JP2014024412A - Vehicle drive device - Google Patents

Abstract

An object of the present invention is to provide a vehicle drive device capable of suppressing an increase in power loss for driving an oil pump even when a differential gear device vibrates.
A vehicle drive device 1 includes an input member I, an output member G, a rotating electrical machine MG1, a differential gear device DG having three rotating elements S, CA, RI, and an oil pump 37. The rotating electrical machine MG1 includes a cylindrical rotor shaft 44 that is disposed coaxially with the input member I and supports the rotor body 43. A pump shaft 36 penetrating the rotor shaft 44 is coupled to the input member I and coupled to rotate integrally with the pump rotor 35. The input member I and the second rotating element CA are drivingly coupled in a state where they can be moved relative to each other.
[Selection] Figure 2

Description

  The present invention includes an input member drivingly connected to an internal combustion engine, an output member drivingly connected to a wheel, a rotating electrical machine having a rotor body, a first rotating element drivingly connected to the rotor body, and a driving connection to the input member. The present invention relates to a vehicle drive device including a differential gear device having a second rotary element and a third rotary element drivingly connected to an output member, and an oil pump having a pump shaft and a pump rotor.

  As such a vehicle drive device, for example, a device described in Japanese Patent Application Laid-Open No. 2011-183946 (Patent Document 1) is already known. In the apparatus described in Patent Document 1, as shown in FIGS. 3 and 4 of Patent Document 1, the pump drive shaft 54 (pump shaft) of the oil pump 55 is a cylindrical first rotor shaft 31. It is inserted through the [rotor shaft] and connected so as to rotate integrally with the input shaft I [input member] and the pump rotor on both sides in the axial direction. The input member and the carrier CA [second rotating element] of the power distribution device PT [differential gear device] are integrated and connected by welding or the like. Thus, in the apparatus described in Patent Document 1, the first rotor Ro1 [rotor body] of the first rotating electrical machine MG1 [rotating electrical machine] and the pump rotor of the oil pump are connected to the rotor shaft and the first rotating element [sun gear S]. , The second rotating element, the input member, and the pump shaft are integrally connected as a whole.

  By the way, due to individual manufacturing errors of the rotating electrical machine, errors in assembling the rotating electrical machine to the vehicle drive device, and the like, a certain amount of vibration may occur when the rotating electrical machine (rotor body) is driven. Even if there is no such error, vibration may occur due to the influence of cogging torque, torque ripple, and the like. In such a case, in the structure of Patent Document 1 in which the rotor body and the pump rotor are integrally connected as a whole, vibration generated in the rotating electrical machine (rotor body) is transmitted to the pump rotor via the differential gear device. End up. Further, the meshing vibration generated in each gear of the differential gear device is also transmitted to the pump rotor. If the pump rotor is driven in a vibrating state, the power loss for driving the oil pump increases by the amount of the vibration. As a result, the energy efficiency of the entire vehicle drive device is reduced.

JP 2011-183946 A

  Therefore, it is desired to realize a vehicle drive device that can suppress an increase in power loss for driving the oil pump even when the differential gear device vibrates.

  An input member drivingly connected to an internal combustion engine, an output member drivingly connected to a wheel, a rotating electrical machine having a rotor body, a first rotating element drivingly connected to the rotor body, and the input member according to the present invention And a differential gear device having a second rotating element drivingly connected to the output member, and a third rotating element drivingly connected to the output member, and an oil pump having a pump shaft and a pump rotor. The rotating electrical machine includes a cylindrical rotor shaft that is disposed coaxially with the input member and supports the rotor body, and the pump shaft penetrates radially inward of the rotor shaft in the axial direction. The pump is connected to the input member so as to rotate integrally with the input member, and the pump is connected to the pump connecting portion provided on the first axial direction side that is one side of the input member in the axial direction. Linked to over motor integrally rotated with the input member and the second rotating element is in that it is drivingly connected in a state capable of relative movement.

In the present application, “drive connection” means a state in which two rotating elements are connected so as to be able to transmit a driving force (synonymous with torque). This concept includes a state in which the two rotating elements are connected so as to rotate integrally, and a state in which the driving force is transmitted through one or more transmission members. Such transmission members include various members (shafts, gear mechanisms, belts, etc.) that transmit rotation at the same speed or at different speeds, and engaging devices (frictions) that selectively transmit rotation and driving force. Engagement devices, meshing engagement devices, etc.).
The “rotary electric machine” is used as a concept including a motor (electric motor), a generator (generator), and a motor / generator that performs both functions of the motor and the generator as necessary.

  According to this characteristic configuration, the oil pump can be driven by rotating the pump rotor with the torque transmitted to the input member via the pump shaft coupled to rotate integrally with the input member and the pump rotor. At this time, the rotor main body of the rotating electrical machine and the pump rotor of the oil pump are drivingly connected via a cylindrical rotor shaft, a differential gear device, an input member, and a pump shaft, of which the input member and the differential gear The second rotary element of the device is drive-coupled in a state where it can move relative to the second rotary element. Thereby, compared with the structure where the 2nd rotation element and the input member are completely integrated, power transmission can be performed between them, attenuating a vibration component effectively. Therefore, the torque of the internal combustion engine transmitted to the input member can be appropriately transmitted to the second rotating element of the differential gear device, and the vibration of the differential gear device can be transmitted integrally with the input member and the pump shaft and pump that rotate integrally therewith. It can be made difficult to be transmitted to the rotor. Therefore, even when the differential gear device vibrates, it is possible to realize a vehicle drive device that can suppress an increase in power loss for driving the oil pump.

  Here, the input member and the second rotating element are drivingly connected by an engaging portion, and the engaging portion does not transmit torque between the input member and the second rotating element. The input member and the second rotating element can move relative to each other at least in the radial direction, and torque is transmitted between the input member and the second rotating element. It is preferable that the force to match the rotational axis of the two-rotating element is not applied.

  According to this configuration, even when torque is transmitted at the engaging portion between the input member and the second rotating element, the rotational axes of the two do not completely coincide with each other and the relative movement in the radial direction is achieved. There is room for possible. Therefore, in such an engagement portion that can be relatively moved in the radial direction, the transmitted vibration component can be effectively attenuated, and an increase in power loss for driving the oil pump can be effectively suppressed. .

  In addition, as a specific configuration example for drivingly connecting the input member and the second rotating element, a square spline connecting portion can be exemplified.

  A case having a first support wall extending in a radial direction on the first axial direction side of the differential gear device; and contacting the second rotation element from the first axial direction side and the first support. It is preferable to further include a first bearing disposed so as to be in contact with the wall from the second axial direction side opposite to the first axial direction side.

  According to this configuration, the second rotating element can be supported in the axial direction via the first bearing from the first axial direction side of the second rotating element by the first support wall of the case. Therefore, also in the vehicle drive device having the structure in which the input member and the second rotating element are driven and connected in a state where they can be relatively moved without being completely integrated as described above, the attitude of the second rotating element is It can stabilize and it can suppress that a vibration arises in the said 2nd rotation element. Therefore, vibration transmitted to the pump rotor via the input shaft and the pump shaft can be reduced, and an increase in power loss for driving the oil pump can be effectively suppressed.

  The first support wall is provided at a central portion in the axial direction of the case so as to partition a first housing space that houses the differential gear device and a second housing space that houses the rotating electrical machine. It is preferable that

  According to this structure, the 1st accommodation space and the 2nd accommodation space which exist on the both sides of the axial direction of a 1st support wall can be functioned as a kind of buffer space. Therefore, even if the vibration generated in the differential gear device is transmitted to the first support wall via the first bearing, the vibration component can be attenuated in the buffer space. Therefore, the diffusion of vibration to the outside of the case can be suppressed.

  And a second bearing arranged to contact the first rotating element from the first axial direction side and to contact the second rotating element from the second axial direction side. It is preferable that the rotating element is supported from the first axial direction side by the first support wall via the first bearing, the second rotating element, and the second bearing.

  According to this configuration, the first rotating element is supported in the axial direction via the second bearing from the first axial direction side of the first rotating element by the second rotating element supported by the first support wall of the case. be able to. As a result, the first rotating element can be axially supported by the first support wall via the first bearing, the second rotating element, and the second bearing. Therefore, it is possible to stabilize the overall postures of the first rotating element and the second rotating element, and to effectively suppress the occurrence of vibration in the second rotating element.

  Further, the first rotating element is a sun gear, the second rotating element is a carrier that supports a plurality of pinion gears, the third rotating element is a ring gear, and the sun gear, the pinion gear, and the ring gear include: Helical teeth each having a torsion angle are provided, and each of the helical gears of the sun gear and the pinion gear transmits the positive torque, which is a torque in the rotational direction of the internal combustion engine, to the output member. It is preferable that the thrust force directed toward the first direction is formed in a direction in which the sun gear is generated.

According to this configuration, the sun gear, the carrier pinion gear, and the ring gear of the differential gear device are each provided with helical teeth, so that smooth power is provided compared to the case where flat teeth having no torsion angle are provided. Transmission is possible. Therefore, generation | occurrence | production of the vibration and noise in each meshing location in a differential gear apparatus can be suppressed.
At this time, the respective helical teeth of the sun gear and the pinion gear are formed in a direction in which a thrust force directed toward the first axial direction is generated in the sun gear during normal traveling in which the positive torque of the internal combustion engine is transmitted to the output member. Therefore, the first rotating element can be supported in the axial direction by the first support wall via the first bearing, the second rotating element, and the second bearing during normal traveling that is realized at a relatively high frequency. Therefore, it is possible to effectively suppress the vibration in the second rotating element in a state where the realization frequency is high.

  The case further includes a second support wall extending in a radial direction on the second axial direction side of the differential gear device, and the input member is axially and radially oriented with respect to the second support wall. And a fourth bearing disposed so as to contact the first rotating element from the second axial direction side and to contact the input member from the first axial direction side. It is preferable to further provide.

  According to this configuration, the input member can be supported in the axial direction and the radial direction via the third bearing by the second support wall of the case on the second axial direction side of the differential gear device. At this time, if a relatively high load capacity third bearing capable of supporting both the axial direction and the radial direction is used, the radial support accuracy of the input member and the pump shaft rotating integrally therewith can be increased. Further, the input member supported by the second support wall of the case can support the first rotating element in the axial direction via the fourth bearing from the second axial direction side of the first rotating element. As a result, the second support wall can support the first rotating element in the axial direction via the third bearing, the input member, and the fourth bearing. Therefore, it is possible to stabilize the overall posture of the differential gear device including the first rotating element, and to effectively suppress vibrations from occurring in the second rotating element.

Skeleton diagram of vehicle drive device according to embodiment Expanded sectional view of the vehicle drive device Partial enlarged view of FIG. IV-IV partial sectional view in FIG. VV partial sectional view in FIG. Partial sectional view showing another embodiment of the engaging portion between the input shaft and the carrier Development sectional drawing of the drive device for vehicles concerning other embodiments

  An embodiment of a vehicle drive device according to the present invention will be described with reference to the drawings. The vehicle drive device 1 is a drive device (hybrid vehicle drive device) for driving a vehicle (hybrid vehicle) provided with both the internal combustion engine E and the rotating electrical machines MG1 and MG2 as a driving force source for the wheels W. . Specifically, the vehicle drive device 1 is configured as a drive device for a two-motor split type hybrid vehicle.

  In the following description, “axial direction L”, “radial direction R”, and “circumferential direction” are input axis I and coaxial rotation axis X of first rotating electrical machine MG1 unless otherwise specified. (See FIG. 2). Further, the first rotary electric machine MG1 side (left side in FIG. 2) that is one side in the axial direction L is defined as the first axial direction L1 side, and the relative side is the opposite side (the other side in the axial direction L). Specifically, the input shaft I side (the right side in FIG. 2) is defined as the second axial direction L2 side. In addition, the direction about each member represents the direction in the state in which they were assembled | attached to the vehicle drive device 1. FIG. Moreover, the term regarding the direction, position, etc. about each member is a concept including the state which has the difference by the error which can be accept | permitted on manufacture.

1. Schematic Configuration of Vehicle Drive Device A schematic configuration of the vehicle drive device 1 according to the present embodiment will be described. As shown in FIG. 1, the vehicle drive device 1 includes an input shaft I that is drivingly connected to the internal combustion engine E, an output gear G that is drivingly connected to the wheels W, a first rotating electrical machine MG1, and a second rotating electrical machine. MG2 and a differential gear device DG are provided. As shown in FIG. 2, the vehicle drive device 1 includes an oil pump 37 that is drivingly connected so as to rotate integrally with the input shaft I. The input shaft I, the differential gear device DG, the first rotating electrical machine MG1, and the oil pump 37 are arranged coaxially with each other, and these are described from the second axial direction L2 side toward the first axial direction L1 side. Are arranged in the order. As shown in FIG. 1, the vehicle drive device 1 includes a counter gear mechanism C and an output differential gear device DF. The input shaft I and the like, the second rotary electric machine MG2, the counter gear mechanism C, and the output differential gear device DF are arranged on mutually different shafts.

  As shown in FIG. 1, the input shaft I is drivingly connected to the internal combustion engine E. Here, the internal combustion engine E is a prime mover (such as a gasoline engine) that is driven by combustion of fuel inside the engine to extract power. In this example, the input shaft I is drivably coupled to an internal combustion engine output shaft Eo such as a crankshaft of the internal combustion engine E via a damper DA. A configuration in which the input shaft I is directly coupled to the internal combustion engine output shaft Eo via a clutch or the like in addition to the damper DA or directly without the damper DA or the clutch is also preferable. In the present embodiment, the input shaft I corresponds to the “input member” in the present invention.

  The first rotating electrical machine MG1 includes a first stator St1 fixed to the case 2 and a first rotor Ro1 that is rotatably supported inside the radial direction R of the first stator St1. The first rotor Ro1 is drivingly coupled so as to rotate integrally with the sun gear S of the differential gear device DG. The first rotating electrical machine MG1 can perform a function as a motor (electric motor) that generates power upon receiving power supply and a function as a generator (generator) that generates power upon receiving power supply. It is said that. Therefore, the first rotating electrical machine MG1 is electrically connected to a power storage device (battery, capacitor, etc.). The first rotating electrical machine MG1 functions as a generator that generates electric power mainly by the torque of the internal combustion engine E transmitted to the input shaft I, charges the battery, or supplies electric power for driving the second rotating electrical machine MG2. However, when the internal combustion engine E is started or when the vehicle is traveling at high speed, the first rotating electrical machine MG1 may function as a motor that powers and outputs driving force. In the present embodiment, the first rotating electrical machine MG1 corresponds to the “rotating electrical machine” in the present invention.

  The second rotating electrical machine MG2 includes a second stator St2 fixed to the case 2 and a second rotor Ro2 that is rotatably supported inside the radial direction R of the second stator St2. The second rotor Ro2 is drivingly connected so as to rotate integrally with the second rotating electrical machine output gear 94. The second rotating electrical machine MG2 can also serve as a motor and a generator, and is electrically connected to the power storage device. In this example, the second rotating electrical machine MG2 mainly functions as a motor that assists the driving force for running the vehicle. However, when the vehicle is decelerated, the second rotating electrical machine MG2 may function as a generator that regenerates the inertial force of the vehicle as electric energy.

  In the present embodiment, the differential gear device DG is configured as a single pinion type planetary gear device. The differential gear device DG has three rotating elements: a carrier CA that supports a plurality of pinion gears PI, and a sun gear S and a ring gear RI that mesh with the pinion gears PI, respectively. The sun gear S is drivingly connected so as to rotate integrally with the rotor shaft 44 of the first rotor Ro1 (the rotor body 43 shown in FIG. 2) of the first rotating electrical machine MG1. The carrier CA is drivingly connected so as to rotate integrally with the input shaft I. The ring gear RI is integrally formed with the outer cylindrical member 71 on which the output gear G is formed. These three rotating elements of the differential gear device DG are a sun gear S (first rotating element), a carrier CA (second rotating element), and a ring gear RI (third rotating element) in order of rotational speed. Here, the “order of rotational speed” is equal to the order of arrangement of the rotational elements in the speed diagram (collinear diagram). This can be either the order from the high speed side to the low speed side, or the order from the low speed side to the high speed side, depending on the state of the differential gear device DG. does not change. Note that the speed diagram (collinear diagram) of the differential gear device DG is well known to those skilled in the art, and is not shown.

  The differential gear device DG distributes the torque of the internal combustion engine E transmitted to the input shaft I to the first rotary electric machine MG1 and the outer cylindrical member 71. The input shaft I is drivably coupled to a carrier CA that is intermediate in the order of rotational speed of the differential gear device DG. Further, the first rotor Ro1 of the first rotating electrical machine MG1 is drivingly connected to the sun gear S on one side with respect to the carrier CA in the order of the rotation speed, and the ring gear RI on the other side is integrally formed with the outer cylindrical member 71. Is formed. When the internal combustion engine E is driven, the positive torque of the internal combustion engine E is transmitted to the carrier CA via the input shaft I, and the negative torque (negative torque) output from the first rotating electrical machine MG1 is the rotor shaft 44. Is transmitted to the sun gear S. The first rotating electrical machine MG1 generates negative torque and functions as a reaction force receiver for the torque of the internal combustion engine E. Thus, the differential gear device DG uses a part of the torque of the internal combustion engine E for the first rotating electrical machine MG1. The torque attenuated with respect to the torque of the internal combustion engine E is transmitted to the outer cylindrical member 71 via the ring gear RI. The differential gear device DG functions as a power distribution device. An output gear G is formed integrally with the outer cylindrical member 71 in the outer cylindrical member 71. The output gear G is drivably coupled to the wheels W via a counter gear mechanism C, an output differential gear device DF, and an axle O. In the present embodiment, the output gear G corresponds to the “output member” in the present invention.

  The counter gear mechanism C reverses the rotation direction of the output gear G and further transmits the torque transmitted to the output gear G to the wheel W side. The counter gear mechanism C has a counter shaft 91, a first gear 92, and a second gear 93. The first gear 92 is engaged with the output gear G. The first gear 92 also meshes with the second rotating electrical machine output gear 94 at a position different from the output gear G in the circumferential direction on the basis of the counter shaft 91. The second gear 93 meshes with the differential input gear 95 of the output differential gear device DF on the first axial direction L1 side of the first gear 92. The counter gear mechanism C reverses the rotation directions of the output gear G and the second rotating electrical machine output gear 94, and transmits the torque transmitted to the output gear G and the torque of the second rotating electrical machine MG2 to the output differential gear device DF. introduce.

  The output differential gear unit DF distributes the torque transmitted to the differential input gear 95 to the plurality of wheels W and transmits the torque. The differential gear device for output DF is configured by using a plurality of bevel gears that mesh with each other, and distributes torque transmitted from the second gear 93 of the counter gear mechanism C to the differential input gear 95 to each of the axles. It is transmitted to the left and right wheels W via O. At this time, the output differential gear device DF transmits the rotation to the wheel W while reversing the rotation direction of the second gear 93. As a result, the vehicle drive device 1 rotates the wheels W in the same direction as the rotation direction of the input shaft I (internal combustion engine E) and travels in the same direction as the internal combustion engine E and the second rotating electrical machine MG2 when the vehicle travels forward. This torque is transmitted to the wheels W to drive the vehicle.

2. Specific Configuration of Each Part of Vehicle Drive Device A specific configuration of each part of the vehicle drive device 1 according to the present embodiment will be described. First rotating electrical machine MG1, second rotating electrical machine MG2, differential gear device DG, outer cylindrical member 71 on which output gear G is formed, counter gear mechanism C, and output differential gear The device DF is accommodated in the case 2. As shown in FIG. 2, in the present embodiment, the case 2 is partitioned into a first accommodation space P1 and a second accommodation space P2. The first accommodation space P1 mainly accommodates the differential gear device DG and the outer cylindrical member 71. In the second housing space P2, mainly the first rotating electrical machine MG1 and the second rotating electrical machine MG2 are housed.

  As shown in FIG. 2, the case 2 includes a case peripheral wall 21 formed in a deformed cylindrical shape so as to cover the outer periphery of each housing component, and a first end support wall 22 extending from the case peripheral wall 21 in the radial direction R. , Intermediate support wall 25, and second end support wall 27.

  The first end support wall 22 has a shape corresponding to the outer shape of the case peripheral wall 21 so as to close the end opening of the case peripheral wall 21 on the first axial direction L1 side. The first end support wall 22 is formed as a substantially flat plate-like member extending in the radial direction R and the circumferential direction. The first end support wall 22 includes a cylindrical (boss-shaped) first axial protrusion 23 that protrudes toward the second axial direction L2 (the first rotating electrical machine MG1 that is the inner side of the case 2). Have. The first axial protrusion 23 is formed integrally with the first end support wall 22. A flat plate-like pump cover 24 extending in the radial direction R and the circumferential direction is attached to the end surface of the first end support wall 22 on the side in the first axial direction L1 that is the outside of the case 2. The pump cover 24 is fastened and fixed to the first end support wall 22 in a state of being in contact with the first end support wall 22 from the first axial direction L1 side. A pump chamber is formed between the first end support wall 22 and the pump cover 24.

  The intermediate support wall 25 is formed as a substantially flat plate-like member extending in the radial direction R and the circumferential direction so as to divide the case circumferential wall 21 in the axial direction L. A second housing space P <b> 2 is formed as a space surrounded by the case peripheral wall 21, the first end support wall 22, and the intermediate support wall 25. The intermediate support wall 25 is disposed between the first rotating electrical machine MG1 and the differential gear device DG in the axial direction L. That is, the intermediate support wall 25 is disposed on the second axial direction L2 side with respect to the first rotating electrical machine MG1 and on the first axial direction L1 side with respect to the differential gear device DG. Further, an axial through hole is formed in the intermediate support wall 25, and the rotor shaft 44 of the first rotating electrical machine MG1 is inserted into the through hole. The intermediate support wall 25 has a cylindrical intermediate axial protrusion 26 that protrudes around the rotor shaft 44 in the second axial direction L2 side (the differential gear device DG side when viewed from the intermediate support wall 25). The intermediate axial protrusion 26 is formed integrally with the intermediate support wall 25. In the present embodiment, the intermediate support wall 25 corresponds to the “first support wall” in the present invention.

  The second end support wall 27 has a shape corresponding to the outer shape of the case peripheral wall 21 so as to close the end opening of the case peripheral wall 21 on the second axial direction L2 side. The second end support wall 27 is formed as a substantially flat plate-like member extending in the radial direction R and the circumferential direction. A first accommodation space P <b> 1 is formed as a space surrounded by the case peripheral wall 21, the intermediate support wall 25, and the second end support wall 27. The second end support wall 27 is disposed closer to the second axial direction L2 than the differential gear device DG. The second end support wall 27 is formed with an axial through hole, and the input shaft I is inserted through the through hole. As shown in FIGS. 2 and 3, the second end support wall 27 is disposed around the input shaft I in the first axial direction L1 side (the differential gear device DG side when viewed from the second end support wall 27). A cylindrical second axially projecting portion 28 that projects in the shape of a cylindrical shape. The second axial protrusion 28 is formed integrally with the second end support wall 27. In the present embodiment, the second end support wall 27 corresponds to the “second support wall” in the present invention.

  As shown in FIG. 2, in the present embodiment, the intermediate axial protrusion 26 and the second axial protrusion 28 are arranged to face each other in the first accommodation space P1. These are formed coaxially and of the same size, and are arranged so as to have overlapping portions when viewed in the axial direction L. Here, regarding the arrangement of the two members, “having overlapping portions when seen 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 a region where the virtual straight line intersects both of the two members exists at least in part.

  As shown in FIG.2 and FIG.3, the input shaft I is arrange | positioned in the state which penetrates case 2 (2nd edge part support wall 27). The input shaft I is supported by the second axial projecting portion 28 in a state that it can rotate via the input bearing 81. The input shaft I includes a shaft main body portion 31 that extends along the axial direction L, and a large diameter portion 32 that has a larger diameter than the shaft main body portion 31. The large-diameter portion 32 has a predetermined length in the axial direction L width, and is formed integrally with the shaft main body portion 31 at the end of the shaft main body portion 31 on the first axial direction L1 side. The large-diameter portion 32 is drivingly connected to the carrier CA (carrier case 61) through the space between the inner cylindrical member 51 in which the sun gear S is formed and the second axially protruding portion 28. Further, a shaft end hole 33 extending in the axial direction L is formed at the center of the end portion of the shaft main body 31 on the first axial direction L1 side (see FIG. 2).

  As shown in FIG. 2, the rotor shaft 44 of the first rotating electrical machine MG1 is formed in a cylindrical shape (cylindrical in this example) having a through hole 45 extending in the axial direction L. The rotor shaft 44 is disposed in a state of penetrating the intermediate support wall 25, and supports the rotor body 43 on the outer peripheral surface thereof in the second accommodation space P2. The rotor shaft 44 is supported by the first axial protrusion 23 while being rotatable via the first rotor bearing 82, and is also supported by the intermediate axial protrusion 26 while being rotatable via the second rotor bearing 83. It is supported by. As shown in FIGS. 2 and 3, the rotor shaft 44 has an inner cylindrical member 51 at the first engagement portion α provided at the end portion on the second axial direction L2 side in the first accommodation space P1. It is connected to. The first engagement portion α is formed by spline teeth formed on the inner peripheral surface of the end portion on the second axial direction L2 side of the rotor shaft 44, and the outer periphery of the end portion on the first axial direction L1 side of the inner cylindrical member 51. It is an engaging part comprised by the spline teeth formed in the surface.

  The inner cylindrical member 51 is a cylindrical member (cylindrical member in this example) disposed on the inner side in the radial direction R with respect to the carrier case 61. A sun gear S is formed on the outer peripheral surface of the inner cylindrical member 51 on the side in the second axial direction L2 from the first engagement portion α with the rotor shaft 44. Thereby, the rotor shaft 44 passes through the intermediate support wall 25 and is drivingly connected to the sun gear S in the first accommodation space P1.

  The carrier case 61 constituting the carrier CA includes a first support portion 62 and a second support portion 66 that support pinion shafts that are rotation shafts of the plurality of pinion gears PI on both sides in the axial direction L, respectively. The first support portion 62 is disposed closer to the first axial direction L1 than the pinion gear PI, and is formed as a thick portion having a predetermined axial length L width. The first support portion 62 is disposed on the outer side in the radial direction R of the rotor shaft 44 and the inner tubular member 51 with a small gap on the second axial direction L2 side with respect to the intermediate axial direction protruding portion 26.

  The second support portion 66 is disposed closer to the second axial direction L2 than the pinion gear PI, and is formed in a disc shape. The second support portion 66 is a cylindrical tube that protrudes around the large-diameter portion 32 of the input shaft I in the second axial direction L2 side (the second end support wall 27 side when viewed from the second support portion 66). A protrusion 67. The cylindrical projecting portion 67 is formed integrally with the second support portion 66 at the end portion on the inner side in the radial direction R of the second support portion 66. In addition, the axial length L of the cylindrical protruding portion 67 is set to a value comparable to the axial length L of the large diameter portion 32.

  The cylindrical protrusion 67 is connected so as to rotate integrally with the large-diameter portion 32 (input shaft I) at the second engagement portion β provided over the entire axial direction L. The second engaging portion β is configured by spline teeth formed on the outer peripheral surface of the large diameter portion 32 of the input shaft I and spline teeth formed on the inner peripheral surface of the cylindrical protruding portion 67 of the carrier case 61. It is an engaging part. As described above, in this embodiment, the input shaft I and the carrier case 61 (carrier CA) are not completely integrated by welding or the like, but are separated from each other configured as separate parts (non-integrated state). The drive is connected as it is. In this manner, the input shaft I and the carrier case 61 are configured as separate parts that directly mesh with each other at the second engagement portion β. In such a configuration, in the second engagement portion β, the input shaft I and the carrier case 61 are not kept in a fixed positional relationship but are driven and connected in a state where there is room for relative movement. The

  The outer cylindrical member 71 is a cylindrical member (cylindrical member in this example) disposed on the outer side in the radial direction R with respect to the carrier case 61. The outer cylindrical member 71 is disposed on the outer side in the radial direction R so as to surround the sun gear S and the carrier CA. A ring gear RI is integrally formed with the outer cylindrical member 71 on the inner peripheral surface of the outer cylindrical member 71. The ring gear RI is formed at the central portion in the axial direction L of the outer cylindrical member 71. The differential gear device DG having the sun gear S, the carrier CA, and the ring gear RI is entirely inside the radial direction R of the outer cylindrical member 71 and overlaps with the outer cylindrical member 71 when viewed in the radial direction R. Is arranged.

  Further, the outer cylindrical member 71 is disposed so as to have a portion that overlaps with both the intermediate axial protrusion 26 and the second axial protrusion 28 when viewed in the radial direction R. And the 1st output bearing 84 and the 2nd output bearing 85 are arrange | positioned at the said overlapping part, respectively. Thereby, the outer cylindrical member 71 on which the output gear G is formed is supported by the intermediate axial protrusion 26 in a rotatable state via the first output bearing 84, and via the second output bearing 85. It is supported by the second axial protrusion 28 in a rotatable state.

  As shown in FIG. 2, a pump rotor 35 is disposed in a pump chamber formed between the first end support wall 22 and the pump cover 24 on the first axial direction L1 side of the first rotating electrical machine MG1. Yes. In the present embodiment, as such a pump rotor 35, an inner rotor and an outer rotor inscribed in each other are used. The pump rotor 35 (here, the inner rotor) is drivingly connected to a tubular pump shaft 36 extending along the axial direction L. The pump rotor 35 and the pump shaft 36 are arranged coaxially with the input shaft I and the first rotating electrical machine MG1. In the present embodiment, the oil pump 37 is configured by including the pump rotor 35 and the pump shaft 36.

  The pump shaft 36 is inserted so as to penetrate the inner side in the radial direction R of the cylindrically formed rotor shaft 44 in the axial direction L. The pump shaft 36 is connected to the input shaft I and the pump rotor 35 (inner rotor) on both sides of the rotor shaft 44 in the axial direction L, respectively. Specifically, the pump shaft 36 is coupled so as to rotate integrally with the input shaft I at a third engagement portion γ provided closer to the second axial direction L2 than the rotor shaft 44. The third engagement portion γ includes spline teeth formed on the outer peripheral surface of the end portion of the pump shaft 36 on the second axial direction L2 side, and spline formed on the inner peripheral surface of the shaft end hole portion 33 of the input shaft I. It is an engaging part comprised with a tooth | gear. The pump shaft 36 is coupled to rotate integrally with the pump rotor 35 at a fourth engagement portion δ provided on the shaft first direction L1 side with respect to the input shaft I and the rotor shaft 44. The fourth engagement portion δ includes spline teeth formed on the outer peripheral surface of the end portion of the pump shaft 36 on the first axial direction L1 side, and the inner periphery of the center hole provided in the center portion of the pump rotor 35 (inner rotor). It is an engaging part comprised by the spline teeth formed in the surface. In the present embodiment, the fourth engagement portion δ corresponds to the “pump connection portion” in the present invention.

  Thus, in this embodiment, the input shaft I and the pump shaft 36 are connected so as to rotate integrally, and the pump rotor 35 (oil pump 37) is driven by the rotation of the input shaft I and the pump shaft 36. The The oil discharged by the oil pump 37 passes through the in-shaft oil passage 39 formed in the pump shaft 36 and the input shaft I, and the differential gear unit DG, the plurality of gears, and It is supplied to a plurality of bearings and the like to lubricate and cool them.

3. Connection Form at Each Engagement Part A connection form at each engagement part α, β, γ, δ will be described. In the present embodiment, each of the engaging portions α, β, γ, and δ is divided into two members to be driven and connected so as to extend in the axial direction L, and is engaged with each other in the circumferential direction when rotated. It consists of spline teeth that fit together. In other words, in each of the engaging portions α, β, γ, and δ, two members are driven and connected by spline connection, and these two members are driven and connected so as to be relatively movable in the axial direction L, respectively. Yes.

  As shown in FIG. 4, the first engagement portion α between the rotor shaft 44 and the inner cylindrical member 51 is configured as an involute spline connecting portion designed so that the tooth surface of the spline teeth follows the involute curve. . Here, the involute curve is a plane curve (a circle extending line) whose normal is always in contact with one constant circle.

  In the present embodiment, the third engagement portion γ between the pump shaft 36 and the input shaft I and the fourth engagement portion δ between the pump shaft 36 and the pump rotor 35 (inner rotor) are also configured as an involute spline connection portion. Yes. In an involute spline, the tooth width of the tooth root portion can be increased, so that the tooth root strength is increased and high power transmission capability can be ensured. In addition, when the torque load is not applied, the two members can move relative to each other at least in the radial direction. There is an advantage of being minded. Furthermore, involute splines are the current mainstream in spline connection because high-precision processing is easy and manufacturability is excellent.

  On the other hand, as shown in FIG. 5, the second engaging portion β between the input shaft I and the carrier case 61 (carrier CA) has a spline tooth surface that is different from the involute curve (including a straight line). It is configured as a non-involute spline connecting portion designed to follow. In the present embodiment, the second engagement portion β is configured as a square spline connecting portion having spline teeth (square spline teeth) whose tooth surfaces are flat surfaces parallel to the rotational axis X of the input shaft I. Here, the “square spline teeth” are spline teeth whose shape when viewed from the rotational axis X of the input shaft I is rectangular or trapezoidal. In such a square spline (a kind of non-involute spline), the two members can move relative to each other at least in the radial direction in a state where the torque load is not applied, and both are automatically aligned even when the torque load is applied. There is nothing. That is, in the state where torque is transmitted between the two members, the force for matching the rotational axes of the two members does not act. Here, “the force that makes the rotational axes of the two members coincide does not act” means that the force that can finally make the rotational axes of the two members substantially coincide does not act. Therefore, this concept includes that a force in a direction that causes both rotation axes to coincide with each other to the extent that they do not substantially coincide is applied.

  In the present embodiment, the input shaft I and the carrier case 61 (carrier CA) are configured as separate parts that directly mesh with each other, and the second engagement portion β that is the engagement portion is intentionally formed as a non-mainstream square spline. It is configured as a connecting part. For this reason, for example, even when the torque of the internal combustion engine E is transmitted to the differential gear device DG (carrier CA) via the second engagement portion β during normal traveling of the vehicle, the input shaft I and the carrier case 61 are connected. There is no self-alignment, leaving room for relative movement in the radial direction R. Therefore, as compared with a structure in which the carrier CA and the input shaft I are completely integrated, for example, by welding or the like, it is possible to transmit power between them while effectively attenuating the vibration component.

  Here, in manufacturing the vehicle drive device 1, it is unavoidable that manufacturing errors of individual component parts themselves and assembly errors during assembly occur to some extent. Therefore, there is a possibility that a certain amount of vibration is generated in the driven first rotating electrical machine MG1 due to such a manufacturing error or an assembly error. In addition, a certain amount of vibration may occur in the driven first rotating electrical machine MG1 due to the influence of cogging torque, torque ripple, and the like. The vibration component generated in the first rotating electrical machine MG1 can be transmitted to the carrier CA (carrier case 61) via the rotor shaft 44, the inner cylindrical member 51, the sun gear S, and the pinion gear PI. In addition, meshing vibration may occur between the output gear G and the first gear 92. In this case, the vibration component can be transmitted to the carrier CA (carrier case 61) via the outer cylindrical member 71, the ring gear RI, and the pinion gear PI. Further, meshing vibration may occur between the gears of the differential gear device DG.

  Even in such a case, in the present embodiment, since the input shaft I and the carrier case 61 are drivingly connected by the square spline connection at the second engaging portion β, the carrier case 61 is connected to the input shaft I. Transmission of vibration components is suppressed. Therefore, even when the differential gear device DG vibrates due to various factors as described above, the vibration component is attenuated by the second engagement portion β, and the input shaft I and the pump shaft that rotates integrally therewith are attenuated. 36 and the pump rotor 35 can be made difficult to be transmitted. Thereby, an increase in power loss for driving the oil pump 37 can be effectively suppressed, and a decrease in energy efficiency of the vehicle drive device 1 as a whole can be suppressed.

4). Support structure of input shaft and differential gear device The support structure of the input shaft I and differential gear device DG, here, the support structure mainly in the axial direction L will be described. In the present embodiment, the rotational elements of the input shaft I and the differential gear device DG are relatively relative to each other using mainly the input bearing 81, the first thrust bearing 86, the second thrust bearing 87, and the third thrust bearing 88. The case 2 is supported in a rotatable state.

  As shown in FIGS. 2 and 3, the input shaft I is supported by the input bearing 81 in the axial direction L and the radial direction R with respect to the second end support wall 27. In the present embodiment, the input bearing 81 corresponds to the “third bearing” in the present invention. In the present embodiment, the input shaft I is supported by the second axial protrusion 28 in a state where the input shaft I can rotate via one input bearing 81. Corresponding to the input shaft I being cantilevered in this way, as the input bearing 81, a ball group composed of a plurality of balls dispersedly arranged in the circumferential direction of the input bearing 81 is divided into two in the axial direction L. A double bearing (double ball bearing) having a row is used. Further, as such an input bearing 81, a self-aligning bearing in which the outer ring raceway is spherical and the center of curvature thereof coincides with the center of the bearing may be used. The outer ring of the input bearing 81 is in contact with the wall surface of the step provided in the second axial protrusion 28 from the first axial direction L1 side. Further, the inner ring of the input bearing 81 is in contact with the large diameter portion 32 of the input shaft I from the second axial direction L2 side. As a result, the second end support wall 27 supports the input shaft I in the axial direction L via the input bearing 81 from the second axial direction L2 side of the large diameter portion 32. As the input bearing 81, it is preferable to use a high load capacity type.

  The carrier case 61 (carrier CA) is supported in the axial direction L with respect to the intermediate support wall 25 by a first thrust bearing 86. In the present embodiment, the carrier case 61 is supported by the intermediate axial protrusion 26 in a rotatable state via the first thrust bearing 86. The washer disk on the first axial direction L1 side of the first thrust bearing 86 is in contact with the wall surface of the step provided on the intermediate axial direction protruding portion 26 from the second axial direction L2 side. Further, the bearing disc on the second axial direction L2 side of the first thrust bearing 86 is in contact with the wall surface of the first support portion 62 of the carrier case 61 from the first axial direction L1 side. As a result, the intermediate support wall 25 supports the carrier case 61 in the axial direction L via the first thrust bearing 86 from the first axial direction L1 side of the carrier case 61. In the present embodiment, the first thrust bearing 86 corresponds to the “first bearing” in the present invention.

  The inner cylindrical member 51 in which the sun gear S is formed is supported in the axial direction L with respect to the carrier case 61 by a second thrust bearing 87. In the present embodiment, the inner cylindrical member 51 is supported by the carrier case 61 so as to be rotatable via the second thrust bearing 87. The bearing disc on the first axial direction L1 side of the second thrust bearing 87 is in contact with the wall surface of the step portion provided on the first support portion 62 of the carrier case 61 from the second axial direction L2 side. Further, the bearing disc on the second axial direction L2 side of the second thrust bearing 87 is in contact with the wall surface of the step portion provided on the inner cylindrical member 51 from the first axial direction L1 side. Accordingly, the intermediate support wall 25 is connected to the inner cylindrical member 51 via the first thrust bearing 86, the carrier case 61, and the second thrust bearing 87 from the first axial direction L1 side with respect to the differential gear device DG. Is supported in the axial direction L. In the present embodiment, the second thrust bearing 87 corresponds to the “second bearing” in the present invention.

  The inner cylindrical member 51 is supported in the axial direction L with respect to the input shaft I by a third thrust bearing 88. In the present embodiment, the inner cylindrical member 51 is supported by the input shaft I in a state that it can rotate via the third thrust bearing 88. The washer on the first axial direction L1 side of the third thrust bearing 88 is in contact with the wall surface of the inner cylindrical member 51 from the second axial direction L2 side. Further, the bearing disc on the second axial direction L2 side of the third thrust bearing 88 is in contact with the wall surface of the input shaft I (large diameter portion 32) from the first axial direction L1 side. As a result, the second end support wall 27 passes through the input bearing 81, the input shaft I (large diameter portion 32), and the third thrust bearing 88 from the second axial direction L2 side with respect to the differential gear device DG. The inner cylindrical member 51 is supported in the axial direction L. In the present embodiment, the third thrust bearing 88 corresponds to the “fourth bearing” in the present invention.

  In the present embodiment, since the input shaft I and the carrier case 61 are not completely integrated, each rotary element of the differential gear device DG is likely to change its posture. In consideration of such points, in the present embodiment, the input shaft I, the carrier case 61, and the inner cylindrical member 51 are entirely replaced with the input bearing 81, the first thrust bearing 86, the second thrust bearing 87, and the third. The thrust bearing 88 is appropriately supported in the axial direction L. Thereby, the whole attitude | position of each rotation element of the differential gear apparatus DG can be stabilized, and it can suppress effectively that a vibration arises in the differential gear apparatus DG. Therefore, also from this point, the vibration component can be made difficult to be transmitted to the pump rotor 35, and an increase in power loss for driving the oil pump 37 can be effectively suppressed.

  By the way, in this embodiment, in order to enable smooth power transmission and to further suppress the generation of vibration and noise, the sun gear S, pinion gear PI, and ring gear RI of the differential gear device DG are each provided with helical teeth having a twist angle. Is provided. FIG. 3 illustrates a part of the helical teeth provided on the sun gear S.

  The helical gears of the sun gear S and the pinion gear PI are directed toward the first axial direction L1 in a state where the torque of the internal combustion engine E (here, positive torque that is torque in the rotational direction) is transmitted to the output gear G. The thrust force is formed in a direction in which the sun gear S (inner cylindrical member 51) is generated. In the present embodiment, during normal traveling of the vehicle, the torque of the internal combustion engine E is transmitted to the output gear G formed on the outer cylindrical member 71 with the reaction force supported by the negative torque of the first rotating electrical machine MG1. Is done. Therefore, each helical tooth of the sun gear S and the pinion gear PI is in a state where the first rotating electrical machine MG1 outputs a negative torque (a state where the torque load from the first rotating electrical machine MG1 is transmitted to the sun gear S). It can be said that the thrust force toward the first direction L1 is formed in the direction in which the sun gear S is generated. In this case, the direction of the helical teeth formed on the ring gear RI is determined according to the direction of the helical teeth formed on the pinion gear PI, and the ring gear RI (outer cylindrical member 71) has a thrust toward the second axial direction L2 side. Power is generated.

  For example, when the first rotating electrical machine MG1 outputs a positive torque and the internal combustion engine E that starts the stopped internal combustion engine E is started by the torque of the first rotating electrical machine MG1 transmitted to the input shaft I, the shaft A thrust force toward the second direction L2 is generated in the sun gear S (inner cylindrical member 51). In this case, a thrust force toward the first axial direction L1 is generated in the ring gear RI (outer cylindrical member 71).

  In the present embodiment, since the helical teeth of the sun gear S and the pinion gear PI are set as described above, the inner cylindrical member 51 and the carrier case 61 are axially moved by the intermediate support wall 25 during normal travel with high realization frequency. L can be supported appropriately. At this time, the thrust force generated in the inner cylindrical member 51 is transmitted to the intermediate support wall 25 to some extent. Accordingly, the vibration of the differential gear device DG may be transmitted to the intermediate support wall 25. However, since the intermediate support wall 25 is provided in the central portion of the case 2 in the axial direction L, the first storage space P1 and the second storage space P2 existing on both sides of the intermediate support wall 25 function as buffer spaces. Can be made. Therefore, the vibration component can be attenuated in the buffer space, and vibration and noise diffusion to the outside of the case 2 can be suppressed.

5. Other Embodiments Finally, other embodiments of the vehicle drive device according to the present invention 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 configuration in which the second engagement portion β is configured as a square spline coupling portion has been described as an example. However, the embodiment of the present invention is not limited to this. The second engaging portion β is preferably a non-involute spline connecting portion that is not automatically aligned even when a torque load is applied between the input shaft I and the carrier case 61, and has other configurations. May be. For example, as shown in FIG. 6, the second engagement portion β may be configured as an arc-shaped spline coupling portion designed so that the tooth surface of the spline teeth follows an arc-shaped continuous curve. Moreover, although illustration is abbreviate | omitted, you may comprise as an engaging part using the key and keyway which mutually engage. Alternatively, the second engaging portion β may also be configured as an involute spline connecting portion in the same manner as the other engaging portions α, γ, and δ.

(2) In the above embodiment, the configuration in which the input shaft I and the carrier case 61 are configured by separate parts that directly mesh with each other at the second engagement portion β has been described as an example. However, the embodiment of the present invention is not limited to this. For example, the input shaft I and the carrier case 61 may be configured to indirectly mesh with each other via another member. For example, the input shaft I and the carrier case 61 may be configured to mesh with each other via a splined cylindrical member that meshes with the input shaft I on the inner peripheral surface side and meshes with the carrier case 61 on the outer peripheral surface side. good. In this case, at least one of the engaging portion between the cylindrical member and the input shaft I and the engaging portion between the cylindrical member and the carrier case 61 is configured as a non-involute spline connecting portion. It is preferable that

(3) In the above embodiment, the thrust force toward the first axial direction L1 side is generated when the helical teeth of the sun gear S and the pinion gear PI are in the state where the first rotating electrical machine MG1 outputs negative torque. The configuration formed in the direction that occurs in the above has been described as an example. However, the embodiment of the present invention is not limited to this. On the contrary, the helical gears of the sun gear S and the pinion gear PI are directed in the direction in which the thrust force toward the shaft second direction L2 is generated in the sun gear S while the first rotating electrical machine MG1 outputs a negative torque. It may be formed.

(4) In the above embodiment, the configuration in which the helical gears are provided in each of the sun gear S, the pinion gear PI, and the ring gear RI of the differential gear device DG has been described as an example. However, the embodiment of the present invention is not limited to this. Spur teeth may be provided on each of the sun gear S, the pinion gear PI, and the ring gear RI.

(5) The specific configuration of each of the bearings 81 to 88 described in the above embodiment can be changed as appropriate according to the purpose of use. For example, instead of the first thrust bearing 86 in the above-described embodiment, the carrier case 61 is in contact with the axial first direction L1 side and the intermediate axial direction protruding portion 26 is in contact with the axial second direction L2 side. A support bearing 89 may be disposed (see FIG. 7). In this case, the carrier case 61 can be supported not only in the axial direction L but also in the radial direction R with respect to the intermediate support wall 25 by the support bearing 89. For example, although illustration is omitted, as a rotation support mechanism corresponding to the input bearing 81 in the above-described embodiment, a normal ball bearing may be used, or a radial bearing and a thrust bearing may be used in combination.

(6) In the above embodiment, the first thrust bearing 86 and the second thrust bearing 87 are added to the drive device having the structure of the conventional specification in which the input shaft I and the carrier case 61 are completely integrated. The above configuration has been described as an example. However, the embodiment of the present invention is not limited to this. For example, when the posture of each rotating element of the differential gear device DG can be autonomously stabilized, or when stabilization of the posture is not particularly problematic, the first thrust bearing 86 and the second thrust bearing At least one of the bearings 87 can be omitted.

(7) Regarding other configurations as well, the embodiments disclosed herein are illustrative in all respects, and the embodiments of the present invention are not limited thereto. In other words, configurations that are not described in the claims of the present application can be modified as appropriate without departing from the object of the present invention.

  The present invention can be used in a vehicle drive device used in a split type hybrid vehicle.

1: Vehicle drive device 2: Case 25: Intermediate support wall (first support wall)
27: Second end support wall (second support wall)
35: Pump rotor 36: Pump shaft 37: Oil pump 41: Stator main body 43: Rotor main body 44: Rotor shaft 81: Input bearing (third bearing)
86: First thrust bearing (first bearing)
87: Second thrust bearing (second bearing)
88: Third thrust bearing (fourth bearing)
E: Internal combustion engine I: Input shaft (input member)
MG1: First rotating electrical machine (rotating electrical machine)
DG: Differential gear device S: Sun gear (first rotating element)
CA: Carrier (second rotating element)
RI: Ring gear (third rotating element)
PI: Pinion gear G: Output gear (output member)
W: Wheel β: Second engagement portion (engagement portion)
δ: Fourth engagement part (pump connection part)
L: axial direction L1: axial first direction L2: axial second direction

Claims (8)

An input member drivingly connected to the internal combustion engine, an output member drivingly connected to the wheel, a rotating electrical machine having a rotor body, a first rotating element drivingly connected to the rotor body, and drivingly connected to the input member A vehicle drive device comprising: a second rotating element; a differential gear device having a third rotating element drivingly connected to the output member; and an oil pump having a pump shaft and a pump rotor,
The rotating electrical machine includes a cylindrical rotor shaft that is arranged coaxially with the input member and supports the rotor body,
The pump shaft is inserted so as to penetrate the radially inner side of the rotor shaft in the axial direction, and is connected to rotate integrally with the input member, and is on one side in the axial direction with respect to the input member. It is connected so as to rotate integrally with the pump rotor in the pump connecting portion provided on the first axial direction side,
The vehicle drive device by which the said input member and said 2nd rotation element are drive-coupled in the state which can be moved relatively. The input member and the second rotating element are drivingly connected by an engaging portion,
The engaging portion is capable of relatively moving the input member and the second rotating element at least in a radial direction in a state where torque transmission is not performed between the input member and the second rotating element, and the input member And a force for causing the rotation axis of the input member to coincide with the rotation axis of the second rotation element in a state where torque is transmitted between the rotation element and the second rotation element. Item 2. The vehicle drive device according to Item 1.   The vehicle drive device according to claim 1, wherein the input member and the second rotating element are drivingly connected by a square spline connecting portion. A case having a first support wall extending in a radial direction on the first axial direction side of the differential gear device;
The second rotating element is disposed so as to be in contact with the second rotating element from the first axial direction side and to be in contact with the first support wall from the second axial direction side opposite to the first axial direction side. One bearing,
The vehicle drive device according to any one of claims 1 to 3, further comprising:   The first support wall is provided at an axially central portion of the case so as to partition a first housing space that houses the differential gear device and a second housing space that houses the rotating electrical machine. The vehicle drive device according to claim 4. A second bearing arranged to contact the first rotating element from the first axial direction side and to contact the second rotating element from the second axial direction side;
The first rotating element is supported from the first axial direction side by the first support wall via the first bearing, the second rotating element, and the second bearing. Vehicle drive system. The first rotating element is a sun gear, the second rotating element is a carrier supporting a plurality of pinion gears, and the third rotating element is a ring gear;
The sun gear, the pinion gear, and the ring gear are each provided with helical teeth having a twist angle,
Each of the helical gears of the sun gear and the pinion gear transmits a positive torque, which is a torque in the rotational direction of the internal combustion engine, to the output member, and a thrust force directed toward the first axial direction side is applied to the sun gear. The vehicle drive device according to claim 6, wherein the vehicle drive device is formed in a direction generated in the vehicle. The case further includes a second support wall extending in a radial direction on the second axial direction side of the differential gear device,
A third bearing for supporting the input member axially and radially with respect to the second support wall;
A fourth bearing disposed so as to contact the first rotating element from the second axial direction side and to contact the input member from the first axial direction side;
The vehicle drive device according to any one of claims 4 to 7, further comprising:

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