WO2020203916A1

WO2020203916A1 - Vehicle drive device

Info

Publication number: WO2020203916A1
Application number: PCT/JP2020/014364
Authority: WO
Inventors: 井上亮平
Original assignee: アイシン・エィ・ダブリュ株式会社
Priority date: 2019-03-29
Filing date: 2020-03-27
Publication date: 2020-10-08

Abstract

A vehicle drive device equipped with a rotary electric machine (1), an input member (3) drivably coupled to the rotary electric machine (1), a pair of output members (61, 62), a transmission mechanism (T) for drivably coupling the input member (3) and the pair of output members (61, 62), a case (2) for accommodating the rotary electric machine (1) and the transmission mechanism (T), and a hydraulic pump (7) driven by driving force transmitted through a power transmission path (P) connecting the rotary electric machine (1) and a wheel (W), wherein the power transmission path (P) is configured so as to continuously transmit driving force between the rotary electric machine (1) and the hydraulic pump (7), and at least a portion of a rotation member (RT) of the hydraulic pump (7) is arranged within an oil storage section (S) inside the case (2).

Description

Vehicle drive

The present invention is driven by a rotary electric machine which is a driving force source for wheels, a counter gear mechanism, a differential gear mechanism, a case accommodating them, and a driving force transmitted through a power transmission path connecting the rotary electric machine and wheels. The present invention relates to a hydraulic pump and a drive device for a vehicle.

An example of such a vehicle drive device is disclosed in Patent Document 1 below. Hereinafter, in the description of this background technique, the reference numerals in Patent Document 1 are quoted in parentheses.

In the vehicle drive device (1) of Patent Document 1, when the rotary electric machine (10) is rotated in the normal direction (rotated in the direction in which the vehicle is advanced), the hydraulic pump (51) stores oil in the case (40). The oil stored in the section (70) is pumped up and supplied to the oil passages (91, 97, etc.). The oil supplied to the oil passages (91, 97, etc.) is used as a cooling target for the rotor (14) of the rotary electric machine (10) and a lubrication target for the counter gear mechanism (20), the differential gear mechanism (30), etc. After flowing, it is stored again in the storage unit (70) in the case (40). As described above, since the oil circulates in the case (40) during the normal rotation of the rotary electric machine (10), the rotating members such as the rotor of the hydraulic pump (51) are always lubricated by the oil. It has become.

International Publication No. 2018/061443 (Figs. 1 and 6)

On the other hand, when the rotary electric machine (10) is reversed (rotated in the direction of moving the vehicle backward), the hydraulic pump (51) stores the oil in the oil passages (91, 97, etc.) in the case (40). Backflow to 70). Therefore, when the reversal of the rotary electric machine (10) is maintained for more than a certain period of time, there is almost no oil in the oil passages (91, 97, etc.). As a result, the oil does not flow from the oil passages (91, 97, etc.) to the hydraulic pump (51), resulting in insufficient lubrication of the rotating members of the hydraulic pump (51).

In the vehicle drive device (1) of Patent Document 1, since the hydraulic pump (51) is always linked with the rotary electric machine (10), the rotation of the hydraulic pump (51) is stopped during the reversal of the rotary electric machine (10). It is a configuration that cannot be done. In such a configuration, as a means for avoiding insufficient lubrication of the rotating member of the hydraulic pump (51) during reversal of the rotary electric machine (10), an oil passage for supplying oil to the rotating member of the hydraulic pump (51). It is conceivable to provide an oil supply mechanism such as. However, the installation of such an oil supply mechanism causes an increase in the manufacturing cost of the vehicle drive device (1) and an increase in the size of the vehicle drive device (1).

Therefore, in a configuration in which the hydraulic pump is always linked with the rotary electric machine, the rotating member of the hydraulic pump is appropriate even during the reversal of the rotary electric machine while suppressing an increase in the manufacturing cost of the vehicle drive device and an increase in the size of the vehicle drive device. A vehicle drive device that can be lubricated is desired.

In view of the above, the characteristic configuration of the vehicle drive device is
The rotating electric machine that is the driving force source for the wheels,
With the input member driven and connected to the rotary electric machine,
A pair of output members that are driven and connected to the wheels, respectively.
A transmission mechanism that drives and connects the input member and the pair of output members,
A case for accommodating the rotary electric machine and the transmission mechanism, and
A hydraulic pump driven by a driving force transmitted through a power transmission path connecting the rotary electric machine and the wheels is provided.
The power transmission path is configured to constantly transmit a driving force between the rotary electric machine and the hydraulic pump.
An oil storage unit for storing oil is provided in the case.
At least a part of the rotating member of the hydraulic pump is arranged in the oil storage part.

According to this characteristic configuration, at least a part of the rotating member of the hydraulic pump is in constant contact with the oil stored in the oil storage section. Therefore, the oil stored in the oil storage unit can be supplied to the rotating member of the pump regardless of the rotation direction of the rotary electric machine. Therefore, in a configuration in which the power transmission path connecting the rotary electric machine and the wheels constantly transmits the driving force between the rotary electric machine and the hydraulic pump, an oil passage or the like that supplies oil to the rotating member of the hydraulic pump during the reversal of the rotary electric machine. Even if the oil supply mechanism is not provided, the rotating member of the hydraulic pump can be properly lubricated. That is, according to this configuration, in the configuration in which the hydraulic pump is always linked with the rotary electric machine, the hydraulic pressure is suppressed even during the reversal of the rotary electric machine while suppressing the increase in the manufacturing cost of the vehicle drive device and the increase in size of the vehicle drive device. The rotating members of the pump can be properly lubricated.

Sectional drawing along the axial direction of the vehicle drive device which concerns on 1st Embodiment Skeleton diagram of the vehicle drive device according to the first embodiment Sectional drawing orthogonal to the axial direction of the vehicle drive device which concerns on 1st Embodiment Enlarged sectional view around the hydraulic pump of the vehicle drive device according to the first embodiment. Cross-sectional view orthogonal to the axial direction of the vehicle drive device according to the second embodiment.

1. 1. First Embodiment In the following, the vehicle drive device 100 according to the first embodiment will be described with reference to the drawings. As shown in FIGS. 1 and 2, the vehicle drive device 100 includes a rotary electric machine 1, a case 2, an input member 3, a transmission mechanism T, and a first output member 61 and a second output member 62. I have. In the present embodiment, the transmission mechanism T includes an input gear 32 included in the input member 3, a counter gear mechanism 4, and a differential gear mechanism 5.

The rotary electric machine 1 is arranged on the first axis A1 as its rotation axis. In this embodiment, the input member 3 is also arranged on the first axis A1. The counter gear mechanism 4 is arranged on the second axis A2 as its rotation axis. The differential gear mechanism 5 is arranged on the third axis A3 as its rotation axis. In the present embodiment, the first output member 61 and the second output member 62 are also arranged on the third axis A3. The first axis A1, the second axis A2, and the third axis A3 are virtual axes that are different from each other and are arranged in parallel with each other.

In the following description, the direction parallel to the above axes A1 to A3 is referred to as the "axial direction L" of the vehicle drive device 100. Then, in the axial direction L, the side on which the rotary electric machine 1 is arranged with respect to the input member 3 is referred to as the "axial first side L1", and the opposite side is referred to as the "axial second side L2". Further, the direction orthogonal to each of the first axis A1, the second axis A2, and the third axis A3 is defined as the "radial direction R" with respect to each axis. When it is not necessary to distinguish which axis is used as a reference, or when it is clear which axis is used as a reference, it may be simply described as "diameter direction R".

As shown in FIG. 1, the case 2 houses the rotary electric machine 1, the input gear 32 as the transmission mechanism T, the counter gear mechanism 4, and the differential gear mechanism 5. In the present embodiment, the case 2 has a peripheral wall portion 21, a first side wall portion 22, a second side wall portion 23, and a partition wall portion 24.

The peripheral wall portion 21 is formed in a tubular shape that surrounds the rotary electric machine 1, the input member 3, the counter gear mechanism 4, the differential gear mechanism 5, and the outer sides of the first output member 61 and the second output member 62 in the radial direction R. There is. The first side wall portion 22 and the second side wall portion 23 are formed so as to extend along the radial direction R. The first side wall portion 22 is fixed to the end portion of the peripheral wall portion 21 on the axial first side L1 so as to close the opening of the peripheral wall portion 21 on the axial first side L1. The second side wall portion 23 is fixed to the end portion of the peripheral wall portion 21 on the axial second side L2 so as to close the opening of the peripheral wall portion 21 on the axial second side L2. The partition wall portion 24 is a space inside the peripheral wall portion 21 in the radial direction R, and is formed so as to partition the space between the first side wall portion 22 and the second side wall portion 23 in the axial direction L.

In the present embodiment, the rotary electric machine 1 is arranged between the first side wall portion 22 and the partition wall portion 24. An input member 3, a counter gear mechanism 4, and a differential gear mechanism 5 are arranged between the second side wall portion 23 and the partition wall portion 24.

The rotary electric machine 1 functions as a driving force source for the pair of wheels W. The rotary electric machine 1 has a stator 11 and a rotor 12. Here, in the present application, "rotary electric machine" is used as a concept including any of a motor (electric motor), a generator (generator), and, if necessary, a motor / generator that functions as both a motor and a generator.

The stator 11 has a stator core 111 fixed to a non-rotating member (for example, case 2). The rotor 12 has a rotor core 121 that can rotate with respect to the stator 11, and a rotor shaft 122 that is connected so as to rotate integrally with the rotor core 121. In the present embodiment, the rotary electric machine 1 is a rotating field type rotary electric machine. Therefore, a coil is wound around the stator core 111 so that coil end portions 112 projecting from the stator core 111 on both sides in the axial direction L (the first side L1 in the axial direction and the second side L2 in the axial direction) are formed. ing. A permanent magnet 123 is provided on the rotor core 121. Further, in the present embodiment, the rotary electric machine 1 is an inner rotor type rotary electric machine. Therefore, the rotor core 121 is arranged inside the stator core 111 in the radial direction R. The rotor shaft 122 is connected to the inner peripheral surface of the rotor core 121.

The rotor shaft 122 is a rotating member that rotates around the first shaft A1. The rotor shaft 122 is formed so as to extend along the axial direction L. In the present embodiment, the rotor shaft 122 is rotatably supported with respect to the case 2 via the first rotor bearing B1a and the second rotor bearing B1b. Specifically, the end portion of the rotor shaft 122 on the first side L1 in the axial direction is rotatably supported with respect to the first side wall portion 22 of the case 2 via the first rotor bearing B1a. Then, the end portion of the rotor shaft 122 on the second side L2 in the axial direction is rotatably supported with respect to the partition wall portion 24 of the case 2 via the second rotor bearing B1b.

The input member 3 is drive-connected to the rotary electric machine 1. The input member 3 includes an input shaft 31 and an input gear 32.

The input shaft 31 is a rotating member that rotates around the first shaft A1. The input shaft 31 is formed so as to extend along the axial direction L. In the present embodiment, the input shaft 31 is inserted into a through hole that penetrates the partition wall portion 24 of the case 2 in the axial direction L. The end of the input shaft 31 on the first axial side L1 is connected to the end of the rotor shaft 122 on the second axial side L2. In the illustrated example, the end of the axial first side L1 of the input shaft 31 is the end of the axial second side L2 of the rotor shaft 122 so that the input shaft 31 is located inside the radial direction R of the rotor shaft 122. It is inserted into the portions and these ends are connected by spline engagement.

In the present embodiment, the input shaft 31 is rotatably supported with respect to the case 2 via the first input bearing B3a and the second input bearing B3b. Specifically, the portion of the input shaft 31 on the first side L1 in the axial direction with respect to the central portion in the axial direction L, and the portion L2 on the second side in the axial direction with respect to the connecting portion with the rotor shaft 122 is the second portion. It is rotatably supported with respect to the partition wall portion 24 of the case 2 via the 1 input bearing B3a. Then, the end portion of the input shaft 31 on the second side L2 in the axial direction is rotatably supported with respect to the second side wall portion 23 of the case 2 via the second input bearing B3b.

The input gear 32 corresponds to the "first gear". The input gear 32 transmits the driving force from the rotary electric machine 1 to the counter gear mechanism 4. The input gear 32 is connected to the input shaft 31 so as to rotate integrally with the input shaft 31. In this embodiment, the input gear 32 is integrally formed with the input shaft 31. Further, in the present embodiment, the input gear 32 is arranged between the first input bearing B3a and the second input bearing B3b.

The counter gear mechanism 4 is arranged between the input member 3 and the differential gear mechanism 5 in the power transmission path P connecting the rotary electric machine 1 and the pair of wheels W. The counter gear mechanism 4 has a counter shaft 41, a first counter gear 42, and a second counter gear 43.

The counter shaft 41 is a rotating member that rotates around the second shaft A2. The counter shaft 41 is formed so as to extend along the axial direction L. In the present embodiment, the counter shaft 41 is rotatably supported with respect to the case 2 via the first counter bearing B4a and the second counter bearing B4b. Specifically, the end portion of the counter shaft 41 on the first side L1 in the axial direction is rotatably supported with respect to the partition wall portion 24 of the case 2 via the first counter bearing B4a. Then, the end portion of the counter shaft 41 on the second side L2 in the axial direction is rotatably supported with respect to the second side wall portion 23 of the case 2 via the second counter bearing B4b.

The first counter gear 42 is an input element of the counter gear mechanism 4. The first counter gear 42 meshes with the input gear 32 of the input member 3. That is, the first counter gear 42 corresponds to the "second gear" that meshes with the first gear. The first counter gear 42 is connected to the counter shaft 41 so as to rotate integrally with the counter shaft 41. In the present embodiment, the first counter gear 42 is connected to the counter shaft 41 by spline engagement. Further, in the present embodiment, the first counter gear 42 is arranged between the first counter bearing B4a and the second counter bearing B4b, and is arranged on the second side L2 in the axial direction with respect to the second counter gear 43. ..

The second counter gear 43 is an output element of the counter gear mechanism 4. The second counter gear 43 is connected to the counter shaft 41 so as to rotate integrally with the counter shaft 41. That is, the second counter gear 43 corresponds to a "third gear" that rotates integrally with the second gear. In the present embodiment, the second counter gear 43 is integrally formed with the counter shaft 41. Further, in the present embodiment, the second counter gear 43 is formed to have a smaller diameter than the first counter gear 42. In the illustrated example, the second counter gear 43 is located between the first counter bearing B4a and the second counter bearing B4b, and is arranged on the first side L1 in the axial direction with respect to the first counter gear 42.

The differential gear mechanism 5 distributes the driving force transmitted from the rotary electric machine 1 side to the first output member 61 and the second output member 62. In the present embodiment, the differential gear mechanism 5 includes a differential input gear 51, a differential case 52, a pinion shaft 53, a pair of pinion gears 54, and a first side gear 55 and a second side gear 56. There is. In the present embodiment, the pair of pinion gears 54, and the first side gear 55 and the second side gear 56 are all bevel gears.

The differential input gear 51 is an input element of the differential gear mechanism 5. The differential input gear 51 meshes with the second counter gear 43 of the counter gear mechanism 4. That is, the differential input gear 51 corresponds to the "fourth gear" that meshes with the third gear. The differential input gear 51 is connected to the differential case 52 so as to rotate integrally with the differential case 52.

The differential case 52 is a rotating member that rotates around the third axis A3. In the present embodiment, the differential case 52 is rotatably supported with respect to the case 2 via the first differential bearing B5a and the second differential bearing B5b. Specifically, the end portion of the differential case 52 on the first side L1 in the axial direction is rotatably supported with respect to the partition wall portion 24 of the case 2 via the first differential bearing B5a. Then, the end portion of the second side L2 in the axial direction of the differential case 52 is rotatably supported with respect to the second side wall portion 23 of the case 2 via the second differential bearing B5b.

The differential case 52 is a hollow member. A pinion shaft 53, a pair of pinion gears 54, and a first side gear 55 and a second side gear 56 are housed inside the differential case 52.

The pinion shaft 53 extends along the radial direction R with respect to the third axis A3. The pinion shaft 53 is inserted into a pair of pinion gears 54 and rotatably supports them. The pinion shaft 53 is arranged so as to penetrate the differential case 52. The pinion shaft 53 is locked to the differential case 52 by the locking member 53a and rotates integrally with the differential case 52. In the illustrated example, the locking member 53a is a rod-shaped pin that is inserted into both the differential case 52 and the pinion shaft 53.

The pair of pinion gears 54 are attached to the pinion shaft 53 in a state where they face each other at intervals along the radial direction R with respect to the third axis A3. The pair of pinion gears 54 are configured to be rotatable (rotating) about the pinion shaft 53 and rotating (revolving) about the third axis A3.

The first side gear 55 and the second side gear 56 are rotating elements after distribution of the driving force in the differential gear mechanism 5. The first side gear 55 and the second side gear 56 are arranged so as to face each other with the pinion shaft 53 interposed therebetween at intervals in the axial direction L. The first side gear 55 is arranged on the first side L1 in the axial direction with respect to the second side gear 56. The first side gear 55 and the second side gear 56 are configured to rotate in the circumferential direction in the internal space of the differential case 52, respectively. The first side gear 55 and the second side gear 56 mesh with a pair of pinion gears 54. The first side gear 55 is connected so as to rotate integrally with the first output member 61. On the other hand, the second side gear 56 is connected so as to rotate integrally with the second output member 62.

Each of the first output member 61 and the second output member 62 is drive-connected to the wheel W. Each of the first output member 61 and the second output member 62 transmits the driving force distributed by the differential gear mechanism 5 to the wheel W.

In the present embodiment, the first output member 61 includes the first axle 611 and the relay member 612. Each of the first axle 611 and the relay member 612 is a rotating member that rotates around the third axle A3. The first axle 611 is drive-connected to the wheel W on the first side L1 in the axial direction. The relay member 612 is a shaft member extending in the axial direction L. The relay member 612 is inserted into a through hole that penetrates the partition wall portion 24 of the case 2 in the axial direction L. The relay member 612 is rotatably supported with respect to the first side wall portion 22 of the case 2 via the output bearing B6.

The end portion of the relay member 612 on the first side L1 in the axial direction is exposed to the outside of the case 2 through a through hole penetrating the first side wall portion 22 of the case 2 in the axial direction L. The end of the relay member 612 on the first side L1 in the axial direction is connected so as to rotate integrally with the first axle 611. In the present embodiment, the relay member 612 is formed in a tubular shape in which the end surface of the first side L1 in the axial direction is open. Then, corresponding splines are formed on the inner peripheral surface of the relay member 612 and the outer peripheral surface of the end portion of the second side L2 in the axial direction of the first axle 611, and these splines engage with each other. As a result, the relay member 612 and the first axle 611 are connected so as to rotate integrally.

On the other hand, the end of the relay member 612 on the second side L2 in the axial direction is connected so as to rotate integrally with the first side gear 55 of the differential gear mechanism 5. In the present embodiment, corresponding splines are formed on the outer peripheral surface of the end portion of the second side L2 in the axial direction of the relay member 612 and the inner peripheral surface of the first side gear 55, and the splines are engaged with each other. By engaging, the relay member 612 and the first side gear 55 are connected so as to rotate integrally.

In the present embodiment, the second output member 62 includes the second axle 621. The second axle 621 is a rotating member that rotates around the third axle A3. The second axle 621 is drive-connected to the wheel W on the second side L2 in the axial direction. The second axle 621 is connected so as to rotate integrally with the second side gear 56. In the present embodiment, corresponding splines are formed on the outer peripheral surface of the end portion of the first side L1 in the axial direction of the second axle 621 and the inner peripheral surface of the second side gear 56, and the splines are formed on each other. By engaging, the second axle 621 and the second side gear 56 are connected so as to rotate integrally.

As shown in FIG. 1, the vehicle drive device 100 includes a hydraulic pump 7. The hydraulic pump 7 is a so-called mechanical hydraulic pump driven by a driving force transmitted through a power transmission path P connecting the rotary electric machine 1 and the pair of wheels W. The power transmission path P is configured to constantly transmit a driving force between the rotary electric machine 1 and the hydraulic pump 7. That is, an engaging device or the like for switching the transmission state of the driving force is not provided between the rotary electric machine 1 and the hydraulic pump 7 in the power transmission path P, and the hydraulic pump 7 is always interlocked with the rotary electric machine 1. There is.

As shown in FIG. 4, in the present embodiment, the hydraulic pump 7 includes a pump input gear 71, a pump drive shaft 72, an inner rotor 73 and an outer rotor 74 as a pump rotor, a pump cover 75 as a pump case, and a pump housing. It has 78 and. In this example, the hydraulic pump 7 is configured as an internal gear pump (for example, a trochoidal pump).

The pump input gear 71 is an input element of the hydraulic pump 7. The pump input gear 71 meshes with a pump drive gear 57 provided so as to rotate integrally with the differential input gear 51 of the differential gear mechanism 5. In the present embodiment, the pump drive gear 57 is connected to the differential case 52 so as to rotate integrally.

The pump drive shaft 72 is connected so as to rotate integrally with the pump input gear 71. In the present embodiment, the pump input gear 71 is arranged at the end of the second side L2 in the axial direction of the pump drive shaft 72. The inner rotor 73 is connected so as to rotate integrally with the pump drive shaft 72. In the present embodiment, the inner rotor 73 is connected to the end of the pump drive shaft 72 on the first side L1 in the axial direction. The outer rotor 74 is arranged so as to surround the outer side in the radial direction R with respect to the inner rotor 73. In the present embodiment, the pump drive shaft 72, the inner rotor 73, and the outer rotor 74 correspond to the “rotating member RT” of the hydraulic pump 7. Further, in the present embodiment, the pump drive shaft 72 is arranged along the rotation axis of the inner rotor 73 and the outer rotor 74 as the pump rotor, and rotates integrally with the inner rotor 73 which is a part of the pump rotor. Is connected to.

The internal teeth formed on the inner peripheral surface of the outer rotor 74 mesh with the external teeth formed on the outer peripheral surface of the inner rotor 73, and the outer rotor 74 rotates as the inner rotor 73 rotates. The space sandwiched between the outer teeth of the inner rotor 73 and the inner teeth of the outer rotor 74 is the pump chamber 79. That is, the rotation axes of the inner rotor 73 and the outer rotor 74 are eccentric, and the radial distance R of the space sandwiched between the outer teeth of the inner rotor 73 and the inner teeth of the outer rotor 74 depends on the position in the circumferential direction. It's different. Therefore, the space sandwiched between the outer teeth of the inner rotor 73 and the inner teeth of the outer rotor 74 is, when viewed at each position in the circumferential direction, after the interval in the radial direction R gradually increases due to the rotation of the inner rotor 73 and the outer rotor 74. It changes so that it gradually shrinks. As a result, the space sandwiched between the outer teeth of the inner rotor 73 and the inner teeth of the outer rotor 74 becomes a pump chamber 79 whose volume changes due to the rotation of the inner rotor 73 and the outer rotor 74.

The pump cover 75 and the pump housing 78 as the pump case are provided so as to cover the inner rotor 73 and the outer rotor 74. In the present embodiment, the pump housing 78 is formed with a columnar recess for accommodating the inner rotor 73 and the outer rotor 74. The pump cover 75 is arranged so as to cover the opening portion of the recess of the pump housing 78. Further, the pump cover 75 is fixed to the pump housing 78 by using a fastening member such as a bolt. The space surrounded by the pump housing 78 and the pump cover 75 serves as a pump rotor accommodating chamber in which the inner rotor 73 and the outer rotor 74 are accommodated. The suction port and the discharge port of the hydraulic pump 7 are formed so as to open into the pump rotor accommodating chamber and communicate with the pump chamber 79. The inner surfaces of the pump housing 78 and the pump cover 75 formed so as to surround the pump rotor accommodating chamber correspond to the "inner surface of the pump case". In this embodiment, the pump housing 78 is integrally formed with the case 2.

The hydraulic pump 7 includes a pump shaft support portion 75A that supports the outer peripheral surface of the pump drive shaft 72 from the outside in the radial direction R. In the present embodiment, the pump shaft support portion 75A is provided on the pump cover 75. Specifically, the pump cover 75 includes a tubular portion arranged so as to surround the outside of the pump drive shaft 72 in the radial direction R, and the tubular portion serves as a pump shaft support portion 75A. .. The inner peripheral surface of the pump shaft support portion 75A faces the outer peripheral surface of the pump drive shaft 72 with a gap in the radial direction R. As a result, the pump shaft support portion 75A rotatably supports the outer peripheral surface of the pump drive shaft 72 from the outside in the radial direction R. In other words, the pump shaft support portion 75A is provided with a through hole that penetrates the pump cover 75 in the axial direction L, and the pump drive shaft 72 is inserted through the through hole.

Then, in the present embodiment, the shaft support gap 77, which is the gap between the outer peripheral surface of the pump drive shaft 72 and the pump shaft support portion 75A, communicates with the oil storage portion S. As will be described later, the pump drive shaft 72 is arranged below the oil level position OL of the oil storage unit S in the steady circulation state in which the circulation state of the oil F in the case 2 is in the steady state. .. Therefore, the pump drive shaft 72 is basically located in the oil F of the oil storage unit S. A gap through which the oil F can pass is also formed between the pump input gear 71 and the pump shaft support portion 75A in the axial direction L. Therefore, the shaft support gap 77 communicates with the oil storage portion S via a gap in the axial direction L between the pump input gear 71 and the pump shaft support portion 75A. Therefore, the oil F of the oil storage portion S is always supplied to the shaft support gap 77. As a result, the shaft support gap 77 of the pump drive shaft 72, which requires the most lubrication among the hydraulic pumps 7, can be appropriately lubricated.

Further, in the present embodiment, the gap between the inner rotor 73 and the outer rotor 74 and the inner surfaces of the pump cover 75 and the pump housing 78 is set as the rotor gap 80, and between the shaft support gap 77 and the pump chamber 79 in the rotor gap 80. A seal structure 76 is provided. As described above, the pump cover 75 and the pump housing 78 form a columnar pump rotor accommodating chamber for accommodating the inner rotor 73 and the outer rotor 74. Therefore, the rotor gap 80 is formed along substantially the entire inner surface surrounding the cylindrical pump rotor accommodating chamber. More specifically, the rotor gap 80 is formed along a portion formed along the surface of the inner rotor 73 and the outer rotor 74 on the first side L1 in the axial direction, and along the surface of the inner rotor 73 and the outer rotor 74 on the second side L2 in the axial direction. It has a portion formed by the outer rotor 74 and a portion formed along the outer peripheral surface of the outer rotor 74. Since the pump drive shaft 72 is arranged so as to project toward the inner rotor 73 and the outer rotor 74 on the second side L2 in the axial direction, the shaft support gap 77 is also arranged so as to project from the inner rotor 73 and the outer rotor 74 on the second side L2 in the axial direction. Is formed in. Further, the pump chamber 79 is arranged outside the pump drive shaft 72 in the radial direction R. Therefore, in the present embodiment, the seal structure 76 is radially R than the connecting portion with the shaft support gap 77 in the rotor gap 80 formed along the surface of the inner rotor 73 and the outer rotor 74 on the second side L2 in the axial direction. At the position of the radial direction R, which is outside of the pump chamber 79 and inside the radial direction R of the pump chamber 79, the pump chamber 79 is continuously provided over the entire circumferential direction. Here, the seal structure 76 can be, for example, a structure in which the gap interval (in this example, the interval in the axial direction L) is formed to be narrower than that of other portions. Alternatively, a member such as a seal ring may be separately arranged as the seal structure 76. Further, the seal structure 76 may be provided so as to be in close contact with at least one of the inner rotor 73 and the outer rotor 74 so that the rotor gap 80 becomes zero. By providing such a seal structure 76, it is possible to restrict the oil F that lubricates the shaft support gap 77 from reaching the pump chamber 79 through the rotor gap 80 while appropriately lubricating the shaft support gap 77. ..

When the rotary electric machine 1 rotates in the normal direction, the hydraulic pump 7 pumps up the oil F stored in the oil storage unit S (see FIG. 3) and supplies it to the oil passage 9. The oil passage 9 is connected to the discharge port of the hydraulic pump 7. In the present embodiment, the oil passage 9 includes a first lubricating oil passage 23a and a second lubricating oil passage 23b formed in the second side wall portion 23 of the case 2. The oil F supplied to the oil passage 9 flows to the lubrication target of the input member 3, the counter gear mechanism 4, the differential gear mechanism 5, and the like, and then is stored in the oil storage unit S again. In this way, the oil F circulates in the case 2 during the normal rotation of the rotary electric machine 1. Here, the forward rotation of the rotary electric machine 1 means that the rotor shaft 122 of the rotary electric machine 1 rotates in the direction of advancing the vehicle on which the vehicle drive device 100 is mounted.

On the other hand, when the rotary electric machine 1 reverses, the hydraulic pump 7 causes the oil F in the oil passage 9 to flow back to the oil storage unit S. Here, the reversal of the rotary electric machine 1 means that the rotor shaft 122 of the rotary electric machine 1 rotates in the direction in which the vehicle on which the vehicle drive device 100 is mounted is moved backward.

As shown in FIG. 3, the oil storage unit S is a space provided in the case 2 for storing the oil F. In the present embodiment, the oil storage portion S is a space surrounded by the inner surface of the lower portion of the case 2. Here, the entire portion of the internal space of the case 2 that may be below the oil level is referred to as the oil storage portion S. A strainer 8 is provided in the oil storage unit S. The strainer 8 is a filter that removes foreign substances contained in the oil F when the hydraulic pump 7 pumps the oil F stored in the oil storage unit S. The strainer 8 includes a suction port 81 for sucking the oil F stored in the oil storage unit S, a filter (not shown) for filtering the oil F sucked through the suction port 81, and the like.

The positional relationship of each element housed in Case 2 will be described below. In the following description, the vertical direction of the vehicle drive device 100 mounted on the vehicle is referred to as "vertical direction V". The upper position of the vertical direction V is represented by using "upper" such as upper and upper ends, and the lower position of the vertical direction V is "lower" such as lower and lower ends. Is expressed using.

As shown in FIG. 3, the hydraulic pump 7 is arranged so that at least a part of the rotating member RT is located in the oil storage portion S. In the illustrated example, the entire hydraulic pump 7 is located below the oil level position OL of the oil storage unit S. In the present embodiment, the oil level position OL is the height of the oil level of the oil storage unit S in the steady circulation state in which the circulation state of the oil F in the case 2 is a steady state. Here, the steady circulation state is a state in which the rotary electric machine 1 rotates in the normal direction and the hydraulic pump 7 is driven, and the oil level position OL is stable.

The height of the oil level of the oil storage unit S varies depending on the state of the vehicle drive device 100. Here, the lowest oil level height in this fluctuation range is the oil level position OL. By determining the position of the hydraulic pump 7 with reference to such an oil level position OL, at least a part of the rotating member RT of the hydraulic pump 7 is constantly brought into contact with the oil F stored in the oil storage unit S. Can be kept. It is preferable that the pump drive shaft 72 is arranged below the oil level position OL of the oil storage unit S. More specifically, at least the lower end of the pump drive shaft 72 is oil so that the oil F can be supplied to the inner rotor 73 and the outer rotor 74 covered by the pump cover 75 through the gap between the pump cover 75 and the pump drive shaft 72. It is preferable that it is arranged below the surface position OL. As a result, the pump drive shaft 72, which requires the most lubrication among the rotating members RT of the hydraulic pump 7, can be appropriately lubricated.

In the present embodiment, the hydraulic pump 7 is arranged at a position overlapping the differential input gear 51 of the differential gear mechanism 5 in the axial direction along the axial direction L of the first output member 61 and the second output member 62. ing. Here, regarding the arrangement of the two elements, "overlapping in a specific direction" means that the virtual straight line is 2 when the virtual straight line parallel to the line-of-sight direction is moved in each direction orthogonal to the virtual straight line. It means that there is at least a part of the area where both of the two elements intersect.

Further, in the present embodiment, as shown in FIG. 1, the hydraulic pump 7 is arranged so that the arrangement area of the hydraulic pump 7 in the axial direction L and the arrangement area of the rotary electric machine 1 in the axial direction L overlap. .. That is, the hydraulic pump 7 is arranged so that at least a part of the arrangement area of the hydraulic pump 7 in the axial direction L is included in the arrangement area of the rotary electric machine 1 in the axial direction L. In the illustrated example, a part of the hydraulic pump 7 is arranged on the second side L2 in the axial direction with respect to the rotary electric machine 1. Then, a part of the axial first side L1 in the axial direction L arrangement region of the hydraulic pump 7 is included in the axial direction L arrangement region of the rotary electric machine 1.

As shown in FIG. 3, in the present embodiment, the input member 3, the counter gear mechanism 4, and the differential gear mechanism 5 have the first axis A1 and the third axis in the horizontal direction in the axial view along the axial direction L. The second axis A2 is arranged so as to be located between the A3 and the second axis A2. Further, in the present embodiment, in the input member 3, the counter gear mechanism 4, and the differential gear mechanism 5, the first axis A1 is located between the second axis A2 and the third axis A3 in the vertical direction V. Is located in. In the illustrated example, the input member 3 and the counter gear mechanism 4 are arranged above the oil level position OL. The differential gear mechanism 5 is arranged so that the lower end of the differential input gear 51 is located below the oil level position OL. Further, in the illustrated example, the lower end of the pump drive gear 57 is also arranged so as to be located below the oil level position OL.

Further, in the present embodiment, the lower end of the stator 11 of the rotary electric machine 1 is located below the oil level position OL. As a result, the stator 11 can be cooled by the oil F stored in the oil storage unit S while the vehicle on which the vehicle drive device 100 is mounted is running. Further, in the present embodiment, the lower end of the rotor 12 of the rotary electric machine 1 is located above the oil level position OL. As a result, the agitation resistance of the oil F by the rotor 12 can be reduced while the vehicle on which the vehicle drive device 100 is mounted is running.

2. Second Embodiment In the following, the vehicle drive device 100 according to the second embodiment will be described with reference to FIG. In the present embodiment, the positional relationship of the counter gear mechanism 4 and the differential gear mechanism 5 in the vertical direction V is different from that of the first embodiment. Further, in the present embodiment, the connection mode of the hydraulic pump 7 is different from that of the first embodiment. Hereinafter, the differences from the first embodiment will be mainly described. The points not particularly described are the same as those in the first embodiment.

As shown in FIG. 5, in the present embodiment, the input member 3, the counter gear mechanism 4, and the differential gear mechanism 5 have a third axis between the first axis A1 and the second axis A2 in the vertical direction V. It is arranged so that A3 is located. That is, in the present embodiment, the axis of the counter gear mechanism 4 (second axis A2) is arranged below the axis of the differential gear mechanism 5 (third axis A3).

Further, in the present embodiment, the hydraulic pump 7 is located at a position that does not overlap with the differential input gear 51 of the differential gear mechanism 5 in the axial view along the axial direction L of the first output member 61 and the second output member 62. Have been placed. The hydraulic pump 7 is arranged so that the pump input gear 71 meshes with the first counter gear 42 of the counter gear mechanism 4. That is, in the present embodiment, the hydraulic pump 7 is driven by the rotation of the counter gear mechanism 4. Therefore, in this embodiment, the pump drive gear 57 is not provided.

3. 3. Other Embodiments (1) In the first embodiment, the pump drive gear provided so that the pump input gear 71 of the hydraulic pump 7 rotates integrally with the differential input gear 51 of the differential gear mechanism 5. The configuration that meshes with 57 has been described as an example. However, the configuration is not limited to such a configuration, and for example, the pump input gear 71 may be configured to mesh with the differential input gear 51 of the differential gear mechanism 5. In this configuration, the pump input gear 71 and the second counter gear 43 of the counter gear mechanism 4 are arranged so as to mesh with the differential input gear 51 at different positions in the circumferential direction of the differential input gear 51.

(2) In the second embodiment, the configuration in which the pump input gear 71 meshes with the first counter gear 42 of the counter gear mechanism 4 and the hydraulic pump 7 is driven by the rotation of the first counter gear 42 will be described as an example. did. However, without being limited to such a configuration, for example, the pump input gear 71 is provided so as to rotate integrally with the second counter gear 43 or the second counter gear 43 of the counter gear mechanism 4. It may mesh with the pump drive gear. Alternatively, the pump input gear 71 is not provided, the pump drive shaft 72 is connected so as to rotate integrally with the counter shaft 41 of the counter gear mechanism 4, and the hydraulic pump 7 is driven by the rotation of the counter shaft 41. Is also good.

(3) In the above embodiment, the configuration in which the oil storage portion S is formed by the inner surface of the case 2 has been described as an example. However, the oil storage portion S may be configured by, for example, a member different from the case 2 fixed to the inner surface of the case 2 without being limited to such a configuration.

(4) In the above embodiment, a configuration in which the arrangement area of the hydraulic pump 7 in the axial direction L and the arrangement area of the rotary electric machine 1 in the axial direction L overlap has been described as an example. However, the configuration is not limited to such a configuration, and the arrangement area of the hydraulic pump 7 in the axial direction L and the arrangement area of the rotary electric machine 1 in the axial direction L may not overlap. For example, the hydraulic pump 7 may be arranged on the second side L2 in the axial direction with respect to the differential input gear 51 of the differential gear mechanism 5.

(5) In the above embodiment, a configuration in which at least a part of the pump drive shaft 72 is arranged below the oil level position OL of the oil storage unit S has been described as an example. However, the present invention is not limited to such a configuration, and the entire pump drive shaft 72 may be arranged above the oil level position OL of the oil storage portion S. Even in this case, it is desirable that at least a part of the rotating member RT of the hydraulic pump 7 is arranged in the oil storage section S, specifically below the oil level position OL of the oil storage section S. ..

(6) In the above embodiment, the seal structure 76 between the shaft support gap 77 and the pump chamber 79 in the rotor gap 80, which is the gap between the inner rotor 73 and the outer rotor 74 and the inner surfaces of the pump cover 75 and the pump housing 78. The configuration in which is provided is described as an example. However, such a seal structure 76 is not essential, and the seal structure 76 may not be provided between the shaft support gap 77 in the rotor gap 80 and the pump chamber 79. Alternatively, a seal structure may be provided at another location in the rotor gap 80.

(7) In the above embodiment, an example in which the hydraulic pump 7 is configured as an inscribed gear pump has been described. However, the present invention is not limited to this, and the hydraulic pump 7 may be configured as another type of pump. For example, it may be configured as a vane pump or a circumscribed gear pump. For example, when the hydraulic pump 7 is a vane pump, one rotor provided with a vane is the pump rotor.

(8) In the above embodiment, an example in which the transmission mechanism T is a gear mechanism including an input gear 32 included in the input member 3, a counter gear mechanism 4, and a differential gear mechanism 5 has been described. However, the present invention is not limited to this, and as the transmission mechanism T, various types of mechanisms capable of transmitting power can be used. For example, it may be configured not to include either the counter gear mechanism 4 or the differential gear mechanism 5, or it may be configured to include a gear mechanism other than these. Further, a transmission mechanism other than the gear mechanism, for example, a transmission mechanism using a chain or a belt, or a transmission mechanism using a fluid may be provided.

(9) The configurations disclosed in each of the above-described embodiments can be applied in combination with the configurations disclosed in other embodiments as long as there is no contradiction. With respect to other configurations, the embodiments disclosed herein are merely exemplary in all respects. Therefore, various modifications can be made as appropriate without departing from the gist of the present disclosure.

4. Outline of the above-described embodiment The outline of the vehicle drive device (100) described above will be described below.

The vehicle drive device (100)
The rotating electric machine (1), which is the driving force source for the wheels (W),
With the input member (3) driven and connected to the rotary electric machine (1),
A pair of output members (61, 62) that are driven and connected to the wheel (W), respectively.
A transmission mechanism (T) that drives and connects the input member (3) and the pair of output members (61, 62), and
A case (2) accommodating the rotary electric machine (1) and the transmission mechanism (T), and
A hydraulic pump (7) driven by a driving force transmitted through a power transmission path (P) connecting the rotary electric machine (1) and the wheels (W) is provided.
The power transmission path (P) is configured to constantly transmit a driving force between the rotary electric machine (1) and the hydraulic pump (7).
An oil storage unit (S) for storing oil (F) is provided in the case (2).
At least a part of the rotating member (RT) of the hydraulic pump (7) is arranged in the oil storage portion (S).

According to this configuration, at least a part of the rotating member (RT) of the hydraulic pump (7) is in constant contact with the oil (F) stored in the oil storage unit (S). Therefore, the oil (F) stored in the oil storage unit (S) can be supplied to the rotating member (RT) of the pump regardless of the rotation direction of the rotary electric machine (1). Therefore, in a configuration in which the power transmission path (P) connecting the rotary electric machine (1) and the wheels (W) constantly transmits the driving force between the rotary electric machine (1) and the hydraulic pump (7), the rotary electric machine (1) ) Is not provided with an oil supply mechanism such as an oil passage for supplying oil (F) to the rotating member (RT) of the hydraulic pump (7) during the reversal of the hydraulic pump (7). Can be properly lubricated. That is, according to this configuration, in a configuration in which the hydraulic pump (7) is always linked with the rotary electric machine (1), the manufacturing cost of the vehicle drive device (100) is increased and the vehicle drive device (100) is large. The rotating member (RT) of the hydraulic pump (7) can be appropriately lubricated even during the reversal of the rotating electric machine (1) while suppressing the change.

Here, the rotating member (RT) is arranged along the rotation axis of the pump rotor (73, 74) and the pump rotor (73, 74), and the pump rotor (73, 74). A pump drive shaft (72) connected so as to rotate integrally is included, and the pump drive shaft (72) has a steady state of oil (F) circulation in the case (2). It is preferable that the oil storage portion (S) is arranged below the oil level position (OL) in the steady circulation state.

According to this configuration, the pump drive shaft (72) of the hydraulic pump (7) is basically located in the oil (F) of the oil storage unit (S). Therefore, it becomes easy to appropriately lubricate the pump drive shaft (72), which requires the most lubrication among the rotating members (RT) of the hydraulic pump (7).

Further, the rotating member (RT) is arranged along the rotation axis of the pump rotor (73, 74) and the pump rotor (73, 74) and is integrated with the pump rotor (73, 74). A pump drive shaft (72) connected so as to rotate in a radial manner is included, and the hydraulic pump (7) supports a pump shaft supporting the outer peripheral surface of the pump drive shaft (72) from the outside in the radial direction. A shaft support gap (77), which is further provided with a portion (75A) and is a gap between the outer peripheral surface of the pump drive shaft (72) and the pump shaft support portion (75A), communicates with the oil storage portion (S). It is preferable to do so.

According to this configuration, the oil (F) of the oil storage portion (S) can be easily applied to the shaft support gap (77), which is the gap between the outer peripheral surface of the pump drive shaft (72) and the pump shaft support portion (75A). Can be supplied. Therefore, the shaft support gap (77) of the pump drive shaft (72), which requires the most lubrication among the hydraulic pumps (7), can be appropriately lubricated.

Further, as described above, in the configuration in which the shaft support gap (77) communicates with the oil storage portion (S), the hydraulic pump (7) is a pump that covers the pump rotors (73, 74). A case (75, 78) is further provided, and a space where a volume change occurs due to rotation of the pump rotor (73, 74) is defined as a pump chamber (79), and the pump rotor (73, 74) and the pump case (75, 78) are provided. ) Is defined as a rotor gap (80), and a seal structure (76) is provided between the shaft support gap (77) and the pump chamber (79) in the rotor gap (80). Is suitable.

According to this configuration, the shaft support gap (77) is formed while appropriately lubricating the shaft support gap (77), which is the gap between the outer peripheral surface of the pump drive shaft (72) and the pump shaft support portion (75A). It is possible to regulate that the lubricating oil (F) reaches the pump chamber (79) through the rotor gap (80).

Further, the transmission mechanism (T) includes a first gear (32) included in the input member (3), a second gear (42) that meshes with the first gear (32), and the second gear (42). A counter gear mechanism (4) having a third gear (43) that rotates integrally with the third gear, and a fourth gear (51) that meshes with the third gear (43), and the rotation of the fourth gear (51). Is preferably provided with a differential gear mechanism (5) that distributes the power to the pair of output members (61, 62).

According to this configuration, the driving force of the rotary electric machine (1) can be appropriately transmitted to the pair of output members (61, 62).

Further, the hydraulic pump (7) overlaps with the fourth gear (51) of the differential gear mechanism (5) in an axial view along the axial direction (L) of the output members (61, 62). The hydraulic pump (7) is arranged so as to overlap the axial direction (L) arrangement area of the hydraulic pump (7) and the rotary electric machine (1) in the axial direction (L) arrangement area. Is suitable.

The fourth gear (51) is generally the portion of the differential gear mechanism (5) having the largest radial dimension (R). According to this configuration, the hydraulic pump (7) is arranged by utilizing the space overlapping the fourth gear (51) in the axial direction. As a result, it is possible to suppress the increase in size of the vehicle drive device (100) in the radial direction (R) due to the arrangement of the hydraulic pump (7).
Further, according to this configuration, the hydraulic pump (7) is arranged by utilizing the space where the arrangement area in the axial direction (L) overlaps with the rotary electric machine (1). As a result, it is possible to suppress the increase in size of the vehicle drive device (100) in the axial direction (L) due to the arrangement of the hydraulic pump (7).

Further, the hydraulic pump (7) includes a pump input gear (71) which is an input element of the hydraulic pump (7).
The pump input gear (71) is a pump drive gear (57) provided so as to rotate integrally with the fourth gear (51) of the differential gear mechanism (5) or the fourth gear (51). ) Is meshed with.

The differential gear mechanism (5) is generally arranged so that the lower end of the fourth gear (51) is located at the lower part of the case (2). Therefore, according to this configuration, the pump input gear (71) of the hydraulic pump (7) that meshes with the fourth gear (51) or the pump drive gear (57) that rotates integrally with the fourth gear (51). It becomes easy to arrange it in the lower part of the case (2). Therefore, at least a part of the rotating member (RT) of the hydraulic pump (7) is arranged in the oil storage portion (S) which is often arranged in the lower part of the case (2), and the rotary electric machine (1) It becomes easy to lubricate the rotating member (RT) of the hydraulic pump (7) during the reversal.

Further, the axis (A2) of the counter gear mechanism (4) is arranged below the axis (A3) of the differential gear mechanism (5).
It is preferable that the hydraulic pump (7) is driven by the rotation of the counter gear mechanism (4).

According to this configuration, the axis (A2) of the counter gear mechanism (4) is arranged below the axis (A3) of the differential gear mechanism (5). Therefore, the counter gear mechanism (4) is arranged at a relatively low position in the case (2). This makes it easy to dispose the hydraulic pump (7) driven by the rotation of the counter gear mechanism (4) at the lower part of the case (2). Therefore, at least a part of the rotating member (RT) of the hydraulic pump (7) is arranged in the oil storage portion (S) which is often arranged in the lower part of the case (2), and the rotary electric machine (1) It becomes easy to lubricate the rotating member (RT) of the hydraulic pump (7) during the reversal.

The technology according to the present disclosure includes a rotary electric machine which is a driving force source for wheels, a counter gear mechanism, a differential gear mechanism, a case for accommodating them, and a driving force transmitted through a power transmission path connecting the rotary electric machine and wheels. It can be used for a vehicle drive device equipped with a hydraulic pump driven by.

100: Vehicle drive device 1: Rotating electric machine 2: Case 3: Input member 32: Input gear (first gear)
4: Counter gear mechanism 42: 1st counter gear (2nd gear)
43: 2nd counter gear (3rd gear)
5: Differential gear mechanism 51: Differential input gear (4th gear)
61: 1st output member 62: 2nd output member 7: Hydraulic pump 71: Pump input gear 72: Pump drive shaft 73: Inner rotor (pump rotor)
74: Outer rotor (pump rotor)
75: Pump cover (pump case)
75A: Pump shaft support 76: Seal structure 77: Shaft support gap 78: Pump housing (pump case)
79: Pump chamber 80: Rotor gap F: Oil S: Oil storage unit T: Transmission mechanism RT: Rotating member W: Wheel P: Power transmission path

Claims

The rotating electric machine that is the driving force source for the wheels,
With the input member driven and connected to the rotary electric machine,
A pair of output members that are driven and connected to the wheels, respectively.
A transmission mechanism that drives and connects the input member and the pair of output members,
A case for accommodating the rotary electric machine and the transmission mechanism, and
A hydraulic pump driven by a driving force transmitted through a power transmission path connecting the rotary electric machine and the wheels is provided.
The power transmission path is configured to constantly transmit a driving force between the rotary electric machine and the hydraulic pump.
An oil storage unit for storing oil is provided in the case.
A vehicle drive device in which at least a part of a rotating member of the hydraulic pump is arranged in the oil storage unit.
The rotating member includes a pump rotor and a pump drive shaft that is arranged along the rotation axis of the pump rotor and is connected so as to rotate integrally with the pump rotor.
The pump drive shaft according to claim 1, wherein the pump drive shaft is arranged below the oil level position of the oil storage portion in the steady circulation state in which the oil circulation state in the case is a steady state. Vehicle drive device.
The rotating member includes a pump rotor and a pump drive shaft that is arranged along the rotation axis of the pump rotor and is connected so as to rotate integrally with the pump rotor.
The hydraulic pump further includes a pump shaft support portion that supports the outer peripheral surface of the pump drive shaft from the outside in the radial direction.
The vehicle drive device according to claim 1 or 2, wherein a shaft support gap, which is a gap between the outer peripheral surface of the pump drive shaft and the pump shaft support portion, communicates with the oil storage portion.
The hydraulic pump further includes a pump case that covers the pump rotor.
The space where the volume changes due to the rotation of the pump rotor is used as the pump chamber, and the gap between the pump rotor and the inner surface of the pump case is used as the rotor gap.
The vehicle drive device according to claim 3, wherein a seal structure is provided between the shaft support gap and the pump chamber in the rotor gap.
The transmission mechanism
The first gear included in the input member and
A counter gear mechanism having a second gear that meshes with the first gear and a third gear that rotates integrally with the second gear.
The present invention according to any one of claims 1 to 4, further comprising a fourth gear that meshes with the third gear and a differential gear mechanism that distributes the rotation of the fourth gear to the pair of output members. The vehicle drive device described.
The hydraulic pump is arranged so as to overlap the fourth gear of the differential gear mechanism in an axial view along the axial direction of the output member, and is arranged with the axial arrangement region of the hydraulic pump. The vehicle drive device according to claim 5, which is arranged so as to overlap with the axially arranged area of the rotary electric machine.
The hydraulic pump includes a pump input gear that is an input element of the hydraulic pump.
The vehicle according to claim 5 or 6, wherein the pump input gear meshes with the fourth gear of the differential gear mechanism or a pump drive gear provided so as to rotate integrally with the fourth gear. Drive device.
The axis of the counter gear mechanism is arranged below the axis of the differential gear mechanism.
The vehicle drive device according to claim 5 or 6, wherein the hydraulic pump is driven by rotation of the counter gear mechanism.