Transmission and vehicle drive transmission device equipped therewith

Abstract

A first fixing device (2) comprises a first gear (21) to be fixed that rotates integrally with a first fixing element (13) of a planetary gear mechanism (1), a first fixing gear (22) that engages with the first gear to be fixed, and a first friction engagement device (4) that causes the first fixing gear to selectively engage with a non-rotating member (NR). A second fixing device (3) comprises a second gear (31) to be fixed that rotates integrally with a second fixing element (14) of the planetary gear mechanism (1), a second fixing gear (32) that engages with the second gear to be fixed, and a second friction engagement device (5) that causes the second fixing gear to selectively engage with the non-rotating member (NR). The first friction engagement device (4) is disposed coaxially with the first fixing gear (22), and the second friction engagement device (5) is disposed coaxially with the second fixing gear (32). The axis of rotation of the first fixing gear (22) and the axis of rotation of the second fixing gear (32) are disposed in parallel to each other. The first friction engagement device (4) and the second friction engagement device (5) are disposed so as not to overlap each other as viewed in the axial direction along the axial direction (L).

Description

Technical Field

[0001] The present invention relates to a transmission including a planetary gear mechanism having an input element drivingly connected to a drive source of a wheel, an output element drivingly connected to the wheel, a first fixed element, and a second fixed element, a first fixing device for selectively fixing the first fixed element to a non-rotating member, and a second fixing device for selectively fixing the second fixed element to a non-rotating member, and a vehicle drive transmission device including the same.

Background Art

[0002] An example of such a technique is disclosed in Patent Document 1 below. In the following description of the background art, the reference numerals in Patent Document 1 are cited in parentheses.

[0003] In the transmission of Patent Document 1, the planetary gear mechanism (5) includes a carrier (53) rotatably supporting a large-diameter pinion gear (52a) and a small-diameter pinion gear (52b) that rotate integrally with each other, a sun gear (51) that rotates integrally with the rotor (32) of the rotary electric machine (3) and meshes with the large-diameter pinion gear (52a), a first ring gear (54a) that meshes with the large-diameter pinion gear (52a), and a second ring gear (55a) that meshes with the small-diameter pinion gear (52b).

[0004] The first fixing device is configured to selectively fix the first ring gear (54a) to the case (2) as a non-rotating member. The second fixing device is configured to selectively fix the second ring gear (55a) to the case (2) as a non-rotating member.

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0006] In the transmission of Patent Document 1, the first friction engagement device (61) constituting the first fixing device and the second friction engagement device (62) constituting the second fixing device are arranged side by side in the axial direction (the left - right direction in FIG. 1 of Patent Document 1). Therefore, the transmission is likely to be enlarged in the axial direction.

[0007] Furthermore, the first friction engagement device (61) and the second friction engagement device (62) are arranged on the outer side in the radial direction (the upper side in FIG. 1 of Patent Document 1) with respect to the planetary gear mechanism (5). Therefore, the transmission is likely to be enlarged in the radial direction.

[0008] Therefore, in a configuration including a pair of friction engagement devices, it is desired to realize a technology that facilitates downsizing of the transmission.

Means for Solving the Problems

[0009] In view of the above, the characteristic configuration of the transmission is a planetary gear mechanism including an input element drivingly connected to a driving source of a wheel, an output element drivingly connected to the wheel, a first fixed element, and a second fixed element; a first fixing device that selectively fixes the first fixed element to a non - rotating member; a second fixing device that selectively fixes the second fixed element to the non - rotating member, and is a transmission, the first fixing device includes a first fixed gear connected to rotate integrally with the first fixed element, a first fixing gear meshing with the first fixed gear, and a first friction engagement device that selectively engages the first fixing gear with the non - rotating member; the second fixing device includes a second fixed gear connected to rotate integrally with the second fixed element, a second fixing gear meshing with the second fixed gear, and a second friction engagement device that selectively engages the second fixing gear with the non - rotating member; the first friction engagement device is arranged coaxially with the first fixing gear; the second friction engagement device is arranged coaxially with the second fixing gear; The rotation axis of the first fixed gear and the rotation axis of the second fixed gear are arranged parallel to each other. Taking the direction along the rotation axis of the first fixed gear and the rotation axis of the second fixed gear as the axial direction, the first friction engagement device and the second friction engagement device are arranged so as not to overlap each other in the axial direction view along the axial direction.

[0010] According to this characteristic configuration, the first fixing device includes a first fixed gear connected to rotate integrally with the first fixed element of the planetary gear mechanism, a first fixed gear meshing with the first fixed gear, and a first friction engagement device for selectively engaging the first fixed gear with a non-rotating member. And the first friction engagement device is arranged coaxially with the first fixed gear. Also, the second fixing device includes a second fixed gear connected to rotate integrally with the second fixed element of the planetary gear mechanism, a second fixed gear meshing with the second fixed gear, and a second friction engagement device for selectively engaging the second fixed gear with a non-rotating member. And the second friction engagement device is arranged coaxially with the second fixed gear. Thereby, it becomes easy to arrange the first friction engagement device and the second friction engagement device on different axes from each other. Therefore, compared with the configuration in which they are arranged coaxially, it is easy to suppress the axial dimension of the transmission to be small. Also, according to this characteristic configuration, by setting the diameter of the first fixed gear with respect to the first fixed gear in the first fixing device to be small, the torque required to fix the first fixed element of the planetary gear mechanism to the non-rotating member can be suppressed to be small. Thereby, it is easy to reduce the diameter of the first friction engagement device. Similarly, for the second fixing device, it is also easy to reduce the diameter of the second friction engagement device. As described above, according to this characteristic configuration, in a configuration provided with a pair of friction engagement devices, it is easy to reduce the size of the transmission.

[0011] In view of the above, the characteristic configuration of the vehicle drive transmission device is the drive source is a rotary electric machine having a rotor, a rotor shaft that rotates integrally with the rotor, A first output member drivingly connected to the first wheel, which is the wheel; A second output member drivingly connected to the second wheel, which is the wheel and different from the first wheel; A differential gear mechanism including a differential input element, a first differential output element, and a second differential output element connected to rotate integrally with the rotor shaft, and distributing the torque transmitted from the rotor shaft to the differential input element to the first differential output element and the second differential output element; A first transmission, which is the transmission according to claim 1; A vehicle drive transmission device including a second transmission, which is the transmission according to claim 1 and different from the first transmission, wherein: The input element of the first transmission is connected to rotate integrally with the first differential output element; The output element of the first transmission is connected to rotate integrally with the first output member; The input element of the second transmission is connected to rotate integrally with the second differential output element; The output element of the second transmission is connected to rotate integrally with the second output member; The first fixed gear of the first transmission and the first fixed gear of the second transmission are arranged coaxially; The first fixed gear of the first transmission and the first fixed gear of the second transmission are arranged coaxially and are connected to rotate integrally with each other; The second fixed gear of the first transmission and the second fixed gear of the second transmission are arranged coaxially; The second fixed gear of the first transmission and the second fixed gear of the second transmission are arranged coaxially and are connected to rotate integrally with each other; The first friction engagement device of the first transmission and the first friction engagement device of the second transmission are common; The second friction engagement device of the first transmission and the second friction engagement device of the second transmission are common.

[0012] According to this characteristic configuration, in a configuration where a transmission is provided in each of the power transmission paths connecting the differential gear mechanism and the first output member, and the differential gear mechanism and the second output member, the first fixed gears constituting the first fixing device of the pair of transmissions are coaxially arranged and are connected so as to rotate integrally with each other. Further, the second fixed gears constituting the second fixing device of the pair of transmissions are coaxially arranged and are connected so as to rotate integrally with each other. Thereby, the pair of first fixed gears can be selectively engaged with the non-rotating member by one first friction engagement device, and the pair of second fixed gears can be selectively engaged with the non-rotating member by one second friction engagement device. Therefore, in a configuration including a pair of transmissions, it is easy to reduce the size of the pair of first fixing devices and the pair of second fixing devices, and thus to reduce the size of the vehicle drive transmission device.

[0013] In view of the above, the characteristic configuration of the vehicle drive transmission device is The drive source is a rotating electric machine having a rotor, A rotor shaft that rotates integrally with the rotor, A first output member that is drivingly connected to the first wheel, which is the wheel, A second output member that is drivingly connected to the second wheel, which is the wheel and is different from the first wheel, The transmission according to claim 1, A vehicle drive transmission device including a differential input element, a first differential output element, and a second differential output element, and a differential gear mechanism that distributes the torque transmitted from the transmission to the differential input element to the first differential output element and the second differential output element, The input element of the transmission is connected so as to rotate integrally with the rotor shaft, The output element of the transmission is connected so as to rotate integrally with an external gear drive gear, The differential input element is connected so as to rotate integrally with an external gear driven gear that meshes with the drive gear, The first differential output element is connected so as to rotate integrally with the first output member, The second differential output element is connected so as to rotate integrally with the second output member. Regarding the rotor shaft and the shaft on which the planetary gear mechanism of the transmission is disposed as a first shaft, the shaft on which the first fixed gear of the transmission is disposed as a second shaft, the shaft on which the second fixed gear of the transmission is disposed as a third shaft, and the shaft on which the differential gear mechanism is disposed as a fourth shaft, the first shaft, the second shaft, the third shaft, and the fourth shaft are arranged parallel to each other. The second shaft, the third shaft, and the fourth shaft are arranged so as to surround the first shaft.

[0014] According to this characteristic configuration, in a configuration where the planetary gear mechanism of the transmission is arranged coaxially with the rotor shaft and the differential gear mechanism is arranged on a shaft different from the rotor shaft, the second shaft on which the first fixed gear of the transmission is arranged, the third shaft on which the second fixed gear of the transmission is arranged, and the fourth shaft on which the differential gear mechanism is arranged are arranged so as to surround the first shaft on which the rotor shaft and the planetary gear mechanism of the transmission are arranged. Therefore, it is easy to suppress the radial dimension of the vehicle drive transmission device with respect to the first shaft.

Brief Description of the Drawings

[0015]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Mode for Carrying Out the Invention

[0016] 1. First Embodiment Hereinafter, the vehicle drive transmission device 100 according to the first embodiment will be described with reference to FIGS. 1 to 4.

[0017] As shown in FIGS. 1 and 2, the vehicle drive transmission device 100 includes a transmission 10. In the present embodiment, the vehicle drive transmission device 100 includes a pair of transmissions 10. The transmission 10 includes a planetary gear mechanism 1, a first fixing device 2, and a second fixing device 3.

[0018] The planetary gear mechanism 1 includes an input element 11 that is drivingly connected to a drive source D of a wheel W (see FIG. 2), an output element 12 that is drivingly connected to the wheel W, a first fixing element 13, and a second fixing element 14.

[0019] Here, in the present application, "driving connection" refers to a state in which two rotating elements are connected so as to be able to transmit a driving force, and includes a state in which the two rotating elements are connected so as to rotate integrally, or a state in which the two rotating elements are connected so as to be able to transmit a driving force via one or two or more transmission members. Such transmission members include various members that transmit rotation at the same speed or with speed change, for example, shafts, gear mechanisms, belts, chains, etc. Note that the transmission members may include engagement devices that selectively transmit rotation and driving force, for example, friction engagement devices, meshing engagement devices, etc. However, when referring to "driving connection" for each rotating element of the planetary gear mechanism, it shall refer to a state in which they are connected without passing through other rotating elements.

[0020] In the present embodiment, the rotating electric machine MG including the stator ST and the rotor RT corresponds to the drive source D. In the present application, the "rotating electric machine" is used as a concept including any of a motor (electric motor), a generator (dynamo), and a motor-generator that performs the functions of both a motor and a generator as necessary.

[0021] In the present embodiment, the planetary gear mechanism 1 is disposed on the first axis X1 which is the rotation axis of the rotor RT of the rotating electric machine MG.

[0022] In the present embodiment, the input element 11 is the sun gear S1. And the output element 12 is the carrier C1. Further, in the present embodiment, the first fixed element 13 includes a first annular portion A11 formed in a ring shape and an internal-toothed first ring gear R11 provided on the inner peripheral surface of the first annular portion A11. And the second fixed element 14 includes a second annular portion A12 formed in a ring shape and an internal-toothed second ring gear R12 provided on the inner peripheral surface of the second annular portion A12.

[0023] In the present embodiment, the carrier C1 rotatably supports a large-diameter pinion gear P11 and a small-diameter pinion gear P12 that rotate integrally with each other. Each of the large-diameter pinion gear P11 and the small-diameter pinion gear P12 rotates (autogyrates) around its own axis and rotates (revolves) around the sun gear S1 together with the carrier C1. A plurality of the large-diameter pinion gears P11 and the small-diameter pinion gears P12 are provided at intervals along their respective revolution trajectories.

[0024] The large-diameter pinion gear P11 meshes with both the sun gear S1 and the second ring gear R12. In the present embodiment, the large-diameter pinion gear P11 is formed to have a larger diameter than the sun gear S1. The small-diameter pinion gear P12 meshes with the first ring gear R11. The small-diameter pinion gear P12 is formed to have a smaller diameter than the large-diameter pinion gear P11.

[0025] The first fixing device 2 is a device that selectively fixes the first fixing element 13 of the planetary gear mechanism 1 to the non-rotating member NR. The second fixing device 3 is a device that selectively fixes the second fixing element 14 of the planetary gear mechanism 1 to the non-rotating member NR. In the present embodiment, the non-rotating member NR is the case 9 that houses the components of the vehicle drive transmission device 100 including the transmission 10.

[0026] The first fixing device 2 includes a first fixed gear 21, a first fixing gear 22, and a first friction engagement device 4.

[0027] The first fixed gear 21 is connected so as to rotate integrally with the first fixing element 13 of the planetary gear mechanism 1. The first fixing gear 22 is arranged so as to mesh with the first fixed gear 21. In the present embodiment, the first fixed gear 21 is an external gear provided on the outer peripheral surface of the first annular portion A11. Also, in the present embodiment, the first fixed gear 21 is formed to have a larger diameter than the large-diameter pinion gear P11. And the first fixing gear 22 is formed to have a smaller diameter than the first fixed gear 21. Also, in the present embodiment, the first fixed gear 21 is arranged on the first axis X1. And the first fixing gear 22 is arranged on a second axis X2 different from the first axis X1.

[0028] The first friction engagement device 4 is a device that selectively engages the first fixing gear 22 with the non-rotating member NR. The detailed configuration of the first friction engagement device 4 will be described later.

[0029] The second fixing device 3 includes a second fixed gear 31, a second fixing gear 32, and a second friction engagement device 5.

[0030] The second fixed gear 31 is connected so as to rotate integrally with the second fixed element 14 of the planetary gear mechanism 1. The second fixed gear 32 is arranged so as to mesh with the second fixed gear 31. In the present embodiment, the second fixed gear 31 is a gear with external teeth provided on the outer peripheral surface of the second annular portion A12. Also, in the present embodiment, the second fixed gear 31 is formed to have a larger diameter than the large-diameter pinion gear P11. And the second fixed gear 31 is formed to have the same diameter as the first fixed gear 21. Further, the second fixed gear 32 is formed to have a smaller diameter than the second fixed gear 31. In the present embodiment, the second fixed gear 31 is arranged on the first axis X1. And the second fixed gear 32 is arranged on a third axis X3 different from the first axis X1 and the second axis X2.

[0031] The second friction engagement device 5 is a device that selectively engages the second fixed gear 32 with the non-rotating member NR. The detailed configuration of the second friction engagement device 5 will be described later.

[0032] The rotation axis of the first fixed gear 22 (here, the second axis X2) and the rotation axis of the second fixed gear 32 (here, the third axis X3) are arranged parallel to each other. In the present embodiment, the first axis X1, the second axis X2, and the third axis X3 are arranged parallel to each other. In the following description, the direction along the rotation axis of the first fixed gear 22 (here, the second axis X2) and the rotation axis of the second fixed gear 32 (here, the third axis X3) is defined as the "axial direction L". And one side of the axial direction L is defined as the "first axial side L1", and the other side of the axial direction L is defined as the "second axial side L2".

[0033] Also, the direction orthogonal to the rotation axis of the first fixed gear 22 (here, the second axis X2) is defined as the "first radial direction RA". And the direction orthogonal to the rotation axis of the second fixed gear 32 (here, the third axis X3) is defined as the "second radial direction RB". Hereinafter, including the first radial direction RA and the second radial direction RB, the direction orthogonal to the rotation axis of any rotating member is defined as the "radial direction R". That is, the radial direction R is defined based on the rotation axes of rotating members such as the first fixed gear 22 and the second fixed gear 32. When there is no need to distinguish which rotation axis is the reference or when it is clear which rotation axis is the reference, it may be simply referred to as the "radial direction R".

[0034] As shown in FIG. 3, the first friction engagement device 4 includes a first friction member 41, a second friction member 42, a first support member 43, a second support member 44, and a first pressing device 45.

[0035] The first friction member 41 and the second friction member 42 are arranged on the second axis X2. That is, the first friction member 41 and the second friction member 42 are arranged coaxially with the first fixed gear 22. The first friction member 41 and the second friction member 42 are arranged to face each other in the axial direction L. In the present embodiment, a plurality of first friction members 41 and a plurality of second friction members 42 are provided, and they are alternately arranged along the axial direction L. Either the first friction member 41 or the second friction member 42 can be a friction plate and the other can be a separator plate.

[0036] The first support member 43 is a member that supports the first friction member 41 while restricting the relative rotation of the first friction member 41. The first support member 43 is connected so as to rotate integrally with the first fixed gear 22. In the present embodiment, the first support member 43 is formed in a cylindrical shape extending along the axial direction L. And the first support member 43 supports the outer peripheral portion of the first friction member 41.

[0037] The second support member 44 is a member that supports the second friction member 42 while restricting the relative rotation of the second friction member 42. The second support member 44 is fixed to the non-rotating member NR. In the present embodiment, the second support member 44 is formed in a cylindrical shape extending along the axial direction L. And the second support member 44 supports the inner peripheral portion of the second friction member 42. Further, in the present embodiment, the second support member 44 is fixed to the first support wall portion 91 provided in the case 9 as the non-rotating member NR. The first support wall portion 91 is formed so as to extend along the first radial direction RA. And the first support wall portion 91 is arranged so as to cover the first friction member 41 and the second friction member 42 from the first side L1 in the axial direction. In the example shown in FIG. 3, the second support member 44 is integrally formed with the first support wall portion 91 so as to project from the first support wall portion 91 to the second side L2 in the axial direction.

[0038] The first pressing device 45 is a device that presses the first friction member 41 and the second friction member 42 in the axial direction L. In the present embodiment, the first pressing device 45 includes a first pressing member 46 that applies a pressing force to the first friction member 41 and the second friction member 42, a first drive motor 47, and a screw-type first linear motion conversion mechanism 48 that converts the rotational driving force of the first drive motor 47 into a driving force in the axial direction L and transmits it to the first pressing member 46.

[0039] The first pressing member 46 is arranged at a position overlapping the first friction member 41 and the second friction member 42 in a view in the axial direction along the axial direction L. In the present embodiment, the first pressing member 46 is formed in a plate shape extending along the first radial direction RA. Here, regarding the arrangement of the two elements, "overlapping in a specific direction view" means that when a virtual straight line parallel to the line-of-sight direction is moved in each direction orthogonal to the virtual straight line, there is at least a part of a region where the virtual straight line intersects both of the two elements.

[0040] The first drive motor 47 is a motor that generates a rotational driving force for driving the first pressing member 46. In the present embodiment, the first drive motor 47 is disposed outside the first support member 43 in the first radial direction RA and at a position overlapping the first support member 43 in a view in the first radial direction along the first radial direction RA. Further, in the present embodiment, the first drive motor 47 is disposed at a position overlapping the planetary gear mechanism 1 in an axial view along the axial direction L.

[0041] In the present embodiment, the first linear motion conversion mechanism 48 includes a first screw shaft member 481, a first nut member 482, a first connecting member 483, a first supported member 484, and a first reduction mechanism 49.

[0042] The first screw shaft member 481 is formed to extend along the axial direction L. The first nut member 482 is formed in an annular shape that covers the first screw shaft member 481 from the outside in the first radial direction RA. The first screw shaft member 481 and the first nut member 482 are configured to be screwed together. Specifically, a male screw is formed on the outer peripheral portion of the first screw shaft member 481, and a female screw that screws with the male screw of the first screw shaft member 481 is formed on the inner peripheral portion of the first nut member 482. Therefore, when the first screw shaft member 481 rotates, the first nut member 482 performs a linear motion along the axial direction L according to the rotation direction and the directions of the male screw and the female screw.

[0043] The first nut member 482 is non-rotatable relative to the non-rotating member NR and is supported so as to be movable in the axial direction L. In the present embodiment, the first nut member 482 is disposed inside the first radial direction RA with respect to the second support member 44 fixed to the non-rotating member NR. And the first nut member 482 is non-rotatable relative to the second support member 44 and is connected so as to be relatively movable in the axial direction L via an annular first anti-rotation member 48a disposed between the first nut member 482 and the second support member 44 in the first radial direction RA. In the example shown in FIG. 3, a plurality of spline teeth extending in the axial direction L are formed dispersedly in the circumferential direction on the outer peripheral portion of the first nut member 482. And on the inner peripheral portion of the first anti-rotation member 48a, a plurality of spline teeth engaging with the plurality of spline teeth formed on the outer peripheral portion of the first nut member 482 are formed dispersedly in the circumferential direction so as to extend in the axial direction L. Further, a plurality of spline teeth extending in the axial direction L are formed dispersedly in the circumferential direction on the inner peripheral portion of the second support member 44. And on the outer peripheral portion of the first anti-rotation member 48a, a plurality of spline teeth engaging with the plurality of spline teeth formed on the inner peripheral portion of the second support member 44 are formed dispersedly in the circumferential direction so as to extend in the axial direction L.

[0044] Further, the first nut member 482 is connected so as to move integrally with the first pressing member 46 in the axial direction L. In the example shown in FIG. 3, the first nut member 482 is integrally formed with the first pressing member 46. Therefore, as the first screw shaft member 481 rotates, the first pressing member 46 moves in the axial direction L via the first nut member 482.

[0045] The first connecting member 483 connects the first screw shaft member 481 and the first reduction mechanism 49. In the present embodiment, the first connecting member 483 is formed in a cylindrical shape extending in the first axial direction L1 from the first screw shaft member 481.

[0046] The first supported member 484 is supported in the axial direction L with respect to the non-rotating member NR. In the present embodiment, the first supported member 484 is formed so as to protrude outward in the first radial direction RA from the first connecting member 483. And the first supported member 484 is supported from the second side L2 in the axial direction via a first thrust bearing B1 by a support portion 44a formed so as to protrude inward in the first radial direction RA from a second support member 44 fixed to the non-rotating member NR.

[0047] The first speed reduction mechanism 49 is configured to reduce the rotation of the first drive motor 47. In the present embodiment, the first speed reduction mechanism 49 includes a first gear 491, a second gear 492, a third gear 493, and a fourth gear 494.

[0048] The first gear 491 is connected so as to rotate integrally with the output shaft of the first drive motor 47. In the present embodiment, the first gear 491 is disposed on the first side L1 in the axial direction with respect to the first drive motor 47.

[0049] The second gear 492 meshes with the first gear 491. The second gear 492 is formed to have a larger diameter than the first gear 491.

[0050] The third gear 493 is connected so as to rotate integrally with the second gear 492. The third gear 493 is formed to have a smaller diameter than the second gear 492. In the present embodiment, the third gear 493 is disposed on the second side L2 in the axial direction with respect to the second gear 492.

[0051] The fourth gear 494 meshes with the third gear 493. The fourth gear 494 is formed to have a larger diameter than the third gear 493. In the present embodiment, the fourth gear 494 is disposed on the second axis X2.

[0052] The number of teeth of the second gear 492 is larger than the number of teeth of the first gear 491. And the number of teeth of the fourth gear 494 is larger than the number of teeth of the third gear 493 that rotates integrally with the second gear 492. Therefore, the rotation transmitted from the first drive motor 47 to the first gear 491 is decelerated between the first gear 491 and the second gear 492 and then transmitted to the third gear 493. And the rotation of the third gear 493 is decelerated between the third gear 493 and the fourth gear 494.

[0053] In the present embodiment, the first connecting member 483 connects the first screw shaft member 481 and the fourth gear 494. Specifically, a gear connecting portion 495 extending axially from the fourth gear 494 to the second side L2 in the axial direction is connected to the first connecting member 483 so as to rotate integrally therewith while being disposed inside the first radial direction RA with respect to the first connecting member 483. In the example shown in FIG. 3, a plurality of spline teeth extending in the axial direction L are formed on the inner peripheral portion of the first connecting member 483 in a circumferentially dispersed manner. And a plurality of spline teeth engaging with the plurality of spline teeth formed on the inner peripheral portion of the first connecting member 483 are formed on the outer peripheral portion of the gear connecting portion 495 in a circumferentially dispersed manner so as to extend in the axial direction L.

[0054] In the present embodiment, the first linear motion conversion mechanism 48 is disposed inside the first radial direction RA with respect to the first friction member 41 and the second friction member 42 and at a position overlapping the first friction member 41 and the second friction member 42 in a first radial direction view along the first radial direction RA. In the example shown in FIG. 3, the first screw shaft member 481, the first nut member 482, the first connecting member 483, and the first supported member 484 of the first linear motion conversion mechanism 48 are disposed inside the first radial direction RA with respect to the first friction member 41 and the second friction member 42 and at a position overlapping the first friction member 41 and the second friction member 42 in a first radial direction view along the first radial direction RA.

[0055] In the first friction engagement device 4, when the first pressing member 46 moves axially to the first side L1 and presses the first friction member 41 and the second friction member 42, the movement of the first friction member 41 and the second friction member 42 axially to the first side L1 is restricted by the first support wall portion 91 of the case 9 as the non-rotating member NR. As a result, the first friction member 41 and the second friction member 42 are connected so as not to be relatively rotatable with respect to each other, and the first friction engagement device 4 is in an engaged state. Therefore, when the first friction engagement device 4 is in the engaged state, the first support member 43 that supports the first friction member 41 is fixed to the second support member 44 fixed to the non-rotating member NR. At this time, the first fixed gear 22 connected to the first support member 43 is fixed to the non-rotating member NR. Therefore, the first fixed element 13 connected to rotate integrally with the first fixed gear 21 that meshes with the first fixed gear 22 is fixed to the non-rotating member NR.

[0056] On the other hand, when the first pressing member 46 moves axially to the second side L2 and the pressing of the first friction member 41 and the second friction member 42 by the first pressing member 46 is released, the first friction member 41 and the second friction member 42 are in a state where they can rotate relative to each other, and the first friction engagement device 4 is in a released state. When the first friction engagement device 4 is in the released state, the first support member 43 that supports the first friction member 41 is in a state where it can rotate relative to the second support member 44 fixed to the non-rotating member NR. At this time, the first fixed gear 22 connected to the first support member 43 is in a state where it can rotate relative to the non-rotating member NR. Therefore, the first fixed element 13 connected to rotate integrally with the first fixed gear 21 that meshes with the first fixed gear 22 is not fixed to the non-rotating member NR.

[0057] As shown in FIG. 4, the second friction engagement device 5 includes a third friction member 51, a fourth friction member 52, a third support member 53, a fourth support member 54, and a second pressing device 55.

[0058] The third friction member 51 and the fourth friction member 52 are arranged on the third axis X3. That is, the third friction member 51 and the fourth friction member 52 are arranged coaxially with the second fixed gear 32. The third friction member 51 and the fourth friction member 52 are arranged so as to face each other in the axial direction L. In the present embodiment, a plurality of the third friction members 51 and the fourth friction members 52 are provided, and these are alternately arranged along the axial direction L. Either the third friction member 51 or the fourth friction member 52 can be a friction plate, and the other can be a separator plate.

[0059] The third support member 53 is a member that supports the third friction member 51 while restricting the relative rotation of the third friction member 51. The third support member 53 is connected so as to rotate integrally with the second fixed gear 32. In the present embodiment, the third support member 53 is formed in a cylindrical shape extending along the axial direction L. And the third support member 53 supports the outer peripheral portion of the third friction member 51.

[0060] The fourth support member 54 is a member that supports the fourth friction member 52 while restricting the relative rotation of the fourth friction member 52. The fourth support member 54 is fixed to the non-rotating member NR. In the present embodiment, the fourth support member 54 is formed in a cylindrical shape extending along the axial direction L. And the fourth support member 54 supports the inner peripheral portion of the fourth friction member 52. Also, in the present embodiment, the fourth support member 54 is fixed to the second support wall portion 92 provided in the case 9 as the non-rotating member NR. The second support wall portion 92 is formed so as to extend along the second radial direction RB. And the second support wall portion 92 is arranged so as to cover the third friction member 51 and the fourth friction member 52 from the first axial side L1. In the example shown in FIG. 4, the fourth support member 54 is integrally formed with the second support wall portion 92 so as to protrude from the second support wall portion 92 toward the second axial side L2.

[0061] The second pressing device 55 is a device that presses the third friction member 51 and the fourth friction member 52 in the axial direction L. In the present embodiment, the second pressing device 55 includes a second pressing member 56 that applies a pressing force to the third friction member 51 and the fourth friction member 52, a second drive motor 57, and a screw-type second linear motion conversion mechanism 58 that converts the rotational driving force of the second drive motor 57 into a driving force in the axial direction L and transmits it to the second pressing member 56.

[0062] The second pressing member 56 is disposed at a position overlapping the third friction member 51 and the fourth friction member 52 in a view in the axial direction L along the axial direction. In the present embodiment, the second pressing member 56 is formed in a plate shape extending along the second radial direction RB.

[0063] The second drive motor 57 is a motor that generates a rotational driving force for driving the second pressing member 56. In the present embodiment, the second drive motor 57 is disposed outside the second radial direction RB with respect to the third support member 53 and at a position overlapping the third support member 53 in a view in the second radial direction along the second radial direction RB. Further, in the present embodiment, the second drive motor 57 is disposed at a position overlapping the planetary gear mechanism 1 in a view in the axial direction L along the axial direction.

[0064] In the present embodiment, the second linear motion conversion mechanism 58 includes a second screw shaft member 581, a second nut member 582, a second connecting member 583, a second supported member 584, and a second reduction mechanism 59.

[0065] The second screw shaft member 581 is formed to extend along the axial direction L. The second nut member 582 is formed in an annular shape that covers the second screw shaft member 581 from the outside in the second radial direction RB. The second screw shaft member 581 and the second nut member 582 are configured to be screwed together. Specifically, a male screw is formed on the outer peripheral portion of the second screw shaft member 581, and a female screw that screws with the male screw of the second screw shaft member 581 is formed on the inner peripheral portion of the second nut member 582. Therefore, when the second screw shaft member 581 rotates, the second nut member 582 performs a linear motion along the axial direction L according to the rotational direction and the directions of the male screw and the female screw.

[0066] The second nut member 582 is non-rotatable relative to the non-rotating member NR and is supported so as to be movable in the axial direction L. In the present embodiment, the second nut member 582 is disposed inside the second radial direction RB with respect to the fourth support member 54 fixed to the non-rotating member NR. And the second nut member 582 is non-rotatable relative to the fourth support member 54 and is connected so as to be relatively movable in the axial direction L via an annular second anti-rotation member 58a disposed between the second nut member 582 and the fourth support member 54 in the second radial direction RB. In the example shown in FIG. 4, on the outer peripheral portion of the second nut member 582, a plurality of spline teeth extending in the axial direction L are formed so as to be dispersed in the circumferential direction. And on the inner peripheral portion of the second anti-rotation member 58a, a plurality of spline teeth engaging with the plurality of spline teeth formed on the outer peripheral portion of the second nut member 582 are formed so as to be dispersed in the circumferential direction so as to extend in the axial direction L. Further, on the inner peripheral portion of the fourth support member 54, a plurality of spline teeth extending in the axial direction L are formed so as to be dispersed in the circumferential direction. And on the outer peripheral portion of the second anti-rotation member 58a, a plurality of spline teeth engaging with the plurality of spline teeth formed on the inner peripheral portion of the fourth support member 54 are formed so as to be dispersed in the circumferential direction so as to extend in the axial direction L.

[0067] Also, the second nut member 582 is connected so as to move integrally with the second pressing member 56 in the axial direction L. In the example shown in FIG. 4, the second nut member 582 is integrally formed with the second pressing member 56. Therefore, with the rotation of the second screw shaft member 581, the second pressing member 56 moves in the axial direction L via the second nut member 582.

[0068] The second connecting member 583 connects the second screw shaft member 581 and the second reduction mechanism 59. In the present embodiment, the second connecting member 583 is formed in a cylindrical shape extending from the second screw shaft member 581 to the first side L1 in the axial direction.

[0069] The second supported member 584 is supported in the axial direction L with respect to the non-rotating member NR. In the present embodiment, the second supported member 584 is formed so as to protrude outward in the second radial direction RB from the second connecting member 583. And the second supported member 584 is supported from the second axial side L2 via a second thrust bearing B2 by a support portion 54a formed so as to protrude inward in the second radial direction RB from a fourth support member 54 fixed to the non-rotating member NR.

[0070] The second speed reduction mechanism 59 is configured to reduce the rotation of the second drive motor 57. In the present embodiment, the second speed reduction mechanism 59 includes a fifth gear 591, a sixth gear 592, a seventh gear 593, and an eighth gear 594.

[0071] The fifth gear 591 is connected so as to rotate integrally with the output shaft of the second drive motor 57. In the present embodiment, the fifth gear 591 is disposed on the first axial side L1 with respect to the second drive motor 57.

[0072] The sixth gear 592 meshes with the fifth gear 591. The sixth gear 592 is formed to have a larger diameter than the fifth gear 591.

[0073] The seventh gear 593 is connected so as to rotate integrally with the sixth gear 592. The seventh gear 593 is formed to have a smaller diameter than the sixth gear 592. In the present embodiment, the seventh gear 593 is disposed on the second axial side L2 with respect to the sixth gear 592.

[0074] The eighth gear 594 meshes with the seventh gear 593. The eighth gear 594 is formed to have a larger diameter than the seventh gear 593. In the present embodiment, the eighth gear 594 is disposed on the third axis X3.

[0075] The number of teeth of the sixth gear 592 is larger than that of the fifth gear 591. And the number of teeth of the eighth gear 594 is larger than that of the seventh gear 593 that rotates integrally with the sixth gear 592. Therefore, the rotation transmitted from the second drive motor 57 to the fifth gear 591 is decelerated between the fifth gear 591 and the sixth gear 592 and then transmitted to the seventh gear 593. And the rotation of the seventh gear 593 is decelerated between the seventh gear 593 and the eighth gear 594.

[0076] In the present embodiment, the second connecting member 583 connects the second screw shaft member 581 and the eighth gear 594. Specifically, a gear connecting portion 595 extending axially from the eighth gear 594 to the second side L2 in the axial direction is connected to the second connecting member 583 so as to rotate integrally therewith while being disposed inside the second radial direction RB with respect to the second connecting member 583. In the example shown in FIG. 4, a plurality of spline teeth extending in the axial direction L are formed circumferentially dispersed on the inner peripheral portion of the second connecting member 583. And a plurality of spline teeth engaging with the plurality of spline teeth formed on the inner peripheral portion of the second connecting member 583 are formed circumferentially dispersed so as to extend in the axial direction L on the outer peripheral portion of the gear connecting portion 595.

[0077] In the present embodiment, the second linear motion conversion mechanism 58 is disposed inside the second radial direction RB with respect to the third friction member 51 and the fourth friction member 52 and at a position overlapping the third friction member 51 and the fourth friction member 52 in a second radial view along the second radial direction RB. In the example shown in FIG. 4, the second screw shaft member 581, the second nut member 582, the second connecting member 583, and the second supported member 584 of the second linear motion conversion mechanism 58 are disposed inside the second radial direction RB with respect to the third friction member 51 and the fourth friction member 52 and at a position overlapping the third friction member 51 and the fourth friction member 52 in a second radial view along the second radial direction RB.

[0078] In the second friction engagement device 5, when the second pressing member 56 moves to the first axial side L1 and presses the third friction member 51 and the fourth friction member 52, the movement of the third friction member 51 and the fourth friction member 52 toward the first axial side L1 is restricted by the second support wall portion 92 of the case 9 as the non-rotating member NR. As a result, the third friction member 51 and the fourth friction member 52 are connected so as not to be relatively rotatable with respect to each other, and the second friction engagement device 5 is brought into an engaged state. Therefore, when the second friction engagement device 5 is in the engaged state, the third support member 53 that supports the third friction member 51 is fixed to the fourth support member 54 fixed to the non-rotating member NR. At this time, the second fixed gear 32 connected to the third support member 53 is fixed to the non-rotating member NR. Therefore, the second fixed element 14 connected to rotate integrally with the second fixed gear 31 meshing with the second fixed gear 32 is fixed to the non-rotating member NR.

[0079] On the other hand, when the second pressing member 56 moves to the second axial side L2 and the pressing of the third friction member 51 and the fourth friction member 52 by the second pressing member 56 is released, the third friction member 51 and the fourth friction member 52 are in a state where they can rotate relative to each other, and the second friction engagement device 5 is in a released state. When the second friction engagement device 5 is in the released state, the third support member 53 that supports the third friction member 51 is in a state where it can rotate relative to the fourth support member 54 fixed to the non-rotating member NR. At this time, the second fixed gear 32 connected to the third support member 53 is in a state where it can rotate relative to the non-rotating member NR. Therefore, the second fixed element 14 connected to rotate integrally with the second fixed gear 31 meshing with the second fixed gear 32 is not fixed to the non-rotating member NR.

[0080] As shown in FIGS. 1 and 2, in the present embodiment, when the first friction engagement device 4 is in the engaged state, the first ring gear R11 having a relatively small diameter that meshes with the small-diameter pinion gear P12 is fixed to the non-rotating member NR. Further, when the second friction engagement device 5 is in the engaged state, the second ring gear R12 having a relatively large diameter that meshes with the large-diameter pinion gear P11 is fixed to the non-rotating member NR.

[0081] Therefore, in the present embodiment, when the first friction engagement device 4 is in the engaged state and the second friction engagement device 5 is in the released state, a gear stage (low speed stage) with a relatively large gear ratio is formed. Further, when the first friction engagement device 4 is in the released state and the second friction engagement device 5 is in the engaged state, a gear stage (high speed stage) with a relatively small gear ratio is formed.

[0082] Also, when both the first friction engagement device 4 and the second friction engagement device 5 are in the engaged state, the carrier C1 as the output element 12 is fixed to the non-rotating member NR. As a result, the wheel W drivingly connected to the output element 12 is locked. Thus, the first friction engagement device 4 and the second friction engagement device 5 function as a parking brake.

[0083] Also, when both the first friction engagement device 4 and the second friction engagement device 5 are in the released state, the first ring gear R11 of the first fixed element 13 and the second ring gear R12 of the second fixed element 14 are not fixed to the non-rotating member NR. As a result, the driving force of the drive source D cannot be transmitted to the wheel W (neutral state).

[0084] As described above, the transmission 10 includes a planetary gear mechanism 1 including an input element 11 drivingly connected to a drive source D of the wheel W, an output element 12 drivingly connected to the wheel W, a first fixed element 13, and a second fixed element 14, a first fixing device 2 that selectively fixes the first fixed element 13 to the non-rotating member NR, a second fixing device 3 that selectively fixes the second fixed element 14 to the non-rotating member NR, and is a transmission 10, the first fixing device 2 includes a first fixed gear 21 connected to rotate integrally with the first fixed element 13, a first fixing gear 22 meshing with the first fixed gear 21, and a first friction engagement device 4 that selectively engages the first fixing gear 22 with the non-rotating member NR, The second fixing device 3 includes a second fixed gear 31 that is connected to rotate integrally with the second fixing element 14, a second fixed gear 32 that meshes with the second fixed gear 31, and a second friction engagement device 5 that selectively engages the second fixed gear 32 with the non-rotating member NR. The first friction engagement device 4 is arranged coaxially with the first fixed gear 22. The second friction engagement device 5 is arranged coaxially with the second fixed gear 32. The rotation axis of the first fixed gear 22 and the rotation axis of the second fixed gear 32 are arranged parallel to each other. The first friction engagement device 4 and the second friction engagement device 5 are arranged so as not to overlap each other in an axial view along the axial direction L.

[0085] According to this configuration, the first fixing device 2 includes a first fixed gear 21 that is connected to rotate integrally with the first fixing element 13 of the planetary gear mechanism 1, a first fixed gear 22 that meshes with the first fixed gear 21, and a first friction engagement device 4 that selectively engages the first fixed gear 22 with the non-rotating member NR. And the first friction engagement device 4 is arranged coaxially with the first fixed gear 22. Further, the second fixing device 3 includes a second fixed gear 31 that is connected to rotate integrally with the second fixing element 14 of the planetary gear mechanism 1, a second fixed gear 32 that meshes with the second fixed gear 31, and a second friction engagement device 5 that selectively engages the second fixed gear 32 with the non-rotating member NR. And the second friction engagement device 5 is arranged coaxially with the second fixed gear 32. Thereby, it becomes easy to arrange the first friction engagement device 4 and the second friction engagement device 5 on different axes from each other. Therefore, compared with the configuration in which they are arranged coaxially, it is easy to keep the dimension of the transmission 10 in the axial direction L small. Further, according to this configuration, by setting the diameter of the first fixed gear 22 with respect to the first fixed gear 21 in the first fixing device 2 to be small, the torque required to fix the first fixing element 13 of the planetary gear mechanism 1 to the non-rotating member NR can be kept small. Thereby, it is easy to reduce the diameter of the first friction engagement device 4. Similarly, for the second fixing device 3, it is easy to reduce the diameter of the second friction engagement device 5. As described above, according to this configuration, in a configuration including a pair of friction engagement devices 4 and 5, it is easy to reduce the size of the transmission 10.

[0086] As described above, in the present embodiment, the first friction engagement device 4 includes a first friction member 41 disposed coaxially with the first fixed gear 22, a second friction member 42 disposed coaxially with the first fixed gear 22 and facing the first friction member 41 in the axial direction L, a first support member 43 connected to rotate integrally with the first fixed gear 22 and supporting the first friction member 41 in a state where relative rotation of the first friction member 41 is restricted, a second support member 44 fixed to the non-rotating member NR and supporting the second friction member 42 in a state where relative rotation of the second friction member 42 is restricted, and a first pressing device 45 that presses the first friction member 41 and the second friction member 42 in the axial direction L. The second friction engagement device 5 includes a third friction member 51 disposed coaxially with the second fixed gear 32, a fourth friction member 52 disposed coaxially with the second fixed gear 32 and facing the third friction member 51 in the axial direction L, a third support member 53 connected to rotate integrally with the second fixed gear 32 and supporting the third friction member 51 in a state where relative rotation of the third friction member 51 is restricted, a fourth support member 54 fixed to the non-rotating member NR and supporting the fourth friction member 52 in a state where relative rotation of the fourth friction member 52 is restricted, and a second pressing device 55 that presses the third friction member 51 and the fourth friction member 52 in the axial direction L. The first pressing device 45 includes a first pressing member 46 that applies a pressing force to the first friction member 41 and the second friction member 42, a first drive motor 47, and a screw-type first linear motion conversion mechanism 48 that converts the rotational driving force of the first drive motor 47 into a driving force in the axial direction L and transmits it to the first pressing member 46. The first linear motion conversion mechanism 48 is disposed inside the first friction member 41 and the second friction member 42 in the first radial direction RA and at a position overlapping the first friction member 41 and the second friction member 42 in a view in the first radial direction RA along the first radial direction RA. The second pressing device 55 includes a second pressing member 56 that applies a pressing force to the third friction member 51 and the fourth friction member 52, a second drive motor 57, and a screw-type second linear motion conversion mechanism 58 that converts the rotational driving force of the second drive motor 57 into a driving force in the second axial direction and transmits it to the second pressing member 56. The second linear motion conversion mechanism 58 is disposed inside the second radial direction RB with respect to the third friction member 51 and the fourth friction member 52, and at a position overlapping the third friction member 51 and the fourth friction member 52 in a second radial view along the second radial direction RB.

[0087] According to this configuration, the first friction engagement device 4 has a configuration including a first friction member 41, a second friction member 42, and a first support member 43 that are arranged coaxially with the first fixed gear 22. Therefore, compared with a configuration in which the first friction member 41, the second friction member 42, and the first support member 43 are arranged coaxially with the first fixed element 13 of the planetary gear mechanism 1, the dimension in the radial direction R of the first friction engagement device 4 can be easily suppressed to be small. Similarly, for the second fixing device 3, compared with a configuration in which the third friction member 51, the fourth friction member 52, and the third support member 53 are arranged coaxially with the second fixed element 14 of the planetary gear mechanism 1, the dimension in the radial direction R of the second friction engagement device 5 can be easily suppressed to be small. Also, according to this configuration, the first linear motion conversion mechanism 48 of the first pressing device 45 is arranged using the space inside the first radial direction RA with respect to the first friction member 41 and the second friction member 42, and the second linear motion conversion mechanism 58 of the second pressing device 55 is arranged using the space inside the second radial direction RB with respect to the third friction member 51 and the fourth friction member 52. Therefore, it is easy to reduce the size of the first friction engagement device 4 including the first pressing device 45 and the second friction engagement device 5 including the second pressing device 55, and thus to reduce the size of the transmission 10. Also, according to this configuration, the first pressing member 46 operates in the axial direction L by the screw-type first linear motion conversion mechanism 48, and the second pressing member 56 operates in the axial direction L by the screw-type second linear motion conversion mechanism 58. Thereby, even when the driving forces of the first drive motor 47 and the second drive motor 57 are not present, the positions of the first pressing member 46 and the second pressing member 56 can be held. Therefore, even when power is not supplied to the transmission 10, both the first friction engagement device 4 and the second friction engagement device 5 can be brought into an engaged state to lock the output element 12 of the planetary gear mechanism 1 so as not to rotate. Accordingly, it is possible to eliminate the need for separately providing a parking brake.

[0088] Also, as described above, in the present embodiment, the first fixed element 13 includes a first annular portion A11 formed in an annular shape and an internal gear first ring gear R11 provided on the inner peripheral surface of the first annular portion A11. The second fixed element 14 includes a second annular portion A12 formed in an annular shape and an internal gear second ring gear R12 provided on the inner peripheral surface of the second annular portion A12. The first fixed gear 21 is an external gear provided on the outer peripheral surface of the first annular portion A11. The second fixed gear 31 is an external gear provided on the outer peripheral surface of the second annular portion A12.

[0089] According to this configuration, it is easy to arrange the first fixed gear 21 and the second fixed gear 31 in the outer region in the radial direction R with respect to the planetary gear mechanism 1. Therefore, in a configuration in which the first fixed gear 21 meshes with the first fixed gear 22 and the second fixed gear 31 meshes with the second fixed gear 32, it is easy to reduce the size of the transmission 10.

[0090] As described above, in the present embodiment, the vehicle drive transmission device 100 includes a pair of transmissions 10. In the following description, one of the pair of transmissions 10 is referred to as the "first transmission 10A" and the other is referred to as the "second transmission 10B".

[0091] As shown in FIGS. 1 and 2, in the present embodiment, the vehicle drive transmission device 100 includes, in addition to the first transmission 10A and the second transmission 10B, a rotor shaft 6, a differential gear mechanism 7, a first output member 81, and a second output member 82.

[0092] The rotor shaft 6 is a shaft member that rotates integrally with the rotor RT of the rotating electric machine MG. In the present embodiment, the rotor shaft 6 is disposed on the first axis X1. Further, the rotor shaft 6 is formed in a cylindrical shape extending along the axial direction L. And the rotor shaft 6 is disposed so as to support the rotor RT from the inner side in the radial direction R.

[0093] The differential gear mechanism 7 includes a differential input element 71, a first differential output element 72, and a second differential output element 73. In the present embodiment, the differential gear mechanism 7 distributes the torque transmitted from the rotor shaft 6 to the differential input element 71 to the first differential output element 72 and the second differential output element 73. Also, in the present embodiment, the differential gear mechanism 7 is disposed on the first axis X1.

[0094] The differential input element 71 is an input element of the differential gear mechanism 7. In the present embodiment, the differential input element 71 is connected so as to rotate integrally with the rotor shaft 6. The first differential output element 72 and the second differential output element 73 are output elements of the differential gear mechanism 7.

[0095] Also, in the present embodiment, the differential gear mechanism 7 is a planetary gear type differential gear mechanism including a differential sun gear S2, a differential carrier C2, and a differential ring gear R2. Here, the differential gear mechanism 7 is a double pinion type planetary gear mechanism. Therefore, the differential carrier C2 rotatably supports an inner pinion gear P21 that meshes with the differential sun gear S2, and an outer pinion gear P22 that meshes with the inner pinion gear P21 and the differential ring gear R2.

[0096] In this embodiment, the differential ring gear R2 is connected so as to rotate integrally with the rotor shaft 6. That is, in this embodiment, the differential ring gear R2 functions as a differential input element 71. In the example shown in FIG. 1, the end portion on the first axial side L1 of the rotor shaft 6 extends radially outward in the radial direction R along the end face on the first axial side L1 of the rotor RT, and is connected to the differential ring gear R2.

[0097] In this embodiment, the differential carrier C2 functions as a first differential output element 72. And the differential sun gear S2 functions as a second differential output element 73.

[0098] The first output member 81 is drivingly connected to the first wheel W1 (see FIG. 2), which is the above-mentioned wheel W. The second output member 82 is drivingly connected to the second wheel W2 (see FIG. 2), which is the above-mentioned wheel W and is different from the first wheel W1. In this embodiment, the first output member 81 is connected via the first drive shaft DS1 (see FIG. 2) so as to rotate integrally with the first wheel W1. Further, the second output member 82 is connected via the second drive shaft DS2 (see FIG. 2) so as to rotate integrally with the second wheel W2. In this embodiment, the first output member 81 and the second output member 82 are arranged on the first axis X1. Note that the first wheel W1 and the second wheel W2 are a pair of left and right wheels (for example, a pair of left and right front wheels or a pair of left and right rear wheels).

[0099] In this embodiment, on the first axis X1, from the first axial side L1 toward the second axial side L2, the planetary gear mechanism 1 of the first transmission 10A, the differential gear mechanism 7, the rotating electric machine MG, and the planetary gear mechanism 1 of the second transmission 10B are arranged in the described order. That is, in this embodiment, the planetary gear mechanism 1 of the first transmission 10A and the planetary gear mechanism 1 of the second transmission 10B are separated and arranged on both sides in the axial direction L with respect to the rotating electric machine MG and the differential gear mechanism 7.

[0100] The input element 11 of the first transmission 10A is connected so as to rotate integrally with the first differential output element 72. In the present embodiment, the sun gear S1 as the input element 11 of the first transmission 10A is connected via the first connecting shaft J1 so as to rotate integrally with the differential carrier C2 as the first differential output element 72. The first connecting shaft J1 is a shaft member extending along the axial direction L so as to connect the sun gear S1 and the differential carrier C2 of the first transmission 10A.

[0101] The output element 12 of the first transmission 10A is connected so as to rotate integrally with the first output member 81. In the present embodiment, the carrier C1 as the output element 12 of the first transmission 10A is formed integrally with the first output member 81.

[0102] The input element 11 of the second transmission 10B is connected so as to rotate integrally with the second differential output element 73. In the present embodiment, the sun gear S1 as the input element 11 of the second transmission 10B is connected via the second connecting shaft J2 so as to rotate integrally with the differential sun gear S2 as the second differential output element 73. The second connecting shaft J2 is a shaft member extending along the axial direction L so as to connect the sun gear S1 and the differential sun gear S2 of the second transmission 10B. In the present embodiment, the second connecting shaft J2 is disposed so as to penetrate the inside in the radial direction R with respect to the rotor shaft 6 in the axial direction L.

[0103] The output element 12 of the second transmission 10B is connected so as to rotate integrally with the second output member 82. In the present embodiment, the carrier C1 as the output element 12 of the second transmission 10B is formed integrally with the second output member 82.

[0104] The first fixed gear 21 of the first transmission 10A and the first fixed gear 21 of the second transmission 10B are disposed on the first axis X1. That is, the first fixed gear 21 of the first transmission 10A and the first fixed gear 21 of the second transmission 10B are coaxially disposed.

[0105] The second fixed gear 31 of the first transmission 10A and the second fixed gear 31 of the second transmission 10B are arranged on the first axis X1. That is, the second fixed gear 31 of the first transmission 10A and the second fixed gear 31 of the second transmission 10B are coaxially arranged.

[0106] The first fixed gear 22 of the first transmission 10A and the first fixed gear 22 of the second transmission 10B are arranged on the second axis X2. That is, the first fixed gear 22 of the first transmission 10A and the first fixed gear 22 of the second transmission 10B are coaxially arranged. Further, the first fixed gear 22 of the first transmission 10A and the first fixed gear 22 of the second transmission 10B are connected so as to rotate integrally with each other. In the present embodiment, the first fixed gear 22 of the first transmission 10A and the first fixed gear 22 of the second transmission 10B are connected via a first fixed gear connecting member 221 so as to rotate integrally with each other. The first fixed gear connecting member 221 is a shaft member formed to extend along the axial direction L.

[0107] The second fixed gear 32 of the first transmission 10A and the second fixed gear 32 of the second transmission 10B are arranged on the third axis X3. That is, the second fixed gear 32 of the first transmission 10A and the second fixed gear 32 of the second transmission 10B are coaxially arranged. Further, the second fixed gear 32 of the first transmission 10A and the second fixed gear 32 of the second transmission 10B are connected so as to rotate integrally with each other. In the present embodiment, the second fixed gear 32 of the first transmission 10A and the second fixed gear 32 of the second transmission 10B are connected via a second fixed gear connecting member 321 so as to rotate integrally with each other. The second fixed gear connecting member 321 is a shaft member formed to extend along the axial direction L.

[0108] In this embodiment, the first fixed gear 22 of the first transmission 10A and the first fixed gear 22 of the second transmission 10B are connected via a first fixed gear connecting member 221 so as to rotate integrally with the first support member 43 of the first friction engagement device 4. Therefore, when the first friction engagement device 4 is in the engaged state, the first fixed gear 22 of the first transmission 10A and the first fixed gear 22 of the second transmission 10B are fixed with respect to the non-rotating member NR. On the other hand, when the first friction engagement device 4 is in the released state, the first fixed gear 22 of the first transmission 10A and the first fixed gear 22 of the second transmission 10B are in a state of being relatively rotatable with respect to the non-rotating member NR. Thus, in this embodiment, the first transmission 10A and the second transmission 10B share one first friction engagement device 4. That is, in this embodiment, the first friction engagement device 4 of the first transmission 10A and the first friction engagement device 4 of the second transmission 10B are common.

[0109] In this embodiment, the second fixed gear 32 of the first transmission 10A and the second fixed gear 32 of the second transmission 10B are connected via a second fixed gear connecting member 321 so as to rotate integrally with the third support member 53 of the second friction engagement device 5. Therefore, when the second friction engagement device 5 is in the engaged state, the second fixed gear 32 of the first transmission 10A and the second fixed gear 32 of the second transmission 10B are fixed with respect to the non-rotating member NR. On the other hand, when the second friction engagement device 5 is in the released state, the second fixed gear 32 of the first transmission 10A and the second fixed gear 32 of the second transmission 10B are in a state of being relatively rotatable with respect to the non-rotating member NR. Thus, in this embodiment, the first transmission 10A and the second transmission 10B share one second friction engagement device 5. That is, in this embodiment, the second friction engagement device 5 of the first transmission 10A and the second friction engagement device 5 of the second transmission 10B are common.

[0110] As described above, in this embodiment, the drive source D is a rotary electric machine MG having a rotor RT, The vehicle drive transmission device 100 is, a rotor shaft 6 that rotates integrally with the rotor RT, a first output member 81 that is drivingly connected to a first wheel W1 that is a vehicle wheel W, A wheel W, a second output member 82 drivingly connected to a second wheel W2 different from the first wheel W1, A differential gear mechanism 7 including a differential input element 71, a first differential output element 72, and a second differential output element 73 connected to rotate integrally with the rotor shaft 6, and distributing the torque transmitted from the rotor shaft 6 to the differential input element 71 to the first differential output element 72 and the second differential output element 73, A first transmission 10A which is the above-described transmission 10, A vehicle drive transmission device 100 including the above-described transmission 10 and a second transmission 10B different from the first transmission 10A, An input element 11 of the first transmission 10A is connected to rotate integrally with the first differential output element 72, An output element 12 of the first transmission 10A is connected to rotate integrally with the first output member 81, An input element 11 of the second transmission 10B is connected to rotate integrally with the second differential output element 73, An output element 12 of the second transmission 10B is connected to rotate integrally with the second output member 82, A first fixed gear 21 of the first transmission 10A and a first fixed gear 21 of the second transmission 10B are coaxially arranged, A first fixed gear 22 of the first transmission 10A and a first fixed gear 22 of the second transmission 10B are coaxially arranged and connected to rotate integrally with each other, A second fixed gear 31 of the first transmission 10A and a second fixed gear 31 of the second transmission 10B are coaxially arranged, A second fixed gear 32 of the first transmission 10A and a second fixed gear 32 of the second transmission 10B are coaxially arranged and connected to rotate integrally with each other, A first friction engagement device 4 of the first transmission 10A and a first friction engagement device 4 of the second transmission 10B are common, A second friction engagement device 5 of the first transmission 10A and a second friction engagement device 5 of the second transmission 10B are common.

[0111] According to this configuration, in a configuration in which a transmission 10 is provided in each of a power transmission path connecting the differential gear mechanism 7 and the first output member 81 and a power transmission path connecting the differential gear mechanism 7 and the second output member 82, a first fixed gear 22 constituting the first fixing device 2 of the pair of transmissions 10 is arranged coaxially and is connected so as to rotate integrally with each other. Also, second fixed gears 32 constituting the second fixing device 3 of the pair of transmissions 10 are arranged coaxially and are connected so as to rotate integrally with each other. Thereby, the pair of first fixed gears 22 can be selectively engaged with the non-rotating member NR by one first friction engagement device 4, and the pair of second fixed gears 32 can be selectively engaged with the non-rotating member NR by one second friction engagement device 5. Therefore, in a configuration including a pair of transmissions 10, it is easy to reduce the size of the pair of first fixing devices 2 and the pair of second fixing devices 3, and thus to reduce the size of the vehicle drive transmission device 100.

[0112] In the present embodiment, the first friction engagement device 4 and the second friction engagement device 5 are arranged such that the arrangement regions in their axial direction L overlap each other. And the first friction engagement device 4 and the second friction engagement device 5 are arranged so as not to overlap in the axial direction view along the axial direction L. Note that the first friction engagement device 4 and the second friction engagement device 5 may be arranged to be separated from each other in the axial direction L. In this case, for example, the first friction engagement device 4 and the second friction engagement device 5 may be arranged separately on both sides in the axial direction L with respect to the rotating electrical machine MG and the planetary gear mechanism 1 of the pair of transmissions 10. Also, the first friction engagement device 4 and the second friction engagement device 5 may be arranged so as to overlap in the axial direction view along the axial direction L.

[0113] 2. Second Embodiment Hereinafter, the vehicle drive transmission device 100 according to the second embodiment will be described with reference to FIGS. 5 to 8. In the present embodiment, there is one transmission 10 included in the vehicle drive transmission device 100, and the position of the transmission 10 in the power transmission path connecting the drive source D, the first output member 81, and the second output member 82 is different from that of the first embodiment. Hereinafter, the description will focus on the differences from the first embodiment. Note that points not particularly described are the same as those in the first embodiment.

[0114] As shown in FIGS. 5 to 7, in the present embodiment, the input element 11 of the transmission 10 is the first sun gear S11 and the second sun gear S12 that rotate integrally with each other. The first sun gear S11 meshes with the small-diameter pinion gear P12. The second sun gear S12 meshes with the large-diameter pinion gear P11. The second sun gear S12 is formed to have a smaller diameter than the first sun gear S11. In the present embodiment, the large-diameter pinion gear P11 and the small-diameter pinion gear P12 are supported so as to be relatively rotatable with respect to each other. Also, in the present embodiment, the second ring gear R12 that meshes with the large-diameter pinion gear P11 and the first ring gear R11 that meshes with the small-diameter pinion gear P12 are formed to have the same diameter. Further, in the present embodiment, the first fixed gear 21 that rotates integrally with the first ring gear R11 is formed to have a smaller diameter than the second fixed gear 31 that rotates integrally with the second ring gear R12.

[0115] Also, in the present embodiment, the input element 11 of the transmission 10 is connected so as to rotate integrally with the rotor shaft 6. Here, the first sun gear S11 and the second sun gear S12 as the input element 11 are formed on the input shaft 15 that is connected so as to rotate integrally with the rotor shaft 6. In the illustrated example, the second sun gear S12 is arranged on the second side L2 in the axial direction with respect to the first sun gear S11.

[0116] Further, in the present embodiment, the output element 12 of the transmission 10 is connected so as to rotate integrally with the external gear drive gear 16. The drive gear 16 is disposed on the first axis X1. In the present embodiment, the drive gear 16 is disposed on the second axial side L2 with respect to the planetary gear mechanism 1 of the transmission 10. And the drive gear 16 is disposed on the outer side in the radial direction R with respect to the input shaft 15.

[0117] In the present embodiment, the differential gear mechanism 7 is not disposed on the first axis X1, but is disposed on a fourth axis X4 different from the first axis X1, the second axis X2, and the third axis X3.

[0118] In the present embodiment, the differential input element 71 of the differential gear mechanism 7 is connected so as to rotate integrally with the external gear driven gear 74 that meshes with the drive gear 16. The driven gear 74 is disposed on the fourth axis X4. In the present embodiment, the driven gear 74 is on the outer side in the radial direction R with respect to the differential ring gear R2 as the differential input element 71, and is disposed at a position overlapping the differential ring gear R2 in a radial view along the radial direction R.

[0119] Further, in the present embodiment, the first differential output element 72 of the differential gear mechanism 7 is connected so as to rotate integrally with the first output member 81. And the second differential output element 73 of the differential gear mechanism 7 is connected so as to rotate integrally with the second output member 82. In the example shown in FIG. 5, the first output member 81 is formed so as to extend from the differential carrier C2 as the first differential output element 72 to the second axial side L2. And the second output member 82 is formed so as to extend from the differential sun gear S2 as the second differential output element 73 to the first axial side L1.

[0120] Thus, in the present embodiment, the differential gear mechanism 7 distributes the torque transmitted from the transmission 10 to the differential input element 71 to the first differential output element 72 and the second differential output element 73.

[0121] As shown in FIGS. 5 to 7, in the present embodiment, the first axis X1, the second axis X2, the third axis X3, and the fourth axis X4 are arranged parallel to each other. Further, as shown in FIG. 8, in the present embodiment, the second axis X2, the third axis X3, and the fourth axis X4 are arranged so as to surround the first axis X1. Specifically, in the axial view along the axial direction L, the first axis X1 is arranged inside a triangle (here, an acute triangle) having the second axis X2, the third axis X3, and the fourth axis X4 as vertices.

[0122] As described above, in the present embodiment, the drive source D is a rotary electric machine MG including a rotor RT. The vehicle drive transmission device 100 includes a rotor shaft 6 that rotates integrally with the rotor RT, a first output member 81 that is drivingly connected to a first wheel W1 that is a wheel W, a second output member 82 that is drivingly connected to a second wheel W2 that is a wheel W and is different from the first wheel W1, the above-described transmission 10, a differential gear mechanism 7 that includes a differential input element 71, a first differential output element 72, and a second differential output element 73, and distributes the torque transmitted from the transmission 10 to the differential input element 71 to the first differential output element 72 and the second differential output element 73. The vehicle drive transmission device 100 is The input element 11 of the transmission 10 is connected so as to rotate integrally with the rotor shaft 6. The output element 12 of the transmission 10 is connected so as to rotate integrally with an external gear drive gear 16. The differential input element 71 is connected so as to rotate integrally with an external gear driven gear 74 that meshes with the drive gear 16. The first differential output element 72 is connected so as to rotate integrally with the first output member 81. The second differential output element 73 is connected so as to rotate integrally with the second output member 82. Taking the axis on which the rotor shaft 6 and the planetary gear mechanism 1 of the transmission 10 are arranged as the first axis X1, the axis on which the first fixed gear 22 of the transmission 10 is arranged as the second axis X2, the axis on which the second fixed gear 32 of the transmission 10 is arranged as the third axis X3, and the axis on which the differential gear mechanism 7 is arranged as the fourth axis X4, The first axis X1, the second axis X2, the third axis X3, and the fourth axis X4 are arranged parallel to each other, and the second axis X2, the third axis X3, and the fourth axis X4 are arranged so as to surround the first axis X1.

[0123] According to this configuration, in the configuration where the planetary gear mechanism 1 of the transmission 10 is arranged coaxially with the rotor shaft 6 and the differential gear mechanism 7 is arranged on a different axis from the rotor shaft 6, the second axis X2 on which the first fixed gear 22 of the transmission 10 is arranged, the third axis X3 on which the second fixed gear 32 of the transmission 10 is arranged, and the fourth axis X4 on which the differential gear mechanism 7 is arranged are arranged so as to surround the rotor shaft 6 and the first axis X1 on which the planetary gear mechanism 1 of the transmission 10 is arranged. Therefore, it is easy to keep the dimension in the radial direction R with respect to the first axis X1 of the vehicle drive transmission device 100 small.

[0124] 3. Third Embodiment Hereinafter, the vehicle drive transmission device 100 according to the third embodiment will be described with reference to FIG. 9. In this embodiment, the configuration of the transmission 10 is different from that of the second embodiment described above. Hereinafter, the description will focus on the differences from the second embodiment. For points not particularly described, the same applies as in the second embodiment.

[0125] As shown in FIG. 9, in this embodiment, the input element 11 of the transmission 10 is the sun gear S1. And the output element 12 of the transmission 10 is the second ring gear R12. Also, the first fixed element 13 is the first ring gear R11. And the second fixed element 14 is the carrier C1.

[0126] In this embodiment, the carrier C1 rotatably supports a large-diameter pinion gear P11 and a small-diameter pinion gear P12 that rotate integrally with each other. The large-diameter pinion gear P11 meshes with both the sun gear S1 and the second ring gear R12. In this embodiment, the large-diameter pinion gear P11 is formed to have a smaller diameter than the sun gear S1. The small-diameter pinion gear P12 meshes with the first ring gear R11.

[0127] In this embodiment, the second fixed gear 31 is connected so as to rotate integrally with the carrier C1 as the second fixing element 14. And the second fixed gear 31 is arranged on the second side L2 in the axial direction with respect to the planetary gear mechanism 1.

[0128] Also, in this embodiment, the drive gear 16 is connected so as to rotate integrally with the second ring gear R12 as the output element 12. And the drive gear 16 is arranged on the first side L1 in the axial direction with respect to the planetary gear mechanism 1.

[0129] 4. Other Embodiments (1) In the above embodiment, the configuration in which each of the first pressing device 45 and the second pressing device 55 converts the rotational driving force of the drive motor into the driving force in the axial direction L by a screw-type linear motion conversion mechanism and transmits it to the pressing member has been described as an example. However, the configuration is not limited to such a configuration. For example, each of the first pressing device 45 and the second pressing device 55 may be configured to drive the pressing member by an electromagnetic actuator such as a solenoid. Alternatively, each of the first pressing device 45 and the second pressing device 55 may be configured to drive the pressing member by hydraulic pressure.

[0130] (2) In the above embodiment, the configuration in which the first support member 43 of the first friction engagement device 4 supports the outer peripheral portion of the first friction member 41 and the second support member 44 supports the inner peripheral portion of the second friction member 42 has been described as an example. However, the configuration is not limited to such a configuration, and a configuration in which the first support member 43 supports the inner peripheral portion of the first friction member 41 and the second support member 44 supports the outer peripheral portion of the second friction member 42 may also be used. Also, in the above embodiment, the configuration in which the third support member 53 of the second friction engagement device 5 supports the outer peripheral portion of the third friction member 51 and the fourth support member 54 supports the inner peripheral portion of the fourth friction member 52 has been described as an example. However, the configuration is not limited to such a configuration, and a configuration in which the third support member 53 supports the inner peripheral portion of the third friction member 51 and the fourth support member 54 supports the outer peripheral portion of the fourth friction member 52 may also be used.

[0131] (3) In the above-described embodiment, the configuration in which the first fixed gear 21 is an external gear provided on the outer peripheral surface of the first annular portion A11 has been described as an example. However, the present invention is not limited to such a configuration. For example, the first fixed gear 21 may be an internal gear provided on the inner peripheral surface of an annular portion different from the first annular portion A11. In this configuration, it is preferable to provide a member for connecting the annular portion provided with the first fixed gear 21 and the first annular portion A11 provided with the first ring gear R11.

[0132] (4) In the above-described embodiment, the configuration in which the differential gear mechanism 7 is a double pinion type planetary gear mechanism has been described as an example. However, the present invention is not limited to such a configuration. For example, the differential gear mechanism 7 may be a Ravigneaux type planetary gear mechanism. Alternatively, the differential gear mechanism 7 may not be a planetary gear type differential gear mechanism but a bevel gear type differential gear mechanism.

[0133] (5) Note that the configurations disclosed in the above-described embodiments can be applied in combination with the configurations disclosed in other embodiments as long as no contradiction occurs. Regarding other configurations as well, the embodiments disclosed in this specification are merely examples in all respects. Therefore, various modifications can be made as appropriate without departing from the spirit of the present disclosure.

[0134] Summary of the present embodiment Hereinafter, an overview of the transmission (10) and the vehicle drive transmission device (100) described above will be described.

[0135] The transmission (10) includes a planetary gear mechanism (1) including an input element (11) drivingly connected to a drive source (D) of a wheel (W), an output element (12) drivingly connected to the wheel (W), a first fixed element (13), and a second fixed element (14), a first fixing device (2) for selectively fixing the first fixed element (13) to a non-rotating member (NR), a second fixing device (3) for selectively fixing the second fixed element (14) to the non-rotating member (NR), and is a transmission (10). The first fixing device (2) includes a first fixed gear (21) connected to rotate integrally with the first fixing element (13), a first fixed gear (22) meshing with the first fixed gear (21), and a first friction engagement device (4) for selectively engaging the first fixed gear (22) with the non-rotating member (NR). The second fixing device (3) includes a second fixed gear (31) connected to rotate integrally with the second fixing element (14), a second fixed gear (32) meshing with the second fixed gear (31), and a second friction engagement device (5) for selectively engaging the second fixed gear (32) with the non-rotating member (NR). The first friction engagement device (4) is arranged coaxially with the first fixed gear (22). The second friction engagement device (5) is arranged coaxially with the second fixed gear (32). The rotation axis of the first fixed gear (22) and the rotation axis of the second fixed gear (32) are arranged parallel to each other. Taking the direction along the rotation axis of the first fixed gear (22) and the rotation axis of the second fixed gear (32) as the axial direction (L). The first friction engagement device (4) and the second friction engagement device (5) are arranged so as not to overlap each other in the axial direction view along the axial direction (L).

[0136] According to this configuration, the first fixing device (2) includes a first fixed gear (21) connected to rotate integrally with the first fixed element (13) of the planetary gear mechanism (1), a first fixed gear (22) meshing with the first fixed gear (21), and a first friction engagement device (4) for selectively engaging the first fixed gear (22) with a non-rotating member (NR). And the first friction engagement device (4) is arranged coaxially with the first fixed gear (22). Further, the second fixing device (3) includes a second fixed gear (31) connected to rotate integrally with the second fixed element (14) of the planetary gear mechanism (1), a second fixed gear (32) meshing with the second fixed gear (31), and a second friction engagement device (5) for selectively engaging the second fixed gear (32) with a non-rotating member (NR). And the second friction engagement device (5) is arranged coaxially with the second fixed gear (32). Thus, it is easy to arrange the first friction engagement device (4) and the second friction engagement device (5) on different axes from each other. Therefore, compared with the configuration in which they are arranged coaxially, it is easier to suppress the axial dimension (L) of the transmission (10) to be small. Also, according to this configuration, by setting the diameter of the first fixed gear (22) with respect to the first fixed gear (21) in the first fixing device (2) to be small, the torque required to fix the first fixed element (13) of the planetary gear mechanism (1) to the non-rotating member (NR) can be suppressed to be small. Thereby, it is easy to reduce the diameter of the first friction engagement device (4). Similarly, for the second fixing device (3), it is also easy to reduce the diameter of the second friction engagement device (5). As described above, according to this configuration, in the configuration including the pair of friction engagement devices (4, 5), it is easy to miniaturize the transmission (10).

[0137] Here, the first friction engagement device (4) includes a first friction member (41) disposed coaxially with the first fixed gear (22), a second friction member (42) disposed coaxially with the first fixed gear (22) and facing the first friction member (41) in the axial direction (L), a first support member (43) connected to rotate integrally with the first fixed gear (22) and supporting the first friction member (41) while restricting relative rotation of the first friction member (41), a second support member (44) fixed to the non-rotating member (NR) and supporting the second friction member (42) while restricting relative rotation of the second friction member (42), and a first pressing device (45) for pressing the first friction member (41) and the second friction member (42) in the axial direction (L). The second friction engagement device (5) includes a third friction member (51) disposed coaxially with the second fixed gear (32), a fourth friction member (52) disposed coaxially with the second fixed gear (32) and facing the third friction member (51) in the axial direction (L), a third support member (53) connected to rotate integrally with the second fixed gear (32) and supporting the third friction member (51) while restricting relative rotation of the third friction member (51), a fourth support member (54) fixed to the non-rotating member (NR) and supporting the fourth friction member (52) while restricting relative rotation of the fourth friction member (52), and a second pressing device (55) for pressing the third friction member (51) and the fourth friction member (52) in the axial direction (L). Taking the direction orthogonal to the rotation axis of the first fixed gear (22) as the first radial direction (RA) and the direction orthogonal to the rotation axis of the second fixed gear (32) as the second radial direction (RB). The first pressing device (45) includes a first pressing member (46) for applying a pressing force to the first friction member (41) and the second friction member (42), a first drive motor (47), and a screw-type first linear motion conversion mechanism (48) for converting the rotational driving force of the first drive motor (47) into a driving force in the axial direction (L) and transmitting it to the first pressing member (46). The first linear motion conversion mechanism (48) is located inside the first radial direction (RA) with respect to the first friction member (41) and the second friction member (42), and is arranged at a position overlapping the first friction member (41) and the second friction member (42) in a first radial view along the first radial direction (RA). The second pressing device (55) includes a second pressing member (56) that applies a pressing force to the third friction member (51) and the fourth friction member (52), a second drive motor (57), and a screw-type second linear motion conversion mechanism (58) that converts the rotational driving force of the second drive motor (57) into a driving force in the axial direction (L) and transmits it to the second pressing member (56). The second linear motion conversion mechanism (58) is preferably arranged inside the second radial direction (RB) with respect to the third friction member (51) and the fourth friction member (52), and at a position overlapping the third friction member (51) and the fourth friction member (52) in a second radial view along the second radial direction (RB).

[0138] According to this configuration, the first friction engagement device (4) has a configuration including a first friction member (41), a second friction member (42), and a first support member (43) arranged coaxially with the first fixed gear (22). Therefore, compared with a configuration in which the first friction member (41), the second friction member (42), and the first support member (43) are arranged coaxially with the first fixed element (13) of the planetary gear mechanism (1), it is easier to suppress the radial dimension (R) of the first friction engagement device (4) to be small. Similarly, for the second fixing device (3), compared with a configuration in which the third friction member (51), the fourth friction member (52), and the third support member (53) are arranged coaxially with the second fixed element (14) of the planetary gear mechanism (1), it is easier to suppress the radial dimension (R) of the second friction engagement device (5) to be small. Also, according to this configuration, the first linear motion conversion mechanism (48) of the first pressing device (45) is arranged using the space inside the first radial direction (RA) with respect to the first friction member (41) and the second friction member (42), and the second linear motion conversion mechanism (58) of the second pressing device (55) is arranged using the space inside the second radial direction (RB) with respect to the third friction member (51) and the fourth friction member (52). Therefore, it is easy to miniaturize the first friction engagement device (4) including the first pressing device (45) and, by extension, the second friction engagement device (5) including the second pressing device (55), and thus easy to miniaturize the transmission (10). Also, according to this configuration, the first pressing member (46) operates in the axial direction (L) by the screw-type first linear motion conversion mechanism (48), and the second pressing member (56) operates in the axial direction (L) by the screw-type second linear motion conversion mechanism (58). Thereby, the positions of the first pressing member (46) and the second pressing member (56) can be held even when the driving forces of the first drive motor (47) and the second drive motor (57) are not present. Therefore, even when power is not supplied to the transmission (10), both the first friction engagement device (4) and the second friction engagement device (5) can be brought into an engaged state to lock the output element (12) of the planetary gear mechanism (1) so that it does not rotate. Therefore, it is possible to eliminate the need for separately providing a parking brake.

[0139] Also, the drive source (D) is a rotating electric machine (MG) having a rotor (RT), The vehicle drive transmission device (100) is, a rotor shaft (6) that rotates integrally with the rotor (RT), a first output member (81) that is drivingly connected to a first wheel (W1) which is the wheel (W), a second output member (82) that is drivingly connected to a second wheel (W2) which is the wheel (W) and is different from the first wheel (W1), a differential gear mechanism (7) including a differential input element (71), a first differential output element (72), and a second differential output element (73) that are connected so as to rotate integrally with the rotor shaft (6), and that distributes the torque transmitted from the rotor shaft (6) to the differential input element (71) to the first differential output element (72) and the second differential output element (73), The first transmission (10A) which is the above-described transmission (10), A vehicle drive transmission device (100) including the second transmission (10B) which is the above-described transmission (10) and is different from the first transmission (10A), The input element (11) of the first transmission (10A) is connected so as to rotate integrally with the first differential output element (72), The output element (12) of the first transmission (10A) is connected so as to rotate integrally with the first output member (81), The input element (11) of the second transmission (10B) is connected so as to rotate integrally with the second differential output element (73), The output element (12) of the second transmission (10B) is connected so as to rotate integrally with the second output member (82), The first fixed gear (21) of the first transmission (10A) and the first fixed gear (21) of the second transmission (10B) are arranged coaxially, The first fixed gear (22) of the first transmission (10A) and the first fixed gear (22) of the second transmission (10B) are arranged coaxially and are connected so as to rotate integrally with each other, The second fixed gear (31) of the first transmission (10A) and the second fixed gear (31) of the second transmission (10B) are arranged coaxially, The second fixed gear (32) of the first transmission (10A) and the second fixed gear (32) of the second transmission (10B) are arranged coaxially and are connected so as to rotate integrally with each other, The first friction engagement device (4) of the first transmission (10A) and the first friction engagement device (4) of the second transmission (10B) are common, It is preferable that the second friction engagement device (5) of the first transmission (10A) and the second friction engagement device (5) of the second transmission (10B) are common.

[0140] According to this configuration, in a configuration in which a transmission (10) is provided in each of the power transmission paths connecting the differential gear mechanism (7) and the first output member (81), and the power transmission path connecting the differential gear mechanism (7) and the second output member (82), the first fixed gears (22) constituting the first fixing device (2) of the pair of transmissions (10) are arranged coaxially and are connected so as to rotate integrally with each other. Also, the second fixed gears (32) constituting the second fixing device (3) of the pair of transmissions (10) are arranged coaxially and are connected so as to rotate integrally with each other. Thereby, the pair of first fixed gears (22) can be selectively engaged with the non-rotating member (NR) by one first friction engagement device (4), and the pair of second fixed gears (32) can be selectively engaged with the non-rotating member (NR) by one second friction engagement device (5). Therefore, in a configuration including a pair of transmissions (10), it is easy to reduce the size of the pair of first fixing devices (2) and the pair of second fixing devices (3), and by extension, the size of the vehicle drive transmission device (100).

[0141] Also, the drive source (D) is a rotating electric machine (MG) having a rotor (RT). The vehicle drive transmission device (100) is a rotor shaft (6) that rotates integrally with the rotor (RT), a first output member (81) that is drivingly connected to a first wheel (W1) which is the wheel (W), a second output member (82) that is drivingly connected to a second wheel (W2) which is the wheel (W) and is different from the first wheel (W1), the above-described transmission (10), a differential gear mechanism (7) including a differential input element (71), a first differential output element (72), and a second differential output element (73), which distributes the torque transmitted from the transmission (10) to the differential input element (71) to the first differential output element (72) and the second differential output element (73), and is a vehicle drive transmission device (100), the input element (11) of the transmission (10) is connected so as to rotate integrally with the rotor shaft (6). The output element (12) of the transmission (10) is connected so as to rotate integrally with the externally toothed driving gear (16). The differential input element (71) is connected so as to rotate integrally with the externally toothed driven gear (74) that meshes with the driving gear (16). The first differential output element (72) is connected so as to rotate integrally with the first output member (81). The second differential output element (73) is connected so as to rotate integrally with the second output member (82). Taking the axis on which the rotor shaft (6) and the planetary gear mechanism (1) of the transmission (10) are arranged as the first axis (X1), the axis on which the first fixed gear (22) of the transmission (10) is arranged as the second axis (X2), the axis on which the second fixed gear (32) of the transmission (10) is arranged as the third axis (X3), and the axis on which the differential gear mechanism (7) is arranged as the fourth axis (X4), the first axis (X1), the second axis (X2), the third axis (X3), and the fourth axis (X4) are arranged parallel to each other. Preferably, the second axis (X2), the third axis (X3), and the fourth axis (X4) are arranged so as to surround the first axis (X1).

[0142] According to this configuration, in a configuration where the planetary gear mechanism (1) of the transmission (10) is arranged coaxially with the rotor shaft (6) and the differential gear mechanism (7) is arranged on a different axis from the rotor shaft (6), the second axis (X2) on which the first fixed gear (22) of the transmission (10) is arranged, the third axis (X3) on which the second fixed gear (32) of the transmission (10) is arranged, and the fourth axis (X4) on which the differential gear mechanism (7) is arranged are arranged so as to surround the first axis (X1) on which the rotor shaft (6) and the planetary gear mechanism (1) of the transmission (10) are arranged. Therefore, it is easy to suppress the radial (R) dimension of the vehicle drive transmission device (100) with respect to the first axis (X1).

Industrial Applicability

[0143] The technology according to the present disclosure can be used in a transmission including a planetary gear mechanism having an input element drivingly connected to a drive source of a wheel, an output element drivingly connected to the wheel, a first fixed element, and a second fixed element, a first fixing device for selectively fixing the first fixed element to a non-rotating member, and a second fixing device for selectively fixing the second fixed element to a non-rotating member, and a vehicle drive transmission device including the same.

Explanation of Signs

[0144] 100: Vehicle drive transmission device, 10: Transmission, 10A: First transmission, 10B: Second transmission, 1: Planetary gear mechanism, 11: Input element, 12: Output element, 13: First fixed element, 14: Second fixed element, 16: Drive gear, 2: First fixing device, 21: First fixed gear, 22: First fixing gear, 3: Second fixing device, 31: Second fixed gear, 32: Second fixing gear, 4: First friction engagement device, 41: First friction member, 42: Second friction member, 43: First support member, 44: Second support member, 45: First pressing device, 46: First pressing member, 47: First drive motor, 48: First linear motion conversion mechanism, 5: Second friction engagement device, 51: Third friction member, 52: Fourth friction member, 53: Third support member, 54: Fourth support member, 55: Second pressing device, 56: Second pressing member, 57: Second drive motor, 58: Second linear motion conversion mechanism, 6: Rotor shaft, 7: Differential gear mechanism, 71: Differential input element, 72: First differential output element, 73: Second differential output element, 74: Driven gear, 81: First output member, 82: Second output member, D: Drive source, MG: Rotating electric machine, ST: Stator, RT: Rotor, A11: First annular portion, A12: Second annular portion, R11: First ring gear, R12: Second ring gear, NR: Non-rotating member, W: Wheel, W1: First wheel, W2: Second wheel, L: Axial direction, RA: First radial direction, RB: Second radial direction, X1: First axis, X2: Second axis, X3: Third axis, X4: Fourth axis

Claims

1. A planetary gear mechanism including an input element drivingly connected to a drive source of a wheel, an output element drivingly connected to the wheel, a first fixed element, and a second fixed element; a first fixing device for selectively fixing the first fixed element to a non-rotating member; a second fixing device for selectively fixing the second fixed element to the non-rotating member, the transmission comprising: the first fixing device includes a first fixed gear connected to rotate integrally with the first fixed element, a first fixing gear meshing with the first fixed gear, and a first friction engaging device for selectively engaging the first fixing gear with the non-rotating member; the second fixing device includes a second fixed gear connected to rotate integrally with the second fixed element, a second fixing gear meshing with the second fixed gear, and a second friction engaging device for selectively engaging the second fixing gear with the non-rotating member; the first friction engaging device is disposed coaxially with the first fixing gear; the second friction engaging device is disposed coaxially with the second fixing gear; the rotation axis of the first fixing gear and the rotation axis of the second fixing gear are arranged parallel to each other; with the direction along the rotation axis of the first fixing gear and the rotation axis of the second fixing gear as the axial direction, the first friction engaging device and the second friction engaging device are arranged so as not to overlap each other in an axial view along the axial direction. A transmission.

2. The first friction engaging device includes a first friction member disposed coaxially with the first fixing gear, a second friction member disposed coaxially with the first fixing gear and facing the first friction member in the axial direction, and a first friction member connected to rotate integrally with the first fixing gear. A first support member that supports the first friction member while restricting relative rotation of the first friction member, a second support member fixed to the non-rotating member and supporting the second friction member while restricting relative rotation of the second friction member, and the first friction member and the second friction member. And a first pressing device for pressing in the axial direction. The second friction engagement device includes a third friction member arranged coaxially with the second fixed gear, a fourth friction member arranged coaxially with the second fixed gear and facing the third friction member in the axial direction, a third support member connected to rotate integrally with the second fixed gear and supporting the third friction member while restricting relative rotation of the third friction member, a fourth support member fixed to the non-rotating member and supporting the fourth friction member while restricting relative rotation of the fourth friction member, and a second pressing device for pressing the third friction member and the fourth friction member in the axial direction. Taking the direction perpendicular to the rotation axis of the first fixed gear as the first radial direction and the direction perpendicular to the rotation axis of the second fixed gear as the second radial direction, The first pressing device includes a first pressing member for applying a pressing force to the first friction member and the second friction member, a first drive motor, and a screw-type first linear motion conversion mechanism for converting the rotational driving force of the first drive motor into an axial driving force and transmitting it to the first pressing member. The first linear motion conversion mechanism is arranged inside the first friction member and the second friction member in the first radial direction and at a position overlapping the first friction member and the second friction member in a first radial view along the first radial direction. The second pressing device includes a second pressing member for applying a pressing force to the third friction member and the fourth friction member, a second drive motor, and a screw-type second linear motion conversion mechanism for converting the rotational driving force of the second drive motor into an axial driving force and transmitting it to the second pressing member. The second linear motion conversion mechanism is arranged inside the third friction member and the fourth friction member in the second radial direction and at a position overlapping the third friction member and the fourth friction member in a second radial view along the second radial direction. The transmission according to claim 1.

3. The drive source is a rotary electric machine having a rotor, a rotor shaft rotating integrally with the rotor, a first output member drivingly connected to the first wheel which is the wheel, a second output member drivingly connected to a second wheel which is the wheel and different from the first wheel, a differential input element, a first differential output element, and a second differential output element connected to rotate integrally with the rotor shaft, and a differential gear mechanism for distributing the torque transmitted from the rotor shaft to the differential input element to the first differential output element and the second differential output element. A first transmission that is the transmission according to claim 1, A vehicle drive transmission device including a second transmission that is the transmission according to claim 1 and is different from the first transmission, The input element of the first transmission is connected so as to rotate integrally with the first differential output element, The output element of the first transmission is connected so as to rotate integrally with the first output member, The input element of the second transmission is connected so as to rotate integrally with the second differential output element, The output element of the second transmission is connected so as to rotate integrally with the second output member, The first fixed gear of the first transmission and the first fixed gear of the second transmission are arranged coaxially, The first fixed gear of the first transmission and the first fixed gear of the second transmission are arranged coaxially and are connected so as to rotate integrally with each other, The second fixed gear of the first transmission and the second fixed gear of the second transmission are arranged coaxially, The second fixed gear of the first transmission and the second fixed gear of the second transmission are arranged coaxially and are connected so as to rotate integrally with each other, The first friction engagement device of the first transmission and the first friction engagement device of the second transmission are common, A vehicle drive transmission device in which the second friction engagement device of the first transmission and the second friction engagement device of the second transmission are common.

4. The drive source is a rotary electric machine including a rotor, A rotor shaft that rotates integrally with the rotor, A first output member that is drivingly connected to a first wheel that is the wheel, A second output member that is drivingly connected to a second wheel that is the wheel and is different from the first wheel, The transmission according to claim 1, A vehicle drive transmission device including a differential input element, a first differential output element, and a second differential output element, and a differential gear mechanism that distributes the torque transmitted from the transmission to the differential input element to the first differential output element and the second differential output element, The input element of the transmission is connected so as to rotate integrally with the rotor shaft, The output element of the transmission is connected so as to rotate integrally with an external-tooth drive gear, The differential input element is connected so as to rotate integrally with an external-tooth driven gear that meshes with the drive gear, The first differential output element is connected so as to rotate integrally with the first output member, The second differential output element is connected so as to rotate integrally with the second output member. Taking the shaft on which the rotor shaft and the planetary gear mechanism of the transmission are arranged as the first shaft, the shaft on which the first fixed gear of the transmission is arranged as the second shaft, the shaft on which the second fixed gear of the transmission is arranged as the third shaft, and the shaft on which the differential gear mechanism is arranged as the fourth shaft, the first shaft, the second shaft, the third shaft, and the fourth shaft are arranged parallel to each other. A vehicle drive transmission device, wherein the second shaft, the third shaft, and the fourth shaft are arranged so as to surround the first shaft.

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