Vehicle drive device

Abstract

The present invention provides a vehicle drive device, in which a part of the first component is difficult to fall off through the opening of the rotor support component when a first component including a rotor, a rotor support component and a friction engagement device is assembled into a second component separated from the first component. In the vehicle drive device, a first engagement device (CL1) is arranged on the axial first side (L1) relative to a flange portion (22) and on the radial inner side (R1) relative to a cylindrical portion (21), a first outer support component is configured to open toward the axial first side and rotate integrally with the cylindrical portion, an annular component (10) formed into an annular shape extending along the circumferential direction is fixed to the inner peripheral portion of the cylindrical portion, and the annular component is arranged at a position that is on the axial first side relative to a first friction plate (412) and a second friction plate (411) and overlaps with at least one of the first piston portion and the second friction plate when viewed along the axial direction.

Description

Technical Field

[0001] The present invention relates to a vehicle drive device, which comprises: an input component connected to an internal combustion engine drive; a rotating electric machine having a stator and a rotor arranged radially inward relative to the stator and functioning as a driving force source for wheels; a power transmission mechanism that transmits the rotation transmitted from the rotating electric machine side to the wheel side; a rotor support component that supports the rotor; and a friction engagement device. Background Art

[0002] An example of such a vehicle drive device is disclosed in the following Patent Document 1. In the following description of the background art, reference numerals in Patent Document 1 are cited within parentheses.

[0003] In the vehicle drive device 1 of Patent Document 1, the rotor support member 30 includes: a cylindrical portion 31 formed in a cylindrical shape extending along the axial direction L, supporting the rotor Ro from the inner side R1 in the radial direction R; and a flange portion 35 formed to extend from the cylindrical portion 31 to the inner side R1 in the radial direction R, and arranged adjacent to the first engagement device CL1 on one side L2 in the axial direction L. That is, the rotor support member 30 is formed in a bottomed cylindrical shape that is open toward the other side L1 in the axial direction L. Furthermore, the first engagement device CL1 and the second engagement device CL2 as friction engagement devices are arranged on the one side L1 in the axial direction L relative to the flange portion 35 and on the inner side R1 in the radial direction R relative to the cylindrical portion 31.

[0004] Patent Document 1: International Publication No. 2017 / 057190 ( Figure 3 )

[0005] In the manufacturing process of the vehicle drive device 1 of patent document 1, the rotor Ro, the rotor support member 30, and the friction engagement devices CL1, CL2, etc. are assembled as a whole to form a first component. Thereafter, the first component is assembled into a second component that is separate from the first component. Generally, the assembly operation of the first component to the second component is performed in a state where the posture of the first component is maintained in such a manner that the rotation axis X of the rotor Ro is along the vertical direction. However, in a case where a component constituting a part of the first component is assembled so as to be relatively movable in the axial direction relative to the rotor support member 30, there is a case where a part of the first component falls off from the opening of the rotor support member 30 due to the deadweight of the component. Therefore, measures such as a clamp for preventing falling off need to be installed, which complicates the manufacturing process.

[0006] Therefore, it is desirable to realize a vehicle drive device having a structure in which, when a first assembly including a rotor, a rotor support member, and a friction engagement device is assembled into a second assembly separate from the first assembly, a portion of the first assembly can be restricted from falling off through an opening of the rotor support member. Summary of the invention

[0007] In view of the above situation, the characteristic structure of the vehicle drive device is that it has: an input member connected to the internal combustion engine; a rotating electric machine having a stator and a rotor arranged radially inward relative to the stator, and functioning as a driving force source for the wheel; a power transmission mechanism that transmits the rotation transmitted from the rotating electric machine side to the wheel side; a rotor support member that supports the rotor; and a first engaging device having a first friction plate and a second friction plate arranged in parallel in the axial direction, and a first movable member that pushes the first friction plate and the second friction plate in the axial direction. The plug portion, the first engaging device is arranged in the power transmission path between the input member and the rotating electric machine, and in the vehicle drive device, it also comprises: a first outer supporting member, which supports the first friction plate from the radial outer side; and a first inner supporting member, which supports the second friction plate from the radial inner side, and the first inner supporting member comprises: a cylindrical supporting portion, which is formed into a cylindrical shape extending along the axial direction, and supports the second friction plate; and a radially extending supporting portion, which extends from the cylindrical supporting portion to the radial inner side. The radially extending support portion is connected to the input member in such a manner that the input member rotates integrally with the first inner support member, the first piston portion is arranged on the axial first side, which is one side of the axial direction, relative to the radially extending support portion, and the rotor support member comprises: a cylindrical portion, which is formed in a cylindrical shape extending along the axial direction and supports the rotor from the inner side of the radial direction; and a flange portion, which is formed in such a manner as to extend along the radial direction on the inner side of the cylindrical portion in the radial direction, is connected to the cylindrical portion, and is provided on the inner side of the cylindrical portion in the radial direction. The first engaging device is arranged on the first axial side of the cylinder and on the radial inner side relative to the cylindrical portion. The first outer supporting member is configured to be open toward the first axial side and rotate integrally with the cylindrical portion. An annular member formed in a ring shape extending along the circumferential direction is fixed to the inner circumference of the cylindrical portion. The annular member is arranged at a position that is on the first axial side relative to the first friction plate and the second friction plate and overlaps with at least one of the first piston portion and the second friction plate when viewed in the axial direction along the axial direction.

[0008] According to this characteristic structure, when the first assembly including the rotor, the rotor support member and the first engaging device is assembled into the second assembly separated from the first assembly, even if the first engaging device moves relative to the rotor support member to the axial first side, at least one of the first piston portion and the second friction plate abuts against the annular member. Thus, the first friction plate of the first engaging device can be restricted from moving relative to the axial first side of the rotor support member. That is, the first friction plate can be restricted from falling off from the rotor support member. Therefore, the following structure is obtained: when the first assembly including the rotor, the rotor support member and the first engaging device is assembled into the second assembly separated from the first assembly, a part of the first assembly can be restricted from falling off through the opening of the rotor support member. BRIEF DESCRIPTION OF THE DRAWINGS

[0009] Figure 1 It is a schematic diagram showing a schematic structure of a vehicle drive device according to an embodiment.

[0010] Figure 2 It is a partial cross-sectional view of a vehicle drive device according to an embodiment.

[0011] Figure 3 It is a partially enlarged cross-sectional view of the vehicle drive device according to the embodiment.

[0012] Figure 4 It is a partially enlarged cross-sectional view of the vehicle drive device according to the embodiment.

[0013] Figure 5 This is an exploded view showing the structure of the first component.

[0014] Figure 6 This is a diagram showing the assembling operation of the first assembly to the second assembly.

[0015] Description of Reference Numerals

[0016] 100...vehicle drive device; 2...rotor support member; 21...cylindrical portion; 22...flange portion; CL1...first engaging device; 411...first inner friction member (second friction plate); 412...first outer friction member (first friction plate); 42...first piston portion; 44...first inner support member; 441...first cylindrical support member (cylindrical support member); 442...first radial extension member (radial extension support member); 48...first outer support member; 10...annular member; MG...rotating electric machine; St...stator; Ro...rotor; T...power transmission mechanism; W...wheel; L...axial direction; L1...axial direction first side; L2...axial direction second side; R...radial direction; R1...radial inner side; R2...radial outer side. DETAILED DESCRIPTION

[0017] Hereinafter, a vehicle drive device 100 according to an embodiment will be described with reference to the accompanying drawings. Figure 1 As shown, the vehicle drive device 100 is a device for driving a vehicle (hybrid vehicle) including both an internal combustion engine EG and a rotary electric machine MG. Specifically, the vehicle drive device 100 is configured as a drive device for a single-motor parallel type hybrid vehicle.

[0018] In the following description, unless otherwise specified, the “axial direction L”, “radial direction R”, and “circumferential direction” are defined with reference to the rotation axis of the rotary electric machine MG. In the radial direction R, the rotation axis side of the rotary electric machine MG is defined as the “radial inner side R1”, and the opposite side is defined as the “radial outer side R2”.

[0019] The directions of the components refer to the directions of the components when they are assembled in the vehicle drive device 100. The terms such as the directions and positions of the components are intended to include states with differences due to allowable errors in manufacturing.

[0020] like Figure 1 As shown, the vehicle drive device 100 includes: an input member I; a rotating electrical machine MG; a power transmission mechanism T; and a first engagement device CL1. In the present embodiment, the vehicle drive device 100 further includes: a second engagement device CL2; a counter gear mechanism CG; a differential gear mechanism DF; and a pair of output members O. In the present embodiment, a portion of the input member I, a portion of the output member O, the first engagement device CL1, the second engagement device CL2, the rotating electrical machine MG, the power transmission mechanism T, the counter gear mechanism CG, and the differential gear mechanism DF are accommodated in the housing 1.

[0021] The rotating electric machine MG functions as a driving force source for the wheels W. The rotating electric machine MG can function as a motor that generates power by receiving power supply, and as a generator that generates power by receiving power supply. Therefore, the rotating electric machine MG is electrically connected to a power storage device (battery, capacitor, etc.). The rotating electric machine MG operates by receiving power supply from the power storage device, or supplies power generated by the torque of the internal combustion engine EG and the inertia of the vehicle to the power storage device to store power.

[0022] The internal combustion engine EG functions as a driving force source for the wheels W, similarly to the rotary electric machine MG. The internal combustion engine EG is a prime mover (such as a gasoline engine or a diesel engine) that is driven by combustion of fuel to obtain power.

[0023] The input member I is drivably connected to the internal combustion engine EG. In the present embodiment, the input member I is drivably connected to the output shaft (crankshaft, etc.) of the internal combustion engine EG via an adjustment device (not shown) that attenuates fluctuations in the transmitted torque.

[0024] Here, in the present application, "drive connection" refers to a state in which two rotating members are connected in a manner that can transmit driving force, including a state in which the two rotating members are connected in a manner that rotates as a whole, or a state in which the two rotating members are connected in a manner that can transmit driving force via one or more transmission components. Such transmission components include various components that transmit rotation at the same speed or at a variable speed, such as shafts, gear mechanisms, belts, chains, etc. In addition, as transmission components, it is also possible to include an engagement device that selectively transmits rotation and driving force, such as a friction engagement device, a meshing engagement device, etc.

[0025] The first engagement device CL1 and the second engagement device CL2 are engagement devices for disconnecting and connecting the power transmission between the two rotating members. Figure 2 As shown, in this embodiment, the first engagement device CL1 and the second engagement device CL2 are arranged in parallel along the axial direction L. In addition, in this embodiment, the rotary electric machine MG and the power transmission mechanism T are arranged in parallel along the axial direction L. Moreover, the second engagement device CL2 is arranged on the power transmission mechanism T side in the axial direction L relative to the first engagement device CL1.

[0026] In the following description, in the axial direction L, the side where the first engagement device CL1 is arranged with respect to the second engagement device CL2 is referred to as “axial direction first side L1 ”, and the opposite side is referred to as “axial direction second side L2 ”.

[0027] like Figure 1As shown, in the present embodiment, the first engagement device CL1 is arranged in the power transmission path between the input member I and the rotary electric machine MG. Therefore, the first engagement device CL1 connects or disconnects the input member I and the rotary electric machine MG. In the present embodiment, the engagement state (direct connection engagement state / sliding engagement state / disengagement state) of the first engagement device CL1 is controlled based on the oil pressure supplied to the first engagement device CL1.

[0028] In the present embodiment, the second engagement device CL2 is arranged in the power transmission path between the rotary electric machine MG and the power transmission mechanism T. Moreover, the second engagement device CL2 connects or disconnects the power transmission mechanism T and the rotary electric machine MG. In the present embodiment, the engagement state (direct connection engagement state / sliding engagement state / disengagement state) of the second engagement device CL2 is controlled based on the oil pressure supplied to the second engagement device CL2.

[0029] The power transmission mechanism T is configured to transmit the rotation transmitted from the rotary electric machine MG to the wheels W. In the present embodiment, the power transmission mechanism T is a transmission TM.

[0030] The transmission TM is a device that has a plurality of speed gears with different speed ratios and changes the speed of the rotation transmitted from the rotating electrical machine MG side at a speed ratio corresponding to the formed speed gear. In the present embodiment, the transmission TM changes the speed of the rotation and torque input to the input member of the transmission TM, that is, the speed input shaft M, according to the speed ratio at each moment, and simultaneously performs torque conversion, and then transmits it to the output member of the transmission TM, that is, the speed output gear G1. In addition, in the present embodiment, the transmission TM is an automatic step-type transmission that has a plurality of speed-changing engagement devices and has a plurality of speed gears with different speed ratios in a switchable manner. In addition, as the transmission TM, an automatic step-type transmission that can infinitely change the speed ratio, a manual step-type transmission that has a plurality of speed gears with different speed ratios in a switchable manner, etc. can also be used.

[0031] The countershaft gear mechanism CG includes a countershaft input gear G2 and a countershaft output gear G3. The countershaft input gear G2 is an input member of the countershaft gear mechanism CG. The countershaft input gear G2 meshes with the speed change output gear G1. The countershaft output gear G3 is an output member of the countershaft gear mechanism CG. The countershaft output gear G3 is connected to the countershaft input gear G2 in a manner that rotates as one. In the present embodiment, the countershaft output gear G3 is connected to the countershaft input gear G2 via a countershaft S extending along the axial direction L. In the illustrated example, the countershaft output gear G3 is arranged at a position closer to the axial first side L1 than the countershaft input gear G2.

[0032] The differential gear mechanism DF includes a differential input gear G4 meshing with the counter output gear G3 of the counter gear mechanism CG. The differential gear mechanism DF distributes the rotation of the differential input gear G4 to a pair of output members O drivingly coupled to the wheels W.

[0033] The vehicle drive device 100 constructed as described above can transmit the torque of one or both of the internal combustion engine EG and the rotary electric machine MG to the wheels W to drive the vehicle by switching the engagement state of the first engagement device CL1 and the second engagement device CL2. In addition, in the vehicle drive device 100 involved in this embodiment, a multi-axis structure is formed in which the input member I and the speed change input shaft M are arranged on the same axis, and a pair of output members O are arranged on different axes in parallel with the input member I and the speed change input shaft M. Such a structure is suitable as a structure of the vehicle drive device 100 mounted on a FF (Front Engine Front Drive) vehicle.

[0034] In addition, in the vehicle drive device 100, when the internal combustion engine EG is started by the driving force of the rotary electric machine MG as the direct connection engagement state of the first engagement device CL1, the second engagement device CL2 is set to the slip engagement state, so that the torque fluctuation at the start of the internal combustion engine EG can be prevented from being transmitted to the wheels W. Here, the "direct connection engagement state" refers to an engagement state in which there is no rotational speed difference (slip) between a pair of friction plates of the friction engagement device. In addition, the "slip engagement state" refers to an engagement state in which there is a rotational speed difference (slip) between a pair of friction plates of the friction engagement device.

[0035] like Figure 2 As shown, in the present embodiment, the housing 1 includes a first side wall portion 11, a second side wall portion 12, and a cylindrical protrusion 13. Although not shown, the housing 1 according to the present embodiment includes a peripheral wall portion covering the rotary electric machine MG from the radially outer side R2 between the first side wall portion 11 and the second side wall portion 12 in the axial direction L.

[0036] The first side wall portion 11 extends along the radial direction R. The first side wall portion 11 is arranged on the first axial side L1 relative to the rotary electric machine MG and the first engagement device CL1. The input member I penetrates the first side wall portion 11 along the axial direction L. In addition, a portion of the input member I that is closer to the first axial side L1 than the first side wall portion 11 is connected to the above-mentioned adjustment device.

[0037] The second side wall portion 12 extends in the radial direction R. The second side wall portion 12 is arranged on the second axial side L2 with respect to the rotary electric machine MG and the second engagement device CL2. The speed change input shaft M passes through the second side wall portion 12 in the axial direction L.

[0038] The cylindrical protrusion 13 is formed in a cylindrical shape protruding from the second side wall portion 12 in the axial direction L. In the present embodiment, the cylindrical protrusion 13 is formed to protrude from the second side wall portion 12 toward the axial first side L1. Moreover, the cylindrical protrusion 13 is formed in a cylindrical shape covering the radial outer side R2 of the speed change input shaft M. In addition, in the present embodiment, the end of the cylindrical protrusion 13 on the axial first side L1 is located closer to the axial second side L2 than the end of the cylindrical protrusion 13 on the axial second side L2 of the input member I. That is, the cylindrical protrusion 13 is separated from the input member I in the axial direction L.

[0039] like Figure 3 as well as Figure 4 As shown, in this embodiment, the cylindrical protrusion 13 includes an inner protrusion 131 and an outer protrusion 132. The inner protrusion 131 and the outer protrusion 132 are connected to each other in a state where the outer peripheral surface of the inner protrusion 131 contacts the inner peripheral surface of the outer protrusion 132. The end of the outer protrusion 132 on the first axial side L1 is located closer to the first axial side L1 than the end of the inner protrusion 131 on the first axial side L1.

[0040] In the present embodiment, the input member I includes a cylindrical input tubular portion Ia whose end surface is open on one side (here, the second axial side L2) in the axial direction L. Furthermore, the speed change input shaft M includes an insertion portion Ma inserted into the radial inner side R1 of the input tubular portion Ia. In addition, the input member I and the speed change input shaft M are configured to rotate relative to each other.

[0041] like Figure 2 As shown, the rotary electric machine MG includes a stator St and a rotor Ro arranged on the radial inner side R1 relative to the stator St. The stator St is fixed to a non-rotating member. In the present embodiment, the stator St is fixed to the first side wall portion 11 of the housing 1 by a fixing member such as a bolt. In the present embodiment, the stator St includes: a stator core Stc; and a coil C wound around the stator core Stc in a manner to form coil ends Ce protruding from the stator core Stc to both sides of the axial direction L (the first axial side L1 and the second axial side L2). The rotor Ro is configured to be rotatable relative to the stator St. In the present embodiment, the rotor Ro includes: a rotor core Roc; a pair of holding members H that hold the rotor core Roc from both sides of the axial direction L; and a permanent magnet PM arranged in the rotor core Roc. In the present embodiment, the stator core Stc and the rotor core Roc are each formed by stacking a plurality of annular plate-shaped magnetic bodies (for example, electromagnetic steel sheets, etc.) in the axial direction L.

[0042] The vehicle drive device 100 includes a rotor support member 2 that supports the rotor Ro. The rotor support member 2 includes a cylindrical portion 21 and a flange portion 22 .

[0043] The cylindrical portion 21 is formed in a cylindrical shape extending along the axial direction L, and supports the rotor Ro from the radial inner side R1. The cylindrical portion 21 is connected to the rotor Ro in a manner of integral rotation. In the present embodiment, the rotor Ro is mounted on the outer peripheral surface of the cylindrical portion 21. In addition, the mounting of the rotor Ro to the outer peripheral surface of the cylindrical portion 21 is performed, for example, by welding, caulking, etc.

[0044] The flange portion 22 is formed to extend along the radial direction R on the radial inner side R1 relative to the cylindrical portion 21. In the present embodiment, the flange portion 22 is arranged adjacent to the second engagement device CL2 on the axial second side L2. In addition, in the present embodiment, the flange portion 22 is arranged on the axial first side L1 relative to the second side wall portion 12. In addition, in the present embodiment, the flange portion 22 is formed in the shape of an annular plate extending along the radial direction R and the circumferential direction.

[0045] The flange portion 22 is connected to the cylindrical portion 21 in a manner that rotates as a whole. In the present embodiment, the flange portion 22 is a component independent of the cylindrical portion 21, and is joined to the cylindrical portion 21 by, for example, welding, caulking, etc. That is, the cylindrical portion 21 as a separate component is joined to the flange portion 22. In the example shown in the figure, the flange portion 22 and the cylindrical portion 21 are joined by welding in a manner that the end portion of the radially outer side R2 of the flange portion 22 and the end portion of the axial second side L2 of the cylindrical portion 21 are connected to each other.

[0046] The first engaging device CL1 is arranged on the radially inner side R1 relative to the cylindrical portion 21 and on the axially first side L1 relative to the flange portion 22. In this way, in the rotor support member 2, a space for arranging the first engaging device CL1 is ensured on the radially inner side R1 relative to the cylindrical portion 21 and on the axially first side L1 relative to the flange portion 22. Therefore, the rotor support member 2 is formed into a bottomed cylindrical shape that is open toward the axially first side L1. In addition, in the present embodiment, the second engaging device CL2 is arranged between the first engaging device CL1 and the flange portion 22 in the axial direction L. Here, as described above, the first engaging device CL1 and the second engaging device CL2 are arranged side by side along the axial direction L. Therefore, the second engaging device CL2 is arranged adjacent to the first engaging device CL1 on the axially second side L2.

[0047] In the present embodiment, the first engagement device CL1 and the second engagement device CL2 are arranged at a position that is radially inside R1 relative to the rotor Ro and overlaps with the rotor Ro when viewed radially along the radial direction R. Here, "radially inside R1" means the inside of the radial direction R relative to the object member regardless of the position of the axial direction L. In addition, the same is true for "radially outside R2". In addition, regarding the configuration of two components, "overlapping when viewed in a specific direction" means that when an imaginary straight line parallel to the line of sight is moved in directions orthogonal to the imaginary straight line, there is at least a portion of the region where the imaginary straight line intersects both sides of the two components.

[0048] like Figure 3 As shown, the first engagement device CL1 includes a first inner friction member 411 and a first outer friction member 412 arranged in parallel along the axial direction L, and a first piston portion 42 that pushes the first inner friction member 411 and the first outer friction member 412 along the axial direction L. In the present embodiment, the first engagement device CL1 further includes: a first working oil chamber 43 to which the working oil of the first piston portion 42 is supplied; and an oil chamber forming member 46 that extends radially outward R2 relative to the input member I and is connected to the input member I in a manner of integral rotation.

[0049] The first inner friction member 411 and the first outer friction member 412 are both formed in an annular plate shape and are arranged so that the rotation axes are aligned with each other. In addition, the first inner friction member 411 and the first outer friction member 412 each have a plurality of them, and they are alternately arranged along the axial direction L. One of the first inner friction member 411 and the first outer friction member 412 can be used as a friction plate, and the other can be used as a partition plate. In addition, in the following description, there is a case where the first inner friction member 411 and the first outer friction member 412 are collectively referred to as the "first friction member 41".

[0050] The first outer friction member 412 corresponds to the "first friction plate". The first outer friction member 412 is supported by the first outer support member 48. The first outer support member 48 is a member that supports the first outer friction member 412 from the radially outer side R2. The first outer support member 48 opens toward the axially first side L1. The first outer support member 48 is configured to rotate integrally with the cylindrical portion 21. In the present embodiment, the first outer support member 48 is formed integrally with the cylindrical portion 21. In the example shown in the figure, a plurality of splines extending in the axial direction L are formed in a circumferentially dispersed manner on the inner peripheral portion of the cylindrical portion 21 over the entire region of the axial direction L. On the other hand, the same splines are also formed on the outer peripheral portion of the first outer friction member 412. And, by engaging these splines with each other, the first outer friction member 412 is supported from the radially outer side R2 by the cylindrical portion 21. In this way, the first outer friction member 412 can be supported slidably in the axial direction L in a state where the relative rotation relative to the cylindrical portion 21 is restricted.

[0051] The first inner friction member 411 is equivalent to the "second friction plate". The first inner friction member 411 is supported by the first inner support member 44. The first inner support member 44 is a member that supports the first inner friction member 411 from the radial inner side R1. The first inner support member 44 includes: a first cylindrical support portion 441 formed in a cylindrical shape extending along the axial direction L; and a first radial extension portion 442 formed to extend from the first cylindrical support portion 441 toward the radial inner side R1.

[0052] The first cylindrical support portion 441 supports the first inner friction member 411 from the radial inner side R1. In the example shown in the figure, a plurality of splines extending in the axial direction L are formed in a circumferentially dispersed manner on the outer peripheral portion of the first cylindrical support portion 441 over the entire region of the axial direction L. On the other hand, the same splines are also formed on the inner peripheral portion of the first inner friction member 411. Moreover, by engaging these splines with each other, the first inner friction member 411 is supported from the radial inner side R1 by the first cylindrical support portion 441. In this way, the first inner friction member 411 is supported slidably in the axial direction L while being restricted from relative rotation with respect to the first cylindrical support portion 441.

[0053] The first radial extension portion 442 is equivalent to a "radial extension support portion". The first radial extension portion 442 is connected to the first cylindrical support portion 441 in a manner that rotates as a whole. In the present embodiment, the first radial extension portion 442 is a component independent of the first cylindrical support portion 441, and is joined to the first cylindrical support portion 441 by, for example, welding, caulking, etc. In the illustrated example, the first radial extension portion 442 and the first cylindrical support portion 441 are joined to each other by welding in a state where the surface on the axial first side L1 of the first radial extension portion 442 is in contact with the surface on the axial second side L2 of the first cylindrical support portion 441. In addition, the first radial extension portion 442 is connected to the input component I in a manner that rotates as a whole. In the present embodiment, the end portion on the radial inner side R1 of the first radial extension portion 442 is connected to the outer peripheral surface of the input component I. In the illustrated example, the radially inner end R1 of the first radially extending portion 442 is joined by welding to a flange-like protrusion formed on the outer peripheral surface of the input member I. In the present embodiment, the first radially extending portion 442 is formed in an annular plate shape extending in the radial direction R and the circumferential direction.

[0054] In the present embodiment, the first engagement device CL1 has a contact portion 442a that contacts the first friction member 41 from the side opposite to the first piston portion 42 side in the axial direction L (here, the axial second side L2). In the illustrated example, the contact portion 442a is formed integrally with the first radially extending portion 442. Specifically, the contact portion 442a is formed by a portion of the first radially extending portion 442 that extends further toward the radially outer side R2 than the first cylindrical support portion 441. In the present embodiment, the contact portion 442a is configured to contact the first inner friction member 411 closest to the axial second side L2 from the axial second side L2.

[0055] The first radially extending portion 442 contacts the oil passage forming member 45 in the axial direction L. In the present embodiment, the first radially extending portion 442 contacts the oil passage forming member 45 from the second axial side L2.

[0056] The oil path forming member 45 is a member that forms an oil path in the first engagement device CL1. In the present embodiment, the oil path forming member 45 is disposed between the first radially extending portion 442 and the first piston portion 42 in the axial direction L. Furthermore, in the present embodiment, the oil path forming member 45 is disposed at a position that overlaps the first cylindrical support portion 441 when viewed radially along the radial direction R and is radially inside R1 relative to the first cylindrical support portion 441. In the present embodiment, the oil path forming member 45 has a connecting portion 451 and a partition portion 452.

[0057] The connecting portion 451 is formed into a cylindrical shape extending along the axial direction L. The connecting portion 451 is connected to the first cylindrical support portion 441 of the first inner support member 44 in a manner that rotates integrally with it. In the present embodiment, the connecting portion 451 is connected to the first cylindrical support portion 441 in a state adjacent to the first cylindrical support portion 441 at the radial inner side R1. Specifically, a plurality of splines extending along the axial direction L are formed in a circumferentially dispersed manner on the inner peripheral portion of the first cylindrical support portion 441. On the other hand, the same splines are also formed on the outer peripheral portion of the connecting portion 451. Moreover, by engaging these splines with each other, the connecting portion 451 is connected to the first cylindrical support portion 441 in a manner that rotates integrally with it.

[0058] The partition portion 452 is formed to extend radially inwardly R1 from the connecting portion 451. In the present embodiment, the partition portion 452 is formed integrally with the connecting portion 451 so that the end portion of the partition portion 452 on the radially outer side R2 and the end portion of the connecting portion 451 on the axial second side L2 are connected to each other. The partition portion 452 is arranged so as to sandwich the space between the first piston portion 42 and the first inner support member 44.

[0059] In the present embodiment, a radial groove 45a is formed along the radial direction R on the contact surface of the oil path forming member 45 that contacts the first radial extension portion 442. In the present embodiment, the partition portion 452 abuts against the first radial extension portion 442 from the axial first side L1 in at least a portion of the entire area of ​​the radial direction R of the partition portion 452. Moreover, a radial groove 45a is formed on the contact surface of the partition portion 452 that contacts the first radial extension portion 442. The radial groove 45a is formed to be continuous over the entire area of ​​the radial direction R of the contact surface of the partition portion 452 that contacts the first radial extension portion 442. That is, the radial groove 45a is formed to connect the radial inner side R1 with the radial outer side R2 with respect to the contact portion between the partition portion 452 and the first radial extension portion 442. In the present embodiment, a plurality of radial grooves 45a are formed dispersedly in the circumferential direction.

[0060] The first piston portion 42 is arranged on the first axial side L1 relative to the first radial extension portion 442 of the first inner support member 44. In the present embodiment, the first piston portion 42 is supported to rotate integrally with the first inner support member 44. In the present embodiment, although not shown in the figure, the relative rotation of the first piston portion 42 relative to the connecting portion 451 is restricted in such a manner that the connecting portion 451 rotates integrally with the first piston portion 42. Here, as described above, the connecting portion 451 is connected to the first cylindrical support portion 441 of the first inner support member 44 in such a manner that the connecting portion 451 rotates integrally with the first inner support member 44. Therefore, in the present embodiment, the first piston portion 42 is supported to rotate integrally with the first inner support member 44 via the connecting portion 451.

[0061] In the present embodiment, the first piston portion 42 is configured to press the first friction member 41 in the axial direction L with a pressure corresponding to the oil pressure supplied to the first hydraulic oil chamber 43 . The first piston portion 42 includes a first sliding portion 421 and a first pressing portion 422 .

[0062] The first sliding portion 421 extends along the radial direction R. In the present embodiment, the first sliding portion 421 is formed in a circular ring plate shape extending along the radial direction R and the circumferential direction. The first sliding portion 421 is configured to slide in the first cylinder portion C1 along the axial direction L. In the present embodiment, the first sliding portion 421 is arranged at a position that overlaps with the first friction member 41 when viewed radially along the radial direction R and relative to the radial inner side R1 of the first friction member 41.

[0063] The first cylinder portion C1 is formed in a cylindrical shape along the axial direction L. In the present embodiment, the first cylinder portion C1 is formed by the input member I and the oil path forming member 45. Specifically, a portion of the outer peripheral surface of the input cylindrical portion Ia in the input member I functions as a sliding surface for the radially inner end portion R1 of the first sliding portion 421 to slide. In addition, a portion of the inner peripheral surface of the connecting portion 451 in the oil path forming member 45 functions as a sliding surface for the radially outer end portion R2 of the first sliding portion 421 to slide.

[0064] The first pressing portion 422 extends from the first sliding portion 421 to the radially outer side R2 in a manner adjacent to the first friction member 41 in the axial direction L. In the present embodiment, the first pressing portion 422 is arranged on the side opposite to the contact portion 442a side of the first radially extending portion 442 (here, the axial first side L1) in the axial direction L with respect to the first friction member 41. Therefore, the first pressing portion 422 is formed to extend from the end portion of the radially outer side R2 of the first sliding portion 421 to the radially outer side R2 while bypassing the first cylindrical support portion 441 through the axial first side L1 of the first cylindrical support portion 441.

[0065] In the present embodiment, the first piston portion 42 is urged toward the first axial side L1 by the first force member 42a. The first force member 42a is arranged between the first sliding portion 421 in the axial direction L and the partition portion 452 of the oil path forming member 45. In the present embodiment, a plurality of first force members 42a are arranged dispersedly in the circumferential direction. As the first force member 42a, for example, a return spring or the like can be used. In this way, if oil of a specified oil pressure is supplied to the first working oil chamber 43 from a hydraulic control device (not shown in the figure), the first piston portion 42 slides toward the second axial side L2 in accordance with the oil pressure to overcome the force of the first force member 42a, and pushes the first friction member 41 toward the second axial side L2.

[0066] The first working oil chamber 43 is disposed adjacent to the first piston portion 42 in the axial direction L. In the present embodiment, the first working oil chamber 43 is formed between the first piston portion 42 and the oil chamber forming member 46. Specifically, the first working oil chamber 43 is formed between the first sliding portion 421 of the first piston portion 42 and the oil chamber forming member 46 in the axial direction L.

[0067] In the present embodiment, the first hydraulic oil chamber 43 is arranged so as to overlap with the first friction member 41 when viewed along the radial direction R. In the present embodiment, the first hydraulic oil chamber 43 is arranged so as not to overlap with the first friction member 41 when viewed along the axial direction L.

[0068] In the present embodiment, the oil chamber forming member 46 is arranged to contact the outer peripheral surface of the input cylindrical portion 1a in the input member 1. In addition, in the present embodiment, the oil chamber forming member 46 is arranged on the axial first side L1 relative to the first piston portion 42. Here, the oil chamber forming member 46 is arranged adjacent to the first sliding portion 421 of the first piston portion 42 on the axial first side L1.

[0069] In the present embodiment, the dimension of the radial direction R of the outermost peripheral portion of the oil chamber forming member 46 is smaller than the dimension of the radial direction R of the inner peripheral surface of the first cylindrical support portion 441. In addition, in the present embodiment, the oil chamber forming member 46 is arranged at a position closer to the radial inner side R1 than the connecting portion 451 of the oil passage forming member 45. Therefore, the first piston portion 42 is formed to extend and protrude toward the first axial side L1 and the radial outer side R2 through the oil chamber forming member 46 and the connecting portion 451 in the radial direction R, so that the first pressing portion 422 is arranged at a position closer to the radial outer side R2 than the connecting portion 451.

[0070] In the present embodiment, a first release oil chamber 47 is formed on the side opposite to the first working oil chamber 43 side in the axial direction L (here, the second axial side L2) with respect to the first piston portion 42. The first release oil chamber 47 is a space for generating an oil pressure that opposes the centrifugal oil pressure generated in the first working oil chamber 43. In the present embodiment, the first release oil chamber 47 is formed between the first piston portion 42 and the oil path forming member 45. That is, a portion of the space between the first piston portion 42 and the first inner side support member 44 that is on the first axial side L1 with respect to the partition portion 452 of the oil path forming member 45 functions as the first release oil chamber 47.

[0071] like Figure 3As shown, the second engagement device CL2 includes: a second inner friction member 511 and a second outer friction member 512 arranged in parallel along the axial direction L, and a second piston portion 52 that pushes the second inner friction member 511 and the second outer friction member 512 along the axial direction L. In the present embodiment, the second engagement device CL2 further includes a second working oil chamber 53 to which the working oil of the second piston portion 52 is supplied.

[0072] The second inner friction member 511 and the second outer friction member 512 are both formed in an annular plate shape and are arranged so that the rotation axes are aligned with each other. In addition, the second inner friction member 511 and the second outer friction member 512 each have a plurality of them, and they are alternately arranged along the axial direction L. One of the second inner friction member 511 and the second outer friction member 512 is used as a friction plate, and the other is used as a partition plate. In addition, in the following description, the second inner friction member 511 and the second outer friction member 512 are collectively referred to as "the second friction member 51".

[0073] The second inner friction member 511 is equivalent to the "fourth friction plate". The second inner friction member 511 is supported by the second inner support member 54. The second inner support member 54 is a member that supports the second inner friction member 511 from the radial inner side R1. In the present embodiment, the second inner support member 54 includes: a second cylindrical support portion 541 formed in a cylindrical shape extending along the axial direction L; and a second radial extension portion 542 formed to extend from the second cylindrical support portion 541 to the radial inner side R1.

[0074] The second cylindrical support portion 541 supports the second inner friction member 511 from the radial inner side R1. In the example shown in the figure, a plurality of splines extending in the axial direction L are formed in a circumferentially dispersed manner on the outer peripheral portion of the second cylindrical support portion 541 over the entire region of the axial direction L. On the other hand, the same splines are also formed on the inner peripheral portion of the second inner friction member 511. Moreover, by engaging these splines with each other, the second inner friction member 511 is supported from the radial inner side R1 by the second cylindrical support portion 541. In this way, the second inner friction member 511 can be supported slidably in the axial direction L while being restricted from relative rotation with respect to the second cylindrical support portion 541.

[0075] The second radially extending portion 542 is connected to the second cylindrical support portion 541 in a manner that it rotates integrally. In the present embodiment, the second radially extending portion 542 is a component independent of the second cylindrical support portion 541, and is joined to the second cylindrical support portion 541 by, for example, welding, caulking, etc. In the illustrated example, the second radially extending portion 542 is joined to the second cylindrical support portion 541 by welding in a manner that the end portion of the radially outer side R2 of the second radially extending portion 542 and the end portion of the axially first side L1 of the second cylindrical support portion 541 are connected to each other. In the present embodiment, the second radially extending portion 542 is formed in the shape of an annular plate extending in the radial direction R and the circumferential direction.

[0076] In addition, the second radial extension portion 542 is connected to the speed change input shaft M in a manner that rotates as a whole. In the present embodiment, the end portion of the radial inner side R1 of the second radial extension portion 542 is connected to the outer peripheral surface of the speed change input shaft M. In the illustrated example, a plurality of splines extending along the axial direction L are formed in a circumferentially dispersed manner on the inner peripheral surface of the cylindrical portion formed at the end portion of the radial inner side R1 of the second radial extension portion 542. On the other hand, the same splines are also formed on the outer peripheral surface of the speed change input shaft M. Moreover, the second radial extension portion 542 is connected to the speed change input shaft M in a manner that rotates as a whole by engaging these splines with each other.

[0077] The second outer friction member 512 is equivalent to the "third friction plate". The second outer friction member 512 is supported by the second outer support component 55. The second outer support component 55 is a component that supports the second outer friction member 512 from the radial outer side R2. In the present embodiment, the second outer support component 55 is formed in a cylindrical shape extending along the axial direction L. In the example shown in the figure, a plurality of splines extending along the axial direction L are formed in a circumferentially dispersed manner on the inner peripheral portion of the second outer support component 55. On the other hand, the same splines are also formed on the outer peripheral portion of the second outer friction member 512. Moreover, by engaging these splines with each other, the second outer friction member 512 is supported from the radial outer side R2 by the second outer support component 55. In this way, the second outer friction member 512 can be supported slidably along the axial direction L in a state where the relative rotation relative to the second outer support component 55 is restricted.

[0078] The second outer support member 55 is configured to rotate integrally with the rotor support member 2. In the present embodiment, the second outer support member 55 is supported by the cylindrical portion 21 of the rotor support member 2 from the radially outer side R2. In the illustrated example, a plurality of splines extending in the axial direction L are formed in a circumferentially dispersed manner on the outer peripheral portion of the second outer support member 55. On the other hand, as described above, a plurality of splines extending in the axial direction L are also formed in a circumferentially dispersed manner on the inner peripheral portion of the cylindrical portion 21. Moreover, by engaging these splines with each other, the second outer support member 55 is supported by the cylindrical portion 21 from the radially outer side R2. In this way, the second outer friction member 512 is supported by the cylindrical portion 21 of the rotor support member 2 via the second outer support member 55.

[0079] In the present embodiment, the second engagement device CL2 includes an abutting member 56 that abuts against the second friction member 51. The abutting member 56 is configured to abut against the second friction member 51 from the side opposite to the second piston portion 52 side in the axial direction L (here, the axial first side L1). In the present embodiment, the abutting member 56 is configured to abut against the second outer friction member 512 closest to the axial first side L1 from the axial first side L1.

[0080] In the present embodiment, the abutment member 56 is supported by the cylindrical portion 21 from the radially outer side R2. In the illustrated example, a plurality of splines extending along the axial direction L are formed in a circumferentially dispersed manner on the outer peripheral portion of the abutment member 56. Moreover, these splines engage with a plurality of splines formed on the inner peripheral portion of the cylindrical portion 21, so that the abutment member 56 is supported by the cylindrical portion 21 from the radially outer side R2 while being restricted from relative rotation relative to the cylindrical portion 21 and being able to slide along the axial direction L. In addition, in the illustrated example, the annular fixing member 56a is fixed to the inner peripheral portion of the cylindrical portion 21 in a manner that it abuts against the abutment member 56 from the axial first side L1. In this way, the movement of the abutment member 56 to the axial first side L1 is restricted by the fixing member 56a. In the present embodiment, the fixing member 56a is a retaining ring.

[0081] In the present embodiment, the second piston portion 52 is configured to push the second friction member 51 in the axial direction L with a pressure corresponding to the oil pressure supplied to the second working oil chamber 53. In addition, in the present embodiment, the second piston portion 52 is arranged at a position closer to the axial second side L2 than the second friction member 51. That is, the second piston portion 52 is arranged so as not to overlap with the second friction member 51 when viewed in the radial direction along the radial direction R. The second piston portion 52 has a second sliding portion 521 and a second pressing portion 522.

[0082] The second sliding portion 521 is configured to slide inside the second cylinder portion C2 along the axial direction L. The second cylinder portion C2 is formed in a cylindrical shape along the axial direction L. In the present embodiment, the second cylinder portion C2 is formed by the cylinder forming portion 23 of the flange portion 22. That is, in the present embodiment, a portion of the flange portion 22 constitutes a portion of the second engagement device CL2.

[0083] The cylinder forming portion 23 protrudes toward the axial second side L2 to form a second cylinder portion C2 on which the second piston portion 52 slides. In the present embodiment, the cylinder forming portion 23 includes an inner cylindrical portion 231 , an outer cylindrical portion 232 , and a radial connection portion 233 .

[0084] The inner cylindrical portion 231 is formed in a cylindrical shape extending along the axial direction L. A portion of the outer peripheral surface of the inner cylindrical portion 231 functions as a sliding surface on which the radially inner end R1 of the second sliding portion 521 slides. In the present embodiment, the inner cylindrical portion 231 is configured to cover the radially outer side R2 of the cylindrical protrusion 13 of the housing 1.

[0085] The outer cylindrical portion 232 is formed in a cylindrical shape extending in the axial direction L. The outer cylindrical portion 232 is arranged radially outward R2 relative to the inner cylindrical portion 231. A part of the inner peripheral surface of the outer cylindrical portion 232 functions as a sliding surface on which the radially outer R2 end of the second sliding portion 521 slides.

[0086] The radial connecting portion 233 extends along the radial direction R in a manner that connects the inner cylindrical portion 231 and the outer cylindrical portion 232. In the present embodiment, the radial connecting portion 233 is formed into a circular ring plate extending along the radial direction R and the circumferential direction. In addition, in the present embodiment, the end of the radial inner side R1 of the radial connecting portion 233 is connected to the end of the axial second side L2 of the inner cylindrical portion 231. Moreover, the end of the radial outer side R2 of the radial connecting portion 233 is connected to the end of the axial second side L2 of the outer cylindrical portion 232. In addition, the portion of the flange portion 22 that is closer to the radial outer side R2 than the cylinder forming portion 23 is formed into a circular ring plate extending along the radial direction R and the circumferential direction, and is connected to the end of the axial first side L1 of the outer cylindrical portion 232. In the example shown in the figure, the flange portion 22 including the inner cylindrical portion 231, the outer cylindrical portion 232 and the radial connecting portion 233 is formed integrally by one component.

[0087] The second pressing portion 522 extends radially outward R2 from the second sliding portion 521. In the present embodiment, the second pressing portion 522 is disposed on the side opposite to the contact member 56 side in the axial direction L (here, the axial second side L2) with respect to the second friction member 51.

[0088] The second piston portion 52 is supported to rotate integrally with the rotor support member 2. In the present embodiment, although not shown in the figure, the relative rotation of the second piston portion 52 with respect to the flange portion 22 of the rotor support member 2 is restricted so that the flange portion 22 and the second piston portion 52 rotate integrally.

[0089] In the present embodiment, the second piston portion 52 is urged toward the axial second side L2 by the second force member 52a mounted on the mounting member 57. The second force member 52a is arranged between the second sliding portion 521 and the mounting member 57 in the axial direction L. In the present embodiment, a plurality of second force members 52a are dispersedly arranged in the circumferential direction. As the second force member 52a, for example, a return spring or the like can be used. In this way, if oil of a specified oil pressure is supplied to the second working oil chamber 53 from a hydraulic control device (not shown in the figure), the second piston portion 52 slides along the axial first side L1 in accordance with the oil pressure to overcome the force of the second force member 52a, and pushes the second friction member 51 toward the axial first side L1.

[0090] The mounting member 57 is arranged on the radially outer side R2 relative to the inner cylindrical portion 231 of the cylinder forming portion 23. In the present embodiment, the mounting member 57 is arranged to contact the outer peripheral surface of the inner cylindrical portion 231. In addition, in the present embodiment, the mounting member 57 is arranged adjacent to the second sliding portion 521 of the second piston portion 52 on the axial first side L1.

[0091] The second working oil chamber 53 is arranged adjacent to the second piston portion 52 in the axial direction L. In the present embodiment, the second working oil chamber 53 is formed between the second piston portion 52 and the cylinder forming portion 23. Specifically, the second working oil chamber 53 is formed between the second sliding portion 521 of the second piston portion 52 and the radial connection portion 233 of the cylinder forming portion 23 in the axial direction L.

[0092] In the present embodiment, the second hydraulic oil chamber 53 is arranged so as to overlap the second friction member 51 when viewed along the axial direction L. In the present embodiment, the second hydraulic oil chamber 53 is arranged so as not to overlap the second friction member 51 when viewed along the radial direction R.

[0093] In the present embodiment, a second release oil chamber 58 is formed on the side (here, the first axial side L1) opposite to the second working oil chamber 53 side in the axial direction L with respect to the second piston portion 52. The second release oil chamber 58 is a space for generating an oil pressure opposing the centrifugal oil pressure generated in the second working oil chamber 53. In the present embodiment, the second release oil chamber 58 is formed between the second piston portion 52 and the mounting member 57.

[0094] In the present embodiment, the flange portion 22 extends to the radially inner side R1 of the second engagement device CL2 . In the example shown in the figure, the inner peripheral end of the flange portion 22 is located radially inner side R1 of the inner peripheral end of the second piston portion 52 .

[0095] like Figure 3 As shown in FIG. 1 , the vehicle drive device 100 includes an annular member 10 fixed to the inner circumference of the cylindrical portion 21. The annular member 10 is formed in a ring shape extending in the circumferential direction. In the present embodiment, the annular member 10 is a snap ring. The annular member 10 is embedded in a second fixing groove 21d (see FIG. 21 ) formed in the inner circumference of the cylindrical portion 21. Figure 5 ), thereby being fixed to the cylindrical portion 21. The second fixing groove 21d is a groove formed continuously in the circumferential direction on the inner circumference of the cylindrical portion 21. In this example, as described above, a plurality of splines extending in the axial direction L are formed in a dispersed manner in the circumferential direction on the inner circumference of the cylindrical portion 21. Moreover, the second fixing groove 21d is formed at least in the protruding portion of the plurality of splines that protrudes toward the radial inner side R1.

[0096] The annular member 10 is arranged at a position that is located at the first axial side L1 relative to the first inner friction member 411 and the first outer friction member 412 and overlaps with at least one of the first piston portion 42 and the first inner friction member 411 when viewed in the axial direction along the axial direction L. In the example shown in the figure, the outer peripheral edge of the first piston portion 42 and the outer peripheral edge of the first inner friction member 411 are arranged at almost the same position in the radial direction R. Therefore, the annular member 10 is configured to overlap with both the first pressing portion 422 of the first piston portion 42 and the first inner friction member 411. In addition, when the positions of the outer peripheral edges of the first piston portion 42 and the outer peripheral edges of the first inner friction member 411 in the radial direction R are different, the annular member 10 is arranged to overlap with at least one of the first piston portion 42 and the first inner friction member 411 that is arranged on the radial outer side R2 when viewed in the axial direction.

[0097] like Figure 2 As shown, in this embodiment, the following formula (1) holds.

[0098] D1-D2<D3···(1)

[0099] In the above formula (1), D1 is the diameter of the inner circumferential surface of the cylindrical portion 21. And, D2 is the outermost diameter of the first piston portion 42. In addition, D3 is the distance in radial direction R from the inner circumferential surface of the cylindrical portion 21 to the inner circumferential end of the annular member 10. Here, the inner circumferential surface of the cylindrical portion 21 is a cylindrical surface facing the radial inner side R1 of the cylindrical portion 21. In the illustrated example, the inner circumferential surface of the cylindrical portion 21 refers to an imaginary surface formed by connecting the ends of the radial inner side R1 of a plurality of splines formed on the inner circumference of the cylindrical portion 21. In addition, in the present embodiment, the outermost diameter of the first piston portion 42 is the diameter of the outer edge of the first pushing portion 422.

[0100] like Figure 3 As shown, in the present embodiment, the vehicle drive device 100 includes a rotation sensor 3 for detecting the rotation of the rotor Ro. The rotation sensor 3 is a sensor for detecting at least one of the position of the rotor Ro relative to the rotation direction of the stator St and the rotation speed of the rotor Ro. As such a rotation sensor 3, for example, a resolver can be used. The rotation sensor 3 includes a rotating body 31 and a fixed body 32. In the present embodiment, the rotating body 31 and the fixed body 32 are respectively formed in an annular shape with the rotation axis of the rotor Ro as a reference.

[0101] The rotating body 31 is supported on the outer peripheral surface of the cylinder forming part 23. That is, the rotating body 31 is arranged at a position that overlaps with the cylinder forming part 23 when viewed radially along the radial direction R relative to the radial outer side R2 of the cylinder forming part 23. In the present embodiment, the rotating body 31 is arranged on the outer peripheral surface of the outer cylindrical part 232 in the cylinder forming part 23. Moreover, the rotating body 31 is connected to the outer cylindrical part 232 in a manner that rotates as a whole. In the example shown in the figure, a plurality of splines extending along the axial direction L are formed in a dispersed manner in the circumferential direction on the outer peripheral surface of the cylinder forming part 23 (here, the outer cylindrical part 232). On the other hand, the same splines are also formed on the inner peripheral surface of the rotating body 31. Moreover, these splines are engaged with each other, so that the rotating body 31 is connected to the rotor support part 2 in a manner that rotates as a whole. In addition, in the example shown in the figure, the annular limiting part 31a is fixed to the outer peripheral surface of the outer cylindrical part 232 in a manner that abuts against the rotating body 31 from the axial second side L2. In this way, the movement of the rotating body 31 to the second axial side L2 is restricted by the restriction member 31 a.

[0102] The fixed body 32 is arranged radially outward R2 with respect to the rotating body 31. The fixed body 32 is supported by a non-rotating member. In the present embodiment, the fixed body 32 is supported by the sensor support portion 14 provided on the second side wall portion 12 of the housing 1.

[0103] In the present embodiment, the rotation sensor 3 is arranged at a position that is radially outside R2 relative to the second sliding portion 521 of the second piston portion 52 and overlaps with the second sliding portion 521 when viewed radially along the radial direction R. In addition, in the present embodiment, the rotation sensor 3 is arranged to overlap with the second friction member 51 when viewed axially along the axial direction L. In the illustrated example, the rotating body 31 is arranged to overlap with the second pressing portion 522 of the second piston portion 52 in addition to the second friction member 51 when viewed axially. Furthermore, in the present embodiment, the rotation sensor 3 is arranged to overlap with the rotor Ro when viewed axially along the axial direction L. In the illustrated example, the portion of the radially outside R2 of the fixed body 32 is arranged to overlap with the rotor Ro when viewed axially.

[0104] like Figure 3 As shown, in this embodiment, the vehicle drive device 100 includes: a first bearing B1 and a second bearing B2 that rotatably support the rotor support member 2; and a third bearing B3 that rotatably supports the input member I. In this embodiment, the first bearing B1, the second bearing B2, and the third bearing B3 are ball bearings.

[0105] The first bearing B1 supports the cylindrical portion 21 of the rotor support member 2 so as to be rotatable. In the present embodiment, the first bearing B1 is arranged at a position closer to the radially outer side R2 than the first cylindrical support portion 441 of the first inner support member 44. In the present embodiment, the first bearing B1 is arranged on the axially first side L1 relative to the rotor Ro. In addition, in the present embodiment, the first bearing B1 is arranged on the outer peripheral surface of the cylindrical portion 21. Specifically, the cylindrical portion 21 has a bearing support portion 211 protruding from the rotor Ro to the axially first side L1. And the first bearing B1 is mounted in such a manner that the inner peripheral surface of the first bearing B1 contacts the outer peripheral surface of the bearing support portion 211. In addition, in the present embodiment, the first bearing B1 is supported by the bearing support portion 11a of the first side wall portion 11 in the housing 1. The bearing support portion 11a protrudes to the axially second side L2 and supports the first bearing B1 from the radially outer side R2. In this way, the first bearing B1 supports the cylindrical portion 21 so as to be rotatable relative to the first side wall portion 11.

[0106] In the present embodiment, the first bearing B1 is configured to overlap with the first piston portion 42 when viewed in the radial direction along the radial direction R. Specifically, the first bearing B1 is configured to overlap with the first pressing portion 422 of the first piston portion 42 when viewed in the radial direction. In addition, in the present embodiment, the first bearing B1 is configured to overlap with the rotor Ro when viewed in the axial direction along the axial direction L. In addition, in the present embodiment, the first bearing B1 is configured to overlap with the coil end Ce of the stator St when viewed in the radial direction along the radial direction R (refer to Figure 2 ).

[0107] In the present embodiment, a protrusion 21a is formed on the cylindrical portion 21 on the first axial side L1 relative to the rotor Ro, and protrudes from the outer peripheral surface of the cylindrical portion 21 toward the radial outer side R2. Here, the protrusion 21a is continuously formed over the entire circumferential area. Moreover, the protrusion 21a is configured in a manner to be clamped by the rotor Ro and the first bearing B1 from both sides of the axial direction L. Specifically, the rotor Ro is configured to abut against the protrusion 21a from the second axial side L2. In addition, the first bearing B1 is configured to abut against the protrusion 21a from the first axial side L1.

[0108] The second bearing B2 supports the flange portion 22 of the rotor support member 2 so as to be rotatable. In the present embodiment, the second bearing B2 is configured to overlap with the second piston portion 52 when viewed in the radial direction along the radial direction R. In addition, in the present embodiment, the second bearing B2 is configured at a position that is radially inside R1 relative to the cylinder forming portion 23 of the flange portion 22 and overlaps with the cylinder forming portion 23 when viewed in the radial direction along the radial direction R. Moreover, the second bearing B2 supports the rotor support member 2 from the radial inside R1. In the example shown in the figure, the second bearing B2 is sandwiched between the inner cylindrical portion 231 of the rotor support member 2 and the cylindrical protrusion 13 (specifically, the outer protrusion 132) of the housing 1.

[0109] In the present embodiment, the third bearing B3 is arranged at a position which is radially inside R1 relative to at least a portion of the first piston portion 42 and overlaps with the first piston portion 42 when viewed radially along the radial direction R. Here, the third bearing B3 is arranged radially inside R1 relative to the first pushing portion 422 of the first piston portion 42. In addition, the third bearing B3 is arranged to overlap with the first pushing portion 422 when viewed radially. Furthermore, in the present embodiment, the third bearing B3 is arranged on the axial first side L1 relative to the oil chamber forming member 46. In addition, the third bearing B3 is arranged radially inside R1 relative to a portion of the oil chamber forming member 46.

[0110] In the present embodiment, the third bearing B3 is arranged on the outer peripheral surface of the input cylindrical portion 1a in the input component 1. Specifically, the third bearing B3 is installed in such a manner that the inner peripheral surface of the third bearing B3 contacts the outer peripheral surface of the input cylindrical portion 1a. In addition, the third bearing B3 is supported from the radially outer side R2 to the first side wall portion 11 of the housing 1. In this way, the third bearing B3 supports the input component 1 so that it can rotate relative to the first side wall portion 11.

[0111] In the present embodiment, the inner race of the third bearing B3 abuts against the step portion formed on the outer peripheral surface of the input cylindrical portion Ia from the first axial side L1. Furthermore, the outer race of the third bearing B3 abuts against the first side wall portion 11 from the second axial side L2. In this way, the third bearing B3 is restricted from moving in the axial direction L by the input cylindrical portion Ia and the first side wall portion 11. As a result, the third bearing B3 can support the thrust load acting on the input component I supported by the third bearing B3.

[0112] like Figure 3 As shown, in this embodiment, the vehicle drive device 100 includes an oil passage for supplying oil to the first hydraulic oil chamber 43 to operate the first piston portion 42. The oil passage includes a first hydraulic oil passage P11, a first hydraulic connection oil passage P12, and a second in-shaft oil passage P13.

[0113] The first hydraulic oil passage P11 is an oil passage communicating with the first hydraulic oil chamber 43. The first hydraulic oil passage P11 is formed from the inner peripheral surface to the outer peripheral surface of the input cylindrical portion 1a in the input member 1.

[0114] The first working connecting oil passage P12 is an oil passage connecting the first working oil passage P11 and the second in-shaft oil passage P13. The first working connecting oil passage P12 is formed in the insertion portion Ma of the speed change input shaft M. In the present embodiment, the first working connecting oil passage P12 is formed along the radial direction R from the second in-shaft oil passage P13 inside the insertion portion Ma to the outer peripheral surface.

[0115] The second in-shaft oil passage P13 is an oil passage formed inside the speed change input shaft M. In the present embodiment, the second in-shaft oil passage P13 is formed along the axial direction L.

[0116] In the present embodiment, the vehicle drive device 100 includes an oil passage for supplying oil to the second hydraulic oil chamber 53 to operate the second piston portion 52. The oil passage includes a second hydraulic oil passage P21, a second hydraulic connection oil passage P22, and a second radial oil passage P23.

[0117] The second hydraulic oil passage P21 is an oil passage that connects the radial inner side R1 of the rotor support member 2 with the second hydraulic oil chamber 53. In the present embodiment, the second hydraulic oil passage P21 is formed in the inner cylindrical portion 231 of the cylinder forming portion 23. The second hydraulic oil passage P21 is formed from the inner peripheral surface to the outer peripheral surface of the inner cylindrical portion 231.

[0118] The second working connecting oil circuit P22 is an oil circuit that connects the second radial oil circuit P23 with the second working oil circuit P21. The second working connecting oil circuit P22 is formed in the cylindrical protrusion 13 of the housing 1. In the present embodiment, the second working connecting oil circuit P22 has: an axial groove P22a formed to extend along the axial direction L at the abutment portion between the outer circumferential surface of the inner protrusion 131 and the inner circumferential surface of the outer protrusion 132; a circumferential groove P22b formed to extend along the circumferential direction at the outer circumferential surface of the outer protrusion 132; and a connecting hole P22c formed along the radial direction R in a manner to connect the above-mentioned axial groove P22a with the above-mentioned circumferential groove P22b.

[0119] The second radial oil passage P23 is an oil passage formed in the second side wall portion 12 of the housing 1. The second radial oil passage P23 is formed along the radial direction R.

[0120] like Figure 4 As shown, in the present embodiment, the vehicle drive device 100 is provided with an oil circuit for supplying oil to the first friction member 41 to lubricate the first friction member 41. The oil circuit includes a first lubricating oil circuit P31, a lubricating connecting oil circuit P32, and a first in-shaft oil circuit P33. In addition, the oil supplied to the first friction member 41 in this way also plays a role in cooling the first friction member 41.

[0121] The first lubricating oil passage P31 is an oil passage for supplying the lubricating oil of the first friction member 41 to the first communicating hole 44a of the first inner support member 44. The first lubricating oil passage P31 is formed to extend from the inner peripheral surface to the outer peripheral surface of the input cylindrical portion 1a in the input member 1. In the present embodiment, the first lubricating oil passage P31 is communicated with the space between the first piston portion 42 and the first inner support member 44. The first communicating hole 44a is equivalent to a "second supply hole" that penetrates the first inner support member 44 in the radial direction R. In the present embodiment, the first communicating hole 44a is formed as the first cylindrical support portion 441 that penetrates the first inner support member 44 in the radial direction R.

[0122] The lubricating connecting oil path P32 is an oil path connecting the first lubricating oil path P31 and the first in-shaft oil path P33. The lubricating connecting oil path P32 is formed in the insertion portion Ma of the speed change input shaft M. In the present embodiment, the lubricating connecting oil path P32 is formed along the radial direction R from the first in-shaft oil path P33 inside the insertion portion Ma to the outer peripheral surface.

[0123] The first in-shaft oil passage P33 is an oil passage formed inside the speed change input shaft M. In the present embodiment, the first in-shaft oil passage P33 is formed along the axial direction L. In the present embodiment, the first in-shaft oil passage P33 is formed independently of the second in-shaft oil passage P13.

[0124] In the present embodiment, the oil flowing in the first shaft inner oil passage P33, the lubrication connection oil passage P32, and the first lubricating oil passage P31 in sequence flows into the space between the first piston portion 42 and the first inner support member 44. Moreover, the oil flowing into the space branches to the space between the first inner support member 44 and the oil passage forming member 45 and the space (first release oil chamber 47) between the first piston portion 42 and the oil passage forming member 45 and flows toward the radial outer side R2. Here, the space between the first piston portion 42 and the oil passage forming member 45, that is, the first release oil chamber 47 is formed as a space that is closed except for the communicating portion communicating with the first lubricating oil passage P31. Therefore, after the first release oil chamber 47 becomes filled with oil, the oil from the first lubricating oil passage P31 mainly flows into the space between the first inner support member 44 and the oil passage forming member 45. Then, the oil flowing into the space between the first inner support member 44 and the oil path forming member 45 passes through the radial groove 45a and reaches the inner peripheral portion of the first cylindrical support portion 441. In the present embodiment, such an oil flow path to the inner peripheral portion of the first cylindrical support portion 441 functions as a supply portion SP that supplies oil to the inner peripheral portion of the first inner support member 44 from the radial inner side R1.

[0125] The oil supplied to the inner circumference of the first cylindrical support portion 441 passes through the first communicating hole 44a and reaches the first friction member 41. In this way, the first friction member 41 is lubricated and cooled by the oil. Thereafter, the oil supplied to the first friction member 41 passes through the gap between the first inner friction material 411 and the first outer friction material 412 and reaches the inner circumference of the cylindrical portion 21.

[0126] like Figure 3 As shown, in the present embodiment, the oil supplied to the inner circumference of the cylindrical portion 21 is supplied to the oil path for cooling the rotor Ro through the rotor cooling hole 21b. The rotor cooling hole 21b is equivalent to the "first supply hole" connected to the oil path for cooling the rotor Ro. In the present embodiment, the gap G between the outer circumferential surface of the cylindrical portion 21 and the inner circumferential surface of the rotor core Roc functions as the oil path for cooling the rotor Ro. In this example, the oil supplied to the gap G flows along the inner circumferential surface of the rotor core Roc in the axial direction L to cool the rotor Ro, and then is discharged from the discharge hole not shown and supplied to the coil end Ce of the stator St and the like.

[0127] In the present embodiment, the rotor cooling hole 21b is formed on the second axial side L2 relative to the annular member 10 so as to open to the inner peripheral portion of the cylindrical portion 21. In addition, in the present embodiment, the rotor cooling hole 21b is formed on the second axial side L2 relative to the protrusion 21a so as to open to the outer peripheral portion of the cylindrical portion 21. In the example shown in the figure, two rotor cooling holes 21b are formed in parallel along the axial direction L.

[0128] like Figure 4 As shown, in the present embodiment, the vehicle drive device 100 is provided with an oil passage for supplying oil to the second friction member 51 to lubricate the second friction member 51. The oil passage includes a second lubricating oil passage P41 and a first radial oil passage P42. In addition, the oil supplied to the second friction member 51 in this way also plays a role in cooling the second friction member 51.

[0129] The second lubricating oil passage P41 is an oil passage for supplying lubricating oil of the second friction member 51 to the second communicating hole 54a of the second inner supporting member 54. The second communicating hole 54a is formed to penetrate the second inner supporting member 54 in the radial direction R. In the present embodiment, the second communicating hole 54a is formed to penetrate the second cylindrical supporting portion 541 of the second inner supporting member 54 in the radial direction R.

[0130] The second lubricating oil passage P41 is formed in the cylindrical protrusion 13 of the housing 1. In the present embodiment, the second lubricating oil passage P41 includes: an axial groove P41a formed to extend along the axial direction L at the abutment portion between the outer circumferential surface of the inner protrusion 131 and the inner circumferential surface of the outer protrusion 132; a cylindrical oil passage P41b formed to be surrounded by the inner circumferential surface of the outer protrusion 132 at a position closer to the axial first side L1 than the end of the inner protrusion 131 on the axial first side L1; and a connecting hole P41c formed along the radial direction R in a manner to connect the cylindrical oil passage P41b to the outer circumferential surface of the outer protrusion 132.

[0131] The first radial oil passage P42 is an oil passage formed in the second side wall portion 12 of the housing 1. The first radial oil passage P42 is formed along the radial direction R. In the present embodiment, the first radial oil passage P42 is formed independently of the second radial oil passage P23.

[0132] In the present embodiment, the oil flowing sequentially through the first radial oil passage P42 and the second lubricating oil passage P41 flows into the space between the flange portion 22 and the second inner support member 54 from the openings of the connecting hole P41c and the end portion of the cylindrical oil passage P41b on the first axial side L1.

[0133] Moreover, of the oil that flows in from the connecting hole P41c, the oil that flows in from the connecting hole P41c sequentially passes through the first through hole 24a and the second through hole 231a to reach the second release oil chamber 58. The first through hole 24a is formed to penetrate the fitting component 24 in the radial direction R. The fitting component 24 is a component that is fitted to the inner peripheral surface of the inner cylindrical portion 231 of the cylinder forming portion 23 in a manner that abuts against the second bearing B2 from the first axial side L1. The second through hole 231a is formed to penetrate the inner cylindrical portion 231 of the cylinder forming portion 23 in the radial direction R. The opening portion of the radially outer side R2 of the second through hole 231a opens in the second release oil chamber 58. Here, the second release oil chamber 58 is formed as a space that is closed except for the communicating portion that communicates with the second through hole 231a. Therefore, after the second cancel oil chamber 58 is filled with oil, the oil from the second lubricating oil passage P41 flows out mainly from the opening at the end portion on the first axial side L1 of the cylindrical oil passage P41 b.

[0134] Thus, the oil flowing out from the opening of the end portion of the tubular oil passage P41 b on the first axial side L1 passes between the fitting member 24 and the second radially extending portion 542 of the second inner support member 54 , and further passes through the second communication hole 54 a to reach the second friction member 51 .

[0135] Below, refer to Figure 5 as well as Figure 6 An example of an operation of assembling the first assembly AS1 including the rotor Ro, the rotor support member 2, and the first engaging device CL1 to the second assembly AS2 separated from the first assembly AS1 is described. In this example, an operation of assembling the first assembly AS1 including the rotor Ro, the rotor support member 2, and the first engaging device CL1 to the second assembly AS2 including the transmission TM is performed (refer to Figure 6 ). In this example, the first assembly AS1 is manufactured as follows.

[0136] First, if Figure 5 As shown, the rotor support member 2, the rotor Ro, the rotating body 31 of the rotation sensor 3, the second piston portion 52, the mounting member 57, and the second outer support member 55 are assembled so that they rotate integrally. In addition, the second bearing B2 is assembled to the rotor support member 2. The second bearing B2 is inserted into the radial inner side R1 of the inner cylindrical portion 231 from the axial first side L1 so that the outer peripheral surface of the second bearing B2 contacts the inner peripheral surface of the inner cylindrical portion 231 of the cylinder forming portion 23. Thereafter, the fitting member 24 is fitted into the inner peripheral surface of the inner cylindrical portion 231 so that it contacts the second bearing B2 from the axial first side L1.

[0137] Next, in a state where the second inner friction members 511 and the second outer friction members 512 are arranged alternately in parallel in the axial direction L, the second cylindrical support portion 541 of the second inner support member 54 is spline-engaged with the plurality of second inner friction members 511. Furthermore, the plurality of second outer friction members 512 are spline-engaged with the second outer support member 55, and the contact member 56 that contacts the second outer friction member 512 closest to the first axial side L1 from the first axial side L1 is spline-engaged with the cylindrical portion 21. Thereafter, in a state where the contact member 56 is located on the second axial side L2 relative to the first fixing groove 21c formed in the inner circumference of the cylindrical portion 21, the fixing member 56a is mounted in the first fixing groove 21c. The first fixing groove 21c is a groove formed continuously in the circumferential direction in the inner circumference of the cylindrical portion 21.

[0138] Next, in a state where the first inner friction member 411 and the first outer friction member 412 are arranged alternately and parallelly in the axial direction L, the first cylindrical support portion 441 of the first inner support member 44 is spline-engaged with the plurality of first inner friction members 411. Here, the first inner support member 44 is integrally connected to the input member I. Furthermore, the oil path forming member 45, the first piston portion 42, and the oil chamber forming member 46 are assembled to the input member I. Thus, the input member I, the first inner support member 44, the oil path forming member 45, the first piston portion 42, and the oil chamber forming member 46 are connected in a manner of integral rotation. Furthermore, the plurality of first outer friction members 412 are spline-engaged with the cylindrical portion 21. Thereafter, in a state where the first pressing portion 422 of the first piston portion 42 is located on the axial second side L2 relative to the second fixing groove 21d formed on the inner circumference of the cylindrical portion 21, the annular member 10 is mounted on the second fixing groove 21d. Furthermore, the second fixing groove 21d is arranged closer to the first side L1 in the axial direction than the first fixing groove 21c.

[0139] like Figure 6 As shown in the figure, the first component AS1 is assembled to the second component AS2 in a state where the first component AS1 is maintained in a posture in such a manner that the rotation axis (axial direction L) of the rotor Ro is along the vertical direction. In this example, the first component AS1 is held by a holding device (not shown) in such a manner that the second engagement device CL2 is located below the first engagement device CL1. On the other hand, the second component AS2 is configured such that the insertion portion Ma of the speed change input shaft M is directed upward. Furthermore, the first component AS1 is brought close to the second component AS2 from above, and the insertion portion Ma of the speed change input shaft M is inserted into the radial inner side R1 of the input cylindrical portion Ia of the input component I.

[0140] At this time, due to the deadweight of the rotor Ro and the like supported by the cylindrical portion 21 of the rotor support member 2, the rotor support member 2 including the cylindrical portion 21 spline-engaged with the first outer friction member 412 moves downward relative to the input member I together with the second engagement device CL2 and the second inner support member 54 and the like. However, the annular member 10 fixed to the inner peripheral portion of the cylindrical portion 21 abuts against the first pressing portion 422 of the first piston portion 42 from above, thereby restricting the further downward movement of the rotor support member 2 and the like. Thus, the first outer friction member 412 can be restricted from relatively moving to a position above the opening of the axial first side L1 of the rotor support member 2. Therefore, the spline engagement between the first outer friction member 412 and the cylindrical portion 21 can be released, and the rotor support member 2 and the like can be restricted from falling off. That is, a structure is provided that can restrict a part of the first assembly AS1 from falling off through the opening of the rotor support member 2.

[0141] In addition, at this time, the above formula (1) holds true, so even if the positions of the input member 1 and the axial center of the rotor support member 2 are offset so that the outer peripheral portion of the first piston portion 42 contacts the inner peripheral surface of the cylindrical portion 21, the annular member 10 can maintain a state of overlapping with the first piston portion 42 when viewed in the axial direction. Therefore, it becomes a structure that can highly reliably restrict a part of the first assembly AS1 from falling off through the opening of the rotor support member 2.

[0142] At this time, due to the deadweight of the second engagement device CL2, etc., the second outer support member 55 supporting the second outer friction member 512 moves downward together with the second inner support member 54, etc. However, further downward movement of the second outer support member 55 is restricted by the flange portion 22. In addition, downward movement of the second piston portion 52 is also restricted by the flange portion 22.

[0143] Furthermore, the stator St, the first bearing B1, and the first side wall portion 11 of the third bearing B3 are assembled and mounted in the first assembly AS1. This assembly operation may be performed either before or after the assembly operation of the first assembly AS1 to the second assembly AS2.

[0144] [Other implementation methods]

[0145] (1) In the above-mentioned embodiment, the first outer supporting member 48 is described as an example in which the first outer supporting member 48 is integrally formed with the cylindrical portion 21. However, the present invention is not limited to such a structure, and the first outer supporting member 48 may be a separate member independent of the cylindrical portion 21, similarly to the second outer supporting member 55.

[0146] (2) In the above-mentioned embodiment, the rotor cooling hole 21b as the first supply hole is formed on the second axial side L2 relative to the protrusion 21a so as to open to the outer peripheral portion of the cylindrical portion 21. However, the present invention is not limited to such a structure. For example, the rotor cooling hole 21b may be formed on the first axial side L1 relative to the protrusion 21a so as to open to the outer peripheral portion of the cylindrical portion 21. Alternatively, the rotor cooling hole 21b may be not provided.

[0147] (3) In the above-mentioned embodiment, the gap G between the outer peripheral surface of the cylindrical portion 21 and the inner peripheral surface of the rotor core Roc is used as an example to explain the structure that functions as an oil path for cooling the rotor Ro, but the present invention is not limited to such a structure. The oil path for cooling the rotor Ro may be formed in any one of the rotor support member 2, the holding member H, and the rotor Ro, or in the gap at the boundary between them. For example, the oil path for cooling the rotor Ro may be formed in the gap at the boundary between the holding member H and the rotor Ro.

[0148] (4) In the above-mentioned embodiment, the supply portion SP for supplying oil to the inner peripheral portion of the first inner support member 44 from the radial inner side R1 is described as an example of a structure in which the first communicating hole 44a is formed as the second supply hole penetrating the first inner support member 44 in the radial direction R. However, the present invention is not limited to such a structure, and for example, the first communicating hole 44a may not be formed, and the oil may be supplied to the first friction member 41 from a direction other than the radial inner side R1. Alternatively, the structure may be a structure without the supply portion SP.

[0149] (5) In the above-mentioned embodiment, the second engaging device CL2 is arranged adjacent to the first engaging device CL1 on the second side L2 in the axial direction. However, the present invention is not limited to such a structure. For example, the second engaging device CL2 may be arranged at a position offset in the radial direction R relative to the first engaging device CL1. Alternatively, the second engaging device CL2 may not be provided.

[0150] (6) In the above-mentioned embodiment, the case where the input component I is held in such a manner that the second engaging device CL2 is located below the first engaging device CL1 when the first component AS1 and the second component AS2 are assembled is described as an example. However, the method is not limited to such a method, and the rotor support component 2 may be held in such a manner that the second engaging device CL2 is located above the first engaging device CL1 when the first component AS1 and the second component AS2 are assembled. In this case, the first pressing portion 422 of the first piston portion 42 abuts against the annular component 10 from above, thereby restricting further downward movement of the first engaging device CL1 and the input component I, etc. Therefore, even in this method, it is possible to restrict a part of the first component AS1 from falling off through the opening of the rotor support component 2.

[0151] (7) In the above-mentioned embodiment, the power transmission mechanism T is described as a transmission TM that has a plurality of gears with different gear ratios and changes the speed of the rotation transmitted from the rotating electrical machine MG side at a gear ratio corresponding to the formed gear. However, the present invention is not limited to such a structure. For example, the power transmission mechanism T may be a fixed gear ratio transmission (reducer or speed increaser) that changes the speed of the rotation transmitted from the rotating electrical machine MG side at a constant gear ratio. Alternatively, the power transmission mechanism T may be configured to transmit the rotation transmitted from the rotating electrical machine MG side to the gear output gear G1 at the same rotation speed.

[0152] (8) In the above-mentioned embodiment, the vehicle drive device 100 is described as an example in which the vehicle drive device 100 is configured as a drive device for a hybrid vehicle of a motor parallel type. However, it is not limited to such a structure. The vehicle drive device 100 can be a drive device for a hybrid vehicle of a so-called series-parallel type having an internal combustion engine EG and two rotating electrical machines, or it can be a drive device for a hybrid vehicle of a so-called split type having an internal combustion engine EG, two rotating electrical machines, and a differential gear mechanism (such as a planetary gear mechanism) for power distribution, and using the differential gear mechanism to distribute the driving force of the internal combustion engine EG to the first rotating electrical machine that mainly functions as a generator, and the wheels, and the second rotating electrical machine that mainly functions as a motor.

[0153] (9) In addition, the structures disclosed in the above-mentioned embodiments can also be combined with the structures disclosed in other embodiments for application as long as no contradiction occurs. With regard to other structures, the embodiments disclosed in this specification are merely illustrative in all aspects. Therefore, various changes can be appropriately made within the scope of the present disclosure.

[0154] [Overview of the above-mentioned embodiment]

[0155] Hereinafter, the outline of the vehicle drive device 100 described above will be described.

[0156] The vehicle driving device 100 includes:

[0157] An input component I is drivingly connected to the internal combustion engine EG;

[0158] The rotary electric machine MG includes a stator St and a rotor Ro disposed on an inner side R1 in the radial direction R relative to the stator St, and functions as a driving force source for the wheels W.

[0159] The power transmission mechanism T transmits the rotation transmitted from the rotating electrical machine MG to the wheel.

[0160] A rotor support member 2 for supporting the rotor Ro; and

[0161] The first engagement device CL1 includes a first friction plate 412 and a second friction plate 411 arranged in parallel along the axial direction L, and a first piston portion 42 for pressing the first friction plate 412 and the second friction plate 411 along the axial direction L.

[0162] The first engagement device CL1 is disposed in a power transmission path between the input member I and the rotary electric machine MG.

[0163] The vehicle driving device 100 further includes:

[0164] a first outer supporting member 48 for supporting the first friction plate 412 from an outer side R2 in the radial direction R; and

[0165] The first inner support member 44 supports the second friction plate 411 from the inner side R1 in the radial direction R.

[0166] The first inner support member 44 includes: a cylindrical support portion 441 formed in a cylindrical shape extending along the axial direction L and supporting the second friction plate 411; and a radially extending support portion 442 formed in a manner extending from the cylindrical support portion 441 to the inner side R1 of the radial direction R.

[0167] The radially extending support portion 442 is connected to the input member I in such a manner that the input member I rotates integrally with the first inner support member 44.

[0168] The first piston portion 42 is disposed on the first axial side L1 which is one side in the axial direction L with respect to the radially extending support portion 442.

[0169] The rotor support member 2 includes: a cylindrical portion 21 formed in a cylindrical shape extending along the axial direction L and supporting the rotor Ro from the inner side R1 in the radial direction R; and a flange portion 22 formed in a manner extending along the radial direction R on the inner side R1 in the radial direction R relative to the cylindrical portion 21 and connected to the cylindrical portion 21.

[0170] The first engagement device CL1 is disposed on the first axial side L1 relative to the flange portion 22 and on the inner side R1 in the radial direction R relative to the common cylindrical portion 21.

[0171] The first outer supporting member 48 is configured to open toward the first axial side L1 and to rotate integrally with the cylindrical portion 21.

[0172] An annular member 10 formed in an annular shape extending in the circumferential direction is fixed to the inner circumference of the cylindrical portion 21.

[0173] The annular member 10 is disposed at the axial first side L1 relative to the first friction plate 412 and the second friction plate 411 and overlaps at least one of the first piston portion 42 and the second friction plate 411 when viewed along the axial direction L.

[0174] According to this structure, when the first assembly AS1 including the rotor Ro, the rotor support member 2, and the first engagement device CL1 is assembled to the second assembly AS2 separated from the first assembly AS1, even if the first engagement device CL1 moves relative to the rotor support member 2 to the first axial side L1, at least one of the first piston portion 42 and the second friction plate 411 contacts the annular member 10. As a result, the first friction plate 412 of the first engagement device CL1 can be restricted from moving relative to the position closer to the first axial side L1 than the opening of the rotor support member 2 on the first axial side L1. In other words, the first friction plate 412 can be restricted from falling off from the rotor support member 2. Therefore, the following structure is obtained: when the first assembly AS1 including the rotor Ro, the rotor support member 2, and the first engagement device CL1 is assembled to the second assembly AS2 separated from the first assembly AS1, a part of the first assembly AS1 can be restricted from falling off through the opening of the rotor support member 2.

[0175] Here, it is preferred that the diameter of the inner circumference of the cylindrical portion 21 is set to D1.

[0176] The outermost diameter of the first piston portion 42 is set to D2.

[0177] The distance in the radial direction R from the inner peripheral surface of the cylindrical portion 21 to the inner peripheral end of the annular member 10 is defined as D3.

[0178] D1-D2<D3.

[0179] According to this structure, even when the input member 1 is eccentric and the outer peripheral portion of the first piston portion 42 contacts the inner peripheral surface of the cylindrical portion 21, the state in which the annular member 10 overlaps with the first piston portion 42 when viewed in the axial direction can be maintained. Therefore, when the first assembly AS1 is assembled to the second assembly AS2, it is possible to restrict a part of the first assembly AS1 from falling off through the opening of the rotor support member 2 with high reliability.

[0180] In addition, it is preferred that the cylindrical portion 21 is formed with a first supply hole 21b that communicates with the oil passage G for cooling the rotor Ro.

[0181] The first supply hole 21 b is formed to open in the inner peripheral portion of the cylindrical portion 21 on the axial second side L2 which is the side opposite to the axial first side L1 with respect to the annular member 10 .

[0182] According to this configuration, the oil supplied to the inner circumference of the tubular portion 21 is restricted from flowing toward the axial first side L1 by the annular member 10, so that a large amount of oil can be supplied to the first supply hole 21b. Thus, the rotor Ro can be efficiently cooled through the first supply hole 21b.

[0183] In addition, it is preferable to further include a supply portion SP that supplies oil from the inner side R1 in the radial direction R to the inner peripheral portion of the first inner supporting member 44.

[0184] The first inner supporting member 44 is provided with a second supply hole 44 a penetrating the first inner supporting member 44 in the radial direction R.

[0185] According to this structure, the centrifugal force of the rotating member such as the rotor support member 2 provided in the vehicle drive device 100 can be used to appropriately supply oil to the inner peripheral portion of the first inner support member 44 from the inner side R1 in the radial direction R. Furthermore, the oil supplied to the inner peripheral portion of the first inner support member 44 can be supplied to the second friction plate 411 through the second supply hole 44a. Therefore, the paired first friction plate 412 and second friction plate 411 can be appropriately lubricated and cooled.

[0186] In addition, it is preferred to also have:

[0187] The second engagement device CL2 includes a third friction plate 512 and a fourth friction plate 511 arranged in parallel along the axial direction L, and a second piston portion 52 for pressing the third friction plate 512 and the fourth friction plate 511 along the axial direction L.

[0188] a second outer supporting member 55 for supporting the third friction plate 512 from an outer side R2 in the radial direction R; and

[0189] The second inner support member 54 supports the fourth friction plate 511 from the inner side R1 in the radial direction R.

[0190] The second engagement device CL2 is disposed adjacent to the first engagement device CL1 on the second axial side L2 which is opposite to the first axial side L1.

[0191] The second outer supporting member 55 is configured to rotate integrally with the rotor supporting member 2.

[0192] The second piston portion 52 is supported so as to rotate integrally with the rotor support member 2 .

[0193] According to this structure, the flange portion 22 is arranged on the axial second side L2 relative to the second engaging device CL2. Thus, the flange portion 22 can be used to restrict the movement of the second engaging device CL2 to the axial second side L2. Therefore, when the first assembly AS1 in which the rotor Ro, the rotor support member 2, the first engaging device CL1, and the second engaging device CL2 are integrally assembled is assembled to the second assembly AS2 separated from the first assembly AS1, the opening of the rotor support member 2 is directed upward, thereby restricting the second engaging device CL2 from falling off from the rotor support member 2.

[0194] Preferably, in the structure including the second engagement device CL2,

[0195] The flange portion extends to a position further inward in the radial direction than the second engagement device.

[0196] According to this structure, when the first assembly AS1 is assembled to the second assembly AS2 in a state where the opening of the rotor support member 2 faces upward, the second engagement device CL2 can be restricted from falling off from the rotor support member 2 with high reliability.

[0197] Furthermore, it is preferable that the second engagement device CL2 is disposed in a power transmission path between the rotary electric machine MG and the power transmission mechanism T.

[0198] According to this structure, by switching the engagement state of the first engagement device CL1 and the second engagement device CL2, it is possible to switch between a state in which only the rotating electric machine MG of the internal combustion engine EG is connected to the power transmission mechanism T, a state in which both the rotating electric machine MG and the internal combustion engine EG are connected to the power transmission mechanism T, and a state in which the rotating electric machine MG and the internal combustion engine EG are connected but separated from the power transmission mechanism T.

[0199] Furthermore, it is preferable that the power transmission mechanism T is a transmission TM including a plurality of speed stages having different speed ratios and which changes the speed of the rotation transmitted from the rotating electrical machine MG at a speed ratio corresponding to the formed speed stage.

[0200] According to this configuration, the driving force transmitted to the wheels W can be changed as necessary.

[0201] Industrial Application Possibility

[0202] The technology disclosed herein can be applied to a vehicle drive device comprising: an input component connected to an internal combustion engine drive; a rotating electric machine having a stator and a rotor arranged radially inwardly relative to the stator and functioning as a driving force source for a wheel; a power transmission mechanism that transmits the rotation transmitted from the rotating electric machine side to the wheel side; a rotor support component that supports the rotor; and a friction engagement device.

Claims

1. A vehicle drive device comprising: An input component, drivingly connected to the internal combustion engine; A rotating electric machine having a stator and a rotor arranged radially inwardly of the stator, and functioning as a driving force source for wheels; A power transmission mechanism transmits the rotation transmitted from the rotating electric machine side to the wheel side; a rotor supporting member for supporting the rotor; and The first engagement device includes a first friction plate and a second friction plate arranged in parallel in the axial direction, and a first piston portion for pressing the first friction plate and the second friction plate in the axial direction. The first engagement device is arranged in a power transmission path between the input member and the rotating electrical machine. The vehicle drive device further comprises: a first outer supporting member for supporting the first friction plate from the outer side in the radial direction; and a first inner supporting member for supporting the second friction plate from the inner side in the radial direction; The first inner support member includes: a cylindrical support portion formed in a cylindrical shape extending along the axial direction and supporting the second friction plate; and a radially extending support portion formed in a manner extending from the cylindrical support portion toward the inner side in the radial direction. The radially extending support portion is connected to the input member so that the input member and the first inner support member rotate integrally. The first piston portion is arranged on a first axial side, which is one axial side, relative to the radially extending support portion. The rotor support member comprises: a cylindrical portion formed in a cylindrical shape extending in the axial direction and supporting the rotor from the inner side in the radial direction; and a flange portion formed in a manner extending in the radial direction with respect to the inner side of the cylindrical portion and connected to the cylindrical portion. The first engaging device is arranged on the first side in the axial direction relative to the flange portion and on the inner side in the radial direction relative to the cylindrical portion. The first outer supporting member is configured to open toward the first side in the axial direction and to rotate integrally with the cylindrical portion. An annular member formed into an annular shape extending in the circumferential direction is fixed to the inner circumference of the cylindrical portion. The annular member is arranged at a position on the first side in the axial direction relative to the first friction plate and the second friction plate and overlaps with at least one of the first piston portion and the second friction plate when viewed in the axial direction along the axial direction. The first piston portion abuts against the second friction plate from the axial first side on the annular member at the axial second side opposite to the axial first side, thereby pressing the first friction plate and the second friction plate in the axial direction.

2. The vehicle drive device according to claim 1, wherein: The diameter of the inner circumference of the cylindrical portion is set to D1. The outermost diameter of the first piston portion is set to D2, The radial distance from the inner peripheral surface of the cylindrical portion to the inner peripheral end of the annular member is defined as D3. D1-D2<D3.

3. The vehicle drive device according to claim 1, wherein: The cylindrical portion is provided with a first supply hole connected to an oil passage for cooling the rotor. The first supply hole is formed to open in the inner peripheral portion of the cylindrical portion on the second axial side which is the side opposite to the first axial side with respect to the annular member.

4. The vehicle drive device according to claim 2, wherein: The cylindrical portion is provided with a first supply hole connected to an oil passage for cooling the rotor. The first supply hole is formed to open in the inner peripheral portion of the cylindrical portion on the second axial side which is the side opposite to the first axial side with respect to the annular member.

5. The vehicle drive device according to claim 1, wherein: further comprising a supply portion that supplies oil to the inner peripheral portion of the first inner supporting member from the inner side in the radial direction, The first inner supporting member is formed with a second supply hole that penetrates the first inner supporting member in the radial direction.

6. The vehicle drive device according to claim 2, wherein: further comprising a supply portion that supplies oil to the inner peripheral portion of the first inner supporting member from the inner side in the radial direction, The first inner supporting member is formed with a second supply hole that penetrates the first inner supporting member in the radial direction.

7. The vehicle drive device according to claim 3, wherein: further comprising a supply portion that supplies oil to the inner peripheral portion of the first inner supporting member from the inner side in the radial direction, The first inner supporting member is formed with a second supply hole that penetrates the first inner supporting member in the radial direction.

8. The vehicle drive device according to claim 4, wherein: further comprising a supply portion that supplies oil to the inner peripheral portion of the first inner supporting member from the inner side in the radial direction, The first inner supporting member is formed with a second supply hole that penetrates the first inner supporting member in the radial direction.

9. The vehicle drive device according to any one of claims 1 to 8, wherein: Also available: a second engaging device including a third friction plate and a fourth friction plate arranged in parallel along the axial direction, and a second piston portion for pressing the third friction plate and the fourth friction plate along the axial direction; a second outer supporting member that supports the third friction plate from the outer side in the radial direction; and a second inner supporting member for supporting the fourth friction plate from the inner side in the radial direction, The second engagement device is disposed adjacent to the first engagement device on the second axial side which is opposite to the first axial side. The second outer support member is configured to rotate integrally with the rotor support member. The second piston portion is supported so as to rotate integrally with the rotor support member.

10. The vehicle drive device according to claim 9, wherein: The flange portion extends to a position further inward in the radial direction than the second engagement device.

11. The vehicle drive device according to claim 9, wherein: The second engagement device is disposed in a power transmission path between the rotating electrical machine and the power transmission mechanism.

12. The vehicle drive device according to claim 10, wherein: The second engagement device is disposed in a power transmission path between the rotating electrical machine and the power transmission mechanism.

13. The vehicle drive device according to any one of claims 1 to 8 and 10 to 12, wherein: The power transmission mechanism is a transmission that includes a plurality of speed stages having different speed ratios and changes the speed of the rotation transmitted from the rotating electric machine at a speed ratio corresponding to the formed speed stage.

14. The vehicle drive device according to claim 9, wherein: The power transmission mechanism is a transmission that includes a plurality of speed stages having different speed ratios and changes the speed of the rotation transmitted from the rotating electric machine at a speed ratio corresponding to the formed speed stage.

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