Vehicle drive device

Abstract

The invention relates to a vehicle drive device. A differential gear mechanism (6) housed in a differential housing (5) is provided with a shaft member (61), a plurality of first bevel gears (62) rotatably supported by the shaft member, and a pair of second bevel gears (63) meshing with the plurality of first bevel gears, and one of the pair of second bevel gears disposed on the second side (L2) in the axial direction with respect to the shaft member (61) is set as a specific bevel gear (63S). Among the pair of output shafts (2), an output shaft that rotates integrally with a specific bevel gear (63S) is set as a specific output shaft (2S), the specific bevel gear is supported by the differential housing (5) in the axial direction (L) but is not supported by the differential housing (5) in the radial direction (R), and an engagement portion (2a) provided on the specific output shaft and an engaged portion (6a) provided on the specific bevel gear engage with each other. Therefore, the relative movement of the specific output shaft and the specific bevel gear in the circumferential direction and the radial direction is limited.

Description

Technical Field

[0001] The present invention relates to a vehicle drive device comprising an input member drivingly connected to a driving force source, a pair of output shafts each drivingly connected to a wheel, a speed reducer for reducing the rotation of the input member, and a differential gear device for distributing the rotation of the input member transmitted via the speed reducer to the pair of output shafts. 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, the reference numerals of Patent Document 1 are cited in parentheses.

[0003] The differential gear device (5) of the vehicle drive device (1) of Patent Document 1 includes a differential case (50) and a differential gear mechanism housed in the differential case. The differential gear mechanism includes: a shaft member (51) formed in a manner extending in a radial direction, a first bevel gear (52) supported by the shaft member so as to be rotatable, and a pair of second bevel gears (54A, 54B) arranged on both sides of the shaft member (51) in an axial direction and meshing with the first bevel gear (52). One second bevel gear (54A) is connected to a first drive shaft (9A) in a manner rotating as a whole, and the other second bevel gear (54B) is connected to a second drive shaft (9B) in a manner rotating as a whole.

[0004] Patent Document 1: Japanese Patent Application Publication No. 2021-107737

[0005] In the above-mentioned vehicle drive device (1), another second bevel gear (54B) includes: a bevel tooth portion meshing with the first bevel gear (52), a bevel tooth support portion formed integrally with the bevel tooth portion and supporting the bevel tooth portion, and a cylindrical shaft portion (540) formed in a cylindrical shape and extending and protruding from the bevel tooth support portion to one side in the axial direction (the left side in Figure 4 of Patent Document 1).

[0006] The cylindrical shaft portion (540) is supported from the radially outer side by the differential case cylindrical portion (72) provided by the differential case (50). In addition, the bevel gear support portion is supported in the axial direction by the inner side surface of the differential case (50) via a gasket inserted through the cylindrical shaft portion (540). In this way, the other second bevel gear (54B) is supported in the axial direction in addition to the radial direction. Therefore, the axial dimension of the other second bevel gear (54B) is likely to become larger.

[0007] In addition, the cylindrical shaft portion (540) is connected to the second drive shaft (9B) arranged radially inward relative to the cylindrical shaft portion (540) in a manner that rotates as a whole. Specifically, the cylindrical shaft portion (540) includes: a clamped portion connected to a clamping portion formed at the front end of the second drive shaft (9B) by spline engagement, and a fitting portion for fitting a portion of the second drive shaft (9B) adjacent to the clamping portion in the axial direction. In this way, the cylindrical shaft portion (540) is restricted from relative rotation relative to the second drive shaft (9B) by the clamped portion, and the deviation and inclination of the rotation axis of the other second bevel gear (54B) and the rotation axis of the second drive shaft (9B) are restricted by the fitting portion. In this way, the cylindrical shaft portion (540) becomes a structure in which the clamped portion and the fitting portion are arranged in parallel in the axial direction. Therefore, the axial dimension of the other second bevel gear (54B) tends to become larger.

[0008] The structure of the second bevel gear as described above leads to an increase in the size of the vehicle drive device. Therefore, it is desired to realize a vehicle drive device that can be easily miniaturized in a structure including a bevel gear type differential gear device. Summary of the invention

[0009] In view of the above situation, the characteristic structure of the vehicle drive device is the following aspects, that is, it has:

[0010] An input member drivingly coupled to a driving force source;

[0011] A pair of output shafts, each of which is drive-connected to a wheel;

[0012] a speed reducer that reduces the speed of rotation of the input member; and

[0013] A differential gear device distributes the rotation of the input member transmitted via the speed reducer to the pair of output shafts, wherein:

[0014] The direction along the rotation axis of the pair of output shafts, i.e., the output rotation axis, is defined as an axial direction, one side of the axial direction is defined as an axial first side, the other side of the axial direction is defined as an axial second side, the direction orthogonal to the output rotation axis is defined as a radial direction, and the direction around the output rotation axis is defined as a circumferential direction,

[0015] The differential gear device includes a differential case and a differential gear mechanism accommodated in the differential case.

[0016] The differential gear mechanism comprises: a shaft member formed in a manner extending in the radial direction, a plurality of first bevel gears rotatably supported by the shaft member and arranged separately in the circumferential direction, and a pair of second bevel gears arranged separately on both sides of the shaft member in the axial direction and meshing with the plurality of first bevel gears.

[0017] The pair of second bevel gears are connected to the pair of output shafts in a manner of integral rotation.

[0018] One of the pair of second bevel gears that is arranged on the second side in the axial direction relative to the shaft member is set as a specific bevel gear, and one of the pair of output shafts that rotates integrally with the specific bevel gear is set as a specific output shaft.

[0019] The engaging portion provided on the specific output shaft and the engaged portion provided on the specific bevel gear are engaged with each other so as to restrict relative movement of the specific output shaft and the specific bevel gear in the circumferential direction and the radial direction.

[0020] The specific bevel gear is supported by the differential case in the axial direction, but is not supported by the differential case in the radial direction.

[0021] According to this characteristic structure, the specific bevel gear is not supported by the differential case in the radial direction, but is supported in the radial direction by the centering effect generated by the meshing of the specific bevel gear and the plurality of first bevel gears. Therefore, the bearing and the fitting part for radially supporting the specific bevel gear on the differential case are not required.

[0022] In addition, according to this characteristic structure, the engaging portion of the specific output shaft and the engaged portion of the specific bevel gear are configured to restrict circumferential relative movement and radial relative movement. Therefore, it is not necessary to provide an engaging portion on the specific bevel gear that engages with the specific output shaft and is used to restrict the deviation or tilt of the rotation axis of the specific output shaft and the rotation axis of the specific bevel gear.

[0023] As described above, according to this characteristic structure, it is easy to achieve miniaturization of the support structure for the specific bevel gear and the specific output shaft of the differential case. Therefore, in the structure including the bevel gear type differential gear device, it is easy to achieve miniaturization of the vehicle drive device. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 It is a cross-sectional view along the axial direction of the vehicle drive device according to the embodiment.

[0025] Figure 2 It is a schematic diagram of a vehicle drive device according to an embodiment.

[0026] Figure 3 It is a partially enlarged view of a cross-sectional view along the axial direction of the vehicle drive device according to the embodiment. DETAILED DESCRIPTION

[0027] Hereinafter, a vehicle drive device 100 according to an embodiment will be described with reference to the drawings.

[0028] like Figure 1 as well as Figure 2As shown, the vehicle drive device 100 includes an input member 10 drivingly connected to a driving force source D, and each of the input members 10 is connected to a wheel W (see Figure 2 ) a pair of output shafts 2 connected by driving, a speed reducer 3 that reduces the rotation of the input member 10, and a differential gear device 4 that distributes the rotation of the input member 10 transmitted via the speed reducer 3 to the pair of output shafts 2.

[0029] In the following description, the direction along the output rotation axis X, which is the rotation axis of the pair of output shafts 2, is referred to as the "axial direction L". Furthermore, one side of the axial direction L is referred to as the "axial first side L1", and the other side of the axial direction L is referred to as the "axial second side L2". In addition, the direction orthogonal to the output rotation axis X is referred to as the "radial direction R". Furthermore, in the radial direction R, the output rotation axis X side is referred to as the "radial inner side R1", and the opposite side is referred to as the "radial outer side R2". In addition, the direction around the output rotation axis X is referred to as the "circumferential direction C".

[0030] In the present embodiment, the input member 10, the pair of output shafts 2, the speed reducer 3, and the differential gear device 4 are arranged on the same axis. That is, the input member 10, the pair of output shafts 2, the speed reducer 3, and the differential gear device 4 are arranged on the output rotation axis X. In addition, in the present embodiment, the input member 10, the speed reducer 3, and the differential gear device 4 are arranged in the order described from the axial first side L1 toward the axial second side L2.

[0031] In this embodiment, the vehicle drive device 100 further includes an outer case 9 that accommodates the input member 10, the speed reducer 3, and the differential gear device 4. In this embodiment, the outer case 9 includes a first case member 91, a second case member 92, a support member 93, and a cover member 94.

[0032] The first housing member 91 includes a first side wall portion 911 and a first peripheral wall portion 912. The first side wall portion 911 is formed to extend along the radial direction R. The first side wall portion 911 is configured to cover the differential gear device 4 from the axial second side L2. The first peripheral wall portion 912 is formed in a cylindrical shape having an axis along the axial direction L. The first peripheral wall portion 912 is configured to cover the reducer 3 and the differential gear device 4 from the radial outer side R2. In the illustrated example, the first side wall portion 911 and the first peripheral wall portion 912 are integrally formed in a manner such that the end portion of the radial outer side R2 of the first side wall portion 911 and the end portion of the axial second side L2 of the first peripheral wall portion 912 are connected. That is, the first housing member 91 is formed in a bottomed cylindrical shape that is open on the axial first side L1.

[0033] The second housing member 92 is formed of a member different from the first housing member 91. The second housing member 92 is joined to the first housing member 91 from the first axial side L1. The second housing member 92 includes a second peripheral wall portion 921. The second peripheral wall portion 921 is formed in a cylindrical shape having an axis along the axial direction L. The second peripheral wall portion 921 is configured to cover the rotating electrical machine 1 from the radially outer side R2. The second peripheral wall portion 921 is joined to the first peripheral wall portion 912 of the first housing member 91 from the first axial side L1.

[0034] The support member 93 is composed of a member different from the first housing member 91 and the second housing member 92. The support member 93 is formed to extend along the radial direction R. The support member 93 is configured to separate the configuration area of ​​the rotating electric machine 1 and the configuration area of ​​the speed reducer 3 and the differential gear device 4 in the inner part of the outer housing 9 along the axial direction L. That is, the support member 93 is configured between the rotating electric machine 1 and the speed reducer 3 in the axial direction L. The support member 93 is fixed to the first housing member 91. In the present embodiment, the support member 93 is fixed to the first peripheral wall portion 912 in a manner extending and protruding toward the radial inner side R1 relative to the first peripheral wall portion 912.

[0035] The cover member 94 is composed of a member different from the first housing member 91, the second housing member 92, and the support member 93. The cover member 94 includes a second side wall portion 941 and a third peripheral wall portion 942. The second side wall portion 941 is formed to extend along the radial direction R. The second side wall portion 941 is configured to cover the rotating electrical machine 1 from the first axial side L1. The third peripheral wall portion 942 is formed in a cylindrical shape having an axis along the axial direction L. The third peripheral wall portion 942 is joined to the second peripheral wall portion 921 of the second housing member 92 from the first axial side L1. In the example shown in the figure, the second side wall portion 941 and the third peripheral wall portion 942 are integrally formed in such a manner that the end portion of the radially outer side R2 of the second side wall portion 941 and the end portion of the axially first side L1 of the third peripheral wall portion 942 are connected. That is, the cover member 94 is formed in a bottomed cylindrical shape that is open on the second axial side L2.

[0036] In the present embodiment, the driving force source D is a rotating electrical machine 1 including a stator 11 and a rotor 12. The rotating electrical machine 1 is a pair of wheels W (see Figure 2 ) functions as a driving force source. The rotating electric machine 1 has a function as a motor (electric motor) that receives a supply of electric power and generates power, and a function as a generator (generator) that receives a supply of power and generates electric power. Specifically, the rotating electric machine 1 is electrically connected to a power storage device (not shown) such as a battery or a capacitor. Moreover, the rotating electric machine 1 performs power operation and generates driving force using the electric power stored in the power storage device. In addition, the rotating electric machine 1 generates electricity using the driving force transmitted from the pair of wheels W to charge the power storage device.

[0037] like Figure 1As shown, the stator 11 of the rotating electric machine 1 includes a cylindrical stator core 11a. The stator core 11a is fixed to the outer housing 9 (here, the second peripheral wall portion 921 of the second housing member 92). The rotor 12 of the rotating electric machine 1 includes a cylindrical rotor core 12a. The rotor core 12a is supported so as to be rotatable relative to the stator core 11a. The rotor core 12a is connected to the rotor shaft 12b in a manner that rotates integrally. In this embodiment, the rotor shaft 12b corresponds to the input member 10.

[0038] The rotor shaft 12b is formed in a cylindrical shape coaxial with the rotor core 12a. In the present embodiment, the rotor shaft 12b is configured to protrude from the rotor core 12a to both sides of the axial direction L. Moreover, the portion of the rotor shaft 12b protruding from the rotor core 12a to the first axial side L1 is rotatably supported by the first support portion 943 provided in the cover member 94 of the outer housing 9 via the first bearing B1. Figure 1 In the example shown, the first support portion 943 is formed into a cylindrical shape that protrudes from the second side wall portion 941 to the second axial side L2 and covers the rotor shaft 12b from the radially outer side R2. In addition, a first bearing B1 is arranged between the first support portion 943 and the rotor shaft 12b in the radial direction R. In addition, in the present embodiment, the portion of the rotor shaft 12b that protrudes from the rotor core 12a to the second axial side L2 is arranged as a support member 93 that penetrates the outer housing 9 in the axial direction L. In addition, the portion of the rotor shaft 12b that protrudes from the rotor core 12a to the second axial side L2 is rotatably supported by the support member 93 via the second bearing B2.

[0039] In the present embodiment, the rotating electrical machine 1 is an inner rotor type rotating electrical machine. Therefore, the rotor core 12a is arranged radially inwardly R1 relative to the stator core 11a. In addition, the rotor shaft 12b is arranged radially inwardly R1 relative to the rotor core 12a.

[0040] In addition, in the present embodiment, the rotating electrical machine 1 is a rotating magnetic field type rotating electrical machine. Therefore, the stator 11 further includes a stator coil 11b. In the present embodiment, the stator coil 11b is wound on the stator core 11a in such a manner that coil ends protrude on both sides of the stator core 11a in the axial direction L. In addition, although not shown in the figure, a permanent magnet is provided on the rotor core 12a.

[0041] In the present embodiment, the speed reducer 3 is a planetary gear mechanism including a sun gear SG, a carrier CR, a first ring gear RG1 , and a second ring gear RG2 .

[0042] In the present embodiment, the sun gear SG is connected to the rotor 12 so as to rotate integrally therewith. Figure 1 In the illustrated example, the sun gear SG is connected to the rotor shaft 12 b by welding or the like so as to rotate integrally therewith.

[0043] In the present embodiment, the planetary carrier CR is configured to support the first pinion gear PG1 and the second pinion gear PG2 so that they can rotate. The first pinion gear PG1 and the second pinion gear PG2 are connected in a manner that they rotate integrally with each other. The first pinion gear PG1 meshes with the sun gear SG and the first ring gear RG1. The second pinion gear PG2 meshes with the second ring gear RG2. The second pinion gear PG2 is formed to have a smaller diameter than the first pinion gear PG1.

[0044] In this embodiment, the first ring gear RG1 is fixed to the outer case 9. Figure 1 In the example shown, the first ring gear RG1 is fixed to a support member 93 of the outer case 9 .

[0045] The differential gear device 4 includes a differential case 5 and a differential gear mechanism 6 accommodated in the differential case 5. The differential gear device 4 is a bevel gear type differential gear device.

[0046] The differential case 5 is configured to rotate around the output rotation axis X. The differential case 5 is an input member of the differential gear device 4. In the present embodiment, the differential case 5 is connected to the second ring gear RG2 of the speed reducer 3 by welding or the like so as to rotate integrally therewith.

[0047] The differential gear mechanism 6 includes a shaft member 61 , a plurality of first bevel gears 62 , and a pair of second bevel gears 63 .

[0048] The shaft member 61 is supported by the differential case 5 so as to rotate integrally with the differential case 5. The shaft member 61 is formed to extend along the radial direction R. In the present embodiment, the shaft member 61 is formed radially along the radial direction R (for example, a cross-shaped structure when viewed along the axial direction L).

[0049] The plurality of first bevel gears 62 are arranged separately along the circumferential direction C. The plurality of first bevel gears 62 are supported by the shaft member 61 so as to be rotatable. More specifically, each of the plurality of first bevel gears 62 is configured to be rotatable (rotational) about its axis, and to be rotatable (revolutionary) about the output rotation axis X. In this example, four first bevel gears 62 are provided.

[0050] The pair of second bevel gears 63 are arranged on both sides of the shaft member 61 in the axial direction L. The pair of second bevel gears 63 mesh with the plurality of first bevel gears 62. The pair of second bevel gears 63 are configured to rotate around the output rotation axis X. The pair of second bevel gears 63 are connected to the pair of output shafts 2 in a manner that they rotate integrally.

[0051] In the following description, the one of the pair of second bevel gears 63 that is arranged on the second axial side L2 with respect to the shaft member 61 is referred to as the "specific bevel gear 63S". Furthermore, the one of the pair of second bevel gears 63 that is arranged on the first axial side L1 with respect to the shaft member 61 is referred to as the "non-specific bevel gear 63N". In addition, the one of the pair of output shafts 2 that rotates integrally with the specific bevel gear 63S is referred to as the "specific output shaft 2S". Furthermore, the one of the pair of output shafts 2 that rotates integrally with the non-specific bevel gear 63N is referred to as the "non-specific output shaft 2N".

[0052] In the present embodiment, the specific output shaft 2S is a drive shaft. In addition, the non-specific output shaft 2N includes a transmission shaft 21 and a drive shaft 22 .

[0053] The transmission shaft 21 is connected to the non-specific bevel gear 63N so as to rotate integrally therewith. Figure 1 In the illustrated example, the transmission shaft 21 is inserted into the non-specific bevel gear 63N from the axial first side L1 at the radial inner side R1 and is coupled to the non-specific bevel gear 63N by spline engagement.

[0054] The transmission shaft 21 is connected to the drive shaft 22 so as to rotate integrally. In the present embodiment, the transmission shaft 21 includes a connection portion 211 connected to the drive shaft 22. The connection portion 211 is disposed at the end portion of the transmission shaft 21 on the first axial side L1. The connection portion 211 is formed in a cylindrical shape that is open on the first axial side L1. Figure 1 In the illustrated example, the drive shaft 22 is inserted into the connection portion 211 from the axial first side L1 at the radially inner side R1 , and they are connected to each other by spline engagement.

[0055] In the present embodiment, the connection portion 211 is rotatably supported by the second support portion 944 provided in the cover member 94 of the outer housing 9 via the third bearing B3. Figure 1 In the illustrated example, the second support portion 944 is formed into a cylindrical shape that protrudes from the second side wall portion 941 toward the axial first side L1 and covers the connection portion 211 from the radial outer side R2. A third bearing B3 is disposed between the second support portion 944 and the connection portion 211 in the radial direction R.

[0056] In the present embodiment, the first seal member 71 is provided between the connection portion 211 and the second support portion 944 in the radial direction R. The first seal member 71 is arranged to seal between the outer peripheral surface of the connection portion 211 and the inner peripheral surface of the second support portion 944 in an oil-tight manner.

[0057] like Figure 3 As shown, in the present embodiment, the specific bevel gear 63S includes a bevel tooth portion 631 , a bevel tooth support portion 632 , and a cylindrical shaft portion 633 .

[0058] The bevel tooth portion 631 is formed to mesh with the plurality of first bevel gears 62. The bevel tooth portion 631 is composed of a plurality of teeth arranged along the circumferential direction C at equal intervals.

[0059] The bevel gear support portion 632 is configured to support the bevel gear portion 631. The bevel gear support portion 632 is formed integrally with the bevel gear portion 631. In more detail, the bevel gear support portion 632 has a side surface of a truncated cone facing the axial first side L1 and the radial outer side R2, and the bevel gear portion 631 is formed on the surface. In the present embodiment, the bevel gear support portion 632 is supported by the differential case 5 so as to be rotatable via a washer WS arranged between a surface facing the axial second side L2 of the bevel gear support portion 632 and a portion of the inner surface of the differential case 5 facing the axial first side L1. In this way, the specific bevel gear 63S is supported by the differential case 5 in the axial direction L.

[0060] The cylindrical shaft portion 633 is formed in a cylindrical shape extending from the bevel gear support portion 632 toward the second axial side L2. Figure 3 In the example shown, the cylindrical shaft portion 633 is formed integrally with the bevel gear support portion 632 .

[0061] In the present embodiment, the differential case 5 includes a differential case cylindrical portion 51. The differential case cylindrical portion 51 is formed in a cylindrical shape. The differential case cylindrical portion 51 is configured to cover the cylindrical shaft portion 633 of the specific bevel gear 63S from the radial outer side R2. A gap in the radial direction R, i.e., a first gap C1, is provided between the outer peripheral surface of the cylindrical shaft portion 633 and the inner peripheral surface of the differential case cylindrical portion 51. In this way, the specific bevel gear 63S is not supported in the radial direction R by the differential case 5. The specific bevel gear 63S is supported in the radial direction R by the aligning action generated by the meshing with the plurality of first bevel gears 62.

[0062] The specific output shaft 2S includes an engaging portion 2a. The specific bevel gear 63S includes an engaged portion 6a for the engaging portion 2a to engage. The engaging portion 2a and the engaged portion 6a are engaged with each other in a manner that limits the relative movement of the specific output shaft 2S and the specific bevel gear 63S in the circumferential direction C and the radial direction R. In the present embodiment, a portion of the specific output shaft 2S that is closer to the second axial side L2 than the portion where the engaging portion 2a is formed is separated from the specific bevel gear 63S (specifically, the cylindrical shaft portion 633). In addition, in the present embodiment, the specific output shaft 2S is separated from the differential case 5. Figure 3 In the illustrated example, a portion of the specific output shaft 2S facing the differential case cylindrical portion 51 in the radial direction R is covered from the radially outer side R2 by a cylindrical shaft portion 633 disposed with a gap in the radial direction R from the differential case cylindrical portion 51 .

[0063] In the present embodiment, each of the engaging portion 2a and the engaged portion 6a is composed of a plurality of spline teeth dispersedly arranged along the circumferential direction C. In addition, in the present embodiment, the specific output shaft 2S is inserted into the cylindrical shaft portion 633 of the specific bevel gear 63S from the axial second side L2 on the radial inner side R1. Moreover, the engaging portion 2a is formed on the outer circumferential surface of the portion of the specific output shaft 2S inserted into the cylindrical shaft portion 633, and the engaged portion 6a is formed on the inner circumferential surface of the cylindrical shaft portion 633.

[0064] As described above, the vehicle drive device 100 includes: an input member 10, which is drivably connected to a driving force source D; a pair of output shafts 2, each of which is drivably connected to a wheel W; a speed reducer 3, which decelerates the rotation of the input member 10; and a differential gear device 4, which distributes the rotation of the input member 10 transmitted via the speed reducer 3 to the pair of output shafts 2, the differential gear device 4 includes a differential case 5, and a differential gear mechanism 6 accommodated in the differential case 5, the differential gear mechanism 6 includes: a shaft member 61 formed in a manner extending along a radial direction R, a plurality of first bevel gears 62 supported by the shaft member 61 so as to be rotatable and separately arranged in a circumferential direction C, and a plurality of first bevel gears 62 separately arranged on both sides of the axial direction L relative to the shaft member 61 and separately arranged in a circumferential direction C. A pair of second bevel gears 63 meshing with the gear 62 are connected to the pair of output shafts 2 in a manner of integral rotation. The one of the pair of second bevel gears 63 that is arranged on the second axial side L2 relative to the shaft member 61 is set as a specific bevel gear 63S, and the one of the pair of output shafts 2 that rotates integrally with the specific bevel gear 63S is set as a specific output shaft 2S. The engaging portion 2a provided on the specific output shaft 2S and the engaged portion 6a provided on the specific bevel gear 63S are engaged with each other to limit the relative movement of the specific output shaft 2S and the specific bevel gear 63S in the circumferential direction C and the radial direction R. The specific bevel gear 63S is supported by the differential case 5 in the axial direction L, but is not supported by the differential case 5 in the radial direction R.

[0065] According to this structure, the specific bevel gear 63S is not supported by the differential case 5 in the radial direction R, but is supported in the radial direction R by the centering effect generated by the meshing of the specific bevel gear 63S and the plurality of first bevel gears 62. Therefore, a bearing or a fitting portion for supporting the specific bevel gear 63S in the differential case 5 in the radial direction R is not required.

[0066] In addition, according to this structure, the engaging portion 2a of the specific output shaft 2S and the engaged portion 6a of the specific bevel gear 63S are configured to restrict relative movement in the circumferential direction C and relative movement in the radial direction R. Therefore, it is not necessary to fit the specific output shaft 2S, and the fitting portion for restricting the deviation and inclination of the rotation axis of the specific output shaft 2S and the rotation axis of the specific bevel gear 63S is provided on the specific bevel gear 63S.

[0067] As described above, according to this configuration, it is easy to achieve miniaturization of the support structure for the specific bevel gear 63S and the specific output shaft 2S of the differential case 5. Therefore, in a configuration including the bevel gear type differential gear device 4, it is easy to achieve miniaturization of the vehicle drive device 100.

[0068] In addition, as described above, in the present embodiment, the specific bevel gear 63S includes: a bevel tooth portion 631 meshing with the plurality of first bevel gears 62, a bevel tooth support portion 632 integrally formed with the bevel tooth portion 631 and supporting the bevel tooth portion 631, and a cylindrical shaft portion 633 formed in a cylindrical shape and extending from the bevel tooth support portion 632 toward the second axial side L2.

[0069] The differential case 5 includes a differential case cylindrical portion 51 formed in a cylindrical shape and arranged to cover the cylindrical shaft portion 633 from the radially outer side R2.

[0070] A first gap C1 , which is a gap in the radial direction R, is provided between the outer peripheral surface of the cylindrical shaft portion 633 and the inner peripheral surface of the differential case cylindrical portion 51 .

[0071] This configuration can appropriately realize a structure in which the specific bevel gear 63S is not supported by the differential case 5 in the radial direction R. Thus, a structure in which the specific bevel gear 63S is supported in the radial direction R by the centering effect produced by the meshing between the specific bevel gear 63S and the first bevel gear 62 can be realized.

[0072] like Figure 3 As shown, in the present embodiment, a gap in the radial direction R, i.e., a second gap C2, is provided between the tooth surfaces of each of the plurality of first bevel gears 62 and the tooth surface of the specific bevel gear 63S. Moreover, the first gap C1 is larger than the second gap C2. Here, the tooth surface of the first bevel gear 62 is a surface that forms the concavoconvexity of the teeth of the first bevel gear 62, and is a surface that faces the outside in a direction orthogonal to the rotation axis of the first bevel gear 62. In addition, the tooth surface of the specific bevel gear 63S is a surface that forms the concavoconvexity of the teeth of the specific bevel gear 63S, and is a surface that faces one side in the axial direction L (here, the axial first side L1). The second gap C2 is the interval in the radial direction R between the tooth surfaces of each of the plurality of first bevel gears 62 and the tooth surface of the specific bevel gear 63S that face each other in the radial direction R. In the example shown in the figure, a portion of the tooth top surface of the first bevel gear 62 and a portion of the tooth bottom surface of the specific bevel gear 63S are arranged to face each other in the radial direction R. More specifically, each of the tooth top surface of the first bevel gear 62 and the tooth bottom surface of the specific bevel gear 63S has an inclined portion that gradually inclines toward the axial first side L1 as it moves toward the radial inner side R1. A second gap C2 is provided in the radial direction R between these inclined portions.

[0073] According to this structure, when the specific output shaft 2S is not rotating, when the first bevel gear 62 moves relative to the specific bevel gear 63S in the radial direction inward R1 in such a manner that the differential case tubular portion 51 and the tubular shaft portion 633 approach each other, the second gap C2 becomes zero before the first gap C1 becomes zero. Thus, it is possible to restrict the first bevel gear 62 from further moving relative to the specific bevel gear 63S in the radial direction inward R1, so that it is possible to avoid the differential case tubular portion 51 and the tubular shaft portion 633 from contacting each other.

[0074] like Figure 3 As shown in FIG. 1 , in this embodiment, the outer case 9 further includes an outer support portion 914. The outer support portion 914 is arranged radially outward R2 relative to the differential case tubular portion 51. Figure 3 In the illustrated example, the outer support portion 914 is formed to protrude radially inward R1 from the radially inner R1 end of the first side wall portion 911 of the first housing member 91. The outer support portion 914 is formed in an annular shape with the output rotation axis X as the axis center.

[0075] In the present embodiment, the differential case 5 further includes a radial extension portion 52. The radial extension portion 52 is formed to extend along the radial direction R. The radial extension portion 52 is arranged on the axial first side L1 relative to the outer support portion 914. A thrust bearing B4 that supports the radial extension portion 52 along the axial direction L is provided between a surface of the radial extension portion 52 that faces the axial second side L2 and a surface of the outer support portion 914 that faces the axial first side L1. Figure 3 In the example shown, the thrust bearing B4 is a needle bearing. In the present embodiment, the spacer WS is provided between the surface of the radially extending portion 52 facing the first axial side L1 and the surface of the bevel gear support portion 632 of the specific bevel gear 63S facing the second axial side L2.

[0076] In the present embodiment, a radial bearing B5 is provided between the outer peripheral surface of the differential case cylindrical portion 51 and the inner peripheral surface of the outer support portion 914 to support the differential case cylindrical portion 51 in the radial direction R. Figure 3 In the example shown, the radial bearing B5 is a bushing.

[0077] Thus, in the present embodiment, there is also an outer case 9 for accommodating the input member 10, the speed reducer 3 and the differential gear device 4, the outer case 9 includes an outer support portion 914 which is arranged on the radial outer side R2 relative to the differential case tubular portion 51, the differential case 5 also includes a radial extension portion 52 which is formed in a manner extending along the radial direction R and is arranged on the axial first side L1 relative to the outer support portion 914, a thrust bearing B4 which supports the radial extension portion 52 along the axial direction L is provided between a surface of the radial extension portion 52 which faces the axial second side L2 and a surface of the outer support portion 914 which faces the axial first side L1, and a radial bearing B5 which supports the differential case tubular portion 51 along the radial direction R is provided between an outer peripheral surface of the differential case tubular portion 51 and an inner peripheral surface of the outer support portion 914.

[0078] According to this structure, since the bearings supporting the differential case 5 with respect to the outer case 9 are divided into the thrust bearing B4 supporting in the axial direction L and the radial bearing B5 supporting in the radial direction R, it is easy to miniaturize the radial bearing B5. Therefore, the structure around the radial bearing B5 in the differential case 5 and the outer case 9 can also be miniaturized.

[0079] In the present embodiment, the outer housing 9 further includes an outer housing cylindrical portion 915. The outer housing cylindrical portion 915 is formed in a cylindrical shape. The outer housing cylindrical portion 915 is configured to cover the cylindrical shaft portion 633 from the radially outer side R2. In the present embodiment, the outer housing cylindrical portion 915 is formed to protrude from the end portion of the radially inner side R1 of the first side wall portion 911 of the first housing member 91 toward the axial second side L2.

[0080] In this embodiment, a second sealing member 72 is provided to seal the outer peripheral surface of the cylindrical shaft portion 633 and the inner peripheral surface of the outer housing cylindrical portion 915 in an oil-tight manner. Figure 3 In the example shown, the cylindrical shaft portion 633 has a protrusion that protrudes toward the second axial side L2 relative to the differential case cylindrical portion 51, and a second sealing member 72 is disposed between the outer peripheral surface of the protrusion of the cylindrical shaft portion 633 and the inner peripheral surface of the outer case cylindrical portion 915. The second sealing member 72 is disposed so as to overlap with the engaged portion 6a of the specific bevel gear 63S when viewed in the radial direction along the radial direction R. Here, regarding the arrangement of the 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, a region where the imaginary straight line intersects with both components at least partially exists.

[0081] Thus, in this embodiment, there is also an outer housing 9 for accommodating the input component 10, the reducer 3 and the differential gear device 4. The outer housing 9 also has an outer housing cylindrical portion 915 formed in a cylindrical shape and configured to cover the cylindrical shaft portion 633 from the radial outer side R2. A second sealing component 72 is provided for sealing the outer peripheral surface of the cylindrical shaft portion 633 and the inner peripheral surface of the outer housing cylindrical portion 915 in an oil-tight manner. The second sealing component 72 is configured to overlap with the engaged portion 6a when viewed radially along the radial direction R.

[0082] As described above, the specific bevel gear 63S is not provided with a fitting portion for limiting the deviation or inclination of the rotation axis of the specific output shaft 2S and the rotation axis of the specific bevel gear 63S, so this structure can be realized. Moreover, according to this structure, compared with a structure in which the second sealing member 72 is arranged to be more deviated in the axial direction L than the engaged portion 6a, the axial dimension L of the vehicle drive device 100 can be suppressed to be smaller, and the oil inside the outer housing 9 can be appropriately limited from leaking from the gap in the radial direction R between the outer peripheral surface of the cylindrical shaft portion 633 and the inner peripheral surface of the outer housing cylindrical portion 915.

[0083] In this embodiment, there is also an outer housing 9 that accommodates the input component 10, the reducer 3 and the differential gear device 4. The outer housing 9 has an outer support portion 914 that is arranged on the radial outside R2 relative to the differential case tubular portion 51. The outer support portion 914, the differential case tubular portion 51 and the engaged portion 6a are arranged to overlap with each other when viewed radially along the radial direction R.

[0084] According to this configuration, compared with a configuration in which the outer support portion 914 , the differential case tubular portion 51 , and the engaged portion 6 a are arranged offset in the axial direction L, the dimension of the vehicle drive device 100 in the axial direction L can be suppressed to be smaller.

[0085] [Other Implementation Methods]

[0086] (1) In the above embodiment, the driving force source D drivingly connected to the input member 10 is described as an example. However, the driving force source D is not limited to such a structure, and the driving force source D may also be an internal combustion engine. In this case, it is possible to set a structure in which the rotating electric machine 1 is not provided, and the wheels W are driven only by the driving force of the internal combustion engine. Alternatively, it is also possible to set a structure in which the wheels W are driven by the driving forces of both the internal combustion engine and the rotating electric machine, that is, it is also possible to set a structure in which the vehicle drive device 100 is a drive device for a hybrid vehicle.

[0087] (2) In the above embodiment, the input member 10, the pair of output shafts 2, the speed reducer 3, and the differential gear device 4 are arranged on the same axis, and the input member 10, the speed reducer 3, and the differential gear device 4 are arranged in the order described from the axial first side L1 toward the axial second side L2. However, the present invention is not limited to such a structure, and at least one of the input member 10, the pair of output shafts 2, the speed reducer 3, and the differential gear device 4 may be arranged on another axis. In addition, the arrangement order of the input member 10, the speed reducer 3, and the differential gear device 4 in the axial direction L may be different from the above-mentioned order.

[0088] (3) In the above embodiment, the structure of the reducer 3 being a planetary gear mechanism arranged on the output rotation axis X is described as an example. However, the structure is not limited to that. For example, the reducer 3 may be a counter gear mechanism instead of a planetary gear mechanism. In this structure, the counter gear mechanism is arranged over the output rotation axis X and an axis different from the output rotation axis X.

[0089] (4) In the above embodiment, the reducer 3 is described as a planetary gear mechanism including the sun gear SG, the carrier CR, the first ring gear RG1, and the second ring gear RG2. However, the structure is not limited to that, and for example, the reducer 3 may be a single pinion type planetary gear mechanism.

[0090] (5) In the above embodiment, the thrust bearing B4 for supporting the radially extending portion 52 in the axial direction L is provided between the surface of the radially extending portion 52 facing the second axial side L2 and the surface of the outer support portion 914 facing the first axial side L1, and the radial bearing B5 for supporting the differential case cylindrical portion 51 in the radial direction R is provided between the outer peripheral surface of the differential case cylindrical portion 51 and the inner peripheral surface of the outer support portion 914. However, the present invention is not limited to such a structure, and for example, ball bearings for supporting the differential case 5 in the axial direction L and the radial direction R may be provided between the surface of the differential case 5 facing the second axial side L2 and the surface of the outer support portion 914 facing the first axial side L1, and between the outer peripheral surface of the differential case 5 and the inner peripheral surface of the outer support portion 914.

[0091] (6) In the above embodiment, the second sealing member 72 is arranged to overlap the engaged portion 6a when viewed in the radial direction along the radial direction R. However, the present invention is not limited to such a structure, and for example, the second sealing member 72 may be arranged on the second axial side L2 relative to the engaged portion 6a.

[0092] (7) In the above embodiment, the outer support portion 914, the differential case cylindrical portion 51, and the engaged portion 6a are arranged to overlap each other when viewed in the radial direction along the radial direction R. However, the present invention is not limited to such a structure, and for example, the engaged portion 6a may be arranged on the second axial side L2 relative to the outer support portion 914 and the differential case cylindrical portion 51.

[0093] (8) In addition, the structures disclosed in the above-mentioned embodiments can 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 examples in all aspects. Therefore, various changes can be appropriately made without departing from the scope of the purpose of the present invention.

[0094] [Summary of the present embodiment]

[0095] Hereinafter, the outline of the vehicle drive device 100 described above will be described.

[0096] The vehicle drive device 100 includes: an input member 10, which is drivably connected to a driving force source D; a pair of output shafts 2, each of which is drivably connected to a wheel W; a speed reducer 3, which reduces the rotation of the input member 10; and a differential gear device 4, which distributes the rotation of the input member 10 transmitted via the speed reducer 3 to the pair of output shafts 2, wherein the direction along the rotation axis of the pair of output shafts 2, that is, the output rotation axis X is defined as an axial direction L, one side of the axial direction L is defined as an axial first side L1, the other side of the axial direction L is defined as an axial second side L2, the direction orthogonal to the output rotation axis X is defined as a radial direction R, and the direction around the output rotation axis X is defined as a circumferential direction C, the differential gear device 4 includes a differential case 5 and a differential gear mechanism 6 accommodating the differential case 5, the differential gear mechanism 6 includes: a shaft member 61 formed in a manner extending along the radial direction R, a shaft member 61 supported by the shaft member 61 so as to be rotatable and distributed along the circumferential direction C. A plurality of first bevel gears 62 are arranged in an open manner, and a pair of second bevel gears 63 are arranged separately in the axial direction L relative to the shaft member 61 and meshed with the plurality of first bevel gears 62. The pair of second bevel gears 63 are respectively connected to the pair of output shafts 2 in a manner of integral rotation. One of the pair of second bevel gears 63 that is arranged on the second axial side L2 relative to the shaft member 61 is set as a specific bevel gear 63S, and one of the pair of output shafts 2 that rotates integrally with the specific bevel gear 63S is set as a specific output shaft 2S. The engaging portion 2a provided on the specific output shaft 2S and the engaged portion 6a provided on the specific bevel gear 63S are engaged with each other to limit the relative movement of the specific output shaft 2S and the specific bevel gear 63S in the circumferential direction C and the radial direction R. The specific bevel gear 63S is supported by the differential case 5 in the axial direction L, but is not supported by the differential case 5 in the radial direction R.

[0097] According to this structure, the specific bevel gear 63S is not supported by the differential case 5 in the radial direction R, but is supported in the radial direction R by the centering effect generated by the meshing of the specific bevel gear 63S and the plurality of first bevel gears 62. Therefore, a bearing or a fitting portion for supporting the specific bevel gear 63S in the differential case 5 in the radial direction R is not required.

[0098] In addition, according to this structure, the engaging portion 2a of the specific output shaft 2S and the engaged portion 6a of the specific bevel gear 63S are configured to restrict relative movement in the circumferential direction C and relative movement in the radial direction R. Therefore, it is not necessary to provide a fitting portion on the specific bevel gear 63S with which the specific output shaft 2S is fitted and for restricting deviation or inclination between the rotation axis of the specific output shaft 2S and the rotation axis of the specific bevel gear 63S.

[0099] As described above, according to this configuration, it is easy to achieve miniaturization of the support structure for the specific bevel gear 63S and the specific output shaft 2S of the differential case 5. Therefore, in a configuration including the bevel gear type differential gear device 4, it is easy to achieve miniaturization of the vehicle drive device 100.

[0100] Here, it is preferred that the specific bevel gear 63S comprises: a bevel tooth portion 631 meshing with the plurality of first bevel gears 62, a bevel tooth support portion 632 integrally formed with the bevel tooth portion 631 and supporting the bevel tooth portion 631, and a cylindrical shaft portion 633 formed as a cylinder extending from the bevel tooth support portion 632 toward the second axial side L2, and the differential case 5 comprises a differential case cylindrical portion 51 formed as a cylinder and configured to cover the cylindrical shaft portion 633 from the outer side R2 of the radial direction R, and a gap of the radial direction R, i.e., a first gap C1, is provided between the outer peripheral surface of the cylindrical shaft portion 633 and the inner peripheral surface of the differential case cylindrical portion 51.

[0101] This configuration can appropriately realize a structure in which the specific bevel gear 63S is not supported by the differential case 5 in the radial direction R. Thus, a structure in which the specific bevel gear 63S is supported in the radial direction R by the centering effect produced by the meshing between the specific bevel gear 63S and the first bevel gear 62 can be appropriately realized.

[0102] Preferably, in a structure in which the first gap C1 is provided between the outer peripheral surface of the cylindrical shaft portion 633 and the inner peripheral surface of the differential case cylindrical portion 51, a gap in the radial direction R, i.e., a second gap C2, is provided between the tooth surface of each of the plurality of first bevel gears 62 and the tooth surface of the specific bevel gear 63S, and the first gap C1 is larger than the second gap C2.

[0103] According to this structure, when the specific output shaft 2S is not rotating, when the first bevel gear 62 moves relative to the specific bevel gear 63S toward the inner side R1 in the radial direction R so that the differential case tubular portion 51 and the tubular shaft portion 633 approach each other, the second gap C2 becomes zero before the first gap C1 becomes zero. Thus, it is possible to restrict the first bevel gear 62 from further moving relative to the specific bevel gear 63S toward the inner side R1 in the radial direction R, so that it is possible to avoid the differential case tubular portion 51 and the tubular shaft portion 633 from contacting each other.

[0104] In addition, it is preferred that the vehicle drive device 100 also includes an outer housing 9 for accommodating the above-mentioned input component 10, the above-mentioned reducer 3 and the above-mentioned differential gear device 4, and the above-mentioned outer housing 9 also includes an outer housing cylindrical portion 915 formed in a cylindrical shape and configured to cover the above-mentioned cylindrical shaft portion 633 from the outer side R2 of the above-mentioned radial direction R, and a sealing component 72 is provided to seal the outer peripheral surface of the above-mentioned cylindrical shaft portion 633 and the inner peripheral surface of the above-mentioned outer housing cylindrical portion 915 in an oil-tight state, and the above-mentioned sealing component 72 is configured to overlap with the above-mentioned engaged portion 6a when observed in the radial direction along the above-mentioned radial direction R.

[0105] As described above, since the specific bevel gear 63S is not provided with a fitting portion for limiting the deviation or inclination of the rotation axis of the specific output shaft 2S and the rotation axis of the specific bevel gear 63S, this structure can be realized. Moreover, according to this structure, compared with a structure in which the second sealing member 72 is arranged to be more deviated in the axial direction L than the engaged portion 6a, the dimension of the axial direction L of the vehicle drive device 100 can be suppressed to be smaller, and the oil inside the outer housing 9 can be appropriately suppressed from leaking from the gap in the radial direction R between the outer peripheral surface of the cylindrical shaft portion 633 and the inner peripheral surface of the outer housing cylindrical portion 915.

[0106] In addition, it is preferred that the vehicle drive device 100 also includes an outer housing 9 for accommodating the above-mentioned input component 10, the above-mentioned reducer 3 and the above-mentioned differential gear device 4, and the above-mentioned outer housing 9 includes an outer support portion 914 arranged on the outer side R2 of the above-mentioned radial direction R relative to the above-mentioned differential case tubular portion 51, and the above-mentioned outer support portion 914, the above-mentioned differential case tubular portion 51 and the above-mentioned engaged portion 6a are arranged to overlap with each other when observed radially along the above-mentioned radial direction R.

[0107] According to this structure, compared with a structure in which the outer support portion 914 , the differential case cylindrical portion 51 , and the engaged portion 6 a are arranged offset in the axial direction L, it is easy to suppress the dimension of the vehicle drive device 100 in the axial direction L to be small.

[0108] Possibility of industrial application

[0109] The technology of the present invention can be used in a vehicle drive device including an input member drivingly connected to a driving force source, a pair of output shafts each drivingly connected to a wheel, a speed reducer for reducing the rotation of the input member, and a differential gear device for distributing the rotation of the input member transmitted via the speed reducer to the pair of output shafts.

[0110] Description of Reference Numerals

[0111] 100: vehicle drive device, 10: input component, 2: output shaft, 2S: specific output shaft, 2a: engaging portion, 3: speed reducer, 4: differential gear device, 5: differential case, 51: differential case tubular portion, 52: radial extension portion, 6: differential gear mechanism, 6a: engaged portion, 61: shaft component, 62: first bevel gear, 63: second bevel gear, 63S: specific bevel gear, 631: bevel gear portion, 632: bevel gear support portion, 633: tubular shaft portion, 72: second sealing component (sealing component), 9: outer case, 914: outer support portion, 915: outer case tubular portion, D: driving force source, B4: thrust bearing, B5: radial bearing, W: wheel, L: axial direction, L1: axial first side, L2: axial second side, R: radial direction, R1: radial inner side, R2: radial outer side, C: circumferential direction.

Claims

1. A vehicle drive device, comprising: An input member drivingly coupled to a driving force source; A pair of output shafts, each of which is drive-connected to a wheel; a speed reducer that reduces the speed of rotation of the input member; and A differential gear device distributes the rotation of the input member transmitted via the speed reducer to the pair of output shafts, wherein: The direction along the rotation axis of the pair of output shafts, i.e., the output rotation axis, is defined as an axial direction, one side of the axial direction is defined as an axial first side, the other side of the axial direction is defined as an axial second side, the direction orthogonal to the output rotation axis is defined as a radial direction, and the direction around the output rotation axis is defined as a circumferential direction, The differential gear device includes a differential case and a differential gear mechanism accommodated in the differential case. The differential gear mechanism comprises: a shaft member formed in a manner extending in the radial direction, a plurality of first bevel gears rotatably supported by the shaft member and arranged separately in the circumferential direction, and a pair of second bevel gears arranged separately on both sides of the shaft member in the axial direction and meshing with the plurality of first bevel gears. The pair of second bevel gears are connected to the pair of output shafts in a manner of integral rotation. One of the pair of second bevel gears that is arranged on the second side in the axial direction relative to the shaft member is set as a specific bevel gear, and one of the pair of output shafts that rotates integrally with the specific bevel gear is set as a specific output shaft. The engaging portion provided on the specific output shaft and the engaged portion provided on the specific bevel gear are engaged with each other so as to restrict relative movement of the specific output shaft and the specific bevel gear in the circumferential direction and the radial direction. The specific bevel gear is supported by the differential case in the axial direction, but is not supported by the differential case in the radial direction.

2. The vehicle drive device according to claim 1, wherein: The specific bevel gear comprises: a bevel tooth portion meshing with the plurality of first bevel gears, a bevel tooth support portion formed integrally with the bevel tooth portion and supporting the bevel tooth portion, and a cylindrical shaft portion formed in a cylindrical shape and extending from the bevel tooth support portion toward the second axial side. The differential case includes a differential case cylindrical portion formed in a cylindrical shape and arranged to cover the cylindrical shaft portion from the radially outer side. The radial gap, that is, the first gap is provided between the outer peripheral surface of the cylindrical shaft portion and the inner peripheral surface of the differential case cylindrical portion.

3. The vehicle drive device according to claim 2, wherein: The radial gap, i.e., the second gap, is provided between the tooth surface of each of the plurality of first bevel gears and the tooth surface of the specific bevel gear. The first gap is larger than the second gap.

4. The vehicle drive device according to claim 2 or 3, wherein: It also includes: an outer case that accommodates the input member, the speed reducer, and the differential gear device; The outer housing further comprises: an outer housing cylindrical portion formed in a cylindrical shape and arranged to cover the cylindrical shaft portion from the outer side in the radial direction; A sealing member is provided to seal the outer peripheral surface of the cylindrical shaft portion and the inner peripheral surface of the outer housing cylindrical portion in an oil-tight manner. The sealing member is arranged so as to overlap with the engaged portion when viewed in the radial direction along the radial direction.

5. The vehicle drive device according to claim 2 or 3, wherein: It also includes: an outer case that accommodates the input member, the speed reducer, and the differential gear device; The outer case includes an outer support portion disposed on the outer side in the radial direction relative to the differential case tubular portion. The outer support portion, the differential case tubular portion, and the engaged portion are arranged so as to overlap with each other when viewed in a radial direction along the radial direction.

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