JP2023066891A - Vehicular driving device - Google Patents

Abstract

To make both supply of oil to a speed changer and supply of oil to a rotary electric machine compatible with each other.SOLUTION: A vehicular driving device is disclosed, comprising: a speed changer arranged on a power transmission path extending from an internal combustion engine at a front part of a vehicle to a rear wheel; a rotary electric machine arranged concentrically with a speed-change output member, at a side closer to the rear wheel than the speed changer in the power transmission path; a first oil passage passing on the inside in a radial direction in the speed changer, concentrically with the speed-change output member; a second oil passage passing on the inside in the radial direction in the rotary electric machine, concentrically with the speed-change output member; a mechanical first oil pump that suctions and discharges oil in an oil pan; a first supply oil passage including a valve body, whose one end is connected to a discharge-side of the first oil pump and whose other end is connected to the first oil passage; an electrically-driven second oil pump that suctions and discharges oil in the oil pan; and a second supply oil passage, provided independently from the first supply oil passage, whose one end is connected to a discharge-side of the second oil pump and whose other end is connected to the second oil passage, where the first oil passage and the second oil passage communicate with each other.SELECTED DRAWING: Figure 3

Description

TECHNICAL FIELD The present disclosure relates to a vehicle drive system.

In a vehicle drive system in which a rotating electric machine is arranged on the rear wheel side of a transmission in a power transmission path from an internal combustion engine provided in the front of a vehicle to wheels via a transmission, the rotating electric machine and the wheels in the power transmission path. A known technique eliminates the need to supply oil to the transmission during inertial running by arranging a clutch between the two.

Japanese Unexamined Patent Application Publication No. 2011-189798

However, in the conventional technology as described above, when the power of the internal combustion engine is being transmitted to the wheels or when the rotating electrical machine is operating, oil is supplied to the transmission and to the rotating electrical machine. It is difficult to efficiently combine

Accordingly, in one aspect, an object of the present disclosure is to efficiently achieve both the supply of oil to the transmission and the supply of oil to the rotating electric machine.

According to one aspect, a transmission arranged in a power transmission path from an internal combustion engine provided in a front portion of a vehicle to rear wheels of the vehicle, for shifting rotation transmitted from the internal combustion engine and transmitting the rotation to a transmission output member;
a rotating electrical machine provided coaxially with the transmission output member on the rear wheel side of the transmission in the power transmission path and including a stator and a rotor;
a housing member that forms a first space that houses the transmission and a second space that houses the rotating electric machine in a manner that is axially adjacent to the first space from a first side in the axial direction;
a first oil passage passing radially inwardly of the transmission coaxially with the shift output member;
a second oil passage passing radially inward of the rotating electric machine coaxially with the speed change output member;
a mechanical first oil pump that operates during operation of the internal combustion engine and sucks and discharges oil in an oil pan provided in the transmission;
a first supply oil passage including a valve body, one end of which is connected to the discharge side of the first oil pump and the other end of which is connected to the first oil passage;
an electric second oil pump that sucks and discharges oil in the oil pan for the transmission;
a second supply oil passage provided separately from the first supply oil passage, one end of which is connected to the discharge side of the second oil pump, and the other end of which is connected to the second oil passage;
A vehicle drive system is provided in which the first oil passage and the second oil passage communicate with each other.

In one aspect, according to the present disclosure, it is possible to efficiently achieve both the supply of oil to the transmission and the supply of oil to the rotating electric machine.

1 is a skeleton diagram showing an example of a vehicle drive system according to an embodiment; FIG. 1 is a cross-sectional view showing a simplified part of a vehicle drive system; FIG. 2 is an enlarged view of an axial portion including a rotating electrical machine in the entire axial direction of the vehicle drive device; FIG. 4 is an enlarged view of a Q1 portion of FIG. 3; FIG. 1 is a diagram schematically showing an entire oil passage configuration and an oil supply system in the vehicle drive system of the present embodiment; FIG. FIG. 2 is an explanatory diagram showing an example of the relationship between the running state of a vehicle to which the vehicle drive system of the present embodiment is applied and the oil supply state according to the temperature; FIG. 11 is a cross-sectional view showing only relevant parts of a vehicle drive system according to a modification;

Each embodiment will be described in detail below with reference to the accompanying drawings. Note that the dimensional ratios in the drawings are merely examples, and the present invention is not limited to these, and shapes and the like in the drawings may be partially exaggerated for convenience of explanation.

FIG. 1 is a skeleton diagram showing an example of a vehicle drive system 1 of this embodiment. FIG. 2 is a cross-sectional view showing a simplified part of the vehicle drive system 1. As shown in FIG. FIG. 3 is an enlarged view of an axial portion including the rotating electrical machine 6 in the entire axial direction of the vehicle drive device 1 .

The vehicle drive system 1 of this embodiment, at the skeleton diagram level as shown in FIG. It may be the same as the driving device.

The vehicle drive system 1 of this embodiment is different from the vehicle drive system disclosed in Japanese Unexamined Patent Application Publication No. 2021-114828 incorporated herein as described above, with the transmission 4 (however, the transmission output member 23 ), the torque converter 7, the input member 20, and the transfer 84 may be the same and will only be outlined herein.

In the following description, “axial direction L”, “radial direction R”, and “circumferential direction” are defined with reference to the rotation axis A ( FIG. 3 ) of the rotating electric machine 6, unless otherwise specified. . A rotor 60 included in the rotating electrical machine 6 and a rotating member arranged coaxially with the rotating electrical machine 6 rotate around the rotation axis A. As shown in FIG. One side in the axial direction L is defined as the "first axial side L1", and the other side in the axial direction L (opposite to the first axial side L1 in the axial direction L) is defined as the "second axial side L2". and Further, the outer side in the radial direction R is defined as "radial outer side R1", and the inner side in the radial direction R is defined as "radial inner side R2". The direction of each member in the following description represents the direction when they are assembled in the vehicle drive system 1 . It should be noted that terms relating to the dimensions, arrangement direction, arrangement position, etc. of each member are concepts that include the state of having differences due to errors (errors to the extent allowable in manufacturing).

Further, in the following description, the vertical direction V means the vertical direction when the vehicle driving device 1 is in use, that is, the vertical direction when the vehicle driving device 1 is arranged in the direction in which it is used. Since the vehicle drive system 1 is mounted on a vehicle and used, the vertical direction V is the vertical direction when the vehicle drive system 1 is mounted on the vehicle. It corresponds to the vertical direction when the vehicle is mounted on a vehicle and the vehicle stops on a flat road (a road along a horizontal plane). The upper side V1 and the lower side V2 mean the upper side and the lower side in the vertical direction V, respectively.

In this specification, 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 (synonymous with torque), and the two rotating elements are connected so as to rotate integrally. or a state in which the two rotating elements are connected to each other via one or more transmission members so as to be able to transmit driving force. Such transmission members include various members (for example, shafts, gear mechanisms, belts, chains, etc.) that transmit rotation at the same speed or at different speeds. The transmission member may include an engagement device (for example, a friction engagement device, a mesh type engagement device, etc.) that selectively transmits rotation and driving force.

Also, as used herein, the term "coupled" refers to a state in which two elements are directly connected. In this case, if the two elements are rotating elements, it is possible to transmit driving force between the two elements. When the two elements are rotating elements, a slight gap (play) in the rotational direction may be set between the two elements.

Also, in this specification, the term "rotary electric machine" is used as a concept including motors (electric motors), generators (generators), and motor generators that function as both motors and generators as necessary. Further, in this specification, regarding the arrangement of two members, "overlapping in a particular direction view" means that when a virtual straight line parallel to the line of sight is moved in each direction orthogonal to the virtual straight line, the virtual straight line It means that there is at least a part of the area where the straight line intersects both of the two members.

A vehicle drive system 1 is provided in a vehicle so as to form a power transmission path from an internal combustion engine 2 to wheels 3 . The internal combustion engine 2 is arranged in a housing space (engine compartment) in the front part of the vehicle.

The vehicle drive system 1 includes a transmission 4 , a rotating electric machine 6 , a case 40 , a transmission unit 82 and a transfer 84 .

The transmission 4 is drivingly connected to an input member 20 drivingly connected to the internal combustion engine 2 . The transmission 4 is housed in the first housing space S<b>1 of the case 40 .

The transmission 4 shifts the rotation transmitted from the input member 20 side and transmits it to the transmission output member 23 . Specifically, the transmission 4 shifts the rotation transmitted from the input member 20 side to the shift input member 22 via the torque converter 7 and transmits it to the shift output member 23 . The shift input member 22 is a member for inputting rotation to the transmission 4 from the input member 20 side, and the shift output member 23 is a member for outputting rotation from the transmission 4 to the transfer input member 27 side. is.

The transmission 4 is arranged on the second axial side L<b>2 with respect to the rotating electric machine 6 . The speed change output member 23 is arranged coaxially with the rotary electric machine 6 . Further, the shift input member 22 is arranged coaxially with the shift output member 23 on the second axial side L2 with respect to the shift output member 23, and the input member 20 is arranged on the second axial side with respect to the shift input member 22. L2 is arranged coaxially with the shift input member 22 .

In this embodiment, the shift output member 23 is coupled to the transmission 4 at the end on the second axial side L2, and coupled to the transfer input member 27 at the first end on the axial direction L1. The shift output member 23 extends in the axial direction L so as to extend beyond the rotating electric machine 6 to the first axial side L1. In this case, the speed change output member 23 is connected to the transmission 4 and the transfer input member 27 at both end portions exposed from the rotor shaft 25 outside in the axial direction L through the interior of the rotor shaft 25 . In another embodiment, the shift output member 23 has an end on the first axial side L1 that passes through the interior of the rotor shaft 25 and is exposed from the rotor shaft 25 on the first axial side L1. It may be coupled to the transfer input member 27 via an extending cylindrical (more specifically, cylindrical) connecting member.

More specifically, the shift output member 23 is arranged along the axial direction L in order from the axial second side L2 toward the axial first side L1. , a portion passing radially inwardly of the planetary gear mechanism 10 described later, a portion passing radially inwardly of the rotary electric machine 6 (i.e., a portion passing through the inside of the rotor shaft 25), and the transfer input member 27. and an end portion on the first axial side L1, which is in the form of a one-piece shaft member. According to such a shift output member 23, the number of parts can be reduced compared to the case where the transmission 4 and the transfer input member 27 are connected via a member of two or more pieces (see FIG. 7). Reduction of the length of the axial direction L of the drive device 1 can be aimed at.

The transmission 4 is configured to be able to change the gear ratio, which is the ratio of the rotation speed of the gear shift input member 22 to the rotation speed of the gear shift output member 23, stepwise or steplessly. and transmitted to the shift output member 23. In this embodiment, the transmission 4 includes a hydraulically driven gear shift engagement device that operates in accordance with the hydraulic pressure supplied from the hydraulic control device 8 (see FIG. 2). is changed according to the state of engagement of the gearshift engagement device.

The rotating electric machine 6 forms a driving force source for the wheels 3 together with the internal combustion engine 2 . Output torque of the rotating electric machine 6 is transmitted to the wheels 3 via the rotor shaft 25 . Therefore, the vehicle drive system 1 can transmit the output torque of one or both of the internal combustion engine 2 and the rotary electric machine 6 to the wheels 3 via the rotor shaft 25 to drive the vehicle. The rotating electric machine 6 is housed in the second housing space S2 of the case 40 .

The rotary electric machine 6 is arranged coaxially with the input member 20 , the shift input member 22 , and the shift output member 23 . The rotating electric machine 6 includes a rotor 60 radially inside R<b>2 with respect to the stator 61 . The stator 61 is fixed to the case 40 (here, a motor case portion 41 to be described later), and the rotor 60 is rotatably supported by the case 40 (here, the motor case portion 41 ) with respect to the stator 61 . The rotor 60 is arranged radially inward R<b>2 with respect to the stator 61 and overlaps the stator 61 when viewed in the radial direction R. The rotor 60 is connected to the rotor shaft 25 so as to rotate together with the rotor shaft 25 . As shown in FIG. 3, the rotor shaft 25 is formed in a tubular shape (more specifically, a cylindrical shape) extending in the axial direction L. As shown in FIG. Here, the rotor shaft 25 is arranged to penetrate the radial inner side R2 of the rotor 60 in the axial direction L, and the rotor 60 is fixed to the outer peripheral surface of the rotor shaft 25 .

The stator 61 includes a stator core 62 and coils 63 wound around the stator core 62 . The stator core 62 is formed in a cylindrical shape extending in the axial direction L. As shown in FIG. The stator 61 includes a first coil end portion 64A protruding from the stator core 62 to the axial first side L1, and a second coil end portion 64B protruding from the stator core 62 to the axial second side L2. A portion of the coil 63 protruding from the stator core 62 to the first side L1 in the axial direction forms a first coil end portion 64A, and a portion of the coil 63 protruding from the stator core 62 to the second side L2 in the axial direction forms a second coil end portion 64B. to form The first coil end portion 64A and the second coil end portion 64B may be molded with resin.

In this embodiment, the gear shift output member 23 is inserted through the interior of the rotor shaft 25 so as to extend in the axial direction L. As shown in FIG. Specifically, as shown in FIG. 3, the outer peripheral surface of the speed change output member 23 is formed to have a smaller diameter than the inner peripheral surface of the rotor shaft 25 in a section passing through the interior of the rotor shaft 25. 23 is radially inside R2 with respect to the rotor shaft 25 and extends in the axial direction L so as to overlap the rotor shaft 25 when viewed in the radial direction.

The transmission unit 82 is arranged within the second housing space S2 of the case 40 . The transmission unit 82 is arranged coaxially with the rotating electrical machine 6 between the transmission 4 and the rotating electrical machine 6 in the axial direction L. As shown in FIG. In this embodiment, the transmission unit 82 includes a speed reducer 83 that reduces the speed of the rotation transmitted from the rotating electric machine 6 and transmits it to the shift output member 23 . The rotation of the rotating electric machine 6 is reduced in accordance with the reduction ratio of the speed reducer 83 and transmitted to the shift output member 23 . In this embodiment, as an example, the transmission unit 82 does not include an engagement device that selectively couples the rotating electrical machine 6 and the speed change output member 23, and the rotating electrical machine 6 and the speed change output member 23 are always engaged. Rotate together.

In this embodiment, the speed reducer 83 includes the planetary gear mechanism 10 . The planetary gear mechanism 10 may be a single pinion type planetary gear mechanism that includes a sun gear 11, a ring gear 13, and a carrier 12 that rotatably supports a pinion gear 14 that meshes with both the sun gear 11 and the ring gear 13. Sun gear 11 is coupled to rotor shaft 25 so as to rotate integrally therewith. In this embodiment, as shown in FIG. 4, at the joint between the sun gear 11 and the rotor shaft 25, spline teeth formed on the inner peripheral surface of the sun gear 11 and spline teeth formed on the outer peripheral surface of the rotor shaft 25 are formed. The teeth are in spline engagement. Further, the carrier 12 is connected to the shift output member 23 so as to rotate together with the shift output member 23 . Also, in this embodiment, as shown in FIG. The formed spline teeth are in spline engagement. Also, the ring gear 13 is fixed to the case 40 (here, a support member 45 to be described later). Therefore, the rotation input from the rotating electric machine 6 to the sun gear 11 is decelerated according to the gear ratio of the planetary gear mechanism 10 and output from the carrier 12 to the shift output member 23 .

The transfer 84 is housed in the third housing space S3 of the case 40 . It is arranged on the first side L1 in the axial direction with respect to the rotating electric machine 6 . That is, the rotating electrical machine 6 is arranged between the transmission 4 and the transfer 84 in the axial direction L. As shown in FIG. In this embodiment, the vehicle drive device 1 is mounted on the vehicle such that the axial direction L extends along the longitudinal direction of the vehicle body and the second axial side L2 faces the front side of the vehicle body.

The transfer input member 27 is coupled to the end portion of the shift output member 23 on the first side L1 in the axial direction so as to rotate integrally with the shift output member 23 . In the example shown in FIG. 3, the shift output member 23 and the transfer input member 27 are composed of spline teeth formed on the outer peripheral surface of the end portion of the shift output member 23 on the first side L1 in the axial direction, and the transfer input member 27 are spline-fitted by meshing with the spline teeth formed on the inner peripheral surface of the portion on the second axial side L2.

The transfer 84 distributes the rotation transmitted from the rotary electric machine 6 side (in other words, from the shift output member 23 side) to the transfer input member 27 to the first connecting member 21A and the second connecting member 21B. That is, the transfer 84 includes a distribution portion 200 that distributes the rotation transmitted to the transfer input member 27 to the first connecting member 21A and the second connecting member 21B. The first connecting member 21A may be drivingly connected to the pair of left and right rear wheels 3A via the rear wheel differential gear mechanism 5A. Also, the second connecting member 21B may be connected to the front wheel differential gear mechanism 5B via, for example, a flexible coupling, a propeller shaft, or the like. The distribution unit 200 may include a mechanism not shown in FIG. 1 (center differential mechanism, limited differential mechanism, etc.).

In the example shown in FIG. 1, a part-time distribution section is employed as the distribution section 200 . That is, the distribution unit 200 shown in FIG. 1 has a two-wheel drive state in which only one of the rear wheels 3A and the front wheels 3B (here, only the rear wheels 3A) is driven, and a four-wheel drive state in which both the rear wheels 3A and the front wheels 3B are driven. and a wheel drive state. Specifically, the distribution section 200 shown in FIG. 1 includes a second sleeve member 201 that is movable in the axial direction L, and a winding transmission mechanism 202 . The winding transmission mechanism 202 includes a first rotating body 202A (for example, a sprocket), a second rotating body 202B (for example, a sprocket) arranged on a different axis from the first rotating body 202A, the first rotating body 202A and and a transmission member 202C (for example, a chain) that is wound around the second rotor 202B. In the example shown in FIG. 1, the rotation of the transfer input member 27 after shifting by the transmission section 100 having the transmission mechanism 102 is transmitted to the intermediate transfer member 28, and the distribution section 200 rotates the intermediate transfer member 28. It is distributed to the first connecting member 21A and the second connecting member 21B. In the example shown in FIG. 1, the intermediate transfer member 28 is coupled to rotate integrally with the first coupling member 21A.

Next, the configuration of the case 40 will be described with reference to FIG. 4 together with FIGS. 2 and 3. FIG. 4 is an enlarged view of the Q1 portion of FIG. 3. FIG.

The case 40 is adjacent to each other in the axial direction L, and includes the first accommodation space S1, the second accommodation space S2, and the third accommodation space described above in order from the second axial side L2 toward the first axial side L1. Form S3. In this embodiment, the case 40 includes a motor case portion 41 , an AT case portion 42 , a transfer case portion 43 , a cover member 46 and a support member 45 .

The motor case portion 41 supports the rotating electric machine 6 and the speed change output member 23 and also supports the transmission unit 82 . The motor case portion 41 forms all or most of the peripheral wall portion 50 . The motor case portion 41 further includes a wall portion including a side wall portion 51 and a tubular portion 52 . The side wall portion 51 extends around the rotation axis A along the circumferential direction. The side wall portion 51 extends over the entire circumferential direction around the rotation axis A. As shown in FIG. The cylindrical portion 52 is formed so as to continue from the radially inner side of the side wall portion 51 . Note that, as schematically shown in FIG. 2, a frame F, which is a frame member of the vehicle body, is arranged below the motor case portion 41 . That is, the vehicle drive device 1 is mounted on the vehicle body such that the motor case portion 41 is positioned above the frame F. As shown in FIG.

The AT case portion 42 supports the transmission 4 and the shift output member 23 . The AT case portion 42 includes an end wall portion 53 on the axial first side L1. The end wall portion 53 partitions in the axial direction L the first housing space S1 and the second housing space S2. The end wall portion 53 has a cylindrical portion 531 on the radially inner side R2. The tubular portion 531 may rotatably support the shift output member 23 via a bush, for example. The motor case portion 41 is joined to the first axial side L1 of the AT case portion 42 . For example, the AT case portion 42 is fixed to the motor case portion 41 using a fixing member 42A (here, a fastening bolt).

The transfer case portion 43 supports the transfer 84 . The transfer case portion 43 is joined to the first axial side L<b>1 of the motor case portion 41 . For example, the transfer case portion 43 is fixed to the motor case portion 41 using fixing members 43A (here, fastening bolts).

The cover member 46 is joined to the first axial side L1 of the motor case portion 41 at the radially inner side R2 of the transfer case portion 43 . The cover member 46 is fixed to the peripheral wall portion 50 or a member fixed to the peripheral wall portion 50 using a fixing member 44A (here, a fastening bolt). The cover member 46 has a side wall portion 461 and a tubular portion 462 . The side wall portion 461 faces the side wall portion 51 in the axial direction L and extends to the first side L1 in the axial direction of the side wall portion 51 . The side wall portion 461 and the tubular portion 462 of the cover member 46 are arranged between the side wall portion 51 and the tubular portion 52 in the axial direction L to form a space portion S11 on the axial first side L1 of the second accommodation space S2. to form The tubular portion 462 supports the second bearing 92 on the radial inner side R2.

The support member 45 is arranged on the second side L2 in the axial direction with respect to the rotating electrical machine 6 . The support member 45 is arranged between the rotating electric machine 6 and the end wall portion 53 in the axial direction L. As shown in FIG. In this embodiment, the support member 45 is provided on the motor case portion 41 . In this embodiment, the support member 45 is a separate member from the peripheral wall portion 50 (here, the portion of the motor case portion 41 surrounding the radially outer side R1 of the second accommodation space S2). , and is integrally connected to the peripheral wall portion 50. As shown in FIG. The support member 45 is fixed to the peripheral wall portion 50 or a member fixed to the peripheral wall portion 50 using a fixing member 44 (here, a fastening bolt).

In this embodiment, the rotating electric machine 6 is supported by the motor case portion 41 in the following manner. The stator core 62 is fixed to the motor case portion 41 using stator fixing members 67 (here, fastening bolts). Specifically, the stator core 62 includes, in addition to a main body portion having a cylindrical outer peripheral surface, protruding portions that protrude radially outward R1 from the main body portion at a plurality of locations (eg, three locations) in the circumferential direction. Then, the projecting portion is fixed to the motor case portion 41 using the stator fixing member 67 . Further, the rotor shaft 25 to which the rotor 60 is fixed is connected to the motor case portion 41 (specifically is supported by a support member 45). A through hole penetrating through the support member 45 in the axial direction L is formed in the center of the support member 45 in the radial direction R. It is arranged in the radial direction R with the surface. Further, the rotor shaft 25 is connected to the motor case portion 41 (specifically, the cylindrical portion) via a first bearing 91 (here, a ball bearing) arranged on the first side L1 in the axial direction with respect to the rotor 60. 52). The first bearing 91 is arranged between the inner peripheral surface of the tubular portion 52 and the outer peripheral surface of the rotor shaft 25 in the radial direction R.

Thus, in this embodiment, the first bearing 91 that supports the rotor shaft 25 is supported by the side wall portion 51 . Here, the first bearing 91 is supported by the side wall portion 51 via the cylindrical portion 52 . A second bearing 92 that supports the end of the transfer input member 27 on the axial second side L<b>2 is supported by the cover member 46 . Here, the second bearing 92 is supported by the side wall portion 461 via the tubular portion 462 . In this embodiment, the cover member 46 further supports a seal member 95 for partitioning the second accommodation space S2 and the third accommodation space S3 in an oil-tight manner. Here, the seal member 95 is supported by the side wall portion 461 via the cylindrical portion 462 . The second bearing 92 and the seal member 95 are arranged side by side in the axial direction L. As shown in FIG. Specifically, the seal member 95 is arranged on the first side L1 in the axial direction with respect to the second bearing 92 .

In this embodiment, the seal member 95 is arranged between the inner peripheral surface of the tubular portion 462 and the outer peripheral surface of the transfer input member 27 . The seal member 95 is provided so as to close the gap between the inner peripheral surface of the tubular portion 462 and the outer peripheral surface of the transfer input member 27 . As a result, the second accommodation space S2 and the third accommodation space S3 are partitioned in an oil-tight manner. By partitioning the second accommodation space S2 and the third accommodation space S3 in an oil-tight manner in this way, for example, while the oil in the case 40 is shared between the transmission 4 and the rotary electric machine 6, the transfer 84 It is possible to use different types of oil for .

The shift output member 23 is supported by the motor case portion 41 in the following manner. As described above, the shift output member 23 is arranged radially inward R<b>2 with respect to the rotor shaft 25 and overlaps the rotor shaft 25 when viewed in the radial direction. Although not shown, a bearing (for example, a bush) may be arranged between the outer peripheral surface of the shift output member 23 and the inner peripheral surface of the rotor shaft 25 in the radial direction R. Therefore, the shift output member 23 is supported by the motor case portion 41 via the rotor shaft 25 .

The transmission unit 82 (specifically, the planetary gear mechanism 10 forming the speed reducer 83) is supported by the motor case portion 41 in the following manner. As shown in FIG. 3, ring gear 13 is fixed to support member 45 . A bearing (here, a bush) may be arranged between the inner peripheral surface of the sun gear 11 and the outer peripheral surface of the shift output member 23 in the radial direction R. Further, the carrier 12 is spline-fitted to the shift output member 23 as described above. That is, as shown in FIG. 4, the carrier 12 is spline-fitted to the shift output member 23 in such a manner that the spline teeth formed on the inner peripheral surface mesh with the spline teeth formed on the outer peripheral surface of the shift output member 23. be done. Therefore, the carrier 12 is supported by the motor case portion 41 via the speed change output member 23 and the rotor shaft 25 . Thus, in this embodiment, the case 40 (specifically, the motor case portion 41) includes the support member 45 that supports the transmission unit 82. As shown in FIG.
Next, still referring to FIGS. 3 and 4, a portion of the oil passage configuration of the vehicle drive system 1 will be described.

The vehicle drive system 1 of this embodiment includes a first oil passage 71 and a second oil passage 72 .

The first oil passage 71 passes through the radially inner side R<b>2 of the transmission 4 in a manner extending coaxially with the shift output member 23 . FIG. 3 shows a portion of the first oil passage 71 on the axial first side L1 side. In this embodiment, the first oil passage 71 is formed in the shift output member 23 and the shift input member 22 .

Specifically, the shift output member 23 has a first axial space portion 231 extending in the axial direction L around the rotation axis A, and the first axial space portion 231 extends in the first oil passage 71. form part of Further, the shift input member 22 has an axial oil passage 221 extending in the axial direction L around the rotation axis A, and the axial oil passage 221 forms part of the first oil passage 71 .

The first axial center space portion 231 may have an oil hole 2310 (see FIG. 3) penetrating in the radial direction R, and when the shift output member 23 rotates, centrifugal force causes the oil to flow from the oil hole 2310 to the radially outer side R1. may be ejected into The first axial center space 231 may have another oil hole penetrating in the radial direction R, such as the oil hole 2310, at a position in the axial direction L according to the position of the component to be lubricated. A plurality of oil holes may be formed according to the component to be lubricated.

Similarly, the shaft center oil passage 221 may have an oil hole 2210 (see FIG. 3) penetrating in the radial direction R, and when the shift input member 22 rotates, centrifugal force causes oil to flow radially from the oil hole 2210. It may jet to the outside R1.

The second oil passage 72 passes through the radially inner side R2 of the rotary electric machine 6 in a manner extending coaxially with the shift output member 23 . FIG. 3 shows the entire second oil passage 72 . In this embodiment, the second oil passage 72 is formed in the shift output member 23 . Specifically, the shift output member 23 has a second axial space 232 extending in the axial direction L around the rotation axis A, and the second axial space 232 extends through the second oil passage 72 . Form. In this case, the second oil passage 72 also passes through the radial inner side R2 in the planetary gear mechanism 10 . The end portion of the second oil passage 72 on the second axial side L2 may be located on the second axial side L2 of the joint surface between the motor case portion 41 and the AT case portion 42 in the axial direction.

The second axial center space portion 232 may have oil holes 2320, 2321, and 2322 (see FIG. 3) penetrating in the radial direction R. When the shift output member 23 rotates, the oil flows through the oil holes 2320, 2321, and 2322 by centrifugal force. You may jet from 2321 and 2322 to radial direction outside R1. The oil holes 2320, 2321, and 2322 penetrating in the radial direction R may be formed at positions in the axial direction L corresponding to the positions in the axial direction L of the components to be lubricated/cooled. A plurality of them may be formed accordingly. In the example shown in FIG. 3 , the oil jetted radially outward R<b>1 from the oil hole 2320 is used to cool the rotor 60 . In this case, the oil jetted from the oil hole 2320 to the radially outer side R1 can cool the rotor 60 from the radially inner side R2 through the hollow interior of the rotor shaft 25 . In addition, the oil jetted from the oil hole 2321 to the radially outer side R1 is used for lubricating the third bearing 93, the planetary gear mechanism 10, and the like. As shown in FIGS. 3 and 4, the rotor shaft 25 may have an oil hole 250 extending in the radial direction R for guiding the oil from the oil hole 2321 to the third bearing 93 . In addition, the oil jetted from the oil hole 2322 to the radially outer side R1 is used for lubricating the second bearing 92 and the like.

The second axial center space 232 may further have an oil hole 2322 (see FIGS. 3 and 4) penetrating in the radial direction R. A case oil passage 7620 forming part of a second supply oil passage 762, which will be described later, is connected to the oil hole 2322 . In the illustrated example, the case oil passage 7620 is formed in the end wall portion 53 of the AT case portion 42 . Oil from case oil passage 7620 is introduced into second shaft center space 232 (second oil passage 72 ) via oil hole 2322 .

In this embodiment, the case oil passage 7620 has an inlet portion 7622 for oil discharged from a second oil pump 752, which will be described later, on the upper side of the AT case portion 42. The inlet portion 7622 is a cylindrical portion. It may be formed below 531 or at other circumferential positions. In either case, the case oil passage 7620 may be formed to extend radially inward R2 from the inlet portion 7622 toward the oil hole 2322 .

In this embodiment, the vehicle drive system 1 has a third oil passage 73 in addition to the first oil passage 71 and the second oil passage 72 .

The third oil passage 73 extends in the axial direction L above the rotary electric machine 6 . The third oil passage 73 is connected to the case oil passage 7620 at the end on the axial second side L2. Although the end portion of the third oil passage 73 on the axial first side L1 is closed in the example shown in FIG. 3, it may be opened or connected to another oil passage. In the example shown in FIG. 3, the third oil passage 73 includes a case oil passage 730 formed in the AT case portion 42 in the axial direction L and a case oil passage formed in the motor case portion 41 (support member 45). 731 and a hollow tubular member 732 . Tubular member 732 may have an oil hole 7320 (see FIG. 3) extending downward therethrough. The oil hole 7320 may be formed at a position in the axial direction L corresponding to each of the first coil end portion 64A and the second coil end portion 64B. In this case, the oil supplied from the case oil passage 7620 to the third oil passage 73 drops from the oil hole 7320 and is used to cool the first coil end portion 64A and the second coil end portion 64B.

In this embodiment, the first oil passage 71 and the second oil passage 72 communicate with each other. That is, the end portion of the first oil passage 71 on the first axial side L1 and the end portion of the second oil passage 72 on the second axial side L2 are adjacent to each other in the axial direction L, communicate with. In this embodiment, the communication passage 70 has a significantly smaller cross-sectional area (cross-sectional area when cut along a plane perpendicular to the axial direction L) than the first oil passage 71 and the second oil passage 72. ). That is, the shift output member 23 has the communicating passage 70 functioning as a throttle portion at the communicating position between the first oil passage 71 and the second oil passage 72 . In addition, in the example shown in FIG. 3, the communication path 70 extends in the axial direction L around the rotation axis A, but it may be formed so as to be offset with respect to the rotation axis A.

FIG. 5 is a diagram schematically showing an entire oil passage configuration and an oil supply system in the vehicle drive system 1 of this embodiment. Note that FIG. 5 also shows a control device CNT that controls the second oil pump 752, and the flow of control signals from the control device CNT is schematically indicated by a dotted line 500. As shown in FIG. Note that the control device CNT may be in the form of an ECU (Electronic Control Unit), and may be shared with a control device (not shown) that controls the vehicle drive device 1 .

The vehicle drive system 1 includes a mechanical first oil pump 751, a first oil supply passage 761, a second electric oil pump 752, and a second oil supply passage 762 as an oil supply system. .

The first oil pump 751 operates when the internal combustion engine 2 is running. That is, the first oil pump 751 operates in a manner interlocking with the rotating member during operation of the internal combustion engine 2 . Arrangement of the first oil pump 751 is arbitrary. For example, the first oil pump 751 may be arranged on the axial second side L2 of the transmission 4 and connected to the shift input member 22 via a transmission member (for example, a chain).

The first oil pump 751 sucks and discharges oil in an oil pan 400 provided in the transmission 4 during operation. Note that the oil pan 400 may be attached to the lower portion of the AT case portion 42 . Note that the first oil pump 751 may suck the oil in the oil pan 400 through the strainer 401 .

The first supply oil passage 761 includes the valve body 404 and has one end connected to the discharge side of the first oil pump 751 and the other end connected to the first oil passage 71 . In the example shown in FIG. 5 , the first supply oil passage 761 includes a valve body 404 , a check valve 405 and an oil cooler 406 in order in the oil flow direction from the discharge side of the first oil pump 751 . In this case, oil cooled by oil cooler 406 is introduced into first oil passage 71 .

The first supply oil passage 761 may be connected to any position in the axial direction of the first oil passage 71 . For example, as schematically shown in FIG. 5 , the first supply oil passage 761 may be connected to the second axial side L2 of the first oil passage 71 . Alternatively, the first supply oil passage 761 may be connected to the first axial side L<b>1 of the first oil passage 71 within the axial extension range of the first axial center space portion 231 in the shift output member 23 .

Second oil pump 752 sucks and discharges oil in oil pan 400 provided in transmission 4 during operation. That is, the second oil pump 752 sucks and discharges the same oil as the first oil pump 751 (the oil in the oil pan 400). Note that the second oil pump 752 may suck the oil in the oil pan 400 through the strainer 402 .

The second oil pump 752 may be arranged inside the AT case portion 42 or the oil pan 400 (that is, inside the first housing space S1), but preferably, as schematically shown in FIG. Alternatively, it is arranged outside the oil pan 400 . As a result, even when the rotary electric machine 6 and the transmission unit 82 are arranged between the existing transmission 4 and the transfer 84, the change of the transmission 4 can be minimized.

For example, the second oil pump 752 may be arranged inside the second accommodation space S2. In this case, the second oil pump 752 may be arranged using the space S12 (see FIG. 3) on the axial second side L2 and below the planetary gear mechanism 10 . In this case, it is possible to effectively use the space S12, which tends to be a dead space, and to minimize the length of the oil passage between the second oil pump 752 and the oil pan 400. can reduce the loss that occurs in Note that when the second oil pump 752 is arranged in the space S12, the case oil passage 7620 may be formed below the cylindrical portion 531 unlike the arrangement shown in FIG. In this case, the flow path length of case oil passage 7620 can be minimized, and the loss caused in case oil passage 7620 can be minimized.

The second supply oil passage 762 is provided separately from the first supply oil passage 761 . Therefore, second supply oil passage 762 does not include valve body 404 or oil cooler 406 . However, in a modified example, second supply oil passage 762 may include an oil cooler different from oil cooler 406 . The second supply oil passage 762 has one end connected to the discharge side of the second oil pump 752 and the other end connected to the second oil passage 72 . In this embodiment, the second supply oil passage 762 has the above-described case oil passage 7620 at the end connected to the second oil passage 72 .

The second supply oil passage 762 is preferably arranged on the second axial side L2 of the rotating electrical machine 6, and as shown in FIG. connected to path 72; As a result, the length of the oil passage of the second supply oil passage 762 from the oil pan 400 to the second oil passage 72 can be minimized, and the loss caused when the oil passage is long can be reduced. However, in a modified example, the second supply oil passage 762 may be connected to the second oil passage 72 on the first side L1 in the axial direction from the rotating electric machine 6 . In this case, an oil passage in the radial direction R like the case oil passage 7620 may be formed in the cover member 46 or the side wall portion 51 .

The second supply oil passage 762 may include a check valve 7624 as schematically shown in FIG. 5, or may have a branch passage to a relief valve 7626 or the like.

According to the overall oil passage configuration and the oil supply system, oil can be efficiently supplied to the transmission 4, the rotary electric machine 6, and the planetary gear mechanism 10 as follows.

During operation of the first oil pump 751 , the oil discharged from the first oil pump 751 is introduced into the first oil passage 71 via the first supply oil passage 761 . As described above, the oil introduced into the first oil passage 71 flows through the axial oil passage 221 of the shift input member 22 and the first axial space 231 of the shift output member 23, and flows through the oil hole in the radial direction R. (oil holes 2210, 2310, etc.) to the radially outer side R1. The oil ejected in this manner is used for lubricating various lubricating objects and cooling objects to be cooled in the transmission 4 as described above.

In this embodiment, part of the oil introduced into the first oil passage 71 can flow from the first oil passage 71 to the second oil passage 72 via the communication passage 70 . This is because the first oil passage 71 and the second oil passage 72 communicate with each other via the communication passage 70 as described above. Thus, the oil discharged from the first oil pump 751 can be used for lubrication of the planetary gear mechanism 10 and cooling of the rotating electric machine 6 through the first oil passage 71 and the second oil passage 72 .

During operation of the second oil pump 752 , the oil discharged from the second oil pump 752 is introduced into the second oil passage 72 via the second supply oil passage 762 . As described above, the oil introduced into the second oil passage 72 flows through the second axial space 232 of the shift output member 23 and passes through the oil holes (oil holes 2320, 2321, 2322) in the radial direction R. is ejected radially outward R1. The oil ejected in this manner is used for lubricating various objects to be lubricated and for cooling objects to be cooled in the planetary gear mechanism 10 and the rotary electric machine 6, as described above.

In this embodiment, part of the oil introduced into the second oil passage 72 can flow from the second oil passage 72 to the first oil passage 71 via the communication passage 70 . This is because the first oil passage 71 and the second oil passage 72 communicate with each other via the communication passage 70 as described above. Thus, the oil discharged from the second oil pump 752 can be used for lubricating various lubrication targets in the transmission 4 via the second oil passage 72 and the first oil passage 71 .

Further, when the second oil pump 752 operates, the oil discharged from the second oil pump 752 is introduced into the third oil passage 73 via the second supply oil passage 762 . The oil introduced into the third oil passage 73 is used for cooling the first coil end portion 64A and the second coil end portion 64B as described above.

As described above, according to this embodiment, two oil pumps, the first oil pump 751 and the second oil pump 752, can be used to effectively cool various objects to be lubricated and cooled.

In addition, in this embodiment, the first oil passage 71 and the second oil passage 72 communicate with each other through the communication passage 70. Therefore, the oil discharged from the first oil pump 751 causes the planetary gear mechanism 10 and the rotary electric machine 6 to move. In addition, the oil discharged from the second oil pump 752 can lubricate various lubrication targets in the transmission 4 .

In particular, according to the present embodiment, part of the oil discharged from the second oil pump 752 in the electric running state (that is, the running state in which the internal combustion engine 2 is stopped and the rotating electric machine 6 is the only drive source). can be supplied to the first oil passage 71 through the communication passage 70 . Here, since various gears and the like of the transmission 4 rotate (that is, co-rotation occurs) even in the electric running state, the oil supplied to the first oil passage 71 is useful. Therefore, according to the present embodiment, it is possible to secure necessary lubricating oil for the various gears of the transmission 4 even in the electric running state in which the first oil pump 751 is not operated.

By the way, the vehicle drive system 1 needs to operate normally even in a severe low-temperature environment such as a cold region. In such a low-temperature environment, when the oil temperature drops, the viscosity of the oil increases. Therefore, in the case of a configuration using an electric oil pump, it becomes necessary to increase the output of the electric oil pump in order to discharge such highly viscous oil. .

In this regard, in this embodiment, as described above, the oil discharged from the first oil pump 751 can lubricate various lubrication targets and cool the cooling targets in the planetary gear mechanism 10 and the rotary electric machine 6 . Therefore, it is possible to supply oil to the second oil passage 72 by the first oil pump 751 in a low temperature environment without requiring an excessively high output of the second oil pump 752, which is an electric oil pump. be able to.

For example, in this embodiment, when the oil temperature is lower than the threshold, the control device CNT may limit the operation of the second oil pump 752 until the oil temperature exceeds the threshold. In this case, the threshold value corresponds to the operating start temperature of the second oil pump 752 and may be adapted depending on the output of the second oil pump 752 . Lower thresholds require more power to dispense low viscosity oil. Therefore, in this embodiment, since the first oil pump 751 can supply oil to the second oil passage 72 even in a low temperature environment, the threshold can be set relatively high (for example, −10° C.). As a result, an increase in the output of the second oil pump 752 can be suppressed.

In this case, control device CNT may determine whether the oil temperature is lower than the threshold based on sensor information from oil temperature sensor 501 .

In this manner, according to the present embodiment, both the supply of oil to the transmission 4 and the supply of oil to the rotary electric machine 6 can be efficiently achieved.

FIG. 6 is an explanatory diagram showing an example of the relationship between the running state of the vehicle to which the vehicle drive system 1 of this embodiment is applied and the oil supply state according to the temperature.

In FIG. 6, the column 600 on the left side is a title column, the letters "HV" represent the hybrid running state (that is, the running state in which the combination of the internal combustion engine 2 and the rotary electric machine 6 is the driving source), and the letters "EV". represents an electric running state (that is, a running state in which the internal combustion engine 2 is in a stopped state and only the rotating electric machine 6 is the driving source). Also in the same heading, "REQ" stands for lubrication or cooling requirements.

In FIG. 6 , the hybrid running state “HV” corresponds to the oil supply state ST60 corresponding to the temperature (oil temperature, for example) along with the regions SC1 and SC2 related to the first oil passage 71 and the second oil passage 72, respectively. attached. In the supply state ST60, the horizontal axis represents the temperature, and the vertical axis schematically shows the distribution of the oil to the first oil passage 71 and the second oil passage 72 respectively. In this case, the hatched area “MOP” represents the distribution of oil discharged from the first oil pump 751 and the hatched area “E-OP” represents the distribution of oil discharged from the second oil pump 752 .

In FIG. 6, the operation start temperature of the second oil pump 752 is -10° C. as an example, but other temperatures may be used as appropriate.

In the case of the hybrid running state “HV”, until −10° C. where the second oil pump 752 is kept stopped, the oil supplied to each of the first oil passage 71 and the second oil passage 72 is 1 is covered by the oil discharged from the oil pump 751 . When the oil temperature reaches −10° C. or higher, the second oil pump 752 starts operating, and the discharge amount from the second oil pump 752 gradually increases as the temperature increases. Accordingly, the proportion of the oil supplied to the second oil passage 72 that is covered by the oil discharged from the first oil pump 751 gradually decreases. All of the oil supplied to the passage 72 is covered by the oil discharged from the first oil pump 751 .

Since the amount of oil discharged from the first oil pump 751 depends on the rotational speed of the internal combustion engine 2, etc., it is not necessary to strictly match the distribution shown in FIG. The flow of oil through the communication passage 70 is determined by the relationship between the amount of oil discharged from the first oil pump 751 and the amount of oil discharged from the second oil pump 752 . In the example shown in FIG. 6, the amount of oil discharged from the second oil pump 752 increases as the oil temperature rises. Based on sensor information, it may be increased as the temperature of coil 63 increases.

Thus, according to this embodiment, in the hybrid running state, when the temperature is lower than the operation start temperature of the second oil pump 752, only the oil discharged from the first oil pump 751 is used for various kinds of lubrication in the transmission 4. Lubrication of the target and lubrication of various lubrication targets of the planetary gear mechanism 10 can be covered. As a result, as described above, it is not necessary to increase the output of the second oil pump 752, which is required when the operation is possible at extremely low temperatures, and the cost of the second oil pump 752 can be reduced.

In FIG. 6, the electric drive state "EV" corresponds to areas SC1 and SC2 associated with the first oil passage 71 and the second oil passage 72, respectively, and an oil supply state ST61 corresponding to temperature (for example, oil temperature). attached. In the supply state ST61, the horizontal axis represents the same temperature as in the supply state ST60, and the vertical axis schematically shows the distribution of oil to the first oil passage 71 and the second oil passage 72 respectively. In this case, the hatched area "-" indicates that no oil is supplied, and the hatched area "E-OP" indicates the distribution of oil discharged from the second oil pump 752.

The electric running state "EV" does not form until -10°C. That is, the rotating electric machine 6 operates when the temperature exceeds -10° C., like the second oil pump 752 . In the electric running state “EV” which can be formed when the temperature exceeds −10° C., substantially all of the oil supplied to each of the first oil passage 71 and the second oil passage 72 is discharged from the second oil pump 752. It is covered with oil that is

Here, the lubrication or cooling requirement "REQ" in FIG. 6 will be explained. Areas SC1 and SC2 related to the first oil passage 71 and the second oil passage 72, respectively, are associated with the requirement "REQ". A required amount of oil for each object (for example, a required amount of oil per unit time) is associated. Regarding the necessary amount of oil, the horizontal axis takes the same temperature as the supply state ST60, and the vertical axis shows the same temperature.

Regarding the area SC1 (first oil passage 71), a hatched area 650 indicates the amount of oil required for lubricating objects such as various gears and bearings (not shown) of the transmission 4, and the required amount of oil is shown in FIG. , it increases relatively slowly with increasing temperature. A hatched area 651 indicates the amount of oil required for lubrication and cooling, which are various friction materials (not shown) of the transmission 4. The required amount of oil is compared with an increase in temperature as shown in FIG. gradually increase. A hatched area 652 represents the amount of oil required to be cooled by the oil cooler 406 .

Regarding the area SC2 (second oil passage 72), a hatched area 660 indicates the amount of oil required for lubricating objects such as various gears (e.g., the planetary gear mechanism 10) and bearings (e.g., third bearing 93) in the second housing space S2. , and the required amount of oil increases relatively gently as the temperature increases, as shown in FIG. A hatched area 662 indicates the required amount of oil for the object to be cooled, which is the rotating electric machine 6. As shown in FIG. 6, the required amount of oil increases relatively significantly as the temperature rises above -10°C. .

According to this embodiment, as described above, since the first oil passage 71 and the second oil passage 72 are provided via the communication passage 70, by adapting the configuration (resistance) of the constricted portion related to the communication passage 70, , the required amount of oil indicated by the requirement "REQ" can be efficiently supplied in a relatively sufficient amount.

Specifically, when the resistance (resistance to oil flow) in the communication passage 70 is excessively small, in a temperature range not exceeding −10° C., the second The amount of oil flowing out to the oil passage 72 tends to be excessive (excessive to the required amount of oil indicated by the hatched area 660). In this case, it may be necessary to increase the capacity of the first oil pump 751 in order to secure the necessary oil amount indicated by hatched areas 650 and 651 with the oil discharged from the first oil pump 751 .

On the other hand, if the resistance (resistance to oil flow) in the communication passage 70 is excessively high, then in the electric running state "EV" (and therefore in the temperature range exceeding -10°C), the oil is discharged from the second oil pump 752. Of the oil, the amount of oil supplied to the first oil passage 71 tends to be too small. Note that even in the electric running state "EV", as described above, the various gears of the transmission 4 rotate (that is, co-rotation occurs), so the supply of oil to the first oil passage 71 is useful. . Further, if the resistance (resistance to oil flow) in the communication passage 70 is excessively large, the second oil passage 72 out of the oil discharged from the first oil pump 751 in a temperature range not exceeding -10°C It is likely that the amount of oil that flows out to the duct is too small (too little relative to the required amount of oil indicated by hatched area 660). In this case, it may be necessary to increase the capacity of the first oil pump 751 in order to secure the required oil amount indicated by the hatched area 660 with the oil discharged from the first oil pump 751 .

On the other hand, according to the present embodiment, by optimizing the configuration (resistance) of the throttle portion related to the communication passage 70, the speed change is performed in a manner suitable for the required amount of oil as shown in the requirement "REQ". The supply of oil to the machine 4 and the supply of oil to the rotary electric machine 6 can be efficiently made compatible.

Next, a modified example will be described with reference to FIG. In FIG. 7, constituent elements that may be substantially similar to those of the embodiment described above are given the same reference numerals, and descriptions thereof are omitted.

FIG. 7 is a cross-sectional view showing only related parts of a vehicle drive system 1A according to a modification. The vehicle drive system 1A according to the modification is different from the above-described embodiment in which the shift output member 23 is in the form of one piece, in that the shift output member 23A and the output member 24 are in the form of two pieces. The spline teeth formed on the inner peripheral surface of the end of the output member 24 on the second axial side L2 and the spline teeth formed on the outer peripheral surface of the end on the first axial side L1 of the shift output member 23A. , spline engagement. The output member 24 is integrally coupled with the carrier 12 of the planetary gear mechanism 10 .

In this modification, the shaft center oil passage 240 of the output member 24 and the second shaft center space 232A of the shift output member 23A form a second oil passage 72A corresponding to the second oil passage 72 of the embodiment described above. can. Further, the first axial center space 231A of the shift output member 23A can form, together with the axial center oil passage 221 of the shift input member 22, a first oil passage 71A corresponding to the first oil passage 71 of the embodiment described above. In this case, the output member 24 may have an oil hole 2410A corresponding to the oil hole 2321 described above, and oil holes (not shown) corresponding to the oil holes 2320 and 2322 . Further, the shift output member 23A may have oil holes 2310A and 2322A corresponding to the oil holes 2310 and 2322, respectively.

This modification can also provide the same effects as the above-described embodiment.

In this modified example, the spline fitting portion between the shift output member 23A and the output member 24 is formed as shown in FIG. 7 when the shift output member 23A and the output member 24 have substantially the same outer diameter. It has a radial step portion 241 . The output member 24 of the speed reducer 83 needs to be strong enough to transmit the combination of the output from the speed change output member 23A and the output from the rotary electric machine 6 . Therefore, it is necessary to relatively increase the thickness (thickness in the axial direction L) of the radial step portion 241 of the spline fitting portion between the shift output member 23A and the output member 24 . As a result, the distance between the transmission 4 and the rotary electric machine 6 in the axial direction L tends to increase, and the length in the axial direction L of the vehicle drive device 1A tends to increase.

In contrast, in the present embodiment described above, the output member of the speed reducer 83 is realized as a one-piece shaft member by the speed change output member 23, as described above. This is advantageous in that such radial steps can be reduced or eliminated. That is, in the present embodiment described above, by moving the end position of the rotor shaft 25 on the second axial side L2 to the second axial side L2, the length of the vehicle drive device 1 in the axial direction L is increased. This modification is more advantageous than the present modification in that it is possible to reduce the load and improve the mountability of the vehicle drive system 1 on the vehicle.

Although each embodiment has been described in detail above, it is not limited to a specific embodiment, and various modifications and changes are possible within the scope described in the claims. It is also possible to combine all or more of the constituent elements of the above-described embodiments. Further, among the effects of each embodiment, the effects related to dependent claims are additional effects distinguished from generic concepts (independent claims).

Reference Signs List 1, 1A Vehicle drive device 2 Internal combustion engine 3A Rear wheel 4 Transmission 400 Oil pan 404 Valve body 23 Speed change output member 6 Rotating electric machine 60 Rotor 61 Stator 40 Case (accommodating member) 53 End wall portion (wall portion) 70 Series Passages (throttle portions) 71, 71A First oil passages 72, 72A Second oil passages 751 First oil pump 752 Second oil pump 761 First supply oil passage 762 Second supply oil passage 7620 Case oil passage (oil passage) CNT Control device S1 First accommodation space (first space) S2・・・Second accommodation space (Second space)

Claims (5)

a transmission arranged in a power transmission path from an internal combustion engine provided in a front portion of a vehicle to rear wheels of the vehicle, the transmission shifting rotation transmitted from the internal combustion engine and transmitting the rotation to a transmission output member;
a rotating electrical machine provided coaxially with the transmission output member on the rear wheel side of the transmission in the power transmission path and including a stator and a rotor;
a housing member that forms a first space that houses the transmission and a second space that houses the rotating electric machine in a manner that is axially adjacent to the first space from a first side in the axial direction;
a first oil passage passing radially inwardly of the transmission coaxially with the shift output member;
a second oil passage passing radially inward of the rotating electric machine coaxially with the speed change output member;
a mechanical first oil pump that operates during operation of the internal combustion engine and sucks and discharges oil in an oil pan provided in the transmission;
a first supply oil passage including a valve body, one end of which is connected to the discharge side of the first oil pump and the other end of which is connected to the first oil passage;
an electric second oil pump that sucks and discharges oil in the oil pan for the transmission;
a second supply oil passage provided separately from the first supply oil passage, one end of which is connected to the discharge side of the second oil pump, and the other end of which is connected to the second oil passage;
The vehicle drive device, wherein the first oil passage and the second oil passage communicate with each other. 2. The vehicle drive device according to claim 1, wherein said first oil passage and said second oil passage communicate with each other via a throttle portion. 3. The vehicle drive device according to claim 1, wherein said shift output member forms at least part of said first oil passage, at least part of said second oil passage, and said throttle portion. The housing member has a wall portion that partitions the first space and the second space in the axial direction,
The vehicle according to any one of claims 1 to 3, wherein the second supply oil passage includes an oil passage formed in the wall portion in a manner extending toward the second oil passage. drive. Further comprising a control device for controlling the second oil pump,
5. The vehicle according to any one of claims 1 to 4, wherein when the oil temperature is lower than the threshold, the control device limits the operation of the second oil pump until the oil temperature exceeds the threshold. Drive for.

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