Vehicle drive device

Abstract

A first rotating element (E1) is a first sun gear (SG1) that rotates integrally with a rotor (12), a third rotating element (E3) is a first ring gear (RG1) that is coupled to a case (9), a fourth rotating element (E4) is a second ring gear (RG2) that rotates integrally with an input element (Ei), and a second rotating element (E2) is a first carrier (CR1) that rotatably supports a first pinion gear (PG1) and a second pinion gear (PG2) which rotate integrally with one another, wherein: the first pinion gear (PG1) meshes with the first sun gear (SG1) and the first ring gear (RG1); the second pinion gear (PG2) has a smaller diameter than the first pinion gear (PG1) and meshes with the second ring gear (RG2); the first sun gear (SG1) is supported in a radial direction (R) with respect to the case (9) by means of a first support bearing (B1); and the second ring gear (RG2) and the input element (Ei) are coupled such that relative displacement in the radial direction (R) is restricted.

Description

Technical Field

[0001] The present invention relates to a vehicle drive device including a rotating electric machine and a planetary gear mechanism.

Background Art

[0002] An example of such a vehicle drive device is disclosed in Patent Documents 1 and 2 below. In the following description of the background art, the reference numerals in the cited patent documents are enclosed in parentheses.

[0003] The planetary gear mechanism (4) of the vehicle drive device (1) in Patent Document 1 includes a sun gear (41), a ring gear (42), and a carrier (6, 7). The sun gear (41) is connected so as to rotate integrally with the rotor (21) of the rotating electric machine (2). The ring gear (42) is fixed to the case (10). The carrier (6, 7) rotatably supports a first pinion gear (431) and a second pinion gear (432) that are connected so as to rotate integrally with each other. The first pinion gear (431) meshes with the sun gear (41). The second pinion gear (432) has a smaller diameter than the first pinion gear (431) and meshes with the ring gear (42). Further, the carrier (6, 7) is connected so as to rotate integrally with the differential case (50) of the output differential gear mechanism (5). Thus, the planetary gear mechanism (4) decelerates the rotation of the rotor (21) and transmits it to the output differential gear mechanism (5).

[0004] In addition, the planetary gear mechanism (3) of the vehicle drive device in Patent Document 2 includes a sun gear (S1), a carrier (C), a first ring gear (R1), and a second ring gear (R2) (see FIG. 4 of Patent Document 2). The sun gear (S1) is connected so as to rotate integrally with the rotor of the rotary electric machine (2). The carrier (C) rotatably supports a first pinion gear (P1) and a second pinion gear (P2) that are connected so as to rotate integrally with each other. The first pinion gear (P1) meshes with the sun gear (S1) and the first ring gear (R1). The second pinion gear (P2) has a smaller diameter than the first pinion gear (P1) and meshes with the second ring gear (R2). The first ring gear (R1) is fixed to the case (1). The second ring gear (R2) is connected to an output differential gear mechanism (4) that is a bevel gear type differential gear mechanism. In this way, the planetary gear mechanism (3) decelerates the rotation of the rotor of the rotary electric machine (2) and transmits it to the output differential gear mechanism (4).

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

Patent Document 2

Summary of the Invention

Problems to be Solved by the Invention

[0006] In the vehicle drive device (1) of Patent Document 1, the input element of the planetary gear mechanism (4) is the sun gear (41), and the output element of the planetary gear mechanism (4) is the carrier (6, 7). With such a configuration, it has been difficult to increase the reduction ratio of the planetary gear mechanism (4) without securing a large radial dimension of the planetary gear mechanism (4).

[0007] In addition, in the vehicle drive device (1) of Patent Document 1, the planetary gear mechanism (4) is arranged on the radially outer side of the bevel gear type output differential gear mechanism (5). Therefore, the axial dimension of the vehicle drive device (1) is suppressed to be small. However, as described above, the carriers (6, 7) that support the first pinion gear (431) and the second pinion gear (432) are connected so as to rotate integrally with the differential case (50) of the output differential gear mechanism (5). Therefore, when the planetary gear mechanism (4) is arranged on the radially outer side of the output differential gear mechanism (5), the vehicle drive device (1) tends to be enlarged in the radial direction.

[0008] On the other hand, the planetary gear mechanism (3) of the vehicle drive device of Patent Document 2 is configured to easily ensure a large reduction ratio while suppressing the radial dimension. By the way, the differential case (DC) of the output differential gear mechanism (4) is generally supported by the case (1) on both axial sides with respect to the plurality of gears (DP1, DP2, DSI1, DSI2) that constitute the output differential gear mechanism (4). The vehicle drive device of Patent Document 2 does not describe such a support structure of the output differential gear mechanism (4).

[0009] Therefore, in a configuration including a planetary gear mechanism for deceleration and an output differential gear mechanism, it is desired to realize a vehicle drive device that can easily achieve miniaturization while ensuring a large reduction ratio of the planetary gear mechanism and appropriately supporting the output differential gear mechanism.

Means for Solving the Problems

[0010] In view of the above, the characteristic configuration of the vehicle drive device is a rotary electric machine having a rotor, a first output member drivingly connected to a first wheel, a second output member drivingly connected to a second wheel, a planetary gear mechanism that decelerates the rotation of the rotor, an output differential gear mechanism having an input element and distributing the rotation transmitted from the planetary gear mechanism to the input element to the first output member and the second output member, A vehicle drive device including: a case that houses the rotary electric machine, the planetary gear mechanism, and the output differential gear mechanism. The rotary electric machine, the first output member, the second output member, the planetary gear mechanism, and the output differential gear mechanism are arranged coaxially. The planetary gear mechanism includes a first rotating element, a second rotating element, a third rotating element, and a fourth rotating element, and is configured such that the order of the rotational speeds of the first rotating element, the second rotating element, the third rotating element, and the fourth rotating element is the same as the described order. The first rotating element is a first sun gear connected to rotate integrally with the rotor. The third rotating element is a first ring gear connected to the case. The fourth rotating element is a second ring gear connected to rotate integrally with the input element. The second rotating element is a first carrier that rotatably supports a first pinion gear and a second pinion gear that rotate integrally with each other. The first pinion gear meshes with the first sun gear and the first ring gear. The second pinion gear has a smaller diameter than the first pinion gear and meshes with the second ring gear. Taking the direction orthogonal to the rotation axis of the rotor as the radial direction, The first sun gear is supported in the radial direction with respect to the case via a first support bearing. The second ring gear and the input element are connected in a state where relative movement in the radial direction is restricted.

[0011] According to this characteristic configuration, the first rotating element of the planetary gear mechanism is connected to the rotor. And the third rotating element of the planetary gear mechanism is connected to the case, and the fourth rotating element of the planetary gear mechanism is connected to the input element of the output differential gear mechanism. Also, each of the third rotating element and the fourth rotating element of the planetary gear mechanism is a ring gear. Thereby, it is easy to ensure a large reduction ratio (for example, 17 to 22) of the planetary gear mechanism that functions as a speed reducer that decelerates the rotation of the rotor and transmits it to the output differential gear mechanism. Further, according to this characteristic configuration, the fourth rotating element connected to the input element of the output differential gear mechanism is a ring gear. As a result, compared with a configuration in which the rotating element connected to the input element of the output differential gear mechanism is a sun gear or a carrier, while suppressing the radial dimensions of the planetary gear mechanism, it is easy to arrange the planetary gear mechanism closer to the output differential gear mechanism in the axial direction. Also, according to this characteristic configuration, the third rotating element connected to the case is a ring gear. As a result, it is easy to form a configuration in which a radially extending support member or the like, which is required when a sun gear or a carrier is connected to the case, can be omitted. Therefore, it is easy to suppress the axial dimensions of the vehicle drive device. Further, according to this characteristic configuration, the first sun gear as the first rotating element of the planetary gear mechanism is supported radially with respect to the case via a first support bearing. And, the second ring gear as the fourth rotating element of the planetary gear mechanism and the input element of the output differential gear mechanism are connected in a state where relative radial movement is restricted. As a result, the input element of the output differential gear mechanism can be supported radially by utilizing the centering action (automatic centering action) of the planetary gear mechanism. As a result, while omitting members such as bearings that support the input element of the output differential gear mechanism radially with respect to the case, the output differential gear mechanism can be appropriately supported. Therefore, it is easy to reduce the size and cost of the vehicle drive device. As described above, according to this characteristic configuration, in a configuration including a planetary gear mechanism for speed reduction and an output differential gear mechanism, it is easy to reduce the size of the vehicle drive device while ensuring a large reduction ratio of the planetary gear mechanism and appropriately supporting the output differential gear mechanism.

Brief Description of the Drawings

[0012]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Embodiments for Carrying Out the Invention

[0013] 1. First Embodiment Hereinafter, the vehicle drive device 100 according to the first embodiment will be described with reference to FIGS. 1 to 3. As shown in FIGS. 1 and 2, the vehicle drive device 100 includes a rotating electric machine 1 having a stator 11 and a rotor 12, a first output member 2 drivingly connected to the first wheel W1, a second output member 3 drivingly connected to the second wheel W2, a planetary gear mechanism 4, an output differential gear mechanism 5, and a case 9.

[0014] Here, in the present application, "driving connection" refers to a state in which two rotating elements are connected so as to be able to transmit a driving force, and includes a state in which the two rotating elements are connected so as to rotate integrally, or a state in which the two rotating elements are connected so as to be able to transmit a driving force via one or two or more transmission members. Such transmission members include various members that transmit rotation at the same speed or with speed change, for example, shafts, gear mechanisms, belts, chains, etc. Note that the transmission members may include engagement devices that selectively transmit rotation and driving force, such as friction engagement devices, meshing engagement devices, etc.

[0015] In the following description, the direction along the rotation axis center of the rotor 12 (refer to the one-dot chain line in FIG. 1) 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 rotation axis center of the rotor 12 is defined as the "radial direction R". And in the radial direction R, the side closer to the rotation axis center of the rotor 12 is defined as the "radial inner side R1", and the opposite side is defined as the "radial outer side R2". Also, the direction of orbiting around the rotation axis center of the rotor 12 is defined as the "circumferential direction C".

[0016] The rotating electrical machine 1, the first output member 2, the second output member 3, the planetary gear mechanism 4, and the output differential gear mechanism 5 are arranged coaxially. In the present embodiment, the output differential gear mechanism 5, the planetary gear mechanism 4, and the rotating electrical machine 1 are arranged in the described order from the first axial side L1 toward the second axial side L2. In the example shown in FIG. 1, a part of the second output member 3 is arranged so as to overlap the rotating electrical machine 1 in a radial view along the radial direction R. Here, regarding the arrangement of 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.

[0017] The rotating electrical machine 1, the planetary gear mechanism 4, and the output differential gear mechanism 5 are housed in the case 9. In the present embodiment, the first output member 2 and the second output member 3 are housed in the case 9 with a part of them exposed to the outside of the case 9.

[0018] As shown in FIG. 1, in the present embodiment, the case 9 includes a peripheral wall portion 91, a first side wall portion 92, a second side wall portion 93, a partition portion 94, and a cover portion 95.

[0019] The peripheral wall portion 91 is formed in a cylindrical shape that covers the radially outer side R2 of the rotating electric machine 1, the first output member 2, the second output member 3, the planetary gear mechanism 4, and the output differential gear mechanism 5. Each of the first side wall portion 92, the second side wall portion 93, and the partition wall portion 94 is formed to extend in the radial direction R and the circumferential direction C. The cover portion 95 is provided so as to cover a part of the second side wall portion 93 from the second side L2 in the axial direction. In the present embodiment, the first side wall portion 92 is formed so as to cover the first side L1 in the axial direction of the output differential gear mechanism 5. And the second side wall portion 93 is formed so as to cover the second side L2 in the axial direction of the rotating electric machine 1. Further, the partition wall portion 94 is disposed between the rotating electric machine 1 and the planetary gear mechanism 4 in the axial direction L. Also, the cover portion 95 is joined to the second side wall portion 93 from the second side L2 in the axial direction. In this example, the first side wall portion 92 is integrally formed with the peripheral wall portion 91 so as to close the opening on the first side L1 in the axial direction of the peripheral wall portion 91. Also, the second side wall portion 93 is integrally formed with the peripheral wall portion 91 so as to close the opening on the second side L2 in the axial direction of the peripheral wall portion 91. Note that in the example shown in FIG. 1, the peripheral wall portion 91 is divided at a plurality of locations (here, two locations) in the axial direction L. And the divided portions of the peripheral wall portion 91 are joined to each other and fastened by a fastening member such as a bolt (not shown).

[0020] The rotating electric machine 1 functions as a driving power source for the first wheel W1 and the second wheel W2 (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. And the rotating electric machine 1 generates a driving force by traveling with the electric power stored in the power storage device. Also, the rotating electric machine 1 generates electric power by the driving force transmitted from the sides of the first wheel W1 and the second wheel W2 and charges the power storage device.

[0021] The stator 11 of the rotating electrical machine 1 includes a cylindrical stator core 11a. The stator core 11a is fixed to the non-rotating member NR. In the present embodiment, the stator core 11a is fixed to the peripheral wall portion 91 of the case 9 as the non-rotating member NR. The rotor 12 of the rotating electrical machine 1 includes a cylindrical rotor core 12a. The rotor core 12a is rotatably supported with respect to the stator core 11a. In the present embodiment, the rotor 12 further includes a rotor shaft 12b connected so as to rotate integrally with the rotor core 12a.

[0022] 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. Further, the rotor shaft 12b is arranged on the radially inner side R1 with respect to the rotor core 12a.

[0023] Further, in the present embodiment, the rotating electrical machine 1 is a rotating field type rotating electrical machine. Therefore, the stator 11 further includes a coil 11b. In the present embodiment, the coil 11b is wound around the stator core 11a such that a first coil end portion 11c protruding to the first axial side L1 with respect to the stator core 11a and a second coil end portion 11d protruding to the second axial side L2 with respect to the stator core 11a are formed. Although not shown, permanent magnets are provided on the rotor core 12a.

[0024] In this embodiment, the rotor shaft 12b is formed in a cylindrical shape having an axis along the axial direction L. Further, the rotor shaft 12b is arranged so as to project from both sides of the rotor core 12a in the axial direction L. In this embodiment, the portion of the rotor shaft 12b that projects from the rotor core 12a to the first axial side L1 in the axial direction is arranged so as to penetrate the partition wall portion 94 of the case 9 in the axial direction L. And the portion of the rotor shaft 12b that projects from the rotor core 12a to the first axial side L1 in the axial direction is rotatably supported with respect to the partition wall portion 94 via the first bearing B1. Also, the portion of the rotor shaft 12b that projects from the rotor core 12a to the second axial side L2 in the axial direction is rotatably supported with respect to the second side wall portion 93 via the second bearing B2. Note that, in this embodiment, the rotation sensor 13 for detecting the rotation of the rotor 12 is provided integrally with the first bearing B1.

[0025] The planetary gear mechanism 4 includes a first rotating element E1, a second rotating element E2, a third rotating element E3, and a fourth rotating element E4. And the planetary gear mechanism 4 is configured such that the order of the rotational speeds of the first rotating element E1, the second rotating element E2, the third rotating element E3, and the fourth rotating element E4 is the same as the described order.

[0026] Here, the "order of rotational speeds" refers to the order of the rotational speeds in the rotational state of each rotating element. The rotational speed of each rotating element changes depending on the rotational state of the planetary gear mechanism, but the order of the magnitudes of the rotational speeds of each rotating element is constant because it is determined by the structure of the planetary gear mechanism. Note that the order of the rotational speeds of each rotating element is equal to the order of arrangement in the speed diagram (see FIG. 3) of each rotating element. Here, the "order of arrangement in the speed diagram of each rotating element" refers to the order in which the axes corresponding to each rotating element in the speed diagram are arranged along the direction orthogonal to the axis. The arrangement direction of the axes corresponding to each rotating element in the speed diagram varies depending on the way the speed diagram is drawn, but the order of arrangement is constant because it is determined by the structure of the planetary gear mechanism.

[0027] The output differential gear mechanism 5 includes an input element Ei. The output differential gear mechanism 5 is configured to distribute the rotation transmitted from the planetary gear mechanism 4 to the input element Ei to the first output member 2 and the second output member 3. In the present embodiment, the output differential gear mechanism 5 is a planetary gear mechanism including a fifth rotating element E5, a sixth rotating element E6, and a seventh rotating element E7. And the output differential gear mechanism 5 is configured such that the order of the rotational speeds of the fifth rotating element E5, the sixth rotating element E6, and the seventh rotating element E7 is the same as the described order. In the present embodiment, the fifth rotating element E5 is connected to the first output member 2. And the seventh rotating element E7 is connected to the second output member 3.

[0028] The planetary gear mechanism 4 functions as a speed reducer that reduces the rotation of the rotor 12 and transmits it to the output differential gear mechanism 5. The first rotating element E1 of the planetary gear mechanism 4 is connected to rotate integrally with the rotor 12. The third rotating element E3 of the planetary gear mechanism 4 is connected to the case 9. The fourth rotating element E4 of the planetary gear mechanism 4 is connected to rotate integrally with the input element Ei of the output differential gear mechanism 5. In the present embodiment, the fourth rotating element E4 is integrally formed with the input element Ei. In the present embodiment, the input element Ei is the sixth rotating element E6.

[0029] The first rotating element E1 of the planetary gear mechanism 4 is the first sun gear SG1. The first sun gear SG1 is supported in the radial direction R with respect to the case 9 via the first bearing B1. The first bearing B1 corresponds to the "first support bearing" that supports the first sun gear SG1 in the radial direction R with respect to the case 9. In the present embodiment, the first sun gear SG1 is connected so as to rotate integrally with the rotor shaft 12b. Further, as described above, in the present embodiment, the portion of the rotor shaft 12b that protrudes axially from the first side L1 from the rotor core 12a is rotatably supported with respect to the partition wall portion 94 of the case 9 via the first bearing B1. Therefore, in the present embodiment, the first bearing B1 is supported by the partition wall portion 94 and is configured to support the first sun gear SG1 in the radial direction R and the rotor 12 in the radial direction R. The partition wall portion 94 corresponds to the "first support wall portion" disposed between the axial direction L of the rotating electric machine 1 and the planetary gear mechanism 4. In the example shown in FIG. 1, the first sun gear SG1 is integrally formed with the rotor shaft 12b.

[0030] The second rotating element E2 of the planetary gear mechanism 4 is the first carrier CR1. The first carrier CR1 rotatably supports the first pinion gear PG1 and the second pinion gear PG2 that rotate integrally with each other. The first pinion gear PG1 meshes with the first sun gear SG1 and the first ring gear RG1. The second pinion gear PG2 meshes with the second ring gear RG2. Further, the second pinion gear PG2 has a smaller diameter than the first pinion gear PG1.

[0031] Each of the third rotating element E3 and the fourth rotating element E4 of the planetary gear mechanism 4 is a ring gear. Specifically, the third rotating element E3 is the first ring gear RG1. And the fourth rotating element E4 is the second ring gear RG2. Further, in the present embodiment, the sixth rotating element E6 of the output differential gear mechanism 5 is the third ring gear RG3. That is, in the present embodiment, the second ring gear RG2 as the fourth rotating element E4 of the planetary gear mechanism 4 and the third ring gear RG3 as the input element Ei of the output differential gear mechanism 5 and the sixth rotating element E6 are connected so as to rotate integrally.

[0032] The second ring gear RG2 and the input element Ei are connected in a state where relative movement in the radial direction R is restricted. In the example shown in FIG. 1, the second ring gear RG2 and the third ring gear RG3 as the input element Ei are integrally formed in a state of being adjacent to each other in the axial direction L.

[0033] As described above, the vehicle drive device 100 includes a rotary electric machine 1 having a rotor 12, a first output member 2 drivingly connected to the first wheel W1, a second output member 3 drivingly connected to the second wheel W2, a planetary gear mechanism 4 that decelerates the rotation of the rotor 12, an output differential gear mechanism 5 that includes an input element Ei and distributes the rotation transmitted from the planetary gear mechanism 4 to the input element Ei to the first output member 2 and the second output member 3, and a case 9 that houses the rotary electric machine 1, the planetary gear mechanism 4, and the output differential gear mechanism 5. The vehicle drive device 100 has the rotary electric machine 1, the first output member 2, the second output member 3, the planetary gear mechanism 4, and the output differential gear mechanism 5 arranged coaxially, the planetary gear mechanism 4 includes a first rotating element E1, a second rotating element E2, a third rotating element E3, and a fourth rotating element E4, and is configured such that the order of the rotational speeds of the first rotating element E1, the second rotating element E2, the third rotating element E3, and the fourth rotating element E4 is the same as the described order, the first rotating element E1 is a first sun gear SG1 connected to rotate integrally with the rotor 12, the third rotating element E3 is a first ring gear RG1 connected to the case 9, the fourth rotating element E4 is a second ring gear RG2 connected to rotate integrally with the input element Ei, the second rotating element E2 is a first carrier CR1 that rotatably supports a first pinion gear PG1 and a second pinion gear PG2 that rotate integrally with each other, the first pinion gear PG1 meshes with the first sun gear SG1 and the first ring gear RG1, The second pinion gear PG2 has a smaller diameter than the first pinion gear PG1, meshes with the second ring gear RG2, The first sun gear SG1 is supported in the radial direction R with respect to the case 9 via the first bearing B1 as the first support bearing, The second ring gear RG2 and the input element Ei are connected in a state where relative movement in the radial direction R is restricted.

[0034] According to this configuration, the first rotating element E1 of the planetary gear mechanism 4 is connected to the rotor 12. And the third rotating element E3 of the planetary gear mechanism 4 is connected to the case 9, and the fourth rotating element E4 of the planetary gear mechanism 4 is connected to the input element Ei of the output differential gear mechanism 5. Also, each of the third rotating element E3 and the fourth rotating element E4 of the planetary gear mechanism 4 is a ring gear. Thereby, it is easy to ensure a large reduction ratio (for example, 17 to 22) of the planetary gear mechanism 4 that functions as a speed reducer for reducing the rotation of the rotor 12 and transmitting it to the output differential gear mechanism 5. Also, according to this configuration, the fourth rotating element E4 connected to the input element Ei of the output differential gear mechanism 5 is a ring gear. Thereby, compared with a configuration in which the rotating element connected to the input element Ei of the output differential gear mechanism 5 is a sun gear or a carrier, while suppressing the radial dimension R of the planetary gear mechanism 4 to be small, it is easy to arrange the planetary gear mechanism 4 closer to the output differential gear mechanism 5 in the axial direction L. Also, according to this configuration, the third rotating element E3 connected to the case 9 is a ring gear. Thereby, it is easy to form a configuration in which a support member or the like extending in the radial direction R, which is required when a sun gear or a carrier is connected to the case 9, can be omitted. Therefore, it is easy to suppress the axial dimension L of the vehicle drive device 100 to be small. Further, according to this configuration, the first sun gear SG1 as the first rotating element E1 of the planetary gear mechanism 4 is supported in the radial direction R with respect to the case 9 via the first bearing B1 as the first support bearing. The second ring gear RG2 as the fourth rotating element E4 of the planetary gear mechanism 4 and the input element Ei of the output differential gear mechanism 5 are connected in a state where relative movement in the radial direction R is restricted. Thereby, the input element Ei of the output differential gear mechanism 5 can be supported in the radial direction R by utilizing the centering action (automatic centering action) of the planetary gear mechanism 4. As a result, while omitting members such as bearings that support the input element Ei of the output differential gear mechanism 5 in the radial direction R with respect to the case 9, the output differential gear mechanism 5 can be appropriately supported. Therefore, it is easy to reduce the size and cost of the vehicle drive device 100. As described above, according to this configuration, in a configuration including the planetary gear mechanism 4 for deceleration and the output differential gear mechanism 5, it is possible to ensure a large reduction ratio of the planetary gear mechanism 4 and appropriately support the output differential gear mechanism 5, while facilitating miniaturization of the vehicle drive device 100.

[0035] As described above, in this embodiment, the case 9 includes a partition wall portion 94 as a first support wall portion disposed between the axial direction L of the rotary electric machine 1 and the planetary gear mechanism 4. The first bearing B1 as the first support bearing is supported by the partition wall portion 94 and is configured to support the first sun gear SG1 in the radial direction R and support the rotor 12 in the radial direction R.

[0036] According to this configuration, compared with a configuration in which both a bearing for supporting the first sun gear SG1 in the radial direction R and a bearing for supporting the rotor 12 in the radial direction R are provided, it is easy to keep the dimension in the axial direction L of the vehicle drive device 100 small.

[0037] As described above, in this embodiment, the output differential gear mechanism 5 includes a fifth rotating element E5, a sixth rotating element E6, and a seventh rotating element E7, and is a planetary gear mechanism configured such that the order of the rotational speeds of the fifth rotating element E5, the sixth rotating element E6, and the seventh rotating element E7 is the same as the described order. The fifth rotating element E5 is connected to the first output member 2, The seventh rotating element E7 is connected to the second output member 3, The sixth rotating element E6 is the third ring gear RG3 and is the input element Ei.

[0038] According to this configuration, the fifth rotating element E5 and the seventh rotating element E7 of the differential gear mechanism 5 for output are connected to the first output member 2 and the second output member 3, respectively. Thereby, the differential gear mechanism 5 for output can be a planetary gear type differential gear mechanism. Therefore, compared with the configuration in which the differential gear mechanism 5 for output is a bevel gear type differential gear mechanism, it is easy to keep the dimension in the axial direction L of the vehicle drive device 100 small. Also, according to this configuration, the third rotating element E3 and the fourth rotating element E4 of the planetary gear mechanism 4 are the first ring gear RG1 and the second ring gear RG2, respectively, and the sixth rotating element E6 of the differential gear mechanism 5 for output is the third ring gear RG3. And the first ring gear RG1 or the second ring gear RG2 is connected so as to rotate integrally with the third ring gear RG3. Thereby, the connection between the fourth rotating element E4 and the sixth rotating element E6 can be performed in the region of the radially outer side R2 with respect to the planetary gear mechanism 4 and the differential gear mechanism 5 for output. Therefore, since it is not necessary to connect those rotating elements to each other using, for example, a connecting member extending in the radial direction R, it is easy to keep the dimension in the axial direction L of the vehicle drive device 100 small.

[0039] Also, in the present embodiment, the differential gear mechanism 5 for output is a planetary gear mechanism including a second sun gear SG2, a second carrier CR2, and a third ring gear RG3, The second sun gear SG2 is connected so as to rotate integrally with the first output member 2, The second carrier CR2 is connected so as to rotate integrally with the second output member 3, The third ring gear RG3 is the input element Ei.

[0040] According to this configuration, by utilizing the centering action (automatic centering action) of the output differential gear mechanism 5 which is a planetary gear mechanism, the second output member 3 connected to the second carrier CR2 can be supported in the radial direction R. As a result, while omitting members such as bearings that support the second output member 3 in the radial direction R with respect to the case 9, the second output member 3 can be appropriately supported. Therefore, it is easy to reduce the size and cost of the vehicle drive device 100.

[0041] In the present embodiment, the output differential gear mechanism 5 is a double pinion type planetary gear mechanism. In the present embodiment, the fifth rotating element E5 of the output differential gear mechanism 5 is the second sun gear SG2. And the seventh rotating element E7 of the output differential gear mechanism 5 is the second carrier CR2. As described above, in the present embodiment, the sixth rotating element E6 of the output differential gear mechanism 5 is the third ring gear RG3. The second carrier CR2 rotatably supports the third pinion gear PG3 and the fourth pinion gear PG4 that mesh with each other. The third pinion gear PG3 meshes with the second sun gear SG2 and the fourth pinion gear PG4. The fourth pinion gear PG4 meshes with the third ring gear RG3 and the third pinion gear PG3.

[0042] Thus, in the present embodiment, the output differential gear mechanism 5 is a double pinion type planetary gear mechanism, the fifth rotating element E5 is the second sun gear SG2, and the seventh rotating element E7 is the second carrier CR2.

[0043] According to this configuration, compared with a configuration in which the output differential gear mechanism 5 is a single pinion type planetary gear mechanism, it is easy to configure such that the torque transmitted from the planetary gear mechanism 4 to the sixth rotating element E6 can be transmitted to the fifth rotating element E5 connected to the first output member 2 and the seventh rotating element E7 connected to the second output member 3 at an equal ratio.

[0044] As shown in FIG. 1, in the present embodiment, the vehicle drive device 100 further includes a parking gear 6 and a parking lock mechanism 7 that selectively engages with the parking gear 6.

[0045] The parking gear 6 is provided on a rotating member that is interlocked with the first wheel W1 and the second wheel W2 (see FIG. 2). In the present embodiment, the parking gear 6 is formed on the cylindrical member 10. The cylindrical member 10 is formed in a cylindrical shape having an axis along the axial direction L. In addition to the parking gear 6, a second ring gear RG2 and a third ring gear RG3 are also formed on the cylindrical member 10. Therefore, in the present embodiment, the parking gear 6 is arranged so as to overlap with the output differential gear mechanism 5 in a radial direction view along the radial direction R. And the parking gear 6 is connected so as to rotate integrally with the third ring gear RG3 as an input element Ei of the output differential gear mechanism 5. In the example shown in FIG. 1, the parking gear 6, the third ring gear RG3, and the second ring gear RG2 are arranged in the described order from the first axial side L1 to the second axial side L2. In this example, the parking gear 6, the third ring gear RG3, and the second ring gear RG2 are integrally formed with each other by cutting or the like with respect to one cylindrical member 10.

[0046] Also, as described above, in the present embodiment, the first ring gear RG1 is connected to the case 9. In the example shown in FIG. 1, the first ring gear RG1 is connected to the peripheral wall portion 91 of the case 9. More specifically, the first ring gear RG1 is connected to the case 9 so as not to rotate by the engagement of the spline engagement portion formed on the outer peripheral surface of the first ring gear RG1 and the spline engagement portion formed on the inner peripheral surface of the peripheral wall portion 91.

[0047] Thus, in the present embodiment, the vehicle drive device 100 further includes a parking gear 6 and a parking lock mechanism 7 that selectively engages with the parking gear 6. The first ring gear RG1 is connected to the case 9. The second ring gear RG2, the third ring gear RG3, and the parking gear 6 are formed on the same cylindrical member 10.

[0048] According to this configuration, the second ring gear RG2, the third ring gear RG3, and the parking gear 6 are integrally formed. Thereby, compared with a configuration in which the second ring gear RG2, the third ring gear RG3, and the parking gear 6 are formed as separate members from each other, it is easy to reduce the size of the vehicle drive device 100 in the axial direction L and the radial direction R.

[0049] Further, in the present embodiment, the parking gear 6 is arranged so as to overlap with the output differential gear mechanism 5 in a radial view along the radial direction R, and is connected so as to rotate integrally with the input element Ei.

[0050] According to this configuration, compared with a configuration in which the parking gear 6 is arranged on one side in the axial direction L with respect to the output differential gear mechanism 5, the dimension of the vehicle drive device 100 in the axial direction L can be kept small.

[0051] In the present embodiment, the cylindrical member 10 is connected so as to rotate integrally with the support member 20 extending along the radial direction R. The support member 20 is formed so as to extend from the cylindrical member 10 toward the radially inner side R1. In the present embodiment, the support member 20 is arranged on the first axial side L1 with respect to the output differential gear mechanism 5. And the support member 20 is rotatably supported with respect to the first side wall portion 92 of the case 9 via the third bearing B3.

[0052] In the present embodiment, the first output member 2 is connected so as to rotate integrally with the second sun gear SG2. In the example shown in FIG. 1, the first output member 2 is formed integrally with the second sun gear SG2. Further, in the present embodiment, the first output member 2 is disposed so as to penetrate the support member 20 and the first side wall portion 92 of the case 9 in the axial direction L. Then, the first output member 2 is connected so as to rotate integrally with the first drive shaft DS1 drivingly connected to the first wheel W1. In the example shown in FIG. 1, the first output member 2 is formed in a cylindrical shape having an axis along the axial direction L. Then, the first drive shaft DS1 is inserted into the first output member 2 from the first axial side L1 in a state where the first drive shaft DS1 is positioned radially inward R1 with respect to the first output member 2, and they are connected to each other by spline engagement.

[0053] In the present embodiment, the second output member 3 includes a connecting member 31 connected so as to rotate integrally with the second drive shaft DS2 drivingly connected to the second wheel W2, and an output shaft 32 extending along the axial direction L so as to connect the connecting member 31 and the seventh rotating element E7.

[0054] In the present embodiment, the connecting member 31 is disposed so as to penetrate the second side wall portion 93 and the cover portion 95 of the case 9 in the axial direction L. Then, the connecting member 31 is rotatably supported with respect to the second side wall portion 93 via the fourth bearing B4 and is rotatably supported with respect to the cover portion 95 via the fifth bearing B5. In the example shown in FIG. 1, the second output member 3 is formed in a cylindrical shape having an axis along the axial direction L. Then, the second drive shaft DS2 is inserted into the second output member 3 from the second axial side L2 in a state where the second drive shaft DS2 is positioned radially inward R1 with respect to the second output member 3, and they are connected to each other by spline engagement.

[0055] In this embodiment, the output shaft 32 penetrates the planetary gear mechanism 4 in the axial direction L at the radially inner side R1 with respect to the planetary gear mechanism 4, and penetrates the rotor core 12a in the axial direction L at the radially inner side R1 with respect to the rotor shaft 12b. And the output shaft 32 is connected so as to rotate integrally with the second carrier CR2 and the connecting member 31. In the example shown in FIG. 1, the output shaft 32 is integrally formed with the second carrier CR2. Further, the output shaft 32 is inserted into the connecting member 31 from the first side L1 in the axial direction so that the output shaft 32 is positioned on the radially inner side R1 with respect to the connecting member 31, and they are connected to each other by spline engagement.

[0056] In this embodiment, a first oil passage 81 is formed inside the output shaft 32. The first oil passage 81 includes an axial oil passage 81a, a first radial oil passage 81b, a second radial oil passage 81c, and a third radial oil passage 81d.

[0057] The axial oil passage 81a is formed so as to extend along the axial direction L inside the output shaft 32. The first radial oil passage 81b, the second radial oil passage 81c, and the third radial oil passage 81d are formed so as to extend along the radial direction R so as to communicate the axial oil passage 81a with the outer peripheral surface of the output shaft 32.

[0058] The first radial oil passage 81b is arranged so as to overlap with the second output member 3 in a radial view along the radial direction R. In this embodiment, a plurality of first radial oil passages 81b are arranged at intervals in the circumferential direction C.

[0059] The second radial oil passage 81c is arranged so as not to overlap with the second output member 3 and to overlap with the rotor shaft 12b in a radial view along the radial direction R. In this embodiment, a plurality of second radial oil passages 81c are arranged at intervals in the axial direction L and the circumferential direction C.

[0060] The third radial oil passage 81d is arranged so as to overlap with the revolution locus of the second pinion gear PG2 of the planetary gear mechanism 4 in a radial view along the radial direction R. In the present embodiment, a plurality of third radial oil passages 81d are arranged at intervals in the axial direction L and the circumferential direction C.

[0061] In the present embodiment, a second oil passage 82 is formed in the second side wall portion 93 of the case 9. The second oil passage 82 is formed so as to extend along the radial direction R. In the example shown in FIG. 1, the second oil passage 82 is formed so as to pass between the second bearing B2 and the fourth bearing B4 in the axial direction L.

[0062] In the present embodiment, the second side wall portion 93 includes a thick wall portion 93a having a relatively large thickness (dimension in the axial direction L) and a thin wall portion 93b having a relatively small thickness. A part of the region in the circumferential direction C of the second side wall portion 93 is the thin wall portion 93b, and the remaining region is the thick wall portion 93a. And the second oil passage 82 is formed in the thick wall portion 93a.

[0063] In the present embodiment, a third oil passage 83 is formed in the connecting member 31. The third oil passage 83 is formed across the inner peripheral surface and the outer peripheral surface of the connecting member 31 so as to communicate the first radial oil passage 81b and the second oil passage 82.

[0064] In the present embodiment, the oil discharged from a hydraulic pump (not shown) provided in the vehicle drive device 100 is supplied to the second oil passage 82. Then, the oil supplied to the second oil passage 82 is supplied to the axial oil passage 81a through the third oil passage 83 and the first radial oil passage 81b. The oil supplied to the axial oil passage 81a is supplied to the inner peripheral surface of the rotor shaft 12b through the second radial oil passage 81c. Also, the oil supplied to the axial oil passage 81a is supplied to the second pinion gear PG2 etc. of the planetary gear mechanism 4 through the third radial oil passage 81d. Further, the oil supplied to the axial oil passage 81a is supplied to the third pinion gear PG3 and the fourth pinion gear PG4 etc. through the fourth oil passage 84 formed in the second carrier CR2 of the output differential gear mechanism 5.

[0065] In this embodiment, the second oil passage 82 is disposed on the side opposite to the side of the planetary gear mechanism 4 and the output differential gear mechanism 5 in the axial direction L with respect to the stator 11 of the rotating electric machine 1. That is, the planetary gear mechanism 4 and the output differential gear mechanism 5 are disposed on the first axial side L1 with respect to the stator 11. And the second oil passage 82 is disposed on the second axial side L2 with respect to the stator 11. In the example shown in FIG. 1, the second oil passage 82 is disposed on the second axial side L2 axially with respect to the second coil end portion 11d of the stator 11.

[0066] As shown in FIG. 1, in this embodiment, the rotating electric machine 1 further includes a terminal portion 14 for connecting the coil 11b of the stator 11 to a power source (not shown). The terminal portion 14 is disposed so as to project from the stator 11 toward the second axial side L2. In this embodiment, the terminal portion 14 is formed such that a part of the circumferential direction C at the second coil end portion 11d projects toward the second axial side L2. For example, when the rotating electric machine 1 is driven by three-phase alternating current, the terminal portion 14 includes three-phase terminals that are electrically connected to the three-phase output terminals of the inverter.

[0067] In this embodiment, the arrangement region of the terminal portion 14 in the circumferential direction C does not overlap with the arrangement region of the second oil passage 82 in the circumferential direction C. And the arrangement region of the terminal portion 14 in the axial direction L overlaps with the arrangement region of the second oil passage 82 in the axial direction L. In this example, the terminal portion 14 is disposed so as not to overlap with the thick wall portion 93a of the second side wall portion 93 and to overlap with the thin wall portion 93b of the second side wall portion 93 in an axial view along the axial direction L. And the terminal portion 14 is disposed so as to overlap with the thick wall portion 93a in which the second oil passage 82 is formed in a radial view along the radial direction R.

[0068] Thus, in this embodiment, the rotating electric machine 1 includes the stator 11 having the coil 11b and the terminal portion 14 for connecting the coil 11b to a power source. The planetary gear mechanism 4 and the output differential gear mechanism 5 are disposed on the first axial side L1 with respect to the stator 11. The terminal portion 14 is disposed so as to project from the stator 11 toward the second axial side L2. A second oil passage 82 extending along the radial direction R is disposed on the second axial side L2 with respect to the stator 11. The arrangement region of the second oil passage 82 in the circumferential direction C does not overlap with the arrangement region of the terminal portion 14 in the circumferential direction C. The arrangement region of the second oil passage 82 in the axial direction L overlaps with the arrangement region of the terminal portion 14 in the axial direction L.

[0069] According to this configuration, compared with the configuration in which the second oil passage 82 and the terminal portion 14 are arranged so as to be displaced from each other in the axial direction L, the dimension of the vehicle drive device 100 in the axial direction L can be suppressed to be small.

[0070] FIG. 3 shows a speed diagram of the planetary gear mechanism 4 and the output differential gear mechanism 5 according to the present embodiment. In the speed diagram of FIG. 3, the vertical lines correspond to the rotational speeds of the respective rotating elements of the planetary gear mechanism 4 and the output differential gear mechanism 5. And each of the plurality of parallel vertical lines corresponds to each rotating element of the planetary gear mechanism 4 and the output differential gear mechanism 5. Further, in the speed diagram of FIG. 3, the reference numerals shown above the plurality of vertical lines are the reference numerals of the corresponding rotating elements. And the reference numerals shown below the plurality of vertical lines are the reference numerals of the elements that rotate integrally with the rotating elements corresponding to the reference numerals shown above. Further, in the speed diagram of FIG. 3, the black circles on the plurality of vertical lines indicate that the rotating elements corresponding to the target vertical line rotate integrally with each other. Further, in the speed diagram of FIG. 3, the crosses on the vertical lines indicate that the rotating elements corresponding to the target vertical line are fixed to the case 9 as the non-rotating member NR.

[0071] As shown in FIG. 3, in the present embodiment, the rotation transmitted from the rotor 12 of the rotating electrical machine 1 to the first sun gear SG1 is reversed and decelerated in the planetary gear mechanism 4 and is transmitted to the second ring gear RG2. As a result, the torque of the rotating electrical machine 1 is amplified and transmitted to the second ring gear RG2. Then, the rotation and torque transmitted from the second ring gear RG2 to the third ring gear RG3 are distributed by the output differential gear mechanism 5 to the first output member 2 connected to the second sun gear SG2 and the second output member 3 connected to the second carrier CR2.

[0072] 2. Second Embodiment Hereinafter, the vehicle drive device 100 according to the second embodiment will be described with reference to FIGS. 4 to 6. In this embodiment, the configuration of the case 9 and the configuration of the output differential gear mechanism 5 are different from those of the first embodiment. Hereinafter, the description will focus on the differences from the first embodiment. For points not particularly described, the same applies as in the first embodiment.

[0073] As shown in FIG. 4, in this embodiment, the case 9 does not include a cover portion 95. Therefore, in this embodiment, the fifth bearing B5 for supporting the second output member 3 with respect to the cover portion 95 is not provided.

[0074] As shown in FIG. 6, in this embodiment, the output differential gear mechanism 5 includes a differential case 51, a shaft member 52, a pinion gear 53, and a pair of side gears 54.

[0075] The differential case 51 is formed to accommodate the pinion gear 53 and the pair of side gears 54. In this embodiment, the differential case 51 is connected so as to rotate integrally with the fourth rotating element E4 of the planetary gear mechanism 4. That is, in this embodiment, the differential case 51 is the input element Ei.

[0076] The shaft member 52 is arranged to extend along the radial direction R. And the shaft member 52 is supported by the differential case 51 so as to rotate integrally with the differential case 51. In this embodiment, a plurality of shaft members 52 are arranged in a dispersed manner in the circumferential direction C along the radial direction R (for example, in a configuration where four shaft members 52 are arranged in a cross shape in an axial view along the axial direction L).

[0077] The pinion gear 53 is rotatably supported by the shaft member 52. The pinion gear 53 is configured to be rotatable (self-rotatable) about the shaft member 52 and rotatable (revolvable) about the rotation axis of the differential case 51 (see the dashed-dotted line in FIG. 6). In the present embodiment, a pinion gear 53 is attached to each of a plurality of shaft members 52 that are dispersedly arranged in the circumferential direction C. Note that the pinion gear 53 corresponds to a "first bevel gear".

[0078] A pair of side gears 54 are arranged on both sides of the shaft member 52 in the axial direction L. And the pair of side gears 54 are meshed with the pinion gear 53. Note that the side gear 54 corresponds to a "second bevel gear". In the following description, among the pair of side gears 54, the side gear 54 on the first side L1 in the axial direction is referred to as the "first side gear 541", and the side gear 54 on the second side L2 in the axial direction is referred to as the "second side gear 542".

[0079] In the present embodiment, the first side gear 541 is connected so as to rotate integrally with the first drive shaft DS1 that is drivingly connected to the first wheel W1 via the first output member 2. In the present embodiment, the first output member 2 is arranged so as to extend from the first side gear 541 to the first side L1 in the axial direction. And the first output member 2 is supported by the differential case 51 so as to be relatively rotatable via the eighth bearing B8. In the example shown in FIG. 6, the first side gear 541 and the first output member 2 are integrally formed. And the first output member 2 is supported by the first member 511 of the differential case 51 so as to be relatively rotatable via the eighth bearing B8. Here, the eighth bearing B8 is a sliding bearing. Also, in the example shown in FIG. 6, the first output member 2 is formed in a cylindrical shape having an axis along the axial direction L. And the first drive shaft DS1 is inserted into the first output member 2 from the first side L1 in the radial direction inner side R1, and they are connected to each other by spline engagement.

[0080] As shown in FIGS. 4 to 6, in the present embodiment, the second side gear 542 is connected so as to rotate integrally with a second drive shaft DS2 that is drivingly connected to the second wheel W2 via the output shaft 32 and the connecting member 31. In the example shown in FIG. 6, the output shaft 32 is inserted into the second side gear 542 from the second side L2 in the axial direction inside the radial direction R, and they are connected to each other by spline engagement. Further, in the example shown in FIG. 4, the connecting member 31 and the output shaft 32 are integrally formed.

[0081] As described above, in the present embodiment, the differential gear mechanism 5 for output includes a differential case 51, a shaft member 52 supported by the differential case 51 and arranged to extend along the radial direction R, a pinion gear 53 accommodated in the differential case 51 and rotatably supported by the shaft member 52, and a pair of side gears 54 accommodated in the differential case 51 and meshing with the pinion gear 53 on both sides of the shaft member 52 in the axial direction L. The differential case 51 is the input element Ei.

[0082] According to this configuration, the differential gear mechanism 5 for output can be a bevel gear type differential gear mechanism. And since the differential case 51 that houses the pinion gear 53 and the side gears 54 is the input element Ei connected to the fourth rotating element E4, it is easy to ensure a high degree of freedom in the connection structure between the planetary gear mechanism 4 and the differential gear mechanism 5 for output.

[0083] As shown in FIG. 6, in the present embodiment, the differential case 51 includes a first member 511 and a second member 512. The first member 511 and the second member 512 are configured to be joined to each other in the axial direction L. In the present embodiment, the first member 511 is arranged on the first side L1 in the axial direction with respect to the shaft member 52, and the second member 512 is arranged on the second side L2 in the axial direction with respect to the shaft member 52. And the first member 511 and the second member 512 support the shaft member 52 so as to sandwich it in the axial direction L.

[0084] As shown in FIG. 6, in the present embodiment, the cylindrical member 10 is not provided. Then, as shown in FIG. 4, the parking gear 6, the first member 511, and the second member 512 are fastened together in the axial direction L by bolts 50. In the example shown in FIG. 4, with the parking gear 6 abutting against the first member 511 from the first side L1 in the axial direction, the bolts 50 are fastened to the parking gear 6, the first member 511, and the second member 512 from the first side L1 in the axial direction in a region where the shaft member 52 does not exist in the circumferential direction C of the differential case 51.

[0085] Thus, in the present embodiment, the vehicle drive device 100 further includes a parking gear 6 and a parking lock mechanism 7 that selectively engages with the parking gear 6. The differential case 51 includes a first member 511 and a second member 512 that are joined to each other in the axial direction L. The parking gear 6, the first member 511, and the second member 512 are fastened together in the axial direction L by bolts 50.

[0086] According to this configuration, the differential case 51 includes the first member 511 and the second member 512 that are joined to each other in the axial direction L. Thereby, the work of assembling the shaft member 52, the pinion gear 53, and the side gear 54 to the differential case 51 can be easily performed. Further, according to this configuration, the parking gear 6, the first member 511, and the second member 512 are fastened together in the axial direction L by bolts 50. Thereby, compared with a configuration in which the connection of the parking gear 6 to the differential case 51 and the connection between the first member 511 and the second member 512 are performed using separate connecting members, the number of parts of the vehicle drive device 100 can be reduced.

[0087] As shown in FIG. 6, in the present embodiment, the differential case 51 as the input element Ei of the output differential gear mechanism 5 is rotatably supported with respect to the first side wall portion 92 of the case 9 via the third bearing B3. In the present embodiment, the third bearing B3 includes a radial bearing B31 and a thrust bearing B32. Note that the first side wall portion 92 corresponds to a “second support wall portion” disposed on the first side L1 in the axial direction with respect to the output differential gear mechanism 5.

[0088] In the present embodiment, the radial bearing B31 is disposed between the first member 511 and the first side wall portion 92 in the radial direction R. And the radial bearing B31 supports the first member 511 in the radial direction R. Further, the radial bearing B31 is disposed on the first side L1 in the axial direction with respect to a plurality of gears (here, a plurality of pinion gears 53 and a pair of side gears 54) constituting the output differential gear mechanism 5. In the present embodiment, the radial bearing B31 is a sliding bearing or a needle roller bearing. In the example shown in FIG. 6, the radial bearing B31 is a sliding bearing. Thus, the radial bearing B31 corresponds to a “second support bearing” that is disposed on the first side L1 in the axial direction with respect to a plurality of gears constituting the output differential gear mechanism 5 and rotatably supports the input element Ei.

[0089] In the present embodiment, the thrust bearing B32 is disposed between the first member 511 and the first side wall portion 92 in the axial direction L. And the thrust bearing B32 supports the first member 511 in the axial direction L. Further, the thrust bearing B32 is disposed on the first side L1 in the axial direction with respect to a plurality of gears (here, a plurality of pinion gears 53 and a pair of side gears 54) constituting the output differential gear mechanism 5. In the example shown in FIG. 6, the thrust bearing B32 is disposed on the second side L2 in the axial direction and on the outer side R2 in the radial direction with respect to the radial bearing B31. Also, in the example shown in FIG. 6, the thrust bearing B32 is a needle roller bearing.

[0090] Also, in the present embodiment, the differential case 51 is rotatably supported with respect to the partition wall portion 94 of the case 9 via the sixth bearing B6 and the seventh bearing B7.

[0091] The sixth bearing B6 is disposed between the second member 512 and the portion of the first carrier CR1 located on the first axial side L1 in the axial direction L with respect to the second pinion gear PG2. The seventh bearing B7 is disposed between the portion of the first carrier CR1 located on the second axial side L2 in the axial direction L with respect to the first pinion gear PG1 and the partition portion 94. Thus, the second member 512 is supported in the axial direction L with respect to the partition portion 94 via the sixth bearing B6 and the seventh bearing B7. In the example shown in FIG. 6, each of the sixth bearing B6 and the seventh bearing B7 is a needle roller bearing.

[0092] Thus, in the present embodiment, the differential case 51 is supported in the radial direction R by the radial bearing B31 and is supported in the axial direction L by the thrust bearing B32, the sixth bearing B6, and the seventh bearing B7. That is, in the present embodiment, the bearing that supports the output differential gear mechanism 5 in the radial direction R is only the radial bearing B31.

[0093] As described above, in the present embodiment, the planetary gear mechanism 4 is disposed on the first axial side L1 in the axial direction with respect to the rotor 12. The output differential gear mechanism 5 is disposed on the first axial side L1 in the axial direction with respect to the planetary gear mechanism 4. The input element Ei of the output differential gear mechanism 5 is supported in the radial direction R with respect to the case 9 via the radial bearing B31 as the second support bearing disposed on the first axial side L1 in the axial direction with respect to the plurality of gears constituting the output differential gear mechanism 5.

[0094] According to this configuration, with respect to the plurality of gears constituting the output differential gear mechanism 5, on the first axial side L1, the input element Ei of the output differential gear mechanism 5 can be supported in the radial direction R by the radial bearing B31 as the second support bearing. Also, on the second axial side L2 with respect to the plurality of gears constituting the output differential gear mechanism 5, as described above, the input element Ei of the output differential gear mechanism 5 can be supported in the radial direction R by utilizing the centering action (self-centering action) of the planetary gear mechanism 4. As a result, it is possible to realize a configuration in which the input element Ei of the output differential gear mechanism 5 is supported in the radial direction R only by the radial bearing B31 disposed on the first axial side L1 in the axial direction with respect to the plurality of gears constituting the output differential gear mechanism 5. Therefore, compared with a configuration in which the input element Ei is supported in the radial direction R by a plurality of bearings disposed on both sides in the axial direction L with respect to the plurality of gears constituting the output differential gear mechanism 5, it is easier to reduce the size and cost of the vehicle drive device 100.

[0095] Also, in the present embodiment, the case 9 includes a first side wall portion 92 as a second support wall portion disposed on the first axial side L1 in the axial direction with respect to the output differential gear mechanism 5. The input element Ei is supported in the radial direction R by a sliding bearing or a needle roller bearing disposed between the input element Ei and the first side wall portion 92 in the radial direction R, and is supported in the axial direction L by a thrust bearing B32 disposed between the input element Ei and the first side wall portion 92 in the axial direction L.

[0096] According to this configuration, compared with a configuration in which the input element Ei is supported in both the radial direction R and the axial direction L by, for example, a ball bearing, it is possible to greatly secure the support rigidity of the input element Ei while suppressing the increase in size of the vehicle drive device 100.

[0097] As shown in FIG. 6, in the present embodiment, the differential case 51 as the input element Ei of the output differential gear mechanism 5 includes a connecting portion 513. In the present embodiment, the connecting portion 513 is formed so as to protrude radially outward R2 from the second member 512. And the connecting portion 513 is integrally formed with the second ring gear RG2. Here, in the present application, "integrally formed" includes that a plurality of elements are formed of the same member and that a plurality of elements are inseparably connected by welding or the like. Note that "connected so as to rotate integrally" includes that a plurality of elements are separably connected such as by spline engagement or the like.

[0098] In the present embodiment, the differential case 51 as the input element Ei of the output differential gear mechanism 5 has a fitting outer peripheral surface 51a facing the radially outer side R2. And the second ring gear RG2 has a fitting inner peripheral surface 4a facing the radially inner side R1. The fitting inner peripheral surface 4a and the fitting outer peripheral surface 51a are fitted to each other so as to be in contact with each other in the radial direction R. In the example shown in FIG. 6, the fitting outer peripheral surface 51a is formed on the outer peripheral surface of the connecting portion 513 of the differential case 51. And the fitting inner peripheral surface 4a is formed on the inner peripheral surface of the portion protruding in the first axial direction L1 from the portion where the tooth portion is formed in the second ring gear RG2.

[0099] In the present embodiment, with the fitting inner peripheral surface 4a and the fitting outer peripheral surface 51a fitted to each other, the second ring gear RG2 and the input element Ei are fixed to each other by welding. In the example shown in FIG. 6, with the connecting portion 513 of the differential case 51 fitted to the second ring gear RG2 from the first axial direction L1, the connecting portion 513 and the second ring gear RG2 are welded from the first axial direction L1.

[0100] Thus, in the present embodiment, the second ring gear RG2 includes a fitting inner peripheral surface 4a facing the radially inner side R1, the input element Ei includes a fitting outer peripheral surface 51a facing the radially outer side R2, and with the fitting inner peripheral surface 4a and the fitting outer peripheral surface 51a fitted to each other so as to be in contact with each other in the radial direction R, the second ring gear RG2 and the input element Ei are fixed to each other by welding.

[0101] According to this configuration, a configuration in which the second ring gear RG2 and the input element Ei are connected in a state where relative movement in the radial direction R is restricted can be easily realized.

[0102] Also, in the present embodiment, the first pinion gear PG1 and the second pinion gear PG2 are helical gears. And the direction of the thrust load received by the first pinion gear PG1 from the first sun gear SG1 and the direction of the thrust load received by the second pinion gear PG2 from the second ring gear RG2 are opposite to the direction of the thrust load received by the first pinion gear PG1 from the first ring gear RG1. In the present embodiment, the direction of the helix of the first pinion gear PG1 and the second pinion gear PG2 is set so that the sum of the magnitude of the thrust load received by the first pinion gear PG1 from the first sun gear SG1 and the magnitude of the thrust load received by the second pinion gear PG2 from the second ring gear RG2 is the same as or close to the magnitude of the thrust load received by the first pinion gear PG1 from the first ring gear RG1. In other words, the direction of the helix of the first pinion gear PG1 and the second pinion gear PG2 is set so that the resultant force of the thrust loads from the first sun gear SG1, the first ring gear RG1, and the second ring gear RG2 acting on the first pinion gear PG1 and the second pinion gear PG2 that rotate integrally with each other becomes zero or a value close to zero. Here, the "direction of the helix" of each pinion gear refers to the direction of the twist angle (twist direction) of the teeth of each pinion gear. In FIG. 6, the black arrow shown on the first pinion gear PG1 adjacent to the first sun gear SG1 represents the direction of the thrust load received by the first pinion gear PG1 from the first sun gear SG1. And the black arrow shown on the first pinion gear PG1 adjacent to the first ring gear RG1 represents the direction of the thrust load received by the first pinion gear PG1 from the first ring gear RG1. Also, the black arrow shown on the second pinion gear PG2 adjacent to the second ring gear RG2 represents the direction of the thrust load received by the second pinion gear PG2 from the second ring gear RG2.

[0103] According to this configuration, the thrust load received by the first pinion gear PG1 from the first sun gear SG1, the thrust load received by the second pinion gear PG2 from the second ring gear RG2, and the thrust load received by the first pinion gear PG1 from the first ring gear RG1 can cancel each other out. Thereby, it is possible to avoid an excessive thrust load acting on the bearings (here, the sixth bearing B6 and the seventh bearing B7) that support the first carrier CR1 that rotatably supports the first pinion gear PG1 and the second pinion gear PG2.

[0104] 3. Third Embodiment Hereinafter, the vehicle drive device 100 according to the third embodiment will be described with reference to FIG. 7. In the present embodiment, the support structure of the differential case 51 of the output differential gear mechanism 5 is different from that of the second embodiment described above. Hereinafter, the description will focus on the differences from the second embodiment. Note that, regarding points not particularly described, the same applies as in the second embodiment.

[0105] As shown in FIG. 7, in the present embodiment, the eighth bearing B8 is not provided. That is, in the present embodiment, the differential case 51 is not supported with respect to the first output member 2, but is supported with respect to the first side wall portion 92 of the case 9 via the radial bearing B31. In the example shown in FIG. 7, the radial bearing B31 is a needle roller bearing. And a gap is formed between the first member 511 of the differential case 51 and the first output member 2 in the radial direction R.

[0106] In the present embodiment, the differential case 51 includes a differential case target portion 514. The differential case target portion 514 corresponds to "the portion on the second axial side L2 with respect to the central position in the axial direction L of the output differential gear mechanism 5 in the differential case 51". Here, in the present embodiment, "the central position in the axial direction L of the output differential gear mechanism 5" is the position of the axis of the shaft member 52 in the axial direction L. In the present embodiment, the differential case target portion 514 is formed to protrude from the second member 512 of the differential case 51 toward the second axial side L2. Further, the differential case target portion 514 is supported so as to be relatively rotatable with respect to the second output member 3 via the ninth bearing B9.

[0107] In this embodiment, the second output member 3 is arranged so as to penetrate the radially inner side R1 in the axial direction L with respect to the differential case target portion 514. And, a ninth bearing B9 is arranged between the inner peripheral surface of the differential case target portion 514 and the outer peripheral surface of the second output member 3. In the example shown in FIG. 7, the output shaft 32 of the second output member 3 is arranged so as to penetrate the radially inner side R1 in the axial direction L with respect to the differential case target portion 514. And, a ninth bearing B9 is arranged between the inner peripheral surface of the differential case target portion 514 and the outer peripheral surface of the output shaft 32. The ninth bearing B9 corresponds to the "third support bearing". Note that in a configuration in which the differential case 51 includes the differential case target portion 514, the ninth bearing B9 may not be provided.

[0108] Thus, in this embodiment, the first output member 2 is arranged on the first side L1 in the axial direction with respect to the second output member 3. Regarding a portion on the second side L2 in the axial direction with respect to the central position in the axial direction L of the output differential gear mechanism 5 in the differential case 51 as the differential case target portion 514, the second output member 3 is arranged so as to penetrate the radially inner side R1 in the axial direction L with respect to the differential case target portion 514. A ninth bearing B9 as a third support bearing is arranged between the inner peripheral surface of the differential case target portion 514 and the outer peripheral surface of the second output member 3.

[0109] According to this configuration, the differential case target portion 514, which is a portion on the second side L2 in the axial direction with respect to the central position in the axial direction L of the output differential gear mechanism 5 in the differential case 51, is supported by the ninth bearing B9. Thereby, the support accuracy of the differential case 51 can be improved.

[0110] 4. Other Embodiments (1) In the above embodiment, a configuration in which the parking gear 6 is arranged so as to overlap the output differential gear mechanism 5 in a radial view along the radial direction R has been described as an example. However, without being limited to such a configuration, the parking gear 6 may be arranged on one side in the axial direction L with respect to the output differential gear mechanism 5.

[0111] (2) In the above-described first embodiment, the configuration in which the second ring gear RG2, the third ring gear RG3, and the parking gear 6 are formed on the same cylindrical member 10 has been described as an example. However, the present invention is not limited to such a configuration, and these may be configured by being divided into a plurality of members. For example, the second ring gear RG2, the third ring gear RG3, and the parking gear 6 may be formed on separate members and connected so as to rotate integrally with each other.

[0112] (3) In the above-described first embodiment, the arrangement region of the second oil passage 82 in the circumferential direction C and the arrangement region of the terminal portion 14 in the circumferential direction C do not overlap, and the arrangement region of the second oil passage 82 in the axial direction L and the arrangement region of the terminal portion 14 in the axial direction L overlap. However, the present invention is not limited to such a configuration, and the second oil passage 82 and the terminal portion 14 may be arranged so as to be displaced from each other in the axial direction L.

[0113] (4) In the above-described second embodiment, the differential case 51 is supported so as to be relatively rotatable with respect to the first output member 2 via the eighth bearing B8 and is rotatably supported with respect to the case 9 via the radial bearing B31. However, the present invention is not limited to such a configuration. For example, the first output member 2 may be rotatably supported with respect to the case 9 via the radial bearing B31, and the differential case 51 may be supported so as to be relatively rotatable with respect to the first output member 2 via the eighth bearing B8. That is, a configuration in which the differential case 51 is indirectly supported by the case 9 via the first output member 2 may be employed.

[0114] (5) In the above-described second and third embodiments, the differential case 51 of the output differential gear mechanism 5 includes a first member 511 and a second member 512 that are joined to each other in the axial direction L, and the parking gear 6, the first member 511, and the second member 512 are described as an example of a configuration in which they are clamped together in the axial direction L by bolts 50. However, the present invention is not limited to such a configuration. For example, the connection of the parking gear 6 to the differential case 51 and the connection of the first member 511 and the second member 512 may be performed using another connecting member. Further, the differential case 51 may not include the first member 511 and the second member 512 and may be constituted by a single member.

[0115] (6) In the above-described second and third embodiments, the input element Ei is supported in the radial direction R by a radial bearing B31, which is a sliding bearing disposed between the input element Ei and the first side wall portion 92 in the radial direction R, and is supported in the axial direction L by a thrust bearing B32 disposed between the input element Ei and the first side wall portion 92 in the axial direction L, and this configuration is described as an example. However, the present invention is not limited to such a configuration. For example, the input element Ei may be supported in both the radial direction R and the axial direction L by a ball bearing.

[0116] (7) In addition, the configurations disclosed in the above-described respective 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 appropriately made without departing from the spirit of the present disclosure.

[0117] 5. Summary of the above embodiments Hereinafter, an overview of the vehicle drive device (100) described above will be described.

[0118] The vehicle drive device (100) includes a rotary electric machine (1) including a rotor (12), a first output member (2) drivingly connected to a first wheel (W1), a second output member (3) drivingly connected to a second wheel (W2), A planetary gear mechanism (4) that decelerates the rotation of the rotor (12); An output differential gear mechanism (5) that includes an input element (Ei) and distributes the rotation transmitted from the planetary gear mechanism (4) to the input element (Ei) to the first output member (2) and the second output member (3); A vehicle drive device (100) including a case (9) that houses the rotary electric machine (1), the planetary gear mechanism (4), and the output differential gear mechanism (5), wherein the rotary electric machine (1), the first output member (2), the second output member (3), the planetary gear mechanism (4), and the output differential gear mechanism (5) are arranged coaxially; the planetary gear mechanism (4) includes a first rotating element (E1), a second rotating element (E2), a third rotating element (E3), and a fourth rotating element (E4), and is configured such that the order of the rotational speeds of the first rotating element (E1), the second rotating element (E2), the third rotating element (E3), and the fourth rotating element (E4) is the same as the described order; the first rotating element (E1) is a first sun gear (SG1) connected so as to rotate integrally with the rotor (12); the third rotating element (E3) is a first ring gear (RG1) connected to the case (9); the fourth rotating element (E4) is a second ring gear (RG2) connected so as to rotate integrally with the input element (Ei); the second rotating element (E2) is a first carrier (CR1) that rotatably supports a first pinion gear (PG1) and a second pinion gear (PG2) that rotate integrally with each other; the first pinion gear (PG1) meshes with the first sun gear (SG1) and the first ring gear (RG1); the second pinion gear (PG2) has a smaller diameter than the first pinion gear (PG1) and meshes with the second ring gear (RG2); Taking the direction orthogonal to the rotation axis of the rotor (12) as the radial direction (R); the first sun gear (SG1) is supported in the radial direction (R) with respect to the case (9) via a first support bearing (B1); The second ring gear (RG2) and the input element (Ei) are connected in a state where relative movement in the radial direction (R) is restricted.

[0119] According to this configuration, the first rotating element (E1) of the planetary gear mechanism (4) is connected to the rotor (12). And the third rotating element (E3) of the planetary gear mechanism (4) is connected to the case (9), and the fourth rotating element (E4) of the planetary gear mechanism (4) is connected to the input element (Ei) of the output differential gear mechanism (5). Also, each of the third rotating element (E3) and the fourth rotating element (E4) of the planetary gear mechanism (4) is a ring gear. Thereby, it is easy to ensure a large reduction ratio (for example, 17 to 22) of the planetary gear mechanism (4) that functions as a speed reducer for reducing the rotation of the rotor (12) and transmitting it to the output differential gear mechanism (5). Also, according to this configuration, the fourth rotating element (E4) connected to the input element (Ei) of the output differential gear mechanism (5) is a ring gear. Thereby, compared with a configuration in which the rotating element connected to the input element (Ei) of the output differential gear mechanism (5) is a sun gear or a carrier, while suppressing the radial dimension (R) of the planetary gear mechanism (4) to be small, it is easy to arrange the planetary gear mechanism (4) closer to the output differential gear mechanism (5) in the axial direction (L). Also, according to this configuration, the third rotating element (E3) connected to the case (9) is a ring gear. Thereby, it is easy to form a configuration in which a support member or the like extending in the radial direction (R), which is required when a sun gear or a carrier is connected to the case (9), can be omitted. Therefore, it is easy to suppress the axial dimension (L) of the vehicle drive device (100) to be small. Also, according to this configuration, the first sun gear (SG1) as the first rotating element (E1) of the planetary gear mechanism (4) is supported in the radial direction (R) with respect to the case (9) via the first support bearing (B1). And the second ring gear (RG2) as the fourth rotating element (E4) of the planetary gear mechanism (4) and the input element (Ei) of the output differential gear mechanism (5) are connected in a state where relative movement in the radial direction (R) is restricted. Thereby, the input element (Ei) of the output differential gear mechanism (5) can be supported in the radial direction (R) by utilizing the centering action (automatic centering action) of the planetary gear mechanism (4). As a result, while omitting members such as bearings that support the input element (Ei) of the output differential gear mechanism (5) in the radial direction (R) with respect to the case (9), the output differential gear mechanism (5) can be appropriately supported. Therefore, it is easy to reduce the size and cost of the vehicle drive device (100). As described above, according to this configuration, in a configuration including the planetary gear mechanism (4) for deceleration and the output differential gear mechanism (5), it is possible to ensure a large reduction ratio of the planetary gear mechanism (4) and appropriately support the output differential gear mechanism (5), while making it easy to reduce the size of the vehicle drive device (100).

[0120] Here, taking the direction along the rotation axis center of the rotor (12) as the axial direction (L), one side of the axial direction (L) as the first axial side (L1), and the other side of the axial direction (L) as the second axial side (L2), the planetary gear mechanism (4) is arranged on the first axial side (L1) with respect to the rotor (12), the output differential gear mechanism (5) is arranged on the first axial side (L1) with respect to the planetary gear mechanism (4), it is preferable that the input element (Ei) is supported in the radial direction (R) with respect to the case (9) via a second support bearing (B31) arranged on the first axial side (L1) with respect to a plurality of gears constituting the output differential gear mechanism (5).

[0121] According to this configuration, on the first axial side (L1), with respect to the plurality of gears constituting the output differential gear mechanism (5), the input element (Ei) of the output differential gear mechanism (5) can be supported in the radial direction (R) by the second support bearing (B31). Also, on the second axial side (L2) with respect to the plurality of gears constituting the output differential gear mechanism (5), as described above, by utilizing the centering action (automatic centering action) of the planetary gear mechanism (4), the input element (Ei) of the output differential gear mechanism (5) can be supported in the radial direction (R). As a result, it is possible to realize a configuration in which the input element (Ei) of the output differential gear mechanism (5) is supported in the radial direction (R) only by the second support bearing (B31) disposed on the first axial side (L1) in the axial direction with respect to the plurality of gears constituting the output differential gear mechanism (5). Therefore, compared with a configuration in which the input element (Ei) is supported in the radial direction (R) by a plurality of bearings disposed on both sides in the axial direction (L) with respect to the plurality of gears constituting the output differential gear mechanism (5), it is easier to reduce the size and cost of the vehicle drive device (100).

[0122] In a configuration in which the input element (Ei) is supported in the radial direction (R) with respect to the case (9) via the second support bearing (B31), The output differential gear mechanism (5) includes a differential case (51), a shaft member (52) supported by the differential case (51) and arranged to extend along the radial direction (R), a first bevel gear (53) housed in the differential case (51) and rotatably supported by the shaft member (52), and a pair of second bevel gears (54) housed in the differential case (51) and meshing with the first bevel gear (53) on both sides in the axial direction (L) with respect to the shaft member (52). It is preferable that the differential case (51) is the input element (Ei).

[0123] According to this configuration, the output differential gear mechanism (5) can be a bevel gear type differential gear mechanism. And since the differential case (51) that houses the pinion gear (53) and the side gear (54) is the input element (Ei) connected to the fourth rotating element (E4), it is easy to ensure a high degree of freedom in the connection structure between the planetary gear mechanism (4) and the output differential gear mechanism (5).

[0124] In the configuration where the output differential gear mechanism (5) includes a differential case (51), the shaft member (52), the first bevel gear (53), and a pair of the second bevel gears (54), The first output member (2) is arranged on the first side (L1) in the axial direction with respect to the second output member (3), Taking the portion on the second side (L2) in the axial direction (L) of the output differential gear mechanism (5) in the differential case (51) as the differential case target portion (514), The second output member (3) is arranged so as to penetrate the inner side (R1) in the radial direction (R) with respect to the differential case target portion (514) in the axial direction (L), It is preferable that a third support bearing (B9) is arranged between the inner peripheral surface of the differential case target portion (514) and the outer peripheral surface of the second output member (3).

[0125] According to this configuration, the differential case target portion (514), which is the portion on the second side (L2) in the axial direction (L) of the output differential gear mechanism (5) in the differential case (51), is supported by the third support bearing (B9). Thereby, the support accuracy of the differential case (51) can be improved.

[0126] Also, the output differential gear mechanism (5) is a planetary gear mechanism including a second sun gear (SG2), a second carrier (CR2), and a third ring gear (RG3), The second sun gear (SG2) is connected so as to rotate integrally with the first output member (2), The second carrier (CR2) is connected so as to rotate integrally with the second output member (3), The third ring gear (RG3) is preferably the input element (Ei).

[0127] According to this configuration, by utilizing the centering action (automatic centering action) of the output differential gear mechanism (5) which is a planetary gear mechanism, the second output member (3) connected to the second carrier (CR2) can be supported in the radial direction (R). As a result, while omitting members such as bearings that support the second output member (3) in the radial direction (R) with respect to the case (9), the second output member (3) can be appropriately supported. Therefore, it is easy to reduce the size and cost of the vehicle drive device (100).

[0128] Also, taking the direction along the rotation axis center of the rotor (12) as the axial direction (L), the case (9) includes a first support wall portion (94) disposed between the rotating electrical machine (1) and the planetary gear mechanism (4) in the axial direction (L), the first support bearing (B1) is preferably supported by the first support wall portion (94) and is configured to support the first sun gear (SG1) in the radial direction (R) and the rotor (12) in the radial direction (R).

[0129] According to this configuration, compared with a configuration in which both a bearing for supporting the first sun gear (SG1) in the radial direction (R) and a bearing for supporting the rotor (12) in the radial direction (R) are provided, it is easy to keep the axial dimension (L) of the vehicle drive device (100) small.

[0130] Also, the second ring gear (RG2) includes a fitting inner peripheral surface (4a) facing the inner side (R1) in the radial direction (R), the input element (Ei) includes a fitting outer peripheral surface (51a) facing the outer side (R2) in the radial direction (R), the second ring gear (RG2) and the input element (Ei) are preferably fixed to each other by welding in a state where the fitting inner peripheral surface (4a) and the fitting outer peripheral surface (51a) are fitted to each other in contact with each other in the radial direction (R).

[0131] According to this configuration, a configuration in which the second ring gear (RG2) and the input element (Ei) are connected in a state where relative movement in the radial direction (R) is restricted can be easily realized.

[0132] Further, the first pinion gear (PG1) and the second pinion gear (PG2) are helical gears, it is preferable that the direction of the thrust load received by the first pinion gear (PG1) from the first sun gear (SG1) and the direction of the thrust load received by the second pinion gear (PG2) from the second ring gear (RG2) are opposite to the direction of the thrust load received by the first pinion gear (PG1) from the first ring gear (RG1).

[0133] According to this configuration, the thrust load received by the first pinion gear (PG1) from the first sun gear (SG1), the thrust load received by the second pinion gear (PG2) from the second ring gear (RG2), and the thrust load received by the first pinion gear (PG1) from the first ring gear (RG1) can cancel each other out. Thereby, it is possible to avoid an excessive thrust load acting on the bearing that supports the first carrier (CR1) that rotatably supports the first pinion gear (PG1) and the second pinion gear (PG2).

[0134] Also, taking the direction along the rotation axis of the rotor (12) as the axial direction (L), one side of the axial direction (L) as the first axial side (L1), and the other side of the axial direction (L) as the second axial side (L2), the case (9) includes a second support wall portion (92) disposed on the first axial side (L1) of the output differential gear mechanism (5) in the axial direction, it is preferable that the input element (Ei) is supported in the radial direction (R) by a sliding bearing or a needle roller bearing disposed between the input element (Ei) and the second support wall portion (92) in the radial direction (R), and is supported in the axial direction (L) by a thrust bearing (B32) disposed between the input element (Ei) and the second support wall portion (92) in the axial direction (L).

[0135] According to this configuration, for example, compared with a configuration in which the input element (Ei) is supported in both the radial direction (R) and the axial direction (L) by a ball bearing, it is possible to suppress the increase in size of the vehicle drive device (100) while ensuring a large support rigidity of the input element (Ei).

Industrial Applicability

[0136] The technology according to the present disclosure can be used for a vehicle drive device including a rotating electric machine and a planetary gear mechanism.

Explanation of Signs

[0137] 100: Vehicle drive device, 1: Rotating electric machine, 12: Rotor, 2: First output member, 3: Second output member, 4: Planetary gear mechanism, 5: Output differential gear mechanism, 9: Case, E1: First rotating element, E2: Second rotating element, E3: Third rotating element, E4: Fourth rotating element, Ei: Input element, SG1: First sun gear, CR1: First carrier, PG1: First pinion gear, PG2: Second pinion gear, RG1: First ring gear, RG2: Second ring gear, W1: First wheel, W2: Second wheel

Claims

1. A rotating electrical machine having a rotor, A first output member drivingly connected to a first wheel, A second output member drivingly connected to a second wheel, A planetary gear mechanism for reducing the rotation of the rotor, An output differential gear mechanism having an input element and distributing the rotation transmitted from the planetary gear mechanism to the input element to the first output member and the second output member, A vehicle drive device including the rotating electrical machine, the planetary gear mechanism, and a case housing the output differential gear mechanism, wherein the rotating electrical machine, the first output member, the second output member, the planetary gear mechanism, and the output differential gear mechanism are arranged coaxially, the planetary gear mechanism includes a first rotating element, a second rotating element, a third rotating element, and a fourth rotating element, and is configured such that the order of the rotational speeds of the first rotating element, the second rotating element, the third rotating element, and the fourth rotating element is the same as the described order, the first rotating element is a first sun gear connected to rotate integrally with the rotor, the third rotating element is a first ring gear connected to the case, the fourth rotating element is a second ring gear connected to rotate integrally with the input element, the second rotating element is a first carrier rotatably supporting a first pinion gear and a second pinion gear that rotate integrally with each other, the first pinion gear meshes with the first sun gear and the first ring gear, the second pinion gear has a smaller diameter than the first pinion gear and meshes with the second ring gear, with the direction orthogonal to the rotation axis of the rotor as the radial direction, the first sun gear is supported in the radial direction with respect to the case via a first support bearing, the second ring gear and the input element are connected in a state where relative movement in the radial direction is restricted. A vehicle drive device.

2. With the direction along the rotation axis of the rotor being the axial direction, one side of the axial direction being the first axial side, and the other side of the axial direction being the second axial side, the planetary gear mechanism is arranged on the first axial side with respect to the rotor in the axial direction, the differential gear mechanism for output is arranged on the first axial side with respect to the planetary gear mechanism in the axial direction, the input element is supported in the radial direction with respect to the case via a second support bearing arranged on the first axial side with respect to a plurality of gears constituting the differential gear mechanism for output. The vehicle drive device according to claim 1.

3. The differential gear mechanism for output includes a differential case, a shaft member supported by the differential case and arranged to extend along the radial direction, a first bevel gear accommodated in the differential case and rotatably supported by the shaft member, and a pair of second bevel gears accommodated in the differential case and meshing with the first bevel gear on both sides of the shaft member in the axial direction. The differential case is the input element. The vehicle drive device according to claim 2.

4. The first output member is arranged on the first axial side with respect to the second output member in the axial direction, with a portion on the second axial side with respect to the central position in the axial direction of the differential gear mechanism for output in the differential case being a differential case target portion, the second output member is arranged to penetrate the inner side in the radial direction with respect to the differential case target portion in the axial direction, and a third support bearing is arranged between the inner peripheral surface of the differential case target portion and the outer peripheral surface of the second output member. The vehicle drive device according to claim 3.

5. The differential gear mechanism for output is a planetary gear mechanism including a second sun gear, a second carrier, and a third ring gear, the second sun gear is connected to rotate integrally with the first output member, the second carrier is connected to rotate integrally with the second output member, The third ring gear is the input element, and is the vehicle drive device according to claim 2.

6. Taking the direction along the rotation axis center of the rotor as the axial direction, the case includes a first support wall portion disposed between the axial directions of the rotary electric machine and the planetary gear mechanism, The first support bearing is supported by the first support wall portion, and is configured to support the radial support of the first sun gear and the radial support of the rotor. The vehicle drive device according to any one of claims 1 to 5.

7. The second ring gear includes a fitting inner peripheral surface facing the inner side in the radial direction, The input element includes a fitting outer peripheral surface facing the outer side in the radial direction, In a state where the fitting inner peripheral surface and the fitting outer peripheral surface are fitted to each other in contact with each other in the radial direction, the second ring gear and the input element are fixed to each other by welding. The vehicle drive device according to any one of claims 1 to 5.

8. The first pinion gear and the second pinion gear are helical gears, The direction of the thrust load received by the first pinion gear from the first sun gear and the direction of the thrust load received by the second pinion gear from the second ring gear are opposite to the direction of the thrust load received by the first pinion gear from the first ring gear. The vehicle drive device according to any one of claims 1 to 5.

9. Taking the direction along the rotation axis center of the rotor as the axial direction, taking one side in the axial direction as the first axial side, and taking the other side in the axial direction as the second axial side, the case includes a second support wall portion disposed on the first axial side with respect to the output differential gear mechanism, The drive device for a vehicle according to any one of claims 1 to 5, wherein the input element is supported in the radial direction by a sliding bearing or a needle roller bearing disposed between the input element and the second support wall portion in the radial direction, and is supported in the axial direction by a thrust bearing disposed between the input element and the second support wall portion in the axial direction.

Images