Patent ID: 12214670

MODES FOR CARRYING OUT THE DISCLOSURE

Hereinafter, a vehicle drive device100according to an embodiment will be described with reference to the drawings. As shown inFIGS.1and2, the vehicle drive device100includes a first drive unit100A that drives first wheels W1, and a second drive unit100B that drives second wheels W2. In the present embodiment, the first wheels W1are front wheels of a vehicle, and the second wheels W2are rear wheels of the vehicle.

As shown inFIG.1, the first drive unit100A includes an input member I drivingly connected to an internal combustion engine EG of the vehicle, a first output member O1drivingly connected to the first wheels W1, a first rotary electric machine MG1, a first rotary electric machine drive gear DG1, a transmission mechanism T including a transmission engagement device CLt, a distribution differential gear mechanism SP, a first distribution output gear SG1, and a first engagement device CL1. In the present embodiment, the first drive unit100A further includes a second distribution output gear SG2, a first output differential gear mechanism DF1, and a second engagement device CL2.

In the present application, “drivingly connected” refers to a state in which two rotation elements are connected so that a driving force can be transmitted, and includes a state in which the two rotation elements are connected so as to rotate integrally or a state in which the two rotation elements are connected so as to be able to transmit a driving force via one, two, or more transmitting members. Such transmitting members include various members that transmit rotation at the same speed or at a shifted speed, such as a shaft, a gear mechanism, a belt, and a chain. The transmitting members may include an engagement device that selectively transmits rotation and driving force, such as a friction engagement device and an intermeshing engagement device.

The distribution differential gear mechanism SP, the first distribution output gear SG1, and the first engagement device CL1are disposed on a first axis X1serving as their rotation axes. In the present embodiment, the input member I, the second distribution output gear SG2, and the second engagement device CL2are also disposed on the first axis X1. The first rotary electric machine MG1and the first rotary electric machine drive gear DG1are disposed on a second axis X2different from the first axis X1. The transmission engagement device CLt is disposed on a third axis X3different from the first axis X1and the second axis X2. In the present embodiment, the first output member O1and the first output differential gear mechanism DF1are disposed on a fourth axis X4different from the first axis X1, the second axis X2, and the third axis X3.

As shown inFIG.2, in the present embodiment, the second drive unit100B includes a second output member O2drivingly connected to the second wheels W2, a second rotary electric machine MG2, a counter gear mechanism CG, and a second output differential gear mechanism DF2.

In the present embodiment, the second rotary electric machine MG2is disposed on a fifth axis X5serving as its rotation axis. The counter gear mechanism CG is disposed on a sixth axis X6different from the fifth axis X5. The second output member O2and the second output differential gear mechanism DF2are disposed on a seventh axis X7different from the fifth axis X5and the sixth axis X6.

In the following description, as shown inFIG.1, a direction parallel to the rotation axis (second axis X2) of the first rotary electric machine MG1will be referred to as “axial direction L” of the vehicle drive device100. The axial direction L includes a “first axial side L1” where the first rotary electric machine MG1is disposed with respect to the first rotary electric machine drive gear DG1, and a “second axial side L2” opposite to the first axial side L1. A direction orthogonal to the axes X1to X7will be referred to as “radial direction R” with respect to each axis. When it is not necessary to distinguish the axis to be used as a reference, or when the axis to be used as a reference is clear, the direction may be simply referred to as “radial direction R”. In this example, the axes X1to X7are parallel to each other.

As shown inFIGS.3and4, in the present embodiment, a part of the input member I, the distribution differential gear mechanism SP, the first distribution output gear SG1, the second distribution output gear SG2, the first engagement device CL1, the second engagement device CL2, the first rotary electric machine MG1, the first rotary electric machine drive gear DG1, the transmission mechanism T, the first output differential gear mechanism DF1, and the first output member O1are housed in a case9.

In the present embodiment, the case9includes a first side wall portion91and a second side wall portion92disposed on the second axial side L2of the first side wall portion91. The first side wall portion91and the second side wall portion92are formed so as to extend along the radial direction R. A housing space for housing the components of the vehicle drive device100is formed between the first side wall portion91and the second side wall portion92in the axial direction L.

As shown inFIG.3, in the present embodiment, the input member I is an input shaft1extending along the axial direction L. In the present embodiment, the input shaft1is disposed so as to pass through the distribution differential gear mechanism SP, the first distribution output gear SG1, the second distribution output gear SG2, the first engagement device CL1, and the second engagement device CL2in the axial direction L. The input shaft1is disposed so as to pass through the second side wall portion92in the axial direction L. As shown inFIG.1, the input shaft1is drivingly connected to an output shaft ES of the internal combustion engine EG via a damper device DP that damps fluctuation in transmitted torque. The internal combustion engine EG is a prime mover (gasoline engine, diesel engine, or the like) that is driven by combustion of fuel to take out driving force. The internal combustion engine EG functions as a driving force source for the first wheels W1.

The first rotary electric machine MG1functions as a driving force source for the first wheels W1. The first rotary electric machine MG1has a function as a motor (electric motor) that receives supply of electric power to generate driving force, and a function as a generator (electric power generator) that receives supply of driving force to generate electric power. Specifically, the first rotary electric machine MG1is electrically connected to a power storage device such as a battery or a capacitor so as to exchange electric power with the power storage device. The first rotary electric machine MG1generates a driving force by power running with electric power stored in the power storage device. The first rotary electric machine MG1generates electric power with a driving force of the internal combustion engine EG or a driving force transmitted from the first output member O1side to charge the power storage device.

As shown inFIG.3, the first rotary electric machine MG1includes a first stator ST1and a first rotor RT1supported so as to be rotatable relative to the first stator ST1. In the present embodiment, the first rotor RT1is disposed on an inner side in the radial direction R with respect to the first stator ST1.

The first stator ST1includes a stator core STC and coil end portions CE. The stator core STC is fixed to a non-rotating member (in this case, the case9). The coil end portion CE is a coil portion protruding in the axial direction L from the stator core STC. Specifically, a coil is wound around the stator core STC so as to protrude from the stator core STC to both sides in the axial direction L (first axial side L1and second axial side L2). Portions of the coil that protrude from the stator core STC to the first axial side L1and the second axial side L2correspond to the coil end portions CE.

The first rotor RT1includes a rotor core RTC supported so as to be rotatable relative to the first stator core STC1. Although illustration is omitted, permanent magnets are disposed in the rotor core RTC.

In the present embodiment, a first rotor shaft RS1extending along the axial direction L is connected to the first rotor RT1so as to rotate integrally with the first rotor RT1. The first rotor shaft RS1is rotatably supported by a first bearing B1and a second bearing B2. In the present embodiment, the first rotor shaft RS1is disposed so as to protrude from the rotor core RTC to the first axial side L1and the second axial side L2. A portion of the first rotor shaft RS1that protrudes from the rotor core RTC to the first axial side L1is rotatably supported by the first side wall portion91of the case9via the first bearing B1. A portion of the first rotor shaft RS1that protrudes from the rotor core RTC to the second axial side L2is rotatably supported by the second side wall portion92of the case9via the second bearing B2.

In the present embodiment, the first rotary electric machine drive gear DG1is connected to the first rotor shaft RS1so as to rotate integrally with the first rotor shaft RS1. In this example, the first rotary electric machine drive gear DG1is connected to the first rotor shaft RS1via a torque limiter TL. Therefore, in a normal state in which a torque equal to or smaller than a permissible transmission torque of the torque limiter TL acts on the first rotary electric machine drive gear DG1, the first rotary electric machine drive gear DG1and the first rotor shaft RS1are connected by the torque limiter TL. When a torque exceeding the permissible transmission torque of the torque limiter TL acts on the first rotary electric machine drive gear DG1, the connection between the first rotary electric machine drive gear DG1and the first rotor shaft RS1by the torque limiter TL is terminated. The first rotary electric machine drive gear DG1rotates relative to the first rotor shaft RS1, thereby limiting torque transmission between the first rotary electric machine drive gear DG1and the first rotor shaft RS1. In the example shown inFIG.3, the torque limiter TL has a multi-plate frictional configuration including a plurality of plate members arranged in the axial direction L.

The distribution differential gear mechanism SP includes a first rotation element E1drivingly connected to the input member I, a second rotation element E2drivingly connected to the transmission mechanism T, and a third rotation element E3drivingly connected to the first rotary electric machine drive gear DG1.

In the present embodiment, the distribution differential gear mechanism SP is a planetary gear mechanism including a sun gear S1, a carrier C1, and a ring gear R1. In this example, the distribution differential gear mechanism SP is a single-pinion planetary gear mechanism including the carrier C1that supports pinion gears P1, the sun gear S1that meshes with the pinion gears P1, and the ring gear R1that is disposed on an outer side in the radial direction R with respect to the sun gear S1and meshes with the pinion gears P1.

In the present embodiment, the first rotation element E1is the sun gear S1. The second rotation element E2is the carrier C1. The third rotation element E3is the ring gear R1. Therefore, the order of rotation speeds of the rotation elements of the distribution differential gear mechanism SP according to the present embodiment is the order of the first rotation element E1, the second rotation element E2, and the third rotation element E3. The “order of rotation speeds” means the order of rotation speeds of the rotation elements in a rotating state. The rotation speeds of the rotation elements change depending on the rotating state of the planetary gear mechanism, but the order of the rotation speeds of the rotation elements is constant because it is determined by the structure of the planetary gear mechanism.

The first distribution output gear SG1is connected to the second rotation element E2so as to rotate integrally with the second rotation element E2. In the present embodiment, the first distribution output gear SG1is disposed on the first axial side L1of the carrier C1serving as the second rotation element E2.

The second distribution output gear SG2is connected to the third rotation element E3so as to rotate integrally with the third rotation element E3. In the present embodiment, the second distribution output gear SG2is formed on the outer peripheral surface of a tubular gear forming member2with its axis on the first axis X1. The ring gear R1serving as the third rotation element E3is formed on the inner peripheral surface of the gear forming member2.

In the present embodiment, the second distribution output gear SG2is disposed on the outer side in the radial direction R with respect to the ring gear R1. The second distribution output gear SG2is disposed so as to overlap the ring gear R1in a radial view along the radial direction R. Regarding the disposition of two elements, the phrase “overlap when viewed in a specific direction” means that, when a virtual straight line parallel to the line-of-sight direction is moved in directions orthogonal to the virtual straight line, an area where the virtual straight line intersects both the two elements is present at least in part.

In the present embodiment, the second distribution output gear SG2is drivingly connected to the first rotary electric machine drive gear DG1via an idler gear IG. That is, the second distribution output gear SG2and the first rotary electric machine drive gear DG1mesh with the idler gear IG at different positions in a circumferential direction. The idler gear IG is disposed on an axis different from the first axis X1to the seventh axis X7. In the present embodiment, the idler gear IG is rotatably supported, via a sixth bearing B6, by a protrusion921formed so as to protrude from the second side wall portion92of the case9to the first axial side L1. In the present embodiment, the sixth bearing B6is supported by the protrusion921from the inner side in the radial direction R. The sixth bearing B6rotatably supports the idler gear IG from the inner side in the radial direction R. In the example shown inFIG.3, a pair of sixth bearings B6is disposed to adjoin each other in the axial direction L.

In the present embodiment, the first distribution output gear SG1and the gear forming member2on which the second distribution output gear SG2is formed are rotatably supported by a support wall portion93of the case9. In the present embodiment, the support wall portion93includes a first tubular portion931having a tubular shape and disposed on the inner side in the radial direction R with respect to the first distribution output gear SG1, and a second tubular portion932having a tubular shape and disposed on the outer side in the radial direction R with respect to the first distribution output gear SG1. The first distribution output gear SG1is rotatably supported by the first tubular portion931via a third bearing B3. The gear forming member2is rotatably supported by the first tubular portion931via a fourth bearing B4.

In the present embodiment, the third bearing B3is supported by the first tubular portion931from the inner side in the radial direction R. The third bearing B3rotatably supports the first distribution output gear SG1from the inner side in the radial direction R. In the example shown inFIG.3, a pair of third bearings B3is disposed to adjoin each other in the axial direction L. In the present embodiment, the fourth bearing B4is supported by the second tubular portion932from the outer side in the radial direction R. The fourth bearing B4rotatably supports the gear forming member2from the outer side in the radial direction R.

The transmission mechanism T transmits the rotation transmitted from the distribution differential gear mechanism SP to the first output member O1. In the present embodiment, the transmission mechanism T includes a first gear21, a second gear22, a transmission output gear23, and a transmission shaft24. The first gear21, the second gear22, the transmission output gear23, and the transmission shaft24are disposed on the third axis X3.

The first gear21meshes with the second distribution output gear SG2. The second gear22meshes with the first distribution output gear SG1. In the present embodiment, each of the first gear21and the second gear22is supported via a bearing so as to be rotatable relative to the transmission shaft24.

The transmission output gear23meshes with a first differential input gear31of the first output differential gear mechanism DF1(seeFIGS.1and4). In the present embodiment, the first differential input gear31corresponds to the first output member O1.

In the present embodiment, the transmission output gear23is connected to the transmission shaft24so as to rotate integrally with the transmission shaft24. In the example shown inFIG.3, the transmission output gear23is formed integrally with the transmission shaft24. In the present embodiment, the transmission output gear23is disposed on the second axial side L2of the first gear21and the second gear22.

The transmission shaft24is formed so as to extend along the axial direction L. In the present embodiment, the transmission shaft24is rotatably supported by a seventh bearing B7and an eighth bearing B8. In the present embodiment, the seventh bearing B7is supported by the first side wall portion91of the case9from the outer side in the radial direction R. The seventh bearing B7rotatably supports the end of the transmission shaft24on the first axial side L1from the outer side in the radial direction R. In the present embodiment, the eighth bearing B8is supported by the second side wall portion92of the case9from the outer side in the radial direction R. The eighth bearing B8rotatably supports the end of the transmission shaft24on the second axial side L2from the outer side in the radial direction R.

As shown inFIG.4, the first output differential gear mechanism DF1distributes the rotation of the first differential input gear31serving as the first output member O1to the pair of first wheels W1. In the present embodiment, the first output differential gear mechanism DF1further includes, in addition to the first differential input gear31, a first differential case32, a pair of first pinion gears33, and a pair of first side gears34. Both the pair of first pinion gears33and the pair of first side gears34are bevel gears.

The first differential case32is connected to the first differential input gear31so as to rotate integrally with the first differential input gear31. In the present embodiment, the first differential case32is rotatably supported by a ninth bearing B9and a tenth bearing B10. In the present embodiment, the ninth bearing B9is supported by the first side wall portion91of the case9from the outer side in the radial direction R. The ninth bearing B9rotatably supports the end of the first differential case32on the first axial side L1from the outer side in the radial direction R. In the present embodiment, the tenth bearing B10is supported by the second side wall portion92of the case9from the outer side in the radial direction R. The tenth bearing B10rotatably supports the end of the first differential case32on the second axial side L2from the outer side in the radial direction R.

The first differential case32is a hollow member. The first differential case32houses the pair of first pinion gears33and the pair of first side gears34.

The pair of first pinion gears33is disposed so as to face each other with a distance along the radial direction R with respect to the fourth axis X4. The pair of first pinion gears33is attached to a first pinion shaft33asupported so as to rotate integrally with the first differential case32. The pair of first pinion gears33is rotatable (spinnable) about the first pinion shaft33aand rotatable (revolvable) about the fourth axis X4.

The pair of first side gears34is output elements of the first output differential gear mechanism DF1. The pair of first side gears34is disposed so as to face each other across the first pinion shaft33awith a distance in the axial direction L. The pair of first side gears34meshes with the pair of first pinion gears33. First drive shafts DS1drivingly connected to the first wheels W1are connected to the pair of first side gears34so as to rotate integrally with the pair of first side gears34.

In the present embodiment, the disposition area of the first output differential gear mechanism DF1in the axial direction L overlaps the disposition areas of the first gear21, the second gear22, and the transmission engagement device CLt in the axial direction L. In the example shown inFIG.4, the disposition areas of the first gear21, the second gear22, and the transmission engagement device CLt in the axial direction L are within the disposition area of the first output differential gear mechanism DF1in the axial direction L. Specifically, the end on the first axial side L1for the second gear22positioned closest to the first axial side L1among the first gear21, the second gear22, and the transmission engagement device CLt is positioned on the second axial side L2of the end on the first axial side L1for the first differential case32of the first output differential gear mechanism DF1. The end on the second axial side L2for the first gear21positioned closest to the second axial side L2among the first gear21, the second gear22, and the transmission engagement device CLt is positioned on the first axial side L1of the end on the second axial side L2for the first differential case32of the first output differential gear mechanism DF1.

According to this configuration, the dimension of the vehicle drive device100in the axial direction L can be reduced compared to a configuration in which the disposition area of the first output differential gear mechanism DF1in the axial direction L does not overlap the disposition area of at least one of the first gear21, the second gear22, and the transmission engagement device CLt in the axial direction L.

As shown inFIG.3, the transmission engagement device CLt of the transmission mechanism T is an engagement device that switches the state of power transmission. In the present embodiment, the transmission engagement device CLt is an intermeshing engagement device (dog clutch) that selectively connects the first gear21or the second gear22to the transmission shaft24.

As described above, the first gear21and the second gear22are disposed coaxially, and the first distribution output gear SG1and the second distribution output gear SG2are disposed coaxially. In the present embodiment, the first gear21is formed to have a smaller diameter than the second gear22. The second distribution output gear SG2that meshes with the first gear21is formed to have a larger diameter than the first distribution output gear SG1that meshes with the second gear22. Therefore, in the present embodiment, the gear ratio of the second gear22to the first distribution output gear SG1is larger than the gear ratio of the first gear21to the second distribution output gear SG2.

In such a configuration, when the transmission engagement device CLt connects the second gear22to the transmission shaft24, a low speed that is a shift speed having a relatively large speed ratio is formed. When the transmission engagement device CLt connects the first gear21to the transmission shaft24, a high speed that is a shift speed having a relatively small speed ratio is formed. In the present embodiment, the transmission engagement device CLt is switchable to a neutral state in which neither of the shift speeds is formed. When the transmission engagement device CLt is in the neutral state, the transmission mechanism T does not transmit the rotation between the distribution differential gear mechanism SP and the first output member O1.

Thus, in the present embodiment, the transmission mechanism T is structured as a parallel-shaft gear transmission including the second distribution output gear SG2and the first gear21that mesh with each other, and the first distribution output gear SG1and the second gear22that mesh with each other.

In the present embodiment, the transmission engagement device CLt is disposed between the first gear21and the second gear22in the axial direction L. The transmission engagement device CLt includes a support member41, a switching member42, a first engaged portion43, and a second engaged portion44.

The support member41is formed so as to protrude outward in the radial direction R from the transmission shaft24. The support member41is connected to the transmission shaft24so as to rotate integrally with the transmission shaft24. In the example shown inFIG.3, the support member41is connected to the transmission shaft24by spline engagement.

The switching member42is formed in a tubular shape covering an outer side of the support member41in the radial direction R. An engaging portion42ahaving a plurality of internal teeth is formed on the inner peripheral portion of the switching member42, and a plurality of external teeth mating with the internal teeth is formed on the outer peripheral portion of the support member41. These internal and external teeth are engaged so as to be relatively movable in the axial direction L and not to be relatively rotatable in the circumferential direction. Thus, the switching member42is supported so as to rotate integrally with the support member41and to move relative to the support member41in the axial direction L. That is, the switching member42is a sleeve of the intermeshing engagement device (dog clutch).

The first engaged portion43is connected to the first gear21so as to rotate integrally with the first gear21. The first engaged portion43is disposed on the second axial side L2of the support member41. The first engaged portion43is formed in a tubular shape with its axis on the third axis X3. A plurality of external teeth engageable with the plurality of internal teeth of the engaging portion42aof the switching member42so as to be relatively movable in the axial direction L and not to be relatively rotatable in the circumferential direction is formed on the outer peripheral portion of the first engaged portion43.

The second engaged portion44is connected to the second gear22so as to rotate integrally with the second gear22. The second engaged portion44is disposed on the first axial side L1of the support member41. The second engaged portion44is formed in a tubular shape with its axis on the third axis X3. A plurality of external teeth engageable with the plurality of internal teeth of the engaging portion42aof the switching member42so as to be relatively movable in the axial direction L and not to be relatively rotatable in the circumferential direction is formed on the outer peripheral portion of the second engaged portion44.

When the switching member42moves to the first axial side L1relative to the support member41and the internal teeth of the engaging portion42aand the external teeth of the second engaged portion44are engaged with each other, the second gear22is connected to the transmission shaft24, that is, the low speed described above is formed. When the switching member42moves to the second axial side L2relative to the support member41and the internal teeth of the engaging portion42aand the external teeth of the first engaged portion43are engaged with each other, the first gear21is connected to the transmission shaft24, that is, the high speed described above is formed. When the internal teeth of the engaging portion42aare engaged with neither the external teeth of the first engaged portion43nor the external teeth of the second engaged portion44, neither the first gear21nor the second gear22is connected to the transmission shaft24, that is, the neutral state described above is achieved.

The first engagement device CL1is a “disconnection engagement device” that connects or disconnects power transmission between the input member I and the first rotation element E1of the distribution differential gear mechanism SP. In the present embodiment, the first engagement device CL1is disposed on the first axial side L1of the first distribution output gear SG1. In the present embodiment, the first distribution output gear SG1is disposed on the first axial side L1of the distribution differential gear mechanism SP. Thus, the distribution differential gear mechanism SP is disposed on the second axial side L2of the first distribution output gear SG1and the first engagement device CL1.

In the present embodiment, the first engagement device CL1includes a friction member51and a piston52that presses the friction member51.

The friction member51includes a plurality of inner friction members supported by a first support member53from the inner side in the radial direction R, and a plurality of outer friction members supported by a second support member54from the outer side in the radial direction R. The inner friction members and the outer friction members are disposed alternately in the axial direction L.

In the present embodiment, the first support member53is connected to the sun gear S1of the distribution differential gear mechanism SP so as to rotate integrally with the sun gear S1. In the example shown inFIG.3, the first support member53is connected to the sun gear S1via a tubular connecting member20disposed between the first tubular portion931of the support wall portion93of the case9and the input shaft1in the radial direction R so as to pass through the first tubular portion931in the axial direction L. The first support member53is formed so as to extend outward in the radial direction R from the connecting member20and further extend to the first axial side L1. A portion of the first support member53that extends to the first axial side L1supports the inner friction members of the friction member51from the inner side in the radial direction R.

In the present embodiment, the second support member54is connected to the input shaft1so as to rotate integrally with the input shaft1. In the example shown inFIG.3, the second support member54is formed so as to extend outward in the radial direction R from a portion of the input shaft1on the first axial side L1of the connection portion between the first support member53and the connecting member20, further extend to the first axial side L1, further extend outward in the radial direction R, and further extend to the second axial side L2. A portion of the second support member54that extends to the second axial side L2supports the outer friction members of the friction member51from the outer side in the radial direction R.

The piston52is urged to the first axial side L1by an urging member52asuch as a spring. When the piston52is pressed from the first axial side L1against an urging force of the urging member52a, the piston52slides to the second axial side L2and presses the friction member51.

In the present embodiment, the piston52is disposed so as to overlap the friction member51in the radial view along the radial direction R. In the example shown inFIG.3, the piston52includes a sliding portion521that slides in the axial direction L in a cylinder portion formed by the input shaft1, a portion of the second support member54that extends outward in the radial direction R from the input shaft1, and a portion that extends to the first axial side L1from the end of that portion on the outer side in the radial direction R. The sliding portion521overlaps the friction member51in the radial view along the radial direction R.

According to this configuration, the dimension of the vehicle drive device100in the axial direction L can be reduced compared to a configuration in which the piston52does not overlap the friction member51in the radial view.

The second engagement device CL2connects or disconnects power transmission between two elements selected from among the three rotation elements that are the first rotation element E1, the second rotation element E2, and the third rotation element E3of the distribution differential gear mechanism SP. In the present embodiment, the second engagement device CL2connects or disconnects power transmission between the carrier C1serving as the second rotation element E2and the ring gear R1serving as the third rotation element E3. In the present embodiment, the second engagement device CL2is an intermeshing engagement device (dog clutch) including a support member61, a switching member62, and an engaged portion63. In the present embodiment, the disposition area of the second engagement device CL2in the axial direction L overlaps the disposition area of the transmission output gear23in the axial direction L.

The support member61is connected to the ring gear R1so as to rotate integrally with the ring gear R1. In the present embodiment, the support member61is formed in a tubular shape protruding from a gear forming member10to the second axial side L2. In the present embodiment, the support member61is rotatably supported by a fifth bearing B5. In the present embodiment, the fifth bearing B5is supported by the second side wall portion92of the case9from the outer side in the radial direction R. The fifth bearing B5rotatably supports the support member61from the outer side in the radial direction R.

The switching member62is supported so as to rotate integrally with the support member61and to move relative to the support member61in the axial direction L. In the present embodiment, the switching member62is formed in a tubular shape covering an inner side of the support member61in the radial direction R. A plurality of external teeth is formed on the outer peripheral portion of the switching member62, and a plurality of internal teeth mating with the external teeth is formed on the inner peripheral portion of the support member61. These internal and external teeth are engaged so as to be relatively movable in the axial direction L and not to be relatively rotatable in the circumferential direction. Thus, the switching member62is a sleeve of the intermeshing engagement device (dog clutch).

In the present embodiment, an engaging portion62ahaving a plurality of internal teeth is formed on the inner peripheral portion of the switching member62.

The engaged portion63is connected to the carrier C1so as to rotate integrally with the carrier C1. In the present embodiment, the engaged portion63is formed in a tubular shape with its axis on the first axis X1. A plurality of external teeth engageable with the plurality of internal teeth of the engaging portion62aof the switching member62so as to be relatively movable in the axial direction L and not to be relatively rotatable in the circumferential direction is formed on the outer peripheral portion of the engaged portion63.

When the switching member62moves in the axial direction L relative to the support member61and the internal teeth of the engaging portion62aare engaged with the external teeth of the engaged portion63, the carrier C1and the ring gear R1are connected to each other. As a result, the three rotation elements E1to E3of the distribution differential gear mechanism SP rotate integrally with each other. When the internal teeth of the engaging portion62aare not engaged with the external teeth of the engaged portion63, the carrier C1and the ring gear R1are disconnected. As a result, the three rotation elements E1to E3of the distribution differential gear mechanism SP rotate relatively.

As described above, the vehicle drive device100(in this case, the first drive unit100A) includes:the input member I drivingly connected to the internal combustion engine EG;the first output member O1drivingly connected to the first wheels W1;the first rotary electric machine MG1including the first rotor RT1;the first rotary electric machine drive gear DG1drivingly connected to the first rotor RT1;the transmission mechanism T including the transmission engagement device CLt configured to switch the state of power transmission;the distribution differential gear mechanism SP including the first rotation element E1drivingly connected to the input member I, the second rotation element E2drivingly connected to the transmission mechanism T, and the third rotation element E3drivingly connected to the first rotary electric machine drive gear DG1;the first distribution output gear SG1connected to the second rotation element E2so as to rotate integrally with the second rotation element E2; andthe first engagement device CL1configured to connect or disconnect the power transmission between the input member I and the first rotation element E1.

The transmission mechanism T is configured to transmit the rotation transmitted from the distribution differential gear mechanism SP to the first output member O1.

The distribution differential gear mechanism SP, the first distribution output gear SG1, and the first engagement device CL1are disposed on the first axis X1.

The first rotary electric machine MG1and the first rotary electric machine drive gear DG1are disposed on the second axis X2different from the first axis X1.

The transmission engagement device CLt is disposed on the third axis X3different from the first axis X1and the second axis X2.

The axial direction L of the first rotary electric machine MG1includes the first axial side L1where the first rotary electric machine MG1is disposed with respect to the first rotary electric machine drive gear DG1, and the second axial side L2opposite to the first axial side L1.

The distribution differential gear mechanism SP is disposed on the second axial side L2of the first distribution output gear SG1and the first engagement device CL1.

According to this configuration, the combination of the distribution differential gear mechanism SP, the first distribution output gear SG1, and the first engagement device CL1, the combination of the first rotary electric machine MG1and the first rotary electric machine drive gear DG1, and the transmission engagement device CLt are disposed on different axes. Thus, the dimension of the vehicle drive device100in the axial direction L can easily be reduced compared to a configuration in which some or all of them are disposed coaxially.

In such a configuration, the first rotary electric machine drive gear DG1is disposed on the second axial side L2of the first rotary electric machine MG1, and the distribution differential gear mechanism SP is disposed on the second axial side L2of the first distribution output gear SG1and the first engagement device CL1. That is, the first rotary electric machine drive gear DG1and the distribution differential gear mechanism SP are disposed on the same side in the axial direction L with respect to the other elements disposed coaxially therewith. Therefore, both the first rotary electric machine MG1and the combination of the first distribution output gear SG1and the first engagement device CL1can be disposed in an area on the first axial side L1of the first rotary electric machine drive gear DG1and the distribution differential gear mechanism SP while the third rotation element E3of the distribution differential gear mechanism SP and the first rotary electric machine drive gear DG1are drivingly connected appropriately. Accordingly, the dimension of the vehicle drive device100in the axial direction L can easily be reduced in the configuration including the input member I, the first output member O1, the first rotary electric machine MG1, the distribution differential gear mechanism SP, the transmission mechanism T, and the first engagement device CL1.

In the present embodiment, both the disposition area of the first distribution output gear SG1in the axial direction L and the disposition area of the first engagement device CL1in the axial direction L overlap the disposition area of the first rotary electric machine MG1in the axial direction L. In the example shown inFIG.3, the disposition areas of the first distribution output gear SG1and the first engagement device CL1in the axial direction L are within the disposition area of the first rotary electric machine MG1in the axial direction L. Specifically, the end on the first axial side L1for the first engagement device CL1positioned on the first axial side L1of the first distribution output gear SG1is positioned on the second axial side L2of the end on the first axial side L1for the coil end portion CE of the first rotary electric machine MG1on the first axial side L1. The end on the second axial side L2for the first distribution output gear SG1is positioned on the first axial side L1of the end on the second axial side L2for the coil end portion CE of the first rotary electric machine MG1on the second axial side L2.

According to this configuration, the dimension of the vehicle drive device100in the axial direction L can be reduced compared to a configuration in which the disposition area of at least one of the first distribution output gear SG1and the first engagement device CL1in the axial direction L does not overlap the disposition area of the first rotary electric machine MG1in the axial direction L.

In the present embodiment, the vehicle drive device100(in this case, the first drive unit100A) further includes the second distribution output gear SG2connected to the third rotation element E3so as to rotate integrally with the third rotation element E3.

The distribution differential gear mechanism SP is the planetary gear mechanism including the sun gear S1, the carrier C1, and the ring gear R1.

The third rotation element E3is the ring gear R1.

The second distribution output gear SG2is disposed on the first axis X1and on the outer side in the radial direction R with respect to the ring gear R1.

The transmission mechanism T includes the first gear21disposed on the third axis X3and meshing with the second distribution output gear SG2.

The ring gear R1and the second distribution output gear SG2overlap each other in the radial view along the radial direction R.

According to this configuration, the dimension of the vehicle drive device100in the axial direction L can be reduced compared to a configuration in which the ring gear R1and the second distribution output gear SG2do not overlap each other in the radial view along the radial direction R.

According to this configuration, the second distribution output gear SG2connected to the ring gear R1serving as the third rotation element E3drivingly connected to the first rotary electric machine drive gear DG1so as to rotate integrally with the ring gear R1is disposed on the outer side in the radial direction R with respect to the ring gear R1. Therefore, the second distribution output gear SG2and the first rotary electric machine drive gear DG1can easily mesh with each other directly or indirectly. Thus, the first rotary electric machine drive gear DG1and the third rotation element E3can be drivingly connected appropriately.

In the present embodiment, the vehicle drive device100(in this case, the first drive unit100A) further includes the first output differential gear mechanism DF1including the first differential input gear31serving as the first output member O1and configured to distribute the rotation of the first differential input gear31to the pair of first wheels W1.

The transmission mechanism T further includes the second gear22disposed on the third axis X3and meshing with the first distribution output gear SG1, and the transmission output gear23disposed on the third axis X3and meshing with the first differential input gear31.

On the third axis X3, the transmission output gear23, the first gear21, the transmission engagement device CLt, and the second gear22are disposed in this order from the second axial side L2.

According to this configuration, the transmission mechanism T can be structured as the parallel-shaft gear transmission including the second distribution output gear SG2and the first gear21that mesh with each other, and the first distribution output gear SG1and the second gear22that mesh with each other. In addition, the rotation shifted by the transmission can be transmitted to the pair of first wheels W1via the first output differential gear mechanism DF1.

According to this configuration, the transmission engagement device CLt is disposed between the first gear21and the second gear22in the axial direction L. Thus, the transmission engagement device CLt can easily switch the states of power transmission of the first gear21and the second gear22.

As shown inFIG.2, the second rotary electric machine MG2functions as a driving force source for the second wheels W2. The second rotary electric machine MG2has a function as a motor (electric motor) that receives supply of electric power to generate driving force, and a function as a generator (electric power generator) that receives supply of driving force to generate electric power. Specifically, the second rotary electric machine MG2is electrically connected to the power storage device so as to exchange electric power with the power storage device. The second rotary electric machine MG2generates a driving force by power running with electric power stored in the power storage device. During regeneration, the second rotary electric machine MG2generates electric power with a driving force transmitted from the second output member O2side to charge the power storage device.

The second rotary electric machine MG2includes a second stator ST2and a second rotor RT2. The second stator ST2is fixed to a non-rotating member (for example, a case that houses the second rotary electric machine MG2and the like). The second rotor RT2is supported so as to be rotatable relative to the second stator ST2. In the present embodiment, the second rotor RT2is disposed on the inner side in the radial direction R with respect to the second stator ST2.

In the present embodiment, a second rotary electric machine drive gear DG2is connected to the second rotor RT2via a second rotor shaft RS2extending along the axial direction L so as to rotate integrally with the second rotor RT2. In the example shown inFIG.2, the second rotor gear RG2is disposed on the first axial side L1of the second rotor RT2.

The counter gear mechanism CG includes a counter input gear71, a counter output gear72, and a counter shaft73connecting these gears71and72so as to rotate integrally.

The counter input gear71is an input element of the counter gear mechanism CG. In the present embodiment, the counter input gear71meshes with the second rotary electric machine drive gear DG2. The counter output gear72is an output element of the counter gear mechanism CG. In the example shown inFIG.2, the counter output gear72is disposed on the second axial side L2of the counter input gear71. The counter output gear72is formed to have a smaller diameter than the counter input gear71.

The second output differential gear mechanism DF2distributes the rotation of the second output member O2to the pair of second wheels W2. In the present embodiment, the second output member O2is a second differential input gear81that meshes with the counter output gear72of the counter gear mechanism CG.

In the present embodiment, the second output differential gear mechanism DF2is a bevel gear type differential gear mechanism. Specifically, the second output differential gear mechanism DF2includes a hollow second differential case, a second pinion shaft supported so as to rotate integrally with the second differential case, a pair of second pinion gears rotatably supported on the second pinion shaft, and a pair of second side gears meshing with the pair of second pinion gears and functioning as output elements. The second differential case houses the second pinion shaft, the pair of second pinion gears, and the pair of second side gears.

In the present embodiment, the second differential input gear81serving as the second output member O2is connected to the second differential case so as to protrude outward in the radial direction R from the second differential case. Second drive shafts DS2drivingly connected to the second wheels W2are connected to the pair of second side gears so as to rotate integrally with the second side gears. Thus, in the present embodiment, the second output differential gear mechanism DF2distributes the rotation of the second output member O2(in this case, the second differential input gear81) to the pair of second wheels W2via the pair of second drive shafts DS2.

Hereinafter, the positional relationship of the elements of the vehicle drive device100in an axial view along the axial direction L will be described with reference toFIG.5. An arrow “V” inFIG.5indicates a vertical direction of the vehicle drive device100mounted on the vehicle (vehicle-mounted state).

As shown inFIG.5, in the present embodiment, the second axis X2serving as the rotation axes of the first rotary electric machine MG1and the first rotary electric machine drive gear DG1is located, in the vehicle-mounted state, above a virtual plane P including the first axis X1serving as the rotation axes of the distribution differential gear mechanism SP, the first distribution output gear SG1, the second distribution output gear SG2, and the like and the fourth axis X4serving as the rotation axes of the first output member O1and the first output differential gear mechanism DF1. The third axis X3serving as the rotation axes of the first gear21, the second gear22, the transmission output gear23, and the like is located below the virtual plane P in the vehicle-mounted state.

As described above, in the present embodiment, the vehicle drive device100(in this case, the first drive unit100A) further includes the first output differential gear mechanism DF1configured to distribute the rotation of the first output member O1to the pair of first wheels W1.

The first output differential gear mechanism DF1is disposed on the fourth axis X4different from the first axis X1, the second axis X2, and the third axis X3.

The second axis X2is located above the virtual plane P including the first axis X1and the fourth axis X4in the vehicle-mounted state.

The third axis X3is located below the virtual plane P in the vehicle-mounted state.

According to this configuration, the first rotary electric machine MG1and the first rotary electric machine drive gear DG1disposed on the second axis X2and the transmission engagement device CLt disposed on the third axis X3can be arranged in the vertical direction V in the vehicle-mounted state. Therefore, the dimension of the vehicle drive device100in a direction orthogonal to the axial direction L, for example, the dimension of the vehicle drive device100in a vehicle fore-and-aft direction (lateral direction inFIG.5) can be reduced easily.

As shown inFIG.6, in the present embodiment, the vehicle drive device100has, as the operation modes, an electric torque converter mode (hereinafter referred to as “eTC mode”), a first EV mode, a second EV mode, a first HV mode, a second HV mode, and a charging mode.

FIG.6shows states of the first engagement device CL1, the second engagement device CL2, and the transmission engagement device CLt in each operation mode of the vehicle drive device100of the present embodiment. In the fields for the first engagement device CL1and the second engagement device CL2inFIG.6, “o” indicates that the target engagement device is engaged, and “x” indicates that the target engagement device is disengaged. In the fields for the transmission engagement device CLt inFIG.6, “Lo” indicates that the transmission engagement device CLt forms the low speed, “Hi” indicates that the transmission engagement device CLt forms the high speed, and “N” indicates that the transmission engagement device CLt is neutral.

The eTC mode is a mode in which the distribution differential gear mechanism SP amplifies the torque of the internal combustion engine EG by using the torque of the first rotary electric machine MG1as a reaction force and transmits the amplified torque to the first output member O1, thereby causing the vehicle to travel. The eTC mode is called “electric torque converter mode” because the torque of the internal combustion engine EG can be amplified and transmitted to the first output member O1.

As shown inFIG.6, in the eTC mode of the present embodiment, control is performed so that the first engagement device CL1is engaged, the second engagement device CL2is disengaged, and the transmission engagement device CLt forms the low speed. In the eTC mode of the present embodiment, the first rotary electric machine MG1generates electric power by outputting a positive torque while rotating backward, and the distribution differential gear mechanism SP combines the driving force of the first rotary electric machine MG1and the driving force of the internal combustion engine EG and outputs a driving force larger than the driving force of the internal combustion engine EG from the second rotation element E2(in this case, the carrier C1). The rotation of the second rotation element E2is shifted in the transmission mechanism T at a speed ratio corresponding to the low speed and transmitted to the first output member O1. Therefore, the eTC mode can be selected even when the charge level of the power storage device is relatively low.

The first EV mode is a mode in which the vehicle travels at a relatively low speed with the driving force of only the first rotary electric machine MG1out of the internal combustion engine EG and the first rotary electric machine MG1. The second EV mode is a mode in which the vehicle travels at a relatively high speed with the driving force of only the first rotary electric machine MG1out of the internal combustion engine EG and the first rotary electric machine MG1.

In the first EV mode of the present embodiment, control is performed so that the first engagement device CL1is disengaged, the second engagement device CL2is engaged, and the transmission engagement device CLt forms the low speed. In the second EV mode of the present embodiment, control is performed so that the first engagement device CL1is disengaged, the second engagement device CL2is engaged, and the transmission engagement device CLt forms the high speed.

In the first EV mode and the second EV mode of the present embodiment, the internal combustion engine EG is separated from the distribution differential gear mechanism SP by disengaging the first engagement device CL1. Therefore, the power transmission between the internal combustion engine EG and the first output member O1is interrupted. By engaging the second engagement device CL2, the three rotation elements E1to E3of the distribution differential gear mechanism SP rotate integrally with each other. As a result, the rotation input from the first rotary electric machine MG1side to the distribution differential gear mechanism SP is transmitted as it is to the first gear21and the second gear22of the transmission mechanism T. The rotation transmitted to the transmission mechanism T is shifted at the speed ratio of the low speed in the first EV mode and at the speed ratio of the high speed in the second EV mode depending on the state of the transmission engagement device CLt, and is transmitted to the first output member O1.

The first HV mode is a mode in which the vehicle travels at a relatively low speed with the driving force of at least the internal combustion engine EG out of the internal combustion engine EG and the first rotary electric machine MG1. The second HV mode is a mode in which the vehicle travels at a relatively high speed with the driving force of at least the internal combustion engine EG out of the internal combustion engine EG and the first rotary electric machine MG1.

In the first HV mode of the present embodiment, control is performed so that both the first engagement device CL1and the second engagement device CL2are engaged and the transmission engagement device CLt forms the low speed. In the second HV mode of the present embodiment, control is performed so that both the first engagement device CL1and the second engagement device CL2are engaged and the transmission engagement device CLt forms the high speed.

In the first HV mode and the second HV mode of the present embodiment, the internal combustion engine EG is connected to the distribution differential gear mechanism SP by engaging the first engagement device CL1. By engaging the second engagement device CL2, the three rotation elements E1to E3of the distribution differential gear mechanism SP rotate integrally with each other. As a result, the rotation input from the internal combustion engine EG side and the first rotary electric machine MG1side to the distribution differential gear mechanism SP is transmitted as it is to the first gear21and the second gear22of the transmission mechanism T. The rotation transmitted to the transmission mechanism T is shifted at the speed ratio of the low speed in the first EV mode and at the speed ratio of the high speed in the second EV mode depending on the state of the transmission engagement device CLt, and is transmitted to the first output member O1.

The charging mode is a mode in which the power storage device is charged by causing the first rotary electric machine MG1to generate electric power by using the driving force of the internal combustion engine EG. In the charging mode of the present embodiment, control is performed so that the first engagement device CL1is engaged, the second engagement device CL2is engaged, and the transmission engagement device CLt is neutral. The control is performed so that the internal combustion engine EG outputs the driving force and the first rotary electric machine MG1outputs the driving force in a direction opposite to the rotation direction of the first rotor RT1rotated by the driving force of the internal combustion engine EG, thereby generating electric power. In the charging mode, the vehicle may be stopped, or may travel by causing the second rotary electric machine MG2to perform power running with electric power generated by the first rotary electric machine MG1and transmitting the driving force of the second rotary electric machine MG2to the second wheels W2. The mode in which the vehicle travels by the driving force of the second rotary electric machine MG2while being in the charging mode is called “series hybrid mode”.

[Other Embodiments]

(1) In the above embodiment, description has been given of the exemplary configuration in which the vehicle drive device100includes the first drive unit100A and the second drive unit100B. However, the present disclosure is not limited to such a configuration. The vehicle drive device100may include the first drive unit100A but not include the second drive unit100B. In this case, the first drive unit100A may include the second rotary electric machine MG2.

(2) In the above embodiment, description has been given of the exemplary configuration in which the transmission mechanism T is the transmission capable of forming either one of the two shift speeds that are the low speed and the high speed. However, the present disclosure is not limited to such a configuration. The transmission mechanism T may form any one of three or more shift speeds. Alternatively, the transmission mechanism T may include a counter gear mechanism or a planetary gear mechanism to shift the rotation transmitted from the distribution differential gear mechanism SP at a constant speed ratio and transmit it to the first output member O1.

(3) In the above embodiment, description has been given of the exemplary configuration in which the second distribution output gear SG2is drivingly connected to the first rotary electric machine drive gear DG1via the idler gear IG. However, the present disclosure is not limited to such a configuration. The second distribution output gear SG2may directly mesh with the first rotary electric machine drive gear DG1.

(4) In the above embodiment, description has been given of the exemplary configuration in which both the disposition area of the first distribution output gear SG1in the axial direction L and the disposition area of the first engagement device CL1in the axial direction L overlap the disposition area of the first rotary electric machine MG1in the axial direction L. However, the present disclosure is not limited to such a configuration. Only one of the disposition area of the first distribution output gear SG1in the axial direction L and the disposition area of the first engagement device CL1in the axial direction L may overlap the disposition area of the first rotary electric machine MG1in the axial direction L. Neither the disposition area of the first distribution output gear SG1in the axial direction L nor the disposition area of the first engagement device CL1in the axial direction L may overlap the disposition area of the first rotary electric machine MG1in the axial direction L.

(5) In the above embodiment, description has been given of the exemplary configuration in which the second distribution output gear SG2is disposed on the outer side in the radial direction R with respect to the ring gear R1at the position where the second distribution output gear SG2overlaps the ring gear R1in the radial view along the radial direction R. However, the present disclosure is not limited to such a configuration. The second distribution output gear SG2may be disposed so as not to overlap the ring gear R1in the radial view. In that case, the second distribution output gear SG2may be disposed at the same position in the radial direction R as the ring gear R1, or may be disposed on the inner side in the radial direction R with respect to the ring gear R1.

(6) In the above embodiment, description has been given of the exemplary configuration in which, on the third axis X3, the transmission output gear23, the first gear21, the transmission engagement device CLt, and the second gear22are disposed in this order from the second axial side L2. However, the disposition order of the first gear21, the second gear22, the transmission output gear23, and the transmission engagement device CLt in the axial direction L may be changed as appropriate without being limited to such a configuration.

(7) In the above embodiment, description has been given of the exemplary configuration in which the second axis X2is located above the virtual plane P including the first axis X1and the fourth axis X4in the vehicle-mounted state and the third axis X3is located below the virtual plane P in the vehicle-mounted state. However, the positions of the first axis X1, the second axis X2, the third axis X3, and the fourth axis X4may be changed as appropriate without being limited to such a configuration.

(8) In the above embodiment, description has been given of the exemplary configuration in which the operation mode of the vehicle drive device100that is realized by engaging the first engagement device CL1and disengaging the second engagement device CL2is the electric torque converter mode (eTC mode). However, the present disclosure is not limited to such a configuration. For example, the distribution differential gear mechanism SP may be configured to realize a so-called split hybrid mode by engaging the first engagement device CL1and disengaging the second engagement device CL2. The split hybrid mode is a mode in which the torque of the internal combustion engine EG is distributed to the first rotary electric machine MG1and the transmission mechanism T and a torque damped relative to the torque of the internal combustion engine EG by using the torque of the first rotary electric machine MG1as a reaction force is transmitted to the transmission mechanism T. In this case, the order of the rotation speeds of the rotation elements of the distribution differential gear mechanism SP may be set to the order of the second rotation element E2, the first rotation element E1, and the third rotation element E3. For example, when the distribution differential gear mechanism SP is structured by a single-pinion planetary gear mechanism, the sun gear may be drivingly connected to the first rotor RT1as the third rotation element E3, the carrier may be drivingly connected to the input member I as the first rotation element E1, and the ring gear may be used as the second rotation element E2to serve as the output element of the distribution differential gear mechanism SP. In this mode, the first rotary electric machine MG1generates electric power by outputting a negative torque while rotating forward, and the distribution differential gear mechanism SP outputs the torque of the internal combustion engine EG from the second rotation element E2by using the torque of the first rotary electric machine MG1as a reaction force. The rotation of the second rotation element E2is transmitted to the transmission mechanism T.

(9) The configurations disclosed in the above embodiments can be applied in combination with the configurations disclosed in other embodiments as long as there is no contradiction. Regarding the other configurations, the embodiments disclosed herein are merely illustrative in all respects. Therefore, various modifications can be made as appropriate without departing from the spirit of the present disclosure.

[Outline of Embodiment Described Above]

Hereinafter, the outline of the vehicle drive device (100) described above will be described.

The vehicle drive device (100) includes:an input member (I) drivingly connected to an internal combustion engine (EG);an output member (O1) drivingly connected to wheels (W1);a rotary electric machine (MG1) including a rotor (RT1);a rotary electric machine drive gear (DG1) drivingly connected to the rotor (RT1);a transmission mechanism (T) including a transmission engagement device (CLt) configured to switch a state of power transmission;a distribution differential gear mechanism (SP) including a first rotation element (E1) drivingly connected to the input member (I), a second rotation element (E2) drivingly connected to the transmission mechanism (T), and a third rotation element (E3) drivingly connected to the rotary electric machine drive gear (DG1);a first distribution output gear (SG1) connected to the second rotation element (E2) so as to rotate integrally with the second rotation element (E2); anda disconnection engagement device (CL1) configured to connect or disconnect power transmission between the input member (1) and the first rotation element (E1), in whichthe transmission mechanism (T) is configured to transmit rotation transmitted from the distribution differential gear mechanism (SP) to the output member (O1),the distribution differential gear mechanism (SP), the first distribution output gear (SG1), and the disconnection engagement device (CL1) are disposed on a first axis (X1),the rotary electric machine (MG1) and the rotary electric machine drive gear (DG1) are disposed on a second axis (X2) different from the first axis (X1),the transmission engagement device (CLt) is disposed on a third axis (X3) different from the first axis (X1) and the second axis (X2),an axial direction (L) of the rotary electric machine (MG1) includes a first axial side (L1) where the rotary electric machine (MG1) is disposed with respect to the rotary electric machine drive gear (DG1), and a second axial side (L2) opposite to the first axial side (L1), andthe distribution differential gear mechanism (SP) is disposed on the second axial side (L2) of the first distribution output gear (SG1) and the disconnection engagement device (CL1).

According to this configuration, the combination of the distribution differential gear mechanism (SP), the first distribution output gear (SG1), and the disconnection engagement device (CL1), the combination of the rotary electric machine (MG1) and the rotary electric machine drive gear (DG1), and the transmission engagement device (CLt) are disposed on different axes. Thus, the dimension of the vehicle drive device (100) in the axial direction (L) can easily be reduced compared to a configuration in which some or all of them are disposed coaxially.

In such a configuration, the rotary electric machine drive gear (DG1) is disposed on the second axial side (L2) of the rotary electric machine (MG1), and the distribution differential gear mechanism (SP) is disposed on the second axial side (L2) of the first distribution output gear (SG1) and the disconnection engagement device (CL1). That is, the rotary electric machine drive gear (DG1) and the distribution differential gear mechanism (SP) are disposed on the same side in the axial direction (L) with respect to the other elements disposed coaxially therewith. Therefore, both the rotary electric machine (MG1) and the combination of the first distribution output gear (SG1) and the disconnection engagement device (CL1) can be disposed in an area on the first axial side (L1) of the rotary electric machine drive gear (DG) and the distribution differential gear mechanism (SP) while the third rotation element (E3) of the distribution differential gear mechanism (SP) and the rotary electric machine drive gear (DG1) are drivingly connected appropriately. Accordingly, the dimension of the vehicle drive device (100) in the axial direction (L) can easily be reduced in the configuration including the input member (I), the output member (O1), the rotary electric machine (MG1), the distribution differential gear mechanism (SP), the transmission mechanism (T), and the disconnection engagement device (CL1).

It is preferable that both a disposition area of the first distribution output gear (SG1) in the axial direction (L) and a disposition area of the disconnection engagement device (CL1) in the axial direction (L) overlap a disposition area of the rotary electric machine (MG1) in the axial direction (L).

According to this configuration, the dimension of the vehicle drive device (100) in the axial direction (L) can be reduced compared to a configuration in which the disposition area of at least one of the first distribution output gear (SG1) and the disconnection engagement device (CL1) in the axial direction (L) does not overlap the disposition area of the rotary electric machine (MG1) in the axial direction (L).

It is preferable that the vehicle drive device (100) further include a second distribution output gear (SG2) connected to the third rotation element (E3) so as to rotate integrally with the third rotation element (E3),the distribution differential gear mechanism (SP) be a planetary gear mechanism including a sun gear (S1), a carrier (C1), and a ring gear (R1),the third rotation element (E3) be the ring gear (R1),the second distribution output gear (SG2) be disposed on the first axis (X1) and on an outer side in a radial direction (R) with respect to the ring gear (R1),the transmission mechanism (T) include a first gear (21) disposed on the third axis (X3) and meshing with the second distribution output gear (SG2), andthe ring gear (R1) and the second distribution output gear (SG2) overlap each other in a radial view along the radial direction (R).

According to this configuration, the dimension of the vehicle drive device (100) in the axial direction (L) can be reduced compared to a configuration in which the ring gear (R1) and the second distribution output gear (SG2) do not overlap each other in the radial view along the radial direction (R).

According to this configuration, the second distribution output gear (SG2) connected to the ring gear (R1) serving as the third rotation element (E3) drivingly connected to the rotary electric machine drive gear (DG1) so as to rotate integrally with the ring gear (R1) is disposed on the outer side in the radial direction (R) with respect to the ring gear (R1). Therefore, the second distribution output gear (SG2) and the rotary electric machine drive gear (DG1) can easily mesh with each other directly or indirectly. Thus, the rotary electric machine drive gear (DG1) and the third rotation element (E3) can be drivingly connected appropriately.

In the configuration including the second distribution output gear (SG2),it is preferable that the vehicle drive device (100) further include an output differential gear mechanism (DF1) including a differential input gear (31) serving as the output member (O1) and configured to distribute rotation of the differential input gear (31) to a pair of the wheels (W1),the transmission mechanism (T) further include a second gear (22) disposed on the third axis (X3) and meshing with the first distribution output gear (SG1), and a transmission output gear (23) disposed on the third axis (X3) and meshing with the differential input gear (31), andon the third axis, the transmission output gear (23), the first gear (21), the transmission engagement device (CLt), and the second gear (22) be disposed in this order from the second axial side (L2).

According to this configuration, the transmission mechanism (T) can be structured as a parallel-shaft gear transmission including the second distribution output gear (SG2) and the first gear (21) that mesh with each other, and the first distribution output gear (SG1) and the second gear (22) that mesh with each other. In addition, the rotation shifted by the transmission can be transmitted to the pair of wheels (W1) via the output differential gear mechanism (DF1).

According to this configuration, the transmission engagement device (CLt) is disposed between the first gear (21) and the second gear (22) in the axial direction (L). Thus, the transmission engagement device (CLt) can easily switch the states of power transmission of the first gear (21) and the second gear (22).

In the configuration including the output differential gear mechanism (DF1),it is preferable that, assuming the disconnection engagement device as a first engagement device (CL1),the vehicle drive device (100) further include a second engagement device (CL2) configured to connect or disconnect power transmission between two elements selected from among three rotation elements that are the first rotation element (E1), the second rotation element (E2), and the third rotation element (E3), anda disposition area of the second engagement device (CL2) in the axial direction (L) overlap a disposition area of the transmission output gear (23) in the axial direction (L).

According to this configuration, the dimension of the vehicle drive device (100) in the axial direction (L) can be reduced compared to a configuration in which the disposition area of the second engagement device (CL2) in the axial direction (L) does not overlap the disposition area of the transmission output gear (23) in the axial direction (L).

It is preferable that the vehicle drive device (100) further include an output differential gear mechanism (DF1) configured to distribute rotation of the output member (O1) to a pair of the wheels (W1),the output differential gear mechanism (DF1) be disposed on a fourth axis (X4) different from the first axis (X1), the second axis (X2), and the third axis (X3),the second axis (X2) be located above a virtual plane (P) including the first axis (X1) and the fourth axis (X4) in a vehicle-mounted state, andthe third axis (X3) be located below the virtual plane (P) in the vehicle-mounted state.

According to this configuration, the rotary electric machine (MG1) and the rotary electric machine drive gear (DG1) disposed on the second axis (X2) and the transmission engagement device (CLt) disposed on the third axis (X3) can be arranged in the vertical direction (V) in the vehicle-mounted state. Therefore, the dimension of the vehicle drive device (100) in a direction orthogonal to the axial direction (L), for example, the dimension of the vehicle drive device (100) in a vehicle fore-and-aft direction can be reduced easily.

INDUSTRIAL APPLICABILITY

The technology according to the present disclosure is applicable to a vehicle drive device including an input member drivingly connected to an internal combustion engine, an output member drivingly connected to wheels, a rotary electric machine, a transmission mechanism including a transmission engagement device for switching the state of power transmission, and a distribution differential gear mechanism.

DESCRIPTION OF THE REFERENCE NUMERALS

100: vehicle drive device, I: input member, O1: first output member (output member), MG1: first rotary electric machine (rotary electric machine), RT1: first rotor (rotor), DG1; first rotary electric machine drive gear (rotary electric machine drive gear), T: transmission mechanism, SP: distribution differential gear mechanism, E1: first rotation element, E2: second rotation element, E3: third rotation element E3, SG1: first distribution output gear, CL1: first engagement device (disconnection engagement device), CLt: transmission engagement device, EG: internal combustion engine, W1: first wheel (wheel), L: axial direction, L1: first axial side, L2: second axial side, X1: first axis, X2: second axis, X3: third axis