown in FIG. 3, a pulley 13c is connected to the rotating shaft 13a of the oil pump 13 in addition to the sprocket 13b. The auxiliary machine 14 includes an alternator 18 and an air conditioner 19. A pulley 18 a is connected to the rotating shaft of the alternator 18. In addition, a pulley 19 a is connected to the rotation shaft of the compressor of the air conditioner 19. An endless belt 35 is stretched around the pulleys 13c, 18a, 19a. Thereby, the alternator 18 and the air conditioner 19 rotate in conjunction with the rotation of the oil pump 13. That is, in the vehicle 100 according to the present embodiment, when the rotary shaft 7 is rotated by the torque transmitted from the engine 2 and the drive wheels 30, the oil pump 13 and the auxiliary machine 14 are rotationally driven by the rotation of the rotary shaft 7.

  For example, as shown by the solid line arrow in FIG. 4, when power is input from the output shaft 2 a of the engine 2 to the torque converter 5, the fluid is transmitted from the torque converter 5 or via the engaged lockup clutch 6. Thus, power is transmitted to the second clutch 12. When the rotational speed of the turbine runner 5b (hereinafter referred to as "turbine rotational speed Nt") and the rotational speed of the rotary shaft 7 are synchronized, the second clutch 12 is engaged and the turbine runner 5b and the lockup clutch 6 are engaged. The power of the engine 2 is transmitted from to the rotary shaft 7. The power input to the rotating shaft 7 is transmitted from the drum 11a of the first clutch 11 to the oil pump 13 through the sprocket 11b and the chain 17 to rotate the oil pump 13.

  Further, as indicated by a broken arrow in FIG. 4, the oil pump 13 is also rotationally driven by the power transmitted from the drive wheel 30 side to the rotary shaft 7 via the speed change mechanism 20 and the first clutch 11. Therefore, for example, when the engine 2 is in a driving state in which the driving wheels 30 are driven, the oil pump 13 and the auxiliary machine 14 are driven by the power of the engine 2 as indicated by solid arrows. On the other hand, when the engine 2 is stopped while the vehicle 100 is traveling, the oil pump 13 and the auxiliary machine 14 are driven by the power transmitted from the drive wheels 30 as indicated by the dashed arrows.

(Stopped)
Next, the operation of the vehicle drive device 1 in each state of the vehicle will be described. When the vehicle 100 is stopped, the controller 50 opens the first clutch 11 and the reverse brake 15 as shown in FIG. In addition, the control unit 50 stops the engine 2 when a stop condition for the engine 2 is satisfied while the vehicle is stopped. The control unit 50 appropriately operates the electric oil pump 9 to supply hydraulic pressure to the hydraulic control unit 40.

(When starting the engine)
The restart of the engine 2 will be described with reference to FIGS. 5 and 6. When the control unit 50 detects a start request for the engine 2 from a state where the engine 2 is stopped, the control unit 50 restarts the engine 2. For example, the control unit 50 restarts the engine 2 when a brake-off is detected while the engine 2 is stopped while the vehicle is stopped. The control unit 50 may restart the engine 2 when the engine 2 needs to be warmed up. When the engine 2 is restarted while the vehicle is stopped, the control unit 50 restarts with the first clutch 11 and the reverse brake 15 opened. With reference to FIG. 6, the flow when the engine 2 is restarted while the vehicle is stopped will be described.

  FIG. 6 shows (a) the vehicle speed, (b) the rotational speed of the engine 2, (c) the rotational speed of the oil pump 13, (d) the command value for the engagement pressure of the lockup clutch 6, (e) the first Command values for the engagement pressure of the clutch 11 are shown. In the column (b), the engine speed Ne, the turbine speed Nt, and the input speed Nin are shown. The input rotation speed Nin is the rotation speed of the input shaft 26 of the transmission mechanism 20.

  When the engine 2 is stopped while the vehicle is stopped, the control unit 50 of the present embodiment keeps the lock-up clutch 6 weakly engaged. The predetermined value P1, which is the value of the command value for the engagement pressure of the lockup clutch 6 at this time, is based on the torque required for driving the oil pump 13. The predetermined value P1 is determined so that, for example, the lockup clutch 6 can transmit a driving torque necessary for the oil pump 13 to discharge oil having a desired pressure.

  The restart of the engine 2 is started at time t1. The controller 50 restarts the engine 2 with the lock-up clutch 6 half-engaged. The control unit 50 rotates the engine 2 with the starter 3. As a result, the engine speed Ne and the turbine speed Nt increase. Since the lock-up clutch 6 is half-engaged, the turbine rotational speed Nt rises to a higher speed earlier than when the lock-up clutch 6 is released. For example, even when the vehicle is stopped for a long time and the amount of oil in the torque converter 5 is reduced, the rotational speed of the rotary shaft 7 increases early due to power transmission via the lock-up clutch 6. The rotational speed of the oil pump 13 (hereinafter simply referred to as “pump rotational speed Np”) increases in conjunction with the increase in the engine rotational speed Ne and the turbine rotational speed Nt.

  The control unit 50 maintains the command value for the engagement pressure of the lockup clutch 6 at the predetermined value P1 even after the restart of the engine 2 is completed. As a result, as shown in FIG. 5, the oil pump 13 continues to be operated by the power of the engine 2 and supplies the necessary hydraulic pressure to the hydraulic pressure control unit 40. Therefore, the first clutch 11 and the reverse brake 15 can be quickly engaged with the start request, and the responsiveness is improved. Further, a sufficient clamping pressure for clamping the belt 23 in the transmission mechanism 20 is ensured. Further, the lock-up clutch 6 is engaged with a minimum engagement pressure within a range of engagement pressures that can generate the hydraulic pressure required for the oil pump 13. Therefore, it is possible to reduce the load on the engine 2 and suppress a decrease in fuel consumption.

  The auxiliary machine 14 is also driven by the power of the engine 2. For this reason, the predetermined value P1 of the engagement pressure of the lockup clutch 6 may be determined so that the oil pressure required for the oil pump 13 can be generated and the necessary power can be transmitted to the auxiliary machine 14. When the discharge pressure or discharge amount of the oil pump 13 is insufficient, the control unit 50 operates the electric oil pump 9 as appropriate to supply the required hydraulic pressure to the hydraulic control unit 40. Moreover, the control part 50 will stop the electric oil pump 9, if the discharge pressure and discharge amount of the oil pump 13 rise to a desired value.

(When starting)
Next, with reference to FIG. 7 and FIG. 8, operation | movement of the vehicle drive device 1 at the time of start is demonstrated. When a start request is made when the engine 2 is stopped and stopped, the control unit 50 restarts the engine 2 to start the vehicle 100. For example, the control unit 50 detects an operation input for switching from accelerator-off to accelerator-on as a start request. In FIG. 8, a start request is detected at time t11. When detecting the start request, the control unit 50 rotates the engine 2 by the starter 3 and restarts the engine 2. When the engine 2 is restarted, the control unit 50 sets the command value for the engagement pressure of the lockup clutch 6 to a predetermined value P1. As a result, the pump rotational speed Np increases as the engine rotational speed Ne and the turbine rotational speed Nt increase. When the engine 2 is started, the power of the engine 2 is transmitted to the rotary shaft 7 by mechanical transmission and fluid transmission via the lock-up clutch 6 as shown in FIG. The lockup clutch 6 transmits a torque necessary for driving the oil pump 13. In fluid transmission, torque transmitted from the pump impeller 5a toward the turbine runner 5b is amplified by the stator 5c.

  The control unit 50 starts the engagement of the first clutch 11 at time t12 after the restart of the engine 2 is completed. The control unit 50 causes the first clutch 11 to slip-engage with the command value of the engagement pressure of the first clutch 11 as the half-engagement value P2. As the first clutch 11 is engaged, the turbine rotational speed Nt and the pump rotational speed Np are decreased, and the turbine rotational speed Nt is synchronized with the input rotational speed Nin. On the other hand, since the lock-up clutch 6 is in the weakly engaged slip state, the influence on the engine speed Ne is small even if the first clutch 11 is engaged.

  The control unit 50 increases the command value for the engagement pressure of the first clutch 11 to the value for complete engagement at time t13. As the engagement pressure of the first clutch 11 increases, the power transmitted from the engine 2 to the rotating shaft 7 is transmitted from the speed change mechanism 20 to the drive wheels 30 via the first clutch 11 as shown in FIG. Is done. Thereby, the vehicle 100 starts. When the vehicle 100 starts, the input rotational speed Nin increases as the vehicle speed increases. As a result, the pump speed Np also increases. The control unit 50 causes the lockup clutch 6 to be semi-engaged while the vehicle speed is equal to or lower than the predetermined vehicle speed V1. In FIG. 8, at time t14, the vehicle speed exceeds the predetermined vehicle speed V1, and the lockup clutch 6 is completely engaged.

  As described above, when the engine 2 is restarted from the state in which the engine 2 is stopped and the vehicle 100 is started, the control unit 50 of the present embodiment causes the lock-up clutch 6 to be halfway while the vehicle speed is equal to or lower than the predetermined vehicle speed V1. Engage. Therefore, the oil pump 13 can be driven more reliably at the start than when the lockup clutch 6 is opened. Therefore, there is an advantage that it is easy to ensure an appropriate hydraulic pressure at a low vehicle speed such as immediately after starting.

  The controller 50 operates the electric oil pump 9 to supply the oil pressure to the oil pressure controller 40 when the oil pressure supplied by the oil pump 13 is insufficient at an extremely low speed (for example, 2.5 km / h or less).

(Constant running)
When the vehicle 100 is traveling at a constant speed by the power of the engine 2, the first clutch 11 is engaged as shown in FIG. In the low to high speed region, the lockup clutch 6 is completely engaged based on the vehicle speed. As a result, the power of the engine 2 is transmitted to the rotary shaft 7 via the lock-up clutch 6 and the second clutch 12 to rotate the oil pump 13 and generate a driving force in the drive wheels 30.

(Free run)
The control unit 50 performs a free run in which the engine 2 is stopped and the vehicle 100 travels by inertia. The free run is executed, for example, with the accelerator off and the brake off during traveling. The control unit 50 stops the engine 2 when a free-run execution condition is satisfied. When the fuel supply of the engine 2 is stopped and the engine speed Ne is reduced, the second clutch 12 is released. As a result, torque fluctuations and rotation speed fluctuations of the engine 2 are not transmitted to the rotating shaft 7. In a vehicle that does not include the second clutch 12, when the engine 2 is automatically stopped during traveling, it is necessary to stop the engine 2 after opening the first clutch 11 in order to suppress a shock due to torque fluctuation. It was.

  On the other hand, in the vehicle drive device 1 according to the present embodiment, when the engine 2 is stopped, the engine 2 side rotation speed and the first clutch 11 side rotation speed of the second clutch 12 are automatically set. The second clutch 12 is released to suppress the occurrence of shock. For this reason, the control part 50 of this embodiment can stop the engine 2 automatically, with the 1st clutch 11 engaged. Therefore, the vehicle drive device 1 of this embodiment can shorten the time required from the execution determination of the free run to the start of the free run, and can improve the fuel consumption.

  The transition to free run will be described with reference to FIG. When the free-run execution condition is satisfied at time t21, the control unit 50 stops the fuel supply of the engine 2. Thereby, the engine speed Ne decreases and the engine 2 stops. Since the vehicle 100 continues running and the first clutch 11 is engaged, the input rotational speed Nin does not change before and after the engine 2 is stopped. When the engine 2 is stopped, the power transmitted from the drive wheels 30 drives the oil pump 13 instead of the power of the engine 2. If the oil pump 13 has already been driven by the power from the drive wheels 30 before the start of the free run, the power transmitted from the drive wheels 30 continues to drive the oil pump 13 after the start of the free run. To do. Thereby, the oil pump 13 rotates even after the engine 2 is stopped, and supplies the hydraulic pressure to the hydraulic pressure control unit 40. The controller 50 keeps the lock-up clutch 6 weakly engaged even during the free run. The command value of the engagement pressure of the lockup clutch 6 at this time is, for example, a predetermined value P1.

  The control unit 50 restarts the engine 2 when returning from the free run. For example, when accelerator-on is detected during free-run execution, the control unit 50 determines that a return request from free-run has been made. The control unit 50 restarts the engine 2 when returning from the free run to the running state using the engine 2 as a power source. When restarting the engine 2, the lockup clutch 6 is preferably engaged. For example, the control unit 50 restarts the engine 2 while causing the lock-up clutch 6 to be half-engaged and slipped. When the engine speed Ne is lower than the input speed Nin, the second clutch 12 is released. Therefore, even if the lockup clutch 6 is completely engaged and the engine 2 is restarted, a shock or the like hardly occurs.

  The control unit 50 according to the present embodiment can variably control the load torque of the auxiliary machine 14 to generate a pseudo engine brake. When starting the free run, the control unit 50 increases the load torque of the auxiliary machine 14 more than before starting the free run. For example, the controller 50 increases the load torque of the auxiliary machine 14 by increasing the power generation amount of the alternator 18 or changing the capacity of the compressor of the air conditioner 19. As a result, the running resistance of the vehicle 100 is increased, so that the feeling of idling when shifting to free run is suppressed. The controller 50 may gradually decrease the increased load torque of the auxiliary machine 14 after shifting to the free run.

  According to the vehicle drive device 1 of the present embodiment, the oil pump 13 can be driven by the power transmitted from the drive wheel 30 side to the rotary shaft 7 when the engine 2 is stopped and traveling. Further, since the connection between the rotary shaft 7 and the oil pump 13 does not have a complicated mechanism such as a one-way clutch, an increase in the shaft length is suppressed. Further, since the oil pump 13 is arranged on a different axis from the rotating shaft 7, the degree of freedom of arrangement of the oil pump 13 is high and an increase in the axial length of the vehicle drive device 1 can be easily suppressed. In the present embodiment, the oil pump 13 is disposed in the outer space in the radial direction than the first clutch 11. Since power is output from the rotating shaft 7 to the oil pump 13 on another shaft by the sprocket 11b, the shaft length of the rotating shaft 7 is suppressed.

  Moreover, since the 2nd clutch 12 is arrange | positioned inside the torque converter 5, it can be added without the increase in axial length. Since the second clutch 12 is arranged so as to overlap the turbine runner 5b and the lockup clutch 6 in the radial direction, an increase in the axial length is suppressed. Therefore, the vehicle drive device 1 according to the present embodiment has an effect that both the oil pump 13 can be driven while the engine 2 is stopped and the increase in the size of the vehicle drive device 1 can be suppressed.

  Further, the oil pump 13 of the present embodiment is disposed on the engine 2 side of the transmission mechanism 20 in the power transmission path. Thereby, the fluctuation | variation of the pump rotation speed Np by a vehicle speed is suppressed rather than the case where the oil pump 13 is arrange | positioned rather than the transmission mechanism 20 at the drive wheel 30 side. Therefore, there is an advantage that fuel consumption can be improved, vibration and noise can be reduced, and the durability of the oil pump 13 can be improved.

[Second Embodiment]
The second embodiment will be described with reference to FIGS. 11 and 12. In the second embodiment, components having the same functions as those described in the first embodiment are given the same reference numerals, and duplicate descriptions are omitted. FIG. 11 is a schematic configuration diagram of a vehicle according to the second embodiment, and FIG.

  Similar to the vehicle drive device 1 of the first embodiment, the vehicle drive device 101 of the present embodiment includes a first clutch 11, a second clutch 12, and an oil pump 13. The vehicle drive device 101 according to the second embodiment further includes a first power transmission path 41 that transmits the power of the engine 2 to the oil pump 13 and a second power transmission that transmits the power from the wheels to the oil pump 13. A path 42 and a switching mechanism for switching between the first power transmission path 41 and the second power transmission path 42 are provided. In the present embodiment, a third clutch 43 and a fourth clutch 44 are provided as a switching mechanism. The first power transmission path 41 connects the pump impeller 5 a and the oil pump 13. That is, the first power transmission path 41 is a transmission path that transmits the power of the engine 2 to the oil pump 13 without passing through the second clutch 12. The second power transmission path 42 connects the rotary shaft 7 and the oil pump 13. In addition, it is preferable that the auxiliary machine 14 is connected with the rotating shaft 13a of the oil pump 13 like the said 1st Embodiment.

  The third clutch 43 is a one-way clutch that is provided in the first power transmission path 41 and blocks transmission of power from the oil pump 13 to the engine 2. The third clutch 43 functions as a third one-way clutch. The fourth clutch 44 is a one-way clutch that is provided in the second power transmission path 42 and that blocks transmission of power from the oil pump 13 toward the drive wheels 30. In other words, the fourth clutch 44 functions as a second one-way clutch provided between the rotating shaft 7 and the oil pump 13. The oil pump 13 is driven by the pump impeller 5a and the rotating shaft 7 that have a higher rotational speed. For example, when the rotational speed of the pump impeller 5a (engine rotational speed Ne) is higher than the rotational speed of the rotary shaft 7, the third clutch 43 is engaged and the fourth clutch 44 is released. Thereby, the oil pump 13 is driven by the rotation of the pump impeller 5a. On the other hand, when the rotation speed of the rotating shaft 7 is higher than the rotation speed of the pump impeller 5a, the fourth clutch 44 is engaged and the third clutch 43 is released. Thereby, the oil pump 13 is driven by the rotation of the rotating shaft 7. The fourth clutch 44 is connected to the rotating shaft 7 via the first clutch 11 and the planetary gear mechanism 16. Therefore, when the first clutch 11 is open, the fourth clutch 44 is not engaged and the third clutch 43 is engaged even if the rotational speed of the rotary shaft 7 is higher than the rotational speed of the pump impeller 5a. Match. In this case, the oil pump 13 is driven by the rotation of the pump impeller 5a.

  As shown in FIG. 12, the third clutch 43 and the fourth clutch 44 share an outer ring 47. The third clutch 43 includes an inner ring 45 and an outer ring 47. The inner ring 45 is connected to the pump impeller 5a and rotates integrally with the pump impeller 5a. The fourth clutch 44 includes an inner ring 46 and an outer ring 47. The inner ring 46 is connected to the drum 11a of the first clutch 11 and rotates integrally with the drum 11a. The outer ring 47 is a sprocket. An endless chain 17 is stretched between the outer ring 47 and the sprocket 13 b of the oil pump 13.

  In the vehicle drive device 101 of the present embodiment, the two one-way clutch outer rings 47 are common. Therefore, the number of parts is reduced and an increase in axial length is suppressed. Therefore, the configuration for selectively driving the oil pump 13 by the first power transmission path 41 and the second power transmission path 42 is simplified, and an increase in the size of the vehicle drive device 101 is greatly suppressed.

  According to the vehicle drive device 101 according to the present embodiment, the control of the lockup clutch 6 can be omitted. For example, in the first embodiment, the lockup clutch 6 is half-engaged when the engine 2 is restarted or when the vehicle 100 is started. In the vehicle drive device 101 of the present embodiment, the pump impeller 5a and the oil pump 13 are mechanically connected even when the lockup clutch 6 is released. Therefore, even if the engine 2 is restarted with the lock-up clutch 6 opened, the oil pump 13 immediately starts rotating to generate hydraulic pressure.

  In the vehicle drive device 101 of the present embodiment, the engine 2 and the oil pump 13 are connected by the third clutch 43 without using the lock-up clutch 6. Therefore, the vehicle drive device 101 can drive the oil pump 13 more reliably even at an extremely low temperature at which the responsiveness and control accuracy of the lockup clutch 6 tend to decrease. As a result, the quality and durability of the vehicle drive device 101 are improved.

  It should be noted that at least one of the third clutch 43 and the fourth clutch 44 may be a clutch that can be arbitrarily engaged and released. For example, both the third clutch 43 and the fourth clutch 44 may be controllable clutches. In this case, the clutches 43 and 44 are controlled by the control unit 50. For example, when the engine 2 is generating power, the control unit 50 engages the third clutch 43 and opens the fourth clutch 44. Further, when the engine 2 is stopped, the control unit 50 opens the third clutch 43 and engages the fourth clutch 44.

[Third Embodiment]
A third embodiment will be described with reference to FIG. In the third embodiment, constituent elements having the same functions as those described in the first embodiment and the second embodiment are denoted by the same reference numerals, and redundant description is omitted. FIG. 13 is a cross-sectional view of main parts of a vehicle drive device according to the third embodiment. The vehicle drive device 102 of the third embodiment is different from the vehicle drive devices 1 and 101 of the above embodiments in that the lockup clutch 6 is released by applying a force in the engagement direction to the lockup clutch 6. It is a point provided with the elastic member to suppress. The elastic member (see reference numeral 48 in FIG. 13) applies a pressure to the lockup clutch 6 to weakly engage it. The elastic member transmits torque required for driving the oil pump 13 and the auxiliary machine 14 to the lockup clutch 6.

  The vehicle drive device 102 of the present embodiment has a disc spring 48 as an elastic member. The disc spring 48 is disposed between the hub 8 in the torque converter 5 and the piston 6a. The disc spring 48 is disposed between the hub 8 and the piston 6a while being compressed in the axial direction, and presses the piston 6a toward the cover 5e in the axial direction. That is, the disc spring 48 presses the lockup clutch 6 in the engaging direction. The disc spring 48 engages the piston 6a with the cover 5e in a state where the hydraulic pressure with respect to the piston 6a is neutral, that is, in a state where the hydraulic pressure on both sides in the axial direction is equal across the piston 6a. At this time, the engagement pressure of the lockup clutch 6 due to the pressure of the disc spring 48 is, for example, the predetermined value P1 of the first embodiment. That is, the disc spring 48 can transmit the torque for driving the oil pump 13 from the engine 2 to the rotating shaft 7 by weakly engaging the lockup clutch 6 by the pressing force of the disc spring 48. The torque capacity of the lockup clutch 6 by the pressurization generated by the disc spring 48 may be, for example, about 10 Nm.

  When causing the vehicle 100 to execute a free run, the control unit 50 may release the lockup clutch 6 by hydraulic pressure. When executing the free run, the control unit 50 can press the piston 6a of the lock-up clutch 6 in the releasing direction by hydraulic pressure, and can open the lock-up clutch 6 against the pressurization of the disc spring 48. As a result, the amount of heat generated by the lock-up clutch 6 can be suppressed, and the running resistance during free-running can be reduced.

  According to the vehicle drive device 102 according to the present embodiment, the control of the lockup clutch 6 can be omitted. For example, in the first embodiment, the lockup clutch 6 is half-engaged when the engine 2 is restarted or when the vehicle 100 is started. In the vehicle drive device 102 of the present embodiment, the disc spring 48 engages the lockup clutch 6 even when the lockup clutch 6 is not driven by hydraulic pressure. Therefore, even if the engine 2 is restarted with the command value for the engagement pressure of the lockup clutch 6 kept at 0, the oil pump 13 starts to rotate and generates hydraulic pressure.

  Therefore, for example, even when the responsiveness and control accuracy of the lock-up clutch 6 are likely to be lowered, power is transmitted from the engine 2 to the oil pump 13 via a mechanical power transmission path bypassing the fluid. can do. As a result, the quality and durability of the vehicle drive device 102 are improved.

[Modification of each embodiment]
A modification of the first to third embodiments will be described. In each of the above embodiments, the second clutch 12 disconnects both the turbine runner 5b and the lockup clutch 6 from the rotary shaft 7 when released, but instead, the turbine runner 5b when released. It may be made to detach only. That is, the power transmitted through the lockup clutch 6 may be transmitted between the engine 2 and the rotary shaft 7 by bypassing the second clutch 12.

  The second clutch 12 may be disposed between the torque converter 5 and the engine 2. That is, the second clutch 12 only needs to have a function of interrupting transmission of power from the first clutch 11 to the engine 2, and its arrangement and the like are arbitrary. The second clutch 12 is a two-way clutch that can be switched to a state in which the transmission of power from the first clutch 11 to the engine 2 is cut off, and the transmission of power from the first clutch 11 to the engine 2 is arbitrarily cut off. It may be a control clutch or the like.

  The first clutch 11 only needs to be able to switch between a state in which power is transmitted in both directions and a state in which power transmission in both directions is interrupted, and may be, for example, a two-way clutch.

  A mechanism for transmitting power to the oil pump 13 and the auxiliary machine 14 may be a belt or a gear instead of the chain 17. For example, in the vehicle drive device 1 of the first embodiment, the rotary shaft 7 and the oil pump 13 may be connected by a gear instead of the sprockets 11b and 13b and the chain 17. The oil pump 13 may be arranged coaxially with the rotary shaft 7.

  The auxiliary machine 14 may be disposed closer to the drive wheel 30 than the first clutch 11. Even with such an arrangement, it is possible to generate a pseudo engine brake by adjusting the load torque of the auxiliary machine 14.

  In each of the above embodiments, when the engine 2 is restarted, the lock-up clutch 6 is half-engaged. Alternatively, the engine 2 may be restarted with the lock-up clutch 6 open. Further, the lock-up clutch 6 may be released when the vehicle 100 is started or during a free run.

  The contents disclosed in each of the above embodiments and modifications can be executed in appropriate combination.

1, 101, 102 Vehicle drive device 2 Engine 5 Torque converter 5a Pump impeller 5b Turbine runner 6 Lock-up clutch 7 Rotating shaft 11 First clutch (clutch)
12 Second clutch (one-way clutch)
DESCRIPTION OF SYMBOLS 13 Oil pump 14 Auxiliary machine 17 Chain 20 Transmission mechanism 26 Input shaft 27 Output shaft 30 Drive wheel 40 Hydraulic control part 41 1st power transmission path 42 2nd power transmission path 43 3rd clutch 44 4th clutch 48 Disc spring 50 Control unit 60 Automatic transmission 100 Vehicle Ne Engine speed Nin Input speed Nt Turbine speed Np Pump speed

Claims (7)

A clutch for arbitrarily transmitting or interrupting power between the engine and the transmission mechanism;
A one-way clutch that blocks transmission of power from the clutch toward the engine;
An oil pump connected to a rotating shaft connecting the clutch and the one-way clutch, and driven by rotation of the rotating shaft;
And a torque converter disposed between the engine and the clutch, wherein the one-way clutch is disposed between the torque converter and the clutch. And a second one-way clutch provided between the rotating shaft and the oil pump;
A transmission path for transmitting the power of the engine to the oil pump without going through the one-way clutch;
The vehicle drive device according to claim 1, further comprising: a third one-way clutch provided in the transmission path and blocking transmission of power from the oil pump toward the engine. The torque converter has a lock-up clutch,
The vehicle drive device according to claim 1, wherein the one-way clutch is disposed between the turbine runner and the lockup clutch of the torque converter and the rotation shaft. And a control unit that automatically stops and restarts the engine,
The vehicle drive device according to any one of claims 1 to 3, wherein the control unit automatically stops the engine while the clutch is engaged. And a control unit that automatically stops and restarts the engine,
The torque converter has a lock-up clutch,
The vehicle drive device according to any one of claims 1 to 3, wherein the control unit restarts the engine in a state in which the lock-up clutch is slipped. And a control unit that automatically stops and restarts the engine,
The torque converter has a lock-up clutch,
The said control part slips the said lockup clutch as long as a vehicle speed is below a predetermined vehicle speed, when restarting the said engine from the state which the said engine stopped and starting a vehicle. The vehicle drive device according to item. The torque converter has a lock-up clutch,
The vehicle drive device according to claim 1, further comprising an elastic member that suppresses release of the lockup clutch by applying a force in an engagement direction to the lockup clutch.

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