JP2016168976A - Vehicle driving device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vehicle driving device which enables reduction of friction loss of a bearing rotatably supporting a pump driving member.SOLUTION: A vehicle driving device includes: a pinion gear P supported by a connection member 10 and having a first engagement part 11 and a second engagement part 12; a pump driving member GO; a first transmission gear S1 which is drivingly coupled to the pump driving member GO and engages with the first engagement part 11; and a second transmission gear S2 which is drivingly coupled to an input member I and engages with the second engagement part 12. The pump driving member GO is supported through a first bearing B1 so as to rotate relative to the connection member 10, and the connection member 10 is supported through a second bearing B2 so as to rotate relative to a case CS.SELECTED DRAWING: Figure 2

Description

  The present invention includes an input member that is drivingly connected to an internal combustion engine, a speed change mechanism that is drivingly connected to a wheel side, a rotor of a rotating electrical machine, a rotor support member that is drivingly connected to the input member and supports the rotor, The present invention relates to a vehicle drive device including a connecting member that connects the rotor support member and the speed change mechanism, and a case that houses the rotating electrical machine and the speed change mechanism.

  With respect to the vehicle drive device as described above, for example, a technique described in Patent Document 1 below is already known. In the technique of Patent Document 1, a pump driving member that transmits driving force to a pump is drivingly connected to a sun gear that meshes with a pinion gear.

German Patent Application Publication No. 102010033364

  Although it is necessary to rotatably support the pump drive member with a bearing, it is desirable to reduce friction loss due to a difference in rotational speed between the bearings as much as possible. However, the technique of Patent Document 1 does not disclose a configuration of a bearing that rotatably supports the pump drive member.

  Therefore, a vehicle drive device that can reduce the friction loss of the bearing that rotatably supports the pump drive member is desired.

  In view of the above, the input member that is drivingly connected to the internal combustion engine, the transmission mechanism that is drivingly connected to the wheels, the rotor of the rotating electrical machine, the connecting member that drives and connects the rotor and the transmission mechanism, and the input A feature configuration of a vehicle drive device including an engagement device that engages or releases a member and the connection member, and a case is supported by the connection member, and includes a first engagement portion and a second engagement portion. Having a pinion gear, a pump driving member drivingly connected to the pump, a first transmission gear drivingly connected to the pump driving member and meshing with the first meshing portion, and drivingly connected to the input member, and the second A second transmission gear meshing with the meshing portion, wherein the pump drive member is rotatably supported with respect to the coupling member via a first bearing, and the coupling member is coupled with the second bearing via the second bearing. Can rotate with respect to the case It lies in being supported.

  In the present application, “driving connection” refers to a state where two rotating elements are connected so as to be able to transmit a driving force, and the two rotating elements are connected so as to rotate integrally, or It is used as a concept including a state in which two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members. Examples of such a transmission member include various members that transmit rotation at the same speed or a variable speed, and include, for example, a shaft, a gear mechanism, a belt, a chain, and the like. Further, as such a transmission member, an engagement device that selectively transmits rotation and driving force, for example, a friction engagement device or a meshing engagement device may be included.

According to said characteristic structure, rotation of the driving force source of an internal combustion engine and a rotary electric machine is transmitted to a pump drive member via a pinion gear and a 1st transmission gear, and it is comprised so that a pump may be rotated. At this time, since the pump drive member also rotates, the rotational speed difference between the pump drive member and the connecting member may be smaller than the rotational speed difference between the pump drive member and the case. In particular, when the engaging device is engaged and the input member and the connecting member rotate at the same rotational speed, the pinion gear does not rotate and revolves at the same speed as the connecting member. As a result, the pump drive member and the connecting member Rotates at the same speed.
Unlike the above characteristic configuration, when the pump driving member is configured to be rotatably supported with respect to the case via the first bearing, the pump driving member is rotated when the pump driving member is rotating. A rotational speed difference is generated between the case and the case, and torque loss due to a frictional force corresponding to the rotational speed difference occurs in the first bearing.
On the other hand, in the above characteristic configuration, the pump drive member is configured to be rotatably supported with respect to the connecting member via the first bearing, so that the rotational speed difference of the first bearing can be reduced. It is possible to reduce the friction force generated in the first bearing and to reduce the torque loss. In particular, when the pump drive member and the connecting member are rotating at the same speed, the rotational speed difference of the first bearing can be made zero, and torque loss can be prevented from occurring.

1 is a skeleton diagram showing a schematic configuration of a vehicle drive device according to an embodiment of the present invention. It is sectional drawing which cut | disconnected the vehicle drive device which concerns on embodiment of this invention by the plane which passes along the rotating shaft center and pinion gear of a rotary electric machine. It is principal part sectional drawing for demonstrating the assembly | attachment of the vehicle drive device which concerns on embodiment of this invention. It is principal part sectional drawing for demonstrating the state after the assembly | attachment of the vehicle drive device which concerns on embodiment of this invention. It is sectional drawing which cut | disconnected the drive device for vehicles which concerns on the comparative example of this invention by the plane which passes along the rotating shaft center and pinion gear of a rotary electric machine. It is sectional drawing which cut | disconnected the drive device for vehicles which concerns on other embodiment of this invention by the plane which passes along the rotating shaft center and pinion gear of a rotary electric machine.

1. Embodiment The vehicle drive device 1 which concerns on embodiment is demonstrated with reference to drawings.
The vehicle drive device 1 drives an input member I that is drivingly connected to the internal combustion engine EN, a transmission mechanism TM that is drivingly connected to the wheel W side, a rotor Ro of the rotating electrical machine MG, a rotor Ro, and the transmission mechanism TM. A coupling member 10 to be coupled, an engagement device CL to engage or release the input member I and the coupling member 10, and a case CS are provided.

  FIG. 1 is a skeleton diagram showing a schematic configuration of the vehicle drive device 1, and FIG. 2 is a cross-sectional view of the vehicle drive device 1 cut along a plane passing through the rotation axis SC and the pinion gear P of the rotating electrical machine MG. 3 is a cross-sectional view of a main part for explaining the assembly of the vehicle drive device 1, and FIG. 4 is a cross-sectional view of the main part after the vehicle drive device 1 is assembled.

  A direction parallel to the rotational axis SC of the rotating electrical machine MG is defined as an axial direction X. Along the axial direction X, the internal combustion engine EN, the rotating electrical machine MG, and the speed change mechanism TM are arranged in this order. A side from the internal combustion engine EN to the speed change mechanism TM in the axial direction X is defined as an axial first side X1, and a side from the speed change mechanism TM to the internal combustion engine EN in the axial direction X is defined as an axial second side X2. The term “radial direction” or “circumferential direction” simply refers to the radial direction or the circumferential direction of the rotating electrical machine MG (specifically, the rotational axis SC of the rotating electrical machine MG).

1-1. Overview of Vehicle Drive Device 1 As shown in FIG. 1, the vehicle drive device 1 is a drive device for a hybrid vehicle that includes an internal combustion engine EN and a rotating electrical machine MG as drive power sources for driving the wheels W. ing. The vehicle drive device 1 includes a speed change mechanism TM, and the speed change mechanism TM shifts the rotational speed of the driving force source transmitted to the speed change input member TI that is an input member of the speed change mechanism TM and converts torque. Then, it is transmitted to the output member O and transmitted to the wheel W that is drivingly connected to the output member O. The internal combustion engine EN, the rotating electrical machine MG, the speed change input member TI of the speed change mechanism TM, the connecting member 10, the first transmission gear S1, the second transmission gear S2, and the pump drive member GO are arranged on the same axis of the rotation axis SC. ing. The pump OP is disposed on an axis different from the rotation axis SC.

  The internal combustion engine EN is a heat engine that is driven by the combustion of fuel. For example, various known engines such as a gasoline engine and a diesel engine are used. The output shaft of the internal combustion engine EN is connected to the input member I via a damper or the like. The rotating electrical machine MG includes a stator St fixed to the case CS and a rotor Ro that is rotatably supported on the radially inner side of the stator St. The case CS accommodates the rotating electrical machine MG, the speed change mechanism TM, and the like.

  The rotor Ro of the rotating electrical machine MG is supported by the rotor support member 40. The rotor support member 40 is drivingly connected to the input member I. In the present embodiment, the rotor support member 40 is configured to be connected to the input member I via the engagement device CL. The engagement device CL is a friction engagement device. When the engagement device CL is engaged, the input member I is connected to the rotor support member 40, and the driving force of the internal combustion engine EN can be transmitted to the wheel W side. On the other hand, when the engagement device CL is released, the input member I is disconnected from the rotor support member 40, and the driving force of the internal combustion engine EN is not transmitted to the wheel W side.

  The vehicle drive device 1 includes a connecting member 10 that connects the rotor support member 40 and the speed change mechanism TM. In the present embodiment, the connecting member 10 connects the rotor Ro (rotor support member 40) and the speed change input member TI of the speed change mechanism TM. In the present embodiment, the speed change mechanism TM is a stepped automatic speed change mechanism having a plurality of speed stages having different speed ratios (gear ratios). The speed change mechanism TM includes a gear mechanism such as a planetary gear mechanism and a plurality of engagement devices in order to form the plurality of speed stages. The speed change mechanism TM shifts the rotational speed of the speed change input member TI at the speed ratio of each speed stage, converts the torque, and transmits the torque to the output member O.

The vehicle drive device 1 is supported by a connecting member 10 and includes a pinion gear P having a first meshing portion 11 and a second meshing portion 12, a pump driving member GO drivingly connected to a pump OP, and a pump driving member GO. The first transmission gear S1 that is driven and connected to the first meshing portion 11 and the second transmission gear S2 that is drivingly connected to the input member I and meshed with the second meshing portion 12 are provided.
The pinion gears P are provided at a plurality of locations in the circumferential direction (for example, three locations arranged at equal intervals in the circumferential direction). The first meshing portion 11 and the second meshing portion 12 are tooth portions constituting the gear tooth surface of each pinion gear P. Thus, the vehicle drive device 1 includes a plurality of pinion gears P as planetary gears, a connecting member 10 that functions as a carrier that supports the plurality of pinion gears P, the first transmission gear S1 that meshes with the plurality of pinion gears P, and the first transmission gear S1. A planetary gear mechanism including two transmission gears S2 is provided. In the present embodiment, the first transmission gear S1 and the second transmission gear S2 are so-called sun gears.

  The first transmission gear S1 is drivingly connected to the pump driving member GO. In the present embodiment, the first transmission gear S1 is connected to rotate integrally with the pump drive member GO. The vehicle drive device 1 includes a pump OP, and the pump drive member GO is drivingly connected to the pump OP. In this embodiment, the pump drive member GO is a sprocket gear, and the pump OP (in this example, the drive gear GI of the pump OP) and the pump drive member GO (sprocket gear) are driven via a chain CH. It is connected. That is, the chain CH is stretched between the sprocket gear and the drive gear GI of the pump OP. Therefore, the rotational driving force of the first transmission gear S1 is transmitted to the pump OP via the power transmission mechanism such as the sprocket gear, the chain CH, and the driving gear GI, and rotationally drives the pump OP.

  In the present embodiment, the pump OP is an oil pump. The engagement device CL and the engagement device of the speed change mechanism TM are hydraulically controlled, and the rotating electrical machine MG is oil-cooled. The oil discharged from the oil pump is supplied to each part of the vehicle drive device 1 such as the engagement device CL, the speed change mechanism TM, and the rotating electrical machine MG.

  The second transmission gear S2 and the connecting member 10 are drivingly connected via the first one-way clutch F1. The first one-way clutch F1 restricts the rotational speed of the connecting member 10 from becoming higher than the rotational speed of the second transmission gear S2. That is, the first one-way clutch F1 is engaged when the rotational speed of the connecting member 10 is to be higher than the rotational speed of the second transmission gear S2, and the rotational speed of the connecting member 10 is that of the second transmission gear S2. If it is lower than the rotation speed, release it. The input member I and the second transmission gear S2 are drivingly connected via a second one-way clutch F2. The second one-way clutch F2 restricts the rotational speed of the input member I from becoming higher than the rotational speed of the second transmission gear S2. That is, the second one-way clutch F2 is engaged when the rotational speed of the input member I is higher than the rotational speed of the second transmission gear S2, and the rotational speed of the connecting member 10 is that of the second transmission gear S2. If it is lower than the rotation speed, release it. By the action of the first and second one-way clutches F1 and F2, the second transmission gear S2 rotates at the same speed as the higher one of the connecting member 10 and the input member I. Therefore, when the engagement device CL is released, the second transmission gear S2 rotates at the same speed as the higher one of the rotating electric machine MG and the internal combustion engine EN.

  When the engagement device CL is engaged, the rotating electrical machine MG (the connecting member 10) and the internal combustion engine EN rotate at the same speed, so the connecting member 10 supporting the pinion gear P and the second transmission gear S2 Rotates at the same speed. Therefore, the pinion gear P does not rotate but revolves at the same speed as the connecting member 10. As a result, the first transmission gear S1 rotates at the same speed as the connecting member 10.

  When the engagement device CL is released and the rotational speed of the rotating electrical machine MG is higher than the rotational speed of the internal combustion engine EN, the second transmission gear S2 is connected to the rotating electrical machine MG (the connecting member 10). And rotate at the same speed. Therefore, the pinion gear P does not rotate but revolves at the same speed as the connecting member 10. As a result, the first transmission gear S1 rotates at the same speed as the connecting member 10.

  On the other hand, when the engagement device CL is released and the rotational speed of the internal combustion engine EN is higher than the rotational speed of the rotating electrical machine MG (the connecting member 10), the second transmission gear S2 is connected to the internal combustion engine EN. It rotates at the same speed as. Therefore, the pinion gear P revolves at the same speed as the connection member 10 while rotating at a rotation speed corresponding to the rotation speed difference between the rotation speed of the internal combustion engine EN and the rotation speed of the connection member 10. As a result, the first transmission gear S1 rotates at the same speed as the internal combustion engine EN.

  Thus, the first transmission gear S1 is rotated at the same speed as the higher one of the rotating electrical machine MG and the internal combustion engine EN, and the pump OP is connected via the pump drive member GO that is drivingly connected to the first transmission gear S1. Is driven to rotate. Therefore, the engagement device CL is engaged, the parallel traveling mode in which the vehicle is driven by the driving force of the rotating electrical machine MG and the internal combustion engine EN, or the engaging device CL is released, the internal combustion engine EN is stopped and the rotating electrical machine MG is stopped. In the case of the electric travel mode in which the vehicle travels with the driving force, the connecting member 10 and the first transmission gear S1 (pump drive member GO) rotate at the same speed. On the other hand, if the engagement device CL is released and the internal combustion engine EN is rotating at the idling rotational speed while the vehicle is stopped and the rotational speed of the rotating electrical machine MG is stopped, the connecting member 10 stops rotating. Then, the first transmission gear S1 (pump drive member GO) rotates at the same speed as the internal combustion engine EN.

1-2. Arrangement Configuration of Vehicle Drive Device 1 As described above, the rotation of the driving force source is transmitted to the pump drive member GO via the pinion gear P and the first transmission gear S1, and the pump OP is configured to rotate. . At this time, since the pump driving member GO also rotates, the rotational speed difference between the pump driving member GO and the connecting member 10 may be smaller than the rotational speed difference between the pump driving member GO and the case CS. In particular, when the engaging device CL is engaged and the input member I and the connecting member 10 rotate at the same rotational speed, the pinion gear P revolves at the same speed as the connecting member 10 without rotating, resulting in a pump drive member. The GO and the connecting member 10 rotate at the same speed.

FIG. 5 shows a comparative example different from the present embodiment. In the comparative example shown in FIG. 5, the connecting member 10 is rotatably supported with respect to the support part 20 of the case CS via the second bearing B2, and the pump drive member GO is interposed via the first bearing B1. The case CS is rotatably supported with respect to the support portion 20.
Therefore, when the pump drive member GO is rotating, a rotational speed difference is generated between the pump drive member GO and the case CS, and a frictional force corresponding to the rotational speed difference is generated in the first bearing B1 to generate torque. Loss occurs. When the pump OP is an oil pump that supplies hydraulic pressure to the transmission mechanism TM, the engagement device CL, and the rotating electrical machine MG as in the present embodiment, the pump OP is rotated at a high frequency. The frequency of occurrence of torque loss in the bearing B1 increases.

  Therefore, in the present embodiment, as shown in FIG. 2, the coupling member 10 is such that the pump drive member GO is supported rotatably with respect to the coupling member 10 via the first bearing B1, and via the second bearing B2. And is configured to be rotatably supported with respect to the case CS. According to this configuration, even when the pump driving member GO is rotating, when the connecting member 10 is rotating, the rotational speed difference of the first bearing B1 is reduced as compared with the comparative example of FIG. Thus, the frictional force generated in the first bearing B1 can be reduced, and the torque loss can be reduced. In particular, when the pump drive member GO and the connecting member 10 are rotating at the same speed, the rotational speed difference of the first bearing B1 can be made zero, and torque loss can be prevented from occurring. In the present embodiment, as described above, the engagement device CL is engaged, the parallel traveling mode in which the vehicle is driven by the driving force of the rotating electrical machine MG and the internal combustion engine EN, or the engagement device CL is released, and the internal combustion engine EN is released. Is stopped, and the pump drive member GO and the connecting member 10 are rotated at the same speed in the electric travel mode in which the vehicle is driven by the driving force of the rotating electrical machine MG. Therefore, since the pump drive member GO and the connecting member 10 rotate at the same speed while the vehicle is traveling, the frequency of rotation at the same speed increases, and the effect of reducing torque loss increases.

  In the present embodiment, as shown in FIG. 2, the connecting member 10 includes a first connecting portion 14 connected to the rotor support member 40 and a second connecting portion 15 connected to the speed change mechanism TM (speed change input member TI). And a radially extending portion 16 that extends in the radial direction by connecting the first connecting portion 14 and the second connecting portion 15, and a bearing support portion 17 that supports a first bearing B1 described later.

The pinion gear P is supported so as to be rotatable with respect to the radially extending portion 16. The first meshing portion 11, the first transmission gear S 1, and the pump drive member GO are first in the axial direction with respect to the radially inner portion 13, which is a portion radially inward of the pinion gear P in the radially extending portion 16. It is arranged at X1. The second meshing portion 12 and the second transmission gear S2 are disposed on the second axial side X2 with respect to the radially inner portion 13.
The bearing support portion 17 is formed in a cylindrical shape (in this example, a cylindrical shape) that protrudes from the radially inner portion 13 to the axial first side X1.

  According to this configuration, the first transmission gear S1 and the pump drive member GO are disposed on the first axial side X1 with respect to the radially inner portion 13 of the radially extending portion 16, and the pump OP is positioned closer to the speed change mechanism TM. Can be arranged. Therefore, it becomes easy to supply the hydraulic pressure generated by the pump OP to the speed change mechanism TM. Further, the pump support member GO disposed on the first axial side X1 with respect to the radial inner side 13 by the bearing support part 17 projecting from the radial inner side 13 to the first axial side X1 is replaced with the first bearing B1. Can be supported. The first bearing B1 is disposed between the pump drive member GO and the connecting member 10.

  In the present embodiment, the radially extending portion 16 is an annular plate-like member that extends radially outward and radially inward from the radial position of the pinion gear P and extends in the circumferential direction. Yes. In the radially extending portion 16, pinion through holes 22 that are cylindrical through holes penetrating in the axial direction X are formed at a plurality of locations in the circumferential direction (for example, three locations arranged at equal intervals in the circumferential direction). Has been. The pinion gear P is a shaft member that connects the first gear P1 constituting the first meshing portion 11, the second gear P2 constituting the second meshing portion 12, and the first gear P1 and the second gear P2. And a certain pinion shaft 21. The pinion shaft 21 is inserted into the pinion through hole 22, and the end portion on the first axial side X <b> 1 of the pinion shaft 21 protrudes to the first axial side X <b> 1 from the pinion through hole 22. The end of the second side X2 protrudes from the pinion through hole 22 to the second axial side X2. A bearing is provided between the pinion through hole 22 and the pinion shaft 21. The first gear P1 is connected to the end of the pinion shaft 21 on the first axial side X1, and the second gear P2 is connected to the end of the pinion shaft 21 on the second axial side X2. The first gear P1 is disposed on the first axial side X1 with respect to the pinion through hole 22, and the second gear P2 is disposed on the second axial side X2 with respect to the pinion through hole 22.

  The first transmission gear S1 is disposed on the first axial side X1 of the connecting member 10, and the second transmission gear S2 is disposed on the second axial side X2 of the connecting member 10. The first transmission gear S1 is disposed on the radially inner side of the first gear P1 (first meshing portion 11), and the second transmission is disposed on the radially inner side of the second gear P2 (second meshing portion 12). A gear S2 is arranged. The radially inner portion 13 is configured by a portion radially inward of the pinion through hole 22 in the radially extending portion 16, and is between the first transmission gear S <b> 1 and the second transmission gear S <b> 2 in the axial direction X. Has been placed.

  A pump drive member GO is disposed on the first axial side X1 of the first transmission gear S1. The first transmission gear S1 and the pump drive member GO are integrally formed as a cylindrical gear forming member 23, and the teeth of the first transmission gear S1 are arranged on the second axial side X2 of the outer peripheral surface of the gear forming member 23. A surface is formed, and a tooth surface of a sprocket gear as the pump drive member GO is formed on the first axial side X1 of the outer peripheral surface of the gear forming member 23. Thus, the pump drive member GO is a sprocket gear disposed on the first axial side X1 with respect to the first transmission gear S1. The portion on the second axial side X2 on the inner circumferential surface of the gear forming member 23 has a larger diameter than the portion on the first axial side X1, and the outer circumferential surface of the first bearing B1 is fitted in the larger diameter portion. Are combined. The first bearing B1 is formed in a cylindrical shape. A washer member 18 to be described later is disposed on the radially inner side of the small diameter portion on the first axial side X1 on the inner peripheral surface of the gear forming member 23.

  The bearing support portion 17 is formed in a cylindrical shape, and extends radially inward from the gear forming member 23 from the radially inner portion 13 to the first axial side X1, and is seen from the gear forming member 23 in the radial direction. Are overlapping. The inner peripheral surface of the first bearing B1 is fitted to the outer peripheral surface of the bearing support portion 17, and the bearing support portion 17 supports the first bearing B1 from the radially inner side. The bearing support portion 17 does not extend to the axial first side X1 up to the small diameter portion on the axial first side X1 on the inner peripheral surface of the gear forming member 23, and overlaps with the small diameter portion when viewed in the radial direction. Has no part. The outer peripheral surface of the first support bearing B <b> 2 a is fitted to the inner peripheral surface of the bearing support portion 17. A washer member 18 is disposed on the first axial side X <b> 1 of the bearing support portion 17, and the bearing support portion 17 and the washer member 18 overlap when viewed in the axial direction X.

  The case CS is a first wall X1 in the axial direction from the connecting member 10 and a peripheral wall (not shown) that covers the outer periphery of the vehicle drive device 1 at an axial position on the second axial side X2 from the speed change mechanism TM. The first radial extending wall 41 having an annular plate shape extending inward in the radial direction is provided. The case CS includes a cylindrical (cylindrical in this example) support portion 20 that extends from the radially inner end of the first radially extending wall 41 to the second axial side X2. The inner peripheral surface of the first support bearing B <b> 2 a is fitted to the outer peripheral surface of the support portion 20. The support portion 20 and the bearing support portion 17 overlap when viewed in the radial direction. The inner peripheral surface of the washer member 18 is fitted to a portion of the outer peripheral surface of the support portion 20 on the first axial side X1 with respect to the fitting portion with the first support bearing B2a. The surface on the first axial side X1 of the washer member 18 is in contact with the surface on the second axial side X2 of the first radially extending wall 41.

  In a space between the first radial extending wall 41 and the radial extending portion 16 of the connecting member 10 in the axial direction X, the first transmission gear S1, the pump drive member GO, the first bearing B1, and the bearing support portion 17 are provided. , And a chain CH are arranged. The pump OP and the drive gear GI are disposed on an axis different from the rotational axis SC of the rotating electrical machine MG, and the chain CH is between the first radially extending wall 41 and the radially extending portion 16. The space extends radially outward from the pump drive member GO and spans the drive gear GI (see FIG. 1).

  A transmission mechanism TM is disposed on the first axial side X1 of the first radially extending wall 41. The speed change input member TI of the columnar speed change mechanism TM is disposed on the radially inner side of the first radially extending wall 41 and the support portion 20, and extends from the axial first side X1 to the axial second side X2. ing. An oil passage extending in the axial direction X for supplying hydraulic pressure to the engagement device CL, the rotating electrical machine MG, each bearing, and the like is formed inside the speed change input member TI. The inner peripheral surface of the support portion 20 rotatably supports the outer peripheral surface of the transmission input member TI via the second support bearing B2b. The connecting member 10 is rotatably supported with respect to the case CS via the second support bearing B2b and the speed change input member TI. In the present embodiment, “first support bearing B2a” and “second support bearing B2b” correspond to “second bearing B2” in the present invention.

  The coupling member 10 includes a cylindrical (cylindrical in this example) inner boss portion 46 that extends from the radially inner end of the radially extending portion 16 to the second axial side X2. The inner peripheral surface of the inner boss portion 46 and the outer peripheral surface of the speed change input member TI are spline fitted and connected so as to rotate integrally. The inner boss portion 46 serves as the second connecting portion 15 of the connecting member 10 connected to the speed change mechanism TM (speed change input member TI). Here, the inner boss portion 46 is an inner rotor of the first one-way clutch F1. An inner peripheral surface of a locking member (such as a sprag) of the first one-way clutch F1 is in contact with the outer peripheral surface of the inner boss portion 46.

  The second transmission gear S2 has an annular plate-like portion extending radially inward from the portion where the tooth surface is formed, and the annular plate-like portion is a portion of the annular plate-like portion. From the radially inner end, the radially outer side of the inner boss portion 46 is connected to a cylindrical (in this example, cylindrical) gear boss portion 45 extending to the second axial side X2. Here, the gear boss 45 serves as both the outer rotor of the first one-way clutch F1 and the inner rotor of the second one-way clutch F2. That is, the outer peripheral surface of the locking member (such as a sprag) of the first one-way clutch F1 is in contact with the inner peripheral surface of the gear boss portion 45. An inner peripheral surface of a locking member (such as a sprag) of the second one-way clutch F2 is in contact with the outer peripheral surface of the gear boss 45.

  The input member I includes a cylindrical (in this example, cylindrical) input boss portion 44 that extends from the input cylindrical portion 24 to be described later to the radially outer side of the gear boss portion 45 toward the first axial side X1. Here, the input boss portion 44 is an outer rotor of the second one-way clutch F2. That is, the outer peripheral surface of the locking member (such as a sprag) of the second one-way clutch F2 is in contact with the inner peripheral surface of the input boss portion 44.

  The case CS is a circle extending radially inward from a peripheral wall (not shown) at a position in the axial direction X on the second axial side X2 from the rotating electrical machine MG and on the first axial direction X1 from the internal combustion engine EN. An annular plate-like second radially extending wall 42 is provided. The case CS includes a cylindrical (cylindrical in this example) second support portion 43 that extends from the radially inner end of the second radially extending wall 42 to the axial first side X1. The rotor support member 40 has a cylindrical rotor support body portion 25 that supports the rotor Ro from the radially inner side, and an annular plate shape that extends radially inward from the central portion in the axial direction X of the rotor support body portion 25. A radial support 48. A cylindrical (in this example, cylindrical) support boss portion 52 that extends to the second axial side X2 is formed at the radially inner end of the radial support portion 48. The outer peripheral surface of the second support portion 43 of the case CS rotatably supports the inner peripheral surface of the support boss portion 52 of the rotor support member 40 via two fourth bearings B4. The rotor of the resolver 49 is fixed to the outer peripheral surface of the support boss portion 52. The stator of the resolver 49 is fixed to a boss portion that extends from the second radially extending wall 42 to the first axial side X1.

  The input member I includes a cylindrical input cylindrical portion 24 that extends from the connecting portion to which the output shaft of the internal combustion engine EN is connected to the first axial side X1. The input tubular portion 24 penetrates the second support portion 43 of the second radially extending wall 42 in the axial direction X on the radially inner side. The inner peripheral surface of the second support portion 43 rotatably supports the outer peripheral surface of the input cylindrical portion 24 via the third bearing B3. The transmission input member TI extends on the second axial side X2 to a position where the radially inner side of the input cylindrical portion 24 overlaps the third bearing B3 in the radial direction. The outer peripheral surface of the speed change input member TI is supported so as to be rotatable with respect to the inner peripheral surface of the input cylindrical portion 24. Therefore, the speed change input member TI is rotatable with respect to the second support portion 43 of the second radially extending wall 42 via the third bearing B3 and the input cylindrical portion 24 on the second axial side X2. It is supported so as to be rotatable with respect to the support portion 20 of the first radially extending wall 41 via the second support bearing B2b on the first axial side X1. As described above, the shift input member TI is supported so as to be rotatable with respect to the case CS at the two positions of the first axial side X1 and the second axial side X2, and the shaft center of the shift input member TI is shaken. It is hard to occur.

  The engagement device CL is inserted between the input side friction plates 48a and the input side friction plates 48a arranged in the axial direction X and connected to the input member I side. A plurality of output side friction plates 48b arranged in the axial direction X and connected to the 10 side. The friction plate 48a on the input side and the friction plate 48b on the output side are pressed against each other by the hydraulic actuator 50 and engaged by frictional force. The hydraulic actuator 50 includes a cylinder, a piston, an elastic member that urges the piston, and the like.

  The engaging device CL includes a cylindrical (cylindrical in this example) clutch hub 53 that supports a plurality of input-side friction plates 48a from the radially inner side, and a plurality of output-side friction plates 48b from the radially outer side. A cylindrical drum (in this example, a cylindrical shape) to be supported is provided. In this embodiment, the clutch drum 51 is a part of the connecting member 10 and has a cylindrical shape (this example) extending from the radially outer end of the radially extending portion 16 to the second axial side X2. Is a cylindrical part). The portion of the outer peripheral surface of the clutch drum 51 on the second axial side X2 and the portion of the inner peripheral surface of the rotor support main body 25 on the first axial side X1 with respect to the radial support portion 48 are integrated by spline fitting. It is connected so as to rotate. Therefore, the portion on the second axial side X <b> 2 of the clutch drum 51 is the first connecting portion 14 of the connecting member 10 connected to the rotor support member 40. The input member I extends radially outward from the input boss portion 44 and is connected to the clutch hub 53 of the engagement device CL.

  The engagement device CL is arranged in the space on the radially inner side of the clutch drum 51 and on the second axial side X2 of the radially extending portion 16. A first one-way clutch F1 and a second one-way clutch F2 are arranged in a space inside the engagement device CL in the radial direction.

  FIG. 3 shows how the vehicle drive device 1 is assembled. In the present embodiment, the vehicle drive device 1 is configured to be assembled in order from the components on the first axial side X1. As shown in FIG. 3, before assembling the connecting member 10 to which the pinion gear P is attached, the pump drive member GO, the first bearing B1, the chain CH, and the pump that are arranged on the first axial side X1 relative to the connecting member 10 The OP is already assembled in the case CS. The first bearing B1 is fitted to the inner peripheral surface of the pump drive member GO (gear forming member 23), and the second axial side X2 of the first bearing B1 is fixed to the pump drive member GO by a snap ring. . The chain CH is stretched between a sprocket gear as the pump drive member GO and a drive gear GI (see FIG. 1) of the pump OP. However, in this embodiment, since the pump drive member GO is rotatably supported with respect to the connection member 10 via the first bearing B1, the pump drive member GO is not assembled when the connection member 10 is not assembled. It is not supported by the connecting member 10 and it is not easy to position the pump drive member GO.

  For this reason, in the present embodiment, the annular ring is located at the radially inner side of the sprocket gear as the pump drive member GO and the first axial direction X1 of the first bearing B1 and overlapping with the sprocket gear when viewed in the radial direction. A plate-shaped washer member 18 is disposed. The washer member 18 can support the pump drive member GO from the inside in the radial direction, and the connecting member 10 can be assembled with the position of the pump drive member GO temporarily determined. Therefore, it becomes easy to fit the outer peripheral surface of the bearing support portion 17 to the inner peripheral surface of the first bearing B1.

  The inner peripheral surface of the washer member 18 is supported from the radially inner side by a support portion 20 provided in the case CS. Since the washer member 18 is supported by the case CS, it is possible to suppress the rotation of the washer member 18 due to the rotation of the rotating member while the connecting member 10 is assembled, and it is possible to suppress the generation of friction loss and noise.

  As shown in FIG. 4, in a state where the connecting member 10 is assembled, in order to prevent frictional resistance between the sprocket gear and the washer member 18, A gap ΔG is formed between the inner peripheral surface of the peripheral surface on the first axial side X1 in the small diameter portion) and the outer peripheral surface of the washer member 18. Therefore, the diameter of the outer peripheral surface of the washer member 18 is smaller than the diameter of the inner peripheral surface of the sprocket gear (small diameter portion of the gear forming member 23).

  However, as shown in FIG. 3, before the connecting member 10 is assembled, the sprocket gear moves below the assembly position by the gap ΔG due to the weight of the sprocket gear or the like, and the upper gap ΔG is It is gone. In this state, the inner peripheral surface of the first bearing B1 is positioned below the outer peripheral surface of the bearing support portion 17 in the upper portion, and the outer periphery of the bearing support portion 17 is positioned on the inner peripheral surface of the first bearing B1. Difficult to fit surfaces.

  Therefore, in the present embodiment, an inclined surface 19 is formed at the end portion of the outer peripheral surface of the bearing support portion 17 on the first axial side X1 so as to go radially inward toward the first axial direction X1. The radius difference ΔR between the large diameter portion and the small diameter portion of the inclined surface 19 is made larger than the gap ΔG between the inner peripheral surface of the sprocket gear and the outer peripheral surface of the washer member 18. According to this configuration, the small-diameter portion of the inclined surface 19 is made smaller than the inner peripheral surface of the first bearing B1 even in a state where the sprocket gear moves downward until the gap ΔG is eliminated due to the weight of the sprocket gear or the like in the upper portion. Can be inserted on the lower side. Therefore, the sprocket gear can be moved upward by using the inclined surface 19 by moving the connecting member 10 to the first axial direction X1, and the outer periphery of the bearing support portion 17 is arranged on the inner peripheral surface of the first bearing B1. The surfaces can be fitted.

[Other Embodiments]
Finally, other embodiments will be described. Note that the configuration of each embodiment described below is not limited to being applied independently, and can be applied in combination with the configuration of other embodiments as long as no contradiction arises.

(1) In the above embodiment, the case where the connecting member 10 (bearing support portion 17) is rotatably supported with respect to the support portion 20 of the case CS via the first support bearing B2a has been described as an example. . However, the embodiment of the present invention is not limited to this. That is, as shown in FIG. 6, the first support bearing B <b> 2 a may not be provided between the inner peripheral surface of the bearing support portion 17 of the connecting member 10 and the outer peripheral surface of the support portion 20 of the case CS. . Even in this case, the inner peripheral surface of the support portion 20 of the case CS rotatably supports the outer peripheral surface of the transmission input member TI via the second support bearing B2b, and the connecting member 10 is connected to the second support bearing B2b. And it is rotatably supported with respect to the case CS via the speed change input member TI. Even in this case, the inner peripheral surface of the inner boss portion 46 of the connecting member 10 is configured to contact the outer peripheral surface of the speed change input member TI except for the spline fitting portion, and the connection member 10 is connected to the speed change input member TI. Therefore, the shaft support accuracy of the connecting member 10 can be maintained even if the first support bearing B2a is not provided.

(2) In the above-described embodiment, the pump drive member GO has been described as an example in which the pump drive member GO is connected to rotate integrally with the first transmission gear S1. However, the embodiment of the present invention is not limited to this. That is, the pump drive member GO and the first transmission gear S1 may be configured to be coupled via an engagement device such as a one-way clutch or a friction engagement device.

(3) In the above embodiment, the second transmission gear S2 and the connecting member 10 are drivingly connected via the first one-way clutch F1, and the input member I and the second transmission gear S2 are the second one-way. The case where it is drive-coupled via the clutch F2 has been described as an example. However, the embodiment of the present invention is not limited to this. The first one-way clutch F1 and the second one-way clutch F2 as in the above embodiment may not be provided. For example, the first transmission gear S1 is drivingly connected to the rotor support member 40 and the connecting member 10 via the engagement device CL, and the first transmission gear S1 is drivingly connected to the pump driving member GO via the first one-way clutch. The pump driving member GO may be drivingly connected to the connecting member 10 via the second one-way clutch. Even in this case, the engaging device CL engages or releases the input member I and the connecting member 10.
Alternatively, the second transmission gear S2 is connected to the input member I (internal combustion engine EN), the first transmission gear S1 is connected to the pump drive member GO, and the rotor support member 40 and the connection member 10 are connected via the engagement device CL. The input member I may be drivingly connected.

(4) In the above embodiment, the pump driving member GO (sprocket gear) and the pump OP have been described as an example in which they are drivingly connected via the chain CH. However, the embodiment of the present invention is not limited to this. That is, the pump drive member GO and the pump OP may be drivingly connected via a gear mechanism, a belt-type transmission mechanism, or the like.

(5) In the above embodiment, the first meshing portion 11, the first transmission gear S 1, and the pump drive member GO are closer to the first axial side X 1 than the radially inner portion 13 of the radially extending portion 16. The case where the second meshing portion 12 and the second transmission gear S2 are arranged on the second axial side X2 relative to the radial inner portion 13 has been described as an example. However, the embodiment of the present invention is not limited to this. For example, the connecting member 10 includes a cylindrical cylindrical portion extending in the axial direction X, and the pinion gear P is rotatably supported by the cylindrical portion while penetrating the cylindrical portion in the radial direction. The first transmission gear S1 that meshes with the outer portion in the direction and the pump drive member GO that is drivingly connected to the first transmission gear S1 are arranged radially outside the cylindrical portion and mesh with the radially inner portion of the pinion gear P. The two transmission gears S2 may be configured to be arranged on the radially inner side of the cylindrical portion.

(6) In the above embodiment, the case where the washer member 18 is provided on the radially inner side of the pump drive member GO (sprocket gear) has been described as an example. However, the embodiment of the present invention is not limited to this. That is, the washer member 18 may not be provided. For example, at the time of assembly, the pump drive member GO is configured to be held at a position where the outer peripheral surface of the bearing support portion 17 can be fitted to the inner peripheral surface of the first bearing B1 by an assembly holder. May be. Alternatively, the first radially extending wall 41 of the case CS is radially inward of the sprocket gear and the first axial side X1 of the first bearing B1, up to a position overlapping the sprocket gear when viewed in the radial direction, You may have the annular plate-shaped part of the shape similar to the washer member 18 which protruded to the axial direction 2nd side X2.

2. Outline of Embodiment of the Present Invention The embodiment of the present invention described above has at least the following configuration.
An input member (I) that is drivingly connected to the internal combustion engine (EN), a transmission mechanism (TM) that is drivingly connected to the wheel (W) side, a rotor (Ro) of a rotating electrical machine (MG), and a rotor (Ro) A coupling member (10) for driving and coupling the transmission mechanism (TM), an engagement device (CL) for engaging or releasing the input member (I) and the coupling member (10), a case (CS), A drive device (1) for a vehicle having a pinion gear (P) supported by a connecting member (10) and having a first meshing portion (11) and a second meshing portion (12), and a pump ( OP), a first drive gear (S1) that is drivingly connected to the pump driving member (GO) and meshes with the first meshing portion (11), and an input member (I). And a second transmission gear (S2) engaged with the second meshing portion (12). The connecting member (10) is rotatably supported with respect to the case (CS) via the second bearing (B2), and the pump drive member (GO) is connected to the connecting member via the first bearing (B1). (10) is supported rotatably.

According to the above configuration, the rotation of the driving force source of the internal combustion engine (EN) and the rotating electrical machine (MG) is transmitted to the pump driving member (GO) via the pinion gear (P) and the first transmission gear (S1). The pump (OP) is configured to rotate. At this time, since the pump driving member (GO) also rotates, the rotational speed difference between the pump driving member (GO) and the connecting member (10) is determined by the rotational speed difference between the pump driving member (GO) and the case (CS). May also be smaller. In particular, when the engaging device is engaged and the input member (I) and the connecting member (10) rotate at the same rotational speed, the pinion gear (P) does not rotate and revolves at the same speed as the connecting member (10). As a result, the pump drive member (GO) and the connecting member (10) rotate at the same speed.
Unlike the above configuration, when the pump drive member (GO) is configured to be rotatably supported with respect to the case (CS) via the first bearing (B1), the pump drive member (GO) Is rotating, a rotational speed difference is generated between the pump drive member (GO) and the case (CS), and a frictional force corresponding to the rotational speed difference is generated in the first bearing (B1). Loss occurs.
On the other hand, in the above configuration, the pump drive member (GO) is configured to be rotatably supported with respect to the connecting member (10) via the first bearing (B1). The difference in rotational speed of B1) can be reduced, the frictional force generated in the first bearing (B1) can be reduced, and the torque loss can be reduced. In particular, when the pump drive member (GO) and the connecting member (10) are rotating at the same speed, the difference in rotational speed of the first bearing (B1) can be made zero, so that torque loss does not occur. Can be.

  In the embodiment of the present invention, the internal combustion engine (EN), the rotating electrical machine (MG), and the speed change mechanism (TM) are arranged in this order along the axial direction (X), and the speed is changed from the internal combustion engine (EN) in the axial direction X. The side toward the mechanism (TM) is the first axial direction (X1), and the side from the speed change mechanism (TM) in the axial direction X to the internal combustion engine (EN) is the second axial direction (X2). The gear (S1) is disposed on the first axial side (X1) of the connecting member (10), and the second transmission gear (S2) is disposed on the second axial side (X2) of the connecting member (10). The pump drive member (GO) is a sprocket gear disposed on the first axial side (X1) with respect to the first transmission gear (S1). The pump (OP) and the sprocket gear are connected to the chain (CH). The first bearing (B1) is connected to the pump drive member (GO). Between the connecting member (10) and the sprocket gear radially inward and on the first axial side (X1) of the first bearing (B1) at a position overlapping the sprocket gear when viewed in the radial direction. It is preferable that an annular plate washer member (18) is disposed.

  Since the pump drive member (GO) is rotatably supported with respect to the connection member (10) via the first bearing (B1), the connection member (10) in the manufacturing process of the vehicle drive device (1). In the state where is not assembled, the pump drive member (GO) is not supported by the connecting member (10), and it is not easy to position the pump drive member (GO). According to the above configuration, the washer member (18) can support the pump drive member (GO) from the radially inner side, and the connection member (10) in a state where the position of the pump drive member (GO) is provisionally determined. ) Can be assembled. Therefore, it becomes easy to assemble the pump drive member (GO), the first bearing (B1), and the connecting member (10).

  Moreover, in embodiment of this invention, a connection member (10) is provided with the cylindrical bearing support part (17) which supports a 1st bearing (B1) from radial inside, and the outer peripheral surface of a bearing support part (17) In the end of the first axial direction (X1), an inclined surface (19) is formed which is directed radially inward toward the first axial direction (X1), and a large diameter portion of the inclined surface (19) is formed. The difference in radius (ΔR) from the small diameter portion is preferably larger than the gap (ΔG) between the inner peripheral surface of the sprocket gear and the outer peripheral surface of the washer member (18).

  Before the connecting member (10) is assembled, the sprocket gear moves below the assembly position by the gap (ΔG) due to the weight of the sprocket gear or the like, and the upper gap (ΔG) disappears. In this state, it is difficult to assemble the pump drive member (GO), the first bearing (B1), and the connecting member (10). According to said structure, a small diameter part of an inclined surface (19) can be inserted below an inner peripheral surface of a 1st bearing (B1) in an upper part. Therefore, at the time of assembly, the sprocket gear can be moved upward using the inclined surface (19) by moving the connecting member (10) to the first axial direction (X1), and the pump drive member (GO) ), The first bearing (B1), and the connecting member (10) can be easily assembled.

  Moreover, in embodiment of this invention, it is suitable if the internal peripheral surface of a washer member (18) is supported from the radial inside by the support part (20) provided in the case (CS).

  According to this configuration, since the washer member (18) is supported by the case (CS), the washer member (18) is rotated by the rotation of the rotating member in a state where the connecting member (10) is assembled. It is possible to suppress the generation of friction loss and abnormal noise.

  Moreover, in embodiment of this invention, the rotor support member (40) which supports a rotor (Ro) is provided, and a connection member (10) is connected with the 1st connection part (14) connected with a rotor support member (40). , A radially extending portion (16) extending in the radial direction by connecting the second connecting portion (15) connected to the transmission mechanism (TM), the first connecting portion (14), and the second connecting portion (15). And a bearing support portion (17) that supports the first bearing (B1), and the pinion gear (P) is rotatably supported with respect to the radially extending portion (16), and is axially (X). Are arranged in the order of the internal combustion engine (EN), the rotating electrical machine (MG), and the speed change mechanism (TM), and the side toward the speed change mechanism (TM) from the internal combustion engine (EN) in the axial direction X is defined as the axial first side ( X1), and the side from the speed change mechanism (TM) toward the internal combustion engine (EN) in the axial direction X is the axis The first meshing portion (11), the first transmission gear (S1), and the pump drive member (GO) are located on the second direction side (X2) than the pinion gear (P) in the radially extending portion (16). The second meshing portion (12) and the second transmission gear (S2) are arranged on the first inner side (X1) in the axial direction relative to the inner radial portion (13) that is the radially inner portion. It is arranged on the second axial side (X2) from (13), and the bearing support (17) is formed in a cylindrical shape protruding from the radial inner side (13) to the first axial side (X1). It is preferable that

  According to this configuration, the first transmission gear (S1) and the pump drive member (GO) are arranged on the first axial side (X1) with respect to the radially inner portion (13) of the radially extending portion (16). The pump (OP) can be disposed at a position close to the transmission mechanism (TM). And it arrange | positioned at the axial direction 1st side (X1) rather than the radial direction inner side part (13) by the bearing support part (17) which protruded from the radial direction inner side part (13) to the axial direction 1st side (X1). The pump drive member (GO) can be supported via the first bearing (B1).

  In the embodiment of the present invention, the second transmission gear (S2) and the connecting member (10) are drivingly connected via the first one-way clutch (F1), and the first one-way clutch (F1) is connected. The rotation speed of the member (10) is restricted to be higher than the rotation speed of the second transmission gear (S2), and the input member (I) and the second transmission gear (S2) are connected to the second one-way clutch (F2). ), And the second one-way clutch (F2) is preferably configured to restrict the rotational speed of the input member (I) from being higher than the rotational speed of the second transmission gear (S2). is there.

  According to this configuration, the first transmission gear (S1) is rotated at the same speed as the higher one of the rotating electrical machine (MG) and the internal combustion engine (EN), and is driven by the first transmission gear (S1). The pump (OP) is rotationally driven through the connected pump drive member (GO). Accordingly, the engagement device (CL) is engaged and the parallel running mode in which the vehicle is driven by the driving force of the rotating electrical machine (MG) and the internal combustion engine (EN), or the engagement device (CL) is released, and the internal combustion engine ( In the electric travel mode in which the rotation is stopped and the vehicle is driven by the driving force of the rotating electrical machine (MG), the pump drive member (GO) and the connecting member (10) are rotated at the same speed. Therefore, while the vehicle is traveling in the parallel traveling mode or the electric traveling mode, the pump driving member (GO) and the connecting member (10) rotate at the same speed, so the frequency of rotation at the same speed increases, and the first bearing The effect of reducing the torque loss (B1) is increased.

  The present invention includes an input member that is drivingly connected to an internal combustion engine, a transmission mechanism that is drivingly connected to a wheel side, a rotor of a rotating electrical machine, a connecting member that drives and connects the rotor and the transmission mechanism, and the input member It can utilize suitably for the drive device for vehicles provided with the engagement apparatus which engages or releases | releases and the said connection member, and a case.

DESCRIPTION OF SYMBOLS 1: Vehicle drive device 10: Connecting member 11: 1st meshing part 12: 2nd meshing part 13: Radial direction inner side part 14: 1st coupling part 15: 2nd coupling part 16: Radial direction extension part 17 : Bearing support portion 18: washer member 19: inclined surface 20: case support portion 40: rotor support member B1: first bearing B2: second bearing CH: chain CL: engagement device CS: case EN: internal combustion engine F1: First one-way clutch F2: Second one-way clutch GO: Pump drive member I: Input member MG: Rotating electric machine OP: Pump P: Pinion gear Ro: Rotating electric machine rotor S1: First transmission gear S2: Second transmission gear TI: Shifting Input member TM: Transmission mechanism X: Axial direction X1: Axial first side X2: Axial second side ΔG: Clearance between the inner peripheral surface of the sprocket gear and the outer peripheral surface of the washer member

Claims (6)

An input member that is drivingly connected to the internal combustion engine, a transmission mechanism that is drivingly connected to the wheel side, a rotor of a rotating electrical machine, a connecting member that drives and connects the rotor and the transmission mechanism, the input member, and the connecting member A vehicle drive device comprising: an engagement device that engages or releases; and a case,
A pinion gear supported by the connecting member and having a first meshing portion and a second meshing portion, a pump driving member drivingly connected to a pump, and drivingly connected to the pump driving member, and connected to the first meshing portion. A first transmission gear that meshes, and a second transmission gear that is drivingly connected to the input member and meshes with the second meshing portion,
The pump driving member is rotatably supported with respect to the connecting member via a first bearing, and the connecting member is rotatably supported with respect to the case via a second bearing. apparatus. The internal combustion engine, the rotating electrical machine, and the speed change mechanism are arranged in this order along the axial direction, and the side toward the speed change mechanism from the internal combustion engine in the axial direction is defined as the first side in the axial direction. The side facing the internal combustion engine is the second axial direction,
The first transmission gear is disposed on the first axial side of the connecting member,
The second transmission gear is disposed on the second axial side of the connecting member,
The pump drive member is a sprocket gear disposed on the first axial side of the first transmission gear,
The pump and the sprocket gear are drivingly connected via a chain,
The first bearing is disposed between the pump driving member and the connecting member;
An annular plate washer member is disposed at a position radially inward of the sprocket gear and on the first axial side of the first bearing and overlapping the sprocket gear when viewed in the radial direction. Item 2. The vehicle drive device according to Item 1. The connecting member includes a cylindrical bearing support portion that supports the first bearing from the radially inner side,
At the end portion on the first axial side of the outer peripheral surface of the bearing support portion, an inclined surface is formed which is directed radially inward toward the first axial direction side.
The vehicle drive device according to claim 2, wherein a difference in radius between the large-diameter portion and the small-diameter portion of the inclined surface is larger than a gap between the inner peripheral surface of the sprocket gear and the outer peripheral surface of the washer member.   4. The vehicle drive device according to claim 2, wherein an inner peripheral surface of the washer member is supported from a radially inner side by a support portion provided in the case. 5. A rotor support member for supporting the rotor;
The connecting member connects the first connecting part connected to the rotor support member, the second connecting part connected to the speed change mechanism, the first connecting part and the second connecting part in the radial direction. A radially extending portion that extends, and a bearing support portion that supports the first bearing,
The pinion gear is supported rotatably with respect to the radially extending portion,
The internal combustion engine, the rotating electrical machine, and the speed change mechanism are arranged in this order along the axial direction, and the side toward the speed change mechanism from the internal combustion engine in the axial direction is defined as the first side in the axial direction. The side facing the internal combustion engine is the second axial direction,
The first meshing portion, the first transmission gear, and the pump driving member are on the first axial side with respect to the radially inner portion that is a radially inner portion of the radially extending portion than the pinion gear. Placed in
The second meshing portion and the second transmission gear are disposed on the second axial side than the radially inner portion,
5. The vehicle drive device according to claim 1, wherein the bearing support portion is formed in a cylindrical shape protruding from the radially inner portion toward the first axial side. The second transmission gear and the connecting member are drivingly connected via a first one-way clutch,
The first one-way clutch restricts the rotational speed of the connecting member from being higher than the rotational speed of the second transmission gear;
The input member and the second transmission gear are drivingly connected via a second one-way clutch,
The vehicle drive device according to any one of claims 1 to 5, wherein the second one-way clutch regulates that the rotation speed of the input member is higher than the rotation speed of the second transmission gear.

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