Vehicle drive device

Abstract

A vehicle drive device (1) comprising a rotary electric machine (MG), a fluid coupling (TC) arranged coaxially with the rotary electric machine (MG) on a side of a first axial direction (L1) with respect to the rotary electric machine (MG), and a housing (3) accommodating the rotary electric machine (MG) and the fluid coupling (TC), wherein the side of the first axial direction (L1) is a side in an axial direction (L) with respect to the rotary electric machine (MG), and the fluid coupling (TC) has a clutch input member (2) drivingly coupled to a rotor member (21) of the rotary electric machine (MG), and a clutch output member (4) drivingly coupled to wheels (W), wherein: the housing (3) has a support wall portion (31) extending in a radial direction (R) of the rotary electric machine (MG) at a location in the axial direction (L) between the rotary electric machine (MG) and the fluid coupling (TC), and a first bearing (75) and a second bearing (76), which is separate from the first bearing (75), are arranged at mutually different positions in the radial direction (R), wherein the first bearing (75) is designed to support the rotor component (21) in the radial direction (R) such that it is rotatable with respect to the support wall region (31), and the second bearing (76) is designed to support the clutch input component (2) in the radial direction (R) such that it is rotatable with respect to the support wall region (31).

Description

TECHNICAL FIELD

[0001] The present invention relates to a vehicle drive device comprising a rotary electric machine, a fluid coupling arranged coaxially with the rotary electric machine, and a housing accommodating the rotary electric machine and the fluid coupling, wherein the fluid coupling has a clutch input component drivingly coupled to a rotor component of the rotary electric machine and a clutch output component drivingly coupled to the wheels. STATE OF THE ART

[0002] An example of the above-described prior art vehicle drive device is described in Japanese Patent Publication No. 3080612 B2 (Patent Document 1). In the description in the "PRIOR ART" section, the names of components used in Patent Document 1 are cited in square brackets for descriptive purposes. In the structure described in Patent Document 1, as shown in Fig. 1 of the document, a rotor member [a rotor 8] and a clutch input member [a pump impeller 5] are fixed to each other, and a bearing [a radial bearing 9] is provided for jointly supporting the rotor member and the clutch input member in the radial direction so as to be rotatable with respect to a housing [a housing 10].

[0003] However, in the configuration described in Patent Document 1, the clutch input member constituting a heavy fluid coupling (a torque converter) and the rotor member requiring high bearing accuracy in the radial direction are supported by a common bearing in the radial direction with respect to the housing, and thus, it is necessary to use a relatively large bearing. Therefore, in the configuration according to Patent Document 1, constraints such as the size of the bearing itself and the arrangement of its surrounding support structure tend to make the bearing and surrounding support structure large, resulting in the entire device becoming large. Generally, as the bearing becomes larger, power loss due to rotation of the bearing tends to increase. Therefore, in the structure according to Patent Document 1, as the bearing becomes large, the energy efficiency of the device may be correspondingly reduced. State-of-the-art documentsPatent documents

[0004] Patent Document 1: Japanese Patent JP 3080612 B2 ( Fig. 1)

[0005] DE 10 2009 035 918 A1 discloses a combined power transmission and drive unit as well as a drive train for a hybrid system.

[0006] JP 2011-194 942 A and JP 2006-137 406 A disclose further vehicle drive devices. SUMMARY OF THE INVENTION Problem to be solved by the invention

[0007] In view of the foregoing, it is desirable to provide a vehicle drive device that can easily achieve both a reduction in size of the entire device and an improvement in its energy efficiency. Means to solve the problem

[0008] The present invention provides a vehicle drive device having the features of claim 1. Further developments of the invention are specified in the dependent claims.

[0009] The term "drivingly coupled" as used herein refers to a state in which two rotating elements are coupled to each other in a manner that enables transmission of a driving force, including a state in which the two rotating elements are coupled to rotate together, and a state in which the two rotating elements are coupled to each other via one or more transmission members in a manner that enables transmission of a driving force. Examples of such transmission members include various members that transmit rotation at the same or changed speed, such as a shaft, a gear mechanism, a belt, and a chain.Additional examples of such transmission components include engagement devices that selectively transmit rotation and drive force, such as a friction engagement device and a gear engagement device.

[0010] The term "rotary electric machine" as used herein refers to any one of an engine (electric motor), a generator (electric generator) and a motor generator which operates as both a motor and a generator as necessary.

[0011] The term “fluid coupling” as used herein refers to a torque converter that has a torque amplification function and a normal fluid coupling that does not have a torque amplification function.

[0012] The term “extend” in a specific direction as used herein for the shape of a component is not limited to the extension of the component in a direction parallel to a reference direction defined by a specific direction, but also includes an extension of the component in a direction intersecting the reference direction and also an extension of the component in a direction intersecting the reference direction at a specific angle within a predetermined range.

[0013] According to the characteristic configuration described above, the rotor member and the clutch input member can be supported by the first bearing and the second bearing, which are provided exclusively for the rotor member and the clutch member, respectively. Consequently, the first bearing and the second bearing can be configured as small bearings, and the degree of freedom in designing the arrangement of the support structures can be easily improved compared to a case where the rotor member and the clutch input member are supported by a common bearing. This results in the ability to reduce the size of the entire device. By constructing the first bearing and the second bearing as small bearings, it is easy to reduce power loss due to rotation, which accordingly improves the energy efficiency of the device.

[0014] Furthermore, according to the characteristic structure described above, the first bearing and the second bearing are arranged at different positions from each other in the radial direction. Thus, it is easy to reduce the axial length of the space occupied by the two bearings, including the supporting structures surrounding them.

[0015] Preferably, the support wall portion has a tubular protruding portion protruding to a side of the second axial direction that is an opposite side to the first axial direction, and the first bearing is arranged on an outer side in the radial direction with respect to the tubular protruding portion, and the second bearing is arranged on an inner side in the radial direction with respect to the tubular protruding portion.

[0016] According to this configuration, it is easy to arrange both the first bearing and the second bearing near the support wall portion (e.g., the tubular protruding portion) without interfering with each other. Thus, support structures between both the first bearing and the second bearing and the support wall portion (e.g., structures that fix both the first bearing and the second bearing to the support wall portion) can be simplified to reduce the space occupied by the bearings and their surrounding support structures.

[0017] Preferably, the vehicle drive device further comprises: an input member drivingly coupled to an internal combustion engine, and an engagement device provided in a power transmission path between the input member and the rotor member and capable of changing an engagement state, wherein the engagement device is arranged at a position where the engagement device partially overlaps the first bearing as viewed in the axial direction.

[0018] The above-described engagement device is provided for separating the internal combustion engine from the wheels to suppress energy loss due to drag of the internal combustion engine when the vehicle is driven only by torque of the rotary electric machine. According to the above-described configuration, the radial length of the space occupied by the engagement device and the first bearing can be reduced by the amount by which the engagement device and the first bearing overlap each other as viewed in the axial direction.

[0019] In the above-described structure having the engagement device provided in the power transmission path between the input member and the rotor member and capable of changing an engagement state, the rotor member preferably includes a rotor body and a rotor support member extending inward in the radial direction from the rotor body for supporting the rotor body, and the engagement device is arranged on the inside of the rotor body in the radial direction and at a position where the engagement device partially overlaps the rotor body as viewed in the radial direction.

[0020] According to the structure, the axial length of the space occupied by the engagement device and the rotor body can be reduced by an amount by which the engagement device and the rotor body overlap each other as viewed in the radial direction.

[0021] In the vehicle drive device having all the configurations described above, the second bearing is preferably arranged at a position where the second bearing partially overlaps the first bearing as viewed in the radial direction.

[0022] According to the configuration, the axial length of the space occupied by the first bearing and the second bearing can be reduced by an amount by which the first bearing and the second bearing overlap each other as viewed in the radial direction.

[0023] Preferably, the rotor component includes a rotor body and a rotor support member extending inward in the radial direction from the rotor body for supporting the rotor body, the rotor support member includes an axially protruding portion which is a tubular protruding portion protruding to the first axial direction side, and an outer peripheral surface or an inner peripheral surface of the axially protruding portion serves as a supported portion supported with respect to the support wall portion by the first bearing.

[0024] According to this configuration, the rotor support member can be appropriately supported in the radial direction with respect to the support wall portion, making it easy to minimize the clearance (air gap) between the rotor body and a stator. As a result, the size of the rotary electric machine can be reduced while ensuring output torque.

[0025] Preferably, the rotor component and the clutch input component are drivingly coupled to one another such that they are movable relative to one another in the axial direction.

[0026] According to the structure, it is easy to maintain the rotor member at a constant position in the axial direction regardless of the presence or absence of a load in the axial direction that may act on the clutch input member, while appropriately ensuring torque transmission between the rotor member and the clutch input member. Thus, it is possible to keep the axial length of the rotor body small and short, compared to a case where the rotor member and the clutch input member are drivingly coupled to each other so as to be immovable relative to each other in the axial direction, resulting in a reduction in the size of the rotary electric machine.

[0027] Preferably, the support wall portion has a tubular protruding portion protruding to a side of the second axial direction, which is a side opposite to the first axial direction. The tubular protruding portion is arranged on an inner side with respect to the rotor component in the radial direction and at a position where the tubular protruding portion partially overlaps the rotor component as viewed in the radial direction. The vehicle drive device further has a clutch portion extending in the axial direction through a location on a radially inner side with respect to the tubular protruding portion and extending on the second axial direction side with respect to a distal end portion of the tubular protruding portion to a location with respect to the tubular protruding portion on an outer side in the radial direction.and the rotor component and the clutch input component are coupled to each other via the clutch area.,

[0028] According to the structure, the axial length of the space occupied by the tubular protruding portion and the rotor member can be reduced by an amount by which the tubular protruding portion and the rotor member overlap each other in the radial direction in the case where the support wall portion includes the tubular protruding portion. In addition, the rotor member and the clutch input member, which are arranged separately on respective sides of the support wall portion in the axial direction, are appropriately coupled to each other. BRIEF DESCRIPTION OF THE DRAWINGS [ Fig. 1] Fig. 1 is a schematic diagram illustrating a schematic structure of a vehicle drive device according to an embodiment of the present invention. [ Fig. 2] Fig. 2 is a partial cross-sectional view of the vehicle drive device according to the embodiment of the present invention. [ Fig. 3] Fig. 3 is a partially enlarged view of Fig. 2. EMBODIMENTS FOR CARRYING OUT THE INVENTION

[0029] A vehicle drive device according to an embodiment of the present invention will be described with reference to the drawings. In the following description, unless specifically distinguished, the "axial direction L", the "radial direction R", and the "circumferential direction" are with respect to the rotational axis of a rotary electric machine MG (an axis X shown in Fig. 2). The “first axial direction L1” indicates the direction from the rotary electric machine MG to a torque converter TC along the axial direction L (towards the right in Fig. 2). The “second axial direction L2” indicates the direction opposite to the first axial direction L1 (in Fig. 2 to the left). The "radially inward direction R1" indicates the direction in the radial direction R toward the inside. The "radially outward direction R2" indicates the direction in the radial direction R toward the outside. Directions for each component indicate directions with the component installed in or assembled with the vehicle drive device 1. Expressions concerning the direction, position, etc. of each component may allow for differences based on manufacturing errors. 1. Overall structure of the vehicle drive device

[0030] Fig. 1 is a schematic diagram showing a schematic structure of a vehicle drive device according to the embodiment. As shown in Fig. 1, the vehicle drive device 1 comprises a rotary electric machine MG, a torque converter TC and a housing 3 (see Fig. 2) that houses the rotary electric machine MG and the torque converter TC. The torque converter TC is drivingly coupled to the rotary electric machine MG. More specifically, the torque converter TC is provided in a power transmission path between the rotary electric machine MG and an output shaft O. The output shaft O is drivingly coupled to wheels W via an output differential gear device DF. Rotation and torque transmitted to the output shaft O are distributed and transmitted to the two, left and right, wheels W via the output differential gear device DF. This enables the vehicle drive device 1 to transmit torque of the rotary electric machine MG to the wheels for traveling the vehicle. In the embodiment, the torque converter TC corresponds to the "fluid coupling" according to the present invention.

[0031] The vehicle drive device 1 according to the embodiment can transmit torque of an internal combustion engine E to the wheels W for driving the vehicle. That is, the vehicle drive device 1 has an input shaft I drivingly coupled to the internal combustion engine E. As shown in Fig. As shown in Fig. 1, the input shaft I, the rotary electric machine MG, the torque converter TC, and the output shaft O are provided in this order from the engine E side in the power transmission path connecting the engine E and the wheels W. Thus, the vehicle drive device 1 according to the embodiment is configured as a vehicle drive device for a hybrid vehicle (a hybrid drive device), more specifically, a so-called one-motor parallel type hybrid drive device that uses only one or both of the internal combustion engine E and the rotary electric machine MG as driving power sources for the vehicle. In the embodiment, the input shaft I corresponds to the "input member" according to the present invention.

[0032] The internal combustion engine E is a motor driven by the combustion of fuel in the internal combustion engine to generate power and may be, for example, a gasoline engine, a diesel engine, or the like. In the embodiment, the input shaft I is drivingly connected to an output shaft (such as a crankshaft) of the internal combustion engine E via a damper 16 (see Fig. 6, not in Fig. 1). The input shaft I can also be coupled to the output shaft of the internal combustion engine E without the damper 16.

[0033] In the embodiment, as shown in Fig. 1, a first clutch C1 is arranged in the power transmission path between the input shaft I and the rotary electric machine MG. The first clutch C1 functions as an engine disconnect clutch that disconnects the engine E from the wheels W. A speed change mechanism TM is arranged in the power transmission path between the torque converter TC and the output shaft O. The speed change mechanism TM is configured as a mechanism that can change the speed ratio stepwise or continuously (such as a stepped automatic transmission), and transmits rotation of the intermediate shaft M (a transmission input shaft) to the output shaft O (a transmission output shaft) with the speed changed at a predetermined speed ratio. In the embodiment, the first clutch C1 corresponds to the "engagement device" according to the present invention.

[0034] In the embodiment, the input shaft I, the first clutch C1, the rotary electric machine MG, the torque converter TC, the speed change mechanism TM and the output shaft O are all arranged on the axis X (see Fig. 2). The vehicle drive device 1 according to the embodiment has a single-axle structure suitable for mounting in FR (front-engine rear-wheel drive) vehicles. 2. Structure of various components of the drive device

[0035] Next, the structure of various components of the vehicle drive device according to the embodiment will be described with reference to FIG. Fig. 2 and Fig. 3 are described. Fig. 2 is a cross-sectional view of a part of the vehicle drive device 1 according to the embodiment taken along a plane including the axis X. Fig. 3 is a partially enlarged view of Fig. 2. 2-1. Housing

[0036] In the embodiment shown in Fig. 2, the housing 3 includes a first support wall portion 31, a second support wall portion 32, a third support wall portion 33, and a peripheral wall portion 34. The peripheral wall portion 34 is formed in a substantially cylindrical shape for covering the outer periphery of the rotary electric machine MG, the first clutch C1, the torque converter TC, and so on. The second support wall portion 32, the first support wall portion 31, and the third support wall portion 33 are formed in this order from a second axial direction L2 side to partition a housing interior space formed on the radially inward direction R1 side with respect to the peripheral wall portion 34 in the axial direction L. In the embodiment, the first support wall portion 31 corresponds to the “support wall portion” according to the present invention.

[0037] As it is in Fig. 2, the rotary electric machine MG and the first clutch C1 are accommodated in a space between the first support wall portion 31 and the second support wall portion 32 in the housing 3. In the embodiment, the space between the first support wall portion 31 and the second support wall portion 32 is formed in such a shape that a portion on the radially inward direction R1 side has a shorter length in the axial direction L than a portion on the radially outward direction R2 side. The torque converter TC is accommodated in a space in the housing 3 between the first support wall portion 31 and the third support wall portion 33. The damper 16 is accommodated in a space in the housing 3 with respect to the second support wall portion 32 on the second axial direction L2 side.

[0038] The first support wall portion 31 is formed in the axial direction L between the rotary electric machine MG and the torque converter TC to extend in the radial direction R. In the embodiment, the first support wall portion 31 is a circular plate-shaped wall portion extending in the circumferential direction in addition to the radial direction R. A through hole (hereinafter referred to as "first through hole") penetrating it in the axial direction L is formed in the central portion of the first support wall portion 31 in the radial direction R. The first support wall portion 31 is shaped such that a portion on the radially inward direction R1 side is offset in the axial direction L so as to be located on the second axial direction L2 side with respect to a portion on the radially outward direction R2 side.

[0039] The first support wall portion 31 has a tubular protruding portion 40 protruding toward the second axial direction L2 side. In the embodiment, the first tubular protruding portion 40 is arranged coaxially with the axis X at the center portion of the first support wall portion 31 in the radial direction R. An inner peripheral surface 40b (see Fig. 3) The first tubular protruding portion 40 forms the outer peripheral portion of the first through-hole. That is, the first tubular protruding portion 40 serves as a thick-walled portion (protrusion portion) having a predetermined thickness in the axial direction L and formed at an end portion of the first support wall portion 31 on the radially inward direction R side. In the embodiment, the first tubular protruding portion 40 corresponds to the "tubular protruding portion" according to the present invention.

[0040] The first tubular protruding portion 40 is arranged on the radially inward direction R1 side with respect to a rotor member 21, which will be discussed later, and at a position where the first tubular protruding portion 40 partially overlaps the rotor member 21 as viewed in the radial direction R. The term "partially overlapped as viewed in a predetermined direction" used herein for the arrangement of two members indicates that when the viewing direction is determined as the predetermined direction and the viewing point is moved in directions perpendicular to the viewing direction, the two members are seen from the viewing point as overlapping each other in a certain area.

[0041] In the embodiment shown in Fig. 3, a distal end portion 40a of the first tubular protruding portion 40 is disposed on the second axial direction L2 side in the axial direction L at a position where the distal end portion 40a overlaps the central region of the rotary electric machine MG in the axial direction L as viewed in the radial direction R, and a base end portion of the first tubular protruding portion 40 is positioned on a first axial direction L1 side with respect to an end portion of the rotor member 21 on the first axial direction L1 side. A part of a power transmission member T, to be discussed later, is disposed on the radially inward direction R1 side with respect to the first tubular protruding portion 40, that is, in the first through-hole.A step portion 40d having a surface (in this example, a cylindrical surface) facing the radially inward direction R1 side is formed on a side surface portion of the first tubular projecting portion 40 on the first axial direction L1 side.

[0042] The first support wall portion 31 has a second tubular protruding portion 41 having a larger diameter than the first tubular protruding portion 40. Like the first tubular protruding portion 40, the second tubular protruding portion 41 is formed to protrude toward the second axial direction L2 side and is arranged coaxially with the axis X. As shown in Fig. 3, the protrusion amount of the second tubular protruding portion 41 is smaller than the protrusion amount of the first tubular protruding portion 40, and a distal end portion 41a of the second tubular protruding portion 41 on the second axial direction L2 side is located with respect to the distal end portion 40a of the first tubular protruding portion 40 on the first axial direction L1 side. The second tubular protruding portion 41 is formed to have a smaller thickness in the radial direction R than the first tubular protruding portion 40. An inner peripheral step portion 41d having a surface (in this example, a circular surface) facing the second axial direction L2 side is formed on an inner peripheral surface 41b of the second tubular protruding portion 41.With the inner peripheral step portion 41d serving as the boundary, a portion on the second axial direction L2 side with respect to the inner peripheral step portion 41d is defined as a large diameter portion, and a portion on the first axial direction L1 side with respect to the inner peripheral step portion 41d is defined as a small diameter portion.

[0043] As it is in Fig. 2, the second support wall portion 32 is arranged on the second axial direction L2 side with respect to the rotary electric machine MG (in this example, in the axial direction L between the rotary electric machine MG and the damper 16) to extend in the radial direction R. In the embodiment, the second support wall portion 32 is a wall portion in the shape of a circular plate that extends in the circumferential direction in addition to the radial direction R. A through hole (hereinafter referred to as "second through hole") extending in the axial direction L is formed in the central portion of the second support wall portion 32 in the radial direction R. The input shaft I is inserted into the second through hole.The second support wall portion 32 is formed such that a portion on the radially inward direction R1 side is offset in the axial direction L to be located on the first axial direction L1 side with respect to a portion on the radially outward direction R2 side. As shown in FIG. Fig. 3, an inner circumferential step portion 32d having a surface (in this example, an annular surface) facing the first axial direction L1 side is formed on an inner circumferential surface 32b of a portion of the second support wall portion 32 on the radially inward direction R1 side, which forms the outer peripheral portion of the second through-hole. With the inner circumferential step portion 32d serving as the boundary, a portion on the first axial direction L1 side with respect to the inner circumferential step portion 32d is defined as a large diameter portion, and a portion on the second axial direction L2 side with respect to the inner circumferential step portion 32d is defined as a small diameter portion.

[0044] As it is in Fig. 2, the third support wall portion 33 is on the side of the first axial direction L1 with respect to the torque converter TC (in this example, in the axial direction L between the torque converter TC and the speed change mechanism TM (see Fig. 1)) to extend in the radial direction R. In the embodiment, the third support wall portion 33 is a wall portion in the shape of a flat circular plate extending in the circumferential direction in addition to the radial direction R. A through hole (hereinafter referred to as "third through hole") extending in the axial direction L is formed in the central portion of the second support wall portion 32 in the radial direction R. The intermediate shaft M is inserted into the third through hole. The third support wall portion 33 is provided with an oil pump 9. A pump drive shaft 67, which drives the oil pump 9, is drivingly coupled to a pump impeller 61, which will be discussed later, of the torque converter TC so as to rotate together with the pump impeller 61.This allows the oil pump 9 to discharge oil along with rotation of the pump impeller 61, thereby generating hydraulic pressure for supplying oil to various components of the vehicle drive device 1. The pump drive shaft 67 is supported in the radial direction R so as to be rotatable with respect to the third support wall portion 33 and a pump housing via a ninth bearing 79 (a needle bearing in this example). 2-2. Rotary electric machine

[0045] As it is in Fig. 2, the rotary electric machine MG is arranged between the first support wall portion 31 and the second support wall portion 32 in the axial direction L. In the embodiment, oil discharged from the oil pump 9 is supplied to a space partitioned on both sides in the axial direction L by the first support wall portion 31 and the second support wall portion 32 and partitioned on the radially outward direction R2 side by the circumferential wall 34, for cooling the rotary electric machine MG.

[0046] As it is in Fig. 2, the rotary electric machine MG includes a stator St fixed to the casing 3 and the rotor member 21. The stator St has coil end portions Ce provided on respective sides in the axial direction L. The rotor member 21 includes a rotor Ro and a rotor support member 22 extending in the radially inward direction R1 from the rotor Ro for supporting the rotor Ro. The rotor Ro is disposed on the radially inward direction R1 side with respect to the stator St and supported so as to be rotatable with respect to the casing 3 via the rotor support member 22, which rotates together with the rotor Ro. In the embodiment, the rotor Ro corresponds to the "rotor body" according to the present invention.

[0047] The rotor support member 22 is a member that supports the rotor Ro from the radially inward direction R1 side. In the embodiment, the rotor support member 22 includes a rotor holding portion 25 that holds the rotor Ro and a radially extending portion 26. The rotor holding portion 25 is arranged coaxially with the axis X and formed in the shape of a cylinder having an outer peripheral portion contacting the inner peripheral surface of the rotor Ro and flange portions contacting both side surfaces of the rotor Ro in the axial direction L. The radially extending portion 26 is integrally formed with the rotor holding portion 25 and formed to extend from a portion of the rotor holding portion 25 with respect to the center portion of the rotor holding portion 25 in the axial direction L on the first axial direction L1 side in the radially inward direction R1.The radially extending portion 26 is formed as a ring plate-like portion extending in the circumferential direction in addition to the radial direction R. In the embodiment, the radially extending portion 26 is formed to extend parallel to the radial direction R such that an end portion of the radially extending portion 26 on the radially inward direction R1 side is located on the radially outward direction R2 side with respect to the outer peripheral surface of the first tubular projecting portion 40. In the embodiment, as shown in FIG. Fig. 3, a first bushing member 94 is disposed in a gap in the radial direction R between an end portion of the radially extending portion 26 on the radially inward direction R1 side (in the example, the inner peripheral surface of a second axially extending portion 24, which will be described later) and the outer peripheral surface of the first tubular projecting portion 40. The first bushing member 94 is provided for retaining a passage of oil in the axial direction L through the gap.

[0048] The radially extending portion 26 has a first axially protruding portion 23, which is a tubular protruding portion protruding toward the first axial direction L1 side. The first axially protruding portion 23 is arranged coaxially with the axis X. In the embodiment, the first axially protruding portion 23 is formed integrally with the radially extending portion 26 at an end portion of the radially extending portion 26 on the radially inward direction R1 side. As shown in Fig. 3, the first axially protruding portion 23 is disposed in the radial direction R between the first tubular protruding portion 40 and the second tubular protruding portion 41 and at a position where the first axially protruding portion 23 partially overlaps the second tubular protruding portion 41 as viewed in the radial direction R. A space partitioned by an outer peripheral surface 23c of the first axially protruding portion 23 and the inner peripheral surface 41b of the second tubular protruding portion 41 on both sides in the radial direction R and partitioned by the radially extending portion 26 and the first support wall portion 31 (the inner peripheral step portion 41d of the second tubular protruding portion 41) on both sides in the axial direction L serves as a bearing arrangement space for placing a fifth bearing 75, which will be discussed later.In the embodiment, the first axially protruding portion 23 corresponds to the “axially protruding portion” according to the present invention.

[0049] The radially extending portion 26 also includes a second axially protruding portion 24, which is a tubular protruding portion protruding toward the second axial direction L2 side. The second axially protruding portion 24 is arranged coaxially with the axis X. In the embodiment, the second axially protruding portion 24 is formed integrally with the radially extending portion 26 at an end portion of the radially extending portion 26 on the radially inward direction R1 side. As shown in Fig. 3, a distal end portion 24a of the second axially projecting portion 24 is disposed on the second axial direction L2 side with respect to the distal end portion 40a of the first tubularly projecting portion 40 on the second axial direction L2 side.

[0050] A plate-like member 27 is fixed to the rotor support member 22. The plate-like member 27 is formed as a ring plate-like member extending in the circumferential direction in addition to the radial direction R. In the embodiment, as shown in Fig. 3, the plate-like member 27 is provided such that the outer peripheral surface of the plate-like member 27 is fitted (in this example, by spline engagement) into the inner peripheral surface of a portion of the rotor holding portion 25 on the second axial direction L2 side with respect to the central portion of the rotor holding member 25 in the axial direction L. This allows the plate-like member 27 to rotate together with the rotor support member 22. An inner peripheral step portion 25d having a surface (in this example, an annular surface) facing the second axial direction L2 side is formed on the inner peripheral surface of the rotor holding portion 25.With the inner peripheral step portion 25d serving as the boundary, a region on the second axial direction L2 side with respect to the inner peripheral step portion 25d is defined as a large diameter region, and a region on the first axial direction L1 side with respect to the inner peripheral step portion 25d is defined as a small diameter region. A snap ring 93 is held on a portion of the inner peripheral surface of the rotor holding portion 25 that is located opposite to the inner peripheral step portion 25d in the axial direction L with respect to the outer peripheral surface of the plate-like member 27. The plate-like member 27 fixed to the rotor holding portion 25 is prevented from moving in the first axial direction L1 by the inner peripheral step portion 25d and from moving in the second axial direction L2 by the snap ring 93, while allowing some movement with respect to the rotor holding portion 25 in the axial direction L. Fig. 3 shows a state in which a gap in the axial direction L (a fourth gap D4) is provided between the plate-like member 27 and the snap ring 93 with the plate-like member 27 abutting against a surface of the inner peripheral step portion 25d facing the second axial direction L2 side.

[0051] In the embodiment, the plate-like member 27 is shaped such that a portion on the radially inward direction R1 side is offset in the axial direction L to be located on the second axial direction L2 side with respect to a portion on the radially outward direction R2 side. A thick-walled portion 28 is formed at an end portion of the plate-like member 27 on the radially inward direction R1 side. The thick-walled portion 28 has a large thickness in the axial direction L compared to a portion of the plate-like member 27 on the radially outward direction R2 side. An outer peripheral step portion 28d having a surface (in this example, an annular surface) facing the second axial direction L2 side is formed on an outer peripheral surface 28c of the thick-walled portion 28.With the outer peripheral step portion 28d serving as the boundary, a region on the first axial direction L1 side with respect to the outer peripheral step portion 28d is defined as a large diameter region, and a region on the second axial direction L2 side with respect to the outer peripheral step portion 28d is defined as a small diameter region. The outer peripheral step portion 28d of the plate-like member 27 is arranged on the first axial direction L1 side of the second support wall portion 32 with respect to the inner peripheral step portion 32d.A space partitioned by the outer peripheral surface 28c of the thick-walled portion 28 of the plate-like member 27 and the inner peripheral surface 32b of the second support wall portion 32 on both sides in the radial direction R and partitioned by the outer peripheral step portion 28d of the plate-like member 27 and the inner peripheral step portion 32d of the second support wall portion 32 on both sides in the axial direction L serves as a bearing arrangement space for arranging a seventh bearing 77, which will be described later. 2-3. First clutch

[0052] The first clutch C1 is a device provided in a power transmission path between the input shaft I and the rotor member 21 and capable of changing the engagement state. That is, the first clutch C1 can switch the engagement state between two engagement members to be engaged with the first clutch C1, between a state in which the two engagement members are engaged with each other (including a slip engagement state) and a state in which the two engagement members are not engaged with each other (disengaged from each other). A driving force is transmitted between the input shaft I and the rotor member 21 when the two engagement members are engaged with each other. No driving force is transmitted between the input shaft I and the rotor member 21 when the two engagement members are disengaged from each other.

[0053] As it is in Fig. 3, the first clutch C1 is arranged in the axial direction L between the radially extending portion 26 and the plate-like member 27. The first clutch C1 is arranged on the radially inward direction R1 side with respect to the rotor Ro and at a position where the first clutch C1 partially overlaps the rotor Ro as viewed in the radial direction R. In the embodiment, the first clutch C1 is arranged at a position in the axial direction L where the first clutch C1 overlaps the central region of the rotor Ro in the axial direction L as viewed in the radial direction R.

[0054] In the embodiment, the first clutch C1 includes a clutch hub 51, a friction member 53, and a piston 54, and is configured as a wet multi-disk clutch mechanism. In the embodiment, the rotor support member 25 of the rotor support member 22 functions as a clutch drum. The first clutch C1 includes a pair of an input-side friction member and an output-side friction member as the friction member 53. The input-side friction member is held from the radially inward direction R1 side by the outer peripheral portion of the clutch hub 51. The output-side friction member is held from the radially outward direction R2 side by the inner peripheral portion of the rotor support portion 25.

[0055] A portion of the clutch hub 51 excluding the portion for holding the friction member 53 is formed as a ring plate-like portion extending in the radial direction R and the circumferential direction. An end portion of the ring plate-like portion on the radially inward direction R1 side is coupled (welded in this case) to a flange portion 1a of the input shaft I. Oil discharged from the oil pump 9 is supplied to a space partitioned by the radially extending portion 26 and the plate-like member 27 on both sides in the axial direction L and partitioned by the rotor holding portion 25 on the radially outward direction R2 side, for cooling the friction member 53. 2-4. Torque converter

[0056] As it is in Fig. As shown in FIG. 2, the torque converter TC is arranged coaxially with the rotary electric machine MG on the first axial direction L1 side with respect to the rotary electric machine MG. The torque converter TC is arranged between the first support wall portion 31 and the third support wall portion 33 in the axial direction L. The torque converter TC includes a clutch input member 2 drivingly coupled to the rotor member 21 of the rotary electric machine MG and a clutch output member 4 drivingly coupled to the wheels W.

[0057] As it is in Fig. 2, the torque converter TC includes the pump impeller 61, a turbine impeller 62, a second clutch C2 serving as a lock-up clutch, and a cover portion 63 housing these components. The cover portion 63 is coupled to rotate together with the pump impeller 61 disposed in the cover portion 63. As discussed above, the pump drive shaft 67 is coupled to the cover portion 63 to rotate together with the cover portion 63. In the embodiment, the clutch input member 2 is formed of the pump impeller 61, the cover portion 63, and the pump drive shaft 67. In the embodiment, as will be discussed in detail later, the clutch input member 2 is drivingly coupled to the rotor member 21 via a clutch member 10.In the embodiment, as will be discussed later, the clutch input member 2 and the rotor member 21 are drivingly coupled to each other so as to be movable relative to each other in the axial direction.

[0058] The clutch output component 4 is formed from the turbine runner 62. The turbine runner 62 is drivingly coupled to the intermediate shaft M. Consequently, as shown in Fig. 1, the clutch output member 4 is drivingly coupled to the wheels W via the intermediate shaft M, the speed change mechanism TM, the output shaft O, and the output differential gear device DF. In the embodiment, the turbine impeller 62 and the intermediate shaft M are drivingly coupled to each other by a spline fit so that they are movable relative to each other in the axial direction L and move together with each other with a little clearance (play) in the circumferential direction.

[0059] As it is in Fig. 3, the cover portion 63 includes a radially extending cover portion 65 provided on the first axial direction L1 side with respect to the first support wall portion 31 to extend in the radial direction R, and a tubular projecting cover portion 64 in the shape of a tube that projects toward the second axial direction L2 side from the radially extending cover portion 65 (in the example, an end portion of the radially extending cover portion 65 on the radially inward direction R1 side). The radially extending cover portion 65 is formed to extend in the radially outward direction R2 from an end portion of the tubular projecting cover portion 64 on the first axial direction L1 side.In the example, the radially extending cover portion 65 is formed as a ring plate-like portion extending in the circumferential direction in addition to the radial direction R. A thick-walled portion 66 is formed at a portion of the radially extending cover portion 65 on the tubularly projecting cover portion 64 side. The thick-walled portion 66 has a large thickness in the axial direction L compared with a portion of the radially extending cover portion 65 on the radially outward direction R2 side. The tubularly projecting cover portion 64 is arranged coaxially with the axis X. First spline teeth 91 extending in the axial direction L are formed on the outer peripheral surface (in this example, at only a portion of the outer peripheral surface on the base end side) of the tubularly projecting cover portion 64.A fastening hole 64e for fastening a fastening member 90 is formed in a portion of the tubular protruding cover portion 64 on the radially inward direction R1 side. In the embodiment, the radially extending cover portion 65 and the tubular protruding cover portion 64 are integrally formed with each other.

[0060] As it is in Fig. 3, the radially extending cover portion 65 is disposed away from the first support wall portion 31 so that a gap in the axial direction L is formed between the first support wall portion 31 and the radially extending cover portion 65. A gap in the axial direction L between a side surface portion of the radially extending cover portion 65 on the second axial direction L2 side and a side surface portion of the first support wall portion 31 on the first axial direction L1 side serves as a bearing arrangement space for arranging a first bearing 71 to be discussed later. More specifically, the step portion 40d, as described above, is formed on a side surface portion of the first tubular projecting portion 40 of the first support wall portion 31 on the first axial direction L1 side.A step portion 66d having a surface (in this example, a cylindrical surface) facing toward the radially outward direction R2 side is formed on a side surface portion of the radially extending cover portion 65 on the second axial direction L2 side, which is located on the radially inward direction R1 side with respect to the step portion 40d. In the example, the step portion 66d is formed on the thick-walled portion 66 of the radially extending cover portion 65.A space partitioned by the step portion 40d of the first support wall portion 31 (more precisely, the first tubular protruding portion 40) and the step portion 66d of the radially extending cover portion 65 (more precisely, the thick-walled portion 66) on both sides in the radial direction R and partitioned by the first support wall portion 31 (more precisely, the first tubular protruding portion 40) and the radially extending cover portion 65 (more precisely, the thick-walled portion 66) on both sides in the axial direction L serves as a bearing arrangement space for arranging the first bearing 71, which will be discussed later. 2-5. Power transmission component

[0061] The power transmission member T is formed by coupling the rotor member 21 and the clutch input member 2 so that they rotate together. The term "together" means that a speed ratio between the input member 21 and the clutch input member 2 is determined to be a constant value. In the embodiment, the power transmission member T is formed by coupling the rotor member 21 and the clutch input member 2 so that they rotate together. In the embodiment, the rotor member 21 and the clutch input member 2 are coupled to each other via the coupling member 10, which will be discussed below. That is, in the embodiment, the power transmission member T is formed to include the rotor member 21, the clutch input member 2, and the clutch member 10.

[0062] As it is in Fig. 3, the coupling member 10 is configured to extend in the axial direction L through a location on the radially inward direction R1 side with respect to the first tubular projecting portion 40 to a location on the radially outward direction R2 side with respect to the first tubular projecting portion 40 on the second axial direction L2 side with respect to the distal end portion 40a of the first tubular projecting portion 40. In other words, the coupling member 10 includes a radially extending coupling portion 12 provided on the second axial direction L2 side with respect to the first support wall portion 31 for extending in the radial direction R, and a tubular projecting coupling portion 11 formed in the shape of a tube projecting to the first axial direction L1 side from the radially extending coupling portion 12.The coupling tubular projecting portion 11 is disposed on the radially inward direction R1 side with respect to the first tubular projecting portion 40. The radially extending coupling portion 12 is formed to extend from an end portion of the coupling tubular projecting portion 11 on the second axial direction L2 side in the radially outward direction R2. In the example, the radially extending coupling portion 12 is formed as a ring plate-like portion extending in the circumferential direction in addition to the radial direction R. In the embodiment, the radially extending coupling portion 12 and the coupling tubular projecting portion 11 are integrally formed with each other. In the embodiment, the coupling member 10 constitutes the "coupling portion" according to the present invention.

[0063] The tubular projecting coupling portion 11 is arranged coaxially with the axis X. Second spline teeth 92 extending in the axial direction L are formed on the inner peripheral surface (in this example, only on a portion on the inner peripheral surface on the distal end side) of the tubular projecting coupling portion 11. The second spline teeth 92 are configured to engage with the first spline teeth 91 formed on the outer peripheral surface of the tubular projecting cover portion 64. As shown in Fig. 3, the cover portion 63 and the clutch member 10 are coupled to each other by spline fitting through the spline teeth 91 and 92, with the inner peripheral surface of the tubular projecting portion 11 externally fitted with the outer peripheral surface of the tubular projecting cover portion 64. That is, the cover portion 63 (the clutch input member 2) and the clutch member 10 are coupled to each other so as to rotate together with each other. The tubular projecting cover portion 64 and the tubular projecting clutch portion 11, which are coupled to each other by spline fitting, constitute an axially extending portion 5 of the power transmission member T, which extends in the axial direction L through a location on the radially inward direction R1 side with respect to the first support wall portion 31.

[0064] The tubular projecting cover portion 64 and the tubular projecting coupling portion 11 are splined to each other by the spline teeth 91 and 92 extending in the axial direction L. Consequently, relative movement in the axial direction L between the radially extending cover portion 65, which is integrally formed with the tubular projecting cover portion 64, and the radially extending coupling portion 12, which is integrally formed with the tubular projecting coupling portion 11, is not hindered by the spline coupling.In this regard, in the embodiment, in order for the first support wall portion 31 (more precisely, the first tubular protruding portion 40) to block both movement of the clutch input member 2 in the first axial direction L1 and movement of the clutch input member 2 in the second axial direction L2, the radially extending cover portion 65 and the radially extending clutch portion 12, which are arranged on respective sides in the axial direction L to the first tubular protruding portion 40, are configured to be coupled to each other via the axially extending portion 5, wherein relative movement in the axial direction L between the radially extending cover portion 65 and the radially extending clutch portion 12 is blocked. Such an arrangement is achieved by providing a movement blocking mechanism MR, which will be described below.

[0065] The movement blocking mechanism MR is a mechanism that blocks relative movement in the axial direction L between the tubular projecting cover portion 64 and the tubular projecting coupling portion 11. In the embodiment, as shown in Fig. 3, an end surface (a distal end portion 11a) of the tubular projecting coupling portion 11 on the first axial direction L1 side abuts against the radially extending cover portion 65 (in the example, the thick-walled portion 66), and a surface of the fixing member 90 fixed to the tubular projecting cover portion 64 facing the first axial direction L1 side abuts against a surface of the tubular projecting coupling portion 11 facing the second axial direction L2 side, thereby forming the movement blocking mechanism MR. More specifically, in the embodiment, an inner peripheral step portion 11d having a surface (in this example, an annular surface) facing the second axial direction L2 side is formed on the inner peripheral surface of the tubular projecting coupling portion 11.The fastening member 90 (in this example, a fastening bolt) has a ring portion (in this example, a bolt head portion of a flanged bolt) protruding toward the radially outward direction R2 side with respect to the outer peripheral surface of the tubular protruding cover portion 64, and the fastening member 90 is fixed to the fixing hole 64e of the tubular protruding cover portion 64. The ring portion of the fastening member 90 abuts against a surface of the inner peripheral step portion 11d facing the second axial direction L2 side, thereby forming the movement blocking mechanism MR.

[0066] The radially extending coupling portion 12 is coupled to the rotor support member 22 at a location on the radially outward direction R2 side with respect to the first tubular protruding portion 40. In the embodiment, an end portion of the radially extending coupling portion 12 on the radially outward direction R2 side and an end portion (the distal end portion 24a) of the second axially protruding portion 24 of the rotor support member 22 on the second axial direction L2 side are coupled (engaged) to be relatively movable in the axial direction L and rotate together with each other.Specifically, an end portion of the radially extending coupling portion 12 on the radially outward direction R2 side is formed as an externally toothed engaging portion in which a plurality of engaging pieces projecting toward the radially outward direction R2 side are distributed in the circumferential direction. The distal end portion 24a of the second axially projecting portion 24 is formed as a cylindrical engaging portion in which a plurality (the same number as engaging pieces) of through holes extending in the radial direction R and having a width in the circumferential direction and a length in the axial direction L such that they allow insertion of the engaging pieces are distributed in the circumferential direction.In the example, the through holes are formed as through holes formed in a U-shape as viewed in the radial direction, which open in an end edge of the second axially protruding portion 24 on the second axial direction L2 side and whose length in the axial direction L is longer than the engagement parts. Such a toothed engagement mechanism couples the second axially protruding portion 24 and the radially extending clutch portion 12 so that they are relatively movable in the axial direction L and rotate together with each other. As a result, the rotor member 21 and the radially extending clutch portion 12, in other words, the rotor member 21 and the clutch input member 2, are drivingly coupled to each other so that they are relatively movable in the axial direction.

[0067] The outer peripheral surface of the coupling tubular protruding portion 11 is disposed on the radially inward direction R1 side with respect to the inner peripheral surface 40b of the first tubular protruding portion 40. A gap in the radial direction between the outer peripheral surface of the coupling tubular protruding portion 11 and the inner peripheral surface 40b of the first tubular protruding portion 40 serves as a bearing arrangement space for arranging a sixth bearing 76, which will be discussed later. A second bushing member 95 is disposed in a portion of the gap on the second axial direction L2 side with respect to the sixth bearing 76. The second bushing member 95 is provided for blocking a passage of oil in the radial direction L through the gap.

[0068] The radially extending coupling portion 12 is arranged with its side surface portion on the first axial direction L1 side located on the second axial direction L2 side with respect to the distal end portion 40a of the first tubular protruding portion 40, so that a gap in the axial direction L is formed between the distal end portion 40a and the side surface portion of the radially extending coupling portion 12. A gap in the axial direction L between the side surface portion of the radially extending coupling portion 12 on the first axial direction L1 side and the distal end portion 40a of the first tubular protruding portion 40 serves as a bearing arrangement space for arranging a second bearing 72, which will be discussed later.In the embodiment, a step portion 12d having a surface (in this example, a cylindrical surface) facing the radially inward direction R1 side is formed on a side surface portion of the radially extending coupling portion 12 on the first axial direction L1 side. The second sleeve member 95 is arranged to partially protrude to the second axial direction L2 side with respect to the distal end portion 40a of the first tubular projecting portion 40. In the embodiment, the bearing arrangement space for arranging the second bearing 72 is formed as a space partitioned by the step portion 12d of the radially extending coupling portion 12 and the outer peripheral surface of the second sleeve member 95 on both sides in the radial direction R. 3. Support structure of various individual components

[0069] Next, for the purpose of describing the support structure for various individual components of the vehicle drive device 1 according to the embodiment, the support structure for the power transmission member T will be mainly described. 3-1. Support structure in the radial direction

[0070] As it is in the Fig. 2 and Fig. 3, the vehicle drive device 1 includes the fifth bearing 75 and the seventh bearing 77 as bearings that support the rotor member 21 in the radial direction R. The rotor member 21 is supported in the radial direction R by the fifth bearing 75 and the seventh bearing 77 on respective sides in the axial direction L. The fifth bearing 75 is a bearing that supports the rotor member 21 in the radial direction R so as to be rotatable with respect to the first support wall portion 31. A radial bearing (a ball bearing in the example) that can bear a load in the radial direction R is used as the fifth bearing 75. The seventh bearing 77 is a bearing that supports the rotor member 21 in the radial direction R so as to be rotatable with respect to the second support wall portion 32. A radial bearing (in this example a ball bearing) that can support a load in the radial direction R is used as the fifth bearing 75.In the embodiment, the fifth bearing 75 corresponds to the “first bearing” according to the present invention.

[0071] In the embodiment, the fifth bearing 75 is arranged on the radially outward direction R2 side with respect to the first tubular protruding portion 40 of the first support wall portion 31. More specifically, the fifth bearing 75 is arranged to contact the inner peripheral surface 41b of the second tubular protruding portion 41 of the first support wall portion 31 and the outer peripheral surface 23c of the first axially protruding portion 23 of the rotor support member 22. Thereby, the rotor member 21 can be supported by the inner peripheral surface 41b of the second tubular protruding portion 41 via the fifth bearing 75. In this way, in the embodiment, the outer peripheral surface 23c of the first axially protruding portion 23 serves as a supported portion supported with respect to the first support wall portion 31 by the fifth bearing 75. In the example shown in Fig. 3, the fifth bearing 75 is arranged to contact a surface of the inner peripheral step portion 41d of the second tubular protruding portion 41 facing the second axial direction L2 side. As shown in Fig. 3, the first clutch C1 is arranged at a position where the first clutch C1 partially overlaps the fifth bearing 75 as viewed in the axial direction L. More specifically, a portion of the clutch hub 51 on the radially outward direction R2 side and a portion of the friction member 53 supported by the clutch hub 51 on the radially inward direction R1 side in the radial direction R are arranged at the same position as the fifth bearing 75.

[0072] In the embodiment, the seventh bearing 77 is arranged on the radially inward direction R1 side with respect to the fifth bearing 75. More specifically, the seventh bearing 77 is arranged at a position where the seventh bearing 77 partially overlaps the first tubular projecting portion 40 as viewed in the axial direction L. More specifically, the seventh bearing 77 is arranged to contact the inner peripheral surface 32b of a portion of the second support wall portion 32 on the radially inward direction R1 side and the outer peripheral surface 28c of the thick-walled portion 28 of the plate-like member 27 fixed to the rotor support member 22. This allows the rotor member 21 to be supported by the inner peripheral surface 32b of the second support wall portion 32 via the plate-like member 27 and the seventh bearing 77.In this way, the seventh bearing 77 supports the power transmission member T formed from the rotor member 21 in the radial direction R so as to be rotatable relative to the second support wall portion 32. In the example, the seventh bearing 77 is indirectly supported in the radial direction R via the plate-like member 27.

[0073] In the embodiment, the seventh bearing 77 is press-fitted (tightly fitted) to the inner peripheral surface 32b of the second support wall portion 32 and fixed to the second support wall portion 32 with the seventh bearing 77 abutting against a surface facing the first axial direction L1 side of the inner peripheral step portion 32d formed on the inner peripheral surface 32b. On the other hand, the seventh bearing 77 is fitted (loosely fitted) on the outer peripheral surface 28c of the thick-walled portion 28 of the plate-like member 27, allowing some movement of the seventh bearing 77 in the axial direction L. Fig. 3 illustrates a state in which the plate-like member 27 is slightly moved in the first axial direction L1 from a position where the plate-like member 27 abuts against the seventh bearing 77, and a gap in the axial direction L (a third gap D3) is present between a surface facing the second axial direction L2 side of the outer peripheral step portion 28d formed on the outer peripheral surface 28c of the thick-walled portion 28 and the seventh bearing 77.

[0074] In the embodiment, an eighth bearing 78 (in the example, a needle bearing) is arranged on the radially inward direction R1 side with respect to the seventh bearing 77 for supporting the input shaft I in the radial direction R so as to be rotatable with respect to the second support wall portion 32. The eighth bearing 78 is arranged to contact the outer peripheral surface of the input shaft I and the inner peripheral surface of the thick-walled portion 28 of the plate-like member 27. The input shaft I is supported by the inner peripheral surface 32b of the second support wall portion 32 via the thick-walled portion 28 and the seventh bearing 77 in addition to the eighth bearing 78.

[0075] The vehicle drive device 1 has the sixth bearing 76 and the ninth bearing 79 (see Fig. 2) as bearings that support the clutch input component 2 in the radial direction R. The clutch input component 2 is supported in the radial direction R by the sixth bearing 76 and the ninth bearing 79 on respective sides in the axial direction L. As shown in Fig. 3, the sixth bearing 76 is a bearing that supports the clutch input member 2 in the radial direction R so as to be rotatable with respect to the first support wall portion 31. A radial bearing (in the example, a needle bearing) that can support a load in the radial direction R is used as the sixth bearing 76. In the embodiment, the sixth bearing 76 corresponds to the "second bearing" according to the present invention.

[0076] In the embodiment, the sixth bearing 76 is arranged on the radially inward direction R1 side with respect to the first tubular protruding portion 40 of the first support wall portion 31. More specifically, the sixth bearing 76 is arranged to contact the inner peripheral surface 40b of the first tubular protruding portion 40 and the outer peripheral surface of the clutch tubular protruding portion 11. This allows the clutch input member 2 to be supported via the clutch member 10 through the inner peripheral wall 40b of the first tubular protruding portion 40, which is coupled to rotate together with the clutch input member 2 and fixed by the movement blocking mechanism MR to be relatively immovable in the axial direction L.

[0077] As described above, the fifth bearing 75 is arranged on the radially outward direction R2 side with respect to the first tubular protruding portion 40 of the first support wall portion 31, and the sixth bearing 76 is arranged on the radially inward direction R1 side with respect to the first tubular protruding portion 40 of the first support wall portion 31. That is, the fifth bearing 75 and the sixth bearing 76 are arranged at different positions from each other in the radial direction R. In the embodiment, the sixth bearing 76 is arranged at a position where the sixth bearing 76 partially overlaps the fifth bearing 75 as viewed in the radial direction R.More specifically, the sixth bearing 76 is slightly shifted in the second axial direction L2 with respect to the fifth bearing 75 such that a portion of the sixth bearing 76 on the first axial direction L1 side is at the same position in the axial direction L as a portion of the fifth bearing 75 on the second axial direction L2 side. 3-2. Support structure in axial direction

[0078] As it is in the Fig. 2 and Fig. 3, the vehicle drive device 1 includes the first bearing 71 and the second bearing 72 as bearings that support the power transmission member T in the axial direction L with respect to the first support wall portion 31. The first bearing 71 is a bearing that supports the power transmission member T from the second axial direction L2 side so as to be rotatable with respect to the first support wall portion 31. A bearing (in this example, a thrust bearing) that can receive a load in the axial direction L is used as the first bearing 71. The second bearing 72 is a bearing that supports the power transmission member T from the first axial direction L1 side so as to be rotatable with respect to the first support wall portion 31. A bearing (in this example, a thrust bearing) that can receive a load in the axial direction L is used as the second bearing 72.

[0079] In the embodiment, the first bearing 71 and the second bearing 72 support the clutch input member 2 and the clutch member 10, which are fixed so as not to be movable relative to each other in the axial direction L, among the members constituting the power transmission member T, with respect to the first support wall portion 31. More specifically, as shown in Fig. 3, the first bearing 71 supports the radially extending cover portion 65 from the second axial direction L2 side, and the second bearing 72 supports the radially extending coupling portion 12 from the first axial direction L1 side. As will be discussed later, each of the first bearing 71 and the second bearing 72 is configured not to prevent relative movement of components arranged on both sides in the axial direction L in directions away from each other in the axial direction L.

[0080] Like it Fig. 3, the first bearing 71 is disposed at a location where the first support wall portion 31 and the radially extending cover portion 65 face each other in the axial direction L. More specifically, the first bearing 71 is disposed at a location where a side surface portion of the first tubular protruding portion 40 of the first support wall portion 31 on the first axial direction L1 side and a side surface portion of the thick-walled portion 66 of the radially extending cover portion 65 on the second axial direction L2 side face each other. In the embodiment, facing portions are arranged in a space partitioned by the step portion 40d of the first tubular protruding portion 40 and the step portion 66d of the thick-walled portion 66 on both sides in the radial direction R.The first bearing 71 is fitted (loosely fitted) with some movement clearance in the axial direction L with respect to at least one surface of the stepped portion 66d of the thick-walled portion 66 facing the radially outward direction R2 side and one surface of the stepped portion 40d of the first tubular protruding portion 40 facing the radially inward direction R1 side. Thus, the first bearing 71 does not prevent movement of the clutch input member 2 in the first axial direction L1 with respect to the first support wall portion 31. Fig. 3 illustrates a state in which the clutch input member 2 is slightly moved in the first axial direction L1 from a state in which no gap (space) is provided in the axial direction L at the location where the first bearing 71 is arranged, so that a gap in the axial direction L (a first gap D1) is present between a side surface portion of the first tubular projecting portion 40 on the first axial direction L1 side and the first bearing 71.

[0081] As it is in Fig. 3, the second bearing 72 is disposed at a location where the first support wall portion 31 and the radially extending coupling portion 12 face each other in the axial direction L. More specifically, the second bearing 72 is disposed at a location where the distal end portion 40a of the first tubular projecting portion 40 of the first support wall portion 31 and a side surface portion of the radially extending coupling portion 12 on the first axial direction L1 side face each other. In the embodiment, the facing portions are arranged in a space partitioned by the step portion 12d of the radially extending coupling portion 12 and the outer peripheral surface of the second sleeve member 95 on both sides in the radial direction R.The second bearing 72 is fitted (loosely fitted) with some clearance in the axial direction L with respect to at least one of the surface of the stepped portion 12d of the radially extending clutch portion 12 facing the radially inward direction R1 side and the outer peripheral surface of the second bushing member 95. Thus, the second bearing 72 does not prevent movement of the clutch member 10 in the second axial direction L2 with respect to the first support wall portion 31. Fig. 3 illustrates a state in which no gap is provided in the axial direction L at the location where the second bearing 72 is arranged and the second bearing 72 contacts both the distal end portion 40a of the first tubular projecting portion 40 and the side surface portion of the radially extending coupling portion 12 on the first axial direction L1 side.

[0082] Further, in the embodiment, a third bearing 73 (in the example, a thrust bearing) capable of supporting a load in the axial direction L is disposed in the axial direction between the radially extending clutch portion 12 and the flange portion 1a of the input shaft I, and a fourth bearing (in this example, a thrust bearing) capable of supporting a load in the axial direction L is disposed in the axial direction L between the flange portion 1a of the input shaft I and the thick-walled portion 28 of the plate-like member 27. Each of the third bearing 73 and the fourth bearing 74 is also configured not to prevent relative movement of members disposed on both sides in the axial direction L in directions away from each other in the axial direction L. Fig. 3 illustrates a state in which no gap is provided in the axial direction L at the location where the third bearing 73 is arranged, and a gap in the axial direction L (a second gap D2) is present between the fourth bearing 74 and the thick-walled portion 28 at a location where the fourth bearing 74 is arranged.

[0083] In the embodiment shown in Fig. 3, the first bearing 71 is arranged to partially overlap the second bearing 72 as viewed in the axial direction L. In the embodiment, the first bearing 71 is further arranged to partially overlap the third bearing 73, the fourth bearing 74, and the seventh bearing 77 as viewed in the axial direction L. In the example, the first bearing 71, the second bearing 72, the third bearing 73, the fourth bearing 74, and the seventh bearing 77 are arranged so that there is a location in the radial direction R included in each of a region in the radial direction R in which the first bearing 71 is arranged, a region in the radial direction R in which the second bearing 72 is arranged, a region in the radial direction R in which the third bearing 73 is arranged, a region in the radial direction R in which the fourth bearing 74 is arranged, and a region in the radial direction R in which the seventh bearing 77 is arranged.

[0084] In the case where there is a speed difference between the pump impeller 61 and the turbine impeller 62 of the torque converter TC, the speed difference causes an attractive force that brings the pump impeller 61 and the turbine impeller 62 closer to each other. In this case, since the turbine impeller 62 is drivingly coupled to the intermediate shaft M so that they are relatively movable in the axial direction L, substantially no load in the axial direction acts on the pump impeller 61. However, in some cases, movement of the turbine impeller 62 in the first axial direction L1 may be hindered, and a large load in the second axial direction L2 may act on the pump impeller 61.

[0085] In the embodiment, a load in the second axial direction L2 that may act on the pump impeller 61 is thus mainly supported by the first bearing 71, which is a thrust bearing. This makes it possible to prevent a large load in the axial direction from acting on the seventh bearing 77, which is a radial bearing, making it possible to use a small bearing as the seventh bearing 77 compared to a case where a large load in the axial direction acts on the seventh bearing 77. Such an arrangement is achieved by setting the total sum (hereinafter referred to as a "first total sum S1") of gaps.Gaps in the axial direction L existing between the radially extending cover portion 65 and the first support wall portion 31 are set to be smaller than the total sum (hereinafter referred to as a “second total sum S2”) of gaps in the axial direction L existing between the radially extending coupling portion 12 and the second support wall portion 32. The first total sum S1 is determined by the gaps when the radially extending cover portion 65 is arranged at the outermost end of the movement range of the radially extending cover portion 65 in the axial direction L on the first axial direction L1 side. The second total sum S2 is determined by the gaps when the radially extending coupling portion 12 is arranged at the outermost end of the movement range of the radially extending coupling portion 12 in the axial direction L on the first axial direction L1 side.

[0086] More specifically, in the embodiment, the rotor member 21 and the radially extending cover portion 65 (the clutch input member 2) are drivingly coupled to each other so as to be movable relative to each other in the axial direction L. Thus, a load in the second axial direction L2 acting on the pump impeller 61 is hardly transmitted to the rotor member 21. In this case, as is apparent from Fig. 3, it is necessary that the load in the axial direction should be supported by at least one of the first bearing 71, the second bearing 72, the third bearing 73, the fourth bearing 74, and the seventh bearing 77. That is, in the embodiment, the gaps contributing to the first total S1 include only a gap in the axial direction L at the location where the first bearing 71 is arranged. Meanwhile, the gaps contributing to the second total S2 include a gap in the axial direction L at the location where the second bearing 72 is arranged, a gap in the axial direction L at the location where the third bearing 73 is arranged, a gap in the axial direction L at the location where the fourth bearing 74 is arranged, and a gap in the axial direction L at the location where the seventh bearing 77 is arranged.Such gaps at the location where each bearing is arranged also include a gap present in the bearing that allows relative movement in the axial direction L between the components that make up the bearing.

[0087] A detailed description is given on the basis of Fig. 3 made. Fig. 3 illustrates a situation in which the clutch input member 2 and the clutch member 10, which are coupled to each other so as to be immovable relative to each other in the axial direction L, are arranged at the extreme end of the movable range in the axial direction L on the first axial direction L1 side. Consequently, there is no gap in the axial direction L at the location where the second bearing 72 is arranged, and there is a gap in the axial direction L (the first gap D1) at the location where the first bearing 71 is arranged. In this case, the first total sum S1 is "D1." Meanwhile, Fig. 3 illustrates a state where there is no gap in the axial direction L at the location where the third bearing 73 is arranged, a gap in the axial direction L (the second gap D2) is arranged at the location where the second bearing 72 is arranged, and a gap in the axial direction L (the third gap D3) is arranged at the location where the seventh bearing 77 is arranged. In this case, the second total S2 is "D2 + D3".

[0088] In the embodiment, the first total sum S1 is set to be smaller than the second total sum S2 (D1 < D2 + D3). Thus, even in the case where a large load in the second axial direction L2 acts on the pump impeller 61, the gap in the axial direction L existing between the radially extending cover portion 65 and the first support wall portion 31 disappears before the gap in the axial direction L existing between the radially extending coupling portion 12 and the second support wall portion 32 disappears. Consequently, such a load can be absorbed by the first bearing 71 for preventing a large load in the axial direction from acting on the seventh bearing 77.

[0089] In the embodiment, in order to prevent a large load in the second axial direction L2 acting on the pump impeller 61 from acting not only on the seventh bearing 77 but also on the snap ring 93 held on the rotor holding portion 25, the following structure is adopted. In this, the first total sum S1 is set to be in the range shown in Fig. 3 is smaller than the gap in the axial direction L (the fourth gap D4) between the plate-like component 27 and the snap ring 93. In Fig. 3, the rotor member 21 is arranged to contact the fifth bearing 75, and the plate-like member 27 is positioned at the outermost end of the movable range of the plate-like member 27 in the axial direction L on the first axial direction L1 side (at a position where the plate-like member 27 abuts against the inner peripheral step portion 25d). In this case, it is possible to further prevent a load in the axial direction L from acting on the snap ring 93 by designing various components to satisfy the relationship of "D4 > D2 + D3". 4. Further embodiments

[0090] Finally, vehicle drive devices according to other embodiments of the present invention will be described. A configuration disclosed in each of the following embodiments can be applied in combination with a configuration disclosed in any other embodiment as long as no inconsistency occurs. (1) In the embodiment described above, the rotor member 21 and the radially extending clutch portion 12 (the clutch input member 2) are drivingly coupled to each other so as to be movable relative to each other in the axial direction L. However, the present invention is not limited to this. The rotor member 21 and the clutch input member 2 may be drivingly coupled to each other so as to be immovable relative to each other in the axial direction L by coupling the clutch member 10 and the rotor support member 22 so as to be immovable relative to each other in the axial direction L. In this case, the clutch member 10 may also not be separate from (a separate member independent of) the rotor support member 22 and may be formed integrally with the rotor support member 22. In this case, the second sum total S2 in the Fig.3, the example “D3” and various areas are preferably constructed so that the relationship “D1 < D3” is maintained. (2) In the above-described embodiment, the clutch member 10 has the radially extending clutch portion 12 extending to a location on the radially outward direction R2 side with respect to the first tubular protruding portion 40, and the engagement portions of the clutch member 10 and the rotor support member 22 are arranged on the radially outward direction R2 side with respect to the first tubular protruding portion 40. However, the present invention is not limited to this. The rotor support member 22 may have a portion extending to a location on the radially inward direction R1 side with respect to the first tubular protruding portion 40, and the engagement portions of the clutch member 10 and the rotor support member 22 may be arranged on the radially inward direction R1 side with respect to the first tubular protruding portion 40.In this case, the coupling component 10 may also have only the tubular protruding coupling area 11. (3) In the above-described embodiment, the clutch member 10 is formed separately from the clutch input member 2. However, the present invention is not limited to this. The clutch member 10 may be formed integrally with the clutch input member 2. (4) In the above-described embodiment, the inner peripheral step portion 11d is formed on the inner peripheral surface of the tubular projecting coupling portion 11, and a surface facing the first axial direction L1 side of the fastening member 90 fixed to the tubular projecting cover portion 64 abuts against a surface of the inner peripheral step portion 11d facing the second axial direction L2 side, thereby forming the movement blocking mechanism MR. However, the present invention is not limited to this. The tubular projecting coupling portion 11 may not have the inner peripheral step portion 11d, and a surface of the fastening member 90 facing the first axial direction L1 side may abut against a surface facing the second axial direction L2 side of a base end portion of the tubular projecting coupling portion 11 on the second axial direction L2 side.The movement blocking mechanism MR may be a mechanism that blocks relative movement in the axial direction L between the tubular projecting cover portion 64 and the tubular projecting coupling portion 11 using a snap ring or the like. (5) In the above-described embodiment, the cover portion 63 and the coupling member 10 are coupled to each other by spline fitting, with the inner peripheral surface of the tubular projecting coupling portion being externally fitted with the outer peripheral surface of the tubular projecting cover portion 64. However, the present invention is not limited to this. The tubular projecting cover portion 64 may have spline teeth on its inner peripheral surface, the tubular projecting coupling portion 11 may have spline teeth on its outer peripheral surface, and the cover portion 63 and the coupling member 10 may be coupled to each other by spline fitting, with the inner peripheral surface of the tubular projecting cover portion 64 being externally fitted with the outer peripheral surface of the tubular projecting coupling portion 11. (6) In the above-described embodiment, the fifth bearing 75 is arranged on the radially outward direction R2 side with respect to the first tubular protruding portion 40, and the sixth bearing 76 is arranged on the radially inward direction R1 side with respect to the first tubular protruding portion 40. However, the present invention is not limited to this. The fifth bearing 75 and the sixth bearing 76 may both be arranged on the same side in the radial direction R with respect to the first tubular protruding portion 40. (7) In the above-described embodiment, the first clutch C1 is arranged at a position where the first clutch C1 partially overlaps the fifth bearing 75 as viewed in the axial direction L. However, the present invention is not limited to this. For example, the first clutch C1 may be arranged at a different position in the radial direction R from the fifth bearing 75 (for example, on the radially inward direction R1 side with respect to the fifth bearing 75) so that it does not partially overlap the fifth bearing 75 as viewed in the axial direction L. (8) In the embodiment described above, the first clutch C1 is arranged on the radially inward direction R1 side with respect to the rotor Ro and at a position where the first clutch C1 partially overlaps the rotor Ro as viewed in the radial direction R. However, the present invention is not limited to this. The first clutch C1 may be arranged on the first axial direction L1 side or on the second axial direction L2 side with respect to the rotor Ro so that it does not partially overlap the rotor Ro as viewed in the radial direction R. Alternatively, the first clutch C1 may be arranged on the radially outward direction R2 side with respect to the first clutch C1. (9) In the above-described embodiment, the sixth bearing 76 is arranged at a position where the sixth bearing 76 partially overlaps the fifth bearing 75 as viewed in the radial direction R. However, the sixth bearing 76 may also be arranged at a different position in the axial direction L from the fifth bearing 75 so that it does not partially overlap the fifth bearing 75 as viewed in the radial direction R. (10) In the above-described embodiment, an end portion of the radially extending coupling portion 12 on the radially outward direction R2 side is formed as an externally toothed engaging portion in which a plurality of engaging pieces projecting toward the radially outward direction R2 side are distributed in the circumferential direction, and the distal end portion 24a of the second axially projecting portion 24 is formed as a cylindrical engaging portion in which a plurality (the same number as the engaging pieces) of through holes extending in the radial direction R and having such a width in the circumferential direction and such a length in the axial direction L as to allow insertion of the engaging pieces are distributed in the circumferential direction. However, the present invention is not limited to this.For example, the distal end portion 24a of the second axially protruding portion 24 may be formed as an internally toothed portion in which a plurality of engagement pieces protruding toward the radially inward direction R1 side are distributed in the circumferential direction instead of the through holes. In such a configuration, unlike the above-described embodiment, the second axially protruding portion 24 also has, at the distal end portion 24a, a ring body portion extending continuously over the entire circumference. (11) In the above-described embodiment, the outer peripheral surface 23c of the first axially protruding portion 23 of the rotor support member 22 serves as a supported portion supported with respect to the first support wall portion 31 by the fifth bearing 75. However, the present invention is not limited to this. The fifth bearing 75 may also be arranged to contact the inner peripheral surface 23b of the first axially protruding portion 23 and the outer peripheral surface of the first support wall portion 31 (for example, the outer peripheral surface of the first tubular protruding portion 40). That is, the inner peripheral surface 23b of the first axially protruding portion 23 may be a supported portion supported with respect to the first support wall portion 31 by the fifth bearing 75.A portion of the rotor support member 22 other than the first axially protruding portion 23 (such as the inner peripheral surface of the second axially protruding portion 24) may be a supported portion supported by a bearing with respect to the first support wall portion 31. In this case, the rotor support member 22 may also not have a first axially protruding portion 23. (12) In the above-described embodiment, the first axially protruding portion 23 of the rotor support member 22 is formed at an end portion of the radially extending portion 26 on the radially inward direction R1 side. However, the present invention is not limited to this. The first axially protruding portion 23 may be formed at an intermediate portion of the radially extending portion 26 in the radial direction R (for example, on the radially outward direction R2 side with respect to the second tubular protruding portion 41). (13) In the above-described embodiment, the first bearing 71 and the second bearing 72 support the power transmission member T with respect to the first tubular protruding portion 40 of the first support wall portion 31. However, the present invention is not limited to this. At least one of the first bearing 71 and the second bearing 72 may support the power transmission member T with respect to a portion of the first support wall portion 31 having a uniform thickness in the axial direction L. In such a configuration, the first support wall portion 31 may not have the first tubular protruding portion 40. (14) In the above-described embodiment, the vehicle drive device 1 has a single-axle structure. However, the present invention is not limited to this. The vehicle drive device 1 may also be a drive device with a multi-axle configuration, for example, having a counter gear mechanism or the like. Such a configuration is suitable for mounting on FF (front-engine front-wheel drive) vehicles. (15) In the above-described embodiment, the vehicle drive device includes the input shaft I drivingly coupled to the internal combustion engine E and the first clutch C1. However, the present invention is not limited to this. The vehicle drive device 1 may also not include the input shaft I or the first clutch C1. (16) Regarding other configurations or arrangements, the embodiment disclosed here is exemplary in all respects, and the present invention is not limited thereto. That is, a configuration not described in the claims of the present invention may be modified without departing from the scope of the present invention. INDUSTRIAL APPLICABILITY

[0091] The present invention can be suitably applied to a vehicle drive device including a rotary electric machine, a fluid coupling arranged coaxially with the rotary electric machine, and a housing accommodating the rotary electric machine and the fluid coupling, the fluid coupling having a clutch input member drivingly coupled to a rotor member of the rotary electric machine and a clutch output member drivingly coupled to wheels. Description of reference symbols 1 vehicle drive device 2 clutch input component 3 housings 4 Clutch output component 10 Clutch component (clutch area) 21 Rotor component 22 Rotor support component 23 first axially protruding area (axially protruding area) 31 first retaining wall area (retaining wall area) 40 first tubular protruding portion (tubular protruding portion) 75 fifth camp (first camp) 76 sixth camp (second camp) C1 first clutch (engagement device) E internal combustion engine, I Input shaft (input component) L axial direction L1 first axial direction L2 second axial direction MG rotary electric machine R radial direction Ro Rotor (rotor body) TC torque converter (fluid coupling) In Rad

Claims

[1] A vehicle drive device (1) comprising a rotary electric machine (MG), a fluid coupling (TC) arranged coaxially with the rotary electric machine (MG) on a side of a first axial direction (L1) with respect to the rotary electric machine (MG), and a housing (3) accommodating the rotary electric machine (MG) and the fluid coupling (TC), wherein the side of the first axial direction (L1) is a side in an axial direction (L) with respect to the rotary electric machine (MG), and the fluid coupling (TC) has a clutch input member (2) drivingly coupled to a rotor member (21) of the rotary electric machine (MG), and a clutch output member (4) drivingly coupled to wheels (W), wherein: the housing (3) has a support wall portion (31) extending in a radial direction (R) of the rotary electric machine (MG) at a location in the axial direction (L) between the rotary electric machine (MG) and the fluid coupling (TC), and a first bearing (75) and a second bearing (76), which is separate from the first bearing (75), are arranged at mutually different positions in the radial direction (R), wherein the first bearing (75) is designed to support the rotor component (21) in the radial direction (R) such that it is rotatable with respect to the support wall region (31), and the second bearing (76) is designed to support the clutch input component (2) in the radial direction (R) such that it is rotatable with respect to the support wall region (31). [2] Vehicle drive device according to claim 1, wherein the support wall portion (31) has a tubular projecting portion (40) projecting to a side of a second axial direction (L2) which is an opposite side to the first axial direction (L1), and the first bearing (75) is arranged on an outer side in the radial direction (R) with respect to the tubular projecting portion (40) and the second bearing (76) is arranged on an inner side in the radial direction (R) with respect to the tubular projecting portion (40). [3] A vehicle drive device according to claim 1 or 2, further comprising: an input component (I) which is drivingly coupled to an internal combustion engine (E), and an engagement device (C1) provided in a power transmission path between the input member (I) and the rotor member (21) and capable of changing an engagement state, wherein the engagement device (C1) is arranged at a position where the engagement device (C1) partially overlaps the first bearing (75) as seen in the axial direction (L). [4] Vehicle drive device according to claim 3, wherein the rotor component (21) comprises a rotor body (Ro) and a rotor support component (22) extending inwardly from the rotor body (21) for supporting the rotor body (21) in the radial direction (R), and the engagement device (C1) is arranged on an inner side in the radial direction (R) with respect to the rotor body (Ro) and at a position where the engagement device (C1) partially overlaps the rotor body (Ro) as seen in the radial direction (R). [5] A vehicle drive device according to any one of claims 1 to 4, wherein the second bearing (76) is arranged at a position where the second bearing partially overlaps the first bearing (75) as viewed in the radial direction. [6] Vehicle drive device according to one of claims 1 to 5, in which the rotor component (21) comprises a rotor body (Ro) and a rotor support component (22) extending inwardly from the rotor body (Ro) for supporting the rotor body (Ro) in the radial direction (R), the rotor support member (22) has an axially projecting portion (23) which is a tubular projecting portion projecting to the side of the first axial direction (L1), and an outer peripheral surface or an inner peripheral surface of the axially projecting portion (23) serves as a supported portion supported with respect to the support wall portion (31) by the first bearing (75). [7] Vehicle drive device according to one of claims 1 to 6, wherein the rotor component (21) and the clutch input component (2) are drivingly coupled to one another so that they are movable relative to one another in the axial direction (L). [8] Vehicle drive device according to one of claims 1 to 7, in which the support wall portion (31) has a tubular projecting portion (40) projecting to a side of the second axial direction (L2) which is a side opposite to the first axial direction (L1), the tubular protruding portion (40) is arranged on an inner side in the radial direction (R) with respect to the rotor component (21) and at a position where the tubular protruding portion (40) partially overlaps the rotor component (21) as seen in the radial direction (R), the vehicle drive device (1) further comprises a coupling portion (10) extending in the axial direction (L) through a location on a radially inner side with respect to the tubular protruding portion (40) and extending on the second axial direction (L2) side with respect to a distal end portion of the tubular protruding portion (40) to a location with respect to the tubular protruding portion (40) in the radial direction (R) on an outer side, and the rotor component (21) and the clutch input component (2) are coupled to one another via the clutch region (10).

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