Vehicle drive unit

Abstract

To provide a vehicular driving device that enables deterioration of steering performance of a vehicle to be suppressed and can be downsized.SOLUTION: A first planetary gear mechanism 4 comprises a first rotation element E1, a second rotation element E2 and a third rotation element E3. A second planetary gear mechanism 5 comprises a fourth rotation element E4, a fifth rotation element E5 and a sixth rotation element E6. A third planetary gear mechanism 6 comprises a seventh rotation element E7, an eighth rotation element E8 and a ninth rotation element E9. The first rotation element E1 is connected to a rotor 12 in such a way that the first rotation element E1 is rotatable together the rotor 12, the second rotation element E2 is connected to the fourth rotation element E4 in such a way that the second rotation element E2 is rotatable together with the fourth rotation element E4, and the third rotation element E3 is connected to the seventh rotation element E7 in such a way that the third rotation element E3 is rotatable together with the seventh rotation element E7. The fifth rotation element E5 is connected to a non-rotation member NR in such a way that the fifth rotation element E5 is rotatable together with the a non-rotation member NR, the sixth rotation element E6 is connected to a second output member 3 that is connected to a second wheel in a driving manner, the eighth rotation element E8 is connected to a first output member 2 that is connected to a first wheel in a driving manner, and the ninth rotation element E9 is connected to the non-rotation member NR.SELECTED DRAWING: Figure 1

Description

[Technical Field]

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

[0002] An example of such a vehicle drive device is disclosed in the following Patent Document 1. In the following explanations of the "Background Art" and "Problems to be Solved by the Invention," the reference numerals in Patent Document 1 will be quoted in parentheses.

[0003] The vehicle drive device (2) of Patent Document 1 includes a single-pinion planetary gear mechanism (5) including a sun gear (10), a carrier (12), and a ring gear (13). The sun gear (10) is connected to rotate integrally with a rotor of a rotating electric machine (4). The carrier (12) is connected to rotate integrally with a first output member (9) drivingly connected to a first wheel (RF). The ring gear (13) is connected to rotate integrally with a first gear (6). The first gear (6) meshes with a second gear (7) connected to rotate integrally with a second output member (8) drivingly connected to a second wheel (LF). In this way, the planetary gear mechanism (5) reduces the speed of rotation of the rotor of the rotating electric machine (4) and distributes the rotation to the first output member (9) and the second output member (8). [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Publication No. 2018-167769 Summary of the Invention [Problem to be solved by the invention]

[0005] In the vehicle drive device (2) of Patent Document 1, the rotor of the rotating electric machine (4) is decelerated only once by the planetary gear mechanism (5). Therefore, it is difficult to ensure a large reduction ratio in the power transmission path from the rotating electric machine (4) to the pair of output members (8, 9). Accordingly, it is necessary to ensure a large output torque of the rotating electric machine (4), which leads to an increase in the size of the rotating electric machine (4).

[0006] Furthermore, in the vehicle drive device (2) of Patent Document 1, in order to rotate the pair of output members (8, 9) in the same direction, a first gear (6) and a second gear (7) that mesh with each other are provided in a power transmission path between the ring gear (13) and the second output member (8). However, with this configuration, the pair of output members (8, 9) are arranged on different axes, which may deteriorate the steering performance of the vehicle.

[0007] Therefore, it is desirable to realize a vehicle drive device that can suppress deterioration in vehicle steering performance and that can be easily made smaller. [Means for solving the problem]

[0008] In view of the above, the characteristic configuration of the vehicle drive device is as follows: a rotating electric machine having a rotor; a first output member drivingly connected to the first wheel; a second output member drivingly connected to the second wheel; a first planetary gear mechanism including a first rotating element, a second rotating element, and a third rotating element, wherein the rotational speeds of the first rotating element, the second rotating element, and the third rotating element are configured in the order described above; a second planetary gear mechanism including a fourth rotation element, a fifth rotation element, and a sixth rotation element, wherein the rotation speeds of the fourth rotation element, the fifth rotation element, and the sixth rotation element are configured in the order described above; a third planetary gear mechanism including a seventh rotation element, an eighth rotation element, and a ninth rotation element, wherein the seventh rotation element, the eighth rotation element, and the ninth rotation element have rotational speeds in the order described above; the first rotating element is coupled to the rotor so as to rotate integrally with the rotor; the second rotation element is connected to the fourth rotation element so as to rotate integrally with the fourth rotation element; the third rotation element is connected to the seventh rotation element so as to rotate integrally with the seventh rotation element, the fifth rotating element is coupled to a non-rotating member; the sixth rotational element is coupled to the second output member; the eighth rotating element is coupled to the first output member; The ninth rotational element is at a point connected to the non-rotational member.

[0009] According to this characteristic configuration, the rotation of the rotor of the rotating electric machine is reduced by the first planetary gear mechanism and distributed to the second planetary gear mechanism and the third planetary gear mechanism. The rotation input to the second planetary gear mechanism is reduced by the second planetary gear mechanism and transmitted to the second output member, while the rotation input to the third planetary gear mechanism is reduced by the third planetary gear mechanism and transmitted to the first output member. In this way, the rotation of the rotor can be reduced twice for each of the first and second output members, making it easy to ensure a large reduction ratio in the power transmission path from the rotor to the pair of output members. This makes it easy to miniaturize the rotating electric machine while ensuring the required torque. In the above configuration, the rotation transmitted to the second planetary gear mechanism and the rotation transmitted to the third planetary gear mechanism rotate in opposite directions. However, the second planetary gear mechanism decelerates and reverses the input rotation before transmitting it to the second output member. The third planetary gear mechanism decelerates the input rotation and transmits it to the first output member while maintaining the same rotational direction. This allows the first output member and the second output member to rotate in the same direction. This allows the rotating electric machine, the first output member, the second output member, the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism to be arranged coaxially. This prevents deterioration in vehicle steerability caused by the arrangement of a pair of output members. As described above, according to this characteristic configuration, it is possible to realize a vehicle drive device that can suppress deterioration in the steering performance of the vehicle and that can be easily made smaller. [Brief explanation of the drawings]

[0010] [Figure 1] 1 is a cross-sectional view of a vehicle drive device according to an embodiment taken along an axial direction; [Figure 2] 1 is a skeleton diagram of a vehicle drive device according to an embodiment; [Figure 3] FIG. 1 is a partially enlarged cross-sectional view of a vehicle drive device according to an embodiment, taken along an axial direction; [Figure 4] FIG. 1 is a partially enlarged cross-sectional view of a vehicle drive device according to an embodiment, taken along an axial direction; [Figure 5] Velocity diagrams of a first planetary gear mechanism, a second planetary gear mechanism, and a third planetary gear mechanism according to an embodiment DETAILED DESCRIPTION OF THE INVENTION

[0011] 1 and 2, the vehicle drive device 100 includes a rotary electric machine 1 including a stator 11 and 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 first planetary gear mechanism 4, a second planetary gear mechanism 5, and a third planetary gear mechanism 6.

[0012] Here, in this application, the term "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 more transmission members. Such transmission members include various members that transmit rotation at the same speed or at variable speeds, such as shafts, gear mechanisms, belts, and chains. Note that transmission members may also include engagement devices that selectively transmit rotation and driving force, such as friction engagement devices and meshing engagement devices.

[0013] In the following description, the direction along the rotational axis of the rotor 12 is referred to as the "axial direction L." One side of the axial direction L is referred to as the "first axial side L1," and the other side of the axial direction L is referred to as the "second axial side L2." The direction perpendicular to the rotational axis of the rotor 12 is referred to as the "radial direction R." In the radial direction R, the side of the rotational axis of the rotor 12 is referred to as the "radial inner side R1," and the opposite side is referred to as the "radial outer side R2."

[0014] The rotating electric machine 1, first output member 2, second output member 3, first planetary gear mechanism 4, second planetary gear mechanism 5, and third planetary gear mechanism 6 are arranged coaxially. In this example, they are arranged in the following order from a first axial side L1 to a second axial side L2: first output member 2, third planetary gear mechanism 6, first planetary gear mechanism 4, rotating electric machine 1, second planetary gear mechanism 5, and second output member 3.

[0015] In this embodiment, the rotating electric machine 1, the first output member 2, the second output member 3, the first planetary gear mechanism 4, the second planetary gear mechanism 5, and the third planetary gear mechanism 6 are housed in a case 9. The first output member 2 and the second output member 3 are housed in the case 9 with parts of them exposed to the outside of the case 9.

[0016] In this embodiment, the case 9 includes a peripheral wall portion 91, a first side wall portion 92, a second side wall portion 93, a first partition wall portion 94, and a second partition wall portion 95.

[0017] 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 first planetary gear mechanism 4, the second planetary gear mechanism 5, and the third planetary gear mechanism 6. In the example shown in Fig. 1 , the peripheral wall portion 91 is divided into a plurality of portions (two portions in this example) in the axial direction L. The divided portions of the peripheral wall portion 91 are joined together and fastened together by fastening members such as bolts (not shown).

[0018] The first side wall portion 92 and the second side wall portion 93 are each formed to extend in the radial direction R. In this embodiment, the first side wall portion 92 is formed to cover the first axial side L1 of the third planetary gear mechanism 6. The second side wall portion 93 is formed to cover the second axial side L2 of the second planetary gear mechanism 5. In this example, the first side wall portion 92 is formed integrally with the peripheral wall portion 91 so as to close the opening of the peripheral wall portion 91 on the first axial side L1. The second side wall portion 93 is formed integrally with the peripheral wall portion 91 so as to close the opening of the peripheral wall portion 91 on the second axial side L2.

[0019] The first partition wall portion 94 and the second partition wall portion 95 are each formed to extend in the radial direction R. In this embodiment, the first partition wall portion 94 is disposed between the rotating electric machine 1 and the first planetary gear mechanism 4 in the axial direction L. The second partition wall portion 95 is disposed between the rotating electric machine 1 and the second planetary gear mechanism 5 in the axial direction L.

[0020] The rotating electric machine 1 functions as a driving force 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 a supply of electric power to generate power, and a function as a generator that receives a supply of power to generate electric power. Specifically, the rotating electric machine 1 is electrically connected to an electric storage device (not shown) such as a battery or a capacitor. The rotating electric machine 1 generates driving force by running using the electric power stored in the electric storage device. The rotating electric machine 1 also generates electricity using the driving force transmitted from the first wheel W1 and the second wheel W2, thereby charging the electric storage device.

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

[0022] In this embodiment, the rotating electric machine 1 is an inner rotor type rotating electric machine. Therefore, the rotor core 12a is arranged radially inward R1 with respect to the stator core 11a. The rotor shaft 12b is also arranged radially inward R1 with respect to the rotor core 12a.

[0023] In this embodiment, the rotating electric machine 1 is a rotating field type rotating electric machine. Therefore, a stator coil is wound around the stator core 11a. In this embodiment, the stator coil is wound around the stator core 11a so as to form a first coil end portion 11b that protrudes from the stator core 11a toward a first axial side L1 and a second coil end portion 11c that protrudes from the stator core 11a toward a second axial side L2. Although not shown, a permanent magnet is provided in the rotor core 12a.

[0024] In this embodiment, the rotor shaft 12b is formed in a cylindrical shape having an axis aligned with the axial direction L. The rotor shaft 12b is arranged to protrude from the rotor core 12a on both sides in the axial direction L. In this embodiment, the rotor shaft 12b is supported in both the axial direction L and the radial direction R by rotor bearings B1. In this embodiment, the rotor bearings B1 include a first rotor bearing B11 and a second rotor bearing B12.

[0025] 3, in this embodiment, the portion of rotor shaft 12b that protrudes from rotor core 12a toward first axial side L1 is disposed so as to penetrate first partition wall 94 of case 9 in the axial direction L. The portion of rotor shaft 12b that protrudes from rotor core 12a toward first axial side L1 is rotatably supported by first partition wall 94 via first rotor bearing B11. In this embodiment, a rotation sensor 13 that detects rotation of rotor 12 is provided integrally with first rotor bearing B11.

[0026] In this embodiment, the first rotor bearing B11 includes a first inner race B11a, a first outer race B11b, and a first rolling element B11c.

[0027] The first inner race B11a is attached to a first outer peripheral surface 12c, which is the outer peripheral surface of a portion of the rotor shaft 12b that protrudes from the rotor core 12a toward the first axial side L1. Therefore, the first inner race B11a is supported in the radial direction R from the radially inner side R1 by the first outer peripheral surface 12c of the rotor shaft 12b. In this embodiment, the first inner race B11a is supported in the axial direction L from the second axial side L2 by a first side surface 12d formed on the rotor shaft 12b and facing the first axial side L1.

[0028] The first outer race B11b is attached to a first inner circumferential surface 94a that faces the radially inward side R1 and is formed on the first partition wall portion 94. Therefore, the first outer race B11b is supported in the radial direction R from the radially outward side R2 by the first inner circumferential surface 94a of the first partition wall portion 94. In this embodiment, the first outer race B11b is supported in the axial direction L from the axial first side L1 by a second side surface 94b that faces the axial second side L2 and is formed on the first partition wall portion 94.

[0029] The first rolling element B11c is disposed between the first inner race B11a and the first outer race B11b in the radial direction R so as to be rotatable relative to them. In this example, the first rolling element B11c is a spherical body. That is, in this example, the first rotor bearing B11 is a ball bearing.

[0030] 4, in this embodiment, a portion of the rotor shaft 12b that protrudes from the rotor core 12a toward the first axial side L1 is rotatably supported by the second partition wall portion 95 via the second rotor bearing B12. In this embodiment, the second rotor bearing B12 includes a second inner race B12a, a second outer race B12b, and second rolling elements B12c.

[0031] The second inner race B12a is attached to a second outer peripheral surface 12e, which is the outer peripheral surface of a portion of the rotor shaft 12b that protrudes from the rotor core 12a toward the second axial side L2. Therefore, the second inner race B12a is supported in the radial direction R from the radially inner side R1 by the second outer peripheral surface 12e of the rotor shaft 12b. In this embodiment, the second inner race B12a is supported in the axial direction L from the first axial side L1 by a third side surface 12f formed on the rotor shaft 12b and facing the second axial side L2.

[0032] The second outer race B12b is attached to a second inner circumferential surface 95a facing the radially inward side R1 and formed on the second partition wall portion 95. Therefore, the second outer race B12b is supported in the radial direction R from the radially outward side R2 by the second inner circumferential surface 95a of the second partition wall portion 95. In this embodiment, the second outer race B12b is supported in the axial direction L from the second axial side L2 by a fourth side surface 95b facing the first axial side L1 and formed on the second partition wall portion 95.

[0033] The second rolling element B12c is disposed between the second inner race B12a and the second outer race B12b in the radial direction R so as to be rotatable relative to them. In this example, the second rolling element B12c is a spherical body. That is, in this example, the second rotor bearing B12 is a ball bearing.

[0034] 1 and 2, the first planetary gear mechanism 4 includes a first rotating element E1, a second rotating element E2, and a third rotating element E3. The first planetary gear mechanism 4 is configured so that the rotational speeds of the first rotating element E1, the second rotating element E2, and the third rotating element E3 are in the order shown.

[0035] The second planetary gear mechanism 5 includes a fourth rotating element E4, a fifth rotating element E5, and a sixth rotating element E6. The second planetary gear mechanism 5 is configured so that the rotation speeds of the fourth rotating element E4, the fifth rotating element E5, and the sixth rotating element E6 are in the order shown.

[0036] The third planetary gear mechanism 6 includes a seventh rotation element E7, an eighth rotation element E8, and a ninth rotation element E9. The third planetary gear mechanism 6 is configured so that the rotation speeds of the seventh rotation element E7, the eighth rotation element E8, and the ninth rotation element E9 are in the order shown.

[0037] Here, "order of rotational speed" refers to the order of 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 high and low rotational speeds of each rotating element is constant because it is determined by the structure of the planetary gear mechanism. The order of rotational speeds of each rotating element is equal to the arrangement order of each rotating element in the speed diagram (see Figure 5). Here, "arrangement order of each rotating element in the speed diagram" refers to the order in which the axes corresponding to each rotating element in the speed diagram are arranged in a direction perpendicular to those axes. The arrangement direction of the axes corresponding to each rotating element in the speed diagram varies depending on how the speed diagram is drawn, but the arrangement order is constant because it is determined by the structure of the planetary gear mechanism.

[0038] The first planetary gear mechanism 4 functions as a differential gear mechanism that reduces the speed of rotation of the rotor 12 and distributes it to the second planetary gear mechanism 5 and the third planetary gear mechanism 6. The second planetary gear mechanism 5 functions as a reducer that reduces the speed of the rotation transmitted from the first planetary gear mechanism 4 and transmits it to the second output member 3. The third planetary gear mechanism 6 functions as a reducer that reduces the speed of the rotation transmitted from the first planetary gear mechanism 4 and transmits it to the first output member 2.

[0039] In this embodiment, the first planetary gear mechanism 4 is a single-pinion planetary gear mechanism including a first sun gear S1, a first carrier C1, and a first ring gear R1. The second planetary gear mechanism 5 is a single-pinion planetary gear mechanism including a second sun gear S2, a second carrier C2, and a second ring gear R2. The third planetary gear mechanism 6 is a single-pinion planetary gear mechanism including a third sun gear S3, a third carrier C3, and a third ring gear R3. In this embodiment, the gear ratio between the first sun gear S1 and the first ring gear R1 is the same as the gear ratio between the second sun gear S2 and the second ring gear R2, and the gear ratio between the third sun gear S3 and the third ring gear R3.

[0040] The first rotating element E1 is connected to the rotor 12 so as to rotate integrally with the rotor 12. In this embodiment, the rotor 12 and the first rotating element E1 are connected to each other via a rotor shaft 12b so as to rotate integrally with the rotor. In this example, a gear serving as the first rotating element E1 is integrally formed on the rotor shaft 12b. In this embodiment, the first rotating element E1 is a first sun gear S1.

[0041] The second rotating element E2 is connected to the fourth rotating element E4 so as to rotate integrally with them. In this embodiment, the second rotating element E2 and the fourth rotating element E4 are connected to each other so as to rotate integrally via a connecting shaft 7. The connecting shaft 7 is disposed radially inward R1 with respect to the rotor shaft 12b.

[0042] In this embodiment, the second rotating element E2 is the first carrier C1. In addition, in this embodiment, the fourth rotating element E4 is the second sun gear S2. The first carrier C1 supports a first pinion gear P1 that meshes with the first sun gear S1 and the first ring gear R1. The first pinion gear P1 rotates (spins) around its axis and also rotates (revolves) around the first sun gear S1 together with the first carrier C1. A plurality of first pinion gears P1 are provided at intervals from one another along the orbital path.

[0043] The third rotating element E3 is connected to the seventh rotating element E7 so as to rotate integrally with them. In this embodiment, the third rotating element E3 and the seventh rotating element E7 are connected to each other so as to rotate integrally via a connecting member 10. The connecting member 10 is disposed between the first planetary gear mechanism 4 and the third planetary gear mechanism 6 in the axial direction L. The connecting member 10 is formed to extend along the radial direction R.

[0044] In this embodiment, the third rotating element E3 is the first ring gear R1, and the seventh rotating element E7 is the third sun gear S3.

[0045] The fifth rotating element E5 is connected to the non-rotating member NR. In this embodiment, the fifth rotating element E5 is the second carrier C2. The second carrier C2 supports a second pinion gear P2 that meshes with the second sun gear S2 and the second ring gear R2. The second pinion gear P2 rotates (spins) around its axis and also rotates (revolves) around the second sun gear S2 together with the second carrier C2. A plurality of second pinion gears P2 are provided at intervals from one another along the orbital path. In the example shown in FIG. 1, the second carrier C2 is connected to a second partition wall portion 95 of the case 9, which serves as the non-rotating member NR.

[0046] The sixth rotating element E6 is connected to the second output member 3. In this embodiment, the sixth rotating element E6 is the second ring gear R2.

[0047] The eighth rotating element E8 is connected to the first output member 2. In this embodiment, the eighth rotating element E8 is the third carrier C3. The third carrier C3 supports a third pinion gear P3 that meshes with the third sun gear S3 and the third ring gear R3. The third pinion gear P3 rotates (spins) around its axis and also rotates (revolves) around the third sun gear S3 together with the third carrier C3. A plurality of third pinion gears P3 are provided at intervals from one another along the orbital path.

[0048] The ninth rotating element E9 is coupled to a non-rotating member NR. In this embodiment, the ninth rotating element E9 is a third ring gear R3. In the example shown in FIG. 1 , the third ring gear R3 is coupled to a peripheral wall portion 91 of a case 9, which serves as a non-rotating member NR. More specifically, a spline engagement portion formed on the outer circumferential surface of the third ring gear R3 engages with a spline engagement portion formed on the inner circumferential surface of the peripheral wall portion 91, thereby coupling the third ring gear R3 to the case 9 so as not to rotate.

[0049] As described above, the vehicle drive device 100 a rotating 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 first planetary gear mechanism 4 including a first rotating element E1, a second rotating element E2, and a third rotating element E3, and configured such that the rotation speeds of the first rotating element E1, the second rotating element E2, and the third rotating element E3 are in the order described above; a second planetary gear mechanism 5 including a fourth rotation element E4, a fifth rotation element E5, and a sixth rotation element E6, and configured such that the rotation speeds of the fourth rotation element E4, the fifth rotation element E5, and the sixth rotation element E6 are in the order described above; a third planetary gear mechanism (6) including a seventh rotational element (E7), an eighth rotational element (E8), and a ninth rotational element (E9), and configured such that the rotation speeds of the seventh rotational element (E7), the eighth rotational element (E8), and the ninth rotational element (E9) are in the order described above; The first rotating element E1 is connected to the rotor 12 so as to rotate integrally with the rotor 12, The second rotating element E2 is connected to the fourth rotating element E4 so as to rotate integrally with the fourth rotating element E4, The third rotating element E3 is connected to the seventh rotating element E7 so as to rotate integrally therewith, The fifth rotating element E5 is connected to the non-rotating member NR, The sixth rotating element E6 is connected to the second output member 3, The eighth rotating element E8 is connected to the first output member 2, The ninth rotating element E9 is connected to the non-rotating member NR.

[0050] According to this configuration, the rotation of the rotor 12 of the rotating electric machine 1 is reduced by the first planetary gear mechanism 4 and distributed to the second planetary gear mechanism 5 and the third planetary gear mechanism 6. The rotation input to the second planetary gear mechanism 5 is reduced in the second planetary gear mechanism 5 and transmitted to the second output member 3, and the rotation input to the third planetary gear mechanism 6 is reduced in the third planetary gear mechanism 6 and transmitted to the first output member 2. In this way, the rotation of the rotor 12 can be reduced twice for each of the first output member 2 and the second output member 3, making it easy to ensure a large reduction ratio in the power transmission path from the rotor 12 to the pair of output members 2 and 3. This makes it easy to reduce the size of the rotating electric machine 1 while ensuring the required torque. In the above configuration, the rotation transmitted to the second planetary gear mechanism 5 and the rotation transmitted to the third planetary gear mechanism 6 rotate in opposite directions. However, the second planetary gear mechanism 5 decelerates and reverses the input rotation before transmitting it to the second output member 3. The third planetary gear mechanism 6 decelerates the input rotation and transmits it to the first output member 2 while maintaining the same rotational direction. This allows the first output member 2 and the second output member 3 to rotate in the same direction. This allows the rotating electric machine 1, the first output member 2, the second output member 3, the first planetary gear mechanism 4, the second planetary gear mechanism 5, and the third planetary gear mechanism 6 to be arranged coaxially. This makes it possible to suppress deterioration in vehicle steering performance due to the arrangement of the pair of output members 2 and 3. As described above, according to this configuration, it is possible to realize a vehicle drive device 100 that can suppress deterioration in the steering performance of the vehicle and that can be easily made smaller.

[0051] In addition, in this embodiment, the first planetary gear mechanism 4 is a single-pinion planetary gear mechanism including a first sun gear S1 as a first rotating element E1, a first carrier C1 as a second rotating element E2, and a first ring gear R1 as a third rotating element E3, The second planetary gear mechanism 5 is a single-pinion planetary gear mechanism including a second sun gear S2 as a fourth rotation element E4, a second carrier C2 as a fifth rotation element E5, and a second ring gear R2 as a sixth rotation element E6, The third planetary gear mechanism 6 is a single-pinion planetary gear mechanism including a third sun gear S3 as a seventh rotation element E7, a third carrier C3 as an eighth rotation element E8, and a third ring gear R3 as a ninth rotation element E9, The gear ratio between the first sun gear S1 and the first ring gear R1, the gear ratio between the second sun gear S2 and the second ring gear R2, and the gear ratio between the third sun gear S3 and the third ring gear R3 are the same.

[0052] With this configuration, it is easier to ensure a large reduction ratio in the power transmission path from the rotor 12 to the pair of output members 2 and 3, compared to, for example, switching the sun gear and ring gear of each planetary gear mechanism, or making at least one of the first planetary gear mechanism 4, the second planetary gear mechanism 5, and the third planetary gear mechanism 6 a double pinion type. Furthermore, with this configuration, the gear ratio of the sun gear and the ring gear of each planetary gear mechanism is the same. This makes it possible to make the reduction ratio of the power transmission path from the rotor 12 to the first output member 2 the same as the reduction ratio of the power transmission path from the rotor 12 to the second output member 3. Furthermore, because the specifications of the gears that make up each planetary gear mechanism are the same, the processing costs of the gears can be kept low.

[0053] In this embodiment, the rotor 12 and the first rotating element E1 are connected via the rotor shaft 12b so as to rotate integrally, The rotor shaft 12b is supported in both the axial direction L and the radial direction R by a rotor bearing B1, A gear (here, a first sun gear S1) serving as a first rotating element E1 is integrally formed on rotor shaft 12b.

[0054] This configuration simplifies the support structure for the gear as the first rotating element E1 compared to a configuration in which the gear is formed on a member separate from the rotor shaft 12b, making it easier to reduce the size of the vehicle drive device 100.

[0055] As shown in FIGS. 1 and 2, the connecting shaft 7 includes a first connecting member 71 and a second connecting member 72. The first connecting member 71 and the second connecting member 72 are made of a plastic material.

[0056] The first connecting member 71 is connected to the second rotating element E2 so as to rotate integrally therewith. In this embodiment, the first connecting member 71 is arranged to penetrate the first planetary gear mechanism 4 in the axial direction L. The first connecting member 71 includes a first support portion 711 that supports the first carrier C1 serving as the second rotating element E2. The first support portion 711 is arranged on a first axial side L1 with respect to the first planetary gear mechanism 4. The first support portion 711 is formed to extend along the radial direction R. In the example shown in FIG. 1, the first support portion 711 is formed integrally with the first carrier C1.

[0057] The second connecting member 72 is connected to the fourth rotating element E4 so as to rotate integrally therewith. In the present embodiment, the second connecting member 72 is arranged to penetrate the second partition wall portion 95 and the second planetary gear mechanism 5 in the axial direction L. The second connecting member 72 includes a second support portion 721 that supports the second sun gear S2 serving as the fourth rotating element E4. The second support portion 721 is formed in a cylindrical shape having an axis along the axial direction L. The second support portion 721 is arranged to support the second sun gear S2 from the radially inner side R1. In the example shown in FIG. 1, the second support portion 721 is formed integrally with the second sun gear S2.

[0058] 3, the first connecting member 71 is supported in the axial direction L from the first axial side L1 by the first connecting bearing B21. In this embodiment, the first connecting bearing B21 is a thrust bearing arranged between the first support portion 711 of the first connecting member 71 and the third sun gear S3 in the axial direction L.

[0059] In this embodiment, the first output member 2 includes a first cylindrical portion 21 and a first flange portion 22.

[0060] The first cylindrical portion 21 is formed in a cylindrical shape with an axis aligned with the axial direction L. In this embodiment, the first cylindrical portion 21 is arranged to penetrate the first side wall portion 92 of the case 9 in the axial direction L. The first cylindrical portion 21 is coupled to a first drive shaft DS1, which is drivingly coupled to the first wheel W1, so as to rotate integrally with the first cylindrical portion 21. In the example shown in FIG. 3 , the first drive shaft DS1 is inserted into the first cylindrical portion 21 from the first axial side L1 so that the first drive shaft DS1 is positioned on the radially inner side R1 of the first cylindrical portion 21, and the first cylindrical portion 21 and the first drive shaft DS1 are coupled to each other by spline engagement.

[0061] The first flange portion 22 is formed to extend along the radial direction R. In the present embodiment, the first flange portion 22 extends from the first cylindrical portion 21 toward the radially outward direction R2 so as to be located between the first side wall portion 92 of the case 9 and the axial direction L between the third planetary gear mechanism 6. The first flange portion 22 is coupled to the third carrier C3 serving as the eighth rotating element E8 so as to rotate integrally with the third carrier C3. In the example shown in FIG. 3, the first flange portion 22 is formed integrally with the third carrier C3.

[0062] In this embodiment, the third sun gear S3 is supported by an intermediate bearing B3 from the first axial side L1 in the axial direction L. In this embodiment, the intermediate bearing B3 is a thrust bearing arranged between the third sun gear S3 and the first flange portion 22 of the first output member 2 in the axial direction L.

[0063] In this embodiment, the first flange portion 22 is supported in the axial direction L from the first axial side L1 by a first output bearing B41. In this embodiment, the first output bearing B41 is a thrust bearing arranged between the first flange portion 22 and the first side wall portion 92 of the case 9 in the axial direction L.

[0064] As shown in FIG. 4, in this embodiment, the second output member 3 includes a second cylindrical portion 31 and a second flange portion 32.

[0065] The second cylindrical portion 31 is formed in a cylindrical shape with an axis aligned with the axial direction L. In this embodiment, the second cylindrical portion 31 is arranged to penetrate the second side wall portion 93 of the case 9 in the axial direction L. The second cylindrical portion 31 is coupled to a second drive shaft DS2, which is drivingly coupled to the second wheel W2, so as to rotate integrally with the second cylindrical portion 31. In the example shown in FIG. 4 , the second drive shaft DS2 is inserted into the second cylindrical portion 31 from the second axial side L2 so that the second drive shaft DS2 is positioned on the radially inner side R1 of the second cylindrical portion 31, and the second cylindrical portion 31 and the second cylindrical portion 31 are coupled to each other by spline engagement.

[0066] The second flange portion 32 is formed to extend along the radial direction R. In the present embodiment, the second flange portion 32 extends from the second cylindrical portion 31 toward the radially outward direction R2 so as to be located between the second side wall portion 93 of the case 9 and the axial direction L between the second planetary gear mechanism 5. The second flange portion 32 is coupled to the second ring gear R2 serving as the sixth rotating element E6 so as to rotate integrally with the second ring gear R2.

[0067] In this embodiment, the second flange portion 32 is supported in the axial direction L from the second axial side L2 by the second output bearing B42. In this embodiment, the second output bearing B42 is a thrust bearing arranged between the second flange portion 32 and the second side wall portion 93 of the case 9 in the axial direction L.

[0068] The second connecting member 72 is supported in the axial direction L from the second axial side L2 by a second connecting bearing B22. In this embodiment, the second connecting bearing B22 is a thrust bearing arranged between the second support portion 721 of the second connecting member 72 and the second flange portion 32 of the second output member 3 in the axial direction L.

[0069] 4, in this embodiment, the first connecting member 71 has a first contact surface 71a facing the second axial side L2, and the second connecting member 72 has a second contact surface 72a facing the first axial side L1.

[0070] In this embodiment, the first connecting member 71 and the second connecting member 72 are connected to each other with a first abutment surface 71a and a second abutment surface 72a abutting against each other in the axial direction L. In the example shown in Fig. 4, the first connecting member 71 is inserted into the second connecting member 72 from the first axial side L1 so that the first connecting member 71 is positioned radially inward R1 relative to the second connecting member 72. In this state, a first spline engagement portion 71b formed on the outer circumferential surface of the first connecting member 71 and a second spline engagement portion 72b formed on the inner circumferential surface of the second connecting member 72 are engaged with each other. In this example, the first abutment surface 71a is a stepped surface facing the second axial side L2, formed between the first spline engagement portion 71b and an outer circumferential surface that is adjacent to the first spline engagement portion 71b on the second axial side L2 and has a smaller diameter than the first spline engagement portion 71b. In addition, the second abutment surface 72a is a stepped surface facing the first axial side L1, formed between the second spline engagement portion 72b and an inner circumferential surface adjacent to the second axial side L2 of the second spline engagement portion 72b and formed with a smaller diameter than the second spline engagement portion 72b.

[0071] In this manner, in this embodiment, the first planetary gear mechanism 4 and the third planetary gear mechanism 6 are disposed on the first axial side L1 with respect to the rotor 12, The second planetary gear mechanism 5 is disposed on the second axial side L2 relative to the rotor 12, The rotor 12 and the first rotating element E1 are connected via a rotor shaft 12b so as to rotate integrally, The rotor shaft 12b is formed in a cylindrical shape with an axis aligned along the axial direction L. The second rotating element E2 and the fourth rotating element E4 are connected to each other so as to rotate integrally via a connecting shaft 7 disposed on the radially inner side R1 of the rotor shaft 12b, The connecting shaft 7 includes a first connecting member 71 connected to the second rotating element E2 so as to rotate integrally with the second rotating element E2, and a second connecting member 72 connected to the fourth rotating element E4 so as to rotate integrally with the fourth rotating element E4, The first connecting member 71 has a first contact surface 71a facing the second axial side L2, The second connecting member 72 has a second contact surface 72a facing the first axial side L1, The first connecting member 71 and the second connecting member 72 are connected to each other in a state in which the first contact surface 71a and the second contact surface 72a are in contact with each other in the axial direction L, The first connecting member 71 is supported in the axial direction L from the axial first side L1 by the first connecting bearing B21, The second connecting member 72 is supported in the axial direction L from the second axial side L2 by a second connecting bearing B22.

[0072] With this configuration, for example, a thrust load acting on the second rotating element E2 of the first planetary gear mechanism 4 toward the second axial side L2 can be received by the second connecting bearing B22, which supports the second connecting member 72 in the axial direction L from the second axial side L2, via the first connecting member 71. Also, a thrust load acting on the fourth rotating element E4 of the second planetary gear mechanism 5 toward the first axial side L1 can be received by the first connecting bearing B21, which supports the first connecting member 71 in the axial direction L from the first axial side L1, via the second connecting member 72. This eliminates the need to provide bearings that directly receive thrust loads acting on the second rotating element E2 and the fourth rotating element E4. This makes it easier to reduce the size of the vehicle drive device 100.

[0073] 3 and 4, in this example, a thrust load acting on the first carrier C1 serving as the second rotating element E2 toward the second axial side L2 is received by the second side wall 93 of the case 9 via the first connecting member 71, the second connecting member 72, the second connecting bearing B22, the second flange 32, and the second output bearing B42. Also, a thrust load acting on the second sun gear S2 serving as the fourth rotating element E4 toward the first axial side L1 is received by the first side wall 92 of the case 9 via the second connecting member 72, the first connecting member 71, the first connecting bearing B21, the third sun gear S3, the intermediate bearing B3, the first flange 22, and the first output bearing B41.

[0074] 3 and 4, in this embodiment, a first oil passage 81 is formed inside the connecting shaft 7. The first oil passage 81 corresponds to an "intra-shaft oil passage." 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.

[0075] The axial oil passage 81a is formed to extend along the axial direction L inside the connecting shaft 7. In this embodiment, the axial oil passage 81a is formed inside the first connecting member 71 of the connecting shaft 7.

[0076] The first radial oil passage 81b, the second radial oil passage 81c, and the third radial oil passage 81d are formed to extend from the axial oil passage 81a toward the radially outer side R2.

[0077] 4, in the present embodiment, the first radial oil passage 81b is arranged to overlap with the second partition wall portion 95 of the case 9 when viewed in the radial direction R. The first radial oil passage 81b is formed across the first connecting member 71 and the second connecting member 72 of the connecting shaft 7 so as to connect the axial oil passage 81a formed inside the first connecting member 71 with the outer circumferential surface of the second connecting member 72 arranged on the radially outer side R2 relative to the first connecting member 71. In the present embodiment, a plurality of first radial oil passages 81b are arranged at intervals in the circumferential direction of the connecting shaft 7. Here, with regard to the arrangement of two elements, "overlapping when viewed in a specific direction" means that when an imaginary line parallel to the line of sight is moved in each direction perpendicular to the imaginary line, there is at least a region where the imaginary line intersects with both of the two elements.

[0078] 3, in this embodiment, the second radial oil passage 81c is arranged so as not to overlap with the second connecting member 72 but to overlap with the rotor shaft 12b when viewed in the radial direction R. The second radial oil passage 81c is formed so as to communicate between the axial oil passage 81a and the outer peripheral surface of the first connecting member 71. In this embodiment, the multiple second radial oil passages 81c are arranged at intervals in the axial direction L and the circumferential direction of the connecting shaft 7.

[0079] In this embodiment, the third radial oil passage 81d is formed inside the first support portion 711 of the first connecting member 71. The third radial oil passage 81d is in communication with an oil passage formed inside the first carrier C1 and an oil passage formed inside the first pinion shaft PS1 that rotatably supports the first pinion gear P1. In this embodiment, the multiple third radial oil passages 81d are arranged at intervals around the circumferential direction of the connecting shaft 7.

[0080] As shown in FIG. 4, in this embodiment, a second oil passage 82 is provided to supply oil to the first oil passage 81. The second oil passage 82 corresponds to an "oil supply passage" that supplies oil to the in-shaft oil passage. The second oil passage 82 is disposed between the rotor 12 and the second planetary gear mechanism 5 in the axial direction L. The second oil passage 82 is formed to extend in the radial direction R. In this embodiment, the second oil passage 82 is formed inside the second partition wall portion 95 of the case 9. The second oil passage 82 is formed to communicate with the first radial oil passage 81b. The second oil passage 82 also communicates with an oil passage formed inside the second pinion shaft PS2 that rotatably supports the second pinion gear P2.

[0081] As shown in FIG. 4, in this embodiment, oil discharged from a hydraulic pump (not shown) provided in the vehicle drive device 100 is supplied to the second oil passage 82. The oil supplied to the second oil passage 82 passes through an oil passage formed inside the second pinion shaft PS2 and is supplied to the second pinion gear P2 and the like. The oil supplied to the second oil passage 82 passes through a first radial oil passage 81b and is supplied to the axial oil passage 81a. As shown in FIG. 3, the oil supplied to the axial oil passage 81a passes through a second radial oil passage 81c and is supplied to the inner circumferential surface of the rotor shaft 12b. The oil supplied to the axial oil passage 81a passes through a third radial oil passage 81d, an oil passage formed inside the first carrier C1, and an oil passage formed inside the first pinion shaft PS1 and is supplied to the first pinion gear P1 and the like. As described above, in this embodiment, the oil discharged from the hydraulic pump is supplied to the inner circumferential surface of the rotor shaft 12b relatively upstream, which makes it easier to improve the cooling performance of the rotating electrical machine 1 via the inner circumferential surface of the rotor shaft 12b.

[0082] In this manner, in this embodiment, the first planetary gear mechanism 4 and the third planetary gear mechanism 6 are disposed on the first axial side L1 with respect to the rotor 12, The second planetary gear mechanism 5 is disposed on the second axial side L2 relative to the rotor 12, The rotor 12 and the first rotating element E1 are connected via a rotor shaft 12b so as to rotate integrally, The rotor shaft 12b is formed in a cylindrical shape with an axis aligned along the axial direction L. The second rotating element E2 and the fourth rotating element E4 are connected to each other so as to rotate integrally via a connecting shaft 7 disposed on the radially inner side R1 of the rotor shaft 12b, A first oil passage 81 is formed inside the connecting shaft 7 as an in-shaft oil passage, A second oil passage 82 serving as an oil supply passage for supplying oil to the intra-shaft oil passage is disposed between the rotor 12 and the second planetary gear mechanism 5 in the axial direction L so as to extend in the radial direction R.

[0083] This configuration makes it easy to arrange the first planetary gear mechanism 4 and the third planetary gear mechanism 6 adjacent to each other, which makes it easy to simplify the connection structure between the first planetary gear mechanism 4 and the third planetary gear mechanism 6. Furthermore, according to this configuration, the first planetary gear mechanism 4 and the second planetary gear mechanism 5, which are arranged separately on either side of the rotor 12 in the axial direction L, are connected via the connecting shaft 7, which is arranged on the radially inner side R1 of the rotor shaft 12b. This allows the second rotating element E2 of the first planetary gear mechanism 4 and the fourth rotating element E4 of the second planetary gear mechanism 5 to be connected appropriately without being obstructed by the rotor 12. Furthermore, according to this configuration, a first oil passage 81 serving as an in-shaft oil passage is formed inside the connecting shaft 7. A second oil passage 82 serving as an oil supply passage for supplying oil to the in-shaft oil passage is disposed so as to extend in the radial direction R between the rotor 12 and the second planetary gear mechanism 5 in the axial direction L. This allows the first oil passage 81 serving as an in-shaft oil passage and the second oil passage 82 serving as an oil supply passage to be appropriately connected without being obstructed by the rotor 12.

[0084] FIG. 5 shows a speed diagram of the first planetary gear mechanism 4, the second planetary gear mechanism 5, and the third planetary gear mechanism 6 according to this embodiment. In the speed diagram of FIG. 5, vertical lines correspond to the rotational speeds of the rotating elements of the planetary gear mechanisms 4, 5, and 6. Each of the multiple parallel vertical lines corresponds to a rotating element of the planetary gear mechanisms 4, 5, and 6. In the speed diagram of FIG. 5, the symbols above the multiple vertical lines indicate the symbols of the corresponding rotating elements. The symbols below the multiple vertical lines indicate the symbols of elements that rotate integrally with the rotating element corresponding to the symbol above. In the speed diagram of FIG. 5, black circles on multiple vertical lines indicate that the rotating elements corresponding to the corresponding vertical lines rotate integrally. In the speed diagram of FIG. 5, crosses on multiple vertical lines indicate that the rotating element corresponding to the corresponding vertical line is fixed to a non-rotating member NR.

[0085] 5, in this embodiment, the rotation transmitted from rotor 12 of rotating electric machine 1 to first sun gear S1 is distributed to first carrier C1 and first ring gear R1 in first planetary gear mechanism 4. At this time, the rotation of first sun gear S1 is decelerated while maintaining the same rotation direction and transmitted to first carrier C1, and is also decelerated while reversing and transmitted to first ring gear R1.

[0086] The rotation transmitted from the first carrier C1 to the second sun gear S2 of the second planetary gear mechanism 5 is reversed and reduced in speed in the second planetary gear mechanism 5, and then transmitted to the second output member 3 connected to the second ring gear R2. The rotation transmitted from the first ring gear R1 to the third sun gear S3 of the third planetary gear mechanism 6 is reduced in speed in the third planetary gear mechanism 6 while maintaining the same rotational direction, and then transmitted to the first output member 2 connected to the third carrier C3.

[0087] Other Embodiments (1) In the above embodiment, the first planetary gear mechanism 4, the second planetary gear mechanism 5, and the third planetary gear mechanism 6 are each a single-pinion planetary gear mechanism. However, the present invention is not limited to such a configuration, and for example, at least one of the first planetary gear mechanism 4, the second planetary gear mechanism 5, and the third planetary gear mechanism 6 may be a double-pinion planetary gear mechanism.

[0088] (2) In the above embodiment, the gear ratio between the first sun gear S1 and the first ring gear R1, the gear ratio between the second sun gear S2 and the second ring gear R2, and the gear ratio between the third sun gear S3 and the third ring gear R3 are the same. However, the present invention is not limited to such a configuration, and the gear ratios between the sun gears and the ring gears of each planetary gear mechanism may be different from each other. Furthermore, in a configuration in which the gear ratios between the sun gears and the ring gears of each planetary gear mechanism are the same, the number of teeth of the sun gears and the number of teeth of the ring gears of each planetary gear mechanism may be different from each other.

[0089] (3) In the above embodiment, the second oil passage 82 is disposed between the rotor 12 and the second planetary gear mechanism 5 in the axial direction L. However, the present invention is not limited to such a configuration, and the second oil passage 82 may be disposed between the rotor 12 and the first planetary gear mechanism 4 in the axial direction L, for example.

[0090] (4) In the above embodiment, the rotor bearing B1 is described as including the first rotor bearing B11 and the second rotor bearing B12. However, the present invention is not limited to such a configuration. For example, the rotor bearing B1 may be including a pair of radial bearings that support the rotor shaft 12b in the radial direction R and a pair of thrust bearings that support the rotor shaft 12b in the axial direction L.

[0091] (5) In the above embodiment, the first connecting member 71 and the second connecting member 72 are connected to each other with the first contact surface 71a and the second contact surface 72a in contact with each other in the axial direction L. However, the present invention is not limited to such a configuration. For example, the first contact surface 71a and the second contact surface 72a may not be provided. In this configuration, it is preferable to provide bearings that directly receive thrust loads acting on the second rotating element E2 and the fourth rotating element E4.

[0092] (6) The configurations disclosed in the above-described embodiments may be combined with configurations disclosed in other embodiments as long as no contradictions arise. Regarding other configurations, the embodiments disclosed in this specification are merely examples in all respects. Therefore, various modifications may be made as appropriate within the scope of the present disclosure. [Industrial Applicability]

[0093] The technology according to the present disclosure can be used in a vehicle drive device including a rotating electric machine and a planetary gear mechanism. [Explanation of symbols]

[0094] 100: vehicle drive device, 1: rotating electric machine, 12: rotor, 2: first output member, 3: second output member, 4: first planetary gear mechanism, 5: second planetary gear mechanism, 6: third planetary gear mechanism, E1: first rotating element, E2: second rotating element, E3: third rotating element, E4: fourth rotating element, E5: fifth rotating element, E6: sixth rotating element, E7: seventh rotating element, E8: eighth rotating element, E9: ninth rotating element, NR: non-rotating member, W1: first wheel, W2: second wheel

Claims

1. a rotating electric machine having a rotor; a first output member drivingly connected to the first wheel; a second output member drivingly connected to the second wheel; a first planetary gear mechanism including a first rotating element, a second rotating element, and a third rotating element, wherein the rotational speeds of the first rotating element, the second rotating element, and the third rotating element are configured in the order described above; a second planetary gear mechanism including a fourth rotation element, a fifth rotation element, and a sixth rotation element, wherein the rotation speeds of the fourth rotation element, the fifth rotation element, and the sixth rotation element are configured in the order described above; a third planetary gear mechanism including a seventh rotation element, an eighth rotation element, and a ninth rotation element, wherein the seventh rotation element, the eighth rotation element, and the ninth rotation element have rotational speeds in the order described above; the first rotating element is coupled to the rotor so as to rotate integrally with the rotor; the second rotation element is connected to the fourth rotation element so as to rotate integrally with the fourth rotation element, the third rotational element is connected to the seventh rotational element so as to rotate integrally with the seventh rotational element, the fifth rotating element is coupled to a non-rotating member; the sixth rotational element is coupled to the second output member; the eighth rotary element is coupled to the first output member; the ninth rotational element is coupled to the non-rotational member; A direction perpendicular to the rotation axis of the rotor is defined as a radial direction, a direction along the rotation axis of the rotor is defined as an axial direction, one side in the axial direction is defined as an axial first side, and the other side in the axial direction is defined as an axial second side, the first planetary gear mechanism and the third planetary gear mechanism are disposed on the first axial side with respect to the rotor, the second planetary gear mechanism is disposed on the second axial side with respect to the rotor, the rotor and the first rotating element are connected to each other via a rotor shaft so as to rotate together; the rotor shaft is formed in a cylindrical shape having an axis aligned with the axial direction, the second rotating element and the fourth rotating element are connected to each other so as to rotate integrally via a connecting shaft disposed radially inside with respect to the rotor shaft, the connecting shaft includes a first connecting member connected to the second rotating element so as to rotate integrally with the second rotating element, and a second connecting member connected to the fourth rotating element so as to rotate integrally with the fourth rotating element, the first connecting member includes a first abutment surface facing the second axial side, the second connecting member includes a second abutment surface facing the first axial side, the first connecting member and the second connecting member are connected to each other with the first abutment surface and the second abutment surface abutting each other in the axial direction, the first connecting member is supported in the axial direction from the first axial side by a first connecting bearing, The second connecting member is supported in the axial direction from the second axial side by a second connecting bearing.

2. the first planetary gear mechanism is a single-pinion planetary gear mechanism including a first sun gear as the first rotating element, a first carrier as the second rotating element, and a first ring gear as the third rotating element, the second planetary gear mechanism is a single-pinion planetary gear mechanism including a second sun gear as the fourth rotational element, a second carrier as the fifth rotational element, and a second ring gear as the sixth rotational element, the third planetary gear mechanism is a single-pinion planetary gear mechanism including a third sun gear as the seventh rotation element, a third carrier as the eighth rotation element, and a third ring gear as the ninth rotation element, 2. The vehicle drive device according to claim 1, wherein a gear ratio between the first sun gear and the first ring gear, a gear ratio between the second sun gear and the second ring gear, and a gear ratio between the third sun gear and the third ring gear are the same.

3. A direction perpendicular to the rotation axis of the rotor is defined as a radial direction, a direction along the rotation axis of the rotor is defined as an axial direction, one side in the axial direction is defined as an axial first side, and the other side in the axial direction is defined as an axial second side, the first planetary gear mechanism and the third planetary gear mechanism are disposed on the first axial side with respect to the rotor, the second planetary gear mechanism is disposed on the second axial side with respect to the rotor, the rotor and the first rotating element are connected to each other via a rotor shaft so as to rotate together; the rotor shaft is formed in a cylindrical shape having an axis along the axial direction, the second rotating element and the fourth rotating element are connected to each other so as to rotate integrally via a connecting shaft disposed radially inside with respect to the rotor shaft, an in-shaft oil passage is formed inside the connecting shaft, 3. The vehicle drive device according to claim 1, wherein an oil supply passage for supplying oil to the in-shaft oil passage is disposed between the rotor and the second planetary gear mechanism in the axial direction so as to extend in the radial direction.

4. A direction perpendicular to the rotation axis of the rotor is defined as a radial direction, and a direction along the rotation axis of the rotor is defined as an axial direction, the rotor and the first rotating element are connected to each other via a rotor shaft so as to rotate together; the rotor shaft is supported in both the axial direction and the radial direction by a rotor bearing, The vehicle drive device according to claim 1 , wherein a gear serving as the first rotating element is integrally formed with the rotor shaft.

Images