JP2022028584A - Vehicular drive device - Google Patents

Abstract

To provide a vehicular drive device which can reduce a radial dimension to a small dimension.SOLUTION: A vehicular drive device is provided with: a first bearing B1 which supports a second rotary member RT2 in a manner that the second rotary member RT2 can rotate relative to a first rotary member RT1; and a second bearing B2 which supports the first rotary member RT1 in a manner that the first rotary member RT1 can rotate relative to a case 4. The first rotary member RT1 includes: a support outer peripheral surface 11a facing the radial outer side R2; and a first radial support surface 13a facing one side in a radial direction R. The second rotary member RT2 includes a support inner peripheral surface 51a facing the radial inner side R1. A support 41 of the case 4 includes a second radial support surface 41a facing the first radial support surface 13a. The first bearing B1 is disposed between the support outer peripheral surface 11a and the support inner peripheral surface 51a. The second bearing B2 is disposed between the radial support surfaces 13a, 41a. The first bearing B1 is disposed at a position which is located at the radial inner side R1 relative to a rotor Ro and overlaps with the rotor Ro in a radial direction view.SELECTED DRAWING: Figure 3

Description

In the present invention, an input member that is driven and connected to an internal combustion engine, an output member that is driven and connected to a wheel, a rotary electric machine that functions as a driving force source for the wheel, and a rotation transmitted from the side of the rotary electric machine are speed-shifted. The present invention relates to a vehicle drive device including a transmission for transmitting to the output member side, a rotary electric machine, and a case for accommodating the transmission.

An example of such a vehicle drive device is disclosed in Patent Document 1 below. Hereinafter, in the description of "background technology" and "problems to be solved by the invention", the reference numerals in Patent Document 1 are quoted in parentheses.

The vehicle drive device of Patent Document 1 includes a first bearing that rotatably supports a rotor support member (3) that supports a rotor (Ro) of a rotary electric machine (MG) with respect to a case (2). (51) and a second bearing (53) that rotatably supports the input member (I) relative to the case (2) are provided. Each of these bearings (51, 53) is directly supported by the case (2).

International Publication No. 2019/187597 (Fig. 4)

In the above configuration, the portions for supporting the two bearings (51, 53) in the case (2) are arranged side by side in the radial direction (R). Therefore, it is easy to increase the size of the vehicle drive device in the radial direction (R).

Therefore, it is desired to realize a vehicle drive device that can easily keep the radial dimension small.

In view of the above, the characteristic configuration of the vehicle drive device is
The input member that is driven and connected to the internal combustion engine and
The output member that is driven and connected to the wheel,
A rotary electric machine equipped with a rotor and functioning as a driving force source for the wheels,
A transmission that shifts the rotation transmitted from the rotary electric machine side and transmits it to the output member side.
A case for accommodating the rotary electric machine and the transmission is provided.
The input member or a member that rotates integrally with the input member is used as a first rotating member, and the rotor or a member that rotates integrally with the rotor is used as a second rotating member.
A first bearing that supports the second rotating member with respect to the first rotating member so that the second rotating member rotates relative to the first rotating member.
A second bearing that supports the first rotating member with respect to the case is provided so that the first rotating member rotates relative to the case.
The case comprises a support for supporting the second bearing.
The first rotating member includes a support outer peripheral surface facing outward in the radial direction and a first radial support surface facing one side in the radial direction.
The second rotating member includes a support inner peripheral surface facing inward in the radial direction.
The support includes a second radial support surface that is radially opposed to the first radial support surface.
The first bearing is arranged between the support outer peripheral surface and the support inner peripheral surface in the radial direction.
The second bearing is arranged between the first radial support surface and the second radial support surface in the radial direction.
The first bearing is located inside the rotor in the radial direction and is arranged at a position overlapping the rotor in the radial direction along the radial direction.

According to this characteristic configuration, the second rotating member is rotatably supported with respect to the case via the first bearing, the first rotating member, and the second bearing. Therefore, the case is formed with a second radial support surface for supporting the second bearing, whereas the surface for supporting the first bearing is not formed, and the first rotating member is formed. , A support outer peripheral surface for supporting the first bearing is formed. Therefore, it is possible to avoid a configuration in which the portion for supporting the first bearing and the portion for supporting the second bearing are arranged side by side in the radial direction in the case. As a result, it is easy to keep the radial dimension of the vehicle drive device small.

Schematic diagram showing a schematic configuration of a vehicle drive device according to a first embodiment. Partial sectional view of the vehicle drive device according to the first embodiment. Partially Enlarged Sectional View of Vehicle Drive Device According to First Embodiment Partial sectional view of the vehicle drive device according to the second embodiment. Partially Enlarged Sectional View of Vehicle Drive Device According to Second Embodiment Partial sectional view of the vehicle drive device according to another embodiment.

1. 1. First Embodiment In the following, the vehicle drive device 100 according to the embodiment will be described with reference to the drawings. The vehicle drive device 100 according to the present embodiment is configured to be mounted on an FF (Front Engine Front Drive) vehicle.

As shown in FIG. 1, the vehicle drive device 100 is a device for driving a vehicle (hybrid vehicle) that uses one or both of an internal combustion engine EG and a rotary electric machine MG as a drive force source for the wheels W. That is, the vehicle drive device 100 is configured as a so-called one-motor parallel type hybrid vehicle drive device.

In the following description, unless otherwise specified, "axial direction L", "diameter direction R", and "circumferential direction" are defined with reference to the rotation axis of the rotary electric machine MG. Then, in the axial direction L, the side on which the rotary electric machine MG is arranged with respect to the internal combustion engine EG is referred to as "axial first side L1", and the opposite side is referred to as "axial second side L2". Further, in the radial direction R, the rotation axis side of the rotary electric machine MG is referred to as "diameter inner side R1", and the opposite side thereof is referred to as "diameter outer side R2". The direction of each member represents the direction in which they are assembled to the vehicle drive device 100. In addition, the terms related to the direction, position, etc. of each member are concepts that include a state in which there is a difference due to an error that can be tolerated in manufacturing.

The rotary electric machine MG functions as a driving force source for the wheels W. The rotary electric machine MG includes a stator St and a rotor Ro. The rotary electric machine MG has a function as a motor (motor) that receives power supply and generates power, and a function as a generator (generator) that receives power supply and generates power. Therefore, the rotary electric machine MG is electrically connected to a power storage device (battery, capacitor, etc.). The rotary electric machine MG receives power supplied from the power storage device to perform power, or supplies power generated by the torque of the internal combustion engine EG or the inertial force of the vehicle to the power storage device to store the power.

The internal combustion engine EG functions as a driving force source for the wheels W, similarly to the rotary electric machine MG. The internal combustion engine EG is a prime mover (gasoline engine, diesel engine, etc.) driven by combustion of fuel to extract power.

As shown in FIG. 1, the vehicle drive device 100 includes an input member 1, an output member 2, a transmission 3, and a case 4 in addition to the rotary electric machine MG described above. In the present embodiment, the vehicle drive device 100 further includes a fluid coupling 5, a disengagement engagement device 6, a counter gear mechanism CG, and a differential gear mechanism DF.

The input member 1 is driven and connected to the internal combustion engine EG. In the present embodiment, it is driven and connected to the output shaft of the internal combustion engine EG via a damper device DP (see FIG. 2) that attenuates fluctuations in the transmitted torque.

Here, in the present application, the "driving connection" refers to a state in which two rotating elements are connected so as to be able to transmit a driving force, and a state in which the two rotating elements are connected so as to rotate integrally, or the said. It includes a state in which two rotating elements are mutably connected so that a driving force can be transmitted through one or more transmission members. Such transmission members include various members that transmit rotation at the same speed or at different speeds, such as a shaft, a gear mechanism, a belt, and a chain. The transmission member may include an engaging device that selectively transmits rotation and driving force, for example, a friction engaging device, a meshing type engaging device, and the like.

The disengagement engaging device 6 is arranged in a power transmission path between the input member 1 and the rotary electric machine MG. The disengagement engaging device 6 corresponds to the "first engaging device CL1" that disconnects and connects the power transmission between the input member 1 and the rotary electric machine MG.

The transmission 3 shifts the rotation transmitted from the side of the rotary electric machine MG and transmits it to the side of the output member 2. In the present embodiment, the transmission 3 includes a shift input shaft 31 as an input element of the transmission 3 and a shift output gear 32 as an output element of the transmission 3. Examples of the transmission 3 include various known automatic transmissions such as a stepped automatic transmission capable of switching between a plurality of gears and a continuously variable automatic transmission capable of steplessly changing the gear ratio. Used.

The fluid coupling 5 is arranged in a power transmission path between the rotary electric machine MG and the transmission 3. The fluid coupling 5 includes a rotary housing 51. In the present embodiment, the fluid coupling 5 is a torque converter including a pump impeller 52, a turbine runner 53, and a lockup clutch 54 in addition to the rotary housing 51.

The rotary housing 51 is connected so as to rotate integrally with the rotor Ro of the rotary electric machine MG. The rotary housing 51 houses the pump impeller 52 and the turbine runner 53. The pump impeller 52 and the turbine runner 53 are arranged so as to face each other in the axial direction L. In the present embodiment, the pump impeller 52 is arranged so as to face the turbine runner 53 on the first side L1 in the axial direction. The pump impeller 52 and the turbine runner 53 are supported so as to rotate relative to each other. The pump impeller 52 is connected to the rotating housing 51 so as to rotate integrally. The turbine runner 53 is connected so as to rotate integrally with the shift input shaft 31 of the transmission 3.

The lockup clutch 54 is configured to selectively engage the pump impeller 52 and the turbine runner 53 in a direct connection state. That is, the lockup clutch 54 is in a directly connected engagement state between the rotary housing 51 that rotates integrally with the rotor Ro of the rotary electric machine MG and the shift input shaft 31 of the transmission 3, and the pump impeller 52 and the turbine runner 53. It is configured to be switchable to any of the states in which power is transmitted through the fluid between the two. As described above, the lockup clutch 54 corresponds to the "second engaging device CL2" that connects and disconnects the power transmission between the rotary electric machine MG and the transmission 3.

The counter gear mechanism CG includes a counter input gear G1 as an input element of the counter gear mechanism CG and a counter output gear G2 as an output element of the counter gear mechanism CG. The counter input gear G1 meshes with the shift output gear 32 of the transmission 3. The counter output gear G2 is connected so as to rotate integrally with the counter input gear G1. In the present embodiment, the counter input gear G1 and the counter output gear G2 are connected so as to rotate integrally via a counter shaft CS extending along the axial direction L.

The differential gear mechanism DF includes a differential input gear G3 that meshes with the counter output gear G2 of the counter gear mechanism CG. The differential gear mechanism DF distributes the rotation of the differential input gear G3 as an input element of the differential gear mechanism DF to the pair of output members 2.

The output member 2 is drive-connected to the wheel W. In the present embodiment, each of the pair of output members 2 is driven and connected to the wheel W via the drive shaft DS.

The case 4 houses the rotary electric machine MG and the transmission 3. In the present embodiment, the case 4 also houses the fluid coupling 5, the disengagement engaging device 6, the counter gear mechanism CG, and the differential gear mechanism DF.

As shown in FIG. 2, the stator St of the rotary electric machine MG has a stator core Stc fixed to a non-rotating member (here, case 4). The rotor Ro of the rotary electric machine MG has a rotor core Roc that rotates relative to the stator St.

In the present embodiment, since the rotary electric machine MG is an inner rotor type rotary electric machine, the rotor core Roc is arranged on the radial inner side R1 of the stator core Stc.

Further, in the present embodiment, the rotary electric machine MG is a rotary field type rotary electric machine. Therefore, the stator coil is wound around the stator core Stc so that coil end portions Ce projecting from the stator core Stc on both sides in the axial direction L (the first side L1 in the axial direction and the L2 on the second side in the axial direction) are formed. Has been done. Further, the rotor core Roc is provided with a permanent magnet (not shown).

As shown in FIG. 2, in the vehicle drive device 100, the second rotating member RT2 is rotated relative to the first rotating member RT1 so that the second rotating member RT2 rotates relative to the first rotating member RT1. A first bearing B1 that supports the first rotating member RT1 and a second bearing B2 that supports the first rotating member RT1 with respect to the case 4 are provided so that the first rotating member RT1 rotates relative to the case 4. ing.

The first rotating member RT1 is an input member 1 or a member that rotates integrally with the input member 1. In the present embodiment, the first rotating member RT1 is an input member 1.

The second rotating member RT2 is a rotor Ro or a member that rotates integrally with the rotor Ro. In the present embodiment, the second rotating member RT2 is a rotating housing 51 of the fluid coupling 5 or a member that rotates integrally with the rotating housing 51. In this example, the second rotating member RT2 is a rotating housing 51.

As shown in FIG. 3, the input member 1 includes a support outer peripheral surface 11a facing the radial outer side R2 and a first radial support surface 13a facing one side of the radial direction R. The rotary housing 51 includes a support inner peripheral surface 51a facing the radial inner R1. In the present embodiment, the rotary housing 51 further includes a rotor support surface 51b facing the radial outer side R2. The rotor support surface 51b is formed so as to support the rotor Ro of the rotary electric machine MG from the radial inner side R1. That is, the rotor support surface 51b is formed so as to be in contact with the inner peripheral surface of the rotor Ro.

The case 4 includes a first support 41. The first support 41 is a "support" that supports the second bearing B2. The first support 41 includes a second radial support surface 41a that faces the radial support surface 13a in the radial direction R.

The first bearing B1 is arranged between the support outer peripheral surface 11a and the support inner peripheral surface 51a in the radial direction R. In the present embodiment, the first bearing B1 is arranged so that the inner peripheral surface of the first bearing B1 and the support outer peripheral surface 11a come into contact with each other, and the outer peripheral surface of the first bearing B1 and the support inner peripheral surface 51a come into contact with each other. Has been done. In the present embodiment, the first bearing B1 is a radial bearing that supports the rotary housing 51 in the radial direction R with respect to the input member 1. In this example, the first bearing B1 is a radial ball bearing.

The second bearing B2 is arranged between the first radial support surface 13a and the second radial support surface 41a in the radial direction R. In the present embodiment, the outer peripheral surface of the second bearing B2 is in contact with the first radial support surface 13a, and the inner peripheral surface of the second bearing B2 is in contact with the second radial support surface 41a. Two bearings B2 are arranged. In the present embodiment, the second bearing B2 is a radial bearing that supports the input member 1 in the radial direction R with respect to the case 4. In this example, the second bearing B2 is a radial ball bearing.

The first bearing B1 is radially inner R1 with respect to the rotor Ro of the rotary electric machine MG, and is arranged at a position overlapping the rotor Ro in the radial direction along the radial direction R. In the present embodiment, both the first bearing B1 and the second bearing B2 are radially inner R1 with respect to the rotor Ro of the rotary electric machine MG, and are arranged at positions overlapping with the rotor Ro in the radial direction. ..

In the present embodiment, the first bearing B1 and the second bearing B2 are arranged so as to overlap each other in the radial direction along the radial direction R. Here, more than half of the axial L region of the first bearing B1 overlaps with the second bearing B2 in the radial direction, and more than half of the axial L region of the second bearing B2 is the first bearing in the radial direction. It is preferable that it overlaps with B1. In this example, three-quarters or more of the regions of the first bearing B1 and the second bearing B2 in the axial direction L overlap each other in the radial direction. In the illustrated example, the dimension of the first bearing B1 in the axial direction L and the dimension of the second bearing B2 in the axial direction L are equivalent. In the present embodiment, the first bearing B1 is radially outside R2 of the second bearing B2, and is arranged at a position overlapping the second bearing B2 in the radial direction along the radial direction R. Here, regarding the arrangement of the two elements, "overlapping in a specific direction" means that the virtual straight line is 2 when the virtual straight line parallel to the line-of-sight direction is moved in each direction orthogonal to the virtual straight line. It means that there is at least a part of the area where both of the two elements intersect.

According to this configuration, the dimension of the vehicle drive device 100 in the axial direction L can be suppressed to be smaller than that in the configuration in which the first bearing B1 and the second bearing B2 are arranged so as to be arranged in the axial direction L.

In the present embodiment, both the first bearing B1 and the second bearing B2 are arranged radially inside R1 with respect to the rotary electric machine MG, and are arranged at positions overlapping with the rotary electric machine MG in the radial direction along the radial direction R. Has been done. In this example, the range that overlaps with the rotary electric machine MG in the radial direction is the axial direction from the end of the axial first side L1 to the end of the axial second side L2 in the stator St including the coil end portion Ce. It is a range of L (see FIG. 2).

According to this configuration, the axial direction L of the vehicle drive device 100 is higher than the configuration in which at least one of the first bearing B1 and the second bearing B2 is arranged on one side of the axial direction L with respect to the rotary electric machine MG. The dimensions can be kept small.

Further, in this example, both the first bearing B1 and the second bearing B2 are arranged at positions overlapping with the rotor Ro in the radial direction along the radial direction R. In this example, the range that overlaps with the rotor Ro in the radial direction is the axial direction from the end of the axial first side L1 to the end of the axial second side L2 in the rotor Ro (here, the rotor core Roc). It is in the range of L.

According to this configuration, the shaft of the vehicle drive device 100 is compared with the configuration in which at least one of the first bearing B1 and the second bearing B2 is arranged on one side of the axial direction L with respect to the rotor Ro of the rotary electric machine MG. The dimension of the direction L can be kept small.

In the present embodiment, the first radial support surface 13a is formed so as to face the radial inner R1.
The second radial support surface 41a is formed so as to face the radial outer side R2.

According to this configuration, in the radial inner side R1 of the second radial support surface 41a of the first support 41 in the case 4, between the first rotating member RT1 and the first support 41 in the radial direction R. It is easy to secure a space for installing the arranged members. That is, it is easy to install a member arranged between the first rotating member RT1 and the first support 41 in the radial direction R on one side of the radial direction R with respect to the first bearing B1 and the second bearing B2. It is composed. As a result, even when a predetermined member is installed between the first rotating member RT1 and the first support 41 in the radial direction R, the dimension of the axial direction L of the vehicle drive device 100 can be kept small. Is easy.

In the present embodiment, as shown in FIG. 2, the vehicle drive device 100 is provided with a third bearing B3 and a fourth bearing B4 that rotatably support the rotary housing 51 with respect to the case 4.

The third bearing B3 is a radial bearing that supports the rotary housing 51 in the radial direction R with respect to the case 4. In the present embodiment, the third bearing B3 supports the axially extending portion 517 included in the rotary housing 51 in the radial direction R with respect to the second support 42 of the case 4. In this example, the third bearing B3 is a radial roller bearing.

The axial extending portion 517 is formed in a cylindrical shape having an axial center along the axial direction L. The axial extending portion 517 is arranged so as to cover the radial outer side R2 with respect to the shift input shaft 31. Here, the third bearing B3 is configured to be movable in the axial direction L between the axial extending portion 517 and at least one of the second support 42. As a result, even if the axial L dimension of the rotary housing 51 fluctuates due to expansion (so-called ballooning) of the rotary housing 51 due to the hydraulic pressure inside the rotary housing 51, the axial extending portion 517 It is permissible to move in the axial direction L.

The fourth bearing B4 is a thrust bearing that supports the rotary housing 51 in the axial direction L with respect to the case 4. In the present embodiment, the fourth bearing B4 supports the radial extending portion 518 included in the rotary housing 51 in the axial direction L with respect to the second support 42 of the case 4. In this example, the fourth bearing B4 is a thrust roller bearing.

The radial extension portion 518 extends along the radial direction R so as to connect the pump accommodating portion 519, which is a portion surrounding the outside of the pump impeller 52 in the rotary housing 51, and the axial extension portion 517. There is. In the present embodiment, the radial extension portion 518 is formed so as to connect the end portion of the radial inner R1 of the pump accommodating portion 519 and the end portion of the axial second side L2 of the axial extension portion 517. Has been done.

In the present embodiment, the first bearing B1 and the second bearing B2 are arranged on the second side L2 in the axial direction with respect to the pump impeller 52 and the turbine runner 53 of the fluid coupling 5. The third bearing B3 and the fourth bearing B4 are arranged on the first side L1 in the axial direction with respect to the pump impeller 52 and the turbine runner 53 of the fluid coupling 5. As described above, in the present embodiment, each of the first bearing B1, the second bearing B2, and the third bearing B3 is a radial bearing. Therefore, in the present embodiment, the rotary housing 51 is supported in the radial direction R with respect to the case 4 via the two bearings B1 and B2 on the second side L2 in the axial direction with respect to the pump impeller 52 and the turbine runner 53. At the same time, it is supported in the radial direction R with respect to the case 4 via one bearing B3 on the first side L1 in the axial direction with respect to the pump impeller 52 and the turbine runner 53. Therefore, in the present embodiment, the rotary housing 51 can be supported in the radial direction R with respect to the case 4 with high support accuracy.

In the present embodiment, an elastic member 10 having elasticity in the axial direction L is provided between the fourth bearing B4 in the axial direction L and the radial extending portion 518. As the elastic member 10, various elastic members such as a compression coil spring, a disc spring, a washer made of rubber or a synthetic resin can be adopted. When the elastic member 10 is elastically deformed in the axial direction L, the size of the rotary housing 51 changes in the axial direction L due to expansion (so-called ballooning) of the rotary housing 51 due to hydraulic pressure inside the rotary housing 51. Even if it does occur, it is permissible for the radial extension 518 to move axially L. That is, the radial extending portion 518 is supported in the axial direction L by the fourth bearing B4 and the elastic member 10, but is allowed to move in the axial direction L. Instead of arranging the elastic member 10 between the fourth bearing B4 in the axial direction L and the radial extending portion 518, between the fourth bearing B4 in the axial direction L and the second support 42 of the case 4. The elastic member 10 may be arranged in the.

As shown in FIG. 3, in the present embodiment, the vehicle drive device 100 further includes a seal member S that seals between the input member 1 and the first support 41 in an oiltight manner.

In the present embodiment, the input member 1 includes a sealing outer peripheral surface 12a facing the radial outer side R2. Further, in the present embodiment, the first support 41 includes a sealing inner peripheral surface 41b facing the radial inner R1. The seal member S is arranged between the outer peripheral surface for sealing 12a and the inner peripheral surface for sealing 41b in the radial direction R. In the present embodiment, the seal member S is arranged radially inside R1 with respect to the second bearing B2.

As described above, in the present embodiment, the vehicle drive device 100 has a seal member S for oil-tightly sealing between the first rotating member RT1 (here, the input member 1) and the first support 41. Further preparation,
The first rotating member RT1 includes a sealing outer peripheral surface 12a facing the radial outer side R2.
The first support 41 includes a sealing inner peripheral surface 41b facing the radial inner R1.
The seal member S is arranged between the outer peripheral surface for sealing 12a and the inner peripheral surface for sealing 41b in the radial direction R.

According to this configuration, it is possible to appropriately prevent oil from flowing out from between the first rotating member RT1 and the first support 41. Further, in the present embodiment, with this configuration, the seal member S is arranged on one side of the radial direction R (here, the radial inner side R1) with respect to the first bearing B1 and the second bearing B2. Can be done. As a result, even if the seal member S is arranged between the first rotating member RT1 and the first support 41 in the radial direction R, the dimension of the axial direction L of the vehicle drive device 100 is kept small. Is easy.

In the present embodiment, the input member 1 includes an outer cylindrical portion 11, an inner tubular portion 12, and a connecting portion 13. The outer tubular portion 11 is formed in a tubular shape having an axial center along the axial direction L. The inner tubular portion 12 is formed in a tubular shape having an axial center along the axial direction L. The inner cylindrical portion 12 is arranged radially inside R1 with respect to the outer tubular portion 11. The connecting portion 13 is formed so as to extend along the radial direction R. The connecting portion 13 is formed so as to connect the outer cylindrical portion 11 and the inner tubular portion 12. In the illustrated example, the outer tubular portion 11 is formed so as to extend from the end portion of the radial outer side R2 of the connecting portion 13 toward the first side L1 in the axial direction. The inner tubular portion 12 is formed so as to extend from the end portion of the radial inner R1 of the connecting portion 13 toward the second side L2 in the axial direction.

In the present embodiment, the support outer peripheral surface 11a is formed on the outer peripheral surface of the outer tubular portion 11. Then, on the outer peripheral surface of the inner tubular portion 12, there is an outer peripheral surface 12a for sealing. Further, the connecting portion 13 has a stepped surface facing the radial inner side R1, and the stepped surface is the first radial support surface 13a. Specifically, the connecting portion 13 is provided with a first stepped portion 131 that forms a first radial support surface 13a as a stepped surface facing the radial inner R1. In the illustrated example, the first step portion 131 is bent to the second side L2 in the axial direction with respect to the portion radially inside R1 of the first step portion 131 in the connection portion 13, and the first step in the connection portion 13 is formed. It is formed so as to bend in the first side L1 in the axial direction with respect to the portion R2 radially outer than the portion 131. The inner peripheral surface of the portion extending in the axial direction L of the first step portion 131 is the first radial support surface 13a as the step surface.

As described above, in the present embodiment, the first rotating member RT1 (here, the input member 1) has an outer cylindrical portion 11 formed in a cylindrical shape having an axial center along the axial direction L and an axial direction L. An inner cylindrical portion 12 formed in a cylindrical shape having an axial center along the axis and arranged radially inside R1 from the outer tubular portion 11, and an outer tubular portion 11 extending along the radial direction R. A connection portion 13 for connecting the inner tubular portion 12 and the inner tubular portion 12 is provided.
A support outer peripheral surface 11a is formed on the outer peripheral surface of the outer tubular portion 11.
An outer peripheral surface 12a for sealing is formed on the outer peripheral surface of the inner tubular portion 12, and the outer peripheral surface 12a is formed.
The connecting portion 13 has a stepped surface facing the inner diameter R1 in the radial direction.
The stepped surface is the first radial support surface 13a.

According to this configuration, the support outer peripheral surface 11a, the first radial support surface 13a, and the sealing outer peripheral surface 12a can be appropriately formed on the first rotating member RT1.

In the present embodiment, as shown in FIG. 2, the case 4 includes a second support 42 and a tubular body 43 in addition to the first support 41 described above. The tubular body 43 is formed in a tubular shape having an axial center along the axial direction L. Each of the first support 41 and the second support 42 is formed so as to extend along the radial direction R. The first support 41 and the second support 42 are arranged at intervals in the axial direction L from each other. In the present embodiment, the second support 42 is arranged on the first side L1 in the axial direction with respect to the first support 41. The first support 41 and the second support 42 are connected to the tubular body 43 so as to extend from the tubular body 43 toward the radial inner side R1. In the present embodiment, the rotary electric machine MG, the fluid coupling 5, and the disengagement engaging device 6 are arranged in the space surrounded by the first support 41, the second support 42, and the tubular body 43. ..

As shown in FIG. 3, in the present embodiment, the first support 41 has a cylindrical support portion 411 formed in a cylindrical shape having an axial center along the axial direction L, and a radial support portion 411 from the tubular support portion 411. It is provided with a radial extending portion 412 extending toward the outer R2. In the present embodiment, the tubular support portion 411 is formed so as to cover the radial outer side R2 with respect to the inner tubular portion 12 of the input member 1. Further, the radial extending portion 412 extends along the radial direction R so as to connect the tubular support portion 411 and the tubular body 43. In the present embodiment, the radial extending portion 412 and the connecting portion 13 of the input member 1 are arranged side by side in the axial direction L. Here, the radial extending portion 412 and the connecting portion 13 are arranged so as to face each other in the axial direction L in a state where no other member is sandwiched between the radial extending portions 412 and the connecting portion 13. In the illustrated example, the radial extending portion 412 is arranged adjacent to the axial second side L2 with respect to the connecting portion 13. Further, the radial extending portion 412 and the connecting portion 13 are arranged in parallel with each other.

In the present embodiment, the second radial support surface 41a is formed on the outer peripheral surface of the tubular support portion 411. The inner peripheral surface of the tubular support portion 411 is an inner peripheral surface for sealing 41b.

As described above, in the present embodiment, the first support 41 has a cylindrical support portion 411 formed in a cylindrical shape having an axial center along the axial direction L, and the tubular support portion 411 to the radial outer side R2. With a radial extension 412, which extends toward
A second radial support surface 41a is formed on the outer peripheral surface of the tubular support portion 411.
An inner peripheral surface for sealing 41b is formed on the inner peripheral surface of the tubular support portion 411.
The radial extending portion 412 and the connecting portion 13 are arranged side by side in the axial direction L.

According to this configuration, the second radial support surface 41a and the inner peripheral surface for sealing 41b can be appropriately formed on the first support 41 of the case 4. Further, since the radial extending portion 412 of the first support 41 and the connecting portion 13 of the first rotating member RT1 (here, the input member 1) are arranged side by side in the axial direction L, these are arranged in the axial direction. It is easy to keep the arrangement area of L small, and it is easy to keep the dimension of the vehicle drive device 100 in the axial direction L small.

As described above, in the present embodiment, the vehicle drive device 100 further includes a fluid coupling 5 arranged in the power transmission path between the rotary electric machine MG and the transmission 3.
The fluid coupling 5 includes a rotating housing 51 that rotates integrally with the rotor Ro, and a lockup clutch 54 that is a second engaging device CL2.
The second rotating member RT2 is a rotating housing 51 or a member that rotates integrally with the rotating housing 51.

According to this configuration, the support inner peripheral surface 51a can be appropriately formed by using the rotary housing 51 of the fluid coupling 5 or the member that rotates integrally with the rotary housing 51.

In the present embodiment, the rotary housing 51 includes a cylindrical portion 511 formed in a cylindrical shape having an axial center along the axial direction L. In the illustrated example, the tubular portion 511 projects from the end portion of the radial inner side R1 of the turbine accommodating portion 520, which is a portion surrounding the outer side of the turbine runner 53 in the rotary housing 51, toward the second side L2 in the axial direction. It is formed like this. In the present embodiment, the support inner peripheral surface 51a is formed on the inner peripheral surface of the tubular portion 511. Further, a rotor support surface 51b is formed on the outer peripheral surface of the tubular portion 511.

As described above, in the present embodiment, the second rotating member RT2 is formed so as to face the radial outer side R2, and includes the rotor support surface 51b that supports the rotor Ro from the radial inner side R1.
The rotary housing 51 includes a tubular portion 511 formed in a tubular shape having an axial center along the axial direction L.
A support inner peripheral surface 51a is formed on the inner peripheral surface of the tubular portion 511.
A rotor support surface 51b is formed on the outer peripheral surface of the tubular portion 511.

According to this configuration, the rotor Ro of the rotary electric machine MG and the first bearing B1 can be arranged so as to be aligned in the radial direction R with the tubular portion 511 of the rotary housing 51 interposed therebetween. Therefore, it becomes easy to keep the dimension of the vehicle drive device 100 in the axial direction L small.

In the present embodiment, the seal member S has a diameter of at least one of the first bearing B1, the second bearing B2, the first support portion SP1, the second support portion SP2, the third support portion SP3, and the fourth support portion SP4. They are arranged so as to overlap each other in the radial direction along the direction R. In the illustrated example, the seal member S is arranged so as to overlap with the first bearing B1, the first support portion SP1, the second support portion SP2, and the fourth support portion SP4 in the radial direction.

The first support portion SP1 is a portion of the first rotating member RT1 that forms a surface in contact with the first bearing B1. As described above, in the present embodiment, the outer cylindrical portion 11 of the input member 1 which is the first rotating member RT1 includes a support outer peripheral surface 11a which comes into contact with the first bearing B1 from the radial inner side R1. Further, in the present embodiment, the outer tubular portion 11 includes, in addition to the support outer peripheral surface 11a, a first side surface 11b that comes into contact with the first bearing B1 from the first side L1 in the axial direction. Therefore, in the present embodiment, the first support portion SP1 is a portion of the outer tubular portion 11 that forms the support outer peripheral surface 11a and the portion that forms the first side surface 11b. The portion forming the support outer peripheral surface 11a and the portion forming the first side surface 11b here are regions in contact with the first bearing B1 extending along each of the support outer peripheral surface 11a and the first side surface 11b. In addition, it is a portion including the entire area in the plate thickness direction from each of the support outer peripheral surface 11a and the first side surface 11b to the surface facing the opposite side to each surface.

The second support portion SP2 is a portion of the second rotating member RT2 that forms a surface in contact with the first bearing B1. As described above, in the present embodiment, the tubular portion 511 of the rotating housing 51, which is the second rotating member RT2, includes a support inner peripheral surface 51a that contacts the first bearing B1 from the radial outer side R2. Therefore, in the present embodiment, the second support portion SP2 is a portion of the tubular portion 511 that forms the support inner peripheral surface 51a. The portion forming the support inner peripheral surface 51a here is, in addition to the region in contact with the first bearing B1 extending along the support inner peripheral surface 51a, from the support inner peripheral surface 51a to the surface. Is the part including the entire area in the plate thickness direction up to the surface facing the opposite side.

The third support portion SP3 is a portion of the first rotating member RT1 that forms a surface in contact with the second bearing B2. As described above, in the present embodiment, the first stepped portion 131 formed in the connecting portion 13 of the input member 1 which is the first rotating member RT1 has a first diameter in contact with the second bearing B2 from the radial outer side R2. It is provided with a directional support surface 13a. Further, in the present embodiment, the first step portion 131 includes, in addition to the first radial support surface 13a, a second side surface 13b that comes into contact with the second bearing B2 from the first side L1 in the axial direction. Therefore, in the present embodiment, the third support portion SP3 is a portion of the first step portion 131 that forms the first radial support surface 13a and the second side surface 13b. The portion forming the first radial support surface 13a and the portion forming the second side surface 13b here are the second bearing B2 extending along each of the first radial support surface 13a and the second side surface 13b. In addition to the region in contact with the surface, the portion including the entire area in the plate thickness direction from each of the first radial support surface 13a and the second side surface 13b to the surface facing the opposite side to each surface.

The fourth support portion SP4 is a portion of the first support 41 that forms a surface in contact with the second bearing B2. As described above, in the present embodiment, the tubular support portion 411 of the first support body 41 includes a second radial support surface 41a that contacts the second bearing B2 from the radial inner side R1. Further, in the present embodiment, the tubular support portion 411 includes, in addition to the second radial support surface 41a, a support side surface 41c that comes into contact with the second bearing B2 from the axial second side L2. Therefore, in the present embodiment, the fourth support portion SP4 is a portion of the tubular support portion 411 that forms the second radial support surface 41a and the support side surface 41c. The portion forming the second radial support surface 41a and the portion forming the support side surface 41c are in contact with the second bearing B2 extending along each of the second radial support surface 41a and the support side surface 41c. In addition to the region, it is a portion including the entire area in the plate thickness direction from each of the second radial support surface 41a and the support side surface 41c to the surface facing the opposite side to each surface.

As described above, in the present embodiment, the portion of the first rotating member RT1 (here, the input member 1) that forms the surface in contact with the first bearing B1 is designated as the first support portion SP1 and the second rotating member RT2 (here, the input member 1). , The portion of the rotary housing 51) that forms a surface in contact with the first bearing B1 is referred to as a second support portion SP2, and the portion of the first rotary member RT1 that forms a surface in contact with the second bearing B2 is designated as a third support portion SP3. The portion of the first support 41 that forms a surface in contact with the second bearing B2 is designated as the fourth support portion SP4.
The seal member S has at least one of the first bearing B1, the second bearing B2, the first support portion SP1, the second support portion SP2, the third support portion SP3, and the fourth support portion SP4, and a diameter along the radial direction R. They are arranged so as to overlap in the directional view.

According to this configuration, the seal member S is axially relative to the first bearing B1, the second bearing B2, the first support portion SP1, the second support portion SP2, the third support portion SP3, and the fourth support portion SP4. The dimension of the vehicle drive device 100 in the axial direction L can be suppressed to be smaller than that of the configuration arranged on one side of L.

As shown in FIG. 3, in the present embodiment, the disengagement engaging device 6 as the first engaging device CL1 presses the first friction member 61 and the first friction member 61 in the axial direction L. It includes a 1-piston portion 62 and a first hydraulic oil chamber 63 to which operating oil for the first piston portion 62 is supplied.

The first friction member 61 includes a first inner friction material 611 and a first outer friction material 612. The first inner friction material 611 and the first outer friction material 612 are both formed in the shape of an annular plate, and are arranged (coaxially) with their axes of rotation aligned with each other. Further, a plurality of first inner friction materials 611 and a plurality of first outer friction materials 612 are provided, and these are alternately arranged along the axial direction L. One of the first inner friction material 611 and the first outer friction material 612 can be a friction plate and the other can be a separate plate.

The first outer friction material 612 is supported from the radial outer side R2 by the first friction material support portion 14 included in the input member 1. The first friction material support portion 14 is formed in a cylindrical shape having an axial center along the axial direction L. In the present embodiment, the first friction material support portion 14 is connected to the outer tubular portion 11 so as to rotate integrally. In the illustrated example, the first friction material support portion 14 is formed so as to extend from the outer cylindrical portion 11 toward the first side L1 in the axial direction. In the illustrated example, the first friction material support portion 14 is integrally formed with the outer tubular portion 11. Further, in the present embodiment, the first friction material support portion 14 is arranged on the inner side R1 in the radial direction with respect to the tubular portion 511 of the rotary housing 51.

In this example, a plurality of spline grooves extending in the axial direction L are formed dispersed in the circumferential direction on the outer peripheral portion of the first outer friction member 612. On the other hand, similar spline grooves are also formed in the inner peripheral portion of the first friction material support portion 14 in a dispersed manner in the circumferential direction. Then, by engaging the spline grooves with each other, the first outer friction material 612 is supported from the radial outer side R2 by the first friction material support portion 14. In this way, the first outer friction material 612 is slidably supported in the axial direction L in a state where the relative rotation is restricted with respect to the first friction material support portion 14.

The first inner friction material 611 is supported from the radial inner side R1 by the second friction material support portion 512 included in the rotary housing 51. The second friction material support portion 512 is formed in a cylindrical shape having an axial center along the axial direction L. In the present embodiment, the second friction material support portion 512 is composed of a part of the rotating housing 51 and is connected to the tubular portion 511 so as to rotate integrally. In the illustrated example, the second friction material support portion 512 extends from the end of the axial first side L1 of the tubular portion 511 toward the radial inner R1 and further toward the axial second side L2. It is formed to extend.

In this example, a plurality of spline grooves extending in the axial direction L are formed dispersed in the circumferential direction on the inner peripheral portion of the first inner friction member 611. On the other hand, similar spline grooves are dispersed in the circumferential direction on the outer peripheral portion of the second friction material support portion 512. Then, by engaging the spline grooves with each other, the first inner friction material 611 is supported from the radial inner side R1 by the second friction material support portion 512. In this way, the first inner friction material 611 is slidably supported in the axial direction L in a state where the relative rotation is restricted with respect to the second friction material support portion 512.

The first piston portion 62 is configured to press the first friction member 61 with a pressure corresponding to the hydraulic pressure supplied to the first hydraulic oil chamber 63. In the present embodiment, the first piston portion 62 has a first sliding portion 621 and a first pressing portion 622.

In the present embodiment, the connecting portion 13 of the input member 1 is provided with a second stepped portion 132 that forms a stepped surface 132a facing the radial outer side R2. In the illustrated example, the second step portion 132 is formed so as to project toward the first side L1 in the axial direction. The first sliding portion 621 is configured to slide the stepped surface 132a of the second stepped portion 132 and the inner peripheral surface 11c of the outer cylindrical portion 11 of the input member 1 in the axial direction L. That is, in the present embodiment, the second step portion 132 and the outer tubular portion 11 form a cylinder portion on which the first sliding portion 621 slides. The first sliding portion 621 includes an annular plate-shaped portion extending along the radial direction R and the circumferential direction, and an end portion of the radial inner side R1 and the end portion of the radial outer side R2 of the annular plate-shaped portion. It is formed into a bottomed double cylinder having two tubular portions extending from each in the axial direction L.

The first pressing portion 622 presses the first friction member 61 in the axial direction L. In the present embodiment, the first pressing portion 622 is arranged adjacent to the second side L2 in the axial direction with respect to the first friction member 61. In the illustrated example, the first pressing portion 622 is formed so as to extend from the first sliding portion 621 toward the first side L1 in the axial direction and further extend to the outer side R2 in the radial direction.

The first hydraulic oil chamber 63 is arranged adjacent to the first piston portion 62 in the axial direction L. In the present embodiment, the first hydraulic oil chamber 63 includes a first sliding portion 621, an outer tubular portion 11, a second step portion 132, and an outer tubular portion 11 and a second step portion 132 in the connecting portion 13. It is formed by the part between and.

In the present embodiment, at least one of the first piston portion 62 and the first hydraulic oil chamber 63 is between the first bearing B1 and the second bearing B2 in the radial direction R, and is viewed in the radial direction along the radial direction R. It is arranged at a position overlapping with at least one of the first bearing B1 and the second bearing B2. In the illustrated example, both the first piston portion 62 and the first hydraulic oil chamber 63 are arranged so as to overlap both the first bearing B1 and the second bearing B2 in the radial direction.

As described above, in the present embodiment, the first engaging device CL1 (here, the disconnecting engaging device 6) for disconnecting and connecting the power transmission between the input member 1 and the rotary electric machine MG is further provided.
The first engaging device CL1 is supplied with oil for operating the first friction member 61, the first piston portion 62 that presses the first friction member 61 in the axial direction L, and the first piston portion 62. With a first hydraulic oil chamber 63,
At least one of the first piston portion 62 and the first hydraulic oil chamber 63 is between the first bearing B1 and the second bearing B2 in the radial direction R, and the first bearing B1 in the radial direction along the radial direction R. And is arranged at a position overlapping with at least one of the second bearing B2.

According to this configuration, both the first piston portion 62 and the first hydraulic oil chamber 63 are for vehicles as compared with the configuration in which both the first piston portion 62 and the first hydraulic oil chamber 63 are arranged on one side of the axial direction L with respect to the first bearing B1 and the second bearing B2. The dimension of the drive device 100 in the axial direction L can be kept small.

Further, in the present embodiment, the first piston portion 62 is between the first bearing B1 and the second bearing B2 in the radial direction R, and the first bearing B1 and the second bearing B1 and the second bearing B2 in the radial direction along the radial direction R. It is arranged at a position overlapping with at least one of the bearings B2. In the illustrated example, the first piston portion 62 is arranged so as to overlap both the first bearing B1 and the second bearing B2 in the radial direction.

According to this configuration, the dimension of the vehicle drive device 100 in the axial direction L is compared with the configuration in which the first piston portion 62 is arranged on one side of the axial direction L with respect to the first bearing B1 and the second bearing B2. Can be kept small.

In the present embodiment, among the plurality of first outer friction materials 612, each of the pair of first outer friction materials 612 adjacent to each other in the axial direction L is formed in an annular shape extending along the circumferential direction. A first elastic body 64 having elasticity in the axial direction L is arranged. When the hydraulic pressure supplied to the first hydraulic oil chamber 63 is less than a predetermined value, the first elastic body 64 causes the adjacent first outer friction materials 612 to be separated from each other in the axial direction L by the elastic force. As a result, the disengagement engaging device 6 can be properly released, the drag torque between the friction materials can be reduced, and the disengagement engaging device 6 is unintentionally engaged by centrifugal hydraulic pressure or the like. It is possible to avoid becoming a state. As the first elastic body 64, for example, a wave spring can be adopted.

As shown in FIG. 3, in the present embodiment, the lockup clutch 54 as the second engaging device CL2 has a second friction member 55 and a second piston portion that presses the second friction member 55 in the axial direction L. 56 and a second hydraulic oil chamber 57 to which oil for operating the second piston portion 56 is supplied are provided.

The second friction member 55 includes a second inner friction material 551 and a second outer friction material 552. The second inner friction material 551 and the second outer friction material 552 are both formed in the shape of an annular plate, and are arranged (coaxially) with their rotation axes aligned with each other. Further, a plurality of second inner friction materials 551 and second outer friction materials 552 are provided, and these are alternately arranged along the axial direction L. One of the second inner friction material 551 and the second outer friction material 552 may be a friction plate and the other may be a separate plate.

The second outer friction material 552 is supported from the radial outer side R2 by the above-mentioned second friction material support portion 512. In this example, a plurality of spline grooves extending in the axial direction L are formed dispersed in the circumferential direction on the outer peripheral portion of the second outer friction member 552. On the other hand, similar spline grooves are also formed in the inner peripheral portion of the second friction material support portion 512 in a dispersed manner in the circumferential direction. Then, by engaging the spline grooves with each other, the second outer friction material 552 is supported from the radial outer side R2 by the second friction material support portion 512. In this way, the second outer friction material 552 is slidably supported in the axial direction L in a state where the relative rotation is restricted with respect to the second friction material support portion 512.

The second inner friction material 551 is supported by the support member 7. The support member 7 is connected so as to rotate integrally with the turbine runner 53 of the fluid coupling 5 and the shift input shaft 31 of the transmission 3. In the present embodiment, the shift input shaft 31 has a connecting portion 311 extending toward the radial outer side R2. Then, with respect to the end of the radial inner R2 of the connecting portion 311, the end of the radial inner R1 of the turbine runner 53 and the end of the radial inner R1 of the support member 7 overlap in the axial direction L. , They are integrally connected.

The support member 7 includes a third friction material support portion 71. The third friction material support portion 71 is formed in a cylindrical shape having an axial center along the axial direction L. The third friction material support portion 71 is formed so as to extend from the connecting portion of the support member 7 with the shift input shaft 31 toward the second side L2 in the axial direction.

In this example, a plurality of spline grooves extending in the axial direction L are formed dispersed in the circumferential direction on the inner peripheral portion of the second inner friction member 551. On the other hand, similar spline grooves are dispersed in the circumferential direction on the outer peripheral portion of the third friction material support portion 71. Then, by engaging the spline grooves with each other, the second inner friction material 551 is supported from the radial inner side R1 by the third friction material support portion 71. In this way, the second inner friction material 551 is slidably supported in the axial direction L in a state where the relative rotation is restricted with respect to the third friction material support portion 71.

The second piston portion 56 is configured to press the second friction member 55 with a pressure corresponding to the hydraulic pressure supplied to the second hydraulic oil chamber 57. In the present embodiment, the second piston portion 56 has a second sliding portion 561 and a second pressing portion 562.

The second sliding portion 561 is configured to slide inside the cylinder portion formed by the cylinder forming portion 513 included in the rotary housing 51. The second sliding portion 561 is formed in the shape of an annular plate extending along the radial direction R and the circumferential direction.

The cylinder forming portion 513 has an outer peripheral portion 514, an inner peripheral portion 515, and a connecting portion 516. The outer peripheral portion 514 is formed in a cylindrical shape having an axial center along the axial direction L. The inner peripheral portion 515 is formed in a cylindrical shape having an axial center along the axial direction L. The inner peripheral portion 515 is arranged radially inside R1 with respect to the outer peripheral portion 514. The connecting portion 516 is formed so as to extend along the radial direction R. The connecting portion 516 is formed so as to connect the outer peripheral portion 514 and the inner peripheral portion 515. In the illustrated example, the outer peripheral portion 514 is formed so as to extend from the end portion of the radial outer side R2 of the connecting portion 516 toward the first side L1 in the axial direction. The inner peripheral portion 515 is formed so as to extend from the end portion of the radial inner R1 of the connecting portion 516 toward the first side L1 in the axial direction. The outer peripheral portion 514, the inner peripheral portion 515, and the connecting portion 516 formed in this way form a cylinder portion on which the second sliding portion 561 slides.

The second pressing portion 562 presses the second friction member 55 in the axial direction L. In the present embodiment, the second pressing portion 562 is arranged adjacent to the second side L2 in the axial direction with respect to the second friction member 55. In the illustrated example, the second pressing portion 562 is formed so as to project from the portion of the radial outer side R2 of the second sliding portion 561 to the first side L1 in the axial direction.

The second hydraulic oil chamber 57 is arranged adjacent to the second piston portion 56 in the axial direction L. In the present embodiment, the second hydraulic oil chamber 57 is formed by a second sliding portion 561, an outer peripheral portion 514, an inner peripheral portion 515, and a connecting portion 516.

In the present embodiment, the second sliding portion 561 of the second piston portion 56 is urged toward the first side L1 in the axial direction by a plurality of urging members 58 dispersed and arranged in the circumferential direction. .. When the hydraulic pressure supplied to the second hydraulic oil chamber 57 is less than a predetermined value, the urging member 58 is first axially separated from the second friction member 55 by the urging force. Move to the side L1. As a result, the lockup clutch 54 can be properly released, and it is possible to prevent the lockup clutch 54 from being unintentionally engaged due to centrifugal oil pressure or the like. As the urging member 58, for example, a compression coil spring can be adopted.

Further, in the present embodiment, among the plurality of second outer friction materials 552, each of the pair of second outer friction materials 552 adjacent to each other in the axial direction L has an annular shape extending along the circumferential direction. A second elastic body 59 that is formed and has elasticity in the axial direction L is arranged. When the hydraulic pressure supplied to the second hydraulic oil chamber 57 is less than a predetermined value, the second elastic body 59 causes the adjacent second outer friction members 552 to be separated from each other in the axial direction L by the elastic force. As a result, the lockup clutch 54 can be properly released, the drag torque between the friction materials can be reduced, and the lockup clutch 54 can be prevented from being unintentionally engaged due to centrifugal hydraulic pressure or the like. can do. As the second elastic body 59, for example, a wave spring can be adopted.

In the present embodiment, the lockup clutch 54 is radially inner R1 with respect to the disengagement engagement device 6, and is located at a position overlapping the disengagement engagement device 6 in a radial direction along the radial direction R. Have been placed. In the illustrated example, the second friction member 55 of the lockup clutch 54 is the radial inner side R1 with respect to the first friction member 61 of the disengagement engaging device 6, and is seen in the radial direction along the radial direction R. It is arranged at a position overlapping with the first friction member 61. As described above, the second friction material support portion 512 supports the first inner friction material 611 of the first friction member 61 from the radial inner side R1, and the second outer friction material of the second friction member 55. It is realized by supporting the 552 from the radial outer side R2.

Further, in the present embodiment, the first piston portion 62 and the second hydraulic oil chamber 57 are arranged so as to overlap each other in the radial direction along the radial direction R. Further, in the present embodiment, both the disengagement engaging device 6 and the lockup clutch 54 are radially inner R1 with respect to the rotor Ro of the rotary electric machine MG, and overlap with the rotor Ro in the radial direction. Is located in.

As described above, in the present embodiment, the second engaging device CL2 (here, the lockup clutch 54) for disconnecting and connecting the power transmission between the rotary electric machine MG and the transmission 3 is further provided.
The second engaging device CL2 is supplied with oil for operating the second friction member 55, the second piston portion 56 that presses the second friction member 55 in the axial direction L, and the second piston portion 56. With a second hydraulic oil chamber 57,
The second engaging device CL2 is radially inner R1 with respect to the first engaging device CL1 (here, the disengagement engaging device 6), and is the first engaging device in the radial direction along the radial direction R. It is placed at a position that overlaps with the device CL1 and is located.
The first piston portion 62 and the second hydraulic oil chamber 57 are arranged so as to overlap each other in the radial direction.
Both the first engaging device CL1 and the second engaging device CL2 are radially inner R1 with respect to the rotor Ro, and are arranged at positions overlapping with the rotor Ro in the radial direction.

According to this configuration, the dimension of the axial direction L of the vehicle drive device 100 is smaller than the configuration in which the second engaging device CL2 is arranged on one side of the axial direction L with respect to the first engaging device CL1. It can be suppressed.

Further, in the present embodiment, both the first engaging device CL1 (here, the disengagement engaging device 6) and the second engaging device CL2 (here, the lockup clutch 54) are attached to the rotary electric machine MG. It is the inner diameter R1 in the radial direction, and is arranged at a position overlapping with the rotary electric machine MG in the radial direction along the radial direction R.

According to this configuration, as compared with the configuration in which at least one of the first engaging device CL1 and the second engaging device CL2 is arranged on one side of the axial direction L with respect to the rotary electric machine MG, the vehicle drive device 100 The dimension of the axial direction L can be kept small.

In this example, the first engaging device CL1 (here, the disengagement engaging device 6) and the second engaging device CL2 (here, the lockup clutch 54) are rotors in a radial direction along the radial direction R. It is placed at a position that overlaps with Ro. In the illustrated example, the entire first engaging device CL1 and the entire second engaging device CL2 are arranged so as to overlap the rotor Ro in the radial direction.

According to this configuration, the shaft of the vehicle drive device 100 is compared with the configuration in which at least one of the first engaging device CL1 and the second engaging device CL2 is arranged on one side of the axial direction L with respect to the rotor Ro. The dimension of the direction L can be kept small.

2. 2. Second Embodiment Hereinafter, the vehicle drive device 100 according to the second embodiment will be described with reference to the drawings. This embodiment is different from the first embodiment in that it does not include the fourth bearing B4 and the elastic member 10, but includes the fixing member 20 and the guide member 30. Further, in the present embodiment, the support structure of the rotor Ro is different from that of the first embodiment. Hereinafter, the differences from the first embodiment will be mainly described. The points not particularly described are the same as those in the first embodiment.

As shown in FIG. 4, in the present embodiment, the fixing member 20 is provided instead of the fourth bearing B4 and the elastic member 10. The fixing member 20 is a member that regulates the movement of the second bearing B2 in the axial direction L. In the present embodiment, the fixing member 20 restricts the second bearing B2 from moving relative to the tubular support portion 411 of the first support 41 in the case 4 in the axial direction L. In the illustrated example, the fixing member 20 is a snap ring formed in an annular shape and fitted in a groove formed in each of the inner peripheral surface of the second bearing B2 and the outer peripheral surface of the cylindrical support portion 411. ..

As described above, in the present embodiment, the fixing member 20 restricts the relative movement of the second bearing B2 with respect to the tubular support portion 411 of the first support 41 in the axial direction L. Therefore, expansion (so-called bearing) of the rotary housing 51 due to the hydraulic pressure inside the rotary housing 51 causes a change in the axial L dimension of the rotary housing 51, and the first support 41 of the case 4 is a shaft. The second bearing B2 is difficult to come off from the tubular support portion 411 even when the bearing is deformed so as to be displaced in the direction L.

In the present embodiment, the rotary housing 51 does not include the cylindrical portion 511, and the rotor support member 9 is connected to the rotary housing 51 so as to rotate integrally with the rotary housing 51. The rotor support member 9 is a member that supports the rotor Ro from the radial inner side R1. In this embodiment, the rotor support member 9 functions as the second rotating member RT2. As shown in FIG. 5, in the present embodiment, the rotor support member 9 includes an outer peripheral side support portion 91, an inner peripheral side support portion 92, and a fixing portion 93.

The outer peripheral side support portion 91 is formed in a cylindrical shape having an axial center along the axial direction L. In the present embodiment, the rotor support surface 51b is formed on the outer peripheral surface of the outer peripheral side support portion 91. A support inner peripheral surface 51a is formed on the inner peripheral surface of the outer peripheral side support portion 91. Therefore, in the present embodiment, a part of the outer peripheral side support portion 91 forms a surface of the second rotating member RT2 (here, the rotor support member 9) in contact with the first bearing B1, the second support portion SP2. Functions as.

The inner peripheral side support portion 92 is formed in a cylindrical shape having an axial center along the axial direction L. The inner peripheral side support portion 92 is arranged on the inner side R1 in the radial direction with respect to the outer peripheral side support portion 91. In the present embodiment, the second friction material support portion 512 does not support the first inner friction material 611, and the inner peripheral side support portion 92 supports the first inner friction material 611 from the radial inner side R1. In this example, a plurality of spline grooves engaging with a plurality of spline grooves formed in the inner peripheral portion of the first inner friction material 611 extend in the axial direction L on the outer peripheral portion of the inner peripheral side support portion 92. It is also dispersed in the circumferential direction. Then, the spline groove of the first inner friction material 611 and the spline groove of the inner peripheral side support portion 92 are engaged with each other, so that the first inner friction material 611 rotates relative to the inner peripheral side support portion 92. In a regulated state, it is slidably supported in the axial direction L. In the present embodiment, the second friction material support portion 512 is formed so as to extend from the turbine accommodating portion 520 of the rotary housing 51 to the second side L2 in the axial direction. The second friction material support portion 512 is connected to the turbine accommodating portion 520 so as to rotate integrally. In this example, the turbine accommodating portion 520 extends to the radial inner R1 with respect to the first friction member 61 of the disengagement engaging device 6, and the end portion of the radial inner R1 of the turbine accommodating portion 520 and the end portion thereof. The end of the second friction material support portion 512 on the first side L1 in the axial direction is connected by welding.

The fixed portion 93 is connected to the turbine accommodating portion 520 so as to rotate integrally. In the illustrated example, the fixed portion 93 is connected to the turbine accommodating portion 520 by a rivet in a state of being in contact with the turbine accommodating portion 520 from the second side L2 in the axial direction. The fixed portion 93 extends along the radial direction R so as to connect the outer peripheral side support portion 91 and the inner peripheral side support portion 92. In the present embodiment, the fixing portion 93 is formed so as to connect the end of the axial first side L1 of the outer peripheral side support portion 91 and the end of the axial first side L1 of the inner peripheral side support portion 92. Has been done.

In the present embodiment, the oil passage P1 is formed between the inner peripheral side support portion 92 and the second friction material support portion 512 in the radial direction R. In this example, a plurality of spline grooves engaging with a plurality of spline grooves formed on the outer peripheral portion of the second friction material support portion 512 extend in the axial direction L on the inner peripheral portion of the inner peripheral side support portion 92. It is also dispersed in the circumferential direction. An oil passage P1 is formed between the spline groove of the second friction material support portion 512 and the spline groove of the inner peripheral side support portion 92. Although not shown, in the present embodiment, the through hole P2 penetrating the inner peripheral side support portion 92 in the radial direction R is formed so as to communicate with the oil passage P1. As a result, the oil supplied to the oil passage P1 flows through the through hole P2 of the inner peripheral side support portion 92 to the first friction member 61 of the disengagement engaging device 6. Therefore, the first friction member 61 can be appropriately lubricated.

Further, in the present embodiment, the guide member 30 for guiding the oil is provided in the oil passage P1. In the present embodiment, the guide member 30 is formed in a cylindrical shape having an axial center along the axial direction L so as to extend from the first piston portion 62 toward the oil passage P1. In the illustrated example, the guide member 30 is in contact with the portion extending along the axial direction L of the first sliding portion 621 of the first piston portion 62 from the radial inner side R1 in a state of being in contact with the first sliding portion 30. It is connected to the portion 621 so as to rotate integrally. In the present embodiment, as the speed change input shaft 31 formed in a cylindrical shape having an axial center along the axial direction L rotates, the rotary housing 51 is passed from the inside of the speed change input shaft 31 through the radial communication hole P3. Oil is supplied between the cylinder forming portion 513 of the above and the connecting portion 13 of the input member 1 and the first piston portion 62. Then, oil flows radially outward R2 between the cylinder forming portion 513, the connecting portion 13, and the first piston portion 62, and reaches the guide member 30. The oil that has reached the guide member 30 flows along the inner peripheral surface of the guide member 30 to the first side L1 in the axial direction, and is between the inner peripheral side support portion 92 and the second friction material support portion 512 in the radial direction R. It is supplied to the oil passage P1 formed in.

Although illustration and description are omitted in the first embodiment, as shown in FIG. 4, the vehicle drive device 100 includes a rotation sensor 8 for detecting the rotation of the rotor Ro of the rotary electric machine MG. In the present embodiment, the rotation sensor 8 includes a fixed body 81 and a rotating body 82.

The fixed body 81 is fixed to the case 4. In this embodiment, the fixed body 81 is supported by the second support 42 of the case 4. The rotating body 82 is connected to the rotor Ro or a member that rotates integrally with the rotor Ro so as to rotate integrally. In the present embodiment, the rotating body 82 is connected to the rotating housing 51 so as to rotate integrally.

In the present embodiment, the rotating body 82 is formed in the shape of an annular plate, and a plurality of teeth are dispersedly arranged in the circumferential direction. Then, the fixed body 81 targets a plurality of teeth in the rotating body 82 as a detection target, and outputs a signal based on the detection target. In the illustrated example, a plurality of teeth are formed on the inner peripheral portion of the rotating body 82. The outer peripheral portion of the rotating body 82 is supported by the pump accommodating portion 519 of the rotating housing 51. Further, in the illustrated example, the pump accommodating portion 519 has a shape bulging toward the first side L1 in the axial direction with respect to the radial extending portion 518, and is radially inner R1 with respect to the pump accommodating portion 519. The rotating body 82 is arranged at a position overlapping the pump accommodating portion 519 in the radial direction along the radial direction R. The fixed body 81 is arranged so as to face the rotating body 82 from the first side L1 in the axial direction.

In this example, the rotation sensor 8 uses an inductive sensor (inductive proximity sensor). The type of the rotation sensor 8 is not limited to the above, and can be configured by using various sensors such as a resolver, a Hall element sensor, an encoder, and a magnetic rotation sensor.

3. 3. Other Embodiment (1) In the first embodiment, a seal is provided between the cylindrical support portion 411 of the first support 41 in the case 4 and the inner tubular portion 12 of the input member 1 in the radial direction R. The configuration in which the member S is arranged has been described as an example. The size between the cylindrical support portion 411 on which the seal member S is arranged and the inner tubular portion 12 in the radial direction R is not particularly limited. For example, as shown in FIG. 6, the radial distance between the cylindrical support portion 411 and the inner tubular portion 12 may be larger than that of the first embodiment. In this case, as the seal member S, a member having a larger thickness (difference between the outer diameter and the inner diameter) in the radial direction R than that of the first embodiment is used. In the example shown in FIG. 6, the seal member S is arranged so as to overlap the second bearing B2 in the radial direction.

(2) In the above embodiment, an example is a configuration in which the first radial support surface 13a is formed so as to face the radial inner R1 and the second radial support surface 41a is formed so as to face the radial outer R2. Explained as. However, without being limited to such a configuration, the first radial support surface 13a is formed so as to face the radial outer side R2, and the second radial support surface 41a is formed so as to face the radial inner R1. You may be.

(3) In the above embodiment, the configuration in which the first bearing B1 and the second bearing B2 are arranged so as to overlap each other in the radial direction along the radial direction R has been described as an example. However, without being limited to such a configuration, the first bearing B1 may be arranged on one side of the axial direction L with respect to the second bearing B2.

(4) In the above embodiment, the input member 1 includes an outer cylindrical portion 11, an inner tubular portion 12, and a connecting portion 13, and a support outer peripheral surface 11a is formed on the outer tubular portion 11 to form an inner tubular portion. A configuration in which the outer peripheral surface 12a for sealing is formed on the 12 and the first radial support surface 13a is formed on the connecting portion 13 has been described as an example. However, the present invention is not limited to such a configuration, and for example, the input member 1 may not have the outer cylindrical portion 11 and the support outer peripheral surface 11a may be formed on the connecting portion 13.

(5) In the above embodiment, the first support 41 of the case 4 includes a tubular support portion 411 and a radial extension portion 412, and the tubular support portion 411 has a second radial support surface 41a and a seal. The configuration in which both of the inner peripheral surfaces 41b are formed has been described as an example. However, without being limited to such a configuration, for example, the first support 41 further includes a tubular inner tubular support portion arranged radially inside R1 with respect to the tubular support portion 411. The inner peripheral surface 41b for sealing may be formed on the inner cylindrical support portion, and the second radial support surface 41a may be formed on the tubular support portion 411.

(6) In the second embodiment, the configuration in which the rotor support member 9 functioning as the second rotating member RT2 is connected so as to rotate integrally with the rotating housing 51 of the fluid coupling 5 has been described as an example. However, the present invention is not limited to such a configuration, and for example, the rotor support member 9 may be driven and connected to the speed change input shaft 31 via the second engaging device CL2 without providing the fluid coupling 5. good.

(7) In the above embodiment, at least one of the first piston portion 62 and the first hydraulic oil chamber 63 of the disengagement engaging device 6 is between the first bearing B1 and the second bearing B2 in the radial direction R. Therefore, a configuration in which the bearings are arranged at positions overlapping with at least one of the first bearing B1 and the second bearing B2 in the radial direction along the radial direction R has been described as an example. However, without being limited to such a configuration, both the first piston portion 62 and the first hydraulic oil chamber 63 are arranged so as not to overlap with both the first bearing B1 and the second bearing B2 in the radial direction. You may have.

(8) In the above embodiment, the first piston portion 62 of the disengagement engaging device 6 is between the first bearing B1 and the second bearing B2 in the radial direction R and has a diameter along the radial direction R. An example of a configuration in which the bearings are arranged at positions overlapping with at least one of the first bearing B1 and the second bearing B2 in a directional view has been described. However, without being limited to such a configuration, the first piston portion 62 may be arranged so as not to overlap with both the first bearing B1 and the second bearing B2 in the radial direction.

(9) In the above embodiment, the lockup clutch 54 as the second engaging device CL2 is radially inner R1 with respect to the disengagement engaging device 6 as the first engaging device CL1 and has a diameter. An example of a configuration is described in which the configuration is arranged at a position overlapping with the disengagement engaging device 6 in a radial view along the direction R. However, the configuration is not limited to such a configuration, and the second engaging device CL2 may be arranged on one side of the axial direction L with respect to the first engaging device CL1.

(10) In the above embodiment, both the disengagement engaging device 6 as the first engaging device CL1 and the lockup clutch 54 as the second engaging device CL2 are relative to the rotor Ro of the rotary electric machine MG. A configuration in which the radial inner side R1 is arranged at a position overlapping the rotor Ro in the radial view along the radial direction R has been described as an example. However, without being limited to such a configuration, for example, only one of the first engaging device CL1 and the second engaging device CL2 is arranged at a position overlapping with the rotor Ro in the radial direction. Is also good. Further, both the first engaging device CL1 and the second engaging device CL2 may be arranged so as not to overlap with the rotor Ro but to overlap with the stator St in the radial direction along the radial direction R. Alternatively, both the first engaging device CL1 and the second engaging device CL2 may be arranged so as not to overlap with the rotary electric machine MG in the radial view along the radial direction R.

(11) In the above embodiment, both the first bearing B1 and the second bearing B2 are radially inner R1 with respect to the rotor Ro of the rotary electric machine MG, and the rotor Ro is viewed in the radial direction along the radial direction R. The configuration arranged at the position overlapping with the above is described as an example. However, without being limited to such a configuration, for example, only the first bearing B1 is arranged at a position overlapping the rotor Ro in the radial direction, and the second bearing B2 does not overlap the rotor Ro in the radial direction. It may be arranged at a position. In this case, the second bearing B2 may be arranged so as not to overlap with the rotor Ro in the radial direction but to overlap with the stator St. Alternatively, the second bearing B2 may be arranged so as not to overlap with the rotary electric machine MG in the radial direction.

(12) The configurations disclosed in each of the above-described embodiments can be applied in combination with the configurations disclosed in other embodiments as long as there is no contradiction. With respect to other configurations as well, the embodiments disclosed herein are merely exemplary in all respects. Therefore, various modifications can be appropriately made without departing from the spirit of the present disclosure.

The technology according to the present disclosure is an input member that is driven and connected to an internal combustion engine, an output member that is driven and connected to wheels, a rotary electric machine that functions as a driving force source for wheels, and rotation transmitted from the side of the rotary electric machine. It can be used for a vehicle drive device including a transmission that shifts and transmits to the output member side, and a case that accommodates a rotary electric machine and a transmission.

100: Vehicle drive device, 1: Input member, 11a: Support outer peripheral surface, 13a: First radial support surface, 2: Output member, 3: Transmission, 4: Case, 41: First support (support body) ), 41a: 2nd radial support surface, 51a: support inner peripheral surface, RT1: 1st rotating member, RT2: 2nd rotating member, B1: 1st bearing, B2: 2nd bearing, MG: rotary electric machine, Ro : Rotor, EG: Internal engine, W: Wheel, R: Radial direction, R1: Radial direction inside, R2: Radial direction outside

Claims (10)

The input member that is driven and connected to the internal combustion engine and
The output member that is driven and connected to the wheel,
A rotary electric machine equipped with a rotor and functioning as a driving force source for the wheels,
A transmission that shifts the rotation transmitted from the rotary electric machine side and transmits it to the output member side.
A case for accommodating the rotary electric machine and the transmission is provided.
The input member or a member that rotates integrally with the input member is used as a first rotating member, and the rotor or a member that rotates integrally with the rotor is used as a second rotating member.
A first bearing that supports the second rotating member with respect to the first rotating member so that the second rotating member rotates relative to the first rotating member.
A second bearing that supports the first rotating member with respect to the case is provided so that the first rotating member rotates relative to the case.
The case comprises a support for supporting the second bearing.
The first rotating member includes a support outer peripheral surface facing outward in the radial direction and a first radial support surface facing one side in the radial direction.
The second rotating member includes a support inner peripheral surface facing inward in the radial direction.
The support includes a second radial support surface that is radially opposed to the first radial support surface.
The first bearing is arranged between the support outer peripheral surface and the support inner peripheral surface in the radial direction.
The second bearing is arranged between the first radial support surface and the second radial support surface in the radial direction.
A vehicle drive device in which the first bearing is arranged inside the rotor in the radial direction and at a position overlapping the rotor in the radial direction along the radial direction. The vehicle drive device according to claim 1, wherein the first bearing and the second bearing are arranged so as to overlap each other in the radial direction. Further, a first engaging device for disconnecting and connecting the power transmission between the input member and the rotary electric machine is provided.
The first engaging device includes a first friction member, a first piston portion that presses the first friction member in the axial direction, and a first hydraulic oil chamber to which operating oil for the first piston portion is supplied. And, with
At least one of the first piston portion and the first hydraulic oil chamber is between the first bearing and the second bearing in the radial direction, and with at least one of the first bearing and the second bearing. The vehicle drive device according to claim 1 or 2, which is arranged at overlapping positions in the radial view. Further, a second engaging device for connecting and disconnecting the power transmission between the rotary electric machine and the transmission is provided.
The second engaging device is supplied with a second friction member, a second piston portion that presses the second friction member in the axial direction, and a second hydraulic oil for operating the second piston portion. With a room,
The second engaging device is arranged at a position inside the radial direction with respect to the first engaging device and overlapping the first engaging device in the radial direction.
The first piston portion and the second hydraulic oil chamber are arranged so as to overlap each other in the radial direction.
Claimed that both the first engaging device and the second engaging device are arranged in the radial direction with respect to the rotor and at positions overlapping with the rotor in the radial direction. 3. The vehicle drive device according to 3. Further provided with a fluid coupling arranged in the power transmission path between the rotary machine and the transmission.
The fluid coupling comprises a rotating housing that rotates integrally with the rotor, and a lockup clutch that is the second engaging device.
The vehicle drive device according to claim 4, wherein the second rotating member is the rotating housing or a member that rotates integrally with the rotating housing. The first radial support surface is formed so as to face the inside of the radial direction.
The vehicle drive device according to any one of claims 1 to 5, wherein the second radial support surface is formed so as to face the outer side in the radial direction. Further, a sealing member for oil-tightly sealing between the first rotating member and the support is provided.
The first rotating member includes an outer peripheral surface for sealing that faces outward in the radial direction.
The support comprises an inner peripheral surface for sealing that faces inward in the radial direction.
The vehicle drive device according to any one of claims 1 to 6, wherein the seal member is arranged between the outer peripheral surface for the seal and the inner peripheral surface for the seal in the radial direction. The portion of the first rotating member that forms a surface in contact with the first bearing is a first support portion, and the portion of the second rotating member that forms a surface in contact with the first bearing is a second support portion. The portion of the one rotating member that forms a surface in contact with the second bearing is designated as the third support portion, and the portion of the support that forms the surface in contact with the second bearing is designated as the fourth support portion.
The seal member overlaps with at least one of the first bearing, the second bearing, the first support portion, the second support portion, the third support portion, and the fourth support portion in the radial view. The vehicle drive device according to claim 7, which is arranged so as to be used. The first rotating member is formed into a cylindrical portion having an axial center along the axial direction and a cylindrical portion having an axial center along the axial direction, and is more than the outer tubular portion. It is provided with an inner cylindrical portion arranged inside in the radial direction and a connecting portion extending along the radial direction to connect the outer tubular portion and the inner tubular portion.
The support outer peripheral surface is formed on the outer peripheral surface of the outer tubular portion.
The outer peripheral surface for sealing is formed on the outer peripheral surface of the inner tubular portion.
The connection portion has a stepped surface facing inward in the radial direction.
The vehicle drive device according to claim 7 or 8, wherein the stepped surface is the first radial support surface. The support includes a cylindrical support portion formed in a cylindrical shape having an axial center along the axial direction, and a radial extension portion extending outward from the tubular support portion in the radial direction. Equipped with
The second radial support surface is formed on the outer peripheral surface of the tubular support portion.
The inner peripheral surface for sealing is formed on the inner peripheral surface of the tubular support portion, and the inner peripheral surface for sealing is formed.
The vehicle drive device according to claim 9, wherein the radial extending portion and the connecting portion are arranged side by side in the axial direction.

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