Friction engagement device and vehicle drive device

Abstract

To lubricate a friction material properly and improve controllability of a frictional engagement device.SOLUTION: A first frictional material support part (41A) is provided with a first oil passage (81) allowing an oil reservoir part (56) and a frictional material arrangement area (P) to communicate with each other. A second oil passage (82) which allows the oil reservoir part (56) and a space other than the friction material arrangement area (P) to communicate with each other is provided in at least one of a first support member (41) and a first pressing member (45). A second opening (82a) which is open to the oil reservoir part (56) side in the second oil passage (82) is disposed spaced apart from a first opening (81a), which is open to the oil reservoir part (56) side in the first oil passage (81), to the inner side in a radial direction (R).SELECTED DRAWING: Figure 4

Description

[Technical field]

[0001] The present invention relates to a friction engagement device and a vehicle drive system. [Background technology]

[0002] A stationary cylinder type friction engagement device is used, which includes a first pressing member that rotates integrally with a rotating member and a second pressing member that is supported by a non-rotating member and rotates relative to the first pressing member, as a pressing member that presses a plurality of friction materials against each other. One example of such a stationary cylinder type friction engagement device is disclosed in Japanese Patent Laid-Open Publication No. 10-122260 (Patent Document 1).

[0003] In the friction engagement device of Patent Document 1, it is conceivable to lubricate the friction material (friction material disk 52 and separator plate 51) with oil supplied from the radial inside. However, the friction engagement device of Patent Document 1 is structured such that oil accumulates in an area surrounded by the first support member (hub 53) and a retaining member (spring retainer 58a) for retaining the biasing member (return spring 58). Since the first support member is a rotating member, centrifugal oil pressure is generated in the accumulated oil during rotation of the first support member, and may act to push back the pressing member (pressing member 33) separately from the biasing member. Such centrifugal oil pressure varies widely, which causes a problem of poor controllability of the friction engagement device. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Publication No. 10-122260 Summary of the Invention [Problem to be solved by the invention]

[0005] Therefore, it is desirable to improve the controllability of the friction engagement device while properly lubricating the friction material. [Means for solving the problem]

[0006] The friction engagement device according to the present disclosure is a first support member including a first friction material support portion that supports a first friction material and is rotatably supported; a second support member including a second friction material support portion that supports a second friction material, the second support member being supported rotatably independent of the first support member; a first pressing member that rotates integrally with the first support member, is supported by the first support member so as to be freely movable in the axial direction, and presses the first friction material and the second friction material in the axial direction so as to press the first friction material and the second friction material against each other; a second pressing member that is supported on the non-rotating member so as to be movable in the axial direction and presses the first pressing member in the axial direction while being rotatable relative to the first pressing member; a pressing drive unit that drives the second pressing member in the axial direction, The first friction material support portion is formed in a cylindrical shape along the axial direction, the second friction material support portion is disposed radially outward of the first friction material support portion and coaxially with the first friction material support portion, the first friction material is connected to the first friction material support portion so as to rotate integrally with the first friction material, the second friction material is connected to the second friction material support portion so as to rotate integrally with the second friction material, the first friction material and the second friction material are disposed between the first friction material support portion and the second friction material support portion in the radial direction so as to face each other in the axial direction, The first support member further includes a radially extending portion extending inward in the radial direction from the first friction material support portion, the first pressing member has a sliding portion that slides along an inner circumferential surface of the first friction material support portion, an oil reservoir is formed in a region surrounded by an inner circumferential surface of the first friction material support portion, the radially extending portion, and the sliding portion; an oil supply unit that supplies oil to the oil reservoir; a first oil passage is provided in the first friction material support portion, the first oil passage communicating with the oil reservoir portion and a friction material arrangement area in which the first friction material and the second friction material are arranged; At least one of the first support member and the first pressing member is provided with a second oil passage that communicates the oil reservoir with a space other than the friction material arrangement area, An opening in the first oil passage that opens toward the oil reservoir is designated as a first opening, and an opening in the second oil passage that opens toward the oil reservoir is designated as a second opening, and the second opening is positioned radially inward and spaced apart from the first opening.

[0007] According to this configuration, the oil supplied from the oil supply unit and stored in the oil reservoir can be supplied to the friction material arrangement area via the first oil passage. Therefore, the first friction material and the second friction material can be appropriately lubricated. In addition, the oil stored in the oil reservoir that is radially inward of the second opening can be discharged to the outside of the oil reservoir via the second oil passage. This makes it possible to regulate the amount of oil stored in the oil reservoir so that it does not become too large. Therefore, the effect of the centrifugal oil pressure caused by the oil stored in the oil reservoir on the first pressing member can be reduced, and as a result, the controllability of the friction engagement device can be improved.

[0008] Further features and advantages of the techniques disclosed herein will become more apparent from the following description of exemplary and non-limiting embodiments, which proceeds with reference to the drawings. [Brief description of the drawings]

[0009] [Figure 1] 1 is a skeleton diagram of a vehicle drive device according to an embodiment of the present invention; [Diagram 2] Cross-sectional view of a vehicle drive device [Diagram 3] Enlarged cross-sectional view of a vehicle drive device [Figure 4] Enlarged cross-sectional view of a vehicle drive device [Diagram 5] FIG. 1 is a schematic diagram of a vehicle drive device viewed from an axial direction; DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0010] An embodiment of a vehicle drive device equipped with a transmission including a friction engagement device will be described with reference to the drawings. As shown in Figs. 1 and 2, a vehicle drive device 100 of this embodiment generally includes a transmission 1, a rotating electric machine 2, a differential gear mechanism 3, and a pair of output members 4 each of which is drivingly connected to wheels W. The transmission 1 also includes a first shaft member 10 including a first gear 12 and a second gear 14, a second shaft member 20 supporting a third gear 22 and a fourth gear 24 and including an output gear 25, a meshing engagement device 30, and a friction engagement device 40. These are housed in a case (drive device case) 6. A part of the output member 4 is exposed to the outside of the case 6.

[0011] Here, the term "rotating electric machine" is used as a concept that includes motors, generators, and motor-generators that function as both a motor and a generator as necessary.

[0012] Moreover, "driving connection" refers to a state in which two rotating elements are connected so as to be able to transmit a driving force. This concept includes a state in which two rotating elements are connected so as to rotate integrally, and a state in which two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members. Such transmission members include various members (shafts, gear mechanisms, belts, chains, etc.) that transmit rotation at the same speed or at a variable speed, and may also include engagement devices (friction engagement devices, meshing engagement devices, etc.) that selectively transmit rotation and driving force.

[0013] The rotating electric machine 2 and the first shaft member 10 are disposed on the first axis X1. The second shaft member 20, the meshing type engagement device 30, and the friction engagement device 40 are disposed on the second axis X2. The differential gear mechanism 3 and the output member 4 are disposed on the third axis X3. The first axis X1, the second axis X2, and the third axis X3 are parallel axes different from one another, and the direction parallel to these axes will be referred to as the "axial direction L" below. In addition, one side of the axial direction L (the left side in FIG. 1 in this example) will be referred to as the axial first side L1, and the other side of the axial direction L (the right side in FIG. 1 in this example) will be referred to as the axial second side L2. In addition, in the following, the state viewed along the axial direction L will be referred to as the "axial view".

[0014] The rotating electric machine 2 includes a stator 2A fixed to a case 6, and a rotor 2B rotatably supported radially inside the stator 2A. The rotating electric machine 2 receives power from an electric storage device (not shown) for power running, or supplies electric power generated by the inertial force of the vehicle or the like to the electric storage device for storage. The rotor 2B is connected to a rotor shaft 2C so as to rotate integrally therewith. The rotor shaft 2C is supported rotatably relative to the case 6 at two points in the axial direction L by rotor bearings 91 (see FIG. 2). The rotor shaft 2C is connected to a first shaft member 10 of the transmission 1 at an end on a first axial side L1 so as to rotate integrally therewith.

[0015] The transmission 1 changes the speed of rotation from the rotating electric machine 2 side and transmits it to the wheels W side. The transmission 1 of this embodiment includes a first shaft member 10 including a first gear 12 and a second gear 14, a second shaft member 20 supporting a third gear 22 and a fourth gear 24 and including an output gear 25, a meshing engagement device 30, and a friction engagement device 40. The meshing engagement device 30 selectively couples either the third gear 22 or the fourth gear 24 to the second shaft member 20, so that the transmission 1 can change the speed of rotation from the rotating electric machine 2 side in two stages and transmit it to the wheels W side. The friction engagement device 40 is engaged when the meshing engagement device 30 couples the fourth gear 24 to the second shaft member 20, thereby synchronizing the rotational speeds of the fourth gear 24 and the second shaft member 20.

[0016] In this embodiment, the meshing engagement device 30 is disposed between the third gear 22 and the fourth gear 24 in the axial direction L. The friction engagement device 40 is disposed on a first axial side L1 with respect to the third gear 22 and the fourth gear 24. The output gear 25 is disposed on a second axial side L2 with respect to the third gear 22 and the fourth gear 24.

[0017] The differential gear mechanism 3 includes a differential input gear 3A, and distributes and transmits the rotation and torque from the transmission 1 side, which is input to the differential input gear 3A, to a pair of output members 4. Each of the pair of output members 4 is drivingly connected to wheels W. In this manner, the rotation transmitted from the rotating electric machine 2 side is transmitted to the differential gear mechanism 3 via the transmission 1, and is further distributed to the pair of output members 4 by the differential gear mechanism 3, and is further transmitted to the pair of wheels W. In this manner, the vehicle drive device 100 can transmit the torque of the rotating electric machine 2 to the wheels W to run the vehicle.

[0018] As shown in FIG. 2, the case 6 includes a first case portion 6A, a second case portion 6B, and a third case portion 6C. The first case portion 6A is joined to the second case portion 6B from the first axial side L1. The first case portion 6A houses the transmission 1 and the differential gear mechanism 3. The first case portion 6A includes a first peripheral wall portion 6Aa that covers the radial outside of the transmission 1 and the differential gear mechanism 3, and a first support wall portion 6Ab that covers the first axial side L1 of the transmission 1 and the differential gear mechanism 3. The second case portion 6B houses the rotating electric machine 2. The second case portion 6B includes a second peripheral wall portion 6Ba that covers the radial outside of the rotating electric machine 2, and a second support wall portion 6Bb that covers the first axial side L1 of the rotating electric machine 2. In the illustrated example, the transmission 1 and a part of the differential gear mechanism 3 are also housed in the second case portion 6B. The third case portion 6C separates an accommodation space for the transmission 1 and the differential gear mechanism 3 from an accommodation space for the rotating electric machine 2 inside the first case portion 6A and the second case portion 6B.

[0019] As shown in Figures 2 and 3, the transmission 1 includes a first shaft member 10 having a first gear 12 and a second gear 14, a second shaft member 20 supporting a third gear 22 and a fourth gear 24 and having an output gear 25, a meshing engagement device 30, and a friction engagement device 40.

[0020] The first shaft member 10 functions as an input member (speed change input member) of the transmission 1. The first shaft member 10 is disposed on the first axial side L1 with respect to the rotor shaft 2C. The first shaft member 10 is connected to the rotor shaft 2C so as to rotate integrally with the rotor shaft 2C with its end on the second axial side L2 inserted into the rotor shaft 2C. The first shaft member 10 is rotatably supported with respect to the case 6 by the first bearing 92 at two points in the axial direction L. The first shaft member 10 is rotatably supported with respect to the first case portion 6A on the first axial side L1, and is rotatably supported with respect to the third case portion 6C on the second axial side L2.

[0021] In this embodiment, the first support wall 6Ab of the first case portion 6A is formed with a first cylindrical support portion 61 that protrudes toward the second axial side L2 (see FIG. 3). One of the pair of first bearings 92 is fitted into the first cylindrical support portion 61.

[0022] The first gear 12 and the second gear 14 are connected to the first shaft member 10 so as to rotate integrally with the first shaft member 10. In this embodiment, the first gear 12 is formed on the outer circumferential surface of the first shaft member 10. The first gear 12 meshes with the third gear 22. The second gear 14 is formed on the outer circumferential surface of a second gear forming member 13 which is connected to the first shaft member 10 so as to rotate integrally with the first shaft member 10. The second gear 14 meshes with the fourth gear 24. The second gear 14 is disposed at a distance from the first gear 12 on the first axial side L1.

[0023] The second shaft member 20 is disposed in parallel with the first shaft member 10. The arrangement area of ​​the second shaft member 20 in the axial direction L overlaps with the arrangement area of ​​the first shaft member 10 in the axial direction L. In this embodiment, the arrangement area of ​​the second shaft member 20 in the axial direction L is included in the arrangement area of ​​the first shaft member 10 in the axial direction L. In addition, the second shaft member 20 is rotatably supported with respect to the case 6 by the second bearing 93 at two points in the axial direction L. The second shaft member 20 is rotatably supported with respect to the first case portion 6A on the first axial side L1, and is rotatably supported with respect to the third case portion 6C on the second axial side L2.

[0024] In this embodiment, the first support wall 6Ab of the first case 6A is formed with a second cylindrical support portion 62 that protrudes toward the second axial side L2 (see FIG. 3). One of the pair of second bearings 93 is fitted into the second cylindrical support portion 62.

[0025] The third gear 22 and the fourth gear 24 are supported by the second shaft member 20 in a state in which they can rotate relative to the second shaft member 20. In this embodiment, the third gear 22 is formed on an outer peripheral surface of a third gear forming member 21 that is rotatably supported by the second shaft member 20 via a bearing. The third gear 22 meshes with the first gear 12. The fourth gear 24 is formed on an outer peripheral surface of a fourth gear forming member 23 that is rotatably supported by the second shaft member 20 via a bearing. The fourth gear 24 meshes with the second gear 14. In the illustrated example, needle roller bearings are used as bearings that support the third gear forming member 21 and the fourth gear forming member 23.

[0026] In this embodiment, the first gear 12 has a smaller diameter than the second gear 14, and the third gear 22 has a larger diameter than the fourth gear 24 correspondingly.

[0027] The output gear 25 is connected to the second shaft member 20 so as to rotate integrally with the second shaft member 20. In this embodiment, the output gear 25 is formed on the outer circumferential surface of the second shaft member 20. The output gear 25 is formed at a position adjacent to the second axial side L2 of the third gear forming member 21 on which the third gear 22 is formed. The output gear 25 functions as an output member (transmission output member) of the transmission 1. The output gear 25 meshes with the differential input gear 3A of the differential gear mechanism 3.

[0028] As shown in FIG. 3, the meshing engagement device 30 includes a first engagement portion 31, a second engagement portion 32, a third engagement portion 33, and a switching member .

[0029] The first engagement portion 31 is connected to the second shaft member 20 so as to rotate integrally with the second shaft member 20. In this embodiment, the first engagement portion 31 is formed on the outer circumferential surface of a connecting member 31A connected to the second shaft member 20 so as to rotate integrally with the second shaft member 20. The first engagement portion 31 is an externally toothed engagement portion.

[0030] The second engagement portion 32 is connected to the third gear 22 so as to rotate integrally with the third gear 22. In this embodiment, the second engagement portion 32 is formed on a third gear forming member 21 having the third gear 22 formed on its outer circumferential surface. The second engagement portion 32 is disposed adjacent to the first engagement portion 31 on the second axial side L2. The second engagement portion 32 is an externally toothed engagement portion having the same diameter and pitch as the first engagement portion 31.

[0031] The third engagement portion 33 is connected to the fourth gear 24 so as to rotate integrally with the fourth gear 24. In this embodiment, the third engagement portion 33 is formed on a fourth gear forming member 23 having the fourth gear 24 formed on its outer circumferential surface. The third engagement portion 33 is disposed adjacent to the first engagement portion 31 on the first axial side L1. The third engagement portion 33 is an engagement portion with external teeth having the same diameter and pitch as the first engagement portion 31 and the second engagement portion 32.

[0032] The switching member 35 is formed in a cylindrical shape covering the outside of the connecting member 31A in the radial direction R. Then, on the inner peripheral surface of the switching member 35, internal tooth engaging portions are formed which mesh with the first engaging portion 31, the second engaging portion 32, and the third engaging portion 33 of the external teeth, respectively. The internal teeth of the switching member 35 and the external teeth of the first engaging portion 31, the second engaging portion 32, and the third engaging portion 33 engage with each other so as to be relatively movable in the axial direction L and relatively unrotatable in the circumferential direction.

[0033] The meshing engagement device 30 connects the third gear 22 and the second shaft member 20 so as to rotate integrally with each other when the switching member 35 is engaged with both the first engagement portion 31 and the second engagement portion 32. The meshing engagement device 30 also connects the fourth gear 24 and the second shaft member 20 so as to rotate integrally with each other when the switching member 35 is engaged with both the first engagement portion 31 and the third engagement portion 33. In this manner, the meshing engagement device 30 selectively connects either the third gear 22 or the fourth gear 24 to the second shaft member 20. When the third gear 22 and the second shaft member 20 are connected so as to rotate integrally with each other, the driving force of the rotating electric machine 2 is transmitted to the wheel W side via the first gear 12 and the third gear 22 which mesh with each other. On the other hand, when the fourth gear 24 and the second shaft member 20 are connected so as to rotate integrally, the driving force of the rotating motor 2 is transmitted to the wheel W side via the second gear 14 and the fourth gear 24 which mesh with each other.

[0034] When the switching member 35 is engaged with the first engagement portion 31 but not engaged with both the second engagement portion 32 and the third engagement portion 33, the meshing engagement device 30 is in a disengaged state (disengaged state). When the meshing engagement device 30 is in a disengaged state and the friction engagement device 40 is also in a disengaged state, the transmission 1 is in a neutral state in which it does not transmit driving force.

[0035] As shown in Figures 3 and 4, the friction engagement device 40 includes a first support member 41, a second support member 42, a first friction material 43, a second friction material 44, a first pressing member 45, a second pressing member 46, and a pressing drive unit 49.

[0036] The first support member 41 is a member for supporting the first friction material 43, and is supported rotatably. The first support member 41 includes a first friction material support portion 41A, a first radial extension portion 41B, and a shaft connection portion 41C. These are integrally formed. The first friction material support portion 41A is formed in a cylindrical shape along the axial direction L, and supports the first friction material 43 from the inside in the radial direction R. External teeth are formed on the outer circumferential surface of the first friction material support portion 41A. The first radial extension portion 41B extends from the first friction material support portion 41A toward the inside in the radial direction R. In this embodiment, the first radial extension portion 41B extends from the end of the axial second side L2 of the first friction material support portion 41A toward the inside in the radial direction R.

[0037] The shaft connecting portion 41C extends in the axial direction L from a lower end of the first radially extending portion 41B. The shaft connecting portion 41C is formed in a cylindrical shape along the axial direction L, and is extrapolated onto the second shaft member 20. The shaft connecting portion 41C is connected to the second shaft member 20 so as to rotate integrally therewith. As a result, the entire first support member 41 is connected to the second shaft member 20 so as to rotate integrally therewith. Of the portions constituting the first support member 41, the first radially extending portion 41B is disposed on the second axial side L2 with respect to the first pressing member 45.

[0038] The second support member 42 is a member for supporting the second friction material 44, and is supported rotatably independent of the first support member 41. The second support member 42 includes a second friction material support portion 42A and a second radially extending portion 42B. These are integrally formed. The second friction material support portion 42A is formed in a cylindrical shape along the axial direction L, and supports the second friction material 44 from the outside in the radial direction R. Internal teeth are formed on the inner peripheral surface of the second friction material support portion 42A. The second friction material support portion 42A is disposed coaxially with the first friction material support portion 41A, outside the radial direction R of the first friction material support portion 41A.

[0039] The second radial extension portion 42B extends from the second friction material support portion 42A toward the inside in the radial direction R. In this embodiment, the second radial extension portion 42B extends from the end of the second axial side L2 of the second friction material support portion 42A toward the inside in the radial direction R. The second radial extension portion 42B is disposed adjacent to the second axial side L2 with respect to the first radial extension portion 41B. Also, the second radial extension portion 42B is disposed adjacent to the first axial side L1 with respect to the fourth gear forming member 23. The second radial extension portion 42B is connected to the fourth gear forming member 23 on which the fourth gear 24 is formed so as to rotate integrally. As a result, the entire second support member 42 is connected to the fourth gear 24 so as to rotate integrally.

[0040] A plurality of first friction materials 43 are arranged side by side in the axial direction L. Internal teeth that mesh with the external teeth of the first friction material support portion 41A are formed on the inner peripheral surface of each first friction material 43. The first friction material 43 is supported on the outer peripheral surface of the first friction material support portion 41A so as to be movable relative to the first friction material support portion 41A in the axial direction L but not rotatable relative to the first friction material support portion 41A in the circumferential direction.

[0041] A plurality of second friction materials 44 are arranged side by side in the axial direction L. The first friction materials 43 and the second friction materials 44 are arranged alternately in the axial direction L and opposed to each other in the axial direction L. External teeth that mesh with the internal teeth of the second friction material support portion 42A are formed on the outer circumferential surface of each second friction material 44. The second friction material 44 is supported on the inner circumferential surface of the second friction material support portion 42A so as to be movable relative to the second friction material support portion 42A in the axial direction L and so as not to be rotatable relative to the second friction material support portion 42A in the circumferential direction.

[0042] The first pressing member 45 cooperates with the second pressing member 46 to press the first friction material 43 and the second friction material 44 against each other. The first pressing member 45 is disposed on the first axial side L1 with respect to the first friction material 43 and the second friction material 44. The first pressing member 45 has internal teeth that mesh with the external teeth of the first friction material support portion 41A, and is supported so as to be movable relative to the first friction material support portion 41A in the axial direction L and not rotatable relative to the first friction material support portion 41A in the circumferential direction. In this way, the first pressing member 45 rotates integrally with the first support member 41 and is supported so as to be movable in the axial direction L with respect to the first support member 41. When the first pressing member 45 is driven in the axial direction L by the pressing drive portion 49 via the second pressing member 46, it presses the first friction material 43 and the second friction material 44 from the first axial side L1 to press the first friction material 43 and the second friction material 44 against each other.

[0043] The first pressing member 45 includes a sliding portion 45A and a pressing portion 45B. The sliding portion 45A is disposed inward of the first frictional material support portion 41A in the radial direction R, and slides along the inner circumferential surface of the first frictional material support portion 41A. In this embodiment, a seal member 51 is disposed between a surface (sliding facing surface) of the sliding portion 45A facing the inner circumferential surface of the first frictional material support portion 41A and the inner circumferential surface of the first frictional material support portion 41A. The sliding portion 45A is formed so as to extend along the radial direction R. In this example, the sliding portion 45A is formed along the radial direction R so as to span the first frictional material support portion 41A and the shaft connecting portion 41C of the first support member 41. The sliding portion 45A is biased toward the first axial side L1 by a biasing member 48 held by a holding member 47. The biasing member 48 biases the first pressing member 45 in the axial direction L in the direction opposite to the side where the first friction material 43 and the second friction material 44 are pressed against each other. In this embodiment, a return spring is used as such a biasing member 48.

[0044] The pressing portion 45B extends outward in the radial direction R from the sliding portion 45A. The pressing portion 45B is disposed outward in the radial direction R from the first friction material support portion 41A. The pressing portion 45B is formed to have a portion disposed between the first friction material support portion 41A and the second friction material support portion 42A in the radial direction R. The pressing portion 45B moves along the axial direction L integrally with the sliding portion 45A to press the first friction material 43 and the second friction material 44.

[0045] The second pressing member 46 cooperates with the first pressing member 45 to press the first friction material 43 and the second friction material 44 against each other. The second pressing member 46 is disposed on the first axial side L1 with respect to the first pressing member 45. In this embodiment, the second pressing member 46 is disposed adjacent to the first pressing member 45 with a thrust bearing 95 interposed therebetween. The second pressing member 46 is supported on the case 6 so as to be movable in the axial direction L. The first support wall 6Ab of the first case portion 6A is formed with a third cylindrical support portion 63 that is cylindrical and protrudes to the second axial side L2. The third cylindrical support portion 63 is formed concentrically with the second cylindrical support portion 62 and has a larger diameter than the second cylindrical support portion 62. The second pressing member 46 is disposed in an annular space between the second cylindrical support portion 62 and the third cylindrical support portion 63 in the radial direction R.

[0046] The second pressing member 46 slides along the inner peripheral surface of the third cylindrical support portion 63 and the outer peripheral surface of the second cylindrical support portion 62. In this embodiment, a seal member 52 is disposed between a surface of the second pressing member 46 facing the inner peripheral surface of the third cylindrical support portion 63 and the inner peripheral surface of the third cylindrical support portion 63. Also, a seal member 53 is disposed between a surface of the second pressing member 46 facing the outer peripheral surface of the second cylindrical support portion 62 and the outer peripheral surface of the second cylindrical support portion 62. The second pressing member 46 is supported in a non-rotating state so as to be movable in the axial direction L.

[0047] The pressing drive unit 49 drives the second pressing member 46 in the axial direction L. The pressing drive unit 49 of this embodiment includes a hydraulic chamber 49A and a hydraulic oil supply unit 49B. The hydraulic chamber 49A is a space for applying hydraulic pressure to the second pressing member 46. In this embodiment, the hydraulic chamber 49A is formed in a space surrounded by the second cylindrical support portion 62, the third cylindrical support portion 63, the first support wall portion 6Ab, and the second pressing member 46. The hydraulic oil supply unit 49B is provided so as to communicate with the hydraulic chamber 49A, and supplies oil (hydraulic oil) to the hydraulic chamber 49A. In this embodiment, the hydraulic oil supply unit 49B constitutes an "oil supply unit that supplies oil to the hydraulic chamber." The hydraulic chamber 49A and the hydraulic oil supply unit 49B are formed in the case 6 (the first case portion 6A in this example).

[0048] When oil of a predetermined hydraulic pressure is supplied from the hydraulic oil supply unit 49B to the hydraulic chamber 49A, the second pressing member 46 moves to the second axial side L2 by the hydraulic pressure. Then, the second pressing member 46 presses the first pressing member 45 from the first axial side L1 while being rotatable relative to the first pressing member 45 via the thrust bearing 95. As a result, the second pressing member 46 and the first pressing member 45 work together to press the first friction material 43 and the second friction material 44 to the second axial side L2, and the first friction material 43 and the second friction material 44 are pressed against each other.

[0049] In this manner, the friction engagement device 40 includes the first support member 41 which includes the first friction material support portion 41A which supports the first friction material 43 and is rotatably supported, the second support member 42 which includes the second friction material support portion 42A which supports the second friction material 44 and is rotatably supported independently of the first support member 41, a first pressing member 45 which rotates integrally with the first support member 41 and is supported so as to be movable in the axial direction L relative to the first support member 41 and presses the first friction material 43 and the second friction material 44 in the axial direction L so as to press the first friction material 43 and the second friction material 44 against each other, a second pressing member 46 which is supported so as to be movable in the axial direction L relative to the case 6 and presses the first pressing member 45 in the axial direction L while being rotatable relative to the first pressing member 45, and a pressing drive unit 49 which drives the second pressing member 46 in the axial direction L.

[0050] According to this configuration, the friction engagement device 40 does not include a single pressing member, but includes a first pressing member 45 and a second pressing member 46 which rotate relatively to each other, and the second pressing member 46 which is driven in the axial direction L by a pressing drive unit 49 is supported so as to be movable in the axial direction L with respect to the case 6 which is a non-rotating member. As a result, the hydraulic oil for driving the second pressing member 46 does not rotate and centrifugal hydraulic pressure is not applied, thereby improving the controllability of the friction engagement device 40.

[0051] In relation to the friction engagement device 40 being provided with the first pressing member 45 and the second pressing member 46 which rotate relatively to each other, the first radial extending portion 41B of the first support member 41 is connected to the second shaft member 20 so as to rotate integrally with the second shaft member 20 on the second axial side L2 further than the second pressing member 46. In addition, the second radial extending portion 42B of the second support member 42 is connected to the fourth gear 24 so as to rotate integrally with the fourth gear 24 on the second axial side L2 further than the first radial extending portion 41B.

[0052] In this way, the first support member 41 further includes a first radial extending portion 41B extending inward in the radial direction R from the first friction material support portion 41A, the first friction material support portion 41A is formed in a cylindrical shape along the axial direction L, and the first radial extending portion 41B is arranged on the second axial side L2 relative to the first pressing member 45, and the second support member 42 further includes a second radial extending portion 42B extending inward in the radial direction R from the second friction material support portion 42A, the second friction material support portion 42A is formed in a cylindrical shape along the axial direction L, and the second radial extending portion 42B is arranged on the second axial side L2 relative to the first radial extending portion 41B.

[0053] According to this configuration, both the connection between the first support member 41 and the second shaft member 20 and the connection between the second support member 42 and the fourth gear 24 can be performed on the second axial side L2 with respect to the first pressing member 45. Therefore, both the first support member 41 and the second support member 42 can be arranged so as not to intersect with the transmission path of the pressing force of the first pressing member 45 and the second pressing member 46 in the axial direction L, and the device configuration can be simplified.

[0054] The second pressing member 46 is arranged concentrically with the second bearing 93 supporting the end of the second shaft member 20 on the first axial side L1 and on the outside of the second bearing 93 in the radial direction R. The second pressing member 46 is arranged with the first bearing 92 supporting the end of the first shaft member 10 on the first axial side L1 in a state in which their outer peripheries face each other. Thus, the second pressing member 46 is arranged on the outside of the second bearing 93 in the radial direction R, and a part of the second pressing member 46 in the circumferential direction is arranged between the first bearing 92 and the second bearing 93. In this embodiment, the arrangement area D3 of the second pressing member 46 in the axial direction L overlaps with both the arrangement area D1 of the first bearing 92 in the axial direction L and the arrangement area D2 of the second bearing 93 in the axial direction L. The term "overlap" is a concept that includes not only the case where the entirety overlaps, but also the case where parts overlap each other.

[0055] Here, the arrangement area D1 of the first bearing 92 in the axial direction L represents the maximum occupied range of the outer ring and the inner ring of the first bearing 92 in the axial direction L. When the arrangement areas of the outer ring and the inner ring are the same, the area is the arrangement area D1. When the arrangement areas of the outer ring and the inner ring are different, and one arrangement area includes the other arrangement area, the arrangement area that includes the other is the arrangement area D1. When the arrangement areas of the outer ring and the inner ring are different, and one arrangement area and the other arrangement area are not in an inclusion relationship, the area from the end of the axial first side L1 located on the axial first side L1 to the end of the axial second side L2 located on the axial second side L2 is the arrangement area D1. The same applies to the arrangement area D2 in the axial direction L of the second bearing 93.

[0056] In this way, the second pressing member 46 is radially outwardly disposed relative to the second bearing 93, with a portion of it in the circumferential direction being disposed between the first bearing 92 and the second bearing 93, and the arrangement area D3 in the axial direction L of the second pressing member 46 overlaps with both the arrangement area D1 in the axial direction L of the first bearing 92 and the arrangement area D2 in the axial direction L of the second bearing 93.

[0057] According to this configuration, the arrangement area D3 in the axial direction L of the second pressing member 46 overlaps with both the arrangement area D1 in the axial direction L of the first bearing 92 and the arrangement area D2 in the axial direction L of the second bearing 93, making it easy to keep the axial dimension of the transmission 1 small. While the friction engagement device 40 is configured to include the first pressing member 45 and the second pressing member 46 to improve controllability, the second pressing member 46 can be disposed by utilizing the space between the first bearing 92 and the second bearing 93, thereby preventing the device from becoming large in size as a whole.

[0058] Note that while the first bearing 92 and the second bearing 93 are fixed to the case 6, the second pressing member 46 is movable in the axial direction L. For this reason, the arrangement area D3 of the second pressing member 46 in the axial direction L represents the maximum movable range of the second pressing member 46 in the axial direction L. In this embodiment, the arrangement area D3 of the second pressing member 46 in the axial direction L entirely overlaps with the arrangement area D1 of the first bearing 92 in the axial direction L. In addition, the arrangement area D3 of the second pressing member 46 in the axial direction L overlaps with the arrangement area D2 of the second bearing 93 in the axial direction L except for a part of the first axial side L1.

[0059] The first bearing 92 is disposed such that a portion of its circumferential direction is located inward in the radial direction R from the second friction material support portion 42A. As shown in Fig. 5, the first bearing 92 is disposed such that the first friction material 43 and the second friction material 44 overlap with each other when viewed in the axial direction. In this embodiment, the first bearing 92 is disposed such that the outer circumferential portions of the first friction material 43 and the second friction material 44 partially overlap with each other.

[0060] The vehicle drive device 100 includes a structure (hereinafter, simply referred to as a "lubrication structure") for lubricating and cooling the first friction material 43 and the second friction material 44. The lubrication structure is configured by utilizing an oil passage formed inside the second shaft member 20 that supports the friction engagement device 40. In this embodiment, an axial oil passage 20a and a radial oil passage 20b are formed inside the second shaft member 20. The axial oil passage 20a is formed linearly along the axial direction L in the center of the second shaft member 20. The radial oil passage 20b is formed so as to extend from the axial oil passage 20a along the radial direction R and open to the outer circumferential surface of the second shaft member 20. The radial oil passage 20b is provided at a plurality of locations in the axial direction L. In this example, oil that has passed through the radial oil passage 20b provided at a position overlapping with the arrangement region of the friction engagement device 40 in the axial direction L among the plurality of radial oil passages 20b is supplied to the friction engagement device 40.

[0061] A lubricant supply unit 55 is formed in the case 6 (first case portion 6A in this example) so as to communicate with an opening of the axial oil passage 20a on the first axial side L1. Oil (hereinafter referred to as "lubricant") supplied from the lubricant supply unit 55 is supplied to the inside of the friction engagement device 40 in the radial direction R through the axial oil passage 20a in the second shaft member 20. The lubricant is then further supplied to the friction engagement device 40 through a specific radial oil passage 20b.

[0062] In this embodiment, a communication oil passage 41d is formed in the shaft connecting portion 41C of the first support member 41, which communicates the inner peripheral surface with the outer peripheral surface. This communication oil passage 41d is provided so as to communicate with the radial oil passage 20b. Therefore, the lubricating oil supplied from the radial oil passage 20b is further supplied through the communication oil passage 41d to a space (oil reservoir 56) on the first friction material support portion 41A side, which is located outside in the radial direction R. Here, the oil reservoir 56 is a portion where the lubricating oil is accumulated, which is formed in an area surrounded by the inner peripheral surface of the first friction material support portion 41A, the first radial extension portion 41B, and the sliding portion 45A. Since the first support member 41 rotates together with the second shaft member 20, the lubricating oil accumulates on the inner peripheral surface side of the first friction material support portion 41A in the oil reservoir 56 due to centrifugal hydraulic pressure. In this embodiment, the lubricating oil supply portion 55, the axial oil passage 20a, the radial oil passage 20b, and the communicating oil passage 41d constitute an "oil supply portion that supplies oil to the oil reservoir."

[0063] A first oil passage 81 is provided in the first friction material support portion 41A of the first support member 41. The first oil passage 81 is provided so as to communicate between the inner peripheral surface and the outer peripheral surface of the first friction material support portion 41A, and communicates between the oil reservoir portion 56 and the region where the first friction member and the second friction member are arranged (friction material arrangement region P). In this embodiment, the first oil passage 81 is formed so as to penetrate the first friction material support portion 41A in the radial direction R. In addition, a plurality of first oil passages 81 are provided in a dispersed manner in the axial direction L and the circumferential direction. The lubricating oil stored in the oil reservoir portion 56 is supplied to the friction material arrangement region P through the first oil passage 81 by centrifugal hydraulic pressure, and lubricates and cools the first friction material 43 and the second friction material 44.

[0064] The more the amount of oil flowing into the oil reservoir 56 from the axial oil passage 20a side is compared with the amount of oil supplied to the frictional material arrangement region P through the first oil passage 81, the more lubricating oil accumulates in the oil reservoir 56. In particular, in this embodiment, the seal member 51 is disposed between the sliding portion 45A of the first pressing member 45 and the first frictional material support portion 41A, and the oil tightness between them is high, so that the lubricating oil is likely to accumulate in the oil reservoir 56. If the amount of lubricating oil accumulated in the oil reservoir 56 becomes too large, centrifugal oil pressure is generated in the accumulated lubricating oil, which may act to push back the first pressing member 45 separately from the biasing member 48. Such centrifugal oil pressure varies widely, and therefore the controllability of the friction engagement device 40 may deteriorate.

[0065] Therefore, in this embodiment, a second oil passage 82 is further provided in the first support member 41 in addition to the first oil passage 81. The second oil passage 82 is provided so as to communicate the oil reservoir 56 with a space other than the friction material arrangement region P. More specifically, the second oil passage 82 is formed so as to penetrate the first radial extension portion 41B of the first support member 41 in the axial direction L. As a result, the second oil passage 82 communicates the oil reservoir 56 with a space between the first radial extension portion 41B of the first support member 41 and the second radial extension portion 42B of the second support member 42 in the axial direction L. The lubricating oil that flows out of the oil reservoir 56 through the second oil passage 82 is then discharged to the outside of the second support member 42 from the through hole 42c formed in the second friction material support portion 42A.

[0066] An opening (second opening 82a) of the second oil passage 82 that opens to the oil reservoir 56 side is disposed inward in the radial direction R and spaced from an opening (first opening 81a) of the first oil passage 81 that opens to the oil reservoir 56 side. This allows a certain amount of lubricating oil according to the position of the second opening 82a to be stored in the oil reservoir 56, thereby appropriately lubricating and cooling the first friction material 43 and the second friction material 44, and restricts the amount of oil stored in the oil reservoir 56 from becoming too large. This makes it possible to minimize the effect of centrifugal oil pressure due to the oil stored in the oil reservoir 56 on the first pressing member 45.

[0067] In this manner, a first oil passage 81 is provided in the first friction material support portion 41A, communicating between the oil reservoir 56 and the friction material arrangement area P in which the first friction member and the second friction member are arranged, and a second oil passage 82 is provided in at least one of the first support member 41 and the first pressing member 45, communicating between the oil reservoir 56 and a space other than the friction material arrangement area P, with an opening in the first oil passage 81 that opens to the oil reservoir 56 side being a first opening 81a and an opening in the second oil passage 82 that opens to the oil reservoir 56 side being a second opening 82a, and the second opening 82a being spaced apart radially inward from the first opening 81a.

[0068] According to this configuration, the oil supplied from the lubricating oil supply unit 55 and stored in the oil reservoir 56 can be supplied to the friction material arrangement region P via the first oil passage 81. Therefore, the first friction material 43 and the second friction material 44 can be appropriately lubricated. In addition, the oil stored in the oil reservoir 56, which is located on the inside in the radial direction R of the second opening 82a, can be discharged to the outside of the oil reservoir 56 via the second oil passage 82. This makes it possible to regulate the amount of oil stored in the oil reservoir 56 so that it does not become too large. Therefore, the influence of the centrifugal oil pressure caused by the oil stored in the oil reservoir 56 on the first pressing member 45 can be reduced, and as a result, the controllability of the friction engagement device 40 can be improved.

[0069] In this embodiment, the second opening 82a is disposed further inward in the radial direction R than the seal member 51. This makes it possible to ensure that the amount of lubricating oil that accumulates in the oil reservoir 56 is at least a certain amount. Moreover, the second opening 82a is disposed further outward in the radial direction R than the center in the radial direction R of the first radially extending portion 41B. Furthermore, the second opening 82a is disposed further outward in the radial direction R than the biasing member 48. This makes it possible to appropriately suppress the amount of lubricating oil that accumulates in the oil reservoir 56, and to greatly reduce the effect of centrifugal oil pressure on the first pressing member 45.

[0070] The vehicle drive device 100 of this embodiment has been described above, and in addition to the main features and advantages described above, the vehicle drive device 100 has the following features and advantages.

[0071] The pressing drive unit 49 includes a hydraulic chamber 49A for applying hydraulic pressure to the second pressing member 46, and a hydraulic oil supply unit 49B for supplying oil to the hydraulic chamber 49A, and the hydraulic chamber 49A and the hydraulic oil supply unit 49B are formed in the case 6.

[0072] According to this configuration, the hydraulic chamber 49A and the hydraulic oil supply unit 49B constituting the pressing drive unit 49 are formed in the case 6, and therefore, unlike the case where the pressing drive unit 49 is disposed on the rotating body, the centrifugal hydraulic pressure does not act on the pressing drive unit 49. Therefore, there is no need to provide a structure for canceling the centrifugal hydraulic pressure, and the device configuration can be simplified.

[0073] The first support member 41 further includes a first radial extending portion 41B extending inward in the radial direction R from the first friction material support portion 41A, the first friction material support portion 41A is formed in a cylindrical shape along the axial direction L, and the first radial extending portion 41B is arranged on a second axial side L2 relative to the first pressing member 45, and the second support member 42 further includes a second radial extending portion 42B extending inward in the radial direction R from the second friction material support portion 42A, the second friction material support portion 42A is formed in a cylindrical shape along the axial direction L, and the second radial extending portion 42B is arranged on the second axial side L2 relative to the first radial extending portion 41B.

[0074] According to this configuration, both the connection between the first support member 41 and the second shaft member 20 and the connection between the second support member 42 and the fourth gear 24 can be performed on the second axial side L2 with respect to the first pressing member 45. Therefore, both the first support member 41 and the second support member 42 can be arranged so as not to intersect with the transmission path of the pressing force of the first pressing member 45 and the second pressing member 46 in the axial direction L, and the device configuration can be simplified.

[0075] The vehicle drive device 100 includes a transmission 1, a rotating electric machine 2 having a rotor 2B arranged coaxially with a first shaft member 10 and drivingly connected to the first shaft member 10, a pair of output members 4 each of which is drivingly connected to wheels W, and a differential gear mechanism 3. Rotation transmitted from the rotating electric machine 2 is transmitted to the differential gear mechanism 3 via the transmission 1 and further distributed to the pair of output members 4 by the differential gear mechanism 3. The transmission 1 further includes an output gear 25 connected to the second shaft member 20 so as to rotate integrally with the second shaft member 20. The axis on which the first shaft member 10 and the rotor 2B are arranged is defined as a first axis X1, and the axis on which the second shaft member 20 is arranged is defined as a second axis X2. The differential gear mechanism 3 includes a differential input gear 3A that is arranged on a third axis X3 parallel to the first axis X1 and the second axis X2 and meshes with the output gear 25.

[0076] According to this configuration, the driving force of the rotating electric machine 2 can be transmitted to a pair of wheels W via the transmission 1 and the differential gear mechanism 3 to drive the vehicle. By employing the transmission 1 that uses both the meshing engagement device 30 and the friction engagement device 40, it is possible to improve both energy efficiency and the smoothness of the gear shifting operation. Since the device configuration of the transmission 1 is kept from becoming complicated, it is also possible to keep the vehicle drive device 100 as a whole from becoming large. Furthermore, the smoothness of the gear shifting operation can be further improved by improving the controllability of the friction engagement device 40 provided in the transmission 1.

[0077] The first friction material 43 is supported on the outer peripheral surface of the first friction material support portion 41A, the first oil passage 81 is formed to penetrate the first friction material support portion 41A in the radial direction R, and the second oil passage 82 is formed to penetrate the first radially extending portion 41B of the first support member 41 in the axial direction L.

[0078] According to this configuration, the first oil passage 81 penetrating the first friction material support portion 41A in the radial direction R supplies oil to the first friction material 43 and the second friction material 44 using centrifugal oil pressure, thereby allowing these materials to be appropriately lubricated. In addition, by providing the second oil passage 82 in the first support member 41, rather than in the first pressing member 45, which is likely to have a complex structure, the degree of freedom in arranging the second oil passage 82 is increased. Therefore, a configuration in which oil collected in the oil reservoir portion 56 is appropriately discharged via the second oil passage 82 can be easily realized.

[0079] A biasing member 48 is attached to the sliding portion 45A, which biases the first pressing member 45 in the axial direction L so as to move the first pressing member 45 away from the friction material arrangement region P, and the second opening 82a is positioned radially outward of the biasing member 48.

[0080] According to this configuration, the position of the second opening 82a can be disposed relatively close to the first friction material support portion 41A side, and the amount of oil that accumulates in the oil reservoir 56 can be kept relatively small. Therefore, the effect of centrifugal oil pressure on the first pressing member 45 can be further reduced, and the controllability of the friction engagement device 40 can be further improved.

[0081] The sliding portion 45A is positioned radially inward of the first friction material support portion 41A and is formed to extend along the radial direction R. A sealing member 51 is disposed between a sliding opposing surface, which is the surface of the sliding portion 45A that faces the inner circumferential surface of the first friction material support portion 41A, and the inner circumferential surface of the first friction material support portion 41A.

[0082] According to this configuration, by providing the sealing member 51, oil can be appropriately stored in the oil reservoir 56 formed in the region along the inner circumferential surface of the first friction material support portion 41A, thereby allowing the first friction material 43 and the second friction material 44 to be appropriately lubricated. Meanwhile, the presence of such sealing member 51 results in a structure in which almost no oil is discharged from the oil reservoir 56, but by providing the second oil passage 82, part of the oil can be discharged to the outside of the oil reservoir 56, so that the amount of oil stored in the oil reservoir 56 can be restricted to a certain amount or less.

[0083] The vehicle drive device 100 includes a friction engagement device 40, a rotating electric machine 2 having a rotor 2B arranged on a first axis X1 and functioning as a driving force source for wheels W, a pair of output members 4 each drivingly connected to the wheels W, a transmission 1 that changes the speed of rotation transmitted from the rotating electric machine 2 side, a differential gear mechanism 3 that distributes the rotation transmitted from the transmission 1 to the pair of output members 4, and a case 6 that houses the rotating electric machine 2, the transmission 1, and the differential gear mechanism 3. The transmission 1 includes a first shaft member 10 arranged on the first axis X1, a first gear 12 and a second gear 14 connected to the first shaft member 10 so as to rotate integrally with the first shaft member 10, a second shaft member 20 arranged on a second axis X2 parallel to the first axis X1, and a gear 12 and a gear 14 supported so as to be rotatable relative to the second shaft member 20. The differential gear mechanism 3 includes a third gear 22 and a fourth gear 24 supported on the second shaft member 20, and an output gear 25 connected to rotate integrally with the second shaft member 20, and the first gear 12 and the third gear 22 mesh with each other, and the second gear 14 and the fourth gear 24 mesh with each other. A meshing engagement device 30 for selectively connecting either the third gear 22 or the fourth gear 24 to the second shaft member 20 is disposed on the second shaft X2 between the third gear 22 and the fourth gear 24 in the axial direction L. The differential gear mechanism 3 is disposed on a third axis X3 parallel to the first axis X1 and the second axis X2, and includes a differential input gear 3A meshing with the output gear 25. A friction engagement device 40 is disposed on the second shaft X2 on one side of the third gear 22 and the fourth gear 24 in the axial direction L.

[0084] According to this configuration, the driving force of the rotating electric machine 2 can be transmitted to a pair of wheels W via the transmission 1 and the differential gear mechanism 3 to drive the vehicle. By employing the transmission 1 that combines the meshing engagement device 30 and the friction engagement device 40, it is possible to improve both energy efficiency and the smoothness of the gear shifting operation. In particular, the controllability of the friction engagement device 40 provided in the transmission 1 is improved, thereby further improving the smoothness of the gear shifting operation.

[0085] The case 6 has a third cylindrical support portion 63 that supports the second bearing 93 from the outside in the radial direction R, and the pressing drive portion 49 has a hydraulic chamber 49A for applying hydraulic pressure to the second pressing member 46, and a hydraulic oil supply portion 49B that supplies oil to the hydraulic chamber 49A, the hydraulic oil supply portion 49B is formed in the case 6, and the inner surface of the hydraulic chamber 49A is formed using the outer surface of the third cylindrical support portion 63.

[0086] According to this configuration, by forming the hydraulic chamber 49A by utilizing the structure of the case 6 for supporting the second bearing 93 (the third cylindrical support portion 63), the pressing drive portion 49 can be easily made compact.

[0087] The first bearing 92 supports an end of the first shaft member 10 on the first axial side L1, and the second bearing 93 supports an end of the second shaft member 20 on the first axial side L1.

[0088] According to this configuration, the ends of both the first shaft member 10 and the second shaft member 20 on the first axial side L1 are supported by the first bearing 92 and the second bearing 93, whose arrangement regions in the axial direction L overlap each other, so that the amount of protrusion of the first shaft member 10 and the second shaft member 20 on the first axial side L1 can be kept small. Therefore, it is easy to keep the axial direction L dimension of the transmission 1 small.

[0089] The first gear 12 and the second gear 14 are supported on the first shaft member 10, and the second shaft member 20 supports a third gear 22 that meshes with the first gear 12 and a fourth gear 24 that meshes with the second gear 14, the second gear 14 and the fourth gear 24 are arranged on a first axial side L1 relative to the first gear 12 and the third gear 22, the friction engagement device 40 is arranged on the first axial side L1 relative to the fourth gear 24, the first support member 41 is connected to the second shaft member 20 so as to rotate integrally, and the second support member 42 is connected to the fourth gear 24 so as to rotate integrally.

[0090] According to this configuration, both the first support member 41 and the second shaft member 20 and the second support member 42 and the fourth gear 24 can be easily connected on the second axial side L2 with respect to the first pressing member 45. As a result, both the first support member 41 and the second support member 42 can be arranged so as not to intersect with the transmission path of the pressing force of the first pressing member 45 and the second pressing member 46 in the axial direction L. This makes it possible to simplify the device configuration.

[0091] When viewed in the axial direction along the axial direction L, the first bearing 92, the first friction material 43, and the second friction material 44 are arranged to overlap each other.

[0092] According to this configuration, the radial dimension R of the transmission 1 can be kept small compared to a configuration in which the first bearing 92 and the first and second friction materials 43 and 44 are arranged offset in the radial direction R. Therefore, it is possible to effectively prevent the device as a whole from becoming large.

[0093] Other embodiments (1) In the above embodiment, an example has been described in which the rotating electric machine 2 is drivingly connected to the first shaft member 10. However, the present invention is not limited to such a configuration, and the rotating electric machine 2 may be drivingly connected to the second shaft member 20, and the rotating electric machine 2, the meshing engagement device 30, and the friction engagement device 40 may be coaxially arranged on the second axis X2. In this case, it is preferable that an output gear 25 is formed on the first shaft member 10.

[0094] (2) In the above embodiment, a configuration has been described in which the first support member 41 is provided with the second oil passage 82 that communicates between the oil reservoir 56 and a space other than the friction material arrangement area P. However, the present invention is not limited to such a configuration, and the second oil passage 82 may be provided in the first pressing member 45, for example. Alternatively, the second oil passage 82 may be provided in both the first support member 41 and the first pressing member 45.

[0095] (3) In the above embodiment, a configuration has been described as an example in which the first oil passage 81 is formed to penetrate the first friction material support portion 41A in the radial direction R. However, the present invention is not limited to such a configuration. For example, the first oil passage 81 may be formed to extend along a direction inclined with respect to the radial direction R.

[0096] (4) In the above embodiment, a configuration has been described as an example in which the second oil passage 82 is formed to penetrate the first radially extending portion 41B in the axial direction L. However, the present invention is not limited to such a configuration. For example, the second oil passage 82 may be formed along a direction inclined with respect to the axial direction L.

[0097] (5) In the above embodiment, the second opening 82a that opens to the oil reservoir 56 side of the second oil passage 82 is disposed in a position that is more inward in the radial direction R than the seal member 51 and more outward in the radial direction R than the biasing member 48. However, the present invention is not limited to such a configuration, and the position of the second opening 82a may be any position as long as it is spaced inward in the radial direction R from the first opening 81a. For example, the second opening 82a may be disposed in a position that overlaps with the seal member 51 when viewed in the axial direction, or may be disposed in the vicinity of the shaft coupling portion 41C in the first radial extending portion 41B.

[0098] (6) In the above embodiment, the pressing drive unit 49 is described as having the hydraulic chamber 49A and the hydraulic oil supply unit 49B. However, the present invention is not limited to such a configuration, and the pressing drive unit 49 may be configured to have, for example, an electric actuator.

[0099] (7) In the above embodiment, a configuration has been described as an example in which a return spring formed of a coil spring is used as the biasing member 48. However, the present invention is not limited to such a configuration, and for example, a leaf spring or the like may be used as the biasing member 48.

[0100] (8) In the above embodiment, the seal member 51 is disposed between the sliding portion 45A and the first friction material support portion 41A. However, the present invention is not limited to such a configuration, and such a seal member 51 does not necessarily have to be provided.

[0101] (9) In the above embodiment, a configuration has been described as an example in which the entire arrangement region D3 of the second pressing member 46 in the axial direction L is included in the arrangement region D1 of the first bearing 92 in the axial direction L and partially overlaps with the arrangement region D2 of the second bearing 93 in the axial direction L. However, without being limited to such a configuration, for example, the entire arrangement region D3 of the second pressing member 46 in the axial direction L may be included in both the arrangement region D1 of the first bearing 92 in the axial direction L and the arrangement region D2 of the second bearing 93 in the axial direction L. Alternatively, the arrangement region D3 of the second pressing member 46 in the axial direction L may partially overlap each of the arrangement region D1 of the first bearing 92 in the axial direction L and the arrangement region D2 of the second bearing 93 in the axial direction L.

[0102] (10) In the above embodiment, the vehicle drive device 100 is described as an example of a configuration in which it is applied to a drive device for an electric vehicle. However, the present disclosure is not limited to such a configuration, and can be applied to other types of vehicle drive devices, such as so-called engine vehicles and hybrid vehicles that use both an engine and a rotating electric machine 2.

[0103] (11) The configurations disclosed in the above-mentioned embodiments (including the above-mentioned embodiments and other embodiments; the same applies below) can be applied in combination with configurations disclosed in other embodiments, as long as no contradiction occurs. As for other configurations, the embodiments disclosed in this specification are illustrative in all respects and can be appropriately modified within the scope of the present disclosure. [Explanation of symbols]

[0104] 1: transmission, 2: rotating electric machine, 2A: stator, 2B: rotor, 2C: rotor shaft, 3: differential gear mechanism, 3A: differential input gear, 4: output member, 6: case, 6A: first case part, 6Aa: first peripheral wall part, 6Ab: first support wall part, 6B: second case part, 6Ba: second peripheral wall part, 6Bb: second support wall part, 6C: third case part, 10: first shaft member, 12: first gear, 13: second gear forming member, 14: second gear, 20: second shaft member, 20a: Axial oil passage, 20b: radial oil passage, 21: third gear forming member, 22: third gear, 23: fourth gear forming member, 24: fourth gear, 25: output gear, 30: meshing type engagement device, 31: first engagement portion, 31A: connecting member, 32: second engagement portion, 33: third engagement portion, 35: switching member, 40: friction engagement device, 41: first support member, 41A: first friction material support portion, 41B: first radial extension portion, 41C: shaft connecting portion, 41d: communicating oil passage, 42: second Support member, 42A: second friction material support portion, 42B: second radial extension portion, 43: first friction material, 44: second friction material, 45: first pressing member, 45A: sliding portion, 45B: pressing portion, 46: second pressing member, 47: holding member, 48: biasing member, 49: pressing drive portion, 49A: hydraulic chamber, 49B: hydraulic oil supply portion, 51: sealing member, 52: sealing member, 53: sealing member, 55: lubricating oil supply portion, 56: oil reservoir portion, 61: first cylindrical support portion, 62: second Cylindrical support portion, 63: third cylindrical support portion, 81: first oil passage, 81a: first opening, 82: second oil passage, 82a: second opening, 91: rotor bearing, 92: first bearing, 93: second bearing, 95: thrust bearing, 100: vehicle drive device, D1: arrangement area, D2: arrangement area, D3: arrangement area, L: axial direction, L1: first axial side, L2: second axial side, P: friction material arrangement area, R: radial direction, W: wheel, X1: first axis, X2: second axis, X3: third axis

Claims

1. a first support member including a first friction material support portion that supports a first friction material and is rotatably supported; a second support member including a second friction material support portion that supports a second friction material, the second support member being supported rotatably independent of the first support member; a first pressing member that rotates integrally with the first support member and is supported by the first support member so as to be movable in the axial direction, and presses the first friction material and the second friction material in the axial direction so as to press the first friction material and the second friction material against each other; a second pressing member that is supported on the non-rotating member so as to be movable in the axial direction and presses the first pressing member in the axial direction while being rotatable relative to the first pressing member; a pressing drive unit that drives the second pressing member in the axial direction, The first friction material support portion is formed in a cylindrical shape along the axial direction, the second friction material support portion is disposed radially outward of the first friction material support portion and coaxially with the first friction material support portion, The first friction material is connected to the first friction material support portion so as to rotate integrally with the first friction material support portion, the second friction material is connected to the second friction material support portion so as to rotate integrally with the second friction material, the first friction material and the second friction material are disposed between the first friction material support portion and the second friction material support portion in the radial direction so as to face each other in the axial direction, The first support member further includes a radially extending portion extending inward in the radial direction from the first friction material support portion, the first pressing member includes a sliding portion that slides along an inner circumferential surface of the first friction material support portion, the sliding portion is disposed radially inward of the first friction material support portion and is formed to extend along the radial direction, a seal member is disposed between a sliding opposing surface of the sliding portion that faces an inner circumferential surface of the first friction material support portion and the inner circumferential surface of the first friction material support portion, an oil reservoir is formed in a region surrounded by an inner circumferential surface of the first friction material support portion, the radially extending portion, and the sliding portion; an oil supply unit that supplies oil to the oil reservoir; a first oil passage is provided in the first friction material support portion, the first oil passage communicating with the oil reservoir and a friction material arrangement area in which the first friction material and the second friction material are arranged; At least one of the first support member and the first pressing member is provided with a second oil passage that communicates the oil reservoir with a space other than the friction material arrangement area, A friction engagement device, wherein an opening in the first oil passage that opens toward the oil reservoir is a first opening, and an opening in the second oil passage that opens toward the oil reservoir is a second opening, and the second opening is positioned radially inward and spaced apart from the first opening.

2. The first friction material is supported on an outer circumferential surface of the first friction material support portion, The first oil passage is formed to penetrate the first friction material support portion in the radial direction, The friction engagement device according to claim 1 , wherein the second oil passage is formed so as to penetrate the radially extending portion of the first support member in the axial direction.

3. a biasing member that biases the first pressing member in the axial direction so as to move the first pressing member away from the friction material arrangement area is attached to the sliding portion, The friction engagement device according to claim 1 , wherein the second opening is disposed radially outward of the biasing member.

4. The friction engagement device according to any one of claims 1 to 3, a rotating electric machine including a rotor disposed on a first shaft and functioning as a driving force source for the wheels; A pair of output members each drivingly connected to one of the wheels; a transmission that changes the speed of rotation transmitted from the rotating electric machine; a differential gear mechanism that distributes rotation transmitted from the transmission to the pair of output members; a case as the non-rotating member that houses the rotating electric machine, the transmission, and the differential gear mechanism, The transmission includes a first shaft member disposed on the first shaft, a first gear and a second gear connected to the first shaft member so as to rotate integrally with the first shaft member, a second shaft member disposed on a second shaft parallel to the first shaft, a third gear and a fourth gear supported so as to be rotatable relative to the second shaft member, and an output gear connected to rotate integrally with the second shaft member, the first gear and the third gear mesh with each other, and the second gear and the fourth gear mesh with each other; a meshing engagement device that selectively connects either the third gear or the fourth gear to the second shaft member is disposed on the second shaft between the third gear and the fourth gear in the axial direction, the differential gear mechanism includes a differential input gear disposed on a third shaft parallel to the first shaft and the second shaft and meshing with the output gear; The friction engagement device is disposed on the second shaft and on one side in the axial direction with respect to the third gear and the fourth gear.

Images