CN118265855A - Joining device - Google Patents

Abstract

The clutch mechanism (1) comprises: a first friction engagement element (11) that rotates integrally with the first rotation member (81); and a second friction engagement element (12) that rotates integrally with the second rotation member (82), wherein the brake mechanism (2) has: a third friction engagement element (21) that rotates integrally with a target rotation member (8T) that is either one of the rotation members (81, 82); and a fourth friction engagement element (22) fixed to the non-rotating member (NR), wherein the pressing mechanism (3) has: a pressing part (31) configured between the friction engagement elements (11, 12) and the axial direction (L) of the friction engagement elements (21, 22); a driven part (32) which is connected with the pressing part (31) in a linkage manner; and a linear motion mechanism (33) for moving the driven part (32) in the axial direction (L), wherein the clutch mechanism (1) and the brake mechanism (2) are selectively engaged according to the movement of the driven part (32) to the first axial side (L1) or to the second axial side (L2) by the linear motion mechanism (33).

Description

Joining device

Technical Field

The present invention relates to an engagement device having a clutch mechanism and a brake mechanism.

Background

An example of such a joining device is disclosed in patent document 1 below. In the following description of the related art, reference numerals in patent document 1 are referred to in brackets.

The joining device (3) disclosed in patent document 1 includes: a clutch mechanism (31) that selectively engages the first rotary member (33) and the second rotary member (34); and a brake mechanism (32) that selectively engages the first rotating member (33) with the non-rotating member (35).

The clutch mechanism (31) has: a first friction engagement element (31 b) connected to the first rotation member (33) so as to rotate integrally therewith; and a second friction engagement element (31 a) connected to the second rotation member (34) so as to rotate integrally therewith. The brake mechanism (32) has: a third friction engagement element (32 a) connected to the first rotation member (33) so as to rotate integrally therewith; and a fourth friction engagement element (32 b) fixed to the non-rotating member (35).

Prior art literature

Patent document 1: japanese patent application laid-open No. 2012-197846.

Disclosure of Invention

Problems to be solved by the invention

The joining device (3) disclosed in patent document 1 includes: a first pressing mechanism (72) that presses the first friction engagement element (31 b) and the second friction engagement element (31 a) of the clutch mechanism (31) in the axial direction (the left-right direction in fig. 2 of patent document 1); and a second pressing mechanism (77) that presses the third friction engagement element (32 a) and the fourth friction engagement element (32 b) of the brake mechanism (32) in the axial direction.

The clutch mechanism (31) and the brake mechanism (32) are arranged in a radial direction (up-down direction in fig. 2 of patent document 1). The first pressing mechanism (72) is disposed on one side in the axial direction (right side in fig. 2 of patent document 1) with respect to the clutch mechanism (31). The second pressing mechanism (77) is disposed on the other side in the axial direction (right side in fig. 2 of patent document 1) with respect to the brake mechanism (32). Such a structure leads to an increase in the size of the joining device (3).

Therefore, in a structure having a clutch mechanism and a brake mechanism, it is desirable to realize an engagement device that can be miniaturized.

Means for solving the technical problems

In view of the above, the characteristic structure of the engagement device is an engagement device having:

a clutch mechanism selectively engaging the first rotating member and the second rotating member; and

A brake mechanism that selectively engages a target rotating member that is either one of the first rotating member and the second rotating member with a non-rotating member, wherein,

The engagement device comprises: a pressing mechanism for changing the state of engagement of the clutch mechanism and the brake mechanism,

The direction along the rotation axis of the first rotation member is set as an axial direction, one side of the axial direction is set as an axial first side, the other side of the axial direction is set as an axial second side,

The clutch mechanism has: a first frictional engagement element connected to the first rotating member so as to integrally rotate therewith; and a second friction engagement element connected to the second rotation member so as to rotate integrally therewith,

The first friction engagement element and the second friction engagement element are arranged to oppose each other in the axial direction and to be friction-engaged with each other by being pressed in the axial direction,

The brake mechanism has: a third friction engagement element connected to the object rotation member so as to integrally rotate therewith; and a fourth frictional engagement element fixed to the non-rotating member,

The third friction engagement element and the fourth friction engagement element are arranged in a manner opposed to each other in the axial direction at positions separated toward the axial second side with respect to the first friction engagement element and the second friction engagement element, and are frictionally engaged with each other by being pressed in the axial direction,

The pressing mechanism includes: a pressing portion disposed between the first and second friction engagement elements and the axial directions of the third and fourth friction engagement elements; a driven part connected to the pressing part in a linked manner; and a linear motion mechanism for moving the driven part along the axial direction,

The first rotating member, the second rotating member, the first friction engagement element, the second friction engagement element, the third friction engagement element, and the fourth friction engagement element are arranged on a coaxial axis,

The clutch mechanism and the brake mechanism are selectively engaged according to the driven portion being moved to the axial first side or to the axial second side by the linear motion mechanism.

According to this feature, the pressing portion that moves in the axial direction via the driven portion by the linear motion mechanism is disposed between the first friction engagement element and the second friction engagement element, and the third friction engagement element and the fourth friction engagement element disposed on the second side in the axial direction with respect to them. Further, the driven portion is moved to the first side in the axial direction by the linear motion mechanism, whereby the first friction engagement element and the second friction engagement element are pressed by the pressing portion to bring the clutch mechanism into the engaged state, and the pressing portion is released from the pressing of the third friction engagement element and the fourth friction engagement element to bring the brake mechanism into the disengaged state. On the other hand, the driven portion is moved to the second side in the axial direction by the linear motion mechanism, whereby the third friction engagement element and the fourth friction engagement element are pressed by the pressing portion to bring the brake mechanism into the engaged state, and the pressing portion releases the pressing of the first friction engagement element and the second friction engagement element to bring the clutch mechanism into the disengaged state. Thereby, the state of engagement of the clutch mechanism and the brake mechanism can be changed by the common pressing mechanism. Therefore, in the structure having the clutch mechanism and the brake mechanism, the engagement device can be miniaturized.

Drawings

Fig. 1 is a cross-sectional view of the engagement device of the first embodiment taken along the axial direction.

Fig. 2 is a partial enlarged view of a cross-sectional view of the engagement device of the first embodiment taken along the axial direction.

Fig. 3 is a sectional view of the engagement device of the second embodiment taken along the axial direction.

Fig. 4 is a partial enlarged view of a cross-sectional view of the engagement device of the second embodiment taken along the axial direction.

Fig. 5 is a cross-sectional view of the vehicle drive device according to the first embodiment taken along the axial direction.

Fig. 6 is a schematic view of the vehicle drive device according to the first embodiment.

Fig. 7 is a speed diagram of the planetary gear mechanism of the vehicle drive device of the first embodiment.

Fig. 8 is a cross-sectional view of the vehicle drive device of the second embodiment taken along the axial direction.

Fig. 9 is a schematic view of a vehicle drive device according to a second embodiment.

Fig. 10 is a cross-sectional view of the vehicular drive apparatus of the third embodiment taken along the axial direction.

Fig. 11 is a schematic view of a vehicle drive device according to a third embodiment.

Fig. 12 is a partial enlarged view of a cross-sectional view of the vehicle drive device according to the third embodiment taken along the axial direction.

Detailed Description

1. The engagement device of the first embodiment

The joining device 100 according to the first embodiment is described below with reference to the drawings. As shown in fig. 1, the joining apparatus 100 includes: a clutch mechanism 1 that selectively engages a first rotary member 81 and a second rotary member 82; a brake mechanism 2 that selectively engages a target rotating member 8T, which is either one of the first rotating member 81 and the second rotating member 82, with a non-rotating member NR; and a pressing mechanism 3 for changing the state of engagement of the clutch mechanism 1 and the brake mechanism 2.

The first rotating member 81 and the second rotating member 82 are supported so as to be rotatable relative to each other freely. In the following description, a direction along the rotation axis of the first rotation member 81 is referred to as "axial direction L". One side in the axial direction L is referred to as "axial first side L1", and the other side is referred to as "axial second side L2". The direction orthogonal to the rotation axes of the rotation members such as the first rotation member 81 is defined as "radial direction R" with respect to each rotation axis. It is noted that the radial direction R may be simply referred to as "radial direction R" unless it is necessary to distinguish which rotation axis is the reference or which rotation axis is the reference.

In the present embodiment, the non-rotating member NR is a case 9 housing the joining apparatus 100. In the present embodiment, the case 9 includes: a first peripheral wall portion 91, a first side wall portion 92, a support wall portion 93, and a cover portion 94.

The first peripheral wall portion 91 is formed to cover the outer sides of the first rotary member 81 and the second rotary member 82 in the radial direction R. The first side wall portion 92 is formed to cover the first axial side L1 of the first rotary member 81 and the second rotary member 82. The support wall portion 93 is formed to cover the axial second sides L2 of the first rotary member 81 and the second rotary member 82. The cover portion 94 is formed to cover the axial second side L2 of the support wall portion 93.

In the present embodiment, the first peripheral wall portion 91 is formed in a tubular shape having an axial center along the axial direction L. The opening of the first peripheral wall portion 91 on the first side L1 in the axial direction is closed by the first side wall portion 92. In addition, the opening of the axial second side L2 of the first peripheral wall portion 91 is blocked by the support wall portion 93. In this example, the first peripheral wall portion 91 and the first side wall portion 92 are integrally formed to constitute the first case portion 9A. The second case portion 9B having the support wall portion 93 is fitted into the first case portion 9A from the axial first side L1 so that the support wall portion 93 is positioned inside the first peripheral wall portion 91 in the radial direction R. In addition, the third case portion 9C having the cover portion 94 is joined to the second case portion 9B from the axial first side L1.

The clutch mechanism 1 includes: the first frictional engagement element 11 is connected to the first rotating member 81 so as to integrally rotate therewith; and the second friction engagement element 12 is connected to the second rotation member 82 so as to integrally rotate therewith.

The first friction engagement element 11 and the second friction engagement element 12 are arranged to oppose each other in the axial direction L. Further, the first friction engagement element 11 and the second friction engagement element 12 are friction-engaged with each other by being pressed in the axial direction L. In the present embodiment, the first friction engagement element 11 and the second friction engagement element 12 are each provided in plural numbers, and are alternately arranged along the axial direction L. One of the first friction engagement element 11 and the second friction engagement element 12 may be used as a friction plate, and the other may be used as a separator plate.

The brake mechanism 2 has: the third friction engagement element 21 is connected to the target rotation member 8T so as to rotate integrally therewith; and a fourth friction engagement element 22 fixed to the non-rotating member NR. In the present embodiment, the first rotating member 81 is the target rotating member 8T.

The third friction engagement element 21 and the fourth friction engagement element 22 are arranged to oppose each other in the axial direction L. Further, the third friction engagement element 21 and the fourth friction engagement element 22 are friction-engaged with each other by being pressed in the axial direction L. The third friction engagement element 21 and the fourth friction engagement element 22 are disposed so as to be separated from the first friction engagement element 11 and the second friction engagement element 12 in the axial direction on the second side L2. In the present embodiment, the third friction engagement element 21 and the fourth friction engagement element 22 are each provided in plural numbers, and are alternately arranged along the axial direction L. One of the third friction engagement element 21 and the fourth friction engagement element 22 may be used as a friction plate, and the other may be used as a separator plate.

The first rotary member 81, the second rotary member 82, the first frictional engagement element 11, the second frictional engagement element 12, the third frictional engagement element 21, and the fourth frictional engagement element 22 are arranged on the first axis X1. That is, the first rotary member 81, the second rotary member 82, the first frictional engagement element 11, the second frictional engagement element 12, the third frictional engagement element 21, and the fourth frictional engagement element 22 are arranged coaxially.

As shown in fig. 2, in the present embodiment, the first rotating member 81 has a first connecting portion 8a connected to the first frictional engagement element 11. The second rotating member 82 has a second connecting portion 8b connected to the second friction engagement element 12. Further, the target rotation member 8T has a third connection portion 8c connected to the third friction engagement element 21. That is, in the present embodiment, the first rotating member 81 has the third connecting portion 8c. In addition, the non-rotating member NR has a fourth connection portion 8d connected to the fourth frictional engagement element 22.

The first connecting portion 8a is disposed on the outer side of the first friction engagement element 11 in the radial direction R and overlaps the first friction engagement element 11 when viewed in the radial direction R. That is, the first friction engagement element 11 is supported by the first connecting portion 8a from the outside in the radial direction R. The first friction engagement element 11 is supported slidably in the axial direction L while being restricted from relative rotation with respect to the first connection portion 8 a. In this example, a plurality of spline grooves extending in the axial direction L are formed in the circumferential direction at the outer peripheral portion of the first friction engagement element 11. On the other hand, similar spline grooves are also formed in the inner peripheral portion of the first connecting portion 8a so as to be circumferentially dispersed. And, these spline grooves are engaged with each other. Here, the term "overlapping when viewed in a specific direction" means that when a virtual straight line parallel to the line of sight is moved in each direction orthogonal to the virtual straight line, a region where the virtual straight line intersects both the two elements is at least partially present.

The second connection portion 8b is disposed on the inner side of the second friction engagement element 12 in the radial direction R and overlaps the second friction engagement element 12 and the first connection portion 8a when viewed in the radial direction R. That is, the second friction engagement element 12 is supported by the second connecting portion 8b from the inside in the radial direction R. The second friction engagement element 12 is supported slidably in the axial direction L in a state where relative rotation to the second connection portion 8b is restricted. In this example, a plurality of spline grooves extending in the axial direction L are formed in the inner peripheral portion of the second friction engagement element 12 so as to be circumferentially dispersed. On the other hand, the same spline grooves are also formed in the outer peripheral portion of the second connecting portion 8b so as to be circumferentially dispersed. And, these spline grooves are engaged with each other.

The third connecting portion 8c is disposed outside the third friction engagement element 21 in the radial direction R and overlaps the third friction engagement element 21 when viewed in the radial direction R. That is, the third friction engagement element 21 is supported by the third connecting portion 8c from the outside in the radial direction R. The third friction engagement element 21 is supported slidably in the axial direction L while being restricted from relative rotation with respect to the third connecting portion 8 c. In this example, a plurality of spline grooves extending in the axial direction L are formed in the outer peripheral portion of the third friction engagement element 21 so as to be circumferentially dispersed. On the other hand, similar spline grooves are also formed in the inner peripheral portion of the third connecting portion 8c so as to be circumferentially dispersed. And, these spline grooves are engaged with each other.

The fourth connecting portion 8d is disposed on the inner side of the fourth friction engagement element 22 in the radial direction R and overlaps the fourth friction engagement element 22 and the third connecting portion 8c when viewed in the radial direction R. That is, the fourth friction engagement element 22 is supported by the fourth connecting portion 8d from the inside in the radial direction R. The fourth friction engagement element 22 is supported slidably in the axial direction L while being restricted from relative rotation with respect to the fourth connecting portion 8 d. In this example, a plurality of spline grooves extending in the axial direction L are formed in the inner peripheral portion of the fourth friction engagement element 22 so as to be circumferentially dispersed. On the other hand, similar spline grooves are formed in the outer peripheral portion of the fourth connecting portion 8d so as to be circumferentially dispersed. And, these spline grooves are engaged with each other.

As shown in fig. 2, in the present embodiment, the first rotating member 81 has: the first outer bearing 811 and the first radial extension 812.

The first outer support portion 811 is formed in a tubular shape with the first axis X1 as an axis. In the present embodiment, the first connecting portion 8a and the third connecting portion 8c are disposed on the first outer support portion 811.

The first radial extension 812 is formed to extend along a radial direction R with reference to the first axis X1. In the present embodiment, the first radial extending portion 812 is formed to extend inward in the radial direction R from an end portion of the first axial side L1 in the first outer side supporting portion 811. In the present embodiment, the first radially extending portion 812 is rotatably supported with respect to the first side wall portion 92 of the case 9 via the first bearing B1. In this example, the first bearing B1 is a thrust bearing disposed between the first radially extending portion 812 and the axial direction L of the first side wall portion 92.

In the present embodiment, the second rotating member 82 has a first inner support 821. The first inner support portion 821 is disposed inside the first outer support portion 811 in the radial direction R. In the present embodiment, the second connecting portion 8b is disposed on the first inner support portion 821.

In the present embodiment, the support wall portion 93 of the case 9 has a second inner support portion 931. The second inner support portion 931 is disposed inward in the radial direction R relative to the first outer support portion 811. In the present embodiment, the second inner support portion 931 is formed in a tubular shape with the first axis X1 as an axis. In the present embodiment, the fourth connecting portion 8d is disposed on the second inner support portion 931.

The pressing mechanism 3 includes: a pressing portion 31 disposed between the first and second friction engagement elements 11 and 12 and the third and fourth friction engagement elements 21 and 22 in the axial direction L; a driven part 32 connected to the pressing part 31 in a interlocking manner; and a linear motion mechanism 33 for moving the driven portion 32 in the axial direction L.

By moving the driven portion 32 to the first axial side L1 by the linear motion mechanism 33, the first friction engagement element 11 and the second friction engagement element 12 are pressed by the pressing portion 31 to bring the clutch mechanism 1 into the engaged state, and the pressing of the third friction engagement element 21 and the fourth friction engagement element 22 by the pressing portion 31 is released to bring the brake mechanism 2 into the disengaged state. On the other hand, by moving the driven portion 32 to the axial second side L2 by the linear motion mechanism 33, the third friction engagement element 21 and the fourth friction engagement element 22 are pressed by the pressing portion 31 to bring the brake mechanism 2 into the engaged state, and the pressing of the first friction engagement element 11 and the second friction engagement element 12 by the pressing portion 31 is released to bring the clutch mechanism 1 into the disengaged state. In this way, the clutch mechanism 1 and the brake mechanism 2 are selectively engaged according to the driven portion 32 being moved to the first axial side L1 or to the second axial side L2 by the linear motion mechanism 33.

As described above, the joining apparatus 100 includes:

A clutch mechanism 1 that selectively engages a first rotary member 81 and a second rotary member 82; and

A brake mechanism 2 that selectively engages a target rotating member 8T, which is either one of the first rotating member 81 and the second rotating member 82, and a non-rotating member NR,

The engagement device 100 has a pressing mechanism 3 for changing the state of engagement of the clutch mechanism 1 and the brake mechanism 2,

The clutch mechanism 1 includes: the first frictional engagement element 11 is connected to the first rotating member 81 so as to integrally rotate therewith; and a second frictional engagement element 12 connected to the second rotating member 82 in such a manner as to integrally rotate therewith,

The first friction engagement element 11 and the second friction engagement element 12 are arranged to oppose each other in the axial direction L, and are frictionally engaged with each other by being pressed in the axial direction L,

The brake mechanism 2 has: the third friction engagement element 21 is connected to the target rotation member 8T so as to rotate integrally therewith; and a fourth frictional engagement element 22 fixed to the non-rotating member NR,

The third friction engagement element 21 and the fourth friction engagement element 22 are disposed at positions apart from the first friction engagement element 11 and the second friction engagement element 12 toward the second axial side L2 so as to face each other in the axial direction L, and are friction-engaged with each other by being pressed in the axial direction L,

The pressing mechanism 3 includes: a pressing portion 31 disposed between the first and second friction engagement elements 11 and 12 and the third and fourth friction engagement elements 21 and 22 in the axial direction L; a driven part 32 connected to the pressing part 31 in a interlocking manner; and a linear motion mechanism 33 for moving the driven portion 32 in the axial direction L,

The first rotary member 81, the second rotary member 82, the first frictional engagement element 11, the second frictional engagement element 12, the third frictional engagement element 21, and the fourth frictional engagement element 22 are arranged on the same axis,

The clutch mechanism 1 and the brake mechanism 2 are selectively engaged according to the driven portion 32 being moved to the axial first side L1 or to the axial second side L2 by the linear motion mechanism 33.

According to this configuration, the pressing portion 31 that moves in the axial direction L via the driven portion 32 by the linear motion mechanism 33 is disposed between the first friction engagement element 11 and the second friction engagement element 12, and the third friction engagement element 21 and the fourth friction engagement element 22 that are disposed on the second side L2 in the axial direction with respect to the first friction engagement element 11 and the second friction engagement element 12. Then, by moving the driven portion 32 to the first axial side L1 by the linear motion mechanism 33, the first friction engagement element 11 and the second friction engagement element 12 are pressed by the pressing portion 31 to bring the clutch mechanism 1 into the engaged state, and the pressing of the third friction engagement element 21 and the fourth friction engagement element 22 by the pressing portion 31 is released to bring the brake mechanism 2 into the disengaged state. On the other hand, by moving the driven portion 32 to the axial second side L2 by the linear motion mechanism 33, the third friction engagement element 21 and the fourth friction engagement element 22 are pressed by the pressing portion 31 to bring the brake mechanism 2 into the engaged state, and the pressing of the first friction engagement element 11 and the second friction engagement element 12 by the pressing portion 31 is released to bring the clutch mechanism 1 into the disengaged state. Thereby, the state of engagement of the clutch mechanism 1 and the brake mechanism 2 can be changed by the common pressing mechanism 3. Therefore, in the configuration having the clutch mechanism 1 and the brake mechanism 2, the reduction in size of the engagement device 100 can be achieved.

In the present embodiment, the linear motion mechanism 33 includes a screw shaft 331 rotatably supported with respect to the non-rotating member NR, and a nut member 332 screwed with the screw shaft 331.

Screw threads are formed on the outer periphery of the screw shaft 331. The screw shaft 331 is formed to extend in the axial direction L. In the present embodiment, the screw shaft 331 is disposed on the first axis X1.

A groove that engages with the thread of the screw shaft 331 is formed in the inner peripheral portion of the nut member 332. By rotating the screw shaft 331, the nut member 332 moves linearly in the axial direction L according to the rotation direction and the direction of the thread of the screw shaft 331. In the present embodiment, the nut member 332 is connected to move integrally with the driven portion 32 in the axial direction L. Accordingly, in the present embodiment, the pressing portion 31 moves in the axial direction L via the nut member 332 and the driven portion 32 with rotation of the screw shaft 331.

In the present embodiment, the nut member 332 is supported so as to be movable relative to the non-rotating member NR in the axial direction L, and so as to be restrained from rotating relative to the non-rotating member NR. In this example, the nut member 332 is disposed inside in the radial direction R with respect to the second inside support portion 931 of the support wall portion 93 in the case 9. The nut member 332 is connected to the second inner support portion 931 by a connecting member 33a disposed between the outer peripheral portion of the nut member 332 and the radial direction R of the inner peripheral portion of the second inner support portion 931, in a state where the nut member can move relative to the case 9 in the axial direction L and relative rotation relative to the case 9 is restricted.

In the present embodiment, the linear motion mechanism 33 is disposed on the second axial side L2 with respect to the second connecting portion 8 b. The linear motion mechanism 33 is disposed inside the fourth connecting portion 8d in the radial direction R and overlaps the fourth connecting portion 8d when viewed in the radial direction R. In this example, the screw shaft 331 and the nut member 332 of the linear motion mechanism 33 are disposed on the second side L2 in the axial direction than the first inner support portion 821 of the second rotating member 82. The screw shaft 331 and the nut member 332 are disposed further inward in the radial direction R than the second inner support portion 931 of the support wall portion 93 in the case 9.

In this way, in the present embodiment, the first rotating member 81 has the first connecting portion 8a connected to the first frictional engagement element 11,

The second rotating member 82 has a second connecting portion 8b connected with the second frictional engagement element 12,

The target rotation member 8T has a third connection portion 8c connected to the third frictional engagement element 21,

The non-rotating member NR has a fourth connection portion 8d with a fourth frictional engagement element 22,

The first connecting portion 8a is disposed outside the first friction engagement element 11 in the radial direction R, and overlaps the first friction engagement element 11 when viewed in the radial direction R,

The third connecting portion 8c is disposed outside the third friction engagement element 21 in the radial direction R, and overlaps the third friction engagement element 21 when viewed in the radial direction R,

The second connecting portion 8b is disposed on the inner side of the second friction engagement element 12 in the radial direction R, and overlaps the second friction engagement element 12 and the first connecting portion 8a when viewed in the radial direction R,

The fourth connecting portion 8d is disposed on the inner side of the fourth frictional engagement element 22 in the radial direction R, and overlaps the fourth frictional engagement element 22 and the third connecting portion 8c when viewed in the radial direction R,

The linear motion mechanism 33 is disposed on the second axial side L2 with respect to the second connecting portion 8b, and is disposed on the inner side of the fourth connecting portion 8d in the radial direction R and at a position overlapping the fourth connecting portion 8d when viewed in the radial direction of the radial direction R.

According to this structure, the linear motion mechanism 33 is disposed on the second axial side L2 with respect to the second connecting portion 8b of the second rotating member 82. As a result, the dimension of the joint device 100 in the radial direction R can be suppressed to be smaller than a structure in which the linear motion mechanism 33 is arranged so as to overlap the second connecting portion 8b when viewed in the radial direction.

Further, according to the present configuration, the linear motion mechanism 33 is disposed on the inner side of the fourth connecting portion 8d of the non-rotating member NR in the radial direction R and overlaps the fourth connecting portion 8d when viewed in the radial direction R. As a result, the dimension in the axial direction L of the joint device 100 can be reduced as compared with a configuration in which the linear motion mechanism 33 is arranged so as to be offset in the axial direction L with respect to the fourth connecting portion 8 d. Further, since the linear motion mechanism 33 disposed inside the fourth connecting portion 8d with respect to the non-rotating member NR is easily supported by the non-rotating member NR, the support structure of the linear motion mechanism 33 is easily simplified.

In the present embodiment, the pressing portion 31 includes: the first pressing portion 311 and the second pressing portion 312.

The first pressing portion 311 is configured to press the first friction engagement element 11 and the second friction engagement element 12 in the axial direction L. The second pressing portion 312 is configured to press the third friction engagement element 21 and the fourth friction engagement element 22 in the axial direction L. In the present embodiment, the first pressing portion 311 and the second pressing portion 312 are constituted by different independent members arranged so as to face each other in the axial direction L. Further, the first pressing portion 311 and the second pressing portion 312 are supported via a fourth bearing B4 so as to be rotatable relative to each other. Therefore, in the present embodiment, the first pressing portion 311 and the second pressing portion 312 are configured to interlock in the axial direction L in a relatively rotatable state. In this example, the fourth bearing B4 is a thrust bearing disposed between the first pressing portion 311 and the second pressing portion 312 in the axial direction L.

The first pressing portion 311 is supported in a state of being relatively movable in the axial direction L with respect to the first rotation member 81 or the second rotation member 82 and integrally rotatable with respect to the first rotation member 81 or the second rotation member 82. In the present embodiment, the first pressing portion 311 is supported in a state of being movable relative to the first outer support portion 811 of the first rotating member 81 in the axial direction L and integrally rotating relative to the first outer support portion 811 of the first rotating member 81. In this example, the end portion on the outer side in the radial direction R of the first pressing portion 311 is connected to the first connection portion 8 a.

The second pressing portion 312 is supported in a state of being relatively movable in the axial direction L with respect to the non-rotating member NR and being restricted in relative rotation with respect to the non-rotating member NR. In the present embodiment, the second pressing portion 312 is connected to the driven portion 32 so as to move integrally therewith in the axial direction L. In this example, the driven portion 32 is formed to extend inward in the radial direction R from the second pressing portion 312. As described above, in the present embodiment, the nut member 332 is supported in a state of being movable relative to the non-rotating member NR in the axial direction L and being restricted from rotating relative to the non-rotating member NR. Therefore, in the present embodiment, the second pressing portion 312 is supported via the driven portion 32 and the nut member 332 so as to be movable relative to the non-rotating member NR in the axial direction L and so as to be restricted from rotating relative to the non-rotating member NR.

As described above, in the present embodiment, the pressing portion 31 includes: a first pressing portion 311 that presses the first friction engagement element 11 and the second friction engagement element 12 in the axial direction L; and a second pressing portion 312 that presses the third friction engagement element 21 and the fourth friction engagement element 22 in the axial direction L,

The first pressing portion 311 is supported in a state of being relatively movable in the axial direction L with respect to the first rotation member 81 or the second rotation member 82 and integrally rotated with the first rotation member 81 or the second rotation member 82,

The second pressing portion 312 is supported in a state of being relatively movable in the axial direction L with respect to the non-rotating member NR and being restricted in relative rotation with respect to the non-rotating member NR,

The first pressing portion 311 and the second pressing portion 312 are constituted to interlock in the axial direction L in a relatively rotatable state,

The driven portion 32 is connected to the second pressing portion 312 so as to move integrally therewith in the axial direction L.

According to this structure, the driven portion 32 that moves in the axial direction L by the linear motion mechanism 33 is connected to the second pressing portion 312 that is supported in a state in which relative rotation with respect to the non-rotating member NR is restricted so as to be integrally movable in the axial direction L. Thus, the pressing mechanism 3 is simplified more easily than a structure in which the driven portion 32 and the first pressing portion 311 supported in a state of integrally rotating with the first rotating member 81 or the second rotating member 82 are connected to be integrally movable in the axial direction L.

As described above, in the present embodiment, the screw shaft 331 is disposed on the first axis X1. That is, in the present embodiment, the screw shaft 331 is coaxially arranged with the first friction engagement element 11, the second friction engagement element 12, the third friction engagement element 21, and the fourth friction engagement element 22. In the present embodiment, the screw shaft 331 is disposed inside the first friction engagement element 11, the second friction engagement element 12, the third friction engagement element 21, and the fourth friction engagement element 22 in the radial direction R.

In this way, in the present embodiment, the linear motion mechanism 33 includes the screw shaft 331 rotatably supported with respect to the non-rotating member NR and the nut member 332 screwed with the screw shaft 331,

The nut member 332 is connected to the driven portion 32 so as to move integrally therewith in the axial direction L,

The screw shaft 331 is disposed coaxially with respect to the first friction engagement element 11, the second friction engagement element 12, the third friction engagement element 21, and the fourth friction engagement element 22, and is disposed inside in the radial direction R.

According to this configuration, the screw shaft 331 for moving the nut member 332 in the axial direction L is disposed on the inner side in the radial direction R with respect to the first friction engagement element 11, the second friction engagement element 12, the third friction engagement element 21, and the fourth friction engagement element 22. This facilitates transmission of a driving force for driving the screw shaft 331 to rotate from the outside in the axial direction L with respect to the friction engagement elements 11, 12, 21, 22 to the screw shaft 331. Therefore, it is easy to realize a structure in which the pressing portion 31 disposed between the first and second friction engagement elements 11 and 12 and the axial directions L of the third and fourth friction engagement elements 21 and 22 can be moved in the axial directions L via the nut member 332 and the driven portion 32.

In addition, according to the present structure, it is easy to dispose the screw shaft 331 of the linear motion mechanism 33 so as to overlap at least a part of the first friction engagement element 11, the second friction engagement element 12, the third friction engagement element 21, and the fourth friction engagement element 22 when viewed in the radial direction of the radial direction R. This can suppress an increase in the size of the joint device 100 in the axial direction L due to the arrangement of the linear motion mechanism 33.

As shown in fig. 1, in the present embodiment, the joint device 100 further includes a drive source 4 for driving the screw shaft 331 to rotate, and a transmission mechanism 5 for transmitting power between the drive source 4 and the screw shaft 331.

In the present embodiment, the drive source 4 is disposed on a second axis X2 different from the first axis X1. That is, in the present embodiment, the drive source 4 is disposed on a shaft different from the screw shaft 331. The arrangement region in the axial direction L of the drive source 4 overlaps with the arrangement region in the axial direction L of the first rotary member 81. In the present embodiment, the transmission mechanism 5 is disposed on the second axial side L2 with respect to the linear motion mechanism 33.

As shown in fig. 2, in the present embodiment, the first rotating member 81 is connected to the first shaft member 10 so as to rotate integrally therewith. The first shaft member 10 is configured to extend from the first rotation member 81 toward the axial first side L1. In the present embodiment, the first shaft member 10 is formed in a tubular shape with the first axis X1 as the axis. The first shaft member 10 is formed to extend from an inner end portion in the radial direction R in the first outer support portion 811 of the first rotary member 81 to the first axial side L1. In this example, the first shaft member 10 is integrally formed with the first rotary member 81. In the present embodiment, the first shaft member 10 is disposed so as to pass through the first side wall 92 of the case 9 in the axial direction L. The first shaft member 10 is rotatably supported with respect to the first side wall 92 via the second bearing B2. In this example, the second bearing B2 is a radial (radial) bearing disposed between the first shaft member 10 and the radial direction R of the first side wall portion 92.

In the present embodiment, the second rotation member 82 is connected to the second shaft member 20 so as to rotate integrally therewith. The second shaft member 20 is configured to extend from the second rotation member 82 toward the axial first side L1. In the present embodiment, the second shaft member 20 is formed to extend from the first inner support portion 821 of the second rotating member 82 toward the axial first side L1. The second shaft member 20 is disposed on the first axis X1. In this example, the second shaft member 20 is integrally formed with the second rotating member 82. In the present embodiment, the second shaft member 20 is disposed so as to pass through the inner side of the first shaft member 10 in the radial direction R. The second shaft member 20 is supported rotatably relative to the first shaft member 10 via a third bearing B3. In this example, the third bearing B3 is a radial bearing disposed between the first shaft member 10 and the second shaft member 20 in the radial direction R.

The engagement device 100 is provided in, for example, a vehicle drive device that transmits driving force of a driving force source such as an internal combustion engine to wheels. In this case, one of the first shaft member 10 and the second shaft member 20 is drivingly connected to a driving force source of an internal combustion engine or the like. The other of the first shaft member 10 and the second shaft member 20 is connected to the wheel drive.

In this way, in the present embodiment, there are further provided a driving source 4 for driving the screw shaft 331 to rotate and a transmission mechanism 5 for transmitting power between the driving source 4 and the screw shaft 331,

The drive source 4 is arranged on a shaft different from the screw shaft,

The arrangement region in the axial direction L of the drive source 4 overlaps with the arrangement region in the axial direction L of the first rotary member 81,

The transmission mechanism 5 is arranged on the second axial side L2 with respect to the linear motion mechanism 33,

The first shaft member 10 disposed so as to extend from the first rotating member 81 toward the first axial side L1 is connected to the first rotating member 81 so as to rotate integrally therewith,

The second shaft member 20 disposed so as to extend from the second rotation member 82 toward the first axial side L1 is connected to the second rotation member 82 so as to rotate integrally therewith.

According to this configuration, the dimension in the axial direction L of the joint device 100 can be suppressed to be smaller than a configuration in which the drive source 4 is disposed coaxially with the first rotary member 81 and is disposed at a position offset in the axial direction L.

As shown in fig. 1, in the present embodiment, the transmission mechanism 5 includes: a first gear 51, a second gear 52, a third gear 53, a fourth gear 54, and a connecting body 55.

The first gear 51 is connected to the output shaft of the drive source 4 so as to rotate integrally therewith. In the present embodiment, the first gear 51 is disposed on the second shaft X2. The first gear 51 is disposed on the second axial side L2 with respect to the drive source 4.

The second gear 52 is meshed with the first gear 51. In the present embodiment, the second gear 52 is formed to have a larger diameter than the first gear 51. The third gear 53 is connected to the second gear 52 so as to rotate integrally therewith. In the present embodiment, the third gear 53 is formed to have a smaller diameter than the second gear 52. The third gear 53 is disposed on the first side L1 in the axial direction with respect to the second gear 52. In the present embodiment, the second gear 52 and the third gear 53 are disposed on a third axis X3 different from the first axis X1 and the second axis X2. In the present embodiment, the second gear 52 and the third gear 53 are rotatably supported by the first shaft 56 with respect to the non-rotating member NR. The first shaft 56 is formed to extend along the axial direction L. In the present embodiment, an end portion of the first shaft 56 on the first side L1 in the axial direction is rotatably supported with respect to the support wall 93. The end of the first shaft 56 on the second side L2 in the axial direction is rotatably supported with respect to the cover 94.

The fourth gear 54 is meshed with the third gear 53. In the present embodiment, the fourth gear 54 is formed to have a larger diameter than the third gear 53. In the present embodiment, the fourth gear 54 is disposed on the first axis X1. In the present embodiment, the fourth gear 54 is rotatably supported by the second shaft body 57 with respect to the non-rotating member NR. The second shaft body 57 is formed to extend along the axial direction L. In the present embodiment, an end portion of the second axial side L2 of the second shaft body 57 is rotatably supported with respect to the cover 94. On the other hand, an end portion of the second shaft body 57 on the first side L1 in the axial direction is connected to the connecting body 55 so as to rotate integrally therewith.

In the present embodiment, the number of teeth of the second gear 52 is larger than that of the first gear 51. The fourth gear 54 has a larger gear ratio than the third gear 53 which rotates integrally with the second gear 52. Therefore, in the present embodiment, the rotation transmitted from the drive source 4 to the first gear 51 is decelerated between the first gear 51 and the second gear 52, and transmitted to the third gear 53. The rotation of the third gear 53 is decelerated between the third gear 53 and the fourth gear 54, and transmitted to the connection body 55.

The connecting body 55 connects the fourth gear 54 and the screw shaft 331 and rotates them integrally. In the present embodiment, the connection body 55 is formed in a cylindrical shape that is open at the second side L2 in the axial direction. In a state where the second shaft body 57 is disposed inside the connection body 55 in the radial direction R, the connection body 55 and the second shaft body 57 are connected to integrally rotate. In the present embodiment, the connection body 55 and the screw shaft 331 are integrally rotatably connected in a state where the screw shaft 331 is arranged to extend from the connection body 55 to the first axial side L1. In the present embodiment, the connection body 55, the second shaft body 57, and the screw shaft 331 are disposed so as to penetrate the support wall 93 in the axial direction L.

As shown in fig. 2, in the present embodiment, the connection body 55 is disposed inside in the radial direction R with respect to the second inner support portion 931 formed in a cylindrical shape of the support wall portion 93. In the present embodiment, the connection body 55 is provided with a supported portion 551 formed so as to protrude outward in the radial direction R from the connection body 55. The second inner support portion 931 is provided with a bearing support portion 932, and the bearing support portion 932 is formed so as to protrude inward in the radial direction R from the second inner support portion 931 and face the supported portion 551 from the axial first side L1. The supported portion 551 is rotatably supported with respect to the bearing support portion 932 via the fifth bearing B5. Thus, the link body 55 is supported rotatably with respect to the non-rotating member NR while being restricted from moving to the first axial side L1 with respect to the non-rotating member NR. In this example, the fifth bearing B5 is a thrust bearing disposed between the supported portion 551 and the axial direction L of the bearing support portion 932.

In the present embodiment, the annular cover portion 933 is fixed to the support wall portion 93 so as to face the supported portion 551 from the axial second side L2. The supported portion 551 is rotatably supported with respect to the cover portion 933 via a sixth bearing B6. Thus, the link body 55 is supported rotatably with respect to the non-rotating member NR while being restricted from moving relative to the non-rotating member NR toward the second axial side L2. In this example, the sixth bearing B6 is a thrust bearing disposed between the supported portion 551 and the axial direction L of the cover portion 933.

In the present embodiment, a pressure sensor (not shown) is provided, and the pressure sensor detects the pressing force of the pressing portion 31 against the first friction engagement element 11 and the second friction engagement element 12 and the pressing force of the pressing portion 31 against the third friction engagement element 21 and the fourth friction engagement element 22. The pressure sensor is disposed, for example, between the supported portion 551 and the axial direction L of the bearing support portion 932, or between the supported portion 551 and the axial direction L of the cover portion 933. Accordingly, the force received by the pressing portion 31 from the first friction engagement element 11, the second friction engagement element 12, the third friction engagement element 21, and the fourth friction engagement element 22 and transmitted to the connection body 55 via the driven portion 32, the nut member 332, and the screw shaft 331 can be measured by the pressure sensor. Based on the measured force, the pressing force of the pressing portion 31 against the first friction engagement element 11 and the second friction engagement element 12 and the pressing force of the pressing portion 31 against the third friction engagement element 21 and the fourth friction engagement element 22 can be calculated.

2. The engagement device of the second embodiment

The joining device 100 according to the second embodiment will be described below with reference to fig. 3 and 4. The present embodiment is different from the first embodiment described above in that the second rotating member 82 is the object rotating member 8T. The following description will focus on differences from the first embodiment. Note that the points not specifically described are the same as those in the first embodiment.

As shown in fig. 3 and 4, in the present embodiment, the second rotating member 82 is the target rotating member 8T. Therefore, in the present embodiment, the second rotating member 82 has the third connecting portion 8c connected to the third frictional engagement element 21.

As shown in fig. 4, in the present embodiment, the second rotating member 82 has a second outer support portion 822 and a second radially extending portion 823 in addition to the first inner support portion 821.

The second outer support 822 is formed in a tubular shape with the first axis X1 as an axis. In the present embodiment, the third connecting portion 8c is disposed on the second outer support portion 822. On the other hand, in the present embodiment, the third connection portion 8c is not disposed on the first outer side support portion 811 of the first rotating member 81, but the first connection portion 8a is disposed. The dimension of the first outer support portion 811 in the axial direction L in the present embodiment is smaller than the dimension of the first outer support portion 811 in the axial direction L in the first embodiment. The first outer support 811 is disposed on the first side L1 in the axial direction with respect to the second outer support 822.

The second radial extension 823 is formed to extend along the radial direction R with reference to the first axis X1. In the present embodiment, the second radially extending portion 823 is formed to extend inward in the radial direction R from the end portion of the axial first side L1 in the second outer support portion 822. The second radially extending portion 823 is supported so as to be movable relative to the first inner support portion 821 in the axial direction L and integrally rotatable with the first inner support portion 821. In this example, an end portion of the second radially extending portion 823 on the inner side in the radial direction R is connected to the second connecting portion 8 b. In addition, in the present embodiment, the second radial extension 823 is connected to the first pressing portion 311 so as to integrally rotate therewith. In this example, the second radial extension 823 is integrally formed with the first pressing portion 311.

3. Vehicle drive device according to first embodiment

A vehicle driving device 1000 according to a first embodiment having the engagement device 100 according to the first embodiment will be described below with reference to fig. 5 to 9. As shown in fig. 5 and 6, the vehicle drive device 1000 includes: a rotating electrical Machine (MG) having a Stator (ST) and a Rotor (RT); an input shaft IS integrally rotated with the rotor RT; an output gear OG drivingly connected to a wheel W (see fig. 6); a drive gear DG rotatably connected to the output gear OG in a linked manner; and a transmission TM having the planetary gear mechanism PL and the engagement device 100 described above. In the present embodiment, the vehicle drive device 1000 further includes: a pair of output members OM integrally rotated with the mutually different wheels W, respectively; and a differential gear mechanism DF that distributes rotation of the output gear OG to a pair of output members OM.

The drive gear DG, the planetary gear mechanism PL, and the coupling device 100 are disposed on a first axis X1 that is the rotation axis of the rotor RT. That is, the rotor RT, the planetary gear mechanism PL, the engagement device 100, and the drive gear DG are coaxially arranged. In the present embodiment, the output gear OG, the pair of output members OM, and the differential gear mechanism DF are arranged on a fourth axis X4 different from the first axis X1. In this example, the first axis X1 and the fourth axis X4 are arranged parallel to each other.

In the present embodiment, the side on which the rotating electrical machine MG IS disposed with respect to the input shaft IS referred to as an axial 1 st side L1 and the opposite side IS referred to as an axial second side L2 in the axial direction L.

The rotating electrical machine MG functions as a driving force source for the wheels W (see fig. 6). The rotating electrical machine MG has a function as a motor (electric motor) that generates power upon receiving supply of electric power, and a function as a generator (generator) that generates electric power upon receiving supply of electric power. Specifically, the rotating electrical machine MG is electrically connected to a power storage device (not shown) such as a battery or a capacitor. The rotating electrical machine MG generates driving force by traction with electric power stored in the power storage device. The rotating electrical machine MG generates electric power by using the driving force transmitted from the wheel W side, and charges the power storage device.

The stator ST of the rotating electrical machine MG is fixed to the non-rotating member NR. The rotor RT of the rotating electrical machine MG is rotatably supported with respect to the stator ST.

As shown in fig. 5, in the present embodiment, the non-rotating member NR is the casing 9. The case 9 houses the rotating electrical machine MG, the input shaft IS, the output gear OG, the drive gear DG, the transmission TM, the output member OM, and the differential gear mechanism DF. In the present embodiment, the case 9 includes the second peripheral wall portion 91a, the third peripheral wall portion 91b, the fourth peripheral wall portion 91c, the second side wall portion 92a, the third side wall portion 92b, and the fourth side wall portion 92d in addition to the first peripheral wall portion 91, the first side wall portion 92, the support wall portion 93, and the cover portion 94.

The second peripheral wall portion 91a is formed to cover the outer side in the radial direction R of the rotary electric machine MG. The third peripheral wall portion 91b is formed to cover the outer sides of the drive gear DG and the planetary gear mechanism PL in the radial direction R. The fourth peripheral wall portion 91c is formed to cover the pair of output members OM and the outer sides of the differential gear mechanism DF in the radial direction R. In the present embodiment, the first peripheral wall portion 91 is formed so as to cover the outer side in the radial direction R of the joining device 100.

The second side wall portion 92a is formed to cover the axial first side L1 of the rotary electric machine MG. The third side wall portion 92b is formed to separate the rotary electric machine MG from the output gear OG, the drive gear DG, and the differential gear mechanism DF in the axial direction L. The fourth side wall portion 92d is formed to cover the axial second side L2 of the differential gear mechanism DF. In the present embodiment, the support wall portion 93 is formed so as to cover the axial second side L2 of the joining device 100. The cover 94 is formed to cover the second axial side L2 of the support wall 93. In addition, the first side wall portion 92 is formed to separate the planetary gear mechanism PL and the engagement device 100 in the axial direction L.

In the present embodiment, the second peripheral wall portion 91a is formed in a tubular shape having an axial center along the axial direction L. Further, the opening of the second peripheral wall portion 91a on the first side L1 in the axial direction is closed by the second side wall portion 92 a. In addition, the opening of the second peripheral wall portion 91a on the second side L2 in the axial direction is closed by the third side wall portion 92 b. In this example, the second peripheral wall portion 91a and the second side wall portion 92a are formed integrally. The third side wall 92b is fitted into the opening of the first axial side L1 of the second peripheral wall 91a from the second axial side L2.

In the present embodiment, the third peripheral wall portion 91b is formed in a tubular shape having an axial center along the axial direction L. The opening of the third peripheral wall portion 91b on the second side L2 in the axial direction is closed by the first side wall portion 92. In the present embodiment, the fourth peripheral wall portion 91c is formed in a tubular shape having an axial center along the axial direction L. The opening of the fourth peripheral wall portion 91c on the second side L2 in the axial direction is closed by the fourth side wall portion 92 d. In this example, the third peripheral wall portion 91b, the fourth peripheral wall portion 91c, the first side wall portion 92, and the fourth side wall portion 92d are formed integrally. The end portions of the first side L1 in the axial direction of the third peripheral wall portion 91b and the fourth peripheral wall portion 91c and the end portion of the second side L2 in the axial direction of the second wall portion 91a are joined to each other so that the openings of the first side L1 in the axial direction of the third peripheral wall portion 91b and the fourth peripheral wall portion 91c are closed by the third side wall portion 92 b.

In the present embodiment, the first peripheral wall portion 91 is formed in a tubular shape having an axial center along the axial direction L. The opening of the first peripheral wall portion 91 on the second side L2 in the axial direction is closed by the support wall portion 93. In this example, the first peripheral wall portion 91 is formed integrally with the first side wall portion 92 such that the opening of the first side L1 in the axial direction of the first peripheral wall portion 91 is blocked by the first side wall portion 92. The support wall 93 is fitted into the opening of the second axial side L2 of the first peripheral wall 91 from the second axial side L2. A cover 94 is joined to the support wall 93 from the axial second side L2.

The planetary gear mechanism PL has: a first rotating element E1, a second rotating element E2, and a third rotating element E3. The planetary gear mechanism PL is configured such that the order of the rotational speeds of the first rotary element E1, the second rotary element E2, and the third rotary element E3 is the order described. The term "rotation speed sequence" refers to a sequence of rotation speeds in the rotation state of each rotary element. The rotational speed of each rotating element varies according to the rotational state of the planetary gear mechanism, but the order of the rotational speeds of the rotating elements is constant because the order is determined by the configuration of the planetary gear mechanism. The order of the rotational speeds of the respective rotary elements is the same as the arrangement order in the speed map (see fig. 7, etc.) of the respective rotary elements. The term "arrangement order in the velocity profile of each rotating element" refers to an order in which axes corresponding to the rotating elements in the velocity profile are arranged along a direction orthogonal to the axes. The arrangement direction of the axes corresponding to the rotary elements in the speed diagram differs according to the drawing method of the speed diagram, but the arrangement order is determined by the configuration of the planetary gear mechanism, and is therefore constant.

In the present embodiment, the planetary gear mechanism PL is a single pinion type planetary gear mechanism having a first sun gear S1, a first carrier C1, and a first ring gear R1.

The first rotary element E1 IS connected to the input shaft IS so as to rotate integrally therewith. In the present embodiment, the first rotary element E1 is the first sun gear S1.

The second rotating element E2 is connected to the drive gear DG so as to rotate integrally therewith. In the present embodiment, the second rotating element E2 is the first carrier C1. The first carrier C1 rotatably supports the first pinion gears P1 meshed with the first sun gear S1 and the first ring gear R1. The first pinion gear P1 rotates (rotates) about its axis, and rotates (revolves) with the first carrier C1 around the first sun gear S1. The first pinion P1 is provided in plural at intervals along the revolution locus thereof.

Depending on the engaged state of the engagement device 100, the third rotary element E3 is switched between a first state of being connected to the non-rotary member NR and a second state of being connected to the first rotary element E1 or the second rotary element E2 so as to integrally rotate. In the present embodiment, the third rotating element E3 is the first ring gear R1. The first ring gear R1 is a gear having internal teeth disposed on the outer side in the radial direction R with respect to the first sun gear S1 and the first carrier C1.

In the present embodiment, the joining apparatus 100 includes: a clutch mechanism 1, a brake mechanism 2, and a pressing mechanism 3.

The clutch mechanism 1 is configured to selectively engage a first rotary member 81 and a second rotary member 82 that are rotatably supported relative to each other. The clutch mechanism 1 includes: the first frictional engagement element 11 is connected to the first rotating member 81 so as to integrally rotate therewith; and the second friction engagement element 12 is connected to the second rotation member 82 so as to integrally rotate therewith.

The first friction engagement element 11 and the second friction engagement element 12 are arranged to oppose each other in the axial direction L. The first friction engagement element 11 and the second friction engagement element 12 are friction-engaged with each other by being pressed in the axial direction L. In the present embodiment, the first friction engagement element 11 and the second friction engagement element 12 are each provided in plural numbers, and are alternately arranged along the axial direction L. One of the first friction engagement element 11 and the second friction engagement element 12 may be used as a friction plate, and the other may be used as a separator plate.

The brake mechanism 2 is configured to selectively engage the first rotating member 81 and the non-rotating member NR. The brake mechanism 2 has: the third friction engagement element 21 is connected to the first rotation member 81 so as to integrally rotate therewith; and a fourth friction engagement element 22 fixed to the non-rotating member NR.

The third friction engagement element 21 and the fourth friction engagement element 22 are arranged to oppose each other in the axial direction L. The third friction engagement element 21 and the fourth friction engagement element 22 are friction-engaged with each other by being pressed in the axial direction L. The third friction engagement element 21 and the fourth friction engagement element 22 are disposed so as to be separated from the first friction engagement element 11 and the second friction engagement element 12 in the axial direction on the second side L2. In the present embodiment, the third friction engagement element 21 and the fourth friction engagement element 22 are each provided in plural numbers, and are alternately arranged along the axial direction L. One of the third friction engagement element 21 and the fourth friction engagement element 22 can be used as a friction plate, and the other can be used as a separator plate.

In the present embodiment, the first rotating member 81 has a first outer support portion 811. The first outer support portion 811 is formed in a tubular shape with the first axis X1 as an axis. The first outer support 811 supports the first frictional engagement element 11 and the third frictional engagement element 21 from the outer side in the radial direction R. In this example, a plurality of spline grooves extending in the axial direction L are formed in the outer peripheral portions of the first friction engagement element 11 and the third friction engagement element 21 so as to be circumferentially dispersed. On the other hand, similar spline grooves are also formed in the inner peripheral portion of the first outer support portion 811 so as to be circumferentially dispersed. And, these spline grooves are engaged with each other.

In the present embodiment, the second rotating member 82 has a first inner support 821. The first inner support portion 821 is disposed inside the first outer support portion 811 in the radial direction R. The first inner support 821 supports the second frictional engagement element 12 from the inner side in the radial direction R. In this example, a plurality of spline grooves extending in the axial direction L are formed in the inner peripheral portion of the second friction engagement element 12 so as to be circumferentially dispersed. On the other hand, similar spline grooves are also formed in the outer peripheral portion of the first inner support portion 821 so as to be circumferentially dispersed. And, these spline grooves are engaged with each other.

In the present embodiment, the support wall 93 of the case 9 has a second inner support 931. The second inner support portion 931 is disposed on the inner side in the radial direction R with respect to the first outer support portion 811 and on the second side L2 in the axial direction with respect to the first inner support portion 821. The second inner support 931 supports the fourth frictional engagement element 22 from the inner side in the radial direction R. In this example, a plurality of spline grooves extending in the axial direction L are formed in the inner peripheral portion of the fourth friction engagement element 22 so as to be circumferentially dispersed. On the other hand, similar spline grooves are also formed in the outer peripheral portion of the second inner support portion 931 so as to be circumferentially dispersed. And, these spline grooves are engaged with each other.

In the present embodiment, the first rotation member 81 is connected to the first shaft member 10 so as to rotate integrally therewith. The first shaft member 10 is configured to extend from the first rotation member 81 toward the axial first side L1. The first shaft member 10 is disposed so as to penetrate the first side wall 92 of the case 9 in the axial direction L. The first shaft member 10 is connected to the first side wall 92 at a position closer to the first side L1 in the axial direction so as to rotate integrally with the first ring gear R1 of the planetary gear mechanism PL. The first shaft member 10 is rotatably supported with respect to the first side wall 92 via the second bearing B2.

In the present embodiment, the second rotating member 82 is disposed inside the first rotating member 81 in the radial direction R. Further, the second rotation member 82 is connected to the second shaft member 20 so as to integrally rotate therewith. The second shaft member 20 is configured to extend from the second rotation member 82 toward the axial first side L1. The second shaft member 20 is disposed inside the first shaft member 10 in the radial direction R. The second shaft member 20 is supported rotatably relative to the first shaft member 10 via a third bearing B3. In the present embodiment, the input shaft IS corresponds to the second shaft member 20.

The pressing mechanism 3 is configured to change the state of engagement of the clutch mechanism 1 and the brake mechanism 2. In the present embodiment, the pressing mechanism 3 includes: a first pressing portion 311 that presses the first friction engagement element 11 and the second friction engagement element 12; a second pressing portion 312 that presses the third friction engagement element 21 and the fourth friction engagement element 22; a linear motion mechanism 33 that moves the first pressing portion 311 and the second pressing portion 312 in the axial direction L; and a transmission mechanism 5 for transmitting power of the drive source 4 to the linear motion mechanism 33.

In the present embodiment, the first pressing portion 311 and the second pressing portion 312 are constituted by different independent members arranged so as to face each other in the axial direction L. The first pressing portion 311 and the second pressing portion 312 are supported via a fourth bearing B4 so as to be relatively rotatable. Therefore, in the present embodiment, the first pressing portion 311 and the second pressing portion 312 are configured to interlock in the axial direction L in a relatively rotatable state. In this example, the fourth bearing B4 is a thrust bearing disposed between the first pressing portion 311 and the second pressing portion 312 in the axial direction L.

In the present embodiment, the linear motion mechanism 33 is constituted by a ball screw. In this example, the nut member 332 screwed with the screw shaft 331 of the linear motion mechanism 33 is connected to the second pressing portion 312 so as to move integrally with it in the axial direction L.

In the present embodiment, the transmission mechanism 5 is constituted by a plurality of gears. In this example, the rotation from the drive source 4 is decelerated between the gears engaged with each other, and transmitted to the linear motion mechanism 33.

The first pressing portion 311 and the second pressing portion 312 are moved to the first axial side L1 by the linear motion mechanism 33, whereby the first friction engagement element 11 and the second friction engagement element 12 are pressed by the first pressing portion 311 to bring the clutch mechanism 1 into the engaged state, and the pressing of the third friction engagement element 21 and the fourth friction engagement element 22 by the second pressing portion 312 is released to bring the brake mechanism 2 into the disengaged state. In this state, the first rotating member 81 rotates with respect to the non-rotating member NR, and the first rotating member 81 and the second rotating member 82 integrally rotate. Accordingly, the first ring gear R1 connected to the first rotating member 81, the first carrier C1 connected to the drive gear DG, and the first sun gear S1 connected to the input shaft IS and the second rotating member 82 rotate integrally. As a result, the rotation of the rotor RT is directly transmitted to the drive gear DG (see reference G2 in fig. 7).

On the other hand, by moving the first pressing portion 311 and the second pressing portion 312 to the second side L2 in the axial direction by the linear motion mechanism 33, the third friction engagement element 21 and the fourth friction engagement element 22 are pressed by the second pressing portion 312 to bring the brake mechanism 2 into the engaged state, and the pressing of the first friction engagement element 11 and the second friction engagement element 12 by the first pressing portion 311 is released to bring the clutch mechanism 1 into the disengaged state. In this state, the relative rotation of the first rotating member 81 with respect to the non-rotating member NR is restricted, and the second rotating member 82 is relatively rotated with respect to the first rotating member 81. Accordingly, the first ring gear R1 connected to the first rotating member 81, the first carrier C1 connected to the drive gear DG, and the first sun gear S1 connected to the input shaft IS and the second rotating member 82 rotate relative to each other. As a result, the rotation of the rotor RT is decelerated by the planetary gear mechanism PL and transmitted to the drive gear DG (see reference symbol G1 in fig. 7).

The drive gear DG is arranged between the rotor RT and the transmission TM in the axial direction L. In the present embodiment, on the first axis X1, the rotor RT, the drive gear DG, the planetary gear mechanism PL, and the coupling device 100 are arranged in the stated order from the axial first side L1 to the axial second side L2.

The input shaft IS formed to extend in the axial direction L. The input shaft IS disposed to penetrate the drive gear DG in the axial direction L. The input shaft IS connects the rotor RT and the first rotary element E1 (the first sun gear S1, among them) so as to rotate integrally. In the present embodiment, the input shaft IS rotatably supported with respect to the drive gear DG via the fifth bearing B5. In the present embodiment, the input shaft IS penetrates the third side wall portion 92b of the case 9 in the axial direction L. The input shaft IS supported rotatably relative to the third side wall 92B via a sixth bearing B6. In the present embodiment, the input shaft IS penetrates the planetary gear mechanism PL in the axial direction L, and IS connected to the second rotating member 82 so as to rotate integrally therewith. The input shaft IS supported rotatably relative to the first carrier C1 of the planetary gear mechanism PL via a 7 th bearing B7.

The diameter of the output gear OG is larger than the diameter of the drive gear DG. Therefore, the rotation of the drive gear DG is decelerated between the drive gear DG and the output gear OG. In the present embodiment, the output gear OG is directly engaged with the drive gear DG.

In the present embodiment, the output gear OG is arranged so as to overlap with both the rotating electrical machine MG and the planetary gear mechanism PL when viewed in the axial direction along the axial direction L. In the example shown in fig. 5, the output gear OG is arranged so as to overlap the stator ST and the rotor RT of the rotary electric machine MG and overlap the first sun gear S1, the first carrier C1, and the first ring gear R1 of the planetary gear mechanism PL when viewed in the axial direction of the axial direction L. Here, the term "overlapping when viewed in a specific direction" means that when a virtual straight line parallel to the line of sight is moved in each direction orthogonal to the virtual straight line, a region where the virtual straight line intersects both the two elements is at least partially present.

According to this configuration, the diameter of the output gear OG is easily increased, and the reduction ratio between the drive gear DG and the output gear OG is easily ensured to be large. As a result, downsizing of the rotating electrical machine MG is easily achieved.

In addition, according to the present configuration, the inter-axis distance between the drive gear DG and the output gear OG (the distance between the first axis X1 and the fourth axis X4 in the radial direction R) is easily suppressed to be small. Therefore, the dimension in the radial direction R of the vehicle drive device 1000 is easily suppressed to be small.

In the present embodiment, the diameter of the drive gear DG is smaller than the diameter of the first sun gear S1 of the planetary gear mechanism PL. According to this configuration, the difference in the radial direction R between the drive gear DG and the output gear OG is easily increased, and the reduction ratio between the drive gear DG and the output gear OG is easily ensured to be large. As a result, downsizing of the rotating electrical machine MG is easily achieved. In the present embodiment, the diameter of the drive gear DG is smaller than the diameter of the first carrier C1 of the planetary gear mechanism PL. In this example, the diameter of the drive gear DG is smaller than the revolution locus of the first pinion gear P1 supported by the first carrier C1. According to this configuration, when the first pinion gear P1 is assembled to the planetary gear mechanism PL from the side of the drive gear DG in the axial direction L (the first axial side L1, among others), interference with the drive gear DG can be avoided, and the first pinion gear P1 can be easily assembled.

The pair of output members OM are arranged in the axial direction L. The output member OM of the first axial side L1 is connected to the first drive shaft DS1 (see fig. 6) extending in the axial direction L so as to rotate integrally with the wheel W of the first axial side L1. The output member OM of the axial second side L2 is connected to the second drive shaft DS2 (see fig. 6) extending in the axial direction L so as to rotate integrally with the wheel W of the axial second side L2. In the following description, the output member OM of the first axial side L1 is referred to as "first output member OM1", and the output member OM of the second axial side L2 is referred to as "second output member OM2".

The differential gear mechanism DF is a planetary gear type differential gear mechanism having a second sun gear S2, a second carrier C2, and a second ring gear R2. In the present embodiment, the differential gear mechanism DF is a double pinion type planetary gear mechanism. Therefore, in the present embodiment, the second carrier C2 rotatably supports the inner pinion gear P21 engaged with the second sun gear S2 and the outer pinion gear P22 engaged with the second ring gear R2.

The second sun gear S2 is connected to the first output member OM1 so as to rotate integrally therewith. In the present embodiment, the first output member OM1 is arranged to extend from the second sun gear S2 toward the first axial side L1. The first output member OM1 is supported rotatably relative to the second carrier C2 via the 8 th bearing B8. In the present embodiment, the first output member OM1 is disposed so as to pass through the third side wall portion 92b and the second side wall portion 92a of the case 9 in the axial direction L. The first output member OM1 is rotatably supported with respect to the third side wall portion 92B via the 9 th bearing B9, and rotatably supported with respect to the second side wall portion 92a via the tenth bearing B10.

The second carrier C2 is connected to the second output member OM2 so as to rotate integrally therewith. In the present embodiment, the second output member OM2 is configured to extend from the second carrier C2 toward the axial second side L2. The second output member OM2 is supported rotatably with respect to the second ring gear R2 via an eleventh bearing B11. In the present embodiment, the second output member OM2 is disposed so as to pass through the fourth side wall portion 92d of the case 9 in the axial direction L. The second output member OM2 is rotatably supported with respect to the fourth side wall 92d via the twelfth bearing B12.

The second ring gear R2 is connected to the output gear OG so as to rotate integrally therewith. In the present embodiment, the second ring gear R2 is disposed inside the output gear OG in the radial direction R. Further, the second ring gear R2 is arranged to overlap the output gear OG as viewed in the radial direction of the radial direction R.

Fig. 7 shows a speed diagram of the planetary gear mechanism PL of the present embodiment. In the speed diagram of fig. 7, the vertical line corresponds to the rotational speeds of the respective rotational elements of the planetary gear mechanism PL. Each of the plurality of vertical lines arranged side by side corresponds to each rotary element of the planetary gear mechanism PL. In the velocity diagram of fig. 7, reference numerals shown above the plurality of vertical lines denote reference numerals of the rotary elements of the corresponding planetary gear mechanism PL. The reference numerals shown below the plurality of vertical lines are references to elements that rotate integrally with the rotating element corresponding to the reference numerals shown above. In the velocity diagram of fig. 7, a black circle on the vertical line corresponding to the third rotary element E3 indicates that the brake mechanism 2 is in the direct-connection engaged state. The "direct-connection engaged state" refers to an engaged state in which there is no difference in rotational speed between the input element and the output element of the friction engagement device.

When the brake mechanism 2 is in the engaged state and the clutch mechanism 1 is in the disengaged state, the first gear G1 is formed in the transmission TM. In this state, as shown in fig. 7, the first ring gear R1 connected to the first rotating member 81, the first carrier C1 connected to the drive gear DG, and the first sun gear S1 connected to the input shaft IS and the second rotating member 82 are rotated relative to each other. As a result, the rotation of the rotor RT is decelerated at a gear ratio corresponding to the first gear G1 in the planetary gear mechanism PL, and transmitted to the drive gear DG.

On the other hand, when the clutch mechanism 1 is in the engaged state and the brake mechanism 2 is in the disengaged state, the second gear G2 is formed in the transmission TM. In this state, the first ring gear R1 connected to the first rotating member 81, the first carrier C1 connected to the drive gear DG, and the first sun gear S1 connected to the input shaft IS and the second rotating member 82 rotate integrally. As a result, since the gear ratio corresponding to the second gear G2 is 1, the rotation of the rotor RT is directly transmitted to the drive gear DG.

4. Vehicle drive device according to second embodiment

A vehicle drive device 1000 according to a second embodiment will be described below with reference to fig. 8 and 9. The vehicular drive apparatus 1000 of the present embodiment is different from the vehicular drive apparatus 1000 of the first embodiment described above in that the output gear OG is not directly meshed with the drive gear DG but is meshed with the intermediate gear IG meshed with the drive gear DG. The following description focuses on differences from the vehicle drive device 1000 according to the first embodiment. The points not specifically described are the same as those of the vehicle drive device 1000 according to the first embodiment.

As shown in fig. 8 and 9, in the present embodiment, as described above, the output gear OG is engaged with the intermediate gear IG engaged with the drive gear DG. That is, the output gear OG and the drive gear DG mesh with the intermediate gear IG at mutually different positions in the circumferential direction of the intermediate gear IG.

In the present embodiment, the output gear OG overlaps the rotating electrical machine MG but does not overlap the planetary gear mechanism PL when viewed in the axial direction along the axial direction L.

In the present embodiment, the case 9 does not include the second peripheral wall portion 91a and the second side wall portion 92a. In this embodiment, the tenth bearing B10 rotatably supporting the first output member OM1 on the second side wall 92a is not provided. The first output member OM1 is shorter in the axial direction L than in the first embodiment.

In the present embodiment, the third side wall portion 92b is integrally formed with the third peripheral wall portion 91b and the fourth peripheral wall portion 91 c. The first side wall portion 92 and the third peripheral wall portion 91b are formed of different members.

As described above, the vehicle drive device 1000 includes:

a rotating electrical Machine (MG) having a Rotor (RT);

An input shaft IS integrally rotated with the rotor RT;

an output gear OG in driving connection with the wheel W; and

The transmission TM has a planetary gear mechanism PL and an engagement device 100, wherein,

The planetary gear mechanism PL has: the order of the rotational speeds of the first rotating element E1, the second rotating element E2, and the third rotating element E3 is the order described,

The first rotating element E1 IS connected to the input shaft IS in such a way as to rotate integrally therewith,

The second rotating element E2 is connected to the driving gear DG in such a way as to rotate integrally therewith,

The third rotary element E3 is switched between a first state connected to the non-rotary member NR and a second state connected to the first rotary element E1 or the second rotary element E2 in an integrally rotated manner according to the state of engagement of the engagement device 100,

The rotor RT, the planetary gear mechanism PL, the engagement device 100 and the drive gear DG are arranged coaxially,

The drive gear DG is arranged between the rotor RT and the transmission TM in the axial direction L,

The input shaft IS penetrates the drive gear DG in the axial direction L, and connects the rotor RT and the first rotary element E1 in an integrally rotatable manner,

The diameter of the output gear OG is larger than the diameter of the drive gear DG,

The drive gear DG meshes with the output gear OG, or an intermediate gear IG meshed with the drive gear DG meshes with the output gear OG.

According to this configuration, the drive gear DG integrally rotatably connected to the second rotary element E2 of the planetary gear mechanism PL directly meshes with the output gear OG formed to have a larger diameter than the drive gear DG, or meshes with the output gear OG formed to have a larger diameter than the drive gear DG via the intermediate gear IG. Thereby, the rotation of the second rotating element E2 transmitted to the drive gear DG can be decelerated between the drive gear DG and the output gear OG. Therefore, for example, the structure of the vehicle drive device 1000 can be simplified as compared with a structure having the planetary gear mechanism PL that decelerates the rotation of the second rotary element E2. In the case of the structure without the intermediate gear IG, when the third rotary element E3 is in the second state, the meshing of the gears in the power transmission path from the rotary electric machine MG to the output gear OG is only at the point where the drive gear DG meshes with the output gear OG. On the other hand, in the case where the third rotary element E3 is in the first state, only the engagement of the inside of the planetary gear mechanism PL is increased. In this way, since the number of gear meshes of the entire vehicle drive device 1000 is small, the transmission efficiency of the power transmission path from the rotating electrical machine MG to the output gear OG is easily improved. In addition, even in the case of the configuration having the intermediate gear IG, the engagement of only one gear is increased as compared with the configuration not having the intermediate gear IG, and the transmission efficiency of the power transmission path from the rotary electric machine MG to the output gear OG is also easily improved.

In addition, according to the present configuration, the rotor RT, the transmission TM, and the drive gear DG are coaxially arranged, and the drive gear DG is arranged between the rotor RT and the transmission TM in the axial direction L. As a result, the size of the vehicle drive device 1000 in the radial direction R can be reduced compared to a configuration in which the drive gear DG is disposed so as to overlap at least one of the rotor RT and the transmission TM when viewed in the radial direction R. Further, the difference in the radial direction R between the drive gear DG and the output gear OG is easily increased, and the reduction ratio between the drive gear DG and the output gear OG is easily ensured to be large. As a result, downsizing of the rotating electrical machine MG is easily achieved.

As described above, according to the present configuration, in the configuration having the transmission TM including the planetary gear mechanism PL and the engagement device 100, the vehicle drive device 1000 can be realized that is small and simple in structure.

In the first and second embodiments, the vehicle driving device 1000 further includes:

The output member OM rotates integrally with the wheel W,

The output gear OG and the output member OM are arranged coaxially.

According to this configuration, the output gear OG that directly meshes with the drive gear DG disposed coaxially with the rotor RT and the transmission TM or meshes with the intermediate gear IG, and the output member OM that rotates integrally with the wheel W are disposed coaxially. This makes it easy to reduce the number of axles of the entire vehicle drive apparatus 1000. Therefore, the dimension in the radial direction R of the vehicle drive device 1000 can be suppressed to be small.

In the first and second embodiments, the vehicle driving device 1000 further includes:

a pair of output members OM integrally rotated with the mutually different wheels W, respectively; and

A planetary differential gear mechanism DF having a second sun gear S2, a second carrier C2 and a second ring gear R2 and distributing rotation of an output gear OG to a pair of output members OM,

The output gear OG is disposed further outside in the radial direction R than the ring gear and overlaps with the ring gear when viewed in the radial direction of the radial direction R.

According to this configuration, since the differential gear mechanism DF is a planetary gear mechanism, the dimension in the axial direction L of the vehicle drive device 1000 is easily suppressed to be smaller than that in a configuration in which the differential gear mechanism DF is a bevel gear mechanism.

In addition, according to the present structure, the output gear OG is disposed further outward in the radial direction R than the second ring gear R2. This makes it easy to increase the diameter of the output gear OG, and to ensure a large reduction ratio between the drive gear DG and the output gear OG. As a result, downsizing of the rotating electrical machine MG is easily achieved.

In addition, according to the present structure, the output gear OG is configured to overlap with the second ring gear R2 as viewed in the radial direction of the radial direction R. As a result, the dimension of the vehicle drive device 1000 in the axial direction L can be suppressed to be smaller than a configuration in which the output gear OG is arranged offset in the axial direction L with respect to the second ring gear R2.

In the first and second embodiments described above, the planetary gear mechanism PL is disposed on the rotor RT side in the axial direction L with respect to the engagement device 100.

According to this structure, the connection structure between the first rotary element E1 of the planetary gear mechanism PL and the rotor RT and the connection structure between the second rotary element E2 of the planetary gear mechanism PL and the drive gear DG can be easily simplified. Therefore, the vehicle drive device 1000 is easily miniaturized.

5. Vehicle drive device according to third embodiment

A vehicle driving device 1000 according to a third embodiment having the engagement device 100 according to the second embodiment will be described below with reference to fig. 10 to 12. As shown in fig. 10 and 11, the vehicle drive device 1000 includes: a rotating electrical Machine (MG) having a Stator (ST) and a Rotor (RT); an input member IM transmitting rotation of the rotor RT; an output member OM integrally rotated with a wheel W (see fig. 11); a speed reducer RD that reduces the rotation of the input member IM and transmits the rotation to the output member OM; and a brake mechanism 2 selectively engaging the input member IM and the non-rotating member NR. In the present embodiment, the vehicle drive device 1000 further includes: a clutch mechanism 1 that selectively engages the rotor RT and the input member IM; a drive mechanism 7 that changes the state of engagement of both the brake mechanism 2 and the clutch mechanism 1; and a casing 9 as a non-rotating member NR. In the present embodiment, the vehicle driving device 1000 is configured as a driving device for the wheel W called an In-wheel motor (In-wheel motor).

The rotor RT, the input member IM, the output member OM, and the brake mechanism 2 are coaxially arranged. In other words, the rotor RT, the input member IM, and the brake mechanism 2 are arranged coaxially with the output member OM that rotates integrally with the wheel W, that is, coaxially with the rotation axis of the wheel W. In the present embodiment, reduction gear RD and clutch mechanism 1 are also coaxially arranged.

As shown in fig. 10, the case 9 houses the rotating electrical machine MG, the input member IM, the output member OM, the speed reducer RD, the brake mechanism 2, the clutch mechanism 1, and the drive mechanism 7. In the present embodiment, the case 9 houses the output member OM and the driving mechanism 7 in a state in which a part of the output member OM and the driving mechanism 7 is exposed to the outside. In the present embodiment, the case 9 includes a fifth side wall portion 95 and a sixth side wall portion 96 in addition to the first peripheral wall portion 91, the first side wall portion 92, the support wall portion 93, and the cover portion 94.

The first peripheral wall portion 91 is formed in a tubular shape that is open at the first side L1 in the axial direction and the second side L2 in the axial direction. The fifth side wall portion 95 and the sixth side wall portion 96 are formed to extend in the radial direction R. The fifth side wall portion 95 is configured to block the opening of the first side L1 in the axial direction of the first peripheral wall portion 91. The sixth side wall portion 96 is configured to block the opening of the axial second side L2 of the first peripheral wall portion 91.

The first side wall portion 92 is formed to extend inward in the radial direction R from the first peripheral wall portion 91. The first side wall 92 is disposed between the fifth side wall 95 and the sixth side wall 96 in the axial direction L. In the present embodiment, the speed reducer RD is disposed between the first side wall portion 92 and the fifth side wall portion 95 in the axial direction L. Further, the rotating electric machine MG, the brake mechanism 2, and the clutch mechanism 1 are disposed between the first side wall portion 92 and the sixth side wall portion 96 in the axial direction L.

The cover portion 94 is formed to cover the axial second side L2 of the sixth side wall portion 96. In the present embodiment, a plurality of vehicle body connection members C1 for connecting the vehicle drive device 1000 to the vehicle body are arranged so as to protrude from the sixth side wall portion 96 toward the second axial side L2, and are distributed in the circumferential direction around the rotation axis of the rotor RT. Further, a cover 94 is disposed on the inner side in the radial direction R with respect to the plurality of vehicle body connecting members C1.

The rotating electrical machine MG functions as a driving force source for the wheels W (see fig. 11). The rotating electrical machine MG has a function as a motor (electric motor) that generates power upon receiving supply of electric power, and a function as a generator (generator) that generates electric power upon receiving supply of electric power. Specifically, the rotating electrical machine MG is electrically connected to a power storage device (not shown) such as a battery or a capacitor. The rotating electrical machine MG generates driving force by traction with electric power stored in the power storage device. The rotating electrical machine MG generates electric power by using the driving force transmitted from the wheel W side, and charges the power storage device.

The stator ST of the rotating electrical machine MG is fixed to the non-rotating member NR. In the present embodiment, the stator ST is fixed to the first peripheral wall portion 91 of the case 9. The rotor RT of the rotating electrical machine MG is rotatably supported with respect to the stator ST. In the present embodiment, the rotor RT is disposed inside the stator ST in the radial direction R.

As shown in fig. 12, in the present embodiment, the rotary electric machine MG further has a rotor supporting member 13. The rotor support member 13 is a member that supports the rotor RT so as to be able to face the case 9. In the present embodiment, the rotor support member 13 includes: an outer cylindrical portion 131, an inner cylindrical portion 132, and a connecting portion 133.

The outer cylindrical portion 131 is formed in a cylindrical shape coaxial with the rotor RT. The outer cylindrical portion 131 is configured to support the rotor RT from the inside in the radial direction R. In the present embodiment, the outer cylindrical portion 131 corresponds to the first rotary member 81.

The inner cylindrical portion 132 is formed in a cylindrical shape coaxial with the outer cylindrical portion 131. The inner cylindrical portion 132 is formed to have a smaller diameter than the outer cylindrical portion 131. In the present embodiment, the inner cylindrical portion 132 is rotatably supported with respect to the first side wall portion 92 of the case 9 via the second bearing B2. The second bearing B2 is a radial bearing disposed between the inner cylindrical portion 132 and the radial direction R of the first side wall portion 92. In the illustrated example, the second bearing B2 is a ball bearing disposed so as to support the inner cylindrical portion 132 from the outside in the radial direction R. In the present embodiment, the inner cylindrical portion 132 corresponds to the first shaft member 10.

The connecting portion 133 extends along the radial direction R so as to connect the outer cylindrical portion 131 and the inner cylindrical portion 132. In the present embodiment, the outer end of the connecting portion 133 in the radial direction R is connected to the end of the outer cylindrical portion 131 on the first side L1 in the axial direction. Further, an inner end of the connecting portion 133 in the radial direction R is connected to an end of the second axial side L2 of the inner cylindrical portion 132. In the illustrated example, the outer cylindrical portion 131, the inner cylindrical portion 132, and the connecting portion 133 are integrally formed.

In the present embodiment, the connection portion 133 is rotatably supported with respect to the first side wall portion 92 of the case 9 via the first bearing B1. The first bearing B1 is a thrust bearing disposed between the connecting portion 133 and the axial direction L of the first side wall portion 92. In the illustrated example, the first bearing B1 is a ball bearing disposed so as to support the connection portion 133 from the axial first side L1.

In the present embodiment, the input member IM includes the second rotation member 82 and the second shaft member 20. The second shaft member 20 is disposed so as to penetrate the first side wall portion 92 of the case 9 in the axial direction L. In the present embodiment, the second shaft member 20 is disposed inside the rotor support member 13 in the radial direction R with respect to the inner cylindrical portion 132. The second shaft member 20 is supported via a third bearing B3 so as to be rotatable relative to the inner cylindrical portion 132. The third bearing B3 is a radial bearing disposed between the second shaft member 20 and the radial direction R of the inner cylindrical portion 132.

In the present embodiment, the brake mechanism 2 and the clutch mechanism 1 are arranged in an aligned manner in the axial direction L. In the illustrated example, the clutch mechanism 1 is disposed on the first axial side L1 with respect to the brake mechanism 2.

As shown in fig. 12, in the present embodiment, the brake mechanism 2 includes: the third friction engagement element 21, the fourth friction engagement element 22, the second outer side bearing 822, the second inner side bearing 931, and the second pressing portion 312.

The third friction engagement element 21 and the fourth friction engagement element 22 are arranged to oppose each other in the axial direction L. The third friction engagement element 21 and the fourth friction engagement element 22 are friction-engaged with each other by being pressed in the axial direction L. In the present embodiment, the third friction engagement element 21 and the fourth friction engagement element 22 are each formed in a disk shape coaxial with the rotor RT. The third friction engagement element 21 and the fourth friction engagement element 22 are each provided in plural numbers, and are alternately arranged along the axial direction L. One of the third friction engagement element 21 and the fourth friction engagement element 22 may be used as a friction plate, and the other may be used as a separator plate.

The second outer support 822 slidably supports the third friction engagement element 21 in the axial direction L so as to rotate integrally with the third friction engagement element 21. In the present embodiment, the second outer support 822 is formed in a cylindrical shape coaxial with the rotor RT. The second outer support 822 supports the third friction engagement element 21 from the outside in the radial direction R. In this example, a plurality of spline teeth extending in the axial direction L are formed in a circumferentially dispersed manner in the inner peripheral portion of the second outer support portion 822. On the other hand, similar spline teeth are formed so as to be circumferentially dispersed also in the outer peripheral portion of the third friction engagement element 21. And, the spline teeth are engaged with each other.

The second inner support portion 931 slidably supports the fourth frictional engagement element 22 in the axial direction L so as to rotate integrally with the fourth frictional engagement element 22. In the present embodiment, the second inner support portion 931 is formed coaxially with the second outer support portion 822 and is formed in a cylindrical shape having a diameter smaller than that of the second outer support portion 822. The second inner support 931 supports the fourth frictional engagement element 22 from the inner side in the radial direction R. In this example, a plurality of spline teeth extending in the axial direction L are formed in a circumferentially dispersed manner on the outer peripheral portion of the second inner support portion 931. On the other hand, similar spline teeth are also formed in the inner peripheral portion of the fourth friction engagement element 22 so as to be circumferentially dispersed. And, the spline teeth are engaged with each other.

The second outer support 822 is connected to the input member IM so as to rotate integrally therewith. The second inner support 931 is fixed to the non-rotating member NR. In the present embodiment, the second inner support portion 931 is fixed to a support wall portion 93 provided in the case 9 as the non-rotating member NR. The support wall portion 93 is formed to extend in the radial direction R. In the present embodiment, the support wall portion 93 is joined from the first side L1 in the axial direction to a portion of the sixth side wall portion 96 covered with the cover portion 94. In the illustrated example, the second inner support portion 931 is integrally formed with the support wall portion 93 so as to protrude from the support wall portion 93 toward the first axial side L1.

The second pressing portion 312 is configured to press the third friction engagement element 21 and the fourth friction engagement element 22. In the present embodiment, the second pressing portion 312 is formed to extend in the radial direction R. And, the second pressing portion 312 is configured to press the third friction engagement element 21 and the fourth friction engagement element 22 from the axial first side L1.

In the present embodiment, the clutch mechanism 1 includes: the first frictional engagement element 11, the second frictional engagement element 12, the first outer side supporting portion 811, the first inner side supporting portion 821, and the first pressing portion 311.

The first friction engagement element 11 and the second friction engagement element 12 are arranged to oppose each other in the axial direction L. The first friction engagement element 11 and the second friction engagement element 12 are friction-engaged with each other by being pressed in the axial direction L. In the present embodiment, the first friction engagement element 11 and the second friction engagement element 12 are each formed in a disk shape coaxial with the rotor RT. The first friction engagement element 11 and the second friction engagement element 12 are provided in plural numbers, and are alternately arranged in the axial direction L. One of the first friction engagement element 11 and the second friction engagement element 12 may be used as a friction plate, and the other may be used as a separator plate.

The first outer support 811 slidably supports the first friction engagement element 11 in the axial direction L so as to rotate integrally with the first friction engagement element 11. In the present embodiment, the first outer support portion 811 is formed in a cylindrical shape coaxial with the rotor RT. The first outer support 811 supports the first friction engagement element 11 from the outside in the radial direction R. In this example, a plurality of spline teeth extending in the axial direction L are formed in a circumferentially dispersed manner on the inner peripheral portion of the first outer support portion 811. On the other hand, similar spline teeth are also formed at the outer peripheral portion of the first friction engagement element 11 so as to be circumferentially dispersed. And, the spline teeth are engaged with each other.

The first inner support 821 slidably supports the second friction engagement element 12 in the axial direction L so as to rotate integrally with the second friction engagement element 12. In the present embodiment, the first inner support portion 821 is formed coaxially with the first outer support portion 811, and is formed in a cylindrical shape having a diameter smaller than that of the first outer support portion 811. The first inner support 821 supports the second friction engagement element 12 from the inner side in the radial direction R. In this example, a plurality of spline teeth extending in the axial direction L are formed in a circumferentially dispersed manner on the outer peripheral portion of the first inner support portion 821. On the other hand, similar spline teeth are also formed in the inner peripheral portion of the second friction engagement element 12 so as to be circumferentially dispersed. And, the spline teeth are engaged with each other.

The first pressing portion 311 is configured to press the first friction engagement element 11 and the second friction engagement element 12. In the present embodiment, the first pressing portion 311 is formed to extend in the radial direction R. And, the first pressing portion 311 is configured to press the first friction engagement element 11 and the second friction engagement element 12 from the axial second side L2. In the present embodiment, the first pressing portion 311 is connected to the second outer support 822 of the brake mechanism 2 so as to rotate integrally therewith. In the illustrated example, the first pressing portion 311 and the second outer support 822 are integrally formed such that an end portion on the outer side in the radial direction R of the first pressing portion 311 is connected to an end portion on the first side L1 in the axial direction of the second outer support 822.

In the present embodiment, the first pressing portion 311 is supported via the fourth bearing B4 so as to be rotatable relative to the second pressing portion 312. The fourth bearing B4 is a thrust bearing disposed between the first pressing portion 311 and the axial direction L of the second pressing portion 312. In the illustrated example, the fourth bearing B4 is a ball bearing disposed so as to support the first pressing portion 311 from the axial second side L2 and support the second pressing portion 312 from the axial first side L1.

The first outer support 811 is connected to the rotor RT so as to rotate integrally therewith. In the present embodiment, the first outer support portion 811 is connected to the outer cylindrical portion 131 of the rotor support member 13 from the inside in the radial direction R. In the illustrated example, the first outer support portion 811 is integrally formed with the outer tubular portion 131.

The first inner support 821 is connected to the input member IM so as to rotate integrally therewith. In the present embodiment, the first inner support portion 821 is connected to a portion (the second rotating member 82, among others) of the input member IM on the second axial side L2 than the connection portion 133 of the rotor support member 13 from the outside in the radial direction R. In the illustrated example, the first inner support 821 is integrally formed with the input member IM.

The first inner support 821 is connected to the second outer support 822 of the brake mechanism 2 so as to rotate integrally therewith. In the present embodiment, the first inner support 821 slidably supports the first pressing portion 311 in the axial direction L so as to rotate integrally with the first pressing portion 311 connected to the second outer support 822. In this example, spline teeth that engage with spline teeth formed on the outer peripheral portion of the first inner support 821 are formed on the inner peripheral portion of the first pressing portion 311 so as to be dispersed in the circumferential direction. And, the spline teeth are engaged with each other. The third friction engagement element 21 of the brake mechanism 2 and the second friction engagement element 12 of the clutch mechanism 1 rotate integrally.

The brake mechanism 2 is disposed on the inner side of the rotor RT of the rotary electric machine MG in the radial direction R and overlaps the rotor RT when viewed in the radial direction R. Here, the term "overlapping when viewed in a specific direction" means that when a virtual straight line parallel to the line of sight is moved in each direction orthogonal to the virtual straight line, a region where the virtual straight line intersects both the two elements is at least partially present.

In the present embodiment, the clutch mechanism 1 is also disposed at a position on the inner side of the rotor RT in the radial direction R and overlapping the rotor RT when viewed in the radial direction R.

As described above, since the decelerator RD is provided to decelerate and transmit the rotation of the input member IM to the output member OM, the moment of inertia of the rotor RT is amplified and acts on the output member OM according to the reduction ratio of the decelerator RD. As a result, for example, when a large torque variation is transmitted from the wheel W to the output member OM due to the wheel W riding over a step or the like on a wavy road, the torque acting on the transmission path of the driving force tends to become excessive. On the other hand, if the strength of the members disposed on the transmission path of the driving force is ensured to be large, the members are increased in size.

According to the present structure, a clutch mechanism 1 that selectively engages the rotor RT and the input member IM is provided. In this way, when an excessive torque acts on the transmission path of the driving force, the clutch mechanism 1 is slipped, and the driving force transmitted between the rotor RT and the input member IM can be prevented from becoming excessive. Therefore, the components disposed on the transmission path of the driving force can be miniaturized.

Further, according to the present configuration, the clutch mechanism 1 is brought into the disengaged state, whereby the rotor RT can be disengaged from the input member IM (and hence from the wheels W). In this way, the rotating electrical machine MG can be stopped during the period when the vehicle is traveling by inertia, during the period when the vehicle is traveling by the driving force of another driving source, or the like. Therefore, the energy efficiency of the vehicle drive device 1000 can be improved.

The drive mechanism 7 is configured to change state between a first state in which the brake mechanism 2 is engaged and the clutch mechanism 1 is disengaged, and a second state in which the brake mechanism 2 is disengaged and the clutch mechanism 1 is engaged. In the present embodiment, the drive mechanism 7 is configured to be changed to a third state in which the brake mechanism 2 is in a disengaged state and the clutch mechanism 1 is in a disengaged state. In the third state, as described above, the rotating electrical machine MG can be stopped during the period when the vehicle is traveling by inertia, during the period when the vehicle is traveling by the driving force of another driving source, or the like. As shown in fig. 10, in the present embodiment, the driving mechanism 7 includes: a linear motion mechanism 33, a transmission mechanism 5, and a drive source 4.

The linear motion mechanism 33 is configured to move the second pressing portion 312 of the brake mechanism 2 and the first pressing portion 311 of the clutch mechanism 1 in the axial direction L. In the present embodiment, the second pressing portion 312 and the first pressing portion 311 are arranged between the third friction engagement element 21 and the fourth friction engagement element 22 and the axial direction L of the first friction engagement element 11 and the second friction engagement element 12. Therefore, the linear motion mechanism 33 is configured to easily move both the second pressing portion 312 and the first pressing portion 311.

As shown in fig. 12, in the present embodiment, the linear motion mechanism 33 includes a screw shaft 331 rotatably supported with respect to the non-rotating member NR, and a nut member 332 screwed with the screw shaft 331.

Screw threads are formed on the outer periphery of the screw shaft 331. The screw shaft 331 is formed to extend in the axial direction L. In the present embodiment, the screw shaft 331 is disposed coaxially with the brake mechanism 2 and the clutch mechanism 1. In the present embodiment, the lead screw shaft 331 is disposed at a position on the inner side of the second inner side support portion 931 of the brake mechanism 2 in the radial direction R and overlapping the second inner side support portion 931 when viewed in the radial direction R.

A groove that engages with the thread of the screw shaft 331 is formed in the inner peripheral portion of the nut member 332. By the rotation of the screw shaft 331, the nut member 332 performs a linear motion in the axial direction L according to the rotation direction and the direction of the thread of the screw shaft 331.

In the present embodiment, the nut member 332 is connected to the second pressing portion 312 of the brake mechanism 2 so as to move integrally therewith in the axial direction L. As described above, in the present embodiment, the fourth bearing B4 is disposed between the second pressing portion 312 and the axial direction L of the first pressing portion 311. Therefore, in the present embodiment, when the screw shaft 331 rotates so as to move the nut member 332 to the first axial side L1, the second pressing portion 312 moves to the first axial side L1 via the nut member 332, and the first pressing portion 311 also moves to the first axial side L1 via the fourth bearing B4. As a result, the first friction engagement element 11 and the second friction engagement element 12 are pressed by the first pressing portion 311 to bring the clutch mechanism 1 into the engaged state, and the pressing of the third friction engagement element 21 and the fourth friction engagement element 22 by the second pressing portion 312 is released to bring the brake mechanism 2 into the disengaged state. In this state, power is transmitted between the rotor RT and the input member IM.

On the other hand, in the present embodiment, when the screw shaft 331 rotates so as to move the nut member 332 to the axial second side L2, the second pressing portion 312 moves to the axial second side L2 via the nut member 332. As a result, the third friction engagement element 21 and the fourth friction engagement element 22 are pressed by the second pressing portion 312 to bring the brake mechanism 2 into the engaged state, and the pressing of the first friction engagement element 11 and the second friction engagement element 12 by the first pressing portion 311 is released to bring the clutch mechanism 1 into the disengaged state. In this state, the power transmission between the rotor RT and the input member IM is cut off.

The transmission mechanism 5 is configured to transmit the power of the drive source 4 to the linear motion mechanism 33. As shown in fig. 10, in the present embodiment, the transmission mechanism 5 includes: first gear 51, second gear 52, third gear 53, fourth gear 54, and connecting body 55.

The first gear 51 is connected to the output shaft of the drive source 4 so as to rotate integrally therewith. In the present embodiment, the first gear 51 is disposed coaxially with the screw shaft 331 of the linear motion mechanism 33. The first gear 51 is disposed on the first side L1 in the axial direction with respect to the drive source 4.

The second gear 52 is meshed with the first gear 51. In the present embodiment, the second gear 52 is formed to have a larger diameter than the first gear 51. The third gear 53 is connected to the second gear 52 so as to rotate integrally therewith. In the present embodiment, the third gear 53 is formed to have a smaller diameter than the second gear 52. The third gear 53 is disposed on the first side L1 in the axial direction with respect to the second gear 52. In the present embodiment, the second gear 52 and the third gear 53 are rotatably supported by the first shaft 56 with respect to the case 9. The first shaft 56 is formed to extend along the axial direction L. In the present embodiment, the first shaft body 56 is disposed so as to pass through the sixth side wall portion 96 in the axial direction L. The end portion of the first shaft 56 on the first side L1 in the axial direction is rotatably supported with respect to the support wall 93. The end of the first shaft 56 on the second side L2 in the axial direction is rotatably supported with respect to the cover 94.

The fourth gear 54 is meshed with the third gear 53. In the present embodiment, the fourth gear 54 is formed to have a larger diameter than the third gear 53. In the present embodiment, the fourth gear 54 is disposed coaxially with the screw shaft 331 of the linear motion mechanism 33. In the present embodiment, the fourth gear 54 is integrally and rotatably connected to the connecting body 55 via the second shaft body 57. The second shaft body 57 is formed to extend along the axial direction L. In the present embodiment, the second shaft body 57 is disposed so as to penetrate the sixth side wall portion 96 and the support wall portion 93 in the axial direction L.

In the present embodiment, the number of teeth of the second gear 52 is larger than that of the first gear 51. The fourth gear 54 has a larger gear ratio than the third gear 53 which rotates integrally with the second gear 52. Therefore, in the present embodiment, the rotation transmitted from the drive source 4 to the first gear 51 is decelerated between the first gear 51 and the second gear 52, and transmitted to the third gear 53. The rotation of the third gear 53 is decelerated between the third gear 53 and the fourth gear 54, and transmitted to the connection body 55.

As shown in fig. 12, the connecting body 55 connects the fourth gear 54 and the screw shaft 331 so that they integrally rotate. In the present embodiment, the connection body 55 is formed in a cylindrical shape that is open at the second side L2 in the axial direction. In a state where the second shaft body 57 is disposed inside the connecting body 55 in the radial direction R, the connecting body 55 and the second shaft body 57 are connected to integrally rotate. In the present embodiment, the connection body 55 and the screw shaft 331 are integrally rotatably connected in a state where the screw shaft 331 is arranged to protrude from the connection body 55 toward the first axial side L1. In the present embodiment, the connecting body 55 is disposed at a position on the inner side of the second inner side support portion 931 of the brake mechanism 2 in the radial direction R and overlapping the second inner side support portion 931 when viewed in the radial direction R.

The drive source 4 is a device that generates power for driving the linear motion mechanism 33. In the present embodiment, the drive source 4 is supported by the cover 94. In the illustrated example, the drive source 4 is connected to the cover 94 from the second axial side L2. In this example, the drive source 4 is an electric motor.

As described above, in the present embodiment, the vehicle drive device 1000 further includes: the driving mechanism 7 changes the state of engagement of both the brake mechanism 2 and the clutch mechanism 1,

The brake mechanism 2 and the clutch mechanism 1 are arranged in an aligned manner in the axial direction L,

The drive mechanism 7 is configured to change state between a first state in which the brake mechanism 2 is engaged and the clutch mechanism 1 is disengaged, and a second state in which the brake mechanism 2 is disengaged and the clutch mechanism 1 is engaged.

According to this configuration, the state of engagement of both the brake mechanism 2 and the clutch mechanism 1 can be changed by the common drive mechanism 7. Therefore, the vehicle driving device 1000 is more easily miniaturized than a configuration in which the brake mechanism 2 and the clutch mechanism 1 are driven by different driving mechanisms.

In the present embodiment, reduction gear RD is a planetary gear mechanism having sun gear SG, carrier CR, and ring gear RG. The speed reducer RD is a single pinion type planetary gear mechanism. In the present embodiment, reduction gear RD is disposed at a position not overlapping rotating electric machine MG when viewed in the radial direction of radial direction R. In the illustrated example, reduction gear RD is disposed on first side L1 in the axial direction with respect to rotating electrical machine MG.

As shown in fig. 10, in the present embodiment, the sun gear SG is connected to the input member IM so as to rotate integrally therewith. That is, in the present embodiment, sun gear SG is an input element of reduction gear RD. In the illustrated example, the sun gear SG is formed in a portion of the input member IM on the first side L1 in the axial direction than the first side wall 92 of the case 9. In the present embodiment, the sun gear SG is disposed further inward in the radial direction R than the rotor RT. In the illustrated example, the sun gear SG is disposed further inward in the radial direction R than the third and fourth friction engagement elements 21 and 22 of the brake mechanism 2 and the first and second friction engagement elements 11 and 12 of the clutch mechanism 1.

The carrier CR rotatably supports the pinion PG. Pinion gear PG meshes with sun gear SG and ring gear RG. The pinion PG rotates (rotates) around its axis, and rotates (revolves) around the sun gear SG together with the carrier CR. The pinion PG is provided in plural numbers along the revolution locus thereof at intervals.

In the present embodiment, the carrier CR is connected to the output member OM so as to rotate integrally therewith. That is, in the present embodiment, the carrier CR is an output element of the speed reducer RD. In the present embodiment, the carrier CR includes: the first supported portion CRa is supported rotatably with respect to the case 9 via a thirteenth bearing B13; and a second supported portion CRb supported rotatably with respect to the case 9 via a fourteenth bearing B14.

In the present embodiment, the first supported portion CRa is formed in a cylindrical shape coaxial with the sun gear SG. The first supported portion CRa is disposed on the first side L1 in the axial direction with respect to the pinion gear PG so as to pass through the fifth side wall portion 95 of the case 9 in the axial direction L. The thirteenth bearing B13 is a radial bearing disposed between the first supported portion CRa and the radial direction R of the fifth side wall portion 95. In the illustrated example, the thirteenth bearing B13 is configured to support the first supported portion CRa from the outside in the radial direction R. The thirteenth bearing B13 is an angular ball bearing inclined with respect to the axial direction L along an imaginary line (line of action) passing through contact points between the rolling elements and the raceway ring of the thirteenth bearing B13.

In the present embodiment, the second supported portion CRb is formed in a cylindrical shape coaxial with the first supported portion CRa. The second supported portion CRb is disposed on the second axial side L2 with respect to the pinion gear PG. The fourteenth bearing B14 is a radial bearing disposed between the second supported portion CRb and the radial direction R of the first side wall portion 92 of the case 9. In the illustrated example, the fourteenth bearing B14 is configured to support the second supported portion CRb from the inside in the radial direction R. The fourteenth bearing B14 is an angular ball bearing inclined with respect to the axial direction L along an imaginary line (line of action) passing through contact points between the rolling elements and the raceway ring of the fourteenth bearing B14. The thirteenth bearing B13 and the fourteenth bearing B14 are disposed such that the directions in which their lines of action incline with respect to the axial direction L are reversed.

In the present embodiment, the ring gear RG is fixed to the case 9. In the illustrated example, the ring gear RG is integrally formed with the first side wall portion 92 of the case 9. In the present embodiment, the ring gear RG is disposed at a position overlapping the stator ST when viewed in the axial direction along the axial direction L.

As described above, in the present embodiment, the reduction gear RD is a planetary gear mechanism having the sun gear SG, the carrier CR, and the ring gear RG, and is disposed at a position not overlapping the rotating electrical machine MG when viewed in the radial direction of the radial direction R,

The rotor RT is disposed inside the radial direction R with respect to the stator ST of the rotating electrical machine MG,

The ring gear RG is arranged in such a manner as to overlap the stator ST when viewed in the axial direction along the axial direction L,

The sun gear SG is disposed further inward in the radial direction R than the rotor RT.

According to this structure, the dimensional difference in the radial direction R between the ring gear RG and the sun gear SG can be ensured to be large. This makes it easy to secure a large reduction ratio of reduction gear RD.

In the present embodiment, reduction gear RD is constituted by one planetary gear mechanism. According to this configuration, for example, the dimension of reduction gear RD in axial direction L can be suppressed to be smaller than a configuration in which parallel shaft gear mechanism and planetary gear mechanism are aligned in axial direction L.

In the present embodiment, the output member OM is a hub (white hub). In the present embodiment, the output member OM has a connection portion OMa and a joint portion OMb.

The connection part OMa is connected to the output element of the speed reducer RD so as to rotate integrally therewith. In the present embodiment, the connection portion OMa is formed to extend along the axial direction L. The connection part OMa is connected to the first supported portion CRa of the carrier CR so as to rotate integrally with the first supported portion CRa in a state of being disposed on the inner side in the radial direction R.

The engagement portion OMb is configured to engage with the wheel W. In the present embodiment, the joint OMb is formed to protrude outward in the radial direction R from a portion of the connecting portion OMa on the first side L1 in the axial direction than the first supported portion CRa of the carrier CR. The joint OMb is connected to the wheel W by a plurality of wheel connecting members C2 disposed so as to be dispersed in the circumferential direction around the axial center thereof, and disposed on the second side L2 in the axial direction with respect to the wheel W.

In this way, in the present embodiment, the output member OM is a hub having an engagement portion OMb with the wheel W,

The speed reducer RD is disposed between the engagement portion OMb and the axial direction L of the rotating electrical machine MG.

According to this configuration, it is easy to keep the size of the radial direction R of the electric rotating machine MG large and to keep the size of the radial direction R of the vehicle drive device 1000 small, as compared with a configuration in which the reduction gear RD is disposed so as to overlap the electric rotating machine MG when viewed in the radial direction R.

As described above, the vehicle drive device 1000 includes:

a rotating electrical Machine (MG) having a Rotor (RT);

an input member IM transmitting rotation of the rotor RT;

An output member OM integrally rotated with the wheel W;

a speed reducer RD that reduces the rotation of the input member IM and transmits the rotation to the output member OM; and

A brake mechanism 2 selectively engages the input member IM and the non-rotating member NR, wherein,

The brake mechanism 2 is disposed on the inner side of the rotor RT in the radial direction R and overlaps with the rotor RT when viewed in the radial direction R,

The rotor RT, the input member IM, and the brake mechanism 2 are arranged coaxially with the output member OM.

According to this structure, the rotor RT is arranged outside the brake mechanism 2 in the radial direction R. As a result, since the rotating electrical machine MG is larger than the brake mechanism 2 in the radial direction R, an increase in output torque due to an increase in the diameter of the rotating electrical machine MG is easily achieved. Further, according to the present configuration, the brake mechanism 2 is disposed at a position overlapping the rotor RT when viewed in the radial direction of the radial direction R. As a result, the dimension in the axial direction L of the vehicle drive device 1000 can be reduced as compared with a configuration in which the brake mechanism 2 is disposed on the side of the rotor RT in the axial direction L. Therefore, according to the present structure, the output torque of the rotating electrical machine MG can be ensured to be large while the dimension in the axial direction L can be suppressed to be small.

In addition, according to the present configuration, the rotor RT, the input member IM, the brake mechanism 2, and the output member OM that rotates integrally with the wheel W are arranged coaxially. This can realize a configuration suitable for a driving device for a wheel W such as an in-wheel motor.

6. Other embodiments

(1) In the above-described embodiment of the joining device 100, the structure in which the linear motion mechanism 33 is disposed on the second side L2 in the axial direction with respect to the second connecting portion 8b has been described as an example. However, the present invention is not limited to this configuration, and for example, the linear motion mechanism 33 may be arranged so as to overlap the second connecting portion 8b when viewed in the radial direction of the radial direction R.

(2) In the above-described embodiment of the coupling device 100, the structure in which the linear motion mechanism 33 is disposed inside the fourth connecting portion 8d of the non-rotating member NR in the radial direction R and overlaps the fourth connecting portion 8d when viewed in the radial direction R has been described as an example. However, the present invention is not limited to this configuration, and the linear motion mechanism 33 may be disposed so as to be offset from the fourth connecting portion 8d in the axial direction to the first side L1 or the axial direction to the second side L2.

(3) In the above-described embodiment of the joining apparatus 100, the structure in which the driven portion 32 is connected to the second pressing portion 312 so as to move integrally therewith in the axial direction L is described as an example, and the second pressing portion 312 is supported in a state in which relative rotation with respect to the non-rotating member NR is restricted. However, the structure is not limited to this, and the driven portion 32 may be connected to the first pressing portion 311 so as to move integrally with the first pressing portion 311 in the axial direction L, and the first pressing portion 311 may be supported so as to rotate integrally with the first rotating member 81 or the second rotating member 82.

(4) In the above-described embodiment of the joining apparatus 100, the structure in which the linear motion mechanism 33 has the screw shaft 331 and the nut member 332 is described as an example. However, the present invention is not limited to this configuration, and the linear motion mechanism 33 may have a rail and a slide member that slides along the rail.

(5) In the above-described coupling device 100 according to the embodiment, the structure in which the screw shaft 331 is coaxially disposed with the first friction coupling element 11, the second friction coupling element 12, the third friction coupling element 21, and the fourth friction coupling element 22, and is disposed inside the radial direction R, is described as an example. However, the present invention is not limited to this configuration, and the screw shaft 331 may be disposed on a different shaft from the first friction engagement element 11, the second friction engagement element 12, the third friction engagement element 21, and the fourth friction engagement element 22. The screw shaft 331 may be disposed further outside in the radial direction R than the first friction engagement element 11, the second friction engagement element 12, the third friction engagement element 21, and the fourth friction engagement element 22.

(6) In the above-described embodiment of the coupling device 100, the configuration in which the drive source 4 is disposed on a shaft different from the screw shaft 331 and the arrangement region in the axial direction L of the drive source 4 overlaps with the arrangement region in the axial direction L of the first rotary member 81 has been described as an example. However, the configuration is not limited to this, and the drive source 4 may be disposed coaxially with the screw shaft 331. The drive source 4 may be disposed so as to be offset from the first rotary member 81 in the axial direction to the first side L1 or the axial direction to the second side L2.

(7) In the above-described embodiment of the coupling device 100, the configuration in which the transmission mechanism 5 decelerates the rotation of the drive source 4 and transmits the same to the screw shaft 331 is described as an example. However, the present invention is not limited to this configuration, and for example, the transmission mechanism 5 may be configured to directly transmit the rotation of the drive source 4 to the screw shaft 331.

(8) In the vehicle drive device 1000 according to the first and second embodiments, the configuration of the planetary gear mechanism PL as a single pinion type planetary gear mechanism is described as an example. However, the configuration is not limited to this, and the planetary gear mechanism PL may be a double pinion type planetary gear mechanism. In this case, for example, the first rotating element E1 may be the first sun gear S1, the second rotating element E2 may be the first ring gear R1, and the third rotating element E3 may be the first carrier C1.

(9) In the vehicle drive device 1000 according to the first and second embodiments, the description has been made taking, as an example, a configuration having the differential gear mechanism DF for distributing the rotation of the output gear OG to the pair of output members OM. However, the present invention is not limited to this configuration, and the rotation of the output gear OG may be transmitted to one output member OM without the differential gear mechanism DF.

(10) In the vehicle driving device 1000 according to the first and second embodiments, the configuration in which the output gear OG and the output member OM are coaxially arranged is described as an example. However, the present invention is not limited to this configuration, and the output gear OG and the output member OM may be disposed on different shafts.

(11) In the vehicle drive device 1000 according to the first and second embodiments, the configuration in which the differential gear mechanism DF is a planetary gear type differential gear mechanism is described as an example. However, the present invention is not limited to such a configuration, and for example, a bevel gear differential gear mechanism may be employed which includes a pair of side gears (side gears) connected to different output members OM so as to rotate integrally with each other, and a plurality of pinion gears engaged with the pair of side gears.

(12) In the vehicle drive device 1000 according to the first and second embodiments, the configuration in which the planetary gear mechanism PL is arranged on the rotor RT side (the first axial side L1) in the axial direction L with respect to the engagement device 100 is described as an example. However, the configuration is not limited to this, and the planetary gear mechanism PL may be disposed on the opposite side (axial second side L2) of the coupling device 100 to the rotor RT side in the axial direction L.

(13) In the vehicle driving device 1000 according to the third embodiment, the configuration in which the vehicle driving device 1000 is configured as an in-wheel motor and the output member OM has the engagement portion OMb that engages with the wheel W is described as an example. However, the present invention is not limited to such a configuration. For example, the output member OM may be a drive shaft connected to the wheel W so as to rotate integrally therewith.

(14) In the vehicle driving device 1000 according to the third embodiment, the description has been made taking, as an example, a configuration having the clutch mechanism 1 that selectively engages the rotor RT and the input member IM. However, the present invention is not limited to this configuration, and the clutch mechanism 1 may not be provided.

(15) In the vehicle driving device 1000 according to the third embodiment, the description has been made taking, as an example, a configuration having the driving mechanism 7 that changes the state of engagement of both the brake mechanism 2 and the clutch mechanism 1. However, the present invention is not limited to this configuration, and for example, a configuration may be adopted in which a drive mechanism for changing the state of engagement of the brake mechanism 2 and a drive mechanism for changing the state of engagement of the clutch mechanism 1 are separately provided.

(16) In the vehicular drive device 1000 according to the third embodiment, a configuration in which the reduction gear RD is disposed at a position that does not overlap with the rotating electrical machine MG when viewed in the radial direction of the radial direction R is described as an example. However, the present invention is not limited to this configuration, and reduction gear RD may be disposed so as to overlap rotating electric machine MG when viewed in the radial direction of radial direction R.

(17) In the vehicle drive device 1000 according to the third embodiment, the configuration of the planetary gear mechanism in which the reduction gear RD is a single pinion type is described as an example. However, the present invention is not limited to this configuration, and for example, reduction gear RD may be a double pinion type planetary gear mechanism. In this case, for example, the sun gear SG may be integrally rotatably connected to the input member IM, the ring gear RG may be integrally rotatably connected to the output member OM, and the carrier CR may be fixed to the non-rotating member NR.

(18) In the vehicle drive device 1000 according to the third embodiment, the description has been made taking, as an example, a case where the reduction gear RD is constituted by one planetary gear mechanism. However, the present invention is not limited to this configuration, and reduction gear RD may be configured by a parallel axis gear mechanism having gears that are disposed on different axes and mesh with each other, for example.

(19) The structures disclosed in the above embodiments may be applied in combination with the structures disclosed in the other embodiments, as long as no contradiction occurs. With respect to other configurations, the embodiments disclosed in this specification are merely examples in all respects. Accordingly, various modifications may be made as appropriate without departing from the spirit of the disclosure.

[ Summary of the above embodiment ]

The outline of the above-described joining device (100) is described below.

The joining device (100) is provided with:

a clutch mechanism (1) that selectively engages a first rotary member (81) and a second rotary member (82); and

A brake mechanism (2) for selectively engaging a target rotating member (8T) and a non-rotating member (NR) which are either one of the first rotating member (81) and the second rotating member (82),

The engagement device (100) has a pressing mechanism (3) for changing the engagement state of the clutch mechanism (1) and the brake mechanism (2),

The direction along the rotation axis of the first rotation member (81) is set as an axial direction (L), one side of the axial direction (L) is set as an axial first side (L1), the other side of the axial direction (L) is set as an axial second side (L2),

The clutch mechanism (1) has: a first friction engagement element (11) connected to the first rotation member (81) so as to rotate integrally therewith; and a second friction engagement element (12) connected to the second rotation member (82) so as to rotate integrally therewith,

The first friction engagement element (11) and the second friction engagement element (12) are arranged to oppose each other in the axial direction (L) and to be friction-engaged with each other by being pressed in the axial direction (L),

The brake mechanism (2) has: a third friction engagement element (21) connected to the target rotation member (8T) so as to rotate integrally therewith; and a fourth friction engagement element (22) fixed to the non-rotating member (NR),

The third friction engagement element (21) and the fourth friction engagement element (22) are disposed so as to face each other in the axial direction (L) at positions separated from the first friction engagement element (11) and the second friction engagement element (12) toward the second side (L2) in the axial direction, and are friction-engaged with each other by being pressed in the axial direction (L),

The pressing mechanism (3) has: a pressing portion (31) disposed between the first friction engagement element (11) and the second friction engagement element (12) and the axial direction (L) of the third friction engagement element (21) and the fourth friction engagement element (22); a driven part (32) connected to the pressing part (31) in a linked manner; and a linear motion mechanism (33) for moving the driven part (32) along the axial direction (L),

The first rotating member (81), the second rotating member (82), the first friction engagement element (11), the second friction engagement element (12), the third friction engagement element (21), and the fourth friction engagement element (22) are arranged coaxially,

The clutch mechanism (1) and the brake mechanism (2) are selectively engaged according to the driven portion (32) being moved to the axial first side (L1) or to the axial second side (L2) by the linear motion mechanism (33).

According to this structure, the pressing portion (31) that moves in the axial direction (L) via the driven portion (32) by the linear motion mechanism (33) is disposed between the first friction engagement element (11) and the second friction engagement element (12) and the axial direction (L) of the third friction engagement element (21) and the fourth friction engagement element (22) that are disposed on the second side (L2) in the axial direction with respect to the first friction engagement element and the second friction engagement element. The driven part (32) is moved to the first side (L1) in the axial direction by a linear motion mechanism (33), so that the first friction engagement element (11) and the second friction engagement element (12) are pressed by a pressing part (31) to bring the clutch mechanism (1) into an engaged state, and the pressing part (31) is released from pressing the third friction engagement element (21) and the fourth friction engagement element (22) to bring the brake mechanism (2) into a disengaged state. On the other hand, the driven part (32) is moved to the axial second side (L2) by the linear motion mechanism (33), so that the third friction engagement element (21) and the fourth friction engagement element (22) are pressed by the pressing part (31) to bring the brake mechanism (2) into an engaged state, and the pressing of the first friction engagement element (11) and the second friction engagement element (12) by the pressing part (31) is released to bring the clutch mechanism (1) into a disengaged state. Thus, the state of engagement of the clutch mechanism (1) and the brake mechanism (2) can be changed by the common pressing mechanism (3). Therefore, in the structure with the clutch mechanism (1) and the brake mechanism (2), the miniaturization of the jointing device (100) can be realized.

Wherein it is preferable that the first rotation member (81) has a first connection portion (8 a) connected to the first frictional engagement element (11),

The second rotating member (82) has a second connecting portion (8 b) connected to the second frictional engagement element (12),

The object rotation member (8T) has a third connection portion (8 c) connected to the third friction engagement element (21),

The non-rotating member (NR) has a fourth connecting portion (8 d) connected to the fourth frictional engagement element (22),

The first connecting portion (8 a) is disposed outside the first friction engagement element (11) in a radial direction (R) and at a position overlapping the first friction engagement element (11) when viewed in the radial direction of the radial direction (R),

The third connecting portion (8 c) is disposed on the outer side of the third friction engagement element (21) in the radial direction (R) and overlaps the third friction engagement element (21) when viewed in the radial direction,

The second connection portion (8 b) is disposed on the inner side of the radial direction (R) with respect to the second friction engagement element (12) and is disposed at a position overlapping the second friction engagement element (12) and the first connection portion (8 a) when viewed from the radial direction,

The fourth connecting portion (8 d) is disposed on the inner side of the radial direction (R) with respect to the fourth friction engagement element (22) and is overlapped with the fourth friction engagement element (22) and the third connecting portion (8 c) when viewed from the radial direction,

The linear motion mechanism (33) is disposed on the second side (L2) in the axial direction with respect to the second connecting portion (8 b), and is disposed on the inner side of the radial direction (R) with respect to the fourth connecting portion (8 d), and is disposed at a position overlapping the fourth connecting portion (8 d) when viewed in the radial direction.

According to this structure, the linear motion mechanism (33) is disposed on the second axial side (L2) with respect to the second connection portion (8 b) of the second rotating member (82). As a result, the dimension of the joint device (100) in the radial direction (R) can be reduced compared to a structure in which the linear motion mechanism (33) is arranged so as to overlap the second connecting portion (8 b) when viewed in the radial direction.

In addition, according to this structure, the linear motion mechanism (33) is disposed on the inner side of the fourth connecting portion (8 d) of the non-rotating member (NR) in the radial direction (R) and is disposed at a position overlapping the fourth connecting portion (8 d) when viewed in the radial direction of the radial direction (R). As a result, the dimension of the joint device (100) in the axial direction (L) can be reduced compared to a configuration in which the linear motion mechanism (33) is arranged so as to be offset in the axial direction (L) relative to the fourth connecting portion (8 d). Further, the linear motion mechanism (33) disposed inside the radial direction (R) with respect to the fourth connection portion (8 d) of the non-rotating member (NR) is easily supported by the non-rotating member (NR), so that the support structure of the linear motion mechanism (33) is easily simplified.

Further, the pressing portion (31) preferably includes: a first pressing portion (311) that presses the first friction engagement element (11) and the second friction engagement element (12) in the axial direction (L); and a second pressing portion (312) that presses the third friction engagement element (21) and the fourth friction engagement element (22) in the axial direction (L),

The first pressing portion (311) is supported in a state of being relatively movable in the axial direction (L) with respect to the first rotation member (81) or the second rotation member (82) and integrally rotatable with the first rotation member (81) or the second rotation member (82),

The second pressing portion (312) is supported in a state of being relatively movable in the axial direction (L) with respect to the non-rotating member (NR) and being restricted in relative rotation with respect to the non-rotating member (NR),

The first pressing portion (311) and the second pressing portion (312) are configured to be interlocked in the axial direction (L) in a relatively rotatable state,

The driven part (32) is connected to the second pressing part (312) so as to move integrally with the second pressing part in the axial direction (L).

According to this structure, the driven part (32) that moves in the axial direction (L) by the linear motion mechanism (33) is connected to the second pressing part (312) that is supported in a state in which the relative rotation to the non-rotating member (NR) is restricted so as to move integrally in the axial direction (L). Thus, the pressing mechanism (3) is simplified as compared with a structure in which the driven part (32) is connected to the first pressing part (311) so as to move integrally with the first pressing part (311) in the axial direction (L), and the first pressing part (311) is supported in a state of integrally rotating with the first rotating member (81) or the second rotating member (82).

Further, the linear motion mechanism (33) preferably includes: a screw shaft (331) rotatably supported with respect to the non-rotating member (NR); and a nut member (332) screwed with the screw shaft (331),

The nut member (332) is connected to the driven part (32) so as to move integrally with the driven part in the axial direction (L),

The screw shaft (331) is coaxially arranged with the first friction engagement element (11), the second friction engagement element (12), the third friction engagement element (21), and the fourth friction engagement element (22) and is arranged inside a radial direction (R).

According to this structure, a screw shaft (331) for moving the nut member (332) in the axial direction (L) is disposed inside the first friction engagement element (11), the second friction engagement element (12), the third friction engagement element (21), and the fourth friction engagement element (22) in the radial direction (R). Thus, the driving force for driving the screw shaft (331) to rotate is easily transmitted to the screw shaft (331) from the outside in the axial direction (L) with respect to the friction engagement elements (11, 12, 21, 22). Therefore, a structure is easily realized in which the pressing portion (31) arranged between the first friction engagement element (11) and the second friction engagement element (12) and the third friction engagement element (21) and the fourth friction engagement element (22) in the axial direction (L) can be moved in the axial direction (L) via the nut member (332) and the driven portion (32).

In addition, according to this structure, it is easy to arrange the screw shaft (331) of the linear motion mechanism (33) so as to overlap at least a part of the first friction engagement element (11), the second friction engagement element (12), the third friction engagement element (21), and the fourth friction engagement element (22) when viewed in the radial direction of the radial direction (R). As a result, the size of the joint device (100) in the axial direction (L) can be suppressed from being increased by arranging the linear motion mechanism (33).

In the structure in which the linear motion mechanism (33) has the screw shaft (331) and the nut member (332), preferably,

The joint device (100) further comprises a drive source (4) for driving the screw shaft (331) to rotate and a transmission mechanism (5) for transmitting power between the drive source (4) and the screw shaft (331),

The drive source (4) is disposed on a shaft different from the screw shaft (331),

An arrangement region in the axial direction (L) of the drive source (4) overlaps with an arrangement region in the axial direction (L) of the first rotary member (81),

The transmission mechanism (5) is arranged on the second axial side (L2) relative to the linear motion mechanism (33),

A first shaft member (10) disposed so as to extend from the first rotation member (81) to the first axial side (L1) is connected to the first rotation member (81) so as to rotate integrally therewith,

A second shaft member (20) disposed so as to extend from the second rotation member (82) to the first axial side (L1) is connected to the second rotation member (82) so as to rotate integrally therewith.

According to this configuration, the dimension of the joint device (100) in the axial direction (L) can be reduced compared with a configuration in which the drive source (4) and the first rotary member (81) are arranged coaxially and at positions offset in the axial direction (L).

Industrial applicability

The techniques of this disclosure can be used with an engagement device having a clutch mechanism and a brake mechanism.

Description of the reference numerals

100: Engagement device, 1: clutch mechanism, 11: first frictional engagement element, 12: second frictional engagement element, 2: brake mechanism, 21: third frictional engagement element, 22: fourth friction engagement element, 3: pressing mechanism, 31: pressing part, 32: driven part, 33: direct action mechanism, 81: first rotating member, 82: second rotation member, 8T: object rotation member, 10: first shaft member, 20: second shaft member, NR: non-rotating member, L: axial direction, L1: axial first side, L2: and an axial second side.

Claims (5)

1. An engagement device, comprising:

a clutch mechanism selectively engaging the first rotating member and the second rotating member; and

A brake mechanism that selectively engages a target rotating member that is either one of the first rotating member and the second rotating member with a non-rotating member, wherein,

The engagement device has: a pressing mechanism for changing the state of engagement of the clutch mechanism and the brake mechanism,

The direction along the rotation axis of the first rotation member is set as an axial direction, one side of the axial direction is set as an axial first side, the other side of the axial direction is set as an axial second side,

The clutch mechanism has: a first friction engagement element connected to the first rotating member so as to rotate integrally with the first rotating member; and a second friction engagement element connected to the second rotating member so as to rotate integrally with the second rotating member,

The first friction engagement element and the second friction engagement element are arranged to oppose each other in the axial direction and to be friction-engaged with each other by being pressed in the axial direction,

The brake mechanism has: a third friction engagement element connected to the object rotation member so as to rotate integrally with the object rotation member; and a fourth frictional engagement element fixed to the non-rotating member,

The third friction engagement element and the fourth friction engagement element are arranged in a manner opposed to each other in the axial direction at positions separated toward the axial second side with respect to the first friction engagement element and the second friction engagement element, and are frictionally engaged with each other by being pressed in the axial direction,

The pressing mechanism includes: a pressing portion disposed between the first and second friction engagement elements and the axial directions of the third and fourth friction engagement elements; a driven part connected to the pressing part in a manner of interlocking with the pressing part; and a linear motion mechanism for moving the driven part along the axial direction,

The first rotating member, the second rotating member, the first friction engagement element, the second friction engagement element, the third friction engagement element, and the fourth friction engagement element are arranged on a coaxial axis,

The clutch mechanism and the brake mechanism are selectively engaged according to the driven portion being moved to the axial first side or to the axial second side by the linear motion mechanism.

2. The engagement device according to claim 1, wherein,

The first rotating member has: a first connecting part connected with the first friction joint element,

The second rotating member has: a second connecting part connected with the second friction joint element,

The object rotation member has: a third connecting part connected with the third friction joint element,

The non-rotating member has: a fourth connecting part connected with the fourth friction joint element,

The first connecting portion is disposed radially outward of the first friction engagement element and overlaps the first friction engagement element when viewed in a radial direction along the radial direction,

The third connecting portion is disposed at a position outside the third friction engagement element in the radial direction and overlapping the third friction engagement element when viewed in the radial direction,

The second connecting portion is disposed on the inner side in the radial direction with respect to the second friction engagement element and overlaps the second friction engagement element and the first connecting portion when viewed in the radial direction,

The fourth connecting portion is disposed on the inner side in the radial direction with respect to the fourth frictional engagement element and overlaps the fourth frictional engagement element and the third connecting portion when viewed in the radial direction,

The linear motion mechanism is disposed on the second axial side with respect to the second connecting portion, and is disposed at a position that is on the inner side in the radial direction with respect to the fourth connecting portion and overlaps with the fourth connecting portion when viewed in the radial direction.

3. The engagement device according to claim 1 or 2, wherein,

The pressing portion has: a first pressing portion that presses the first friction engagement element and the second friction engagement element in the axial direction; and a second pressing portion pressing the third friction engagement element and the fourth friction engagement element in the axial direction,

The first pressing portion is supported in a state of being relatively movable in the axial direction with respect to the first rotating member or the second rotating member and integrally rotated with the first rotating member or the second rotating member,

The second pressing portion is supported in a state of being relatively movable in the axial direction with respect to the non-rotating member and being restricted in relative rotation with respect to the non-rotating member,

The first pressing portion and the second pressing portion are configured to interlock in the axial direction in a relatively rotatable state,

The driven portion is connected to the second pressing portion so as to move integrally with the second pressing portion in the axial direction.

4. The joining device according to any one of claim 1 to 3, wherein,

The linear motion mechanism includes: a screw shaft rotatably supported with respect to the non-rotating member; and a nut member screwed with the screw shaft,

The nut member is connected to the driven portion so as to move integrally with the driven portion in the axial direction,

The screw shaft is disposed coaxially with the first, second, third, and fourth friction engagement elements and radially inward of the first, second, third, and fourth friction engagement elements.

5. The engagement device of claim 4, wherein,

The engagement device further has a drive source for driving the screw shaft to rotate and a transmission mechanism for transmitting power between the drive source and the screw shaft,

The drive source and the screw shaft are arranged on different shafts,

An arrangement region in the axial direction of the drive source overlaps with an arrangement region in the axial direction of the first rotary member,

The transmission mechanism is arranged on the second axial side relative to the linear motion mechanism,

A first shaft member disposed so as to extend from the first rotating member to the first axial side is connected to the first rotating member so as to rotate integrally with the first rotating member,

A second shaft member disposed so as to extend from the second rotating member toward the first axial side is connected to the second rotating member so as to rotate integrally with the second rotating member.