Vehicle drive device

Abstract

A differential gear mechanism (6) accommodated in a differential case (5) comprises a shaft member (61), a plurality of first bevel gears (62) that are rotatably supported by the shaft member (61), and a pair of second bevel gears (63) that mesh with the plurality of first bevel gears (62). Among the pair of second bevel gears (63), the bevel gear that is disposed on an axial-direction second side (L2) of the shaft member (61) is a specific bevel gear (63S), and among a pair of output shafts (2), the output shaft that rotates integrally with the specific bevel gear (63S) is a specific output shaft (2S). The specific bevel gear (63S) is supported relative to the differential case (5) in an axial direction (L) but is not supported in a radial direction (R). An engaging part (2a) that is provided to the specific output shaft (2S) and an engaged part (6a) that is provided to the specific bevel gear (63S) engage with each other so as to restrict the relative movement of the specific output shaft (2S) and the specific bevel gear (63S) in a circumferential direction (C) and the radial direction (R).

Description

Technical Field

[0001] The present invention relates to 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 that reduces the rotation of the input member, and a differential gear device that distributes the rotation of the input member transmitted through the speed reducer to the pair of output shafts.

Background Art

[0002] An example of such a vehicle drive device is disclosed in Patent Document 1 below. In the following description of the background art, the reference numerals in 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 to extend along the radial direction, a first bevel gear (52) rotatably supported by the shaft member, and a pair of second bevel gears (54A, 54B) that are separated and arranged on both axial sides of the shaft member (51) and mesh with the first bevel gear (52). One of the second bevel gears (54A) is connected so as to rotate integrally with the first drive shaft (9A), and the other second bevel gear (54B) is connected so as to rotate integrally with the second drive shaft (9B).

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] In the above-described vehicle drive device (1), the other second bevel gear (54B) includes a bevel gear portion that meshes with the first bevel gear (52), a bevel gear support portion that is integrally formed with the bevel gear portion and supports the bevel gear portion, and a cylindrical shaft portion (540) that is formed in a cylindrical shape and extends from the bevel gear support portion to one side in the axial direction (the left side in FIG. 4 of Patent Document 1).

[0006] The cylindrical shaft portion (540) is supported from the outside in the radial direction by a differential case cylindrical portion (72) provided in the differential case (50). Further, the bevel gear support portion is axially supported with respect to the inner surface of the differential case (50) via a washer inserted through the cylindrical shaft portion (540). Thus, the other second bevel gear (54B) is configured to be supported not only in the radial direction but also in the axial direction. Therefore, the axial dimension of the other second bevel gear (54B) is likely to increase.

[0007] Further, the cylindrical shaft portion (540) is connected so as to rotate integrally with a second drive shaft (9B) disposed radially inward with respect to the cylindrical shaft portion (540). Specifically, the cylindrical shaft portion (540) includes an engaged portion that is connected to an engaging portion formed at the tip of the second drive shaft (9B) by spline engagement, and a fitting portion into which a portion axially adjacent to the engaging portion of the second drive shaft (9B) is fitted. In this way, the relative rotation of the cylindrical shaft portion (540) with respect to the second drive shaft (9B) is restricted by the engaged portion, and the deviation and inclination between 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. Thus, the cylindrical shaft portion (540) has a configuration in which the engaged portion and the fitting portion are arranged side by side in the axial direction. Therefore, the axial dimension of the other second bevel gear (54B) is likely to increase.

[0008] The configuration of the second bevel gear as described above has led to an increase in the size of the vehicle drive device. Therefore, in a configuration including a bevel gear type differential gear device, it is desired to realize a vehicle drive device that is easy to miniaturize.

Means for Solving the Problems

[0009] In view of the above, the characteristic configuration of the vehicle drive device is as follows: An input member drivingly connected to a driving force source; A pair of output shafts each drivingly connected to a wheel; A speed reducer that reduces the rotation of the input member; A vehicle drive device including a differential gear device that distributes the rotation of the input member transmitted through the speed reducer to the pair of output shafts, With the direction along the output rotation axis, which is the rotation axis of the pair of output shafts, defined as the axial direction, one side of the axial direction as the first axial side, the other side of the axial direction as the second axial side, the direction perpendicular to the output rotation axis as the radial direction, and the direction around the output rotation axis as the circumferential direction, The differential gear device includes a differential case and a differential gear mechanism housed in the differential case. The differential gear mechanism includes a shaft member formed to extend along 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 each connected to rotate integrally with the pair of output shafts. Of the pair of second bevel gears, the one arranged on the second axial side with respect to the shaft member is defined as a specific bevel gear, and of the pair of output shafts, the one that rotates integrally with the specific bevel gear is defined as a specific output shaft. An engaging portion provided on the specific output shaft and an 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 in the axial direction with respect to the differential case, but is not supported in the radial direction.

[0010] According to this characteristic configuration, the specific bevel gear is not supported radially with respect to the differential case, but is supported radially by the centering action due to the meshing between the specific bevel gear and the plurality of first bevel gears. Therefore, it is possible to eliminate the need for bearings and fitting portions for radially supporting the specific bevel gear with respect to the differential case. Also, according to this characteristic configuration, the engaging portion of the specific output shaft and the engaged portion of the specific bevel gear are configured to restrict relative movement in the circumferential direction and relative movement in the radial direction. Therefore, it is not necessary to provide a fitting portion on the specific bevel gear for restricting misalignment and inclination between the rotation axis of the specific output shaft and the rotation axis of the specific bevel gear when the specific output shaft is fitted. As described above, according to this characteristic configuration, it is easy to reduce the size of the support structure of the specific bevel gear and the specific output shaft with respect to the differential case. Therefore, in a configuration provided with a bevel gear type differential gear device, it is easy to reduce the size of the vehicle drive device.

Brief Description of the Drawings

[0011]

Figure 1

Figure 2

Figure 3

Modes for Carrying Out the Invention

[0012] Hereinafter, the vehicle drive device 100 according to the embodiment will be described with reference to the drawings. As shown in FIGS. 1 and 2, the vehicle drive device 100 includes an input member 10 drivingly connected to a driving force source D, a pair of output shafts 2 each drivingly connected to a wheel W (see FIG. 2), a speed reducer 3 for reducing the rotation of the input member 10, and a differential gear device 4 for distributing the rotation of the input member 10 transmitted through the speed reducer 3 to the pair of output shafts 2.

[0013] In the following description, the direction along the output rotation axis center X, which is the rotation axis center of the pair of output shafts 2, is defined as the "axial direction L". One side of the axial direction L is defined as the "first axial side L1", and the other side of the axial direction L is defined as the "second axial side L2". Further, the direction orthogonal to the output rotation axis center X is defined as the "radial direction R". In the radial direction R, the side of the output rotation axis center X is defined as the "radial inner side R1", and the opposite side is defined as the "radial outer side R2". Further, the direction around the output rotation axis center X is defined as the "circumferential direction C".

[0014] 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 coaxially. 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 center X. Further, in the present embodiment, the input member 10, the speed reducer 3, and the differential gear device 4 are arranged in the described order from the first axial side L1 toward the second axial side L2.

[0015] In the present embodiment, the vehicle drive device 100 further includes an outer case 9 that houses the input member 10, the speed reducer 3, and the differential gear device 4. In the present 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.

[0016] The first case 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 arranged to cover the differential gear device 4 from the second axial 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 arranged to cover the speed 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 such that the end portion on the radial outer side R2 of the first side wall portion 911 and the end portion on the second axial side L2 of the first peripheral wall portion 912 are connected. That is, the first case member 91 is formed in a bottomed cylindrical shape that opens to the first axial side L1.

[0017] The second case member 92 is formed of a member separate from the first case member 91. The second case member 92 is joined to the first case member 91 from the first axial side L1. The second case 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 arranged to cover the rotating electric 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 case member 91 from the first axial side L1.

[0018] The support member 93 is formed of a member separate from the first case member 91 and the second case member 92. The support member 93 is formed to extend along the radial direction R. The support member 93 is arranged to partition, in the axial direction L, the arrangement region of the rotating electric machine 1 and the arrangement regions of the speed reducer 3 and the differential gear device 4 inside the outer case 9. That is, the support member 93 is arranged 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 case member 91. In the present embodiment, the support member 93 is fixed to the first peripheral wall portion 912 so as to extend radially inward R1 with respect to the first peripheral wall portion 912.

[0019] The cover member 94 is formed of a member separate from the first case member 91, the second case 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 arranged to cover the rotating electric 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 case member 92 from the first axial side L1. In the illustrated example, the second side wall portion 941 and the third peripheral wall portion 942 are integrally formed such that the radially outer R2 end of the second side wall portion 941 and the first axial side L1 end of the third peripheral wall portion 942 are connected. That is, the cover member 94 is formed in a bottomed cylindrical shape that opens to the second axial side L2.

[0020] In this embodiment, the driving force source D is the rotating electric machine 1 including the stator 11 and the rotor 12. The rotating electric machine 1 functions as a driving force source for a pair of wheels W (see FIG. 2). The rotating electric machine 1 has a function as a motor (electric motor) that receives power supply and generates power, and a function as a generator (electric generator) that receives power supply 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. Then, the rotating electric machine 1 travels by the electric power stored in the power storage device and generates a driving force. Further, the rotating electric machine 1 generates electricity by the driving force transmitted from the side of the pair of wheels W and charges the power storage device.

[0021] As shown in FIG. 1, the stator 11 of the rotating electric machine 1 includes a cylindrical stator core 11a. The stator core 11a is fixed to the outer case 9 (here, the second peripheral wall portion 921 of the second case member 92). The rotor 12 of the rotating electric machine 1 includes a cylindrical rotor core 12a. The rotor core 12a is rotatably supported with respect to the stator core 11a. The rotor core 12a is connected so as to rotate integrally with the rotor shaft 12b. In this embodiment, the rotor shaft 12b corresponds to the input member 10.

[0022] 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 arranged so as to protrude from both sides of the rotor core 12a in the axial direction L. And the portion of the rotor shaft 12b protruding from the rotor core 12a to the first side L1 in the axial direction is rotatably supported via a first bearing B1 with respect to a first support portion 943 provided in a cover member 94 of the outer case 9. In the example shown in FIG. 1, the first support portion 943 protrudes from the second side wall portion 941 to the second side L2 in the axial direction and is formed in a cylindrical shape that covers the rotor shaft 12b from the radially outer side R2. And a first bearing B1 is arranged between the first support portion 943 and the rotor shaft 12b in the radial direction R. Further, in the present embodiment, the portion of the rotor shaft 12b protruding from the rotor core 12a to the second side L2 in the axial direction is arranged so as to penetrate a support member 93 of the outer case 9 in the axial direction L. And the portion of the rotor shaft 12b protruding from the rotor core 12a to the second side L2 in the axial direction is rotatably supported via a second bearing B2 with respect to the support member 93.

[0023] In the present embodiment, the rotating electrical machine 1 is an inner rotor type rotating electrical machine. Therefore, the rotor core 12a is arranged on the radially inner side R1 with respect to the stator core 11a. Also, the rotor shaft 12b is arranged on the radially inner side R1 with respect to the rotor core 12a.

[0024] Also, in the present embodiment, the rotating electrical machine 1 is a rotating 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 around the stator core 11a such that coil end portions protruding from both sides of the stator core 11a in the axial direction L are formed. Also, although not shown, permanent magnets are provided on the rotor core 12a.

[0025] 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.

[0026] In this embodiment, the sun gear SG is connected so as to rotate integrally with the rotor 12. In the example shown in FIG. 1, the sun gear SG is connected so as to rotate integrally with the rotor shaft 12b by welding or the like.

[0027] In this embodiment, the carrier CR is configured to rotatably support the first pinion gear PG1 and the second pinion gear PG2. The first pinion gear PG1 and the second pinion gear PG2 are connected so as to 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.

[0028] In this embodiment, the first ring gear RG1 is fixed to the outer case 9. In the example shown in FIG. 1, the first ring gear RG1 is fixed to the support member 93 of the outer case 9.

[0029] The differential gear device 4 includes a differential case 5 and a differential gear mechanism 6 housed in the differential case 5. The differential gear device 4 is a bevel gear type differential gear device.

[0030] The differential case 5 is configured to rotate about the output rotation axis center X. The differential case 5 is an input element of the differential gear device 4. In this embodiment, the differential case 5 is connected by welding or the like so as to rotate integrally with the second ring gear RG2 of the speed reducer 3.

[0031] 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.

[0032] 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 this embodiment, the shaft member 61 has a configuration formed radially along the radial direction R (for example, a configuration formed in a cross shape in an axial direction view along the axial direction L).

[0033] The plurality of first bevel gears 62 are arranged separately in the circumferential direction C. The plurality of first bevel gears 62 are rotatably supported by the shaft member 61. More specifically, each of the plurality of first bevel gears 62 is configured to be rotatable (rotate on its own axis) about its axis and rotatable (revolve) about the output rotation axis X. In this example, four first bevel gears 62 are provided.

[0034] A pair of second bevel gears 63 are arranged separately on both sides of the shaft member 61 in the axial direction L. The pair of second bevel gears 63 are engaged with the plurality of first bevel gears 62. The pair of second bevel gears 63 are configured to rotate about the output rotation axis X. The pair of second bevel gears 63 are respectively connected so as to rotate integrally with the pair of output shafts 2.

[0035] In the following description, among the pair of second bevel gears 63, the one arranged on the second side L2 in the axial direction with respect to the shaft member 61 is referred to as the "specific bevel gear 63S". And, among the pair of second bevel gears 63, the one arranged on the first side L1 in the axial direction with respect to the shaft member 61 is referred to as the "non-specific bevel gear 63N". Also, among the pair of output shafts 2, the one that rotates integrally with the specific bevel gear 63S is referred to as the "specific output shaft 2S". And, among the pair of output shafts 2, the one that rotates integrally with the non-specific bevel gear 63N is referred to as the "non-specific output shaft 2N".

[0036] In the present embodiment, the specific output shaft 2S is a drive shaft. Also, the non-specific output shaft 2N includes a transmission shaft 21 and a drive shaft 22.

[0037] The transmission shaft 21 is connected so as to rotate integrally with the non-specific bevel gear 63N. In the example shown in FIG. 1, the transmission shaft 21 is inserted into the non-specific bevel gear 63N from the first side L1 in the axial direction on the radially inner side R1 with respect to the non-specific bevel gear 63N and is connected to the non-specific bevel gear 63N by spline engagement.

[0038] Further, the transmission shaft 21 is connected so as to rotate integrally with the drive shaft 22. In the present embodiment, the transmission shaft 21 includes a connecting portion 211 that is connected to the drive shaft 22. The connecting portion 211 is disposed at the end of the transmission shaft 21 on the first axial side L1. And the connecting portion 211 is formed in a cylindrical shape that opens to the first axial side L1. In the example shown in FIG. 1, the drive shaft 22 is inserted into the connecting portion 211 from the first axial side L1 in the radially inner direction R1, and they are connected to each other by spline engagement.

[0039] In the present embodiment, the connecting portion 211 is rotatably supported by a second support portion 944 provided in a cover member 94 of the outer case 9 via a third bearing B3. In the example shown in FIG. 1, the second support portion 944 protrudes from the second side wall portion 941 to the first axial side L1 and is formed in a cylindrical shape that covers the connecting portion 211 from the radially outer side R2. And a third bearing B3 is disposed between the second support portion 944 and the connecting portion 211 in the radial direction R.

[0040] Also, in the present embodiment, a first seal member 71 is provided between the connecting portion 211 and the second support portion 944 in the radial direction R. The first seal member 71 is disposed so as to seal the space between the outer peripheral surface of the connecting portion 211 and the inner peripheral surface of the second support portion 944 in an oil-tight manner.

[0041] As shown in FIG. 3, in the present embodiment, the specific bevel gear 63S includes a bevel gear portion 631, a bevel gear support portion 632, and a cylindrical shaft portion 633.

[0042] The bevel gear portion 631 is formed to mesh with a plurality of first bevel gears 62. The bevel gear portion 631 is constituted by a plurality of tooth portions arranged at equal intervals in the circumferential direction C.

[0043] The bevel gear support portion 632 is configured to support the bevel gear portion 631. The bevel gear support portion 632 is integrally formed with the bevel gear portion 631. More specifically, the bevel gear support portion 632 has a frustum side surface facing the first axial side L1 and the radially 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 rotatably supported with respect to the differential case 5 via a washer WS disposed between the surface facing the second axial side L2 of the bevel gear support portion 632 and the portion facing the first axial side L1 on the inner surface of the differential case 5. Thus, the specific bevel gear 63S is supported in the axial direction L with respect to the differential case 5.

[0044] The cylindrical shaft portion 633 is formed in a cylindrical shape extending from the bevel gear support portion 632 to the second axial side L2. In the example shown in FIG. 3, the cylindrical shaft portion 633 is integrally formed with the bevel gear support portion 632.

[0045] 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 disposed so as to cover the cylindrical shaft portion 633 of the specific bevel gear 63S from the radially outer side R2. A first clearance C1, which is a clearance 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. Thus, the specific bevel gear 63S is not supported in the radial direction R with respect to the differential case 5. The specific bevel gear 63S is supported in the radial direction R by a centering action due to meshing with a plurality of first bevel gears 62.

[0046] The specific output shaft 2S is provided with an engaging portion 2a. The specific bevel gear 63S is provided with an engaged portion 6a with which the engaging portion 2a is engaged. The engaging portion 2a and the engaged portion 6a are engaged with each other so as to restrict relative movement in the circumferential direction C and the radial direction R between the specific output shaft 2S and the specific bevel gear 63S. In the present embodiment, the portion on the second axial side L2 with respect to the portion where the engaging portion 2a is formed on the specific output shaft 2S is disposed apart from the specific bevel gear 63S (specifically, the cylindrical shaft portion 633). Further, in the present embodiment, the specific output shaft 2S is disposed apart from the differential case 5. In the example shown in FIG. 3, the 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 the cylindrical shaft portion 633 disposed with a gap in the radial direction R from the differential case cylindrical portion 51.

[0047] In the present embodiment, each of the engaging portion 2a and the engaged portion 6a is constituted by a plurality of spline teeth distributed in the circumferential direction C. Further, 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 second axial side L2 on the radially inner side R1. Then, the engaging portion 2a is formed on the outer peripheral 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 peripheral surface of the cylindrical shaft portion 633.

[0048] As described above, the vehicle drive device 100 is an input member 10 drivingly connected to the drive power source D, a pair of output shafts 2 each drivingly connected to a wheel W, a speed reducer 3 for reducing the rotation of the input member 10, a differential gear device 4 for distributing the rotation of the input member 10 transmitted through the speed reducer 3 to the pair of output shafts 2, and is a vehicle drive device 100 including the differential gear device 4 includes a differential case 5 and a differential gear mechanism 6 housed in the differential case 5, The differential gear mechanism 6 includes a shaft member 61 formed to extend along the radial direction R, a plurality of first bevel gears 62 that are rotatably supported by the shaft member 61 and are arranged separately in the circumferential direction C, and a pair of second bevel gears 63 that are arranged separately on both sides of the shaft member 61 in the axial direction L and mesh with the plurality of first bevel gears 62. The pair of second bevel gears 63 are respectively connected so as to rotate integrally with the pair of output shafts 2. Of the pair of second bevel gears 63, the one arranged on the second axial side L2 with respect to the shaft member 61 is defined as a specific bevel gear 63S, and of the pair of output shafts 2, the one that rotates integrally with the specific bevel gear 63S is defined as a specific output shaft 2S. An engaging portion 2a provided on the specific output shaft 2S and an engaged portion 6a provided on the specific bevel gear 63S are engaged with each other so as to restrict relative movement in the circumferential direction C and the radial direction R between the specific output shaft 2S and the specific bevel gear 63S. The specific bevel gear 63S is supported in the axial direction L with respect to the differential case 5, but is not supported in the radial direction R.

[0049] According to this configuration, the specific bevel gear 63S is not supported in the radial direction R with respect to the differential case 5, and is supported in the radial direction R by the centering action due to the meshing between the specific bevel gear 63S and the plurality of first bevel gears 62. Therefore, it is possible to eliminate the need for bearings and fitting portions for supporting the specific bevel gear 63S in the radial direction R with respect to the differential case 5. Also, according to this configuration, 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, there is no need to provide a fitting portion on the specific bevel gear 63S to regulate the deviation and inclination between the rotation axis of the specific output shaft 2S and the rotation axis of the specific bevel gear 63S when the specific output shaft 2S is fitted. As described above, according to this configuration, it is easy to reduce the size of the support structure of the specific bevel gear 63S and the specific output shaft 2S with respect to the differential case 5. Therefore, in a configuration including the bevel gear type differential gear device 4, it is easy to reduce the size of the vehicle drive device 100.

[0050] Also, as described above, in the present embodiment, the specific bevel gear 63S includes a bevel tooth portion 631 that meshes with a plurality of first bevel gears 62, a bevel gear support portion 632 that is integrally formed with the bevel tooth portion 631 and supports the bevel tooth portion 631, and a cylindrical shaft portion 633 that is formed in a cylindrical shape and extends from the bevel gear support portion 632 to the second side L2 in the axial direction. The differential case 5 includes a differential case cylindrical portion 51 that is formed in a cylindrical shape and is arranged to cover the cylindrical shaft portion 633 from the radially outer side R2. A first clearance C1, which is a clearance 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.

[0051] According to this configuration, a configuration in which the specific bevel gear 63S is not supported in the radial direction R with respect to the differential case 5 can be appropriately realized. Thereby, a configuration in which the specific bevel gear 63S is supported in the radial direction R by the centering action due to the meshing between the specific bevel gear 63S and the first bevel gear 62 can be appropriately realized.

[0052] As shown in FIG. 3, in the present embodiment, a second clearance C2, which is a clearance in the radial direction R, 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. And the first clearance C1 is larger than the second clearance C2. Here, the tooth surface of the first bevel gear 62 is the uneven surface that forms the teeth of the first bevel gear 62, and is the surface facing the outside in the direction orthogonal to the rotation axis of the first bevel gear 62. Also, the tooth surface of the specific bevel gear 63S is the uneven surface that forms the teeth of the specific bevel gear 63S, and is the surface facing one side in the axial direction L (here, the first side L1 in the axial direction). The second clearance C2 is the radial R interval of the portion where the tooth surfaces of each of the plurality of first bevel gears 62 and the tooth surface of the specific bevel gear 63S face each other in the radial direction R. In the illustrated example, a part of the tooth tip surface of the first bevel gear 62 and a part 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 tip surface of the first bevel gear 62 and the tooth bottom surface of the specific bevel gear 63S has an inclined portion that inclines gradually toward the first side L1 in the axial direction as it goes toward the radially inner side R1. And the second clearance C2 is provided between the radial Rs of those inclined portions.

[0053] According to this configuration, when the specific output shaft 2S is not rotating, if the first bevel gear 62 moves relative to the specific bevel gear 63S radially inward R1 so that the differential case cylindrical portion 51 approaches the cylindrical shaft portion 633, the second clearance C2 becomes zero before the first clearance C1 becomes zero. Thereby, since the further relative movement of the first bevel gear 62 relative to the specific bevel gear 63S radially inward R1 can be restricted, contact between the differential case cylindrical portion 51 and the cylindrical shaft portion 633 can be avoided.

[0054] As shown in FIG. 3, in the present embodiment, the outer case 9 further includes an outer support portion 914. The outer support portion 914 is disposed radially outward R2 with respect to the differential case cylindrical portion 51. In the example shown in FIG. 3, the outer support portion 914 is formed so as to protrude radially inward R1 from the radially inner R1 end portion of the first side wall portion 911 of the first case member 91. And the outer support portion 914 is formed in an annular shape with the output rotation axis X as the axis.

[0055] In the present embodiment, the differential case 5 further includes a radially extending portion 52. The radially extending portion 52 is formed so as to extend along the radial direction R. The radially extending portion 52 is disposed on the first axial side L1 with respect to the outer support portion 914. A thrust bearing B4 that supports 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. In the example shown in FIG. 3, the thrust bearing B4 is a needle roller bearing. In the present embodiment, the washer 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.

[0056] In the present embodiment, a radial bearing B5 that supports 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. In the example shown in FIG. 3, the radial bearing B5 is a bush.

[0057] Thus, in this embodiment, an outer case 9 that houses the input member 10, the speed reducer 3, and the differential gear device 4 is further provided. The outer case 9 includes an outer support portion 914 disposed at a radial outer side R2 with respect to the differential case cylindrical portion 51. The differential case 5 further includes a radially extending portion 52 formed to extend along the radial direction R and disposed on the first axial side L1 with respect to the outer support portion 914. A thrust bearing B4 that supports 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. A radial bearing B5 that supports 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.

[0058] According to this configuration, the bearings that support the differential case 5 with respect to the outer case 9 are divided into a thrust bearing B4 that supports in the axial direction L and a radial bearing B5 that supports in the radial direction R. Therefore, it is easy to miniaturize the radial bearing B5. Accordingly, the structure around the radial bearing B5 in the differential case 5 and the outer case 9 is also easy to miniaturize.

[0059] In this embodiment, the outer case 9 further includes an outer case cylindrical portion 915. The outer case cylindrical portion 915 is formed in a cylindrical shape. The outer case cylindrical portion 915 is disposed so as to cover the cylindrical shaft portion 633 from the radial outer side R2. In this embodiment, the outer case cylindrical portion 915 is formed to protrude from the end portion on the radially inner side R1 of the first side wall portion 911 of the first case member 91 toward the second axial side L2.

[0060] In the present embodiment, a second seal member 72 is provided to seal the space between the outer peripheral surface of the cylindrical shaft portion 633 and the inner peripheral surface of the outer case cylindrical portion 915 in an oil-tight manner. In the example shown in FIG. 3, the cylindrical shaft portion 633 has a protruding portion that protrudes in the second axial direction L2 with respect to the differential case cylindrical portion 51, and the second seal member 72 is disposed between the outer peripheral surface of the protruding portion of the cylindrical shaft portion 633 and the inner peripheral surface of the outer case cylindrical portion 915. The second seal member 72 is disposed so as to overlap with the engaged portion 6a of the specific bevel gear 63S in a radial view along the radial direction R. Here, with respect to the arrangement of the two elements, "overlapping in a specific direction view" means that when a virtual straight line parallel to the line-of-sight direction is moved in each direction orthogonal to the virtual straight line, there is at least a part of a region where the virtual straight line intersects both of the two elements.

[0061] Thus, in the present embodiment, an outer case 9 that houses the input member 10, the speed reducer 3, and the differential gear device 4 is further provided. The outer case 9 further includes an outer case cylindrical portion 915 formed in a cylindrical shape and disposed so as to cover the cylindrical shaft portion 633 from the radial outside R2. A second seal member 72 is provided to seal the space between the outer peripheral surface of the cylindrical shaft portion 633 and the inner peripheral surface of the outer case cylindrical portion 915 in an oil-tight manner. The second seal member 72 is disposed so as to overlap with the engaged portion 6a in a radial view along the radial direction R.

[0062] As described above, this configuration is achievable because the fitting portion for restricting the deviation and inclination between the rotation axis of the specific output shaft 2S and the rotation axis of the specific bevel gear 63S is not provided on the specific bevel gear 63S. According to this configuration, compared with a configuration in which the second seal member 72 is disposed axially displaced from the engaged portion 6a in the axial direction L, while suppressing the axial dimension in the axial direction L of the vehicle drive device 100 to be small, it is possible to appropriately restrict the oil inside the outer case 9 from leaking from the radial gap between the outer peripheral surface of the cylindrical shaft portion 633 and the inner peripheral surface of the outer case cylindrical portion 915.

[0063] In the present embodiment, an outer case 9 that houses the input member 10, the speed reducer 3, and the differential gear device 4 is further provided. The outer case 9 includes an outer support portion 914 disposed radially outward R2 with respect to the differential case cylindrical portion 51, and the outer support portion 914, the differential case cylindrical portion 51, and the engaged portion 6a are arranged so as to overlap each other in a radial view along the radial direction R.

[0064] According to this configuration, compared with a configuration in which the outer support portion 914, the differential case cylindrical portion 51, and the engaged portion 6a are arranged with an axial shift in the axial direction L, it is easier to suppress the dimension of the vehicle drive device 100 in the axial direction L.

[0065] 〔Other Embodiments〕 (1) In the above embodiment, the configuration in which the drive power source D drivingly connected to the input member 10 is the rotary electric machine 1 has been described as an example. However, the present invention is not limited to such a configuration, and the drive power source D may be an internal combustion engine. In this case, the rotary electric machine 1 is not provided, and the wheels W may be driven using only the driving force of the internal combustion engine. Alternatively, a configuration in which the wheels W are driven using the driving forces of both the internal combustion engine and the rotary electric machine, that is, a configuration in which the vehicle drive device 100 is a drive device for a hybrid vehicle, is also possible.

[0066] (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 coaxially, and the input member 10, the speed reducer 3, and the differential gear device 4 are arranged in the described order from the first axial side L1 to the second axial side L2 as an example. However, the present invention is not limited to such a configuration, 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 a separate axis. Further, 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.

[0067] (3) In the above-described embodiment, the speed reducer 3 is described by taking as an example the configuration of a planetary gear mechanism disposed on the output rotation axis center X. However, it is not limited to such a configuration. For example, the speed reducer 3 may be a configuration of a counter gear mechanism instead of a planetary gear mechanism. In this configuration, the counter gear mechanism is disposed across the output rotation axis center X and an axis different from the output rotation axis center X.

[0068] (4) In the above-described embodiment, the speed reducer 3 is described by taking as an example the configuration of a planetary gear mechanism including a sun gear SG, a carrier CR, a first ring gear RG1, and a second ring gear RG2. However, it is not limited to such a configuration. For example, the speed reducer 3 may be a single pinion type planetary gear mechanism.

[0069] (5) In the above-described embodiment, a 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 side L2 in the axial direction and the surface of the outer support portion 914 facing the first side L1 in the axial direction, and a 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, it is not limited to such a configuration. For example, a ball bearing 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 side L2 in the axial direction and the surface of the outer support portion 914 facing the first side L1 in the axial direction, and between the outer peripheral surface of the differential case 5 and the inner peripheral surface of the outer support portion 914.

[0070] (6) In the above-described embodiment, the second seal member 72 is described by taking as an example the configuration disposed so as to overlap the engaged portion 6a in a radial view along the radial direction R. However, it is not limited to such a configuration. For example, the second seal member 72 may be disposed on the second side L2 in the axial direction with respect to the engaged portion 6a.

[0071] (7) In the above-described embodiment, the outer support portion 914, the differential case cylindrical portion 51, and the engaged portion 6a are described by taking as an example a configuration in which they are arranged so as to overlap each other in a radial direction view along the radial direction R. However, the present invention is not limited to such a configuration. For example, the engaged portion 6a may be arranged on the second side L2 in the axial direction with respect to the outer support portion 914 and the differential case cylindrical portion 51.

[0072] (8) In addition, the configurations disclosed in the above-described embodiments can be applied in combination with the configurations disclosed in other embodiments as long as no contradiction occurs. Regarding other configurations as well, all the embodiments disclosed in this specification are merely examples in all respects. Therefore, various modifications can be made as appropriate within the scope not departing from the gist of the present disclosure.

[0073] Summary of the present embodiment Hereinafter, an outline of the vehicle drive device (100) described above will be described.

[0074] The vehicle drive device (100) includes an input member (10) drivingly connected to a driving force source (D), a pair of output shafts (2) each drivingly connected to a wheel (W), a speed reducer (3) for reducing the rotation of the input member (10), a differential gear device (4) for distributing the rotation of the input member (10) transmitted through the speed reducer (3) to the pair of output shafts (2), and is a vehicle drive device (100) including Taking the direction along the output rotation axis center (X) which is the rotation axis center of the pair of output shafts (2) as the axial direction (L), one side of the axial direction (L) as the first side (L1) in the axial direction, the other side of the axial direction (L) as the second side (L2) in the axial direction, the direction orthogonal to the output rotation axis center (X) as the radial direction (R), and the direction around the output rotation axis center (X) as the circumferential direction (C), the differential gear device (4) includes a differential case (5) and a differential gear mechanism (6) housed in the differential case (5), The differential gear mechanism (6) includes a shaft member (61) formed to extend along the radial direction (R), a plurality of first bevel gears (62) rotatably supported by the shaft member (61) and arranged separately in the circumferential direction (C), and a pair of second bevel gears (63) arranged separately on both sides of the shaft member (61) in the axial direction (L) and meshing with the plurality of first bevel gears (62). The pair of second bevel gears (63) are each connected so as to rotate integrally with the pair of output shafts (2). Of the pair of second bevel gears (63), the one arranged on the second axial side (L2) with respect to the shaft member (61) is defined as a specific bevel gear (63S), and of the pair of output shafts (2), the one that rotates integrally with the specific bevel gear (63S) is defined as a specific output shaft (2S). An engaging portion (2a) provided on the specific output shaft (2S) and an engaged portion (6a) provided on the specific bevel gear (63S) are engaged with each other so as to restrict relative movement between 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 in the axial direction (L) with respect to the differential case (5), but is not supported in the radial direction (R).

[0075] According to this configuration, the specific bevel gear (63S) is not supported in the radial direction (R) with respect to the differential case (5), and is supported in the radial direction (R) by the centering action due to the meshing between the specific bevel gear (63S) and the plurality of first bevel gears (62). Therefore, it is possible to eliminate the need for bearings and fitting portions for supporting the specific bevel gear (63S) in the radial direction (R) with respect to the differential case (5). Also, according to this configuration, 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, there is no need to provide a fitting portion on the specific bevel gear (63S) for restricting the deviation and inclination between the rotation axis of the specific output shaft (2S) and the rotation axis of the specific bevel gear (63S) when the specific output shaft (2S) is fitted. As described above, according to this configuration, it is easy to reduce the size of the support structure for the specific bevel gear (63S) and the specific output shaft (2S) with respect to the differential case (5). Therefore, in a configuration including the bevel gear type differential gear device (4), it is easy to reduce the size of the vehicle drive device (100).

[0076] Here, the specific bevel gear (63S) includes a bevel gear portion (631) that meshes with a plurality of the first bevel gears (62), a bevel gear support portion (632) that is integrally formed with the bevel gear portion (631) and supports the bevel gear portion (631), and a cylindrical shaft portion (633) that is formed in a cylindrical shape and extends from the bevel gear support portion (632) to the second side (L2) in the axial direction. The differential case (5) includes a differential case cylindrical portion (51) that is formed in a cylindrical shape and is arranged to cover the cylindrical shaft portion (633) from the outer side (R2) in the radial direction (R). It is preferable that a first clearance (C1), which is a clearance 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).

[0077] According to this configuration, a configuration in which the specific bevel gear (63S) is not supported in the radial direction (R) with respect to the differential case (5) can be appropriately realized. Thereby, a configuration in which the specific bevel gear (63S) is supported in the radial direction (R) by the centering action due to the meshing between the specific bevel gear (63S) and the first bevel gear (62) can be appropriately realized.

[0078] In a configuration in which the first clearance (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 second clearance (C2), which is a clearance in the radial direction (R), is provided between the tooth surfaces of each of the plurality of the first bevel gears (62) and the tooth surface of the specific bevel gear (63S). It is preferable that the first clearance (C1) is larger than the second clearance (C2).

[0079] According to this configuration, when the specific output shaft (2S) is not rotating, if the first bevel gear (62) moves relative to the specific bevel gear (63S) radially inward (R1) in the radial direction (R) so that the differential case cylindrical portion (51) approaches the cylindrical shaft portion (633), the second clearance (C2) becomes zero before the first clearance (C1) becomes zero. Thereby, since it is possible to restrict the further relative movement of the first bevel gear (62) radially inward (R1) with respect to the specific bevel gear (63S), it is possible to avoid the differential case cylindrical portion (51) from contacting the cylindrical shaft portion (633).

[0080] Further, the vehicle drive device (100) further includes an outer case (9) that houses the input member (10), the speed reducer (3), and the differential gear device (4). The outer case (9) further includes an outer case cylindrical portion (915) formed in a cylindrical shape and arranged to cover the cylindrical shaft portion (633) from the outside (R2) in the radial direction (R). A seal member (72) is provided to seal the space between the outer peripheral surface of the cylindrical shaft portion (633) and the inner peripheral surface of the outer case cylindrical portion (915) in an oil-tight manner. The seal member (72) is preferably arranged so as to overlap with the engaged portion (6a) in a radial view along the radial direction (R).

[0081] As described above, this configuration is achievable because the fitting portion for restricting the deviation and inclination between the rotation axis of the specific output shaft (2S) and the rotation axis of the specific bevel gear (63S) is not provided on the specific bevel gear (63S). And according to this configuration, compared with the configuration in which the second seal member (72) is arranged axially (L) displaced from the engaged portion (6a), while suppressing the axial (L) dimension of the vehicle drive device (100) to be small, it is possible to appropriately restrict the oil inside the outer case (9) from leaking from the radial (R) gap between the outer peripheral surface of the cylindrical shaft portion (633) and the inner peripheral surface of the outer case cylindrical portion (915).

[0082] The vehicle drive device (100) further includes an outer case (9) that houses the input member (10), the speed reducer (3), and the differential gear device (4). The outer case (9) includes an outer support portion (914) disposed on the outer side (R2) in the radial direction (R) with respect to the differential case cylindrical portion (51). It is preferable that the outer support portion (914), the differential case cylindrical portion (51), and the engaged portion (6a) are arranged so as to overlap each other in a radial view along the radial direction (R).

[0083] According to this configuration, compared with a configuration in which the outer support portion (914), the differential case cylindrical portion (51), and the engaged portion (6a) are arranged with an axial displacement in the axial direction (L), it is easier to suppress the axial dimension of the vehicle drive device (100) in the axial direction (L).

Industrial Applicability

[0084] The technology according to the present disclosure can be used in a vehicle drive device including an input member drivingly connected to a driving power source, a pair of output shafts each drivingly connected to a wheel, a speed reducer that decelerates the rotation of the input member, and a differential gear device that distributes the rotation of the input member transmitted through the speed reducer to the pair of output shafts.

Explanation of Reference Numerals

[0085] 100: Vehicle drive device, 10: Input member, 2: Output shaft, 2S: Specific output shaft, 2a: Engaged portion, 3: Speed reducer, 4: Differential gear device, 5: Differential case, 51: Differential case cylindrical portion, 52: Radially extending portion, 6: Differential gear mechanism, 6a: Engaged portion, 61: Shaft member, 62: First bevel gear, 63: Second bevel gear, 63S: Specific bevel gear, 631: Bevel gear portion, 632: Bevel gear support portion, 633: Cylindrical shaft portion, 72: Second seal member (seal member), 9: Outer case, 914: Outer support portion, 915: Outer case cylindrical portion, D: Driving power source, B4: Thrust bearing, B5: Radial bearing, W: Wheel, L: Axial direction, L1: First axial side, L2: Second axial side, R: Radial direction, R1: Radial inner side, R2: Radial outer side, C: Circumferential direction

Claims

1. An input member drivingly connected to a driving power source, A pair of output shafts each drivingly connected to a wheel, A speed reducer that reduces the rotation of the input member, A vehicle drive device comprising a differential gear device that distributes the rotation of the input member transmitted through the speed reducer to the pair of output shafts, With the direction along the output rotation axis, which is the rotation axis of the pair of output shafts, as the axial direction, one side in the axial direction as the first axial side, the other side in the axial direction as the second axial side, the direction orthogonal to the output rotation axis as the radial direction, and the direction around the output rotation axis as the circumferential direction, The differential gear device includes a differential case and a differential gear mechanism housed in the differential case, The differential gear mechanism includes a shaft member formed to extend along 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 each connected to rotate integrally with the pair of output shafts, Of the pair of second bevel gears, the one arranged on the second axial side with respect to the shaft member is defined as a specific bevel gear, and of the pair of output shafts, the one that rotates integrally with the specific bevel gear is defined as a specific output shaft, An engaging portion provided on the specific output shaft and an engaged portion provided on the specific bevel gear are engaged with each other so as to restrict the 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 in the axial direction with respect to the differential case, but not supported in the radial direction, The specific bevel gear includes a bevel gear portion that meshes with the plurality of first bevel gears, a bevel gear support portion formed integrally with the bevel gear portion to support the bevel gear portion, and a cylindrical shaft portion formed in a cylindrical shape and extending from the bevel gear support portion to 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 outside in the radial direction, A first clearance, which is a clearance in the radial direction, is provided between the outer peripheral surface of the cylindrical shaft portion and the inner peripheral surface of the differential case cylindrical portion, The vehicle drive device further includes an outer case that houses the input member, the speed reducer, and the differential gear device, The outer case further includes an outer case 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 space between the outer peripheral surface of the cylindrical shaft portion and the inner peripheral surface of the outer case cylindrical portion in an oil-tight manner. The sealing member is arranged so as to overlap the engaged portion in a view in the radial direction along the radial direction. A vehicle drive device.

2. An input member drivingly connected to a driving force source, A pair of output shafts each drivingly connected to a wheel, A speed reducer that reduces the rotation of the input member, A vehicle drive device comprising a differential gear device that distributes the rotation of the input member transmitted through the speed reducer to the pair of output shafts, Taking the direction along the output rotation axis, which is the rotation axis of the pair of output shafts, as the axial direction, one side in the axial direction as the first axial side, the other side in the axial direction as the second axial side, the direction orthogonal to the output rotation axis as the radial direction, and the direction around the output rotation axis as the circumferential direction, The differential gear device includes a differential case and a differential gear mechanism housed in the differential case. The differential gear mechanism includes a shaft member formed to extend along 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 each connected so as to rotate integrally with the pair of output shafts. Of the pair of second bevel gears, the one arranged on the second axial side with respect to the shaft member is defined as a specific bevel gear, and of the pair of output shafts, the one that rotates integrally with the specific bevel gear is defined as a specific output shaft. An engaging portion provided on the specific output shaft and an engaged portion provided on the specific bevel gear are engaged with each other so as to restrict the 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 in the axial direction with respect to the differential case, but not supported in the radial direction. The specific output shaft is not supported in the radial direction with respect to the differential case. A vehicle drive device.

3. The specific bevel gear includes a bevel gear portion that meshes with the plurality of first bevel gears, a bevel gear support portion that is integrally formed with the bevel gear portion and supports the bevel gear portion, and a cylindrical shaft portion that extends from the bevel gear support portion to the second side in the axial direction. The differential case includes a differential case cylindrical portion that is formed in a cylindrical shape and is arranged to cover the cylindrical shaft portion from the outside in the radial direction. The vehicle drive device according to claim 2, wherein a first clearance, which is a clearance in the radial direction, is provided between an outer peripheral surface of the cylindrical shaft portion and an inner peripheral surface of the differential case cylindrical portion.

4. A second clearance, which is a clearance in the radial direction, is provided between tooth surfaces of each of the plurality of first bevel gears and a tooth surface of the specific bevel gear. The vehicle drive device according to claim 3, wherein the first clearance is larger than the second clearance.

5. The vehicle drive device further includes an outer case that houses the input member, the speed reducer, and the differential gear device. The outer case includes an outer support portion that is arranged on the outside in the radial direction with respect to the differential case cylindrical portion. The vehicle drive device according to any one of claims 1, 3, and 4, wherein the outer support portion, the differential case cylindrical portion, and the engaged portion are arranged to overlap each other in a radial view along the radial direction.

Images