JP2016222118A - Drive unit for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a drive unit for a vehicle which can be suppressed in enlargement as a whole while having a rotating electric machine as a drive force source of wheels.SOLUTION: A gear change device TM comprises a first differential gear mechanism G1 having three rotating elements e1, e2 and e3 including the rotating element e3 which is drive-connected to an input shaft I, and a second differential gear mechanism G2 having four or more rotating elements e4, e5, e6 and e7 including the rotating element e6 which is drive-connected to a gear change output member 70. The second differential gear mechanism G2 is arranged at a second side L2 in an axial direction being a side opposite to a first side L1 in the axial direction with respect to the first differential gear mechanism G1. A rotating electric machine MG is arranged at the first side L1 in the axial direction with respect to a counter gear mechanism CG being a position in which the rotating electric machine is overlapped on the counter gear mechanism CG when viewed in the axial direction L, and the rotating electric machine MG is also arranged in a position in which the rotating electric machine is overlapped on the first differential gear mechanism G1 when viewed in a radial direction of a gear change device TM in a region of a part of the gear change device TM in a peripheral direction.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a vehicle drive device.

  As a vehicle drive device, one described in Japanese Patent Application Laid-Open No. 2000-220705 (Patent Document 1) is known. Patent Document 1 discloses an input member that is drivingly connected to an internal combustion engine, an output differential gear device that is drivingly connected to a wheel, a transmission that shifts the rotation of the input member and transmits it to a transmission output member, There is disclosed a vehicle drive device that includes an axis parallel to the axial direction of the device and a counter gear mechanism that transmits rotation of a speed change output member to an output differential gear device. The vehicle drive device is arranged adjacent to the internal combustion engine in the axial direction.

  By the way, a hybrid vehicle provided with a rotating electrical machine in addition to an internal combustion engine as a driving force source for wheels has been put into practical use. In the configuration described in Patent Document 1, it is not assumed that a rotating electrical machine is provided as a wheel driving force source, but the vehicle driving device described in Patent Document 1 is replaced with a rotating electrical machine as a wheel driving force source. It is conceivable to change the configuration to include a drive device for a hybrid vehicle. Here, it is preferable to avoid an increase in the size of the entire apparatus in consideration of the in-vehicle performance of the vehicle drive apparatus. However, since it is not assumed in Patent Document 1 that a rotating electrical machine is provided as a driving force source for the wheels, the arrangement configuration of the rotating electrical machine in consideration of in-vehicle performance is not described at all.

Japanese Patent Laid-Open No. 2000-220705 (FIGS. 1, 5, etc.)

  Therefore, it is desired to realize a vehicle drive device that includes a rotating electrical machine as a wheel driving force source and can suppress an increase in size of the entire device.

  In view of the above, the input member that is drivingly connected to the internal combustion engine, the output differential gear device that is drivingly connected to the wheels, the rotating electrical machine that is drivingly connected to the input member, and the rotation of the input member are shifted. A transmission for transmitting to the transmission output member, and a counter gear mechanism having an axis parallel to the axial direction of the transmission and transmitting the rotation of the transmission output member to the differential gear device for output, The characteristic configuration of the vehicle drive device disposed on the first axial side, which is one side of the axial direction with respect to the internal combustion engine, is characterized in that the transmission includes three rotating elements that are drivingly connected to the input member. A second differential gear mechanism having a rotary element, a second differential gear mechanism having four or more rotary elements including a rotary element drivingly connected to the first differential gear mechanism and a rotary element drivingly connected to the speed change output member. Differential gear mechanism and front The second differential gear mechanism is disposed on the second axial side opposite to the first axial side with respect to the first differential gear mechanism, and the counter gear mechanism is disposed on the transmission device. The rotating electrical machine is disposed at a position overlapping with the second differential gear mechanism as viewed in the radial direction of the transmission in a partial region in the circumferential direction, and the rotating electrical machine is arranged on the first axial side with respect to the counter gear mechanism. And is disposed at a position overlapping with the counter gear mechanism when viewed in the axial direction, and the rotating electrical machine is further viewed when viewed in the radial direction of the transmission in a partial region in the circumferential direction of the transmission. It exists in the point arrange | positioned in the position which overlaps with a 1st differential gear mechanism.

  According to the above characteristic configuration, in the configuration in which the vehicle drive device is disposed on the first axial side with respect to the internal combustion engine, the second differential gear mechanism is axially second with respect to the first differential gear mechanism. And the rotating electrical machine is disposed on the first axial side with respect to the counter gear mechanism and at a position overlapping the counter gear mechanism as viewed in the axial direction. In a partial region in the circumferential direction, the first differential gear mechanism is disposed at a position overlapping with the first differential gear mechanism in the radial direction of the transmission. That is, the rotating electrical machine is arranged using a space formed outside the first differential gear mechanism in the radial direction and overlapping with the counter gear mechanism when viewed in the axial direction and in which the counter gear mechanism is not arranged. Thereby, compared with the case where a rotary electric machine is arrange | positioned in the position which does not overlap with a counter gear mechanism seeing in an axial direction, the protrusion of the radial direction of a rotary electric machine can be suppressed. Here, the second differential gear mechanism has a rotating element that is drivingly connected to the speed change output member. Therefore, by arranging the second differential gear mechanism on the second axial side with respect to the first differential gear mechanism, the second differential gear mechanism is axially first with respect to the first differential gear mechanism. Compared with the case where it arrange | positions, it becomes easy to arrange | position a transmission output member near the axial direction 2nd side. As a result, it is easy to place the end portion on the first axial side of the counter gear mechanism that transmits the rotation of the speed change output member to the output differential gear device toward the second side in the axial direction. It becomes possible to arrange the rotating electrical machine arranged using the above-mentioned space close to the second side in the axial direction. As a result, the amount of protrusion of the rotating electrical machine toward the first axial direction with respect to the transmission can be reduced, and the amount of protrusion can be made zero. That is, it is possible to reduce the size of the entire apparatus while providing a rotating electrical machine as a driving force source for wheels.

It is a skeleton figure of the drive device for vehicles concerning an embodiment. 1 is a partial cross-sectional view of a vehicle drive device according to an embodiment. It is a skeleton figure of the transmission which concerns on embodiment. It is a simplified diagram showing the arrangement of each component of the vehicle drive device according to the embodiment as viewed in the axial direction. It is a simplified diagram showing the arrangement of each component of the vehicle drive device according to the embodiment as viewed in the axial direction. It is a skeleton figure of the transmission which concerns on other embodiment.

  An embodiment of a vehicle drive device will be described with reference to the drawings. In the following description, “driving connection” means a state where two rotating elements are connected so as to be able to transmit a driving force. This concept includes a state where the two rotating elements are coupled so as to rotate integrally, and a state where the two rotating elements are coupled so as to be able to transmit the driving force via one or more transmission members. Such transmission members include various members (shafts, gear mechanisms, belts, chains, etc.) that transmit rotation at the same speed or at different speeds, and an engagement device that selectively transmits rotation and driving force. (Such as a friction engagement device or a meshing engagement device) may be included. However, in the case of “driving connection” for each rotating element of the differential gear mechanism, the state in which the three or more rotating elements included in the differential gear mechanism are drivingly connected without intervening other rotating elements. Shall point to. Further, in the following description, regarding the arrangement of the two members, “overlapping in a certain direction” means that when a virtual straight line parallel to the line-of-sight direction is moved in each direction orthogonal to the virtual straight line, It means that the region where the virtual straight line intersects both of the two members exists at least in part.

  As shown in FIG. 1, the vehicle drive device 1 according to the present embodiment drives a vehicle (hybrid vehicle) that includes both an internal combustion engine E and a rotating electrical machine MG as drive power sources for wheels W (hybrid vehicle). Hybrid vehicle drive device). The vehicle drive device 1 of the present embodiment is configured as a drive device for an FF (Front Engine Front Drive) vehicle. Here, the internal combustion engine E is a prime mover (for example, a gasoline engine, a diesel engine, or the like) that is driven by combustion of fuel inside the engine to extract power. The rotating electrical machine MG is used as a concept including a motor (electric motor), a generator (generator), and a motor / generator that functions as both a motor and a generator as necessary.

  As shown in FIG. 1, the vehicle drive device 1 is drive-coupled to the input shaft I, which is drive-coupled to the internal combustion engine E, an output differential gear device DF that is drive-coupled to the wheels W, and the input shaft I. A rotating electrical machine MG, a transmission TM, and a counter gear mechanism CG. The transmission TM shifts the rotation of the input shaft I and transmits it to the transmission output member 70. The counter gear mechanism CG has a counter shaft 81 that is a shaft parallel to the axial direction L, and transmits the rotation of the speed change output member 70 to the output differential gear device DF. The vehicle drive device 1 includes a case 2 that houses the transmission TM. In addition to the transmission device TM, the input shaft I, the output differential gear device DF, the rotating electrical machine MG, and the counter gear mechanism CG are also accommodated in the case 2. The vehicle drive device 1 is disposed on the first axial side L1 which is one side in the axial direction L with respect to the internal combustion engine E. Here, the axial direction L is the axial direction of the transmission apparatus TM (the direction along the rotational axis of the transmission apparatus TM). The side opposite to the axial first side L1 (the other side in the axial direction L) is defined as the axial second side L2. In the present embodiment, the vehicle drive device 1 is mounted on the vehicle such that the axial direction L is along the lateral width direction of the vehicle.

  The input shaft I is drivingly connected to an internal combustion engine output shaft Eo that is an output shaft of the internal combustion engine E. The input shaft I and the internal combustion engine output shaft Eo may be directly connected or may be connected via another member such as a damper. In the present embodiment, as shown in FIG. 1, the input shaft I is drivingly connected to the internal combustion engine output shaft Eo via a torque converter TC having a lockup clutch LC and a damper DP. The torque converter TC is disposed between the internal combustion engine E and the transmission TM in the axial direction L. In the present embodiment, the input shaft I corresponds to an “input member”.

  The output differential gear device DF includes an input gear 91 and a main body 92 connected to the input gear 91. In this example, the input gear 91 is an external gear. The main body 92 has a plurality of bevel gears that mesh with each other and a housing case that houses them, and constitutes a differential gear mechanism. The output differential gear device DF distributes and transmits rotation and torque input to the input gear 91 from the counter gear mechanism CG side to the two left and right wheels W by the main body 92.

  The rotating electrical machine MG includes a stator St fixed to the case 2 and a rotor Ro that is rotatably supported with respect to the stator St. In the present embodiment, the rotor Ro is disposed on the radially inner side of the stator St. The core (rotor core) of the rotor Ro is connected to the rotor shaft 20 so as to rotate integrally. In the present embodiment, the rotating electrical machine MG (rotor Ro) is drivingly connected to the input shaft I via a power transmission mechanism 10 described later.

  The counter gear mechanism CG is disposed on the second side L2 in the axial direction with respect to the third gear 83 and the third gear 83 and the input gear 91 of the output differential gear device DF. And a fourth gear 84 that meshes. In this example, both the third gear 83 and the fourth gear 84 are external gears, and the output gear 71 is also an external gear. In this example, the fourth gear 84 is formed with a smaller diameter than the third gear 83. In the present embodiment, the counter gear mechanism CG functions as a speed reduction mechanism (counter speed reduction mechanism). Specifically, the counter gear mechanism CG decelerates the rotation input to the third gear 83 from the transmission device TM side and amplifies the torque input to the third gear 83 from the transmission device TM side, This is transmitted to the output differential gear unit DF (input gear 91). At this time, torque in the same direction as the rotation direction of the transmission output member 70 is transmitted to the input gear 91.

  As shown in FIGS. 2 and 3, the transmission TM includes a first differential gear mechanism G1 and a second differential gear mechanism G2. The second differential gear mechanism G2 is disposed on the second axial side L2 with respect to the first differential gear mechanism G1. That is, the second differential gear mechanism G2 is disposed between the internal combustion engine E and the first differential gear mechanism G1 in the axial direction L. In this example, the torque converter TC and the first differential gear mechanism in the axial direction L are arranged. It is arranged between G1.

  The first differential gear mechanism G1 has three rotating elements including a rotating element that is drivingly connected to the input shaft I. The second differential gear mechanism G2 has four or more rotating elements including a rotating element that is drivingly connected to the first differential gear mechanism G1 and a rotating element that is drivingly connected to the transmission output member 70. In the present embodiment, the first differential gear mechanism G1 includes a third rotating element e3 as a rotating element that is drivingly connected to the input shaft I. In the present example, the third rotating element e3 is coupled to rotate integrally with the input shaft I. Further, in the present embodiment, the first differential gear mechanism G1 includes two rotary elements other than the third rotary element e3, the first rotary element e1 fixed to the case 2 and the second differential gear mechanism G2. And a second rotary element e2 that is drivingly connected.

  In the present embodiment, the order of the rotational speed of each rotary element of the first differential gear mechanism G1 (arrangement order in the speed diagram or collinear chart) is the first rotary element e1, the second rotary element e2, and the third rotation. The order is element e3. Therefore, in the present embodiment, the first differential gear mechanism G1 decelerates the rotation of the input shaft I transmitted to the third rotating element e3 and amplifies the torque of the input shaft I transmitted to the third rotating element e3. Then, it is transmitted to the second differential gear mechanism G2 via the second rotating element e2. In the present embodiment, the second rotating element e2 is coupled to a later-described seventh rotating element e7 of the second differential gear mechanism G2 via the first clutch C1, and via the third clutch C3. The second differential gear mechanism G2 is connected to a later-described fourth rotating element e4. Therefore, when the first clutch C1 is engaged, the torque amplified by the first differential gear mechanism G1 is transmitted to the seventh rotating element e7 of the second differential gear mechanism G2, and when the third clutch C3 is engaged. The torque amplified by the first differential gear mechanism G1 is transmitted to the fourth rotating element e4 of the second differential gear mechanism G2. In this example, in a state where the first clutch C1 is directly connected and engaged, the second rotating element e2 of the first differential gear mechanism G1 and the seventh rotating element e7 of the second differential gear mechanism G2 rotate integrally, In a state where the three clutches C3 are directly connected and engaged, the second rotating element e2 of the first differential gear mechanism G1 and the fourth rotating element e4 of the second differential gear mechanism G2 rotate integrally. In the present embodiment, the first differential gear mechanism G1 is configured by a single pinion type planetary gear mechanism having a sun gear, a carrier, and a ring gear, and the first rotating element e1 is configured by the sun gear. The second rotating element e2 is configured, and the third rotating element e3 is configured by the ring gear.

  In the present embodiment, the second differential gear mechanism G2 includes two rotation elements, a fourth rotation element e4 and a seventh rotation element e7, as the rotation elements that are drivingly connected to the first differential gear mechanism G1. . As described above, the fourth rotating element e4 is connected to the second rotating element e2 of the first differential gear mechanism G1 via the third clutch C3, and the seventh rotating element e7 is connected to the first clutch C1. It is connected to the second rotating element e2 of the first differential gear mechanism G1. In this example, the fourth rotating element e4 is selectively fixed to the case 2 by the first brake B1. In the present embodiment, the second differential gear mechanism G <b> 2 includes a sixth rotating element e <b> 6 as a rotating element that is drivingly connected to the transmission output member 70. In the present example, the sixth rotating element e6 is coupled to rotate integrally with the output gear 71 (shift output member 70). In the present embodiment, the second differential gear mechanism G2 has four rotating elements, and a fifth rotating element other than the fourth rotating element e4, the sixth rotating element e6, and the seventh rotating element e7, It has a rotating element e5. In the present embodiment, the fifth rotating element e5 is connected to the input shaft I via the second clutch C2, and is selectively fixed to the case 2 by the second brake B2. Therefore, when the second clutch C2 is engaged, the torque of the input shaft I is transmitted as it is (that is, not amplified by the first differential gear mechanism G1) to the fifth rotating element e5 of the second differential gear mechanism G2. Is done. In this example, the fifth rotating element e5 rotates integrally with the input shaft I in a state where the second clutch C2 is directly engaged.

  In this embodiment, the order of the rotation speed of each rotation element of the second differential gear mechanism G2 is the order of the fourth rotation element e4, the fifth rotation element e5, the sixth rotation element e6, and the seventh rotation element e7. ing. In the present embodiment, the second differential gear mechanism G2 is configured by combining two single pinion type planetary gear mechanisms. Specifically, among the three rotating elements of each of the two single pinion type planetary gear mechanisms, two are connected to each other so as to rotate integrally with each other, whereby a second having four rotating elements as a whole. A differential gear mechanism G2 is configured. Specifically, if one of the two single pinion planetary gear mechanisms is a first planetary gear mechanism and the other is a second planetary gear mechanism, the ring gear of the first planetary gear mechanism becomes the sun gear of the second differential gear mechanism. In addition, the carrier of the first planetary gear mechanism is connected to the carrier of the second planetary gear mechanism. A fourth rotating element e4 is constituted by the sun gear of the first planetary gear mechanism, and a fifth rotating element e5 is constituted by the ring gear of the second planetary gear mechanism. The carrier of the first planetary gear mechanism and the second planetary gear that rotate integrally. The sixth rotating element e6 is configured by the carrier of the gear mechanism, and the seventh rotating element e7 is configured by the ring gear of the first planetary gear mechanism and the sun gear of the second planetary gear mechanism that rotate integrally.

  The transmission TM is a stepped automatic transmission that can form a plurality of gears with different gear ratios, and changes the rotation of the input shaft I at a gear ratio according to the gears that are formed to produce a gear shift output. Transmit to member 70. As described above, in the present embodiment, the transmission device TM includes the first clutch C1, the second clutch C2, the third clutch C3, the first brake B1, and the second brake B2 as the gear shift engagement device. Thus, a plurality of shift speeds having different gear ratios are formed in accordance with the respective engagement states of the shift engagement devices. Although details are omitted, in this embodiment, it is possible to form six forward gears with different gear ratios and one reverse gear, and two of the plurality of gear engaging devices are engaged. At the same time, the other gear positions are formed with the other gears released. In the present embodiment, as shown in FIG. 2, the first brake B1 is a band brake using a brake band, and the shift engagement device other than the first brake B1 includes a plurality of friction plates (frictions). A multi-plate clutch or multi-plate brake using a member.

  As shown in FIGS. 1 to 4, in this embodiment, the power transmission mechanism 10 that transmits a driving force between the input shaft I and the rotating electrical machine MG includes a first gear 11 and a second gear 12. Yes. Here, the first gear 11 is a gear that is connected to the input shaft I and disposed on the first axial side L1 with respect to the first differential gear mechanism G1. In the present embodiment, the first gear 11 is an external gear arranged coaxially with the input shaft I. The first gear 11 is coupled to rotate integrally with the input shaft I at the end of the input shaft I on the first axial side L1. The second gear 12 is a gear that is connected to the rotating electrical machine MG and disposed on the first axial side L1 with respect to the rotating electrical machine MG. In the present embodiment, the second gear 12 is an external gear arranged coaxially with the rotating electrical machine MG (rotor shaft 20). The second gear 12 is coupled to rotate integrally with the rotor shaft 20 at the end portion of the first axial side L1 of the rotor shaft 20. In the present embodiment, the power transmission mechanism 10 further includes an idler gear 13 (also referred to as idle gear or idle gear) that meshes with both the first gear 11 and the second gear 12. Therefore, in the present embodiment, the driving force of the rotating electrical machine MG is transmitted to the input shaft I via the second gear 12, the idler gear 13, and the first gear 11. In the present embodiment, the power transmission mechanism 10 functions as a speed reduction mechanism. Specifically, the power transmission mechanism 10 decelerates the rotation input to the second gear 12 from the rotating electrical machine MG side and amplifies the torque input to the second gear 12 from the rotating electrical machine MG side, It is transmitted to the input shaft I (first gear 11). At this time, torque in the same direction as the rotation direction of the rotating electrical machine MG is transmitted to the input shaft I.

  As shown in FIGS. 1, 2, 4, and 5, the input shaft I, the speed change device TM, the output gear 71 (the speed change output member 70), and the first gear 11 are arranged on the first shaft A1. Yes. The third gear 83 and the fourth gear 84 (counter gear mechanism CG) are disposed on the second axis A2. The input gear 91 (output differential gear device DF) is disposed on the third axis A3. The rotor shaft 20 (the rotating electrical machine MG) and the second gear 12 are disposed on the fourth shaft A4. The idler gear 13 is disposed on the fifth axis A5. The first axis A1, the second axis A2, the third axis A3, the fourth axis A4, and the fifth axis A5 are mutually different axes (virtual axes). In the present embodiment, the first axis A1, the second axis A2, the third axis A3, the fourth axis A4, and the fifth axis A5 are arranged in parallel to each other. Therefore, the axial direction L that is the direction along the first axis A1 is a direction parallel to each of the second axis A2, the third axis A3, the fourth axis A4, and the fifth axis A5 in the present embodiment. In the present embodiment, as shown in FIG. 4, when viewed in the axial direction L, the fifth axis A5 is arranged on a straight line connecting the first axis A1 and the fourth axis A4. In FIGS. 4 and 5, a reference pitch circle is shown for each gear, and a shape of the outer peripheral portion is shown for the stator St (rotating electrical machine MG).

  By the way, it is preferable that the whole apparatus is miniaturized as much as possible in consideration of the vehicle-mounted property of the vehicle drive device 1. In the vehicle drive device 1 disposed adjacent to the internal combustion engine E in the axial direction L, it is particularly preferable that the vehicle drive device 1 be downsized in the axial direction L. Hereinafter, a characteristic configuration for shortening the length in the axial direction L in the vehicle drive device 1 according to the present embodiment will be described.

  As shown in FIGS. 1 and 2, the length of the counter gear mechanism CG in the axial direction L is shorter than the length of the transmission device TM in the axial direction L. For this reason, a space that overlaps with the counter gear mechanism CG when viewed in the axial direction L and that does not include the counter gear mechanism CG exists outside the transmission device TM in the radial direction. By arranging the rotary electric machine MG effectively using this space, at least a part of the rotary electric machine MG can be arranged in the arrangement region in the axial direction L of the transmission apparatus TM, and as a result, the shaft of the entire apparatus The length in the direction L can be shortened. In the present embodiment, as shown in FIG. 2, the space as described above is formed on the first axial side L1 with respect to the counter gear mechanism CG. As shown in FIGS. MG is arranged on the first axial side L1 with respect to the counter gear mechanism CG and at a position overlapping with the counter gear mechanism CG when viewed in the axial direction L. In the present embodiment, as shown in FIG. 5, when viewed in the axial direction L, the entire fourth gear 84 and a part of the third gear 83 of the counter gear mechanism CG overlap with the rotating electrical machine MG. Further, as shown in FIG. 5, when viewed in the axial direction L, the fourth axis A <b> 4 on which the rotating electrical machine MG is disposed is included in the reference pitch circle of the third gear 83. In the present embodiment, as shown in FIGS. 1 and 5, the rotating electrical machine MG is the first differential side L1 in the axial direction with respect to the differential output gear device DF, and the differential output for output is viewed in the axial direction L. It arrange | positions in the position which overlaps with gear apparatus DF.

  From the viewpoint of effectively shortening the length of the entire apparatus in the axial direction L, the protrusion amount of the rotating electrical machine MG to the first axial direction L1 with respect to the transmission device TM is suppressed to a small value, or the protrusion amount is set to zero. It is desirable. In the present embodiment, as shown in FIG. 1, the third gear 83 of the counter gear mechanism CG protrudes on the first axial side L1 with respect to the output differential gear device DF. Therefore, by arranging the third gear 83 close to the second axial side L2, the rotary electric machine MG can be arranged close to the second axial side L2 accordingly, and as a result, the amount of protrusion described above can be reduced. It can be kept small or zero. In view of this point, in the vehicle drive device 1 according to the present embodiment, the second differential gear mechanism G2 is arranged on the second axial side L2 with respect to the first differential gear mechanism G1, so that the second Compared to the case where the differential gear mechanism G2 is disposed on the first axial side L1 with respect to the first differential gear mechanism G1, the rotary gear of the second differential gear mechanism G2 (sixth rotating element e6) is driven. The coupled output gear 71 (shift output member 70) can be arranged close to the second axial side L2. Accordingly, the third gear 83 that meshes with the output gear 71 can also be disposed close to the second axial side L2, and the length of the entire apparatus in the axial direction L can be shortened.

  As described above, by arranging the second differential gear mechanism G2 on the second axial side L2 with respect to the first differential gear mechanism G1, as shown in FIG. 2, the counter gear mechanism CG The second differential gear mechanism G2 and a portion disposed at the same position in the axial direction L. In other words, the counter gear mechanism CG is located at a position overlapping with the second differential gear mechanism G2 in the radial direction (the radial direction of the transmission device TM) in a partial region in the circumferential direction (the circumferential direction of the transmission device TM). Has been placed. That is, the arrangement area of the counter gear mechanism CG in the axial direction L and the arrangement area of the second differential gear mechanism G2 in the axial direction L overlap at least partially. Here, the arrangement region in the axial direction L of the counter gear mechanism CG is a set of arrangement regions in the axial direction L of the third gear 83, the fourth gear 84, and the counter shaft 81, and the second differential. The arrangement region in the axial direction L of the gear mechanism G2 is a set of arrangement regions in the axial direction L of the sun gear, pinion gear, carrier, and ring gear constituting the second differential gear mechanism G2 (when there is a discontinuous portion). This is a region where the discontinuous portion is considered to be continuous. In the present embodiment, as shown in FIG. 2, only the portion on the first axial side L1 of the counter gear mechanism CG (the portion including the entire third gear 83) is connected to the second differential gear mechanism G2 and the axial direction L. Are arranged at the same position. The rotating electrical machine MG has a portion arranged at the same position in the axial direction L as the first differential gear mechanism G1. In other words, the rotating electrical machine MG is arranged at a position overlapping with the first differential gear mechanism G1 in the radial direction (the radial direction of the transmission device TM) in a partial region in the circumferential direction (the circumferential direction of the transmission device TM). Has been. That is, the arrangement area in the axial direction L of the rotating electrical machine MG and the arrangement area in the axial direction L of the first differential gear mechanism G1 at least partially overlap. Here, the arrangement area in the axial direction L of the rotating electrical machine MG is a set of arrangement areas in the axial direction L of the rotor Ro and the stator St (including the coil end portion CE), and the first differential gear mechanism. The arrangement region in the axial direction L of G1 is a set of the arrangement regions in the axial direction L of the sun gear, pinion gear, carrier, and ring gear constituting the first differential gear mechanism G1 (if there is a discontinuous part, Area where the continuous part is considered continuous). In the present embodiment, the entire first differential gear mechanism G1 is arranged so as to be included in the arrangement region in the axial direction L of the rotating electrical machine MG. In the present embodiment, the rotor Ro of the rotating electrical machine MG has a portion arranged at the same position in the axial direction L as the pinion gear P constituting the first differential gear mechanism G1.

  Further, in the present embodiment, the third gear 83 is a gear having an inner diameter support structure, so that the counter shaft 81 is supported on both sides in the axial direction L in the radial direction (the radial direction of the counter gear mechanism CG). Of the third bearing 63 and the fourth bearing 64), the third bearing 63 arranged on the first axial side L1 is arranged close to the second axial side L2, and the rotary electric machine MG is axially arranged accordingly. It is also possible to arrange it close to the second side L2. Here, the inner diameter support structure is a structure having a cylindrical portion having a tooth portion formed on the outer peripheral portion and supported from the radially inner side by a bearing in contact with the inner peripheral surface of the cylindrical portion. That is, as shown in FIG. 2, the third gear 83 includes a cylindrical portion 83 a having a tooth portion 83 b formed on the outer peripheral portion, and the third bearing 63 in contact with the inner peripheral surface of the cylindrical portion 83 a. The third gear 83 is supported from the radially inner side. As a result, the third bearing 63 is positioned on the second side in the axial direction as compared with the case where the third bearing 63 supports the outer peripheral surface of the counter shaft 81 from the radially outer side on the first axial side L1 with respect to the third gear 83. It can be arranged close to L2. The third bearing 63 is in contact with the inner peripheral surface of the cylindrical portion 83a on the first axial side L1 with respect to the connecting portion that connects the cylindrical portion 83a and the counter shaft 81.

  Moreover, in this embodiment, as shown in FIG. 2, the transmission output member 70 is provided with the cylindrical main-body part 72 arrange | positioned on the radial direction outer side of the transmission apparatus TM with respect to the 2nd differential gear mechanism G2. Yes. The cylindrical main body 72 is formed in a cylindrical shape. In the present embodiment, the cylindrical main body 72 has a portion disposed at the same position in the axial direction L as the second differential gear mechanism G2. In other words, the cylindrical main body 72 is disposed at a position overlapping the second differential gear mechanism G2 when viewed in the radial direction (the radial direction of the transmission device TM). That is, the cylindrical main body 72 is disposed so as to cover the second differential gear mechanism G2 from the outside in the radial direction of the transmission apparatus TM. An output gear 71 that meshes with the third gear 83 of the counter gear mechanism CG is provided on the outer peripheral surface of the cylindrical main body 72. In the present embodiment, the cylindrical main body 72 connects the respective carriers of the two planetary gear mechanisms that constitute the second differential gear mechanism G2, and constitutes the sixth rotating element e6 together with these two carriers. .

  As shown in FIG. 2, the transmission output member 70 is rotatably supported with respect to the case 2 from the outer side in the radial direction (the radial direction of the transmission device TM) by a bearing in contact with the outer peripheral surface of the cylindrical main body 72. Yes. In the present embodiment, the fifth bearing 65 that contacts the outer peripheral surface of the cylindrical main body 72 on the first axial side L1 with respect to the output gear 71, and the cylindrical main body on the second axial side L2 with respect to the output gear 71. The speed change output member 70 is rotatably supported with respect to the case 2 by the sixth bearing 66 in contact with the outer peripheral surface of the portion 72. In the present embodiment, the cylindrical sleeve member 3 is press-fitted (tightly fitted) to the inner peripheral surface of the case 2, and each of the fifth bearing 65 and the sixth bearing 66 is formed on the inner peripheral surface of the sleeve member 3. It is fixed to the case 2 in contact. As shown in FIG. 2, the sleeve member 3 has a notch 3a in a partial region in the circumferential direction (the circumferential direction of the transmission TM). That is, the sleeve member 3 has a shape that is partly cut out at the site where the cutout portion 3a is formed. The notch 3 a is formed between the fifth bearing 65 and the sixth bearing 66 in the axial direction L. A part of the third gear 83 is inserted radially inward of the sleeve member 3 from the notch 3a, and the output gear 71 and the third gear 83 mesh with each other on the radially inner side of the sleeve member 3. Yes. When the speed change output member 70 is supported from the inner side in the radial direction, generally, a wall portion extending from the peripheral wall portion of the case 2 to the inner side in the radial direction is required. By adopting a configuration in which the speed change output member 70 is supported from the outside in the radial direction by the bearing in contact, it is possible to reduce the length of the entire apparatus in the axial direction L by eliminating such a wall portion. ing.

  Furthermore, in this embodiment, as shown in FIG. 2, the second brake B2 is outside the radial direction of the transmission TM with respect to the second clutch C2, and is in the same position in the axial direction L as the second clutch C2. It has a part arranged in. In other words, the second brake B2 is disposed at a position overlapping the second clutch C2 when viewed in the radial direction (the radial direction of the transmission device TM). Specifically, the cylindrical portion that supports the friction plate in the second clutch C2 from the outside in the radial direction is also used to support the friction plate in the second brake B2 from the inside in the radial direction. The arrangement is simple. The fourth gear 84 of the counter gear mechanism CG has a portion that is disposed at the same position in the axial direction L as both the second brake B2 and the second clutch C2. In other words, the fourth gear 84 includes both the second brake B2 and the second clutch C2 when viewed in the radial direction (radial direction of the transmission device TM) in a partial region in the circumferential direction (circumferential direction of the transmission device TM). It is arranged at the overlapping position. Thereby, the length of the axial direction L of the space in which the fourth gear 84, the second brake B2, and the second clutch C2 are arranged is shortened, and the length of the entire device in the axial direction L is shortened. Yes. In the present embodiment, the second brake B2 corresponds to a “first engagement element”, and the second clutch C2 corresponds to a “second engagement element”.

  In the present embodiment, the length in the axial direction L of the entire apparatus is also shortened by shortening the length in the axial direction L of the space occupied by the power transmission mechanism 10. Specifically, the following configuration is adopted for the first gear 11, the second gear 12, and the idler gear 13 provided in the power transmission mechanism 10. As shown in FIG. 2, the first gear 11 and the second gear 12 have portions disposed at the same position in the axial direction L. In other words, the second gear 12 is arranged at a position overlapping the first gear 11 in the radial direction (the radial direction of the first gear 11) in a partial region in the circumferential direction (the circumferential direction of the first gear 11). Has been. In the present embodiment, the idler gear 13 also has a portion arranged at the same position in the axial direction L as the first gear 11 and the second gear 12. In other words, the idler gear 13 overlaps with the first gear 11 when viewed in the radial direction (radial direction of the first gear 11) in a partial region in the circumferential direction (circumferential direction of the first gear 11). In a partial region in the circumferential direction (circumferential direction of the second gear 12), it is arranged at a position overlapping the second gear 12 when viewed in the radial direction (radial direction of the second gear 12). In this example, the tooth portion 11b of the first gear 11, the tooth portion 12b of the second gear 12, and the tooth portion 13b of the idler gear 13 have portions arranged at the same position in the axial direction L. Furthermore, in the present embodiment, both the first gear 11 and the second gear 12 are gears having an inner diameter support structure, and the idler gear 13 is also a gear having an inner diameter support structure. Specifically, the first gear 11 includes a first cylindrical portion 11a having a tooth portion 11b formed on the outer peripheral portion, and a first bearing 61 in contact with the inner peripheral surface of the first cylindrical portion 11a. The first gear 11 is supported from the radially inner side. In this example, the first bearing 61 is in contact with the inner peripheral surface of the first cylindrical portion 11a on the second axial side L2 with respect to the connecting portion 11d that connects the first cylindrical portion 11a and the input shaft I. ing. Further, the second gear 12 has a cylindrical portion 12a in which a tooth portion 12b is formed on the outer peripheral portion, and the second gear 12 is radially arranged by a second bearing 62 in contact with the inner peripheral surface of the cylindrical portion 12a. Supported from the inside. In this example, the second bearing 62 is in contact with the inner peripheral surface of the cylindrical portion 12a on the first axial side L1 with respect to the connecting portion that connects the cylindrical portion 12a and the rotor shaft 20. The idler gear 13 has a cylindrical portion 13a having a tooth portion 13b formed on the outer peripheral portion thereof, and the idler gear 13 is supported from the radially inner side by a seventh bearing 67 in contact with the inner peripheral surface of the cylindrical portion 13a. . In the present example, the seventh bearing 67 is in contact with the inner peripheral surface of the cylindrical portion 13a over substantially the entire region in the axial direction L.

  In the present embodiment, as shown in FIG. 2, the first gear 11 includes a second cylindrical portion 11c connected to the input shaft I, and the first cylindrical portion 11a and the second cylindrical portion 11c are It is connected by a connecting portion 11d extending in the radial direction. 11 d of connection parts have connected the edge part of the axial direction 1st side L1 in the 1st cylindrical part 11a, and the edge part of the axial direction 2nd side L2 in the 2nd cylindrical part 11c. And in addition to said 1st bearing 61 which contact | connects the internal peripheral surface of the 1st cylindrical part 11a in the axial direction 2nd side L2 with respect to the connection part 11d, in the axial direction 1st side L1 with respect to the connection part 11d An eighth bearing 68 in contact with the outer peripheral surface of the second cylindrical portion 11 c is provided, and the first gear 11 is rotatably supported with respect to the case 2 by the first bearing 61 and the eighth bearing 68.

[Other Embodiments]
Other embodiments of the vehicle drive device will be described. Note that the configurations disclosed in the following embodiments can be applied in combination with the configurations disclosed in other embodiments as long as no contradiction arises.

(1) In the above embodiment, the first differential gear mechanism G1 is configured by a single pinion type planetary gear mechanism, and the second differential gear mechanism G2 is configured by combining two single pinion type planetary gear mechanisms. The case has been described as an example. However, the first differential gear mechanism G1 and the second differential gear mechanism G2 are not limited to such a configuration, and the planetary gear mechanism of another configuration such as a double pinion type planetary gear mechanism is used. It may be configured. For example, as shown in FIG. 6, a Ravigneaux-type planetary gear having a second differential gear mechanism G2 having a first sun gear (a sun gear meshing with a long pinion gear), a second sun gear (a sun gear meshing with a short pinion gear), a carrier, and a ring gear. You may comprise with a gear mechanism. In this case, the first sun gear constitutes the fourth rotating element e4, the carrier constitutes the fifth rotating element e5, the ring gear constitutes the sixth rotating element e6, and the second sun gear constitutes the seventh rotating element e7. The In the above-described embodiment, the configuration in which the second differential gear mechanism G2 has four rotating elements has been described as an example. However, the second differential gear mechanism G2 has a configuration having five or more rotating elements. You can also.

(2) In the above embodiment, the configuration in which the power transmission mechanism 10 includes the idler gear 13 that meshes with both the first gear 11 and the second gear 12 has been described as an example. However, without being limited to such a configuration, the power transmission mechanism 10 may be configured to include a chain, a belt, or the like for drivingly connecting the first gear 11 and the second gear 12.

(3) In the above embodiment, the configuration in which all of the first gear 11, the second gear 12, the idler gear 13, and the third gear 83 are gears having an inner diameter support structure has been described as an example. However, the present invention is not limited to such a configuration, and some or all of these gears may be gears that are supported from the outside in the radial direction by bearings that contact the outer peripheral surface of the rotation shaft of the gear. .

(4) In the above embodiment, the speed change output member 70 is supported by the bearing in contact with the outer peripheral surface of the cylindrical main body 72 so as to be rotatable with respect to the case 2 from the outside in the radial direction (the radial direction of the transmission TM). The configuration to be described has been described as an example. However, the present invention is not limited to such a configuration, and the transmission output member 70 may be supported by the bearing so as to be rotatable with respect to the case 2 from the inside in the radial direction.

(5) Regarding other configurations, it should be understood that the embodiments disclosed herein are merely examples in all respects. Accordingly, those skilled in the art can make various modifications as appropriate without departing from the spirit of the present disclosure.

[Overview of the above embodiment]
Hereinafter, an outline of the vehicle drive device described above will be described.

  The vehicle drive device includes an input member (I) that is drivingly connected to the internal combustion engine (E), an output differential gear device (DF) that is drivingly connected to the wheels (W), and the input member (I). A rotating electrical machine (MG) that is drivingly connected, a transmission (TM) that changes the rotation of the input member (I) and transmits it to the transmission output member (70), and an axial direction (L of the transmission (TM)) ) And a counter gear mechanism (CG) for transmitting the rotation of the speed change output member (70) to the output differential gear device (DF), the internal combustion engine (E ) On the first axial side (L1), which is one side of the axial direction (L), and the transmission (TM) includes the input member (1). I) has three rotating elements (e1 to e3) including a rotating element (e3) drivingly connected to The first differential gear mechanism (G1), the rotation elements (e4, e7) drivingly connected to the first differential gear mechanism (G1), and the rotation element (e6) drivingly connected to the speed change output member (70) And a second differential gear mechanism (G2) having four or more rotating elements (e4 to e7) including the first differential gear mechanism (G1). ) Is disposed on the second axial side (L2) opposite to the first axial side (L1), and the counter gear mechanism (CG) is arranged in the circumferential direction of the transmission (TM). Is disposed at a position overlapping with the second differential gear mechanism (G2) when viewed in the radial direction of the transmission (TM), and the rotating electrical machine (MG) is connected to the counter gear mechanism (CG). ) With respect to the first axial side (L1) and viewed in the axial direction (L). The rotating electrical machine (MG) is disposed in a position overlapping the transmission gear mechanism (CG), and the rotating electric machine (MG) is seen in the radial direction of the transmission (TM) in a partial region in the circumferential direction of the transmission (TM). It arrange | positions in the position which overlaps with said 1st differential gear mechanism (G1).

  With such a configuration, in the configuration in which the vehicle drive device (1) is disposed on the first axial side (L1) with respect to the internal combustion engine (E), the second differential gear mechanism (G2) has the first difference. The rotating electrical machine (MG) is disposed on the first axial side (L1) with respect to the counter gear mechanism (CG) and disposed on the second axial side (L2) with respect to the dynamic gear mechanism (G1). Arranged at a position overlapping with the counter gear mechanism (CG) when viewed in the axial direction (L), the rotating electrical machine (MG) is further connected to the transmission (TM) in a partial region in the circumferential direction of the transmission (TM). The first differential gear mechanism (G1) is disposed at a position overlapping the first differential gear mechanism (G1) when viewed in the radial direction. That is, the rotating electrical machine (MG) overlaps with the counter gear mechanism (CG) as viewed in the axial direction (L) and is formed on the radially outer side of the first differential gear mechanism (G1), and the counter gear mechanism (CG). ) Is placed using a space that is not placed. Thereby, the radial protrusion of the rotating electrical machine (MG) can be suppressed as compared with the case where the rotating electrical machine (MG) is arranged at a position that does not overlap with the counter gear mechanism (CG) when viewed in the axial direction (L). it can. Here, the second differential gear mechanism (G2) has a rotating element (e6) that is drivingly connected to the transmission output member (70). Therefore, the second differential gear mechanism (G2) is arranged on the second axial side (L2) with respect to the first differential gear mechanism (G1), so that the second differential gear mechanism (G2) is the first differential gear mechanism (G2). Compared to the case where the differential gear mechanism (G1) is arranged on the first axial side (L1), the shift output member (70) can be arranged closer to the second axial side (L2). It becomes. As a result, the end portion on the first axial side (L1) of the counter gear mechanism (CG) that transmits the rotation of the speed change output member (70) to the output differential gear device (DF) is connected to the second axial side ( L2) can be easily arranged, and accordingly, the rotating electrical machine (MG) arranged using the above space can be arranged close to the second axial side (L2). It becomes possible. As a result, the amount of protrusion of the rotating electrical machine (MG) toward the first axial direction (L1) with respect to the transmission (TM) can be suppressed to be small, and the amount of protrusion can be made zero. That is, it is possible to reduce the size of the entire apparatus while including the rotating electrical machine (MG) as a driving force source for the wheels (W).

  Here, a power transmission mechanism (10) for transmitting a driving force between the input member (I) and the rotating electrical machine (MG) is coupled to the input member (I) and the first differential gear. A first gear (11) disposed on the first axial side (L1) with respect to the mechanism (G1), and the shaft connected to the rotating electrical machine (MG) and connected to the rotating electrical machine (MG). A second gear (12) disposed on the first direction side (L1), wherein the second gear (12) is arranged in a partial region in the circumferential direction of the first gear (11). It is preferable that it is arranged at a position overlapping with the first gear (11) when viewed in the radial direction of (11).

  According to this configuration, the length in the axial direction (L) of the space occupied by the power transmission mechanism (10) can be kept short. Therefore, the axial length (L) of the entire apparatus can be shortened including the power transmission mechanism (10) required when the rotating electrical machine (MG) is provided.

  The counter gear mechanism (CG) includes a third gear (83) meshing with the output gear (71) of the speed change output member (70), and the second axial side of the third gear (83). L2) and a fourth gear (84) that meshes with the input gear (91) of the output differential gear device (DF), and has a cylindrical portion with teeth formed on the outer periphery, The structure supported from the radially inner side by the bearing in contact with the inner peripheral surface of the cylindrical portion is preferably an inner diameter support structure, and the third gear (83) is preferably the gear of the inner diameter support structure.

  According to this configuration, the bearing (63) that supports the third gear (83) has the shaft (81) of the third gear (83) on the first axial side (L1) with respect to the third gear (83). The bearing (63) that supports the third gear (83) can be disposed closer to the second axial side (L2) than when the outer peripheral surface is supported from the radially outer side. Therefore, it is possible to arrange the rotating electrical machine (MG) closer to the second axial side (L2), and the length of the entire apparatus in the axial direction (L) can be further reduced. .

  The transmission (TM) includes a case (2) that houses the transmission output member (70) in the radial direction of the transmission (TM) with respect to the second differential gear mechanism (G2). A cylindrical main body (72) disposed outside is provided, and an output gear (71) that meshes with the gear (83) of the counter gear mechanism (CG) is provided on the outer peripheral surface of the cylindrical main body (72). By means of bearings (65, 66) in contact with the outer peripheral surface of the cylindrical main body (72), the shift output member (70) is moved from the radially outer side of the transmission (TM) to the case (2). It is preferable that it is supported rotatably.

  When the speed change output member (70) is supported by the bearing from the inside in the radial direction, generally, a wall portion extending from the peripheral wall portion of the case (2) to the inside in the radial direction is required. The length of the entire apparatus in the axial direction (L) can be shortened by the amount that such a wall portion is unnecessary.

  As described above, the power transmission mechanism (10) includes the first gear (11) and the second gear (12), and the second gear (12) is arranged around the first gear (11). In a configuration where the first gear (11) is disposed at a position overlapping with the first gear (11) when viewed in the radial direction of the first gear (11) in a partial region of the direction, a cylindrical portion having teeth formed on the outer peripheral portion And the first gear (11) and the second gear (12) both have a structure supported from the radially inner side by a bearing in contact with the inner peripheral surface of the cylindrical portion as an inner diameter support structure. It is preferable that the gear has the inner diameter support structure.

  According to this configuration, including the bearing (61) supporting the first gear (11) and the bearing (62) supporting the second gear (12), the axial direction of the space occupied by the power transmission mechanism (10) ( L) can be shortened.

  The power transmission mechanism (10) further includes an idler gear (13) that meshes with both the first gear (11) and the second gear (12), and the idler gear (13) includes the inner diameter support structure. It is preferable that the gear is.

  According to this configuration, the diameters of the first gear (11) and the second gear (12) are kept small compared to the case where the first gear (11) and the second gear (12) are directly meshed with each other. A desired gear ratio (reduction ratio) can be ensured. In addition, the axial length (L) of the space occupied by the power transmission mechanism (10) including the bearing (67) supporting the idler gear (13) can be reduced.

  In addition, the first engagement element (B2) is outside in the radial direction of the transmission (TM) with respect to the second engagement element (C2) and seen in the radial direction of the transmission (TM). The counter gear mechanism (CG) is disposed at a position overlapping with the second engagement element (C2), the third gear (83) meshing with the output gear (71) of the transmission output member (70), A fourth gear (84) disposed on the second axial side (L2) with respect to the third gear (83) and meshing with the input gear (91) of the output differential gear device (DF), When the fourth gear (84) is seen in the radial direction of the transmission (TM) in a partial region in the circumferential direction of the transmission (TM), the first engagement element (B2) and the second engagement It is preferable that the element (C2) is disposed at a position overlapping with both of the elements (C2).

  According to this structure, compared with the case where the first engagement element (B2) and the second engagement element (C2) are arranged side by side in the axial direction (L), the fourth gear (84), the first engagement element Shortening the length in the axial direction (L) of the entire apparatus by shortening the length in the axial direction (L) of the space in which the combination element (B2) and the second engagement element (C2) are arranged. Can do.

1: vehicle drive device 2: case 10: power transmission mechanism 11: first gear 12: second gear 13: idler gear 70: transmission output member 71: output gear 72: cylindrical main body 81: counter shaft (in the axial direction) Parallel axes)
83: Third gear 84: Fourth gear 91: Input gear B2: Second brake (first engagement element)
C2: Second clutch (second engagement element)
CG: counter gear mechanism DF: differential gear device for output E: internal combustion engine G1: first differential gear mechanism G2: second differential gear mechanism I: input shaft (input member)
L: Axial direction L1: Axial direction first side L2: Axial direction second side MG: Rotating electrical machine TM: Transmission device W: Wheel e1: First rotating element (rotating element)
e2: Second rotation element (rotation element)
e3: Third rotating element (rotating element driven and connected to the input member)
e4: Fourth rotating element (rotating element drivingly connected to the first differential gear mechanism)
e5: Fifth rotating element (rotating element)
e6: Sixth rotating element (rotating element drivingly connected to the speed change output member)
e7: Seventh rotating element (rotating element drivingly connected to the first differential gear mechanism)

Claims (7)

An input member that is drivingly connected to the internal combustion engine, an output differential gear device that is drivingly connected to the wheels, a rotating electrical machine that is drivingly connected to the input member, and a speed change of the rotation of the input member to the speed change output member A transmission for transmission, and a counter gear mechanism that has an axis parallel to the axial direction of the transmission and transmits the rotation of the transmission output member to the differential gear device for output. A vehicle drive device disposed on an axial first side that is one side of the axial direction,
The transmission includes a first differential gear mechanism having three rotating elements including a rotating element that is drivingly connected to the input member, a rotating element that is drivingly connected to the first differential gear mechanism, and the speed change output member. A second differential gear mechanism having four or more rotating elements including a rotating element drivingly connected to
The second differential gear mechanism is disposed on the second axial side opposite to the first axial side with respect to the first differential gear mechanism,
The counter gear mechanism is disposed at a position overlapping with the second differential gear mechanism when viewed in the radial direction of the transmission in a partial region of the transmission in the circumferential direction;
The rotating electrical machine is disposed on the first axial side with respect to the counter gear mechanism and at a position overlapping the counter gear mechanism when viewed in the axial direction, and the rotating electrical machine is disposed on the transmission device. A vehicle drive device that is disposed at a position overlapping with the first differential gear mechanism as viewed in the radial direction of the transmission in a partial region in the circumferential direction. A power transmission mechanism for transmitting a driving force between the input member and the rotating electrical machine is coupled to the input member and disposed on the first axial side with respect to the first differential gear mechanism. A first gear and a second gear coupled to the rotating electrical machine and disposed on the first axial side with respect to the rotating electrical machine,
2. The vehicle according to claim 1, wherein the second gear is disposed at a position overlapping with the first gear when viewed in a radial direction of the first gear in a partial region in a circumferential direction of the first gear. Drive device. The counter gear mechanism includes a third gear that meshes with the output gear of the speed change output member, and a fourth gear that is disposed on the second axial side of the third gear and meshes with the input gear of the differential gear device for output. With gears,
A structure having a cylindrical part with teeth formed on the outer peripheral part and supported from the radially inner side by a bearing in contact with the inner peripheral surface of the cylindrical part, as an inner diameter support structure,
The vehicle drive device according to claim 1, wherein the third gear is a gear having the inner diameter support structure. A case for housing the transmission,
The transmission output member includes a cylindrical main body portion disposed on the outer side in the radial direction of the transmission with respect to the second differential gear mechanism,
An output gear that meshes with the gear of the counter gear mechanism is provided on the outer peripheral surface of the cylindrical main body,
4. The shift output member is supported by the bearing in contact with the outer peripheral surface of the cylindrical main body so as to be rotatable with respect to the case from the outside in the radial direction of the transmission. The vehicle drive device described in 1. A structure having a cylindrical part with teeth formed on the outer peripheral part and supported from the radially inner side by a bearing in contact with the inner peripheral surface of the cylindrical part, as an inner diameter support structure,
The vehicle drive device according to claim 2, wherein both the first gear and the second gear are gears of the inner diameter support structure. The power transmission mechanism further comprises an idler gear that meshes with both the first gear and the second gear;
The vehicle drive device according to claim 5, wherein the idler gear is a gear having the inner diameter support structure. The first engagement element is disposed radially outside the transmission with respect to the second engagement element, and overlaps the second engagement element when viewed in the radial direction of the transmission;
The counter gear mechanism includes a third gear that meshes with the output gear of the speed change output member, and a fourth gear that is disposed on the second axial side of the third gear and meshes with the input gear of the differential gear device for output. With gears,
The fourth gear is disposed at a position overlapping with both the first engagement element and the second engagement element when viewed in the radial direction of the transmission in a partial region in the circumferential direction of the transmission. The vehicle drive device according to any one of claims 1 to 6.

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