JP2020121634A - Vehicle driving device - Google Patents

Abstract

To realize a vehicle driving device which can properly supply oil for lubrication to a support bearing which supports an input member in a manner that the input member can rotate relative to a case while achieving downsizing of the entire device in a radial direction and an axial direction.SOLUTION: A rotor support member 30 includes an engagement part 34 which engages with an outer peripheral surface of a gear change input member 20. The engagement part 34 is restricted from moving to the first axial side L1 relative to the gear speed input member 20 by a fastening member 40. The gear change input member 20 includes a second oil passage 72 allowing communication between a first oil passage 71 provided at a case 50 and an interior of a first cylindrical part 21. The fastening member 40 includes a third oil passage 73 which penetrates through the fastening member 40 in an axial direction L and allows communication between the interior and an exterior of the first cylindrical part 21. An input member 10 includes a fourth oil passage 74 which supplies oil discharged to the outside of the first cylindrical part 21 from the third oil passage 73 to a support bearing B1.SELECTED DRAWING: Figure 3

Description

The present invention relates to a power transmission path connecting an input member drivingly connected to an internal combustion engine and an output member drivingly connected to a wheel, in order from the input member side, a rotating electric machine, a shift input member, and a shift input member. The present invention relates to a vehicle drive device including a transmission that changes speed and transmits the rotation to the output member side.

An example of the vehicle drive device as described above is disclosed in JP-A-2017-177884 (Patent Document 1). The reference numerals in parentheses in the description of the background art are those of Patent Document 1 below. In the vehicle drive device of Patent Document 1, as shown in FIG. 1 and FIG. 2 of the document, the torque converter (TC) and the speed change mechanism (TM) allow the first connecting member ( The transmission is configured to change the speed of the rotation of (91) and transmit the rotation to the output member (O) side. In this vehicle drive device, the rotor support member (22) included in the rotary electric machine (MG) and the first connecting member (91) are connected via the second connecting member (92). Specifically, the second connecting member (92) is spline-fitted to the outer peripheral surface of the first connecting member (91) on one side in the axial direction (L), and is bolted to the first connecting member (91). ) Is fixed so that it cannot move in the axial direction (L). The second connecting member (92) is connected to the rotor supporting member (22) on the other side in the axial direction (L) so as to rotate integrally with the rotor supporting member (22) so as to be relatively movable in the axial direction. There is.

JP, 2017-177884, A

Although not specified in Patent Document 1, from FIGS. 2 and 3 of Patent Document 1, in the vehicle drive device described in Patent Document 1, the oil inside the cylindrical part of the input member is It is understood that the oil for lubrication is supplied to the support bearing that rotatably supports the input member with respect to the case by discharging the input member radially outward from the through hole formed in the case. Further, in this vehicle drive device, in the connecting member (the above-described second connecting member) that connects the rotor support member and the speed change input member, the axial direction with respect to the bolt for fixing the connecting member and the speed change input member. By forming a through hole in the portion on the side of the input member and supplying the oil in the oil passage provided in the case from the through hole to the inside of the input member via the inside of the connecting member, the oil is supplied to the support bearing. It is understood that the oil passage for supplying the oil is formed avoiding the bolt.

As described above, in the vehicle drive device described in Patent Document 1, the oil passage for supplying oil to the support bearing is formed by using the connecting member. However, the connecting member is the rotor supporting member in the radial direction. And the shift input member, the entire device may become larger in the radial direction than when the connecting member is not provided. Considering the mountability of the vehicle drive device on the vehicle, it is desirable that the size of the vehicle drive device be kept small not only in the radial direction but also in the axial direction.

Therefore, a vehicle drive capable of appropriately supplying oil for lubrication to a support bearing that rotatably supports an input member with respect to a case while achieving downsizing of the entire device in a radial direction and an axial direction. Realization of the device is desired.

A vehicle drive device according to the present disclosure includes, in order from the input member side, a rotary electric machine and a gear shift input in a power transmission path that connects an input member that is drive-connected to an internal combustion engine and an output member that is drive-connected to a wheel. A drive device for a vehicle, comprising: a member; and a transmission that shifts the rotation of the shift input member and transmits the rotation to the output member side, wherein the input member, the rotating electric machine, and the shift input member are The shift input member is coaxially disposed, the shift input member is rotatably supported with respect to the case, and the input member is disposed on the axial first side that is one side in the axial direction with respect to the shift input member. The rotor is rotatably supported with respect to the case via a support bearing, and the rotary electric machine includes a rotor and a rotor support member that supports the rotor from the inside in the radial direction. The shift input member includes an engaging portion that engages with an outer peripheral surface of the shift input member, and the shift input member includes a first tubular portion formed in a tubular shape extending in the axial direction at a portion on the first side in the axial direction. The engagement portion is restricted from moving toward the axial first side with respect to the shift input member by a fastening member that is screwed onto the inner peripheral surface of the first tubular portion from the axial first side. The shift input member includes a second oil passage that communicates a first oil passage provided in the case with an inside of the first tubular portion, and the fastening member includes the fastening member in the axial direction. And a third oil passage that communicates the inside and the outside of the first tubular portion with each other, and the input member collects the oil discharged from the third oil passage to the outside of the first tubular portion. A fourth oil passage is provided to supply to the support bearing.

According to this structure, since the rotor support member includes the engaging portion that engages with the outer peripheral surface of the gear shift input member, the rotor support member and the gear shift input member can be directly connected. Therefore, as compared with the case where the rotor support member and the shift input member are connected via another member arranged between these two members in the radial direction, the size of the entire device in the radial direction can be reduced. it can.
And in the above-mentioned composition, the support bearing which makes the oil of the 1st oilway circulate through the 2nd oilway, the 3rd oilway, and the 4th oilway in order, and supports an input member rotatably to a case. Can be supplied to. Here, since the third oil passage is formed so as to penetrate the fastening member in the axial direction, even if the fastening member restricts the movement of the engagement portion to the first side in the axial direction with respect to the shift input member, the fastening is performed. An oil passage for supplying oil to the support bearing can be formed by using the first tubular portion having the inner peripheral surface on which the member is screwed.
Even in the configuration in which the movement of the engaging portion toward the first axial direction side with respect to the shift input member is restricted by the fastening member, for example, the entire fastening member is arranged on the first axial side with respect to the support bearing. The first tubular portion is formed to be long in the axial direction, and the oil inside the first tubular portion is discharged from a through hole formed so as to penetrate the first tubular portion in the radial direction to form a support bearing. Can be supplied to. However, in this case, since the first tubular portion becomes longer in the axial direction, the entire device tends to be larger in the axial direction. On the other hand, according to the above configuration, by forming the third oil passage by penetrating the fastening member in the axial direction, it is possible to prevent the first tubular portion from being elongated in the axial direction, while supporting the bearing. It is possible to form an oil passage for supplying oil to the.
As described above, according to the above configuration, while the size of the entire apparatus is reduced in the radial direction and the axial direction, the support bearing that rotatably supports the input member is appropriately provided with oil for lubrication. Can be supplied to.

Further features and advantages of the vehicle drive device will be apparent from the following description of the embodiments described with reference to the drawings.

Schematic diagram showing a schematic configuration of a vehicle drive device Sectional drawing which simplifies and shows a part of vehicle drive device. A partially enlarged view of FIG.

An embodiment of a vehicle drive device will be described with reference to the drawings. In the following description, the “axial direction L”, the “radial direction R”, and the “circumferential direction” refer to the rotational axis A of the input member 10 (FIG. 2, FIG. 2) described below, unless otherwise specified. 3)) as a standard. The input member 10 and the rotating member arranged coaxially with the input member 10 rotate around the rotation axis A. Then, one side of the axial direction L is referred to as the “axial first side L1”, and the other side of the axial direction L (opposite to the axial first side L1 in the axial direction L) is referred to as the “axial second side L2”. And Further, the outside in the radial direction R is referred to as “radial outside R1” and the inside in the radial direction R is referred to as “radial inside R2”. The directions of the respective members in the following description represent the directions when they are assembled to the vehicle drive device 1. It should be noted that the terms relating to the dimensions, arrangement directions, arrangement positions, etc., of the respective members are concepts including a state having a difference due to an error (error that can be tolerated in manufacturing).

In the present specification, “drive connection” refers to a state in which two rotating elements are connected so as to be able to transmit a driving force (synonymous with torque), and the two rotating elements are connected so as to rotate integrally. Or a state in which the two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members. Examples of such a transmission member include various members (for example, a shaft, a gear mechanism, a belt, a chain, etc.) that transmit rotation at the same speed or at a changed speed. The transmission member may include an engagement device (for example, a friction engagement device, a meshing engagement device, etc.) that selectively transmits rotation and driving force.

Further, in the present specification, the “rotary electric machine” is used as a concept including both a motor (electric motor), a generator (generator), and a motor/generator that performs both functions of the motor and the generator as necessary. There is. Further, in the present specification, regarding the arrangement of the two members, “overlap in a specific direction view” means that when a virtual straight line parallel to the line-of-sight direction is moved in each direction orthogonal to the virtual straight line, This means that the region where the virtual straight line intersects with both of the two members exists in at least a part.

As shown in FIG. 1, the vehicle drive device 1 includes a power transmission path connecting an input member 10 drivingly connected to the internal combustion engine 2 and an output member 19 drivingly connected to the wheels 3 from the input member 10 side. The rotary electric machine 5, the shift input member 20, and the transmission 4 that shifts the rotation of the shift input member 20 and transmits the rotation to the output member 19 side are provided in order. The input member 10, the rotary electric machine 5, and the shift input member 20 are arranged coaxially. The vehicle drive device 1 further includes a case 50. The vehicle drive device 1 transmits the output torque of one or both of the internal combustion engine 2 and the rotary electric machine 5 to the wheels 3 via the output member 19 to drive the vehicle (the vehicle on which the vehicle drive device 1 is mounted). Let it run. In the present embodiment, the output member 19 is connected to the two left and right wheels 3 (here, the two left and right rear wheels) via the differential gear device 6 (output differential gear device), and is driven by the vehicle. The device 1 transmits the output torque of one or both of the internal combustion engine 2 and the rotary electric machine 5 to the two left and right wheels 3 to drive the vehicle.

The input member 10 is drivingly connected to an internal combustion engine output member 2a which is an output member (a crankshaft or the like) of the internal combustion engine 2. In the present embodiment, the input member 10 is connected to the internal combustion engine output member 2a via the damper 7. The input member 10 may be connected to the internal combustion engine output member 2a without the damper 7 (for example, the input member 10 is connected to rotate integrally with the internal combustion engine output member 2a). .. The internal combustion engine 2 is a prime mover (for example, a gasoline engine, a diesel engine, etc.) that is driven by combustion of fuel inside the engine to take out power.

The input member 10 is drivingly connected to the rotary electric machine 5. In the present embodiment, the vehicle drive device 1 includes the engagement device 60 in the power transmission path between the input member 10 and the rotary electric machine 5, and the input member 10 includes the rotary electric machine via the engagement device 60. It is connected to 5. The engagement device 60 selectively connects (ie, connects or disconnects) the input member 10 and the rotary electric machine 5 to each other in a state where the engagement device 60 is engaged (here, in a direct engagement state). The input member 10 and the rotary electric machine 5 rotate integrally.

As shown in FIG. 2, the engagement device 60 includes an inner support portion 63 that supports the first engagement member 61 of the engagement device 60 from the radially inner side R2. Further, the engagement device 60 includes an outer support portion 64 that supports the second engagement member 62 of the engagement device 60 from the radially outer side R1. The first engagement member 61 and the second engagement member 62 are arranged to be engageable with each other, and the torque by the engagement device 60 is in a state where the first engagement member 61 and the second engagement member 62 are engaged with each other. Is transmitted. In the present embodiment, the inner support portion 63 is connected so as to rotate integrally with the input member 10, and the outer support portion 64 is connected so as to rotate integrally with the rotary electric machine 5. Specifically, the outer support portion 64 is configured to rotate integrally with the rotor support member 30 described later. Here, the outer support portion 64 is integrally formed with a rotor support portion 33, which will be described later, included in the rotor support member 30. The outer supporting portion 64 may be configured by a member different from the rotor supporting member 30, and the outer supporting portion 64 may be connected (for example, spline connection) so as to rotate integrally with the rotor supporting member 30. In the present embodiment, the first engagement member 61 corresponds to the “engagement member”.

In the present embodiment, the engagement device 60 is a friction engagement device (here, a wet multi-plate clutch), and torque is generated by the friction force generated between the first engagement member 61 and the second engagement member 62. To communicate. Specifically, the first engagement member 61 is a friction plate movably supported in the axial direction L in a state where the relative rotation in the circumferential direction with respect to the inner side support portion 63 is restricted, and the second engagement member 61 The member 62 is a friction plate movably supported in the axial direction L in a state in which the relative rotation in the circumferential direction with respect to the outer support portion 64 is restricted. The first engagement member 61 and the second engagement member 62 are arranged such that their friction contact surfaces (end surfaces in the axial direction L) can contact each other in the axial direction L. The engagement device 60 includes a piston 65 that presses the first engagement member 61 and the second engagement member 62 in the axial direction L, and the piston 65 connects the first engagement member 61 and the second engagement member 62. By pressing in the axial direction L, the first engagement member 61 and the second engagement member 62 are engaged. In the present embodiment, the piston 65 is movably supported in the axial direction L in a state in which relative rotation in the circumferential direction with respect to the outer support portion 64 is restricted.

In the present embodiment, the engagement device 60 is a hydraulically driven engagement device that includes a hydraulic drive unit (here, a hydraulic servo mechanism) that operates according to the supplied hydraulic pressure. Specifically, as shown in FIG. 3, the engagement device 60 includes the piston 65, the first oil chamber H1 (operating hydraulic chamber) to which the hydraulic pressure for driving the piston 65 is supplied, and the piston 65. An urging member 66 (here, a coil spring) that urges in a direction opposite to the moving direction by hydraulic pressure is provided. In the present embodiment, the engagement device 60 is a normally open type engagement device, and the first oil chamber H1 is provided with respect to the piston 65 by the first engagement member 61 and the second engagement member 62 formed by the piston 65. Is provided on the side opposite to the pressing direction side. Here, the piston 65 is configured to press the first engaging member 61 and the second engaging member 62 from the axial second side L2, and the first oil chamber H1 is axially opposed to the piston 65. It is formed on the direction second side L2.

In the present embodiment, the engagement device 60 further includes a second oil chamber H2 (cancellation hydraulic chamber) that produces a hydraulic pressure that opposes the centrifugal hydraulic pressure generated in the first oil chamber H1. Specifically, the cancel plate 67 is provided on the side opposite to the first oil chamber H1 side with respect to the piston 65 (in the present embodiment, the axial first side L1), and the second oil chamber H2 is It is formed between the piston 65 and the cancel plate 67 in the axial direction L. The biasing member 66 is arranged in the second oil chamber H2. The second oil chamber H2 is radially inside R2 with respect to the first engaging member 61 and the second engaging member 62, and when viewed in the radial direction along the radial direction R, the first engaging member 61 and the second engaging chamber 61 It is arranged at a position overlapping with the engaging member 62.

As shown in FIG. 1, the rotary electric machine 5 includes a stator 5b fixed to the case 50 and a rotor 5a rotatably supported by the stator 5b. In the present embodiment, the rotary electric machine 5 is an inner rotor type rotary electric machine, and the rotor 5a is arranged at the radially inner side R2 with respect to the stator 5b and at a position overlapping the stator 5b in the radial direction. Further, in the present embodiment, the engagement device 60 is arranged at a position that is on the inner side R2 in the radial direction with respect to the rotor 5a and that overlaps with the rotor 5a in the radial direction. Note that, in FIG. 2, the detailed illustration of the rotary electric machine 5 is omitted, and the rotary electric machine 5 is shown in a simplified manner.

The rotary electric machine 5 is connected so as to rotate integrally with the shift input member 20. Specifically, the rotary electric machine 5 includes a rotor support member 30 that supports the rotor 5a from the radially inner side R2. The rotor 5 a is supported by the rotor support member 30 in a state in which movement in each direction is restricted with respect to the rotor support member 30. As shown in FIGS. 2 and 3, the rotor support member 30 includes an engagement portion 34 that engages with the outer peripheral surface of the shift input member 20. The engaging portion 34 is formed in a tubular shape (here, a cylindrical shape) extending in the axial direction L, and the engaging portion 34 is provided in the shift input member 20 (specifically, in the axial direction of the shift input member 20). It is fitted to the outer peripheral surface of a portion including the end portion of the first side L1). The engaging portion 34 is configured to be spline-engaged with the outer peripheral surface of the shift input member 20. That is, on the inner peripheral surface of the engagement portion 34, a plurality of inner teeth (inner peripheral spline teeth) that are formed so as to extend in the axial direction L and that are arranged along the peripheral direction are formed, and the outer periphery of the speed change input member 20. A plurality of external teeth (outer peripheral spline teeth) are formed on the surface (here, the outer peripheral surface of the first cylindrical portion 21 described later) so as to extend in the axial direction L and are arranged in the circumferential direction. The internal teeth and the external teeth are in spline engagement. Therefore, the rotor 5 a of the rotary electric machine 5 is connected to the gear shift input member 20 so as to rotate integrally with the rotor 5 a while being supported by the rotor support member 30.

As shown in FIG. 2, the rotor support member 30 is formed in a cylindrical shape extending in the axial direction L, and a rotor support portion 33 that supports the rotor 5a from the radially inner side R2, and is formed so as to extend in the radial direction R. The first support portion 31 that supports the rotor support portion 33 from the radially inner side R2. An engaging portion 34 is formed at the end of the first support portion 31 on the radially inner side R2. The first support portion 31 extends from the rotor support portion 33 to the radially inner side R2 between the engagement device 60 and the case 50 (specifically, the first wall portion 51 described later) in the axial direction L. It is arranged. As shown in FIG. 3, a first oil chamber H1 is formed between the first support portion 31 and the piston 65. In the present embodiment, the rotor support member 30 further includes a second support portion 32 that is formed to extend in the radial direction R and that supports the rotor support portion 33 from the radial inner side R2. The second support portion 32 extends from the rotor support portion 33 to the radially inner side R2 between the engagement device 60 and the case 50 (specifically, the second wall portion 52 described later) in the axial direction L. It is arranged.

The transmission 4 is configured such that the transmission ratio can be changed stepwise or steplessly, and the rotation of the transmission input member 20 is changed at the transmission ratio at the present time so that the transmission output member, which is an output member of the transmission 4, is changed. introduce. The shift output member is the output member 19 or a member drivingly connected to the output member 19, and in the present embodiment, the output member 19 is the shift output member. The transmission 4 includes a speed change mechanism (for example, an automatic stepped speed change mechanism or a continuously variable speed change mechanism) for changing the speed ratio. The transmission 4 may be configured to include a torque converter in addition to such a transmission mechanism. In this case, for example, the torque converter is arranged in the power transmission path between the speed change input member 20 and the speed change mechanism, and the speed change input member 20 is coupled so as to rotate integrally with the pump impeller of the torque converter. can do.

Next, the support structure of each member in the vehicle drive device 1 of the present embodiment with respect to the case 50 will be described. As shown in FIG. 2, the case 50 is arranged on the second side L2 in the axial direction with respect to the rotary electric machine 5, and is arranged on the first side L1 in the axial direction with respect to the rotary electric machine 5. And a second wall portion 52. Although illustration is omitted, the case 50 includes a peripheral wall portion that surrounds the rotary electric machine 5 from the radial outside R1, and the first wall portion 51 and the second wall portion in the case internal space formed by being surrounded by the peripheral wall portion. The rotary electric machine 5 is housed in the space between the shaft 52 and the axial direction L. In this embodiment, the engagement device 60 is also accommodated in this space. Further, the transmission 4 is housed in the space on the second side L2 in the axial direction with respect to the first wall part 51 in the case inner space formed by being surrounded by the peripheral wall part. Even if the first wall portion 51 and the second wall portion 52 are integrally formed with the peripheral wall portion so as to extend radially inward R2 from the peripheral wall portion, they are separate members fixed to the peripheral wall portion (the peripheral wall portion included in the case 50). Member different from the above).

The first wall portion 51 is formed so as to extend in the radial direction R, and in the present embodiment, is formed in an annular shape that is coaxial with the rotation axis A when viewed in the axial direction along the axial direction L. That is, the first wall portion 51 includes a disk-shaped wall portion that extends not only in the radial direction R but also in the circumferential direction. A through hole penetrating the first wall portion 51 in the axial direction L is formed in the center portion of the first wall portion 51 in the radial direction R (the end portion on the radial inner side R2), and the shift input member 20 has this through hole. It is inserted through the through hole. The speed change input member 20 is arranged so as to penetrate the first wall portion 51 in the axial direction L, and the rotary electric machine 5 (specifically, arranged on the axial first side L1 with respect to the first wall portion 51). The rotor support member 30) is connected to the transmission 4 arranged on the second side L2 in the axial direction with respect to the first wall portion 51.

In the present embodiment, the first wall portion 51 includes a tubular support portion 53 formed in a tubular shape (here, cylindrical) extending in the axial direction L. The tubular support portion 53 is formed at the center of the first wall portion 51 in the radial direction R. Further, the tubular support portion 53 is formed so as to project to the axial first side L1 with respect to a portion of the first wall portion 51 adjacent to the tubular support portion 53 on the radially outer side R1. .. The through hole of the first wall portion 51 (the through hole into which the shift input member 20 is inserted) is formed so as to be surrounded by the inner peripheral surface of the tubular support portion 53. The engagement portion provided on the rotor support member 30 (specifically, the first support portion 31) on the outer peripheral surface of the portion of the speed change input member 20 that is arranged on the first side L1 in the axial direction with respect to the tubular support portion 53. 34 is engaged. As described below, the tubular support portion 53 supports the shift input member 20 from the radially outer side R1.

A bearing for rotatably supporting the shift input member 20 with respect to the case 50 is disposed between the inner peripheral surface of the cylindrical support portion 53 and the outer peripheral surface of the shift input member 20. As shown in FIG. 3, in the present embodiment, as a bearing for rotatably supporting the speed change input member 20 with respect to the case 50, a fourth bearing B4 (here, a bush) and a fifth bearing B5 (here, a bush). , Bushes) are arranged between the inner peripheral surface of the tubular support portion 53 and the outer peripheral surface of the speed change input member 20. The fifth bearing B5 is arranged axially on the first side L1 with respect to the fourth bearing B4. As described above, the shift input member 20 is rotatably supported by the case 50, and in this embodiment, is rotatably supported by the case 50 via the fourth bearing B4 and the fifth bearing B5. ..

In the present embodiment, the first sleeve member 81 formed in a tubular shape (here, cylindrical shape) extending in the axial direction L is provided between the inner peripheral surface of the tubular support portion 53 and the outer peripheral surface of the shift input member 20. Are arranged. The first sleeve member 81 is fitted on the inner peripheral surface of the tubular support portion 53. The bearings (in the present embodiment, the fourth bearing B4 and the fifth bearing B5) for rotatably supporting the shift input member 20 with respect to the case 50 are connected to the inner peripheral surface of the first sleeve member 81 and the shift input. The first sleeve member 81 and the shift input member 20 are arranged so as to come into contact with the outer peripheral surface of the member 20. The first sleeve member 81 is made of, for example, a material harder than the first wall portion 51. As an example, the first wall portion 51 is made of an aluminum alloy and the first sleeve member 81 is made of steel. In the present embodiment, the first sleeve member 81 corresponds to the “sleeve member”.

As shown in FIG. 3, the shift input member 20 has a tubular shape (here, a cylindrical shape) extending in the axial direction L at a portion on the axial first side L1 (a portion including an end portion of the axial first side L1). ) Is formed on the first tubular portion 21. In the present embodiment, the first tubular portion 21 constitutes a part of the shift input member 20 including the end portion on the axial first side L1. That is, the first tubular portion 21 is formed into a bottomed cylindrical shape having a bottom portion on the axial second side L2. The engaging portion 34 is engaged with the outer peripheral surface of the portion of the first tubular portion 21 that is arranged on the first side L1 in the axial direction with respect to the tubular support portion 53. The first tubular portion 21 includes a portion arranged inside the tubular support portion 53 (a space surrounded by the inner peripheral surface of the tubular support portion 53). In the present embodiment, the portion of the first tubular portion 21 on the axial second side L2 (the portion including the end portion of the axial second side L2) is disposed inside the tubular support portion 53.

The engagement portion 34 is restricted from moving toward the axial first side L1 with respect to the shift input member 20 by the fastening member 40 that is screwed onto the inner peripheral surface of the first tubular portion 21 from the axial first side L1. Has been done. The fastening member 40 includes a shaft portion 41a that is screwed into the inner peripheral surface of the first tubular portion 21 and a head portion 41b that is arranged on the first side L1 in the axial direction with respect to the first tubular portion 21. The bolt 41 is provided. The head 41b is formed, for example, in a hexagonal shape when viewed in the axial direction. On the inner peripheral surface of the first tubular portion 21, a female screw to which a male screw formed on the outer peripheral surface of the shaft portion 41a is screwed is formed. An end portion of the shaft portion 41a on the second axial side L2 is arranged at an intermediate portion of the first tubular portion 21 in the axial direction L.

The position at which the engagement portion 34 comes into contact with the fastening member 40 or the member (for example, a washer) fixed to the first tubular portion 21 by the fastening member 40 from the axial second side L2 is determined. As the limit position, the fastening member 40 restricts the engagement portion 34 from moving to the first axial direction side L1 with respect to the shift input member 20 from the limit position. In the present embodiment, as the fastening member 40 (bolt 41), a flange bolt (bolt with a flange) integrally formed with a flange portion 41c protruding radially outward R1 with respect to the head portion 41b is used. The outer diameter of the flange portion 41c is larger than the outer peripheral surface of the first tubular portion 21. Then, in a state where the fastening member 40 is screwed onto the inner peripheral surface of the first tubular portion 21, the flange portion 41c is arranged so as to face the engaging portion 34 from the axial first side L1. There is. Therefore, in the present embodiment, the limit position is the position where the engagement portion 34 comes into contact with the flange portion 41c that is a part of the fastening member 40 from the axial second side L2.

As described above, in the present embodiment, the flange bolt is used as the fastening member 40 (bolt 41), but the fastening member 40 may be a bolt in which the flange portion 41c is not integrally formed. In this case, for example, a washer having an outer diameter larger than the outer peripheral surface of the first tubular portion 21 is arranged between the head portion 41b and the first tubular portion 21 in the axial direction L, and the washer is attached to the washer. On the other hand, the position at which the engagement portion 34 comes into contact with the second axial direction side L2 may be the limit position described above. In this case, unlike the present embodiment, the engaging portion 34 is provided on the axial second side L2 with respect to the member (specifically, the washer) fixed to the first tubular portion 21 by the fastening member 40. The position that comes into contact with is the limit position. As the fastening member 40, a bolt having an outer diameter of the head portion 41b (a diameter of a circle circumscribing the head portion 41b when viewed in the axial direction) larger than that of the outer peripheral surface of the first tubular portion 21 is used. The position at which the engaging portion 34 comes into contact with the head portion 41b that is a part of the fastening member 40 from the axial second side L2 may be the limit position.

As shown in FIG. 3, in the present embodiment, the movement of the shift input member 20 toward the first axial side L1 is restricted by the sixth bearing B6 (here, a thrust bearing). Specifically, the shift input member 20 is provided on the axial second side L2 with respect to the tubular support portion 53, inside the tubular support portion 53 (a space surrounded by the inner peripheral surface of the tubular support portion 53). The expanded diameter portion 22 is formed to have a diameter larger than that of the arranged portion. The expanded diameter portion 22 is arranged so as to overlap the first wall portion 51 when viewed in the axial direction. The sixth bearing B6 is arranged between the expanded diameter portion 22 and the first wall portion 51 in the axial direction L so as to contact the expanded diameter portion 22 and the first wall portion 51, respectively. As described above, since the fastening member 40 restricts the movement of the engaging portion 34 to the shift input member 20 in the first axial direction L1, it acts on the rotor support member 30 (specifically, the first support portion 31). The load on the axial first side L1 is transmitted to the shift input member 20 via the fastening member 40. The load on the axial first side L1 transmitted to the shift input member 20 is the sixth bearing. It can be received by the first wall portion 51 via B6.

In addition, in the present embodiment, a second bearing B2 (here, a ball bearing) is provided for rotatably supporting the rotor support member 30 with respect to the case 50 with respect to the movement of the shift input member 20 toward the second axial side L2. ) Is regulated by. Specifically, the first support portion 31 of the rotor support member 30 includes a fourth tubular portion 37 formed in a tubular shape (here, cylindrical) extending in the axial direction L. The fourth tubular portion 37 is arranged radially outside the bearing support portion 54 formed on the first wall portion 51 in the radial direction R1 and at a position overlapping the bearing support portion 54 when viewed in the radial direction. The bearing support portion 54 has a cylindrical (here, cylindrical) outer peripheral surface extending in the axial direction L.

Then, the second bearing B2 is arranged between the inner peripheral surface of the fourth tubular portion 37 and the outer peripheral surface of the bearing supporting portion 54 so as to contact the fourth tubular portion 37 and the bearing supporting portion 54, respectively. Has been done. Further, the second bearing B2 is arranged so as to come into contact with the first support portion 31 from the axial second side L2 and also come into contact with the first wall portion 51 from the axial first side L1. .. Specifically, a step portion having a step surface facing the axial second side L2 is formed on the inner peripheral surface of the fourth tubular portion 37, and the second bearing B2 (specifically, the second bearing B2) is formed. The outer ring of the bearing B2 is arranged so as to come into contact with the stepped surface from the axial second side L2. A step portion having a step surface facing the first axial direction side L1 is formed on the outer peripheral surface of the bearing support portion 54, and the second bearing B2 (specifically, the inner ring of the second bearing B2) is It is arranged so as to come into contact with the stepped surface from the axial first side L1. It should be noted that in the present specification, “abutting” with respect to the arrangement of the bearing means at least abutting in a state where the clearance (clearance) in the disposing portion of the bearing is closed.

In this way, the second bearing B2 is arranged so as to come into contact with the first support portion 31 from the axial second side L2 and also come into contact with the first wall portion 51 from the axial first side L1. Therefore, the load acting on the first support portion 31 on the axial second side L2 can be received by the first wall portion 51 via the second bearing B2. That is, the movement of the first support portion 31 toward the axial second side L2 is restricted by the second bearing B2. The load acting on the speed change input member 20 on the second axial side L2 is transmitted to the rotor support member 30 (specifically, the first support portion 31) via the fastening member 40, but the first support portion. Since the movement of 31 to the axial second side L2 is thus regulated by the second bearing B2, the movement of the shift input member 20 to the axial second side L2 is also regulated by the second bearing B2. .. As described above, in the vehicle drive device 1, the movement of the speed change input member 20 toward the second axial side L2 is supported not by the dedicated bearing but by the rotor support member 30 so as to be rotatable with respect to the case 50. It is possible to regulate by the second bearing B2.

The second wall portion 52 is formed so as to extend in the radial direction R, and in the present embodiment, is formed in an annular shape that is coaxial with the rotation axis A when viewed in the axial direction along the axial direction L. That is, the second wall portion 52 includes a disk-shaped wall portion that extends not only in the radial direction R but also in the circumferential direction. A through hole that penetrates the second wall portion 52 in the axial direction L is formed in the center portion of the second wall portion 52 in the radial direction R, and the input member 10 is inserted into this through hole. The input member 10 is arranged so as to penetrate the second wall portion 52 in the axial direction L, and the damper 7 disposed on the axial first side L1 with respect to the second wall portion 52 and the second wall. The engagement device 60 (specifically, the inner support portion 63) arranged on the second side L2 in the axial direction is connected to the portion 52. The input member 10 is arranged on the first side L1 in the axial direction with respect to the shift input member 20.

As shown in FIG. 3, between the inner peripheral surface of the second wall portion 52 (specifically, the inner peripheral surface of the through hole formed in the second wall portion 52) and the outer peripheral surface of the input member 10. Has a first bearing B1 (here, a needle bearing) for rotatably supporting the input member 10 with respect to the case 50. Specifically, the input member 10 includes a second tubular portion 12 formed in a tubular shape (here, cylindrical) extending in the axial direction L. The second tubular portion 12 is formed in a bottomed cylindrical shape having a bottom portion 12b on the first axial side L1. The second tubular portion 12 is arranged radially outside the shift input member 20 in the radial direction and at a position overlapping the shift input member 20 (specifically, the first tubular portion 21) when viewed in the radial direction. It is equipped with a part. The shift input member 20 is arranged so as to be rotatable relative to the input member 10 in a state of being inserted from the axial second side L2 into the space surrounded by the inner peripheral surface of the second tubular portion 12. .. The engagement portion 34 is engaged with the outer peripheral surface of the shift input member 20, and the second cylindrical portion 12 has an inner peripheral surface of the second cylindrical portion 12 spaced from the outer peripheral surface of the engaging portion 34. Are arranged on the radially outer side R1 with respect to the engaging portion 34 so as to face each other. The first bearing B1 is arranged between the inner peripheral surface of the second wall portion 52 and the outer peripheral surface of the second tubular portion 12. In the present embodiment, the first bearing B1 is arranged on the outer side R1 in the radial direction with respect to the fastening member 40 and at a position overlapping the fastening member 40 in the radial direction. In this way, the input member 10 is rotatably supported with respect to the case 50 via the first bearing B1. Further, between the second tubular portion 12 and the first support portion 31 (specifically, the second annular plate-shaped portion 38 described later) in the axial direction L, the second tubular portion 12 and the first tubular portion 12 are provided. The seventh bearing B7 (here, a thrust washer) is arranged so as to come into contact with each of the support portions 31. In the present embodiment, the first bearing B1 corresponds to the “support bearing”.

As shown in FIG. 3, the second tubular portion 12 is provided with a connecting portion 13 that is connected to the inner supporting portion 63 so as to rotate integrally therewith. In the present embodiment, the connecting portion 13 is formed so as to extend from the second tubular portion 12 to the radially outer side R1. Here, the connecting portion 13 is formed in an annular plate shape (flange shape) that extends not only in the radial direction R but also in the circumferential direction. The connecting portion 13 is provided at the end of the second tubular portion 12 on the axial second side L2. Then, the end portion on the radially inner side R2 of the inner support portion 63 is connected (joined here by welding) to the end portion on the radially outer side R1 of the connecting portion 13. The first bearing B1 is arranged so as to support the input member 10 from the radially outer side R1 on the axial first side L1 with respect to the connecting portion 13. Specifically, the first bearing B1 is arranged so as to support a portion of the outer peripheral surface of the second tubular portion 12 on the axial first side L1 with respect to the coupling portion 13 from the radially outer side R1. .. Further, between the second wall portion 52 and the connecting portion 13 in the axial direction L, an eighth bearing B8 (here, a thrust washer) is arranged so as to abut on each of the second wall portion 52 and the connecting portion 13. Has been done.

In the present embodiment, as a bearing for rotatably supporting the rotor support member 30 with respect to the case 50, a third bearing B3 (here, a ball bearing) is provided in addition to the above-described second bearing B2. .. The second bearing B2 is a bearing for rotatably supporting the first support portion 31 with respect to the case 50 (specifically, the first wall portion 51), while the third bearing B3 is the second bearing. It is a bearing for rotatably supporting the support portion 32 with respect to the case 50 (specifically, the second wall portion 52 ). In the present embodiment, the third bearing B3 is arranged at the outer side R1 in the radial direction with respect to the first bearing B1 and at a position overlapping the first bearing B1 in the radial direction.

As shown in FIG. 3, in the present embodiment, a concave portion 11 that is recessed toward the first axial direction side L1 is formed on the surface of the input member 10 that faces the second axial direction side L2. Specifically, the recess 11 is formed on the bottom surface of the bottom portion 12b of the second tubular portion 12 that faces the axial second side L2. The recess 11 is formed in a circular shape when viewed in the axial direction. The inner peripheral surface of the recess 11 has a smaller diameter than the inner peripheral surface of the second tubular portion 12, and the outer diameter of the head portion 41b of the fastening member 40 (bolt 41) (which is circumscribing the head portion 41b in an axial view). (Diameter of the circle). And the recessed part 11 is arrange|positioned so that the head part 41b (here, a part of axial direction 1st side L1 in the head part 41b) may be enclosed from the axial direction 1st side L1 and the radial direction outer side R1. That is, the head portion 41b is arranged in a state of being inserted into the recess 11 from the axial second side L2. A portion of the head portion 41b that is not inserted into the recess 11 (portion on the axial second side L2) is surrounded by the inner peripheral surface of the second tubular portion 12 from the radial outside R1. The head portion 41b is arranged with a space from the recess 11 and the second tubular portion 12.

Next, an oil supply structure for each part in the vehicle drive device 1 of the present embodiment will be described. As shown in FIG. 3, the shift input member 20 is formed inside the first oil passage 71 provided in the case 50 and the first tubular portion 21 (surrounded by the inner peripheral surface of the first tubular portion 21). The second oil passage 72 communicating with the internal space S). As shown by the broken line in FIG. 3, the hydraulic pressure after being controlled by the hydraulic control device (not shown) circulates through the first oil passage 71 and the second oil passage 72 in this order, and then flows into the internal space S. Supplied. In the present embodiment, the first oil passage 71 is provided in the first wall portion 51, and is formed inside the first wall portion 51 here. Then, the first oil passage 71 includes a first opening portion 71 a that opens to the inner peripheral surface of the tubular support portion 53. Here, a recessed portion that is recessed radially outward R1 is formed on the inner peripheral surface of the tubular support portion 53, and the first opening 71a is formed on the bottom surface of the recessed portion (the surface that faces the radially inner side R2). ing.

As described above, in the present embodiment, the damper 7 is arranged on the first side L1 in the axial direction with respect to the second wall portion 52. Therefore, when providing the first oil passage 71 in the second wall portion 52, it is necessary to provide the first oil passage 71 so as to avoid interference with the damper 7, and it is difficult to provide the first oil passage 71. May be. In view of this point, in the present embodiment, the first oil passage 71 is provided in the first wall portion 51 instead of the second wall portion 52.

As shown in FIG. 3, the second oil passage 72 connects the inner peripheral surface of the first tubular portion 21 and the outer peripheral surface of the shift input member 20 (here, the outer peripheral surface of the first tubular portion 21). Is provided. Therefore, the second oil passage 72 includes the second opening 72a that opens to the outer peripheral surface of the shift input member 20 (here, the first tubular portion 21). In addition, the second oil passage 72 is a third opening portion that is opened in a portion of the inner peripheral surface of the first tubular portion 21 on the axial second side L2 with respect to the shaft portion 41a of the fastening member 40 (bolt 41). 72b is provided. In the present embodiment, the second oil passage 72 is formed by a through hole that penetrates the first tubular portion 21 in the radial direction R (here, a through hole that penetrates in parallel to the radial direction R). The second opening 72a is arranged so as to communicate with the first opening 71a of the first oil passage 71, whereby the oil flowing out of the first oil passage 71 through the first opening 71a. Can be made to flow into the second oil passage 72 from the second opening 72a. As described above, in the present embodiment, the first sleeve member 81 is arranged between the inner peripheral surface of the tubular support portion 53 and the outer peripheral surface of the shift input member 20. And the 1st opening part 71a and the 2nd opening part 72a penetrate the 1st sleeve member 81 in the radial direction R, and the 1st through-hole 81a (here, penetrates in parallel to the radial direction R). Through the through hole) formed as described above. The first through hole 81a is formed between the fourth bearing B4 and the fifth bearing B5 in the axial direction L.

In this way, the hydraulic pressure after being controlled by the hydraulic control device is supplied to the internal space S by sequentially flowing through the first oil passage 71 and the second oil passage 72. Then, the oil in the internal space S flows through a third oil passage 73 and a fourth oil passage 74, which will be described below, in order, and is supplied to the first bearing B1. Specifically, as shown in FIG. 3, the fastening member 40 includes a third oil passage 73 that penetrates the fastening member 40 in the axial direction L and connects the inside and the outside of the first tubular portion 21. ing. Therefore, as shown by the broken line in FIG. 3, the oil in the internal space S flows through the third oil passage 73 to the axial first side L1 and is discharged to the outside of the first tubular portion 21. It The third oil passage 73 is formed so as to extend along the axial direction L (here, so as to extend parallel to the axial direction L). As described above, in the present embodiment, the fastening member 40 uses the bolt 41 having the through hole extending in the axial direction L at the center portion in the radial direction R, and the third oil passage 73 is formed by the through hole. Are formed.

The input member 10 includes a fourth oil passage 74 that supplies the oil discharged from the third oil passage 73 to the outside of the first tubular portion 21 to the first bearing B1. That is, the fourth oil passage 74 is formed using the input member 10. As described above, in the present embodiment, the recess 11 formed in the input member 10 is arranged so as to surround the head portion 41b of the fastening member 40 (bolt 41) from the axial first side L1 and the radial outer side R1. ing. The gap formed between the inner surface of the recess 11 and the head portion 41b constitutes part of the fourth oil passage 74. The gap formed between the bottom surface and the inner peripheral surface of the second tubular portion 12 and the head portion 41b and the flange portion 41c also constitutes a part of the fourth oil passage 74. As shown by the broken line in FIG. 3, the oil discharged from the third oil passage 73 to the outside of the first tubular portion 21 has a gap formed between the inner surface of the recess 11 and the head portion 41b. To the radially outer side R1 and supplied to the inner peripheral surface of the second tubular portion 12. The oil supplied to the inner peripheral surface of the second tubular portion 12 is formed so as to penetrate the second tubular portion 12 in the radial direction R on the first side L1 in the axial direction with respect to the connecting portion 13. It circulates to the outer side R1 in the radial direction through the second through hole 12a and is supplied to the first bearing B1. That is, the second through hole 12a also constitutes a part of the fourth oil passage 74. Here, the second through hole 12a is formed so as to penetrate the second tubular portion 12 in parallel with the radial direction R. Part of the oil supplied to the inner peripheral surface of the second tubular portion 12 is supplied to the seventh bearing B7, and the oil after lubricating the seventh bearing B7 is the engagement device 60 or the rotary electric machine 5. Is supplied from the radially inner side R2.

In the present embodiment, a part of the oil that flows out of the first oil passage 71 from the first opening 71a is supplied to the second oil chamber H2. Specifically, as shown in FIG. 3, the tubular support portion 53 has a third inner surface that communicates the inner peripheral surface of the tubular support portion 53 and the end surface of the tubular support portion 53 on the first axial side L1. The through hole 53 a is formed, and a part of the oil flowing out of the first oil passage 71 from the first opening 71 a is part of the third through hole 53 a and the third tubular portion 35 of the first support portion 31. Through a through hole formed so as to penetrate in the radial direction R, and is supplied to the second oil chamber H2. The third tubular portion 35 is formed in a tubular shape (here, a tubular shape) extending in the axial direction L, is radially outside R1 with respect to the tubular support portion 53, and is a tubular body when viewed in the radial direction. It is arranged at a position overlapping with the circular support portion 53. Then, the end portion of the third tubular portion 35 on the second axial side L2 is connected to the fourth annular plate portion 36, which is formed in an annular plate shape extending in the radial direction R and the circumferential direction, via the fourth annular plate portion 36. It is connected to the end of the tubular portion 37 on the first axial side L1. Further, the end portion of the third tubular portion 35 on the first axial side L1 is engaged via a second annular plate-shaped portion 38 formed in an annular plate shape extending in the radial direction R and the circumferential direction. It is connected to the end of the axial direction second side L2 of the portion 34.

In the present embodiment, the first wall portion 51 is also formed with a fifth oil passage 75 for supplying the hydraulic pressure after being controlled by the hydraulic control device to the first oil chamber H1. The oil in the fifth oil passage 75 is formed so as to penetrate the tubular support portion 53 in the radial direction R and the fourth through hole 53b formed in the radial direction R and the second sleeve member 82. The fifth through hole 82a and a through hole formed so as to penetrate the third tubular portion 35 in the radial direction R are sequentially circulated to be supplied to the first oil chamber H1. Here, the second sleeve member 82 is a member formed in a tubular shape (here, a cylindrical shape) extending in the axial direction L, and is an inner peripheral surface of the third tubular portion 35 and an outer circumference of the tubular support portion 53. It is located between the surface and the surface.

[Other Embodiments]
Next, other embodiments of the vehicle drive device will be described.

(1) In the above embodiment, the first opening 71a and the second opening 72a communicate with each other through the first through hole 81a formed so as to penetrate the first sleeve member 81 in the radial direction R. Has been described as an example. However, without being limited to such a configuration, the oil passage (for example, the first opening 71a and the second opening 72a) formed in the first sleeve member 81 so as to extend in the axial direction L (for example, the first opening). It is also possible to adopt a configuration in which they communicate with each other via an oil passage formed inside the sleeve member 81.

(2) In the above embodiment, the concave portion 11 is formed on the surface of the input member 10 facing the second axial direction side L2, and the concave portion 11 allows the head portion 41b of the fastening member 40 (bolt 41) to move toward the first axial direction side. The configuration arranged so as to surround the L1 and the radially outer side R1 has been described as an example. However, without being limited to such a configuration, the concave portion 11 is not formed on the surface of the input member 10 facing the second axial direction side L2 (that is, the bottom surface formed on the bottom portion 12b of the second tubular portion 12). Is formed flat), and the entire head portion 41b may be surrounded by the bottom surface and the inner peripheral surface of the second tubular portion 12 from the axial first side L1 and the radial outer side R1.

(3) In the above embodiment, the configuration in which the first bearing B1 is arranged at the position overlapping the fastening member 40 in the radial direction has been described as an example. However, without being limited to such a configuration, the first bearing B1 is arranged at a position different from the fastening member 40 in the axial direction L so as not to overlap with the fastening member 40 in the radial direction. Can also

(4) In the above embodiment, the configuration in which the vehicle drive device 1 includes the engagement device 60 in the power transmission path between the input member 10 and the rotary electric machine 5 has been described as an example. However, without being limited to such a configuration, the vehicle drive device 1 does not include such an engagement device 60, and the input member 10 and the rotary electric machine 5 always rotate in conjunction with each other (for example, input The member 10 may be connected so as to rotate integrally with the rotary electric machine 5).

(5) Note that the configuration disclosed in each of the above-described embodiments may be applied in combination with the configuration disclosed in another embodiment as long as no contradiction occurs (of the embodiments described as other embodiments. (Including combinations) is also possible. Regarding other configurations, the embodiments disclosed in the present specification are merely examples in all respects. Therefore, various modifications can be appropriately made without departing from the spirit of the present disclosure.

[Outline of the above embodiment]
Hereinafter, the outline of the vehicle drive device described above will be described.

The vehicle drive device (1) has a power transmission path connecting an input member (10) drivingly connected to the internal combustion engine (2) and an output member (19) drivingly connected to the wheels (3) to the input member. A rotating electric machine (5), a speed change input member (20), and a transmission for transmitting the rotation of the speed change input member (20) to the output member (19) side in order from the side of (10). 4), the input member (10), the rotary electric machine (5), and the speed change input member (20) are arranged coaxially, and the speed change input member (20) with respect to the case (50). And is rotatably supported, and the input member (10) is disposed on the axial first side (L1), which is one side of the shift input member (20) in the axial direction (L), and is supported. The rotating electric machine (5) supports the rotor (5a) and the rotor (5a) from the inner side in the radial direction (R) by being rotatably supported by the case (50) via a bearing (B1). A rotor support member (30) for operating the shift input member (20), the rotor support member (30) including an engagement portion (34) that engages with an outer peripheral surface of the shift input member (20). ) Is provided with a first tubular portion (21) formed in a tubular shape extending in the axial direction (L) at a portion on the axial first side (L1), and the engaging portion (34) is By the fastening member (40) screwed to the inner peripheral surface of the first tubular portion (21) from the axial first side (L1), the axial first side with respect to the shift input member (20). Movement to (L1) is restricted, and the shift input member (20) communicates the first oil passage (71) provided in the case (50) with the inside of the first tubular portion (21). And a second oil passage (72), and the fastening member (40) penetrates the fastening member (40) in the axial direction (L) and the inside and the outside of the first tubular portion (21). A third oil passage (73) communicating with each other, and the input member (10) receives the oil discharged from the third oil passage (73) to the outside of the first tubular portion (21) by the support bearing. A fourth oil passage (74) is supplied to (B1).

According to this configuration, since the rotor support member (30) includes the engagement portion (34) that engages with the outer peripheral surface of the gear shift input member (20), the rotor support member (30) and the gear shift input member (20) are Can be directly connected. Therefore, as compared with the case where the rotor support member (30) and the shift input member (20) are connected via another member arranged between these two members in the radial direction (R), It is possible to reduce the size in the radial direction (R).
And in the said structure, the oil of a 1st oil path (71) is made to circulate through a 2nd oil path (72), a 3rd oil path (73), and a 4th oil path (74) in order, and an input member. (10) can be supplied to a support bearing (B1) that rotatably supports the case (50). Here, since the third oil passage (73) is formed by penetrating the fastening member (40) in the axial direction (L), the first axial direction of the engagement portion (34) with respect to the shift input member (20). Even when the fastening member (40) restricts the movement to the side (L1), the support bearing (using the first tubular portion (21) having the inner peripheral surface with which the fastening member (40) is screwed is used. It is possible to form an oil passage for supplying oil to B1).
Even in the configuration in which the fastening member (40) restricts the movement of the engagement portion (34) to the shift input member (20) toward the first axial direction (L1), for example, the entire fastening member (40) is The first tubular portion (21) is formed to be long in the axial direction (L) to such an extent that the first tubular portion (21) is arranged on the first side (L1) in the axial direction with respect to the support bearing (B1). It is conceivable to discharge the internal oil from a through hole formed so as to penetrate the first tubular portion (21) in the radial direction (R) and supply the oil to the support bearing (B1). However, in this case, since the first tubular portion (21) becomes longer in the axial direction (L), the size of the entire device tends to increase in the axial direction (L). On the other hand, according to the above configuration, the first tubular portion (21) is axially formed by penetrating the fastening member (40) in the axial direction (L) to form the third oil passage (73). An oil passage for supplying oil to the support bearing (B1) can be formed while suppressing the lengthening in the direction (L).
As described above, according to the above configuration, the input member (10) is rotatably supported with respect to the case (50) while the size of the entire device is reduced in the radial direction (R) and the axial direction (L). It becomes possible to appropriately supply the lubricating oil to the supporting bearing (B1).

Here, the case (50) is formed in a tubular shape extending in the axial direction (L), and a tubular supporting portion (53) that supports the shift input member (20) from the outside in the radial direction (R). And a sleeve member (81) formed in a tubular shape extending in the axial direction (L) between the inner peripheral surface of the tubular support portion (53) and the outer peripheral surface of the speed change input member (20). Is disposed, the first oil passage (71) includes a first opening (71a) that opens to the inner peripheral surface of the tubular support portion (53), and the second oil passage (72) is A second opening (72a) that opens to the outer peripheral surface of the shift input member (20) is provided, and the first opening (71a) and the second opening (72a) define the sleeve member (81). It is preferable that they communicate with each other through a first through hole (81a) formed so as to penetrate in the radial direction (R).

According to this configuration, when the first opening (71a) and the second opening (72a) communicate with each other through the oil passage formed in the sleeve member (81) so as to extend in the axial direction (L). Compared with, the size of the sleeve member (81) in the radial direction (R) can be easily reduced. Therefore, it is possible to further reduce the size of the entire device in the radial direction (R).

Further, it is preferable that the support bearing (B1) is arranged at a position overlapping the fastening member (40) when viewed in the radial direction along the radial direction (R).

According to this structure, compared with the case where the support bearing (B1) is arranged at a position different from the fastening member (40) in the axial direction (L) so as not to overlap with the fastening member (40) in the radial direction. It is easy to downsize the entire device in the axial direction (L).

The fastening member (40) has a shaft portion (41a) screwed to the inner peripheral surface of the first tubular portion (21) and the axial direction with respect to the first tubular portion (21). A head (41b) arranged on the first side (L1), and a bolt (41) having a head opposite to the axial first side (L1) in the axial direction (L). As the second side (L2), a concave portion (11) concave toward the first axial direction side (L1) is formed on a surface of the input member (10) facing the second axial direction side (L2), and the concave portion is formed. (11) is arranged so as to surround the head portion (41b) from the axial first side (L1) and the radial direction (R) outside, and the inner surface of the recess (11) and the head portion (41b). It is preferable that the gap formed between the first oil passage and the second oil passage forms a part of the fourth oil passage (74).

According to this structure, the fourth oil passage (74) is appropriately formed by inserting the head portion (41b) of the bolt (41) into the concave portion (11) from the second side (L2) in the axial direction. Meanwhile, the input member (10) and the shift input member (20) can be arranged close to each other in the axial direction (L). Therefore, it is possible to further reduce the size of the entire device in the axial direction (L).

Further, an engagement device (60) is provided in a power transmission path between the input member (10) and the rotary electric machine (5), and the engagement device (60) is provided with respect to the rotor (5a). The engaging device (60) is disposed inside the radial direction (R) and at a position overlapping the rotor (5a) when viewed in the radial direction along the radial direction (R). The input member (10) is formed in a tubular shape extending in the axial direction (L), and includes an inner support portion (63) for supporting the engaging member (61) of 60) from the inside in the radial direction (R). A second tubular portion (12) that is formed, and the second tubular portion (12) is outside the radial direction (R) with respect to the shift input member (20) and is viewed in the radial direction. A connecting portion that includes a portion arranged at a position overlapping with the shift input member (20) and is connected to the second tubular portion (12) so as to rotate integrally with the inner support portion (63). (13) is provided, and the support bearing (B1) has the input member (10) outside the radial direction (R) on the axial first side (L1) with respect to the coupling portion (13). And is formed so as to penetrate the second tubular portion (12) in the radial direction (R) at the axial first side (L1) with respect to the connecting portion (13). It is preferable that the second through hole (12a) constitutes a part of the fourth oil passage (74).

According to this structure, the support bearing (B1) is arranged so as to support the input member (10) from the outside in the radial direction (R) on the first side (L1) in the axial direction with respect to the connecting portion (13). Even in this case, the fourth oil passage (74) for supplying oil to the support bearing (B1) can be appropriately formed. In the above configuration, the input member (10) and the shift input member (10) are provided to the extent that the second tubular portion (12) includes a portion that is arranged at a position overlapping the shift input member (20) when viewed in the radial direction. 20) can be arranged close to the axial direction (L), so that the fourth oil passage (74) can be appropriately formed while achieving miniaturization of the entire device in the axial direction (L).

The vehicle drive device according to the present disclosure may have at least one of the effects described above.

1: Vehicle drive device 2: Internal combustion engine 3: Wheels 4: Transmission 5: Rotating electric machine 5a: Rotor 10: Input member 11: Recessed portion 12: Second cylindrical portion 12a: Second through hole 13: Connection portion 19: Output member 20: Shift input member 21: First tubular portion 30: Rotor supporting member 34: Engaging portion 40: Fastening member 41: Bolt 41a: Shaft portion 41b: Head portion 50: Case 53: Cylindrical supporting portion 60: Engaging device 61: first engaging member (engaging member)
63: Inner support 71: First oil passage 71a: First opening 72: Second oil passage 72a: Second opening 73: Third oil passage 74: Fourth oil passage 81: First sleeve member (sleeve member )
81a: First through hole B1: First bearing (support bearing)
L: Axial direction L1: Axial first side L2: Axial second side R: Radial direction

Claims (5)

A rotary electric machine, a shift input member, and a rotation of the shift input member are arranged in order from the input member side in a power transmission path connecting an input member drivingly connected to the internal combustion engine and an output member drivingly connected to the wheels. A vehicle drive device comprising: a transmission that shifts and transmits to the output member side,
The input member, the rotary electric machine, and the shift input member are arranged coaxially,
The shift input member is rotatably supported with respect to the case,
The input member is disposed on an axial first side that is one side in the axial direction with respect to the shift input member, and is rotatably supported with respect to the case via a support bearing,
The rotating electrical machine includes a rotor, and a rotor support member that supports the rotor from a radially inner side,
The rotor support member includes an engaging portion that engages with an outer peripheral surface of the shift input member,
The shift input member includes a first tubular portion formed in a tubular shape extending in the axial direction at a portion on the axial first side,
A movement of the engaging portion with respect to the shift input member to the axial first side is restricted by a fastening member that is screwed onto the inner peripheral surface of the first tubular portion from the axial first side. ,
The shift input member includes a second oil passage that connects the first oil passage provided in the case and the inside of the first tubular portion,
The fastening member includes a third oil passage that penetrates the fastening member in the axial direction and connects the inside and the outside of the first tubular portion,
The vehicle drive device, wherein the input member includes a fourth oil passage that supplies oil discharged from the third oil passage to the outside of the first tubular portion to the support bearing. The case includes a tubular support portion formed in a tubular shape extending in the axial direction and supporting the shift input member from the outside in the radial direction,
A sleeve member formed in a tubular shape extending in the axial direction is arranged between an inner peripheral surface of the tubular support portion and an outer peripheral surface of the shift input member,
The first oil passage includes a first opening portion that opens to an inner peripheral surface of the tubular support portion,
The second oil passage includes a second opening opening on an outer peripheral surface of the shift input member,
The vehicle drive according to claim 1, wherein the first opening portion and the second opening portion communicate with each other through a first through hole formed so as to penetrate the sleeve member in the radial direction. apparatus. The vehicle drive device according to claim 1, wherein the support bearing is arranged at a position overlapping the fastening member when viewed in the radial direction along the radial direction. The fastening member includes a bolt including a shaft portion that is screwed into an inner peripheral surface of the first tubular portion, and a head portion that is disposed on the first axial side with respect to the first tubular portion. And
A recessed portion that is recessed toward the first axial direction is formed on a surface of the input member that faces the second axial direction, with the side opposite to the first axial side in the axial direction as the second axial side. ,
The recess is disposed so as to surround the head from the axial first side and the radial outside.
The vehicle drive device according to claim 1, wherein a gap formed between the inner surface of the recess and the head portion constitutes a part of the fourth oil passage. An engagement device is provided in a power transmission path between the input member and the rotary electric machine,
The engagement device is arranged inside the radial direction with respect to the rotor, and is arranged at a position overlapping with the rotor when viewed in the radial direction along the radial direction.
The engagement device includes an inner support portion that supports the engagement member of the engagement device from the inner side in the radial direction,
The input member includes a second tubular portion formed in a tubular shape extending in the axial direction,
The second tubular portion includes a portion arranged outside the shift input member in the radial direction and at a position overlapping the shift input member when viewed in the radial direction,
The second tubular portion is provided with a connecting portion connected to rotate integrally with the inner support portion,
The support bearing is arranged so as to support the input member from the outer side in the radial direction on the first side in the axial direction with respect to the connecting portion,
A second through hole formed so as to penetrate the second tubular portion in the radial direction on the first side in the axial direction with respect to the connecting portion constitutes a part of the fourth oil passage. The vehicle drive device according to any one of claims 1 to 4.

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