JP2021162052A - Vehicular drive transmission device - Google Patents

Abstract

To provide a technique for suppressing the manufacturing cost of a vehicular drive transmission device including a helical gear.SOLUTION: A second gear 21 is engaged with a connection shaft 23 while abutting on a first step surface 24a of the connection shaft 23 from the second axial side L2. A third gear 22 is formed integrally with the connection shaft 23, and a fourth gear 31 is fixed to a differential case 32 while abutting on a second step surface 33a of the differential case 32 from the second axial side L2. The direction of the oblique teeth of each gear is set so that in the state that a driving force source is power-running in the normal direction, a thrust load F1 directed to the second axial side L2 works from the second gear 21 to a first gear 11, a thrust load F2 directed to the first axial side L1 works from the first gear 11 to the second gear 21, a thrust load F3 directed to the second axial side L2 works from the fourth gear 31 to the third gear 22, and a thrust load F4 directed to the first axial side L1 works from the third gear 22 to the fourth gear 31.SELECTED DRAWING: Figure 3

Description

The present invention relates to a vehicle drive transmission device that transmits a driving force between a driving force source and wheels.

An example of such a vehicle drive transmission device is disclosed in Patent Document 1 below. Hereinafter, in the description of "background technology" and "problems to be solved by the invention", the reference numerals in Patent Document 1 are quoted in parentheses.

The vehicle drive transmission device (2) of Patent Document 1 has a first gear (210) and meshes with an input member (21) that is driven and connected to a driving force source (1) and the first gear (210). A counter gear mechanism (23) including a second gear (232), a third gear (233) that rotates integrally with the second gear, and a connecting shaft (231) that connects these gears, and a third gear. It includes a differential gear mechanism (22) having a fourth gear (225) that meshes with (233).

In the vehicle drive transmission device (2) described above, the third gear (233) is integrally formed with the connecting shaft (231), whereas the second gear (232) is formed on the connecting shaft (231). On the other hand, they are engaged so as to be relatively movable in the axial direction. Therefore, the second gear (232) is a parking gear (234) arranged on one side in the axial direction (hereinafter, referred to as “first side in the axial direction”) with respect to the second gear, and the other in the axial direction. The counter bearings (230) arranged on the side (hereinafter, referred to as "second side in the axial direction") are sandwiched in a state where the movement in the axial direction is restricted.

Japanese Unexamined Patent Publication No. 2001-190042 (Fig. 1)

In the vehicle drive transmission device (2) described above, each of the first gear (210), the second gear (232), the third gear (233), and the fourth gear (225) is an oblique tooth gear. Therefore, depending on the operating state of the driving force source (1), a thrust load directed to the second side in the axial direction acts on the first gear (210) to the second gear (232) for a long period of time. Become. Therefore, in order to receive such a thrust load, a nut that comes into contact with the counter bearing (230) from the second side in the axial direction is screwed into the end portion on the second side in the axial direction of the connecting shaft (231).

However, when the above nuts are installed, the cost of parts of the nut, the cost of thread cutting for screwing the nut to the connecting shaft (231), the cost of assembling the nut to the connecting shaft (231), etc. Therefore, there is a problem that the manufacturing cost of the vehicle drive transmission device (2) increases.

Therefore, it is desired to realize a technology capable of keeping the manufacturing cost of a vehicle drive transmission device equipped with oblique gears low.

In view of the above, the characteristic configuration of the vehicle drive transmission device is
An input member equipped with a first gear and driven and connected to a driving force source,
A pair of output members that are driven and connected to the wheels, respectively.
A counter gear mechanism including a second gear that meshes with the first gear, a third gear that rotates integrally with the second gear, and a connecting shaft that connects the second gear and the third gear.
A fourth gear that meshes with the third gear, a differential gear group that distributes the rotation of the fourth gear to the pair of output members, and the differential gear group are accommodated, and the fourth gear rotates integrally. With a differential gear mechanism, with a differential case connected so that
In the axial direction, the side of the third gear with respect to the second gear is the first side in the axial direction, and the side opposite to the first side in the axial direction is the second side in the axial direction.
The connecting shaft is provided with a first stepped portion that forms a first stepped surface facing the second side in the axial direction.
The second gear is engaged so as to rotate integrally with the connecting shaft in a state of being in contact with the first stepped surface from the second side in the axial direction.
The third gear is integrally formed with the connecting shaft.
The differential case is provided with a second step portion that forms a second step surface facing the second side in the axial direction.
The fourth gear is fixed to the differential case by using a fastening member in a state of being in contact with the second stepped surface from the second side in the axial direction.
Each of the first gear, the second gear, the third gear, and the fourth gear is an oblique tooth gear.
The rotation direction of the driving force source when the vehicle is moved forward is set to the normal rotation direction.
In a state where the driving force source is driving in the forward rotation direction, a thrust load directed to the second side in the axial direction acts from the second gear to the first gear, and the first gear to the first gear. A thrust load directed to the first side in the axial direction acts on the second gear, and a thrust load directed toward the second side in the axial direction acts on the third gear from the fourth gear, and the first gear. The oblique teeth of the first gear, the second gear, the third gear, and the fourth gear so that a thrust load from the third gear toward the first side in the axial direction acts on the fourth gear. Is at the point where the orientation of is set.

According to this characteristic configuration, in a state where the driving force source is powering in the forward rotation direction, the thrust load from the third gear to the fourth gear toward the first side in the axial direction, that is, the fourth gear is a differential case. A thrust load in the direction of pressing against the second stepped surface of the above acts. Here, the fourth gear is fixed to the differential case by using a fastening member in a state of being in contact with the second stepped surface of the differential case from the second side in the axial direction. Therefore, when the driving force source is running in the forward rotation direction, the load in the direction of loosening the fastening member does not act on the fourth gear, and the thrust load acting on the fourth gear is the second step. It is received by the surface. Therefore, it is possible to reduce the possibility that the fastening member that fixes the fourth gear to the differential case will loosen.
Further, according to this configuration, a thrust load directed to the first side in the axial direction acts on the first gear to the second gear in a state where the driving force source is driving in the forward rotation direction, and the fourth gear to the first gear. A thrust load toward the second side in the axial direction acts on the three gears. Therefore, thrust loads directed to opposite sides in the axial direction act on the second gear and the third gear connected by the connecting shaft, and these thrust loads act in the direction of canceling each other on the connecting shaft. Can be done. Therefore, it is possible to reduce the possibility that an excessive thrust load acts on the bearing that supports the connecting shaft.
On top of that, according to this configuration, the second gear is engaged so as to rotate integrally with the connecting shaft in a state of being in contact with the first stepped surface of the connecting shaft from the second side in the axial direction. It is matched. Therefore, when the driving force source is running in the forward rotation direction, the thrust load in the direction of relatively moving the second gear to the first side in the axial direction with respect to the connecting shaft is received by the first stepped surface. Therefore, it is possible to reduce the need to install a receiving member such as a nut for receiving the thrust load in the direction in which the second gear is relatively moved to the second side in the axial direction with respect to the connecting shaft. As a result, the manufacturing cost of the vehicle drive transmission device provided with the oblique gear can be kept low.

A cross-sectional view taken along the axial direction of the vehicle drive transmission device according to the first embodiment. Skeleton diagram of the vehicle drive transmission device according to the first embodiment A cross-sectional view taken along the axial direction showing a main part of the vehicle drive transmission device according to the first embodiment. Skeleton diagram of the vehicle drive transmission device according to the second embodiment

1. 1. First Embodiment In the following, the vehicle drive transmission device 100 according to the first embodiment will be described with reference to the drawings. The vehicle drive transmission device 100 is mounted on, for example, a hybrid vehicle having an internal combustion engine and a rotary electric machine as a driving force source, or an electric vehicle having a rotary electric machine as a driving force source.

As shown in FIGS. 1 and 2, the vehicle drive transmission device 100 includes an input member 1 having an input gear 11 and being driven and connected to a driving force source, a counter input gear 21 that meshes with the input gear 11, and the counter. A counter gear mechanism 2 having a counter output gear 22 that rotates integrally with the input gear 21 and a differential gear mechanism 3 having a differential input gear 31 that meshes with the counter output gear 22 are driven and connected to the wheels W, respectively. A pair of output members 4 and the like. In the present embodiment, the vehicle drive transmission device 100 further includes a transmission shaft 5 that is drive-connected to one of the pair of output members 4.

Here, in the present application, the "driving connection" refers to a state in which two rotating elements are connected so as to be able to transmit a driving force, and the two rotating elements are connected so as to rotate integrally, or the said. It includes a state in which two rotating elements are mutably connected so that a driving force can be transmitted via one or more transmission members. Such transmission members include various members that transmit rotation at the same speed or at different speeds, such as shafts, gear mechanisms, belts, chains, and the like. The transmission member may include an engaging device that selectively transmits rotation and driving force, for example, a friction engaging device, a meshing type engaging device, and the like. However, in the differential gear mechanism 3, the term "drive connection" for each rotating element means a state in which they are driven and connected to each other without interposing other rotating elements.

In the present embodiment, the rotary electric machine MG corresponds to the "driving force source". That is, in the present embodiment, the input member 1 is drive-connected to the rotary electric machine MG. In the present application, "rotary electric machine" is used as a concept including any of a motor (motor), a generator (generator), and, if necessary, a motor / generator that functions as both a motor and a generator.

The rotary electric machine MG and the input member 1 are arranged on the first axis X1 as their rotation axis. The counter gear mechanism 2 is arranged on the second axis X2 as its rotation axis. The differential gear mechanism 3 is arranged on the third axis X3 as its rotation axis. The first axis X1, the second axis X2, and the third axis X3 are virtual axes that are different from each other and are arranged in parallel with each other.

In the following description, the direction parallel to the axes X1 to X3 will be referred to as the "axial direction L" of the vehicle drive transmission device 100. Then, in the axial direction L, the side of the counter output gear 22 with respect to the counter input gear 21 is referred to as the "axial first side L1", and the opposite side is referred to as the "axial second side L2". Further, the direction orthogonal to each of the above axes X1 to X3 is defined as the "diameter direction R" with respect to each axis. When it is not necessary to distinguish which axis is used as a reference, or when it is clear which axis is used as a reference, it may be simply described as "diameter direction R".

In the present embodiment, the rotary electric machine MG, the input member 1, the counter gear mechanism 2, the differential gear mechanism 3, and the pair of output members 4 are housed in the case 9. As shown in FIG. 1, the case 9 includes a first case portion 91, a second case portion 92, and a third case portion 93.

The first case portion 91 has a first peripheral wall portion 911, a second peripheral wall portion 912, and a first side wall portion 913. Each of the first peripheral wall portion 911 and the second peripheral wall portion 912 is formed in a cylindrical shape having an axial center along the axial direction L. The first side wall portion 913 is formed so as to close the opening of the first peripheral wall portion 911 on the second side L2 in the axial direction and the opening of the second peripheral wall portion 912 on the first side L1 in the axial direction. That is, the first side wall portion 913 to the first peripheral wall portion 911 are formed so as to extend to the first side L1 in the axial direction, and the first side wall portion 913 to the second peripheral wall portion 912 are formed to extend from the first side wall portion 913 to the second side L2 in the axial direction. It is formed so as to extend to.

The second case portion 92 has a third peripheral wall portion 921 and a second side wall portion 922. The third peripheral wall portion 921 is formed in a cylindrical shape having an axial center along the axial direction L. The third peripheral wall portion 921 is configured to be joined to the first peripheral wall portion 911 from the first side L1 in the axial direction. In the present embodiment, the ends of the third peripheral wall portion 921 on the second side L2 in the axial direction are in contact with the ends of the first peripheral side L1 in the axial direction of the first peripheral wall portion 911, and these ends are bolted together. Is fixed by. The second side wall portion 922 is formed so as to close the opening of the third peripheral wall portion 921 on the first side L1 in the axial direction.

The third case portion 93 has a fourth peripheral wall portion 931 and a third side wall portion 932. The fourth peripheral wall portion 931 is formed in a cylindrical shape having an axial center along the axial direction L. The fourth peripheral wall portion 931 is configured to be joined to the second peripheral wall portion 912 from the second side L2 in the axial direction. In the present embodiment, the ends of the fourth peripheral wall portion 931 on the first side L1 in the axial direction are in contact with the ends of the second peripheral side L2 in the axial direction of the second peripheral wall portion 912, and these ends are bolted together. Is fixed by.

In the present embodiment, inside the case 9, the first space A1 surrounded by the first peripheral wall portion 911, the first side wall portion 913, the third peripheral wall portion 921, and the second side wall portion 922, and the second peripheral wall portion A second space A2 surrounded by 912, a first side wall portion 913, a fourth peripheral wall portion 931, and a third side wall portion 932 is formed. A rotary electric machine MG is arranged in the first space A1. A counter gear mechanism 2, a differential gear mechanism 3, and a pair of output members 4 are arranged in the second space A2. Further, the input member 1 and the transmission shaft 5 penetrate the first side wall portion 913 in the axial direction L, and are arranged over the first space A1 and the second space A2.

As shown in FIG. 1, the rotary electric machine MG includes a stator ST and a rotor RT. The stator ST has a stator core STC fixed to a non-rotating member (here, case 9). The rotor RT has a rotor core RTC that can rotate with respect to the stator ST, and a rotor shaft RTS that is connected so as to rotate integrally with the rotor core RTC. In the present embodiment, the rotary electric machine MG is a rotary field type rotary electric machine. Therefore, the coil CL is wound around the stator core STC so that coil end portions CLE projecting from the stator core STC on both sides in the axial direction L (the first side L1 in the axial direction and the second side L2 in the axial direction) are formed. Has been done. A permanent magnet PM is provided on the rotor core RTC. Further, in the present embodiment, the rotary electric machine MG is an inner rotor type rotary electric machine. Therefore, the rotor core RTC is arranged inside the stator core STC in the radial direction R. Then, the rotor shaft RTS is connected to the inner peripheral surface of the rotor core RTC.

The rotor shaft RTS is formed so as to extend along the axial direction L. The rotor shaft RTS rotates with the first shaft X1 as the rotation axis. In the present embodiment, the rotor shaft RTS is formed in a cylindrical shape having an axial center along the axial direction L. Further, in the present embodiment, the rotor shaft RTS is rotatably supported by the first rotor bearing B11 and the second rotor bearing B12 arranged on the second side L2 in the axial direction from the first rotor bearing B11. ing. In the illustrated example, the end portion of the rotor shaft RTS on the first side L1 in the axial direction is rotatably supported with respect to the second side wall portion 922 of the case 9 via the first rotor bearing B11. Then, the end portion of the rotor shaft RTS on the second side L2 in the axial direction is rotatably supported with respect to the first side wall portion 913 of the case 9 via the second rotor bearing B12.

The input member 1 includes an input shaft 12 extending along the axial direction L. In the present embodiment, the input shaft 12 is rotatably supported by the first input bearing B21 and the second input bearing B22 arranged on the second side L2 in the axial direction with respect to the first input bearing B21. .. In the illustrated example, the portion of the input shaft 12 on the first side L1 in the axial direction with respect to the central portion in the axial direction L can rotate with respect to the first side wall portion 913 of the case 9 via the first input bearing B21. It is supported. Then, the end portion of the input shaft 12 on the second side L2 in the axial direction is rotatably supported with respect to the third side wall portion 932 of the case 9 via the second input bearing B22.

The input gear 11 corresponds to the "first gear". The input gear 11 is connected so as to rotate integrally with the input shaft 12. In this embodiment, the input gear 11 is integrally formed with the input shaft 12. Further, in the present embodiment, the input gear 11 is arranged between the first input bearing B21 and the second input bearing B22 in the axial direction L.

As shown in FIG. 3, in the present embodiment, the input member 1 is provided with the first input step portion 13 and the second input step portion 14.

The diameter of the portion of the input shaft 12 on the first side L1 in the axial direction with respect to the first input step portion 13 is larger than the diameter of the portion of the portion L2 on the second side in the axial direction with respect to the first input step portion 13. The first input step portion 13 is formed by the step between the portions having different diameters. The first input step portion 13 is formed with a first input step surface 13a facing the first side L1 in the axial direction. In the illustrated example, the input shaft 12 is formed so as to have a constant radial dimension R over the entire area between the first input step surface 13a and the input gear 11 in the axial direction L. The first input step portion 13 corresponds to the "third step portion", and the first input step surface 13a corresponds to the "third step surface".

The first input bearing B21 is arranged so as to come into contact with the first input step surface 13a from the first side L1 in the axial direction. In the illustrated example, the first input bearing B21 is a ball bearing. Then, the inner ring B21a of the first input bearing B21 is fitted to the outer peripheral surface of the input shaft 12 on the first side L1 in the axial direction with respect to the first input step surface 13a, and is axially oriented with respect to the first input step surface 13a. It is arranged so as to abut from the first side L1. Further, the outer ring B21b of the first input bearing B21 is supported by the first side wall portion 913 of the case 9 from the outside in the radial direction R, and the second side L2 in the axial direction formed on the first side wall portion 913 is supported. It is arranged so as to abut from the second side L2 in the axial direction with respect to the facing first input contact surface 9a.

The diameter of the portion of the input shaft 12 on the first side L1 in the axial direction with respect to the second input step portion 14 is larger than the diameter of the portion of the portion L2 on the second side in the axial direction with respect to the second input step portion 14. The second input step portion 14 is formed by the step between the portions having different diameters. The second input step portion 14 is arranged on the second side L2 in the axial direction with respect to the first input step portion 13. The second input step portion 14 is formed with a second input step surface 14a facing the second side L2 in the axial direction. In the illustrated example, the input shaft 12 is formed so as to have a constant radial R dimension over the entire area between the second input step surface 14a and the input gear 11 in the axial direction L. The second input step portion 14 corresponds to the "fourth step portion", and the second input step surface 14a corresponds to the "fourth step surface".

The second input bearing B22 is arranged so as to come into contact with the second input step surface 14a from the second side L2 in the axial direction. In the illustrated example, the second input bearing B22 is a ball bearing. Then, the inner ring B22a of the second input bearing B22 is fitted to the outer peripheral surface of the input shaft 12 on the second side L2 in the axial direction with respect to the second input step surface 14a, and is axially oriented with respect to the second input step surface 14a. It is arranged so as to abut from the second side L2. Further, the outer ring B22b of the second input bearing B22 is supported by the third side wall portion 932 of the case 9 from the outside in the radial direction R, and the first side L1 in the axial direction formed on the third side wall portion 932 is supported. It is arranged so as to abut from the first side L1 in the axial direction with respect to the facing second input contact surface 9b.

As shown in FIG. 1, in the present embodiment, the input shaft 12 is connected to the rotary electric machine MG so as to be integrally rotatable and relatively movable in the axial direction L. In the illustrated example, the portion of the input shaft 12 protruding toward the first side L1 in the axial direction from the first input bearing B21 has a diameter with respect to the portion of the rotor shaft RTS protruding toward the second side L2 in the axial direction with respect to the rotor core RTC. It is inserted inside the direction R from the second side L2 in the axial direction, and these portions are connected to each other by spline engagement.

The counter gear mechanism 2 includes a connecting shaft 23 that connects the counter input gear 21 and the counter output gear 22. The connecting shaft 23 is formed so as to extend along the axial direction L. In the present embodiment, the connecting shaft 23 is rotatably supported by the first counter bearing B31 and the second counter bearing B32 arranged on the second side L2 in the axial direction from the first counter bearing B31. .. In the illustrated example, the end portion of the connecting shaft 23 on the first side L1 in the axial direction is rotatably supported with respect to the first side wall portion 913 of the case 9 via the first counter bearing B31. Then, the end portion of the connecting shaft 23 on the second side L2 in the axial direction is rotatably supported with respect to the third side wall portion 932 of the case 9 via the second counter bearing B32.

The counter input gear 21 corresponds to the "second gear". The counter input gear 21 is engaged so as to rotate integrally with the connecting shaft 23. As shown in FIG. 3, in the present embodiment, the counter input gear 21 is movable relative to the tooth forming portion 211 having a plurality of teeth formed on the outer peripheral surface and the connecting shaft 23 in the axial direction L and in the circumferential direction. It has an engaging portion 212, which is engaged with a relative non-rotatable portion. The tooth forming portion 211 is arranged outside the radial direction R with respect to the engaging portion 212. The tooth forming portion 211 is connected to the engaging portion 212 so as to rotate integrally. The engaging portion 212 is formed in a cylindrical shape that covers the outer peripheral surface of the connecting shaft 23. In the illustrated example, the engaging portion 212 is connected to the connecting shaft 23 by spline engagement.

The counter output gear 22 corresponds to the "third gear". The counter output gear 22 is integrally formed with the connecting shaft 23. In the illustrated example, a plurality of teeth are formed on the outer peripheral surface of the cylindrical portion of the connecting shaft 23 having a diameter larger than that between the counter input gear 21 and the counter output gear 22 in the axial direction L. As a result, the counter output gear 22 is formed. Further, the counter output gear 22 is formed to have a smaller diameter than the counter input gear 21.

The connecting shaft 23 is provided with a counter step portion 24. The connecting shaft 23 is formed so that the diameter of the portion L1 on the first side in the axial direction with respect to the counter step portion 24 is larger than the diameter of the portion L2 on the second side in the axial direction with respect to the step portion 24 of the counter. The counter step portion 24 is formed by the step between the portions having different diameters. The counter step portion 24 is formed with a counter step surface 24a facing the second side L2 in the axial direction. In the illustrated example, the counter step portion 24 is formed so as to have a constant radial dimension R over the entire area between the counter step surface 24a and the counter output gear 22 in the axial direction L. The counter step portion 24 corresponds to the "first step portion", and the counter step surface 24a corresponds to the "first step surface".

The counter input gear 21 is arranged so as to come into contact with the counter step surface 24a from the second side L2 in the axial direction. In the present embodiment, the engaging portion 212 of the counter input gear 21 is in contact with the counter step surface 24a from the second side L2 in the axial direction.

In the present embodiment, the second counter bearing B32 includes an inner ring B32a, an outer ring B32b arranged outside the inner ring B32a in the radial direction R, and a plurality of outer rings B32a arranged between the inner ring B32a and the outer ring B32b. It is a conical roller bearing provided with a conical rolling element B32c. The second counter bearing B32 is arranged so that the axial center of the rolling element B32c faces the inside of the radial direction R of the connecting shaft 23 toward the second side L2 in the axial direction. Further, the second counter bearing B32 is arranged so that the inner ring B32a is fitted to the outer peripheral surface of the connecting shaft 23 and comes into contact with the counter input gear 21 from the second side L2 in the axial direction. In the illustrated example, the inner ring B32a of the second counter bearing B32 is fitted to the outer peripheral surface of the connecting shaft 23 on the second side L2 in the axial direction with respect to the engaging portion 212 of the counter input gear 21, and is fitted on the outer peripheral surface of the connecting shaft 23 on the second side in the axial direction. It is in contact with the engaging portion 212 from L2. Further, in the illustrated example, the outer ring B32b of the second counter bearing B32 is supported by the third side wall portion 932 of the case 9 from the outside in the radial direction R, and the axial direction formed on the third side wall portion 932. It is in contact with the second counter contact surface 9d facing the first side L1 from the first side L1 in the axial direction.

In the present embodiment, the end surface of the second side L2 in the axial direction of the connecting shaft 23 overlaps with the second counter bearing B32 in the radial direction along the radial direction R of the connecting shaft 23. That is, the connecting shaft 23 does not protrude from the second counter bearing B32 on the second side L2 in the axial direction. In the illustrated example, the outer ring B32b of the second counter bearing B32 overlaps with the end face of the second side L2 in the axial direction of the connecting shaft 23 in the radial direction. Here, regarding the arrangement of the two elements, "overlapping in a specific direction" means that the virtual straight line is 2 when the virtual straight line parallel to the line-of-sight direction is moved in each direction orthogonal to the virtual straight line. It means that there is at least a part of the area where both of the two elements intersect.

Further, in the present embodiment, the first counter bearing B31 is arranged between the inner ring B31a, the outer ring B31b arranged outside the inner ring B31a in the radial direction R, and between the inner ring B31a and the outer ring B31b. A conical roller bearing including a plurality of conical rolling elements B31c. The first counter bearing B31 is arranged so that the axial center of the rolling element B31c faces the inside of the radial direction R of the connecting shaft 23 toward the first side L1 in the axial direction. Further, the first counter bearing B31 is arranged so that the inner ring B31a is fitted to the outer peripheral surface of the connecting shaft 23 and comes into contact with the counter output gear 22 from the first side L1 in the axial direction. In the illustrated example, the inner ring B31a of the first counter bearing B31 is fitted to the outer peripheral surface of the connecting shaft 23 on the first side L1 in the axial direction with respect to the counter output gear 22, and the counter output gear is fitted from the first side L1 in the axial direction. It is in contact with 22. Further, in the illustrated example, the outer ring B31b of the first counter bearing B31 is supported by the first side wall portion 913 of the case 9 from the outside in the radial direction R, and the axial direction formed on the first side wall portion 913. It is in contact with the first counter contact surface 9c facing the second side L2 from the second side L2 in the axial direction.

As shown in FIG. 1, the differential gear mechanism 3 includes a differential case 32 and a differential gear group 34.

The differential input gear 31 is connected to the differential case 32 so as to rotate integrally. Specifically, as shown in FIG. 3, the differential case 32 is provided with a differential step portion 33 that forms a differential step surface 33a facing the second side L2 in the axial direction. Then, the differential input gear 31 is fixed to the differential case 32 by using a fastening member F (see FIG. 1) such as a bolt in a state where the differential input gear 31 is in contact with the differential stepped surface 33a from the second side L2 in the axial direction. Has been done. The differential input gear 31 corresponds to the "fourth gear". Further, the differential step portion 33 corresponds to the "second step portion", and the differential step surface 33a corresponds to the "second step surface". In the present embodiment, the differential case 32 is from the main body portion 321 that opens toward the first side L1 in the axial direction and from the first side L1 in the axial direction with respect to the main body portion 321 so as to close the opening of the main body portion 321. It includes a lid portion 322 to be joined. The joint portion between the main body portion 321 and the lid portion 322 is formed so as to project outward in the radial direction R of the differential case 32, and the joint portion is configured as the differential step portion 33. In this example, the differential step portion 33 is formed in a flange shape that projects outward in the radial direction R over the entire peripheral portion of the differential case 32 in the circumferential direction.

Further, in the present embodiment, as shown in FIGS. 1 and 3, the fastening member F penetrates the differential input gear 31, the main body portion 321 and the lid portion 322 in the axial direction L, and integrally fastens them. It is configured to do. In the illustrated example, a female screw portion is formed on the lid portion 322, and a through hole is formed at a position corresponding to the female screw portion on the main body portion 321 and the differential input gear 31. Then, the bolt as the fastening member F is inserted into the through hole formed in the differential input gear 31 and the main body portion 321 from the second side L2 in the axial direction, and screwed into the female screw portion formed in the lid portion 322. There is. As a result, the differential input gear 31 and the lid portion 322 are fastened together with the main body portion 321.

In the present embodiment, the differential case 32 can be rotated by the first differential bearing B41 and the second differential bearing B42 arranged on the second side L2 in the axial direction with respect to the first differential bearing B41. It is supported. In the illustrated example, the end portion of the lid portion 322 of the differential case 32 on the first side L1 in the axial direction is rotatably supported with respect to the first side wall portion 913 of the case 9 via the first differential bearing B41. Has been done. Then, the end portion of the axial second side L2 in the main body portion 321 of the differential case 32 is rotatably supported with respect to the third side wall portion 932 of the case 9 via the second differential bearing B42. ..

In the present embodiment, the first differential bearing B41 includes an inner ring B41a, an outer ring B41b arranged outside the inner ring B41a in the radial direction R, and a plurality of the first differential bearings B41 arranged between the inner ring B41a and the outer ring B41b. It is a conical roller bearing provided with a conical rolling element B41c. The first differential bearing B41 is arranged so that the axial center of the rolling element B41c faces the inside of the radial direction R of the differential case 32 toward the first side L1 in the axial direction. Further, in the present embodiment, the inner ring B41a of the first differential bearing B41 is fitted to the outer peripheral surface of the lid portion 322 of the differential case 32 to form an axial first side L1 formed on the lid portion 322. It is arranged so as to abut from the first side L1 in the axial direction with respect to the facing lid step surface 322a. The outer ring B41b of the first differential bearing B41 is supported by the first side wall portion 913 of the case 9 from the outside in the radial direction R, and the axial second side L2 formed on the first side wall portion 913. It is arranged so as to abut from the second side L2 in the axial direction with respect to the first differential contact surface 9e facing.

Further, in the present embodiment, the second differential bearing B42 is arranged between the inner ring B42a, the outer ring B42b arranged outside the inner ring B42a in the radial direction R, and between the inner ring B42a and the outer ring B42b. It is a conical roller bearing provided with a plurality of conical rolling elements B42c. The second differential bearing B42 is arranged so that the axial center of the rolling element B42c faces the inside of the radial direction R of the differential case 32 toward the second side L2 in the axial direction. Further, in the present embodiment, the inner ring B42a of the second differential bearing B42 is fitted to the outer peripheral surface of the main body portion 321 of the differential case 32 to form an axial second side L2 formed on the main body portion 321. It is arranged so as to come into contact with the main body step surface 321a facing from the second side L2 in the axial direction. The outer ring B42b of the second differential bearing B42 is supported by the third side wall portion 932 of the case 9 from the outside in the radial direction R, and the axial first side L1 formed on the third side wall portion 932. It is arranged so as to abut from the first side L1 in the axial direction with respect to the second differential contact surface 9f facing.

The differential case 32 houses the differential gear group 34. In the present embodiment, a space for accommodating the differential gear group 34 is formed inside the radial direction R in the main body portion 321 of the differential case 32.

As shown in FIG. 1, the differential gear group 34 distributes the rotation of the differential input gear 31 to a pair of output members 4. In the present embodiment, in the axial direction L, the center of the differential gear group 34 in the axial direction L is opposite to the side of the rotary electric machine MG with respect to the differential input gear 31 (here, the second side L2 in the axial direction). ) Is placed.

In the present embodiment, the differential gear group 34 includes a pair of pinion gears 35, a first side gear 36, and a second side gear 37. Here, the pair of pinion gears 35, and the first side gear 36 and the second side gear 37 are all bevel gears.

The pair of pinion gears 35 are arranged so as to face each other at intervals along the radial direction R with respect to the third axis X3. The pair of pinion gears 35 are attached to a pinion shaft 38 supported so as to rotate integrally with the differential case 32. Each of the pair of pinion gears 35 is configured to be rotatable (rotating) about the pinion shaft 38 and rotating (revolving) about the third axis X3.

The first side gear 36 and the second side gear 37 are arranged so as to face each other with the pinion shaft 38 interposed therebetween at intervals in the axial direction L. The first side gear 36 is arranged on the first side L1 in the axial direction with respect to the second side gear 37. The first side gear 36 and the second side gear 37 are configured to rotate in the circumferential direction in the internal space of the differential case 32, respectively. The first side gear 36 and the second side gear 37 mesh with a pair of pinion gears 35.

One of the pair of output members 4 is connected to the first side gear 36 so as to rotate integrally. The other of the pair of output members 4 is connected to the second side gear 37 so as to rotate integrally. In the following description, the output member 4 connected to the first side gear 36 is referred to as a “first output member 41”, and the output member 4 connected to the second side gear 37 is referred to as a “second output member 42”.

In the present embodiment, the first output member 41 is formed in a cylindrical shape having an axial center along the axial direction L. The first output member 41 is arranged inside the radial direction R with respect to the first side gear 36. In the illustrated example, the first output member 41 is integrally formed with the first side gear 36.

Further, in the present embodiment, the first output member 41 is connected so as to rotate integrally with the transmission shaft 5. In the illustrated example, the end of the axial second side L2 of the transmission shaft 5 is inserted from the axial first side L1 inside the radial direction R with respect to the first output member 41, and they are inserted by spline engagement. They are connected to each other.

In the present embodiment, the transmission shaft 5 penetrates the second side wall portion 922 of the case 9 in the axial direction L so that the end portion of the axial first side L1 of the transmission shaft 5 is exposed to the outside of the case 9. doing. The transmission shaft 5 is connected so as to rotate integrally with the first drive shaft DS1. In the illustrated example, the portion of the transmission shaft 5 from the end surface of the first side L1 in the axial direction to the first side L1 in the axial direction from the center of the axial direction L has a cylindrical shape that opens in the first side L1 in the axial direction. It is formed. Then, the first drive shaft DS1 is inserted from the first side L1 in the axial direction inside the radial direction R with respect to the transmission shaft 5, and they are connected to each other by spline engagement. Further, in the present embodiment, the transmission shaft 5 is rotatably supported with respect to the case 9 by the output bearing B5 supported by the second side wall portion 922 of the case 9.

In the present embodiment, the second output member 42 is formed in a cylindrical shape having an axial center along the axial direction L. The second output member 42 is arranged inside the radial direction R with respect to the second side gear 37. In the illustrated example, the second output member 42 is integrally formed with the second side gear 37.

Further, in the present embodiment, the second output member 42 has a third side wall portion 932 of the case 9 so that the end portion of the second side L2 in the axial direction of the second output member 42 is exposed to the outside of the case 9. Penetrates in the axial direction L. The second output member 42 is connected to the second drive shaft DS2 so as to rotate integrally with the second drive shaft DS2. In the illustrated example, the second drive shaft DS2 is inserted from the axial second side L2 inside the radial direction R with respect to the second output member 42, and they are connected to each other by spline engagement.

In the vehicle drive transmission device 100 configured as described above, each of the input gear 11, the counter input gear 21, the counter output gear 22, and the differential input gear 31 is an oblique gear. By using these gears as oblique gears, gear noise can be reduced as compared with the case where these gears are spur gears. On the other hand, since these gears are oblique gears, a load (thrust load) along the axial direction L acts on each gear in a state where torque is transmitted by these gears, such as when the vehicle is running. Here, as shown in FIG. 3, the thrust load acting on the counter input gear 21 from the counter input gear 21 is defined as the “first load F1”, and the thrust load acting on the counter input gear 21 from the input gear 11 is defined as the “second load”. Let it be "F2". Further, the thrust load acting on the counter output gear 22 from the differential input gear 31 is referred to as "third load F3", and the thrust load acting on the differential input gear 31 from the counter output gear 22 is referred to as "fourth load F4". .. The first load F1 and the second load F2 are in opposite directions, and the third load F3 and the fourth load F4 are in opposite directions.

As shown in FIG. 3, in a state where the rotary electric machine MG is driving in the forward rotation direction, the first load F1 faces the second side L2 in the axial direction, and the second load F2 faces the first side L1 in the axial direction. The input gear 11, the counter input gear 21, the counter output gear 22, and the differential input gear 31 so that the third load F3 faces the second side L2 in the axial direction and the fourth load F4 faces the first side L1 in the axial direction. The orientation of each oblique tooth is set. Here, the "forward rotation direction" of the rotary electric machine MG is the rotation of the rotary electric machine MG (here, the rotor RT) when the wheels W are rotated in the direction in which the vehicle on which the vehicle drive transmission device 100 is mounted is advanced. The direction. Further, the "direction of the oblique teeth" of each gear refers to the direction of the helix angle (twisting direction) of the teeth of each gear.

The fourth load F4 is set in a direction in which the differential input gear 31 is pressed against the differential stepped surface 33a of the differential case 32 while the rotary electric machine MG is running in the forward rotation direction. Therefore, when the rotary electric machine MG is forcing in the forward rotation direction, the load in the direction of loosening the fastening member F does not act on the differential input gear 31, but acts on the differential input gear 31. The 4-load F4 is received by the differential stepped surface 33a.

Further, the second load F2 is set in a direction of canceling the third load F3 in a state where the rotary electric machine MG is running in the forward rotation direction. The direction of such a second load F2 coincides with the direction in which the counter input gear 21 is relatively moved toward the first side L1 in the axial direction with respect to the connecting shaft 23. However, as described above, the counter input gear 21 is in contact with the counter step surface 24a of the connecting shaft 23 from the second side L2 in the axial direction. Therefore, the second load F2 is received by the counter step surface 24a of the connecting shaft 23 when the rotary electric machine MG is running in the forward rotation direction.

As shown in FIG. 3, in the present embodiment, the vehicle drive transmission device 100 further includes a parking gear 6. The parking gear 6 is configured to be able to switch between a non-rotatable locked state and a rotatable non-locked state by a parking lock mechanism (not shown). In the present embodiment, the parking gear 6 is arranged so as to rotate with the second axis X2 as the rotation axis. That is, the parking gear 6 is arranged coaxially with the counter gear mechanism 2. Further, in the present embodiment, the parking gear 6 is integrally formed with the counter input gear 21 so as to be adjacent to the counter input gear 21 of the counter gear mechanism 2 in the axial direction L. In the illustrated example, the parking gear 6 is integrally formed with the tooth forming portion 211 of the counter input gear 21 so as to be adjacent to the second side L2 in the axial direction.

2. Second Embodiment In the following, the vehicle drive transmission device 100 according to the second embodiment will be described with reference to FIG. In the present embodiment, the directions of the counter gear mechanism 2 and the differential gear mechanism 3 are different from those of the first embodiment. Hereinafter, the differences from the first embodiment will be mainly described. The points not particularly described are the same as those in the first embodiment.

As shown in FIG. 4, in the present embodiment, in the counter gear mechanism 2, the counter output gear 22 is arranged on the side opposite to the side of the rotary electric machine MG with respect to the counter input gear 21 in the axial direction L. Therefore, in the first embodiment, the first side L1 in the axial direction, which is the side of the counter output gear 22 with respect to the counter input gear 21, is on the side of the rotary electric machine MG with respect to the input member 1. Therefore, in the present embodiment, the first side L1 in the axial direction is on the side of the input member 1 with respect to the rotary electric machine MG.

Further, in the present embodiment, in the differential gear mechanism 3, the center of the differential gear group 34 in the axial direction L is arranged on the side of the rotary electric machine MG in the axial direction L with respect to the differential input gear 31.

3. 3. Other Embodiments (1) In the above embodiment, the end surface of the axial second side L2 of the connecting shaft 23 overlaps with the second counter bearing B32 in the radial direction along the radial direction R of the connecting shaft 23. The configuration is described as an example. However, the configuration is not limited to such a configuration, and the connecting shaft 23 may be configured to project from the second counter bearing B32 to the second side L2 in the axial direction.

(2) In the above embodiment, a configuration in which each of the first counter bearing B31 and the second counter bearing B32 is a conical roller bearing has been described as an example. However, without being limited to such a configuration, for example, at least one of the first counter bearing B31 and the second counter bearing B32 may be a ball bearing.

(3) In the above embodiment, the first input bearing B21 is in contact with the first input step surface 13a from the first side L1 in the axial direction, and the second input bearing B22 is in contact with the second input step surface 14a. On the other hand, a configuration in which the bearing is in contact with the second side L2 in the axial direction has been described as an example. However, the present invention is not limited to such a configuration, and for example, the second input bearing B22 may be arranged so as to come into contact with the input gear 11 from the second side L2 in the axial direction. Alternatively, the first input bearing B21 may be arranged so as to come into contact with the input gear 11 from the first side L1 in the axial direction.

(4) In the above embodiment, a configuration in which the parking gear 6 is integrally formed with the counter input gear 21 so as to be adjacent to the counter input gear 21 in the axial direction L has been described as an example. However, without being limited to such a configuration, for example, the parking gear 6 may be provided independently of the counter input gear 21. Further, for example, the parking gear 6 may be connected so as to rotate integrally with the input shaft 12.

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

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

The vehicle drive transmission device (100) is
An input member (1) having a first gear (11) and being driven and connected to a driving force source (MG),
A pair of output members (4) that are driven and connected to the wheels (W), respectively.
A second gear (21) that meshes with the first gear (11), a third gear (22) that rotates integrally with the second gear (21), and the second gear (21) and the third gear ( A counter gear mechanism (2) provided with a connecting shaft (23) for connecting the 22) and the counter gear mechanism (2).
A fourth gear (31) that meshes with the third gear (22), a differential gear group (34) that distributes the rotation of the fourth gear (31) to a pair of output members (4), and the differential gear. A differential gear mechanism (3) including a differential case (32) accommodating the group (34) and connected so that the fourth gear (31) rotates integrally is provided.
In the axial direction (L), the side of the third gear (22) with respect to the second gear (21) is set as the first side (L1) in the axial direction, and the side opposite to the first side (L1) in the axial direction. As the second side (L2) in the axial direction
The connecting shaft (23) is provided with a first step portion (24) forming a first step surface (24a) facing the second side (L2) in the axial direction.
The second gear (21) rotates integrally with the connecting shaft (23) in a state of being in contact with the first stepped surface (24a) from the axial second side (L2). Engaged like
The third gear (22) is integrally formed with the connecting shaft (23).
The differential case (32) is provided with a second step portion (33) forming a second step surface (33a) facing the second side (L2) in the axial direction.
The fourth gear (31) is in contact with the second stepped surface (33a) from the second side (L2) in the axial direction, and the differential case (32) is provided by using the fastening member (F). ) Is fixed to
Each of the first gear (11), the second gear (21), the third gear (22), and the fourth gear (31) is an oblique gear.
The rotation direction of the driving force source (MG) when the vehicle is moved forward is set to the normal rotation direction.
A thrust load from the second gear (21) to the first gear (11) toward the second side (L2) in the axial direction while the driving force source (MG) is driving in the forward rotation direction. (F1) acts, and the thrust load (F2) toward the first side (L1) in the axial direction acts on the second gear (21) from the first gear (11), and the first gear (F2) acts. A thrust load (F3) directed from the fourth gear (31) to the third gear (22) acts on the second side (L2) in the axial direction, and the third gear (22) to the fourth gear (22). The first gear (11), the second gear (21), the third gear (22), so that the thrust load (F4) toward the first side (L1) in the axial direction acts on 31). And the orientation of each oblique tooth of the fourth gear (31) is set.

According to this configuration, the thrust from the third gear (22) to the fourth gear (31) toward the first side (L1) in the axial direction while the driving force source (MG) is running in the forward rotation direction. The load (F4), that is, the thrust load (F4) in the direction of pressing the fourth gear (31) against the second step surface (33a) of the differential case (32) acts. Here, the fourth gear (31) uses the fastening member (F) in a state where it is in contact with the second stepped surface (33a) of the differential case (32) from the second side (L2) in the axial direction. It is fixed to the differential case (32). Therefore, when the driving force source (MG) is running in the forward rotation direction, the load in the direction of loosening the fastening member (F) does not act on the fourth gear (31), and the fourth gear The thrust load (F4) acting on (31) is received by the second stepped surface (33a). Therefore, the possibility that the fastening member (F) that fixes the fourth gear (31) to the differential case (32) will loosen can be reduced.
Further, according to this configuration, in a state where the driving force source (MG) is driving in the forward rotation direction, the first gear (11) is directed to the second gear (21) toward the first side (L1) in the axial direction. The thrust load (F2) acts, and the thrust load (F3) directed to the second side (L2) in the axial direction acts on the third gear (22) from the fourth gear (31). Therefore, a thrust load directed to the opposite side in the axial direction (L) acts on the second gear (21) and the third gear (22) connected by the connecting shaft (23), and the connecting shaft (21) is connected. In 23), these thrust loads (F2, F3) can be made to act in a direction in which they cancel each other out. Therefore, it is possible to reduce the possibility that an excessive thrust load acts on the bearing supporting the connecting shaft (23).
Then, according to the present configuration, the second gear (21) is connected to the first stepped surface (24a) of the connecting shaft (23) in a state of being in contact with the first step surface (24a) in the axial direction from the second side (L2). It is engaged so as to rotate integrally with the shaft (23). Therefore, when the driving force source (MG) is powering in the forward rotation direction, the thrust in the direction of relatively moving the second gear (21) to the first side (L1) in the axial direction with respect to the connecting shaft (23). The load (F2) is received by the first stepped surface (24a). Therefore, the need to install a receiving member such as a nut for receiving the thrust load in the direction of relatively moving the second gear (21) to the second side (L2) in the axial direction with respect to the connecting shaft (23) is reduced. can do. As a result, the manufacturing cost of the vehicle drive transmission device (100) provided with the oblique tooth gear can be kept low.

In the above configuration, the connecting shaft (23) is arranged on the first counter bearing (B31) and the second counter bearing (L2) in the axial direction with respect to the first counter bearing (B31) (L2). B32) and rotatably supported, the end face of the connecting shaft (23) on the second side (L2) in the axial direction is radially viewed along the radial direction (R) of the connecting shaft (23). It is suitable when it overlaps with the second counter bearing (B32). In such a configuration, the end of the connecting shaft (23) on the second side (L2) in the axial direction does not protrude from the second counter bearing (B32) on the second side (L2) in the axial direction, and the second A receiving member that receives a thrust load in a direction that relatively moves the gear (21) toward the second side (L2) in the axial direction with respect to the connecting shaft (23) is provided on the second side (L2) in the axial direction of the connecting shaft (23). This is because it is difficult to install it at the end of the.

In a configuration in which the connecting shaft (23) is rotatably supported by the first counter bearing (B31) and the second counter bearing (B32).
The second counter bearing (B32) is a conical roller bearing having a plurality of rolling elements (B32c) between the inner ring (B32a) and the outer ring (B32b), and the axial center of the rolling element (B32c) is The inner ring (B32a) is arranged so as to face the inside of the radial direction (R) of the connecting shaft (23) toward the second side (L2) in the axial direction, and the inner ring (B32a) of the connecting shaft (23). It is preferable that the bearing is fitted to the outer peripheral surface and arranged so as to abut the second gear (21) from the second side (L2) in the axial direction.

According to this configuration, the thrust load acting on the second gear (21) toward the second side (L2) in the axial direction is applied from the second side (L2) in the axial direction with respect to the second gear (21). It can be received by the contacting inner ring (B32a). The thrust load from the second gear (21) toward the second side (L2) in the axial direction acting on the inner ring (B32a) is transmitted to the outer ring (B32b) via the rolling element (B32c), and the outer ring (B32b) is transmitted. It is received by the supporting member (9). Therefore, according to this configuration, the second counter bearing (B32) receives the thrust load in the direction in which the second gear (21) is relatively moved toward the second side (L2) in the axial direction with respect to the connecting shaft (23). Can be done. The thrust load in the direction of relatively moving the second gear (21) to the second side (L2) in the axial direction with respect to the connecting shaft (23) is, for example, the driving force source (MG) rotating in the forward rotation direction. It occurs while regenerating, or when the driving force source (MG) is rotating and driving in the reverse direction, which is the opposite direction to the forward rotation direction. It is shorter than the period during which the force source (MG) runs in the forward rotation direction. Therefore, the thrust load in the direction of relatively moving the second gear (21) to the second side (L2) in the axial direction with respect to the connecting shaft (23) can be applied to the second counter bearing (B32) without installing a receiving member. ) Can be properly accepted.

Further, the input member (1) is connected to the driving force source (MG) so as to be integrally rotatable and relatively movable in the axial direction (L), and the first input bearing (B21). And the second input bearing (B22) rotatably supported by the second input bearing (B22) arranged on the second side (L2) in the axial direction with respect to the first input bearing (B21).
A third step portion (13) forming a third step surface (13a) facing the first side (L1) in the axial direction on the input member (1), and the shaft rather than the third step portion (13). A fourth step portion (14) arranged on the second side (L2) in the direction and forming a fourth step surface (14a) facing the second side (L2) in the axial direction is provided.
The first input bearing (B21) is arranged so as to abut against the third stepped surface (13a) from the first side (L1) in the axial direction, and the second input bearing (B22) is the first. It is preferable that the four stepped surfaces (14a) are arranged so as to be in contact with the second side (L2) in the axial direction.

According to this configuration, the thrust load toward the first side (L1) in the axial direction acting on the input member (1) is received by the third step surface (13a) according to the operating state of the driving force source (MG). In addition, the thrust load acting on the input member (1) toward the second side (L2) in the axial direction can be received by the fourth stepped surface (14a). Therefore, it is possible to reduce the need to install a receiving member that receives the thrust load acting on the input member (1). As a result, the manufacturing cost of the vehicle drive transmission device (100) can be further suppressed.

Further, in the axial direction (L), the center of the differential gear group (34) in the axial direction (L) is on the side of the driving force source (MG) with respect to the fourth gear (31). It is preferable that it is arranged on the opposite side.

According to this configuration, the radial dimension (R) of the differential gear mechanism (3) can be reduced as the distance from the driving force source (MG) increases in the axial direction (L). This makes it easy to keep the radial dimension (R) at the end of the vehicle drive transmission device (100) in the axial direction (L) small. Therefore, it is possible to improve the mountability of the vehicle drive transmission device (100) on the vehicle.

Further, a parking gear (6) arranged coaxially with the counter gear mechanism (2) is further provided.
It is preferable that the parking gear (6) is integrally formed with the second gear (21) so as to be adjacent to the second gear (21) in the axial direction (L).

According to this configuration, the vehicle drive transmission device (100) can be easily miniaturized as compared with the configuration in which the parking gear (6) is provided independently of the second gear (21). Further, since it is not necessary to separately perform the assembly work of the parking gear (6), the man-hours for manufacturing the vehicle drive transmission device (100) can be reduced.

The technology according to the present disclosure can be used for a vehicle drive transmission device that transmits a driving force between a driving force source and wheels.

100: Vehicle drive transmission device 1: Input member 11: Input gear (first gear)
2: Counter gear mechanism 21: Counter input gear (second gear)
22: Counter output gear (third gear)
23: Connecting shaft 24: Counter stepped portion (first stepped portion)
24a: Counter stepped surface (first stepped surface)
3: Differential gear mechanism 31: Differential input gear (4th gear)
32: Differential case 33: Differential stepped portion (second stepped portion)
33a: Differential stepped surface (second stepped surface)
34: Differential gear group 4: Output member MG: Rotating electric machine (driving force source)
W: Wheel F1: 1st load F2: 2nd load F3: 3rd load F4: 4th load L: Axial direction L1: Axial direction 1st side L2: Axial direction 2nd side

Claims (6)

An input member equipped with a first gear and driven and connected to a driving force source,
A pair of output members that are driven and connected to the wheels, respectively.
A counter gear mechanism including a second gear that meshes with the first gear, a third gear that rotates integrally with the second gear, and a connecting shaft that connects the second gear and the third gear.
A fourth gear that meshes with the third gear, a differential gear group that distributes the rotation of the fourth gear to the pair of output members, and the differential gear group are accommodated, and the fourth gear rotates integrally. With a differential gear mechanism, with a differential case connected so that
In the axial direction, the side of the third gear with respect to the second gear is the first side in the axial direction, and the side opposite to the first side in the axial direction is the second side in the axial direction.
The connecting shaft is provided with a first stepped portion that forms a first stepped surface facing the second side in the axial direction.
The second gear is engaged so as to rotate integrally with the connecting shaft in a state of being in contact with the first stepped surface from the second side in the axial direction.
The third gear is integrally formed with the connecting shaft.
The differential case is provided with a second step portion that forms a second step surface facing the second side in the axial direction.
The fourth gear is fixed to the differential case by using a fastening member in a state of being in contact with the second stepped surface from the second side in the axial direction.
Each of the first gear, the second gear, the third gear, and the fourth gear is an oblique tooth gear.
The rotation direction of the driving force source when the vehicle is moved forward is set to the normal rotation direction.
In a state where the driving force source is driving in the forward rotation direction, a thrust load directed to the second side in the axial direction acts from the second gear to the first gear, and the first gear to the first gear. A thrust load directed to the first side in the axial direction acts on the second gear, and a thrust load directed toward the second side in the axial direction acts on the third gear from the fourth gear, and the first gear. The oblique teeth of the first gear, the second gear, the third gear, and the fourth gear so that a thrust load from the third gear toward the first side in the axial direction acts on the fourth gear. Drive transmission device for vehicles with a set orientation. The connecting shaft is rotatably supported by a first counter bearing and a second counter bearing arranged on the second side in the axial direction with respect to the first counter bearing.
The vehicle drive transmission device according to claim 1, wherein the end surface of the connecting shaft on the second side in the axial direction overlaps with the second counter bearing in a radial direction along the radial direction of the connecting shaft. The second counter bearing is a conical roller bearing having a plurality of rolling elements between an inner ring and an outer ring, and the diameter of the connecting shaft as the axis of the rolling element is directed toward the second side in the axial direction. The claim that the inner ring is arranged so as to face inward in the direction, and the inner ring is fitted to the outer peripheral surface of the connecting shaft and is arranged so as to abut the second gear from the second side in the axial direction. 2. The vehicle drive transmission device according to 2. The input member is integrally rotatable with respect to the driving force source and is connected so as to be relatively movable in the axial direction, and is connected to the first input bearing and the second in the axial direction than the first input bearing. Rotatably supported by a second input bearing located on the side,
The input member is provided with a third step portion that forms a third step surface facing the first side in the axial direction, and a second step portion in the axial direction that is arranged on the second side in the axial direction with respect to the third step portion. A fourth stepped portion forming a facing fourth stepped surface is provided.
The first input bearing is arranged so as to abut against the third step surface from the first side in the axial direction, and the second input bearing is arranged on the second side in the axial direction with respect to the fourth step surface. The vehicle drive transmission device according to any one of claims 1 to 3, which is arranged so as to come into contact with the vehicle. Any one of claims 1 to 4, wherein in the axial direction, the axial center of the differential gear group is arranged on the side opposite to the driving force source side with respect to the fourth gear. The vehicle drive transmission according to the section. A parking gear arranged coaxially with the counter gear mechanism is further provided.
The vehicle drive according to any one of claims 1 to 5, wherein the parking gear is integrally formed with the second gear so as to be adjacent to the second gear in the axial direction. Transmission device.

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