Transmission and vehicle drive transmission device provided with same

Abstract

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

Description

Technical Field

[0001] The present invention relates to a transmission and a drive transmission device for a vehicle equipped with the transmission, wherein the transmission comprises: a planetary gear mechanism having 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 fixed device selectively fixing the first fixed element to a non-rotating component; and a second fixed device selectively fixing the second fixed element to a non-rotating component. Background Art

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

[0003] In the transmission of patent document 1, the planetary gear mechanism (5) comprises: a planetary carrier (53) that supports a large diameter pinion (52a) and a small diameter pinion (52b) that rotate integrally with each other so as to rotate freely; a sun gear (51) that rotates integrally with a rotor (32) of a rotating electric machine (3) and meshes with the large diameter pinion (52a); a first ring gear (54a) that meshes with the large diameter pinion (52a); and a second ring gear (55a) that meshes with the small diameter pinion (52b).

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

[0005] Patent Document 1: Japanese Patent Application Publication No. 2013-200012

[0006] In the transmission of Patent Document 1, a first friction engagement device (61) constituting a first fixing device and a second friction engagement device (62) constituting a second fixing device are axially spaced apart (the first friction engagement device (61) and the second fixing device (62) are axially spaced apart (the second friction engagement device (62) and the second fixing device) are axially spaced apart (the first friction engagement device (61) and the second fixing device) are axially spaced apart (the second friction engagement device Figure 1 Therefore, the speed changer tends to be large in the axial direction.

[0007] Furthermore, the first friction engagement device (61) and the second friction engagement device (62) are arranged radially outwardly relative to the planetary gear mechanism (5) (see Patent Document 1). Figure 1 Therefore, the transmission tends to be larger in the radial direction.

[0008] Therefore, in a structure including a pair of friction engagement devices, realization of a technology that facilitates miniaturization of the transmission is desired. Summary of the invention

[0009] In view of the above, the characteristic structure of the speed changer is that it has:

[0010] 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;

[0011] A first fixing device selectively fixes the first fixing element to a non-rotating component; and

[0012] A second fixing device selectively fixes the second fixing element to the non-rotating component.

[0013] The first fixing device comprises: a first fixed gear connected to rotate integrally with the first fixing element; a first fixing gear meshing with the first fixed gear; and a first friction engagement device for selectively engaging the first fixing gear with the non-rotating member.

[0014] The second fixing device comprises: a second fixed gear connected to rotate integrally with the second fixing element; a second fixing gear meshing with the second fixed gear; and a second friction engagement device for selectively engaging the second fixing gear with the non-rotating member.

[0015] The first friction engagement device and the first fixed gear are arranged on the same axis.

[0016] The second friction engagement device and the second fixed gear are arranged on the same axis.

[0017] The rotation axis of the first fixed gear and the rotation axis of the second fixed gear are arranged parallel to each other.

[0018] The direction along the rotation axis of the first fixed gear and the rotation axis of the second fixed gear is defined as the axial direction.

[0019] The first friction engagement device and the second friction engagement device are arranged so as not to overlap each other when viewed in the axial direction along the axial direction.

[0020] According to this characteristic structure, the first fixing device comprises: 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, which selectively engages the first fixed gear with a non-rotating component. Moreover, the first friction engagement device and the first fixed gear are arranged on the same axis. In addition, the second fixing device comprises: 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, which selectively engages the second fixed gear with a non-rotating component. Moreover, the second friction engagement device and the second fixed gear are arranged on the same axis. As a result, it is easy to arrange the first friction engagement device and the second friction engagement device on different axes. Therefore, compared with a structure in which they are arranged on the same axis, it is easy to suppress the axial size of the transmission to be small.

[0021] In addition, according to this characteristic structure, the diameter of the first fixed gear relative to the first fixed gear is set small in the first fixing device, thereby being able to suppress the torque required to fix the first fixed element of the planetary gear mechanism to the non-rotating member. As a result, it is easy to reduce the diameter of the first friction engagement device. In addition, the same is true for the second fixing device, and it is easy to reduce the diameter of the second friction engagement device.

[0022] As described above, according to this characteristic structure, in a structure including a pair of friction engagement devices, it is easy to achieve miniaturization of the transmission.

[0023] In view of the above, the characteristic structure of the vehicle drive transmission device is that:

[0024] The driving source is a rotating electric machine having a rotor.

[0025] The vehicle drive transmission device comprises:

[0026] a rotor shaft, rotating integrally with the rotor;

[0027] A first output member drivingly connected to a first wheel as the above-mentioned wheel;

[0028] a second output member drivingly connected to a second wheel different from the first wheel;

[0029] a differential gear mechanism including a differential input element connected to rotate integrally with the rotor shaft, a first differential output element, and a second differential output element, and distributing a torque transmitted from the rotor shaft to the differential input element to the first differential output element and the second differential output element;

[0030] The transmission described in claim 1 is a first transmission; and

[0031] The second transmission is different from the transmission described in claim 1 and is the first transmission.

[0032] The input element of the first transmission is connected to rotate integrally with the first differential output element,

[0033] The output element of the first transmission is connected to rotate integrally with the first output member,

[0034] The input element of the second transmission is connected to rotate integrally with the second differential output element,

[0035] The output element of the second transmission is connected to rotate integrally with the second output member,

[0036] The first fixed gear of the first transmission and the first fixed gear of the second transmission are arranged on the same axis.

[0037] The first fixed gear of the first transmission and the first fixed gear of the second transmission are coaxially arranged and connected to rotate integrally with each other.

[0038] The second fixed gear of the first transmission and the second fixed gear of the second transmission are arranged on the same axis.

[0039] The second fixed gear of the first transmission and the second fixed gear of the second transmission are coaxially arranged and connected to rotate integrally with each other.

[0040] The first friction engagement device of the first transmission is shared with the first friction engagement device of the second transmission.

[0041] The second friction engagement device of the first transmission is commonly used with the second friction engagement device of the second transmission.

[0042] According to this characteristic structure, in a structure in which a transmission is provided in each of the power transmission path connecting the differential gear mechanism and the first output member and the power transmission path connecting the differential gear mechanism and the second output member, the first fixed gear constituting the first fixing device of the pair of transmissions is arranged on the same axis and connected to rotate integrally with each other. In addition, the second fixed gear constituting the second fixing device of the pair of transmissions is arranged on the same axis and connected to rotate integrally with each other. Thus, the pair of first fixed gears can be selectively engaged with the non-rotating member by a first friction engagement device, and the pair of second fixed gears can be selectively engaged with the non-rotating member by a second friction engagement device.

[0043] Therefore, in the configuration including the pair of transmissions, it is easy to achieve miniaturization of the pair of first fixing devices and the pair of second fixing devices, and miniaturization of the vehicle drive transmission device.

[0044] In view of the above, the characteristic structure of the vehicle drive transmission device is that:

[0045] The driving source is a rotating electric machine having a rotor.

[0046] The vehicle drive transmission device comprises:

[0047] a rotor shaft, rotating integrally with the rotor;

[0048] A first output member drivingly connected to a first wheel as the above-mentioned wheel;

[0049] a second output member drivingly connected to a second wheel different from the first wheel;

[0050] The transmission as claimed in claim 1; and

[0051] The differential gear mechanism includes a differential input element, a first differential output element, and a second differential output element, and distributes the torque transmitted from the transmission to the differential input element to the first differential output element and the second differential output element.

[0052] The input element of the transmission is connected to rotate integrally with the rotor shaft.

[0053] The output element of the transmission is connected to the externally toothed drive gear so as to rotate integrally.

[0054] The differential input element is connected to rotate integrally with a driven gear having external teeth meshing with the driving gear.

[0055] The first differential output element is connected to rotate integrally with the first output member.

[0056] The second differential output element is connected to rotate integrally with the second output member.

[0057] The shaft of the planetary gear mechanism on which the rotor shaft and the transmission are arranged is set as a first shaft, the shaft of the first fixed gear of the transmission is set as a second shaft, the shaft of the second fixed gear of the transmission is set as a third shaft, and the shaft of the differential gear mechanism is set as a fourth shaft.

[0058] The first axis, the second axis, the third axis, and the fourth axis are arranged parallel to each other.

[0059] The second axis, the third axis, and the fourth axis are arranged to surround the first axis.

[0060] According to this characteristic structure, in a structure in which the planetary gear mechanism of the transmission is arranged on the same axis as the rotor shaft, and the differential gear mechanism is arranged on a different axis 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 relative to the first shaft to be small. BRIEF DESCRIPTION OF THE DRAWINGS

[0061] Figure 1 It is a cross-sectional view along the axial direction of the vehicle drive transmission device according to the first embodiment.

[0062] Figure 2 It is a schematic diagram of the vehicle drive transmission device according to the first embodiment.

[0063] Figure 3 It is a cross-sectional view of the first friction engagement device of the vehicle drive transmission device according to the first embodiment.

[0064] Figure 4 It is a cross-sectional view of the second friction engagement device of the vehicle drive transmission device according to the first embodiment.

[0065] Figure 5 yes Figure 8 VV section view in.

[0066] Figure 6 yes Figure 8 VI-VI section view in.

[0067] Figure 7 It is a schematic diagram of a vehicle drive transmission device according to a second embodiment.

[0068] Figure 8 It is a diagram showing the positional relationship of each element in the vehicle drive transmission device according to the second embodiment when viewed in the axial direction.

[0069] Fig. 9 It is a schematic diagram of a vehicle drive transmission device according to a third embodiment. DETAILED DESCRIPTION

[0070] 1. First Implementation

[0071] Below, refer to Figures 1 to 4 A vehicle drive transmission device 100 according to a first embodiment will be described.

[0072] like Figure 1 as well as Figure 2 As shown, 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.

[0073] The planetary gear mechanism 1 includes: Figure 2 )'s driving source D, an input element 11 drivingly connected to the wheel W, an output element 12 drivingly connected to the wheel W, a first fixed element 13, and a second fixed element 14.

[0074] Here, in the present application, "drive connection" refers to a state in which two rotating members are connected to be able to transmit driving force, including a state in which the two rotating members are connected to rotate as a whole, or a state in which the two rotating members are connected to be able to transmit driving force via one or more transmission parts. Such transmission parts include various parts that transmit rotation at the same speed or at a variable speed, such as shafts, gear mechanisms, belts, chains, etc. In addition, as transmission parts, engaging devices that selectively transmit rotation and driving force may also be included, such as friction engaging devices, meshing engaging devices, etc. However, with respect to the rotating members of the planetary gear mechanism, when referred to as "drive connection", it refers to a state in which they are connected to each other without passing through other rotating members.

[0075] In the present embodiment, the rotating electrical machine MG including the stator ST and the rotor RT corresponds to the driving source D. In the present application, the term "rotating electrical machine" is used as a concept including a motor (electric motor), a generator (generator), and a motor / generator that realizes the functions of both a motor and a generator as needed.

[0076] In the present embodiment, the planetary gear mechanism 1 is arranged on the first axis X1 which is the rotation axis center of the rotor RT of the rotary electric machine MG.

[0077] In the present embodiment, the input element 11 is a sun gear S1. Moreover, the output element 12 is a planetary carrier C1. In addition, in the present embodiment, the first fixed element 13 includes: a first annular portion A11 formed in an annular shape, and a first ring gear R11 with internal teeth provided on the inner circumference of the first annular portion A11. Moreover, the second fixed element 14 includes: a second annular portion A12 formed in an annular shape, and a second ring gear R12 with internal teeth provided on the inner circumference of the second annular portion A12.

[0078] In this embodiment, the planetary carrier C1 supports the large-diameter pinion P11 and the small-diameter pinion P12 which rotate integrally with each other so as to rotate freely. The large-diameter pinion P11 and the small-diameter pinion P12 rotate (rotate) around their own axes respectively, and rotate (revolve) with the planetary carrier C1 around the sun gear S1 as the center. A plurality of large-diameter pinions P11 and small-diameter pinions P12 are provided at intervals along their own revolution trajectories.

[0079] The large diameter pinion P11 meshes with both the sun gear S1 and the second ring gear R12. In the present embodiment, the large diameter pinion P11 is formed to have a larger diameter than the sun gear S1. The small diameter pinion P12 meshes with the first ring gear R11. The small diameter pinion P12 is formed to have a smaller diameter than the large diameter pinion P11.

[0080] The first fixing device 2 is a device for selectively fixing the first fixing element 13 of the planetary gear mechanism 1 to the non-rotating member NR. In addition, the second fixing device 3 is a device for selectively fixing 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 a housing 9 that accommodates the structural elements of the vehicle drive transmission device 100 including the transmission 10.

[0081] The first fixing device 2 includes a first fixed gear 21 , a first fixing gear 22 , and a first friction engagement device 4 .

[0082] The first fixed gear 21 is connected to rotate integrally with the first fixed element 13 of the planetary gear mechanism 1. The first fixed gear 22 is configured to mesh with the first fixed gear 21. In the present embodiment, the first fixed gear 21 is a gear with external teeth provided on the outer peripheral surface of the first annular portion A11. In addition, in the present embodiment, the first fixed gear 21 is formed to have a larger diameter than the large-diameter pinion P11. Moreover, the first fixed gear 22 is formed to have a smaller diameter than the first fixed gear 21. In addition, in the present embodiment, the first fixed gear 21 is configured on the first axis X1. Moreover, the first fixed gear 22 is configured on a second axis X2 different from the first axis X1.

[0083] The first friction engagement device 4 is a device that selectively engages the first fixed gear 22 with the non-rotating member NR. The detailed structure of the first friction engagement device 4 will be described later.

[0084] The second fixing device 3 includes a second fixed gear 31 , a second fixing gear 32 , and a second friction engagement device 5 .

[0085] The second fixed gear 31 is connected to rotate integrally with the second fixed element 14 of the planetary gear mechanism 1. The second fixed gear 32 is configured 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. In addition, in the present embodiment, the second fixed gear 31 is formed to have a larger diameter than the large-diameter pinion P11. Moreover, the second fixed gear 31 is formed to have the same diameter as the first fixed gear 21. In addition, 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 configured on the first axis X1. Moreover, the second fixed gear 32 is configured on a third axis X3 different from the first axis X1 and the second axis X2.

[0086] 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 structure of the second friction engagement device 5 will be described later.

[0087] 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 referred to as "axial direction L". In addition, one side of the axial direction L is referred to as "axial first side L1", and the other side of the axial direction L is referred to as "axial second side L2".

[0088] In addition, the direction orthogonal to the rotation axis of the first fixed gear 22 (here, the second axis X2) is referred to as the "first radial direction RA". Furthermore, the direction orthogonal to the rotation axis of the second fixed gear 32 (here, the third axis X3) is referred to as the "second radial direction RB". In addition, hereinafter, the direction including the first radial direction RA and the second radial direction RB and orthogonal to the rotation axis of any rotating component is referred to as the "radial direction R". That is, the radial direction R is defined with reference to the rotation axis of the rotating components such as the first fixed gear 22 and the second fixed gear 32. In addition, when it is not necessary to distinguish which rotation axis is used as the reference, or when it is clear which rotation axis is used as the reference, it is sometimes simply referred to as the "radial direction R".

[0089] like Figure 3 As shown, 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 .

[0090] 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 be opposite to 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. One of the first friction member 41 and the second friction member 42 can be set as a friction plate, and the other can be set as a partition plate.

[0091] 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 to the first fixed gear 22 so as to rotate integrally. In the present embodiment, the first support member 43 is formed in a cylindrical shape extending along the axial direction L. Furthermore, the first support member 43 supports the outer peripheral portion of the first friction member 41.

[0092] 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. Moreover, the second support member 44 supports the inner peripheral portion of the second friction member 42. In addition, in the present embodiment, the second support member 44 is fixed to a first support wall portion 91 provided in the housing 9 serving as the non-rotating member NR. The first support wall portion 91 is formed to extend along the first radial direction RA. Moreover, the first support wall portion 91 is configured to cover the first friction member 41 and the second friction member 42 from the first axial side L1. Figure 3 In the illustrated example, the second support member 44 is formed integrally with the first support wall portion 91 so as to protrude from the first support wall portion 91 toward the second axial side L2 .

[0093] The first pressing device 45 is a device for pressing 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 comprises: 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 threaded 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 the driving force to the first pressing member 46.

[0094] The first pressing member 46 is arranged at a position overlapping with the first friction member 41 and the second friction member 42 when viewed 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 two elements, "overlapping when viewed in a specific direction" means that when an imaginary straight line parallel to the line of sight is moved in directions orthogonal to the imaginary straight line, an area where the imaginary straight line intersects with both elements exists in at least a part.

[0095] The first drive motor 47 is a motor that generates a rotational drive force for driving the first pressing member 46. In the present embodiment, the first drive motor 47 is arranged outside the first radial direction RA relative to the first support member 43, and is arranged at a position overlapping with the first support member 43 when viewed in the first radial direction along the first radial direction RA. In addition, in the present embodiment, the first drive motor 47 is arranged at a position overlapping with the planetary gear mechanism 1 when viewed in the axial direction along the axial direction L.

[0096] In the present embodiment, the first linear motion conversion mechanism 48 includes a first threaded shaft member 481 , a first nut member 482 , a first connecting member 483 , a first supported member 484 , and a first speed reduction mechanism 49 .

[0097] The first threaded shaft component 481 is formed to extend along the axial direction L. The first nut component 482 is formed in a ring shape that covers the first threaded shaft component 481 from the outside of the first radial direction RA. The first threaded shaft component 481 and the first nut component 482 are configured to be screwed together. Specifically, an external thread is formed on the outer peripheral portion of the first threaded shaft component 481, and an internal thread that is screwed with the external thread of the first threaded shaft component 481 is formed on the inner peripheral portion of the first nut component 482. Therefore, the first nut component 482 is rotated by the first threaded shaft component 481, thereby performing a linear motion along the axial direction L according to the rotation direction and the orientation of the external thread and the internal thread.

[0098] The first nut member 482 is supported so as to be non-rotatable relative to the non-rotating member NR and to be movable in the axial direction L. In the present embodiment, the first nut member 482 is arranged on the inner side of the first radial direction RA relative to the second support member 44 fixed to the non-rotating member NR. Moreover, the first nut member 482 is connected to the second support member 44 so as to be non-rotatable relative to the non-rotating member NR and to be movable relative to the axial direction L via the first annular anti-rotation member 48a arranged between the first nut member 482 and the first radial direction RA of the second support member 44. Figure 3In the example shown, a plurality of spline teeth extending in the axial direction L are formed in a circumferentially dispersed manner on the outer peripheral portion of the first nut member 482. Furthermore, 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 in a circumferentially dispersed manner on the inner peripheral portion of the first rotation-stopping member 48a in a manner extending in the axial direction L. In addition, a plurality of spline teeth extending in the axial direction L are formed in a circumferentially dispersed manner on the inner peripheral portion of the second support member 44. Furthermore, 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 in a circumferentially dispersed manner on the outer peripheral portion of the first rotation-stopping member 48a in a manner extending in the axial direction L.

[0099] In addition, the first nut member 482 is connected to the first pressing member 46 so as to move in the axial direction L as a whole. Figure 3 In the illustrated example, the first nut member 482 is formed integrally with the first pressing member 46 . Therefore, the first pressing member 46 moves in the axial direction L via the first nut member 482 as the first threaded shaft member 481 rotates.

[0100] The first connection member 483 connects the first threaded shaft member 481 and the first speed reduction mechanism 49. In the present embodiment, the first connection member 483 is formed in a cylindrical shape extending from the first threaded shaft member 481 to the first axial side L1.

[0101] The first supported member 484 is supported by the non-rotating member NR in the axial direction L. In the present embodiment, the first supported member 484 is formed to protrude outward in the first radial direction RA from the first connecting member 483. Furthermore, the first supported member 484 is supported from the axial second side L2 via the first thrust bearing B1 by a support portion 44a formed to protrude inward in the first radial direction RA from the second support member 44 fixed to the non-rotating member NR.

[0102] The first speed reduction mechanism 49 is configured to reduce the speed of 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.

[0103] The first gear 491 is connected to the output shaft of the first drive motor 47 so as to rotate integrally. In the present embodiment, the first gear 491 is arranged on the first side L1 in the axial direction with respect to the first drive motor 47.

[0104] 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.

[0105] The third gear 493 is connected to the second gear 492 so as to rotate integrally. 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 arranged on the second side L2 in the axial direction with respect to the second gear 492.

[0106] 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 arranged on the second axis X2.

[0107] The second gear 492 has a larger number of teeth than the first gear 491. Also, the fourth gear 494 has a larger number of teeth than 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 is transmitted to the third gear 493. Also, the rotation of the third gear 493 is decelerated between the third gear 493 and the fourth gear 494.

[0108] In the present embodiment, the first connecting member 483 connects the first threaded shaft member 481 and the fourth gear 494. Specifically, the gear connecting portion 495 extending from the fourth gear 494 to the second axial side L2 is connected to the first connecting member 483 so as to rotate integrally with the first connecting member 483 while being arranged on the inner side of the first radial direction RA relative to the first connecting member 483. Figure 3 In the example shown, a plurality of spline teeth extending in the axial direction L are formed in a circumferentially dispersed manner on the inner peripheral portion of the first connecting member 483. In addition, a plurality of spline teeth engaging with the plurality of spline teeth formed in the inner peripheral portion of the first connecting member 483 are formed in a circumferentially dispersed manner on the outer peripheral portion of the gear connecting portion 495 in a manner extending in the axial direction L.

[0109] In the present embodiment, the first linear motion conversion mechanism 48 is arranged inside the first friction member 41 and the second friction member 42 in the first radial direction RA, and is arranged at a position overlapping the first friction member 41 and the second friction member 42 when viewed in the first radial direction along the first radial direction RA. Figure 3 In the example shown, the first threaded shaft component 481, the first nut component 482, the first connecting component 483, and the first supported component 484 of the first linear motion conversion mechanism 48 are arranged on the inner side of the first radial direction RA relative to the first friction component 41 and the second friction component 42, and are arranged at a position overlapping with the first friction component 41 and the second friction component 42 when viewed along the first radial direction of the first radial direction RA.

[0110] In the first friction engagement device 4, when the first pressing member 46 moves to the first axial side L1 and presses the first friction member 41 and the second friction member 42, the first support wall portion 91 of the housing 9, which is the non-rotating member NR, restricts the movement of the first friction member 41 and the second friction member 42 to the first axial side L1. As a result, the first friction member 41 and the second friction member 42 are connected to each other so as not to rotate relative 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 an engaged state, the first support member 43 supporting 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 the first fixed gear 21 meshing with the first fixed gear 22 so as to rotate integrally is fixed to the non-rotating member NR.

[0111] On the other hand, if the first pressing member 46 moves toward the second axial side L2 and releases the pressing of the first pressing member 46 on the first friction member 41 and the second friction member 42, the first friction member 41 and the second friction member 42 become relatively rotatable with respect to each other, and the first friction engagement device 4 becomes released. When the first friction engagement device 4 becomes released, the first support member 43 supporting the first friction member 41 becomes relatively rotatable with respect 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 becomes relatively rotatable with respect to the non-rotating member NR. Therefore, the first fixed element 13 connected to the first fixed gear 21 meshing with the first fixed gear 22 is not fixed with respect to the non-rotating member NR.

[0112] like Figure 4 As shown, 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 .

[0113] 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 to be opposite to each other in the axial direction L. In the present embodiment, the third friction member 51 and the fourth friction member 52 are provided in plurality, and they are alternately arranged along the axial direction L. One of the third friction member 51 and the fourth friction member 52 can be set as a friction plate, and the other can be set as a partition plate.

[0114] The third support member 53 is a member that supports the third friction member 51 while restricting relative rotation of the third friction member 51. The third support member 53 is connected to the second fixed gear 32 so as to rotate integrally. In the present embodiment, the third support member 53 is formed in a cylindrical shape extending along the axial direction L. Furthermore, the third support member 53 supports the outer peripheral portion of the third friction member 51.

[0115] 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. Moreover, the fourth support member 54 supports the inner peripheral portion of the fourth friction member 52. In addition, in the present embodiment, the fourth support member 54 is fixed to the second support wall portion 92 provided in the housing 9 serving as the non-rotating member NR. The second support wall portion 92 is formed to extend along the second radial direction RB. Moreover, the second support wall portion 92 is configured to cover the third friction member 51 and the fourth friction member 52 from the first axial side L1. Figure 4 In the illustrated example, the fourth support member 54 is formed integrally with the second support wall portion 92 so as to protrude from the second support wall portion 92 toward the axial second side L2 .

[0116] The second pressing device 55 is a device for pressing 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 comprises: a second pressing member 56 for applying a pressing force to the third friction member 51 and the fourth friction member 52; a second drive motor 57; and a threaded second linear motion conversion mechanism 58 for converting the rotational driving force of the second drive motor 57 into a driving force in the axial direction L and transmitting it to the second pressing member 56.

[0117] The second pressing member 56 is disposed at a position overlapping the third friction member 51 and the fourth friction member 52 when viewed in the axial direction L. In the present embodiment, the second pressing member 56 is formed in a plate shape extending in the second radial direction RB.

[0118] The second drive motor 57 is a motor that generates a rotational drive force for driving the second pressing member 56. In the present embodiment, the second drive motor 57 is arranged outside the second radial direction RB relative to the third support member 53, and is arranged at a position overlapping with the third support member 53 when viewed along the second radial direction of the second radial direction RB. In addition, in the present embodiment, the second drive motor 57 is arranged at a position overlapping with the planetary gear mechanism 1 when viewed along the axial direction of the axial direction L.

[0119] In the present embodiment, the second linear motion conversion mechanism 58 includes a second threaded shaft member 581 , a second nut member 582 , a second connecting member 583 , a second supported member 584 , and a second speed reduction mechanism 59 .

[0120] The second threaded shaft component 581 is formed to extend along the axial direction L. The second nut component 582 is formed in a ring shape that covers the second threaded shaft component 581 from the outside of the second radial direction RB. The second threaded shaft component 581 and the second nut component 582 are configured to be screwed together. Specifically, an external thread is formed on the outer peripheral portion of the second threaded shaft component 581, and an internal thread that is screwed with the external thread of the second threaded shaft component 581 is formed on the inner peripheral portion of the second nut component 582. Therefore, by rotating the second threaded shaft component 581, the second nut component 582 performs a linear motion along the axial direction L according to the rotation direction and the orientation of the external thread and the internal thread.

[0121] The second nut member 582 is supported so as to be non-rotatable relative to the non-rotating member NR and to be movable in the axial direction L. In the present embodiment, the second nut member 582 is arranged on the inner side of the second radial direction RB relative to the fourth support member 54 fixed to the non-rotating member NR. Moreover, the second nut member 582 is connected to the fourth support member 54 so as to be non-rotatable relative to the fourth support member 54 and to be movable in the axial direction L via the annular second anti-rotation member 58a arranged between the second nut member 582 and the second radial direction RB of the fourth support member 54. Figure 4 In the example shown, a plurality of spline teeth extending in the axial direction L are formed in a circumferentially dispersed manner on the outer peripheral portion of the second nut member 582. Furthermore, 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 in a circumferentially dispersed manner on the inner peripheral portion of the second rotation-stopping member 58a in a manner extending in the axial direction L. In addition, a plurality of spline teeth extending in the axial direction L are formed in a circumferentially dispersed manner on the inner peripheral portion of the fourth support member 54. Furthermore, 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 in a circumferentially dispersed manner on the outer peripheral portion of the second rotation-stopping member 58a in a manner extending in the axial direction L.

[0122] In addition, the second nut member 582 is connected to the second pressing member 56 so as to move in the axial direction L as a whole. Figure 4 In the illustrated example, the second nut member 582 is formed integrally with the second pressing member 56 . Therefore, the second pressing member 56 moves in the axial direction L via the second nut member 582 as the second threaded shaft member 581 rotates.

[0123] The second connection member 583 connects the second threaded shaft member 581 and the second speed reduction mechanism 59. In the present embodiment, the second connection member 583 is formed in a cylindrical shape extending from the second threaded shaft member 581 toward the first axial side L1.

[0124] The second supported member 584 is supported relative to the non-rotating member NR in the axial direction L. In the present embodiment, the second supported member 584 is formed to protrude outward in the second radial direction RB from the second connecting member 583. Furthermore, the second supported member 584 is supported from the axial second side L2 via the second thrust bearing B2 by a support portion 54a formed to protrude inward in the second radial direction RB from the fourth support member 54 fixed to the non-rotating member NR.

[0125] The second speed reduction mechanism 59 is configured to reduce the speed of 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.

[0126] The fifth gear 591 is connected to the output shaft of the second drive motor 57 so as to rotate integrally. In the present embodiment, the fifth gear 591 is arranged on the first side L1 with respect to the second drive motor 57 in the axial direction.

[0127] 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.

[0128] The seventh gear 593 is connected to the sixth gear 592 so as to rotate integrally. 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 arranged on the second axial side L2 with respect to the sixth gear 592.

[0129] 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 arranged on the third axis X3.

[0130] The sixth gear 592 has a larger number of teeth than the fifth gear 591. Also, the eighth gear 594 has a larger number of teeth than 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 is transmitted to the seventh gear 593. Also, the rotation of the seventh gear 593 is decelerated between the seventh gear 593 and the eighth gear 594.

[0131] In the present embodiment, the second connecting member 583 connects the second threaded shaft member 581 and the eighth gear 594. Specifically, the gear connecting portion 595 extending from the eighth gear 594 to the second axial side L2 is connected to the second connecting member 583 so as to rotate integrally with the second connecting member 583 while being arranged on the inner side in the second radial direction RB relative to the second connecting member 583. Figure 4 In the example shown, a plurality of spline teeth extending in the axial direction L are formed in a circumferentially dispersed manner on the inner peripheral portion of the second connecting member 583. In addition, a plurality of spline teeth engaging with the plurality of spline teeth formed in the inner peripheral portion of the second connecting member 583 are formed in a circumferentially dispersed manner on the outer peripheral portion of the gear connecting portion 595 in a manner extending in the axial direction L.

[0132] In the present embodiment, the second linear motion conversion mechanism 58 is arranged on the inner side of the third friction member 51 and the fourth friction member 52 in the second radial direction RB, and is arranged at a position overlapping with the third friction member 51 and the fourth friction member 52 when viewed in the second radial direction along the second radial direction RB. Figure 4 In the example shown, the second threaded shaft component 581, the second nut component 582, the second connecting component 583, and the second supported component 584 of the second linear motion conversion mechanism 58 are arranged on the inner side of the second radial direction RB relative to the third friction component 51 and the fourth friction component 52, and are arranged at a position overlapping with the third friction component 51 and the fourth friction component 52 when viewed in the second radial direction along the second radial direction RB.

[0133] 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 to the first axial side L1 is restricted by the second supporting wall portion 92 of the housing 9 as the non-rotating member NR. As a result, the third friction member 51 and the fourth friction member 52 are connected to each other so as not to rotate relative to each other, and the second friction engagement device 5 is in an engaged state. Therefore, when the second friction engagement device 5 is in an engaged state, the third supporting member 53 supporting the third friction member 51 is in a fixed state relative to the fourth supporting member 54 fixed to the non-rotating member NR. At this time, the second fixed gear 32 connected to the third supporting member 53 is in a fixed state relative to the non-rotating member NR. Therefore, the second fixed element 14 connected to the second fixed gear 31 meshing with the second fixed gear 32 so as to rotate integrally is in a fixed state relative to the non-rotating member NR.

[0134] On the other hand, if the second pressing member 56 moves to the second axial side L2 and releases the pressing of the third friction member 51 and the fourth friction member 52 by the second pressing member 56, the third friction member 51 and the fourth friction member 52 become relatively rotatable with respect to each other, and the second friction engagement device 5 becomes released. When the second friction engagement device 5 becomes released, the third support member 53 supporting the third friction member 51 becomes relatively rotatable with respect 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 becomes relatively rotatable with respect to the non-rotating member NR. Therefore, the second fixed element 14 connected to the second fixed gear 31 meshing with the second fixed gear 32 and rotating integrally becomes unfixed with respect to the non-rotating member NR.

[0135] like Figure 1 as well as Figure 2 As shown, in this embodiment, when the first friction engagement device 4 is in the engaged state, the first ring gear R11 with a relatively small diameter meshing with the small diameter pinion P12 is fixed relative to the non-rotating member NR. In addition, when the second friction engagement device 5 is in the engaged state, the second ring gear R12 with a relatively large diameter meshing with the large diameter pinion P11 is fixed relative to the non-rotating member NR.

[0136] Therefore, in the present embodiment, when the first friction engagement device 4 is set to the engaged state and the second friction engagement device 5 is set to the released state, a gear shift with a relatively large speed ratio (low gear) is formed. In addition, when the first friction engagement device 4 is set to the released state and the second friction engagement device 5 is set to the engaged state, a gear shift with a relatively small speed ratio (high gear) is formed.

[0137] In addition, when both the first friction engagement device 4 and the second friction engagement device 5 are in the engaged state, the planetary carrier C1 as the output element 12 is fixed relative to the non-rotating member NR. As a result, the wheels W drivingly connected to the output element 12 are locked. In this way, the first friction engagement device 4 and the second friction engagement device 5 function as parking brakes.

[0138] In addition, when both the first friction engagement device 4 and the second friction engagement device 5 are set to 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 relative to the non-rotating member NR. As a result, the driving force of the driving source D cannot be transmitted to the wheels W (neutral state).

[0139] As described above, the transmission 10 includes: a planetary gear mechanism 1, including an input element 11 drivingly connected to a driving 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 fixed device 2, which selectively fixes the first fixed element 13 to a non-rotating member NR; and a second fixed device 3, which selectively fixes the second fixed element 14 to the non-rotating member NR, the first fixed device 2 including: a first fixed gear 21 connected to rotate integrally with the first fixed element 13; a first fixed gear 22 meshing with the first fixed gear 21; and a first friction engagement device 4, which causes the first fixed gear 22 to rotate integrally with the non-rotating member NR. The component NR is selectively engaged, and the second fixing device 3 includes: a second fixed gear 31, which is connected to rotate integrally with the second fixed element 14; a second fixed gear 32, which meshes with the second fixed gear 31; and a second friction engagement device 5, which selectively engages the second fixed gear 32 with the non-rotating component NR, the first friction engagement device 4 and the first fixed gear 22 are arranged on the same axis, the second friction engagement device 5 and the second fixed gear 32 are arranged on the same axis, 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, and the first friction engagement device 4 and the second friction engagement device 5 are arranged so as not to overlap each other when viewed along the axial direction L.

[0140] According to this structure, the first fixed 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 that selectively engages the first fixed gear 22 with the non-rotating member NR. Moreover, the first friction engagement device 4 and the first fixed gear 22 are arranged on the same axis. In addition, the second fixed 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 that selectively engages the second fixed gear 32 with the non-rotating member NR. Moreover, the second friction engagement device 5 and the second fixed gear 32 are arranged on the same axis. As a result, it is easy to arrange the first friction engagement device 4 and the second friction engagement device 5 on different axes. Therefore, compared with a structure in which they are arranged on the same axis, it is easy to suppress the size of the axial direction L of the transmission 10 to be small.

[0141] In addition, according to this structure, the diameter of the first fixed gear 22 relative to the first fixed gear 21 is set small in the first fixing device 2, thereby being able to suppress the torque required to fix the first fixed element 13 of the planetary gear mechanism 1 to the non-rotating member NR. As a result, it is easy to reduce the diameter of the first friction engagement device 4. In addition, similarly, with respect to the second fixing device 3, it is easy to reduce the diameter of the second friction engagement device 5.

[0142] As described above, according to this configuration, in a configuration including a pair of friction engagement devices 4 and 5 , it is easy to achieve miniaturization of the transmission 10 .

[0143] As described above, in the present embodiment, the first friction engagement device 4 includes: a first friction member 41, which is arranged on the same axis as the first fixed gear 22; a second friction member 42, which is arranged on the same axis as the first fixed gear 22 and is arranged to be opposite to the first friction member 41 in the axial direction L; a first support member 43, which is connected to rotate integrally with the first fixed gear 22 and supports the first friction member 41 while restricting the relative rotation of the first friction member 41; a second support member 44, which is fixed to the non-rotating member NR and supports the second friction member 42 while restricting the relative rotation of the second friction member 42; and a first pressing device 45, which presses the first friction member 41 and the second friction member 42 in the axial direction L,

[0144] The second friction engagement device 5 includes: a third friction member 51, which is arranged on the same axis as the second fixed gear 32; a fourth friction member 52, which is arranged on the same axis as the second fixed gear 32 and is arranged to be opposite to the third friction member 51 in the axial direction L; a third support member 53, which is connected to the second fixed gear 32 to rotate integrally, and supports the third friction member 51 in a state where the relative rotation of the third friction member 51 is restricted; a fourth support member 54, which is fixed to the non-rotating member NR, and supports the fourth friction member 52 in a state where the relative rotation of the fourth friction member 52 is restricted; and a second pressing device 55, which presses the third friction member 51 and the fourth friction member 52 in the axial direction L,

[0145] 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 first threaded 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 the driving force to the first pressing member 46.

[0146] The first linear motion conversion mechanism 48 is arranged on the inner side of the first friction member 41 and the second friction member 42 in the first radial direction RA, and is arranged at a position overlapping with the first friction member 41 and the second friction member 42 when viewed in the first radial direction along the first radial direction RA.

[0147] The second pressing device 55 comprises: a second pressing member 56 for applying a pressing force to the third friction member 51 and the fourth friction member 52; a second drive motor 57; and a threaded second linear motion conversion mechanism 58 for converting the rotational driving force of the second drive motor 57 into a second axial driving force and transmitting the second pressing member 56.

[0148] The second linear motion conversion mechanism 58 is arranged inside the third friction member 51 and the fourth friction member 52 in the second radial direction RB, and is arranged at a position overlapping the third friction member 51 and the fourth friction member 52 when viewed in the second radial direction along the second radial direction RB.

[0149] According to this structure, the first friction engagement device 4 is configured to be coaxially arranged with the first fixed gear 22, and includes the first friction member 41, the second friction member 42, and the first support member 43. Therefore, compared with a structure in which the first friction member 41, the second friction member 42, and the first support member 43 are coaxially arranged with the first fixed element 13 of the planetary gear mechanism 1, it is easy to suppress the radial R dimension of the first friction engagement device 4 to be small. In addition, similarly, with respect to the second fixed device 3, compared with a structure in which the third friction member 51, the fourth friction member 52, and the third support member 53 are coaxially arranged with the second fixed element 14 of the planetary gear mechanism 1, it is easy to suppress the radial R dimension of the second friction engagement device 5 to be small.

[0150] In addition, according to this structure, the first linear motion conversion mechanism 48 of the first pressing device 45 is arranged using the space on the inner side of the first radial direction RA relative 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 on the inner side of the second radial direction RB relative to the third friction member 51 and the fourth friction member 52. Therefore, it is easy to achieve miniaturization 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 miniaturization of the transmission 10.

[0151] In addition, according to this structure, the first pressing member 46 is moved in the axial direction L by the first threaded linear motion conversion mechanism 48, and the second pressing member 56 is moved in the axial direction L by the second threaded linear motion conversion mechanism 58. Thus, the positions of the first pressing member 46 and the second pressing member 56 can be maintained even in the absence of the driving force of the first drive motor 47 and the second drive motor 57. Therefore, even in the state where no power is supplied to the transmission 10, both the first friction engagement device 4 and the second friction engagement device 5 can be set to the engagement state, and the output element 12 of the planetary gear mechanism 1 can be locked so as not to rotate. Therefore, it is not necessary to provide a parking brake separately.

[0152] In addition, as described above, in the present embodiment, the first fixed element 13 comprises: a first annular portion A11, which is formed in an annular shape; and a first gear ring R11 with internal teeth, which is arranged on the inner circumferential surface of the first annular portion A11, and the second fixed element 14 comprises: a second annular portion A12, which is formed in an annular shape; and a second gear ring R12 with internal teeth, which is arranged on the inner circumferential surface of the second annular portion A12, the first fixed gear 21 is a gear with external teeth arranged on the outer circumferential surface of the first annular portion A11, and the second fixed gear 31 is a gear with external teeth arranged on the outer circumferential surface of the second annular portion A12.

[0153] According to this structure, it is easy to arrange the first fixed gear 21 and the second fixed gear 31 in the outer region of the radial direction R relative to the planetary gear mechanism 1. Therefore, in the structure 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 achieve miniaturization of the transmission 10.

[0154] 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 a "first transmission 10A" and the other is referred to as a "second transmission 10B."

[0155] like Figure 1 as well as Figure 2 As shown, in the present embodiment, the vehicle drive transmission device 100 includes a rotor shaft 6, a differential gear mechanism 7, a first output member 81, and a second output member 82 in addition to the first transmission 10A and the second transmission 10B.

[0156] The rotor shaft 6 is a shaft member that rotates integrally with the rotor RT of the rotary electric machine MG. In the present embodiment, the rotor shaft 6 is arranged on the first axis X1. In addition, the rotor shaft 6 is formed in a cylindrical shape extending along the axial direction L. Furthermore, the rotor shaft 6 is arranged to support the rotor RT from the inner side of the radial direction R.

[0157] 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. In addition, in the present embodiment, the differential gear mechanism 7 is arranged on the first axis X1.

[0158] 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 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.

[0159] In addition, in the present embodiment, the differential gear mechanism 7 is a planetary gear type differential gear mechanism having a differential sun gear S2, a differential planetary 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 planetary carrier C2 supports the inner pinion P21 meshing with the differential sun gear S2 and the outer pinion P22 meshing with the inner pinion P21 and the differential ring gear R2 so as to be rotatable.

[0160] In the present embodiment, the differential ring gear R2 is connected to rotate integrally with the rotor shaft 6. That is, in the present embodiment, the differential ring gear R2 functions as the differential input element 71. Figure 1 In the illustrated example, the end portion of the rotor shaft 6 on the first axial side L1 extends outward in the radial direction R along the end surface of the rotor RT on the first axial side L1 and is connected to the differential ring gear R2 .

[0161] In the present embodiment, the differential carrier C2 functions as the first differential output element 72 , and the differential sun gear S2 functions as the second differential output element 73 .

[0162] The first output member 81 is connected to the first wheel W1 (see Figure 2 The second output member 82 is connected to the second wheel W2 (see FIG. 1 ) which is different from the first wheel W1 and is the wheel W described above. Figure 2 In this embodiment, the first output member 81 is connected to the first drive shaft DS1 (see Figure 2 ) is connected to rotate integrally with the first wheel W1. In addition, the second output member 82 is connected to the first wheel W1 via the second drive shaft DS2 (see Figure 2 ) is connected to rotate integrally with the second wheel W2. In the present embodiment, the first output member 81 and the second output member 82 are arranged on the first axis X1. In addition, 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).

[0163] In the present embodiment, the planetary gear mechanism 1 of the first transmission 10A, the differential gear mechanism 7, the rotary electric machine MG, and the planetary gear mechanism 1 of the second transmission 10B are arranged in the order described on the first axis X1 from the axial first side L1 toward the axial second side L2. That is, in the present embodiment, the planetary gear mechanism 1 of the first transmission 10A and the planetary gear mechanism 1 of the second transmission 10B are arranged separately on both sides of the axial direction L with respect to the rotary electric machine MG and the differential gear mechanism 7.

[0164] The input element 11 of the first transmission 10A is connected 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 to rotate integrally with the differential planetary carrier C2 as the first differential output element 72 via the first connecting shaft J1. The first connecting shaft J1 is a shaft member extending along the axial direction L in a manner that connects the sun gear S1 of the first transmission 10A and the differential planetary carrier C2.

[0165] The output element 12 of the first transmission 10A is connected 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.

[0166] The input element 11 of the second transmission 10B is connected 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 to rotate integrally with the differential sun gear S2 as the second differential output element 73 via the second connecting shaft J2. The second connecting shaft J2 is a shaft member extending along the axial direction L in a manner that connects 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 configured to penetrate the inner side of the radial direction R in the axial direction L relative to the rotor shaft 6.

[0167] The output element 12 of the second transmission 10B is connected 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.

[0168] The first fixed gear 21 of the first transmission 10A and the first fixed gear 21 of the second transmission 10B are arranged 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 arranged on the same axis.

[0169] 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 arranged on the same axis.

[0170] 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 arranged on the same axis. In addition, the first fixed gear 22 of the first transmission 10A and the first fixed gear 22 of the second transmission 10B are connected 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 to rotate integrally with each other via the first fixed gear connecting member 221. The first fixed gear connecting member 221 is a shaft member formed to extend along the axial direction L.

[0171] 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 arranged on the same axis. In addition, the second fixed gear 32 of the first transmission 10A and the second fixed gear 32 of the second transmission 10B are connected 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 to rotate integrally with each other via the second fixed gear connecting member 321. The second fixed gear connecting member 321 is a shaft member formed to extend along the axial direction L.

[0172] 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 the 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 in a state of being fixed relative 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 relative to the non-rotating member NR. Thus, in the present embodiment, the first transmission 10A and the second transmission 10B share one first friction engagement device 4. That is, in the present 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 shared.

[0173] 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 the 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 in a state of being fixed relative 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 relative to the non-rotating member NR. Thus, in the present embodiment, the first transmission 10A and the second transmission 10B share one second friction engagement device 5. That is, in the present 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 shared.

[0174] As described above, in the present embodiment, the driving source D is a rotary electric machine MG having a rotor RT, and 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 different from the first wheel W1 and is the same as the wheel W; a differential gear mechanism 7 that includes a differential input element 71 that is connected to rotate integrally with the rotor shaft 6, a first differential output element 72, and a second differential output element 73 that is drivingly connected to the second wheel W2 that is different from the first wheel W1. The first differential output element 73 distributes the torque transmitted from the rotor shaft 6 to the first differential output element 72 and the second differential output element 73; the transmission 10 is the first transmission 10A; and the second transmission 10B is different from the transmission 10 and the first transmission 10A, and the input element 11 of the first transmission 10A is connected to rotate integrally with the first differential output element 72, and the output element 12 of the first transmission 10A is connected to rotate integrally with the first output member 81. The input element 11 of the second transmission 10B is connected to rotate integrally with the second differential output element 73, the output element 12 of the second transmission 10B is connected 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 on the same axis, 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 same axis and connected to rotate integrally with each other, and the first transmission 10A is connected to rotate integrally with the second differential output element 73, and the output element 12 of the second transmission 10B is connected to rotate integrally with the second output member 82. 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 same axis, 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 same axis and are connected 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 shared, and the second friction engagement device 5 of the first transmission 10A and the second friction engagement device 5 of the second transmission 10B are shared.

[0175] According to this structure, in the structure in which the transmission 10 is provided in the power transmission path 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 on the same axis and connected to rotate integrally with each other. In addition, the second fixed gears 32 constituting the second fixing device 3 of the pair of transmissions 10 are arranged on the same axis and connected to rotate integrally with each other. Thus, the pair of first fixed gears 22 can be selectively engaged with the non-rotating member NR by the 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 the one second friction engagement device 5.

[0176] Therefore, in the configuration including the 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 to reduce the size of the vehicle drive transmission device 100 .

[0177] In the present embodiment, the first friction engagement device 4 and the second friction engagement device 5 are configured so that their configuration areas in the axial direction L overlap each other. Moreover, the first friction engagement device 4 and the second friction engagement device 5 are configured so as not to overlap when viewed in the axial direction along the axial direction L. In addition, the first friction engagement device 4 and the second friction engagement device 5 may be configured separately 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 configured separately on both sides of the axial direction L with respect to the rotating electrical machine MG and the planetary gear mechanism 1 of the pair of transmissions 10. In addition, the first friction engagement device 4 and the second friction engagement device 5 may be configured so as to overlap when viewed in the axial direction along the axial direction L.

[0178] 2. Second Implementation

[0179] Below, refer to Figures 5 to 8 A vehicle drive transmission device 100 of the second embodiment is described. In this embodiment, the vehicle drive transmission device 100 has a single transmission 10, and the position of the transmission 10 on the power transmission path connecting the drive source D and the first output member 81 and the second output member 82 is different from that of the first embodiment. The following description will focus on the differences from the first embodiment. In addition, the points not particularly described are the same as those of the first embodiment.

[0180] like Figures 5 to 7 As shown, in the present embodiment, the input element 11 of the transmission 10 is a first sun gear S11 and a second sun gear S12 that rotate integrally with each other. The first sun gear S11 meshes with a small-diameter pinion P12. The second sun gear S12 meshes with a large-diameter pinion 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 P11 and the small-diameter pinion P12 are supported to rotate freely relative to each other. In addition, in the present embodiment, the second ring gear R12 meshed with the large-diameter pinion P11 and the first ring gear R11 meshed with the small-diameter pinion P12 are formed to have the same diameter as each other. In addition, 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.

[0181] In addition, in the present embodiment, the input element 11 of the transmission 10 is connected 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 connected to rotate integrally with the rotor shaft 6. In the example shown in the figure, the second sun gear S12 is arranged on the second axial side L2 relative to the first sun gear S11.

[0182] In addition, in the present embodiment, the output element 12 of the transmission 10 is connected to rotate integrally with the externally toothed drive gear 16. The drive gear 16 is arranged on the first axis X1. In the present embodiment, the drive gear 16 is arranged on the axial second side L2 relative to the planetary gear mechanism 1 of the transmission 10. Moreover, the drive gear 16 is arranged on the outer side of the radial direction R relative to the input shaft 15.

[0183] In the present embodiment, the differential gear mechanism 7 is not arranged on the first axis X1 , but is arranged on a fourth axis X4 that is different from the first axis X1 , the second axis X2 , and the third axis X3 .

[0184] In the present embodiment, the differential input element 71 of the differential gear mechanism 7 is connected to rotate integrally with the driven gear 74 of the external teeth meshing with the drive gear 16. The driven gear 74 is arranged on the fourth axis X4. In the present embodiment, the driven gear 74 is arranged outside the differential ring gear R2 as the differential input element 71 in the radial direction R, and is arranged at a position overlapping with the differential ring gear R2 when viewed in the radial direction of the radial direction R.

[0185] In the present embodiment, the first differential output element 72 of the differential gear mechanism 7 is connected to rotate integrally with the first output member 81. Furthermore, the second differential output element 73 of the differential gear mechanism 7 is connected to rotate integrally with the second output member 82. Figure 5 In the example shown, the first output member 81 is formed to extend from the differential carrier C2 as the first differential output element 72 to the axial second side L2. The second output member 82 is formed to extend from the differential sun gear S2 as the second differential output element 73 to the axial first side L1.

[0186] As described above, 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 .

[0187] like Figures 5 to 7 As shown in FIG. 1 , in this embodiment, the first axis X1, the second axis X2, the third axis X3, and the fourth axis X4 are arranged parallel to each other. Figure 8As shown, in the present embodiment, the second axis X2, the third axis X3, and the fourth axis X4 are arranged to surround the first axis X1. Specifically, when viewed 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.

[0188] As described above, in the present embodiment, the driving source D is a rotary electric machine MG having a rotor RT, and 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 different from the first wheel W1 and is the same as the wheel W; the above-mentioned transmission 10; and 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, distributes 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, connects the input element 11 of the transmission 10 to rotate integrally with the rotor shaft 6, and connects the output element 12 of the transmission 10 to the external drive gear 11. 6, the differential input element 71 is connected to rotate integrally with the driven gear 74 of the external teeth meshing with the drive gear 16, the first differential output element 72 is connected to rotate integrally with the first output member 81, and the second differential output element 73 is connected to rotate integrally with the second output member 82. The axis of the planetary gear mechanism 1 on which the rotor shaft 6 and the transmission 10 are arranged is set as the first axis X1, the axis on which the first fixed gear 22 of the transmission 10 is arranged is set as the second axis X2, the axis on which the second fixed gear 32 of the transmission 10 is arranged is set as the third axis X3, and the axis on which the differential gear mechanism 7 is arranged is set as the fourth axis X4. The first axis X1, the second axis X2, the third axis X3, and the fourth axis X4 are arranged in parallel with each other, and the second axis X2, the third axis X3, and the fourth axis X4 are arranged to surround the first axis X1.

[0189] According to this structure, in a structure in which the planetary gear mechanism 1 of the transmission 10 is arranged on the same axis as 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 dimension of the radial direction R of the vehicle drive transmission device 100 with respect to the first axis X1 to be small.

[0190] 3. Third Implementation

[0191] Below, refer to Fig. 9A vehicle drive transmission device 100 according to a third embodiment is described. In this embodiment, the structure of the transmission 10 is different from that of the second embodiment. The following description will focus on the differences from the second embodiment. In addition, the points not specifically described are the same as those of the second embodiment.

[0192] like Fig. 9 As shown, in this embodiment, the input element 11 of the transmission 10 is the sun gear S1. The output element 12 of the transmission 10 is the second ring gear R12. The first fixed element 13 is the first ring gear R11. The second fixed element 14 is the carrier C1.

[0193] In the present embodiment, the planetary carrier C1 supports the large-diameter pinion P11 and the small-diameter pinion P12 which rotate integrally with each other so as to be rotatable. The large-diameter pinion P11 meshes with both the sun gear S1 and the second ring gear R12. In the present embodiment, the large-diameter pinion P11 is formed to have a smaller diameter than the sun gear S1. The small-diameter pinion P12 meshes with the first ring gear R11.

[0194] In the present embodiment, the second fixed gear 31 is connected to rotate integrally with the carrier C1 as the second fixed element 14. The second fixed gear 31 is arranged on the second axial side L2 with respect to the planetary gear mechanism 1.

[0195] In the present embodiment, the drive gear 16 is connected to rotate integrally with the second ring gear R12 as the output element 12. The drive gear 16 is disposed on the first axial side L1 with respect to the planetary gear mechanism 1.

[0196] 4. Other Implementation Methods

[0197] (1) In the above-mentioned embodiment, the first pressing device 45 and the second pressing device 55 are respectively configured to convert the rotational driving force of the driving motor into the driving force in the axial direction L through a threaded linear motion conversion mechanism, and transmit the same to the pressing component. However, the present invention is not limited to such a structure. For example, the first pressing device 45 and the second pressing device 55 may be respectively configured to drive the pressing component through an electromagnetic actuator such as a solenoid. Alternatively, the first pressing device 45 and the second pressing device 55 may also be respectively configured to drive the pressing component through oil pressure.

[0198] (2) In the above-mentioned embodiment, 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. However, the present invention is not limited to such a structure, and the first support member 43 may support the inner peripheral portion of the first friction member 41, and the second support member 44 may support the outer peripheral portion of the second friction member 42. In addition, in the above-mentioned embodiment, 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. However, the present invention is not limited to such a structure, and the third support member 53 may support the inner peripheral portion of the third friction member 51, and the fourth support member 54 may support the outer peripheral portion of the fourth friction member 52.

[0199] (3) In the above-mentioned embodiment, the structure in which the first fixed gear 21 is a gear with external teeth provided on the outer peripheral surface of the first annular portion A11 is described as an example. However, the present invention is not limited to such a structure, and for example, the first fixed gear 21 may be a gear with internal teeth provided on the inner peripheral surface of an annular portion different from the first annular portion A11. In this structure, it is preferable to provide a member for connecting the annular portion in which the first fixed gear 21 is provided and the first annular portion A11 in which the first ring gear R11 is provided.

[0200] (4) In the above-mentioned embodiment, the differential gear mechanism 7 is described as a double pinion type planetary gear mechanism. However, the differential gear mechanism 7 is not limited to such a structure. For example, the differential gear mechanism 7 may be a Ravigneaux type planetary gear mechanism. Alternatively, the differential gear mechanism 7 may be a bevel gear type differential gear mechanism instead of a planetary gear type differential gear mechanism.

[0201] (5) In addition, the structures disclosed in the above-mentioned embodiments can also be combined with the structures disclosed in other embodiments as long as no contradiction occurs. With regard to other structures, the embodiments disclosed in this specification are merely illustrative in all aspects. Therefore, various changes can be appropriately made without departing from the scope of the present disclosure.

[0202] (Summary of this embodiment)

[0203] Hereinafter, the above-described transmission 10 and vehicle drive transmission device 100 will be described in outline.

[0204] The transmission 10 includes: a planetary gear mechanism 1, including an input element 11 drivingly connected to a driving 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 fixed device 2, which selectively fixes the first fixed element 13 to a non-rotating member NR; and a second fixed device 3, which selectively fixes the second fixed element 14 to the non-rotating member NR, the first fixed device 2 including: a first fixed gear 21 connected to rotate integrally with the first fixed element 13; a first fixed gear 22 meshing with the first fixed gear 21; and a first friction engagement device 4, which selectively engages the first fixed gear 22 with the non-rotating member NR, the second fixed device 3 including: a second fixed gear 3 1, connected to rotate integrally with the above-mentioned second fixed element 14; the second fixed gear 32 is meshed with the above-mentioned second fixed gear 31; and the second friction engagement device 5 makes the above-mentioned second fixed gear 32 selectively engage with the above-mentioned non-rotating member NR, the above-mentioned first friction engagement device 4 and the above-mentioned first fixed gear 22 are arranged on the same axis, the above-mentioned second friction engagement device 5 and the above-mentioned second fixed gear 32 are arranged on the same axis, the rotation axis of the above-mentioned first fixed gear 22 and the rotation axis of the above-mentioned second fixed gear 32 are arranged parallel to each other, and the direction along the rotation axis of the above-mentioned first fixed gear 22 and the rotation axis of the above-mentioned second fixed gear 32 is taken as the axial direction L, and the above-mentioned first friction engagement device 4 and the above-mentioned second friction engagement device 5 are arranged so as not to overlap each other when observed along the axial direction of the above-mentioned axial direction L.

[0205] According to this structure, the first fixed 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 that selectively engages the first fixed gear 22 with the non-rotating member NR. Moreover, the first friction engagement device 4 and the first fixed gear 22 are arranged on the same axis. In addition, the second fixed 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 that selectively engages the second fixed gear 32 with the non-rotating member NR. Moreover, the second friction engagement device 5 and the second fixed gear 32 are arranged on the same axis. As a result, it is easy to arrange the first friction engagement device 4 and the second friction engagement device 5 on different axes. Therefore, compared with a structure in which they are arranged on the same axis, it is easy to suppress the size of the axial direction L of the transmission 10 to be small.

[0206] In addition, according to this structure, the diameter of the first fixed gear 22 relative to the first fixed gear 21 is set small in the first fixing device 2, and 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 a small value. As a result, it is easy to reduce the diameter of the first friction engagement device 4. In addition, the second fixing device 3 is also similarly easy to reduce the diameter of the second friction engagement device 5.

[0207] As described above, according to this configuration, in a configuration including a pair of friction engagement devices 4 and 5 , it is easy to achieve miniaturization of the transmission 10 .

[0208] Here, it is preferred that the first friction engagement device 4 includes: a first friction member 41, which is arranged on the same axis as the first fixed gear 22; a second friction member 42, which is arranged on the same axis as the first fixed gear 22 and is arranged to be opposite to the first friction member 41 in the axial direction L; a first support member 43, which is connected to the first fixed gear 22 to rotate integrally with the first fixed gear 22 and supports the first friction member 41 in a state where the relative rotation of the first friction member 41 is restricted; a second support member 44, which is fixed to the non-rotating member NR and supports the second friction member 42 in a state where the relative rotation of the second friction member 42 is restricted; and a first pressing device 45, which presses the first friction member 41 and the second friction member 42 in the axial direction L,

[0209] The second friction engagement device 5 includes: a third friction member 51, which is arranged on the same axis as the second fixed gear 32; a fourth friction member 52, which is arranged on the same axis as the second fixed gear 32 and is arranged to be opposite to the third friction member 51 in the axial direction L; a third support member 53, which is connected to rotate integrally with the second fixed gear 32 and supports the third friction member 51 in a state where the relative rotation of the third friction member 51 is restricted; a fourth support member 54, which is fixed to the non-rotating member NR and supports the fourth friction member 52 in a state where the relative rotation of the fourth friction member 52 is restricted; and a second pressing device 55, which presses the third friction member 51 and the fourth friction member 52 in the axial direction L,

[0210] A direction perpendicular to the rotation axis of the first fixed gear 22 is referred to as a first radial direction RA, and a direction perpendicular to the rotation axis of the second fixed gear 32 is referred to as a second radial direction RB.

[0211] The first pressing device 45 comprises: 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 threaded first linear motion conversion mechanism 48 for converting the rotational driving force of the first drive motor 47 into the driving force in the axial direction L and transmitting the driving force to the first pressing member 46.

[0212] The first linear motion conversion mechanism 48 is arranged on the inner side of the first radial direction RA relative to the first friction member 41 and the second friction member 42, and is arranged at a position overlapping with the first friction member 41 and the second friction member 42 when viewed along the first radial direction of the first radial direction RA.

[0213] The second pressing device 55 comprises: a second pressing member 56 for applying a pressing force to the third friction member 51 and the fourth friction member 52; a second drive motor 57; and a threaded second linear motion conversion mechanism 58 for converting the rotational driving force of the second drive motor 57 into the driving force in the axial direction L and transmitting the driving force to the second pressing member 56.

[0214] The second linear motion conversion mechanism 58 is arranged inside the third friction member 51 and the fourth friction member 52 in the second radial direction RB and is arranged at a position overlapping the third friction member 51 and the fourth friction member 52 when viewed in the second radial direction along the second radial direction RB.

[0215] According to this structure, the first friction engagement device 4 is configured to be coaxially arranged with the first fixed gear 22, and includes the first friction member 41, the second friction member 42, and the first support member 43. Therefore, compared with a structure in which the first friction member 41, the second friction member 42, and the first support member 43 are coaxially arranged with the first fixed element 13 of the planetary gear mechanism 1, it is easy to suppress the radial R dimension of the first friction engagement device 4 to be small. In addition, similarly, with respect to the second fixed device 3, compared with a structure in which the third friction member 51, the fourth friction member 52, and the third support member 53 are coaxially arranged with the second fixed element 14 of the planetary gear mechanism 1, it is easy to suppress the radial R dimension of the second friction engagement device 5 to be small.

[0216] In addition, according to this structure, the first linear motion conversion mechanism 48 of the first pressing device 45 is arranged using the space on the inner side of the first radial direction RA relative 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 on the inner side of the second radial direction RB relative to the third friction member 51 and the fourth friction member 52. Therefore, it is easy to achieve miniaturization 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 miniaturization of the transmission 10.

[0217] In addition, according to this structure, the first pressing member 46 is moved in the axial direction L by the first threaded linear motion conversion mechanism 48, and the second pressing member 56 is moved in the axial direction L by the second threaded linear motion conversion mechanism 58. Thus, the positions of the first pressing member 46 and the second pressing member 56 can be maintained even in the absence of the driving force of the first drive motor 47 and the second drive motor 57. Therefore, even in the state where no power is supplied to the transmission 10, both the first friction engagement device 4 and the second friction engagement device 5 can be set to the engagement state, and the output element 12 of the planetary gear mechanism 1 can be locked so as not to rotate. Therefore, it is not necessary to provide a parking brake separately.

[0218] In addition, it is preferred that the drive source D is a rotary electric machine MG having a rotor RT, and 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 as the wheel W; a second output member 82 that is drivingly connected to a second wheel W2 that is different from the wheel W and the first wheel W1; a differential gear mechanism 7 that includes a differential input element 71 that is connected to rotate integrally with the rotor shaft 6, a first differential output element 72, and a second differential output element 73 that transmits the output of the first wheel W1 from the rotor shaft 6 to the first wheel W2; and a differential gear mechanism 7 that includes a differential input element 71 that is connected to rotate integrally with the rotor shaft 6, a first differential output element 72, and a second differential output element 73 that transmits the output of the first wheel W1 from the rotor shaft 6 to the first wheel W1. The torque transmitted to the differential input element 71 is distributed to the first differential output element 72 and the second differential output element 73; the first transmission 10A as the transmission 10; and the second transmission 10B, which is different from the transmission 10 and the first transmission 10A, is connected to the input element 11 of the first transmission 10A so as to rotate integrally with the first differential output element 72, the output element 12 of the first transmission 10A is connected to rotate integrally with the first output member 81, and the second transmission 10B is connected to the first differential output element 72 so as to rotate integrally with the first output member 81. The input element 11 is connected to rotate integrally with the second differential output element 73, the output element 12 of the second transmission 10B is connected 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 on the same axis, 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 same axis and connected to rotate integrally with each other, and 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 same axis and connected to rotate integrally with each other. The second fixed gear 31 is coaxially arranged with the second fixed gear 31 of the second transmission 10B, the second fixed gear 32 of the first transmission 10A is coaxially arranged with the second fixed gear 32 of the second transmission 10B and is connected to rotate integrally with each other, the first friction engagement device 4 of the first transmission 10A is shared with the first friction engagement device 4 of the second transmission 10B, and the second friction engagement device 5 of the first transmission 10A is shared with the second friction engagement device 5 of the second transmission 10B.

[0219] According to this structure, in the structure in which the transmission 10 is provided in the power transmission path 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 on the same axis and connected to rotate integrally with each other. In addition, the second fixed gears 32 constituting the second fixing device 3 of the pair of transmissions 10 are arranged on the same axis and connected to rotate integrally with each other. Thus, the pair of first fixed gears 22 can be selectively engaged with the non-rotating member NR by the 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 the one second friction engagement device 5.

[0220] Therefore, in the configuration including the 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 to reduce the size of the vehicle drive transmission device 100 .

[0221] In addition, it is preferred that the drive source D is a rotary electric machine MG having a rotor RT, and 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 as the wheel W; a second output member 82 that is drivingly connected to a second wheel W2 that is different from the wheel W and the first wheel W1; the transmission 10; and 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, connects the input element 11 of the transmission 10 to rotate integrally with the rotor shaft 6, connects the output element 12 of the transmission 10 to rotate integrally with the externally toothed drive gear 16, and connects the differential gear mechanism 7 to the first differential output element 72 and the second differential output element 73. The input element 71 is connected to rotate integrally with the driven gear 74 of the external teeth meshing with the above-mentioned driving gear 16, the above-mentioned first differential output element 72 is connected to rotate integrally with the above-mentioned first output member 81, and the above-mentioned second differential output element 73 is connected to rotate integrally with the above-mentioned second output member 82. The axis of the planetary gear mechanism 1 on which the above-mentioned rotor shaft 6 and the above-mentioned transmission 10 are arranged is set as a first axis X1, the axis on which the above-mentioned first fixed gear 22 of the above-mentioned transmission 10 is arranged is set as a second axis X2, the axis on which the above-mentioned second fixed gear 32 of the above-mentioned transmission 10 is arranged is set as a third axis X3, and the axis on which the above-mentioned differential gear mechanism 7 is arranged is set as a fourth axis X4. The first axis X1, the second axis X2, the third axis X3, and the fourth axis X4 are arranged in parallel with each other, and the second axis X2, the third axis X3, and the fourth axis X4 are arranged to surround the periphery of the above-mentioned first axis X1.

[0222] According to this structure, in a structure in which the planetary gear mechanism 1 of the transmission 10 is arranged on the same axis as 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 dimension of the radial direction R of the vehicle drive transmission device 100 with respect to the first axis X1 to be small.

[0223] Industrial Applicability

[0224] The technology disclosed in the present invention can be used in a transmission and a drive transmission device for a vehicle equipped with the transmission, wherein the transmission comprises: a planetary gear mechanism having 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 fixed device selectively fixing the first fixed element to a non-rotating component; and a second fixed device selectively fixing the second fixed element to a non-rotating component.

[0225] Description of Reference Numerals

[0226] 100...Drive transmission device for vehicle; 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 fixed gear; 3...Second fixing device; 31...Second fixed gear; 32...Second fixed gear; 4...First friction engagement device; 41...First friction member; 42...Second friction member; 43...First supporting member; 44...Second supporting 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...driving source; MG...rotating motor; 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 transmission, wherein: have: 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 for selectively fixing the first fixing element to a non-rotating component; as well as a second fixing device, selectively fixing the second fixing element to the non-rotating component, The first fixing device comprises: a first fixed gear connected to rotate integrally with the first fixing element; a first fixing gear meshing with the first fixed gear; and a first friction engagement device for selectively engaging the first fixing gear with the non-rotating member. The second fixing device comprises: a second fixed gear connected to rotate integrally with the second fixing element; a second fixing gear meshing with the second fixed gear; and a second friction engagement device for selectively engaging the second fixing gear with the non-rotating member. The first friction engagement device and the first fixed gear are arranged on the same axis. The second friction engagement device and the second fixed gear are arranged on the same axis. The rotation axis of the first fixed gear and the rotation axis of the second fixed gear are arranged parallel to each other. The direction along the rotation axis of the first fixed gear and the rotation axis of the second fixed gear is defined as an axial direction. The first friction engagement device and the second friction engagement device are arranged so as not to overlap each other when viewed in the axial direction along the axial direction.

2. The transmission according to claim 1, wherein: The first friction engagement device comprises: a first friction member disposed coaxially with the first fixed gear; a second friction member disposed coaxially with the first fixed gear and disposed to face the first friction member in the axial direction; a first supporting member connected to the first fixed gear so as to rotate integrally with the first fixed gear and supporting the first friction member while restricting the relative rotation of the first friction member; a second supporting member fixed to the non-rotating member and supporting the second friction member while restricting the relative rotation of the second friction member; and a first pressing device for pressing the first friction member and the second friction member in the axial direction, The second friction engagement device comprises: a third friction member disposed coaxially with the second fixed gear; a fourth friction member disposed coaxially with the second fixed gear and disposed to be opposed to the third friction member in the axial direction; a third supporting member connected to the second fixed gear so as to rotate integrally with the third friction member and supporting the third friction member while restricting the relative rotation of the third friction member; a fourth supporting member fixed to the non-rotating member and supporting the fourth friction member while restricting the 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, A direction perpendicular to the rotation axis of the first fixed gear is defined as a first radial direction, and a direction perpendicular to the rotation axis of the second fixed gear is defined as a second radial direction. The first pressing device comprises: a first pressing member, which applies a pressing force to the first friction member and the second friction member; a first drive motor; and a first threaded linear motion conversion mechanism, which converts the rotational driving force of the first drive motor into the axial driving force and transmits it to the first pressing member. The first linear motion conversion mechanism is arranged on the inner side of the first radial direction relative to the first friction member and the second friction member, and is arranged at a position overlapping with the first friction member and the second friction member when viewed in the first radial direction along the first radial direction. The second pressing device comprises: 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 threaded second linear motion conversion mechanism for converting the rotational driving force of the second drive motor into the axial driving force and transmitting the axial driving force 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 is arranged at a position overlapping the third friction member and the fourth friction member when viewed along a second radial direction of the second radial direction.

3. A drive transmission device for a vehicle, wherein: The driving source is a rotating electric machine having a rotor, The vehicle drive transmission device comprises: a rotor shaft, rotating integrally with the rotor; A first output member drivingly connected to a first wheel as the wheel; a second output member drivingly connected to the wheel and a second wheel different from the first wheel; as well as, a differential gear mechanism including a differential input element connected to rotate integrally with the rotor shaft, a first differential output element, and a second differential output element, and distributing torque transmitted from the rotor shaft to the differential input element to the first differential output element and the second differential output element; The transmission described in claim 1 is a first transmission; as well as A second transmission is the transmission according to claim 1 and is different from the first transmission, The input element of the first transmission is coupled 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 coupled 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 on the same axis. The first fixed gear of the first transmission and the first fixed gear of the second transmission are coaxially arranged and 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 on the same axis. The second fixed gear of the first transmission and the second fixed gear of the second transmission are coaxially arranged and connected to rotate integrally with each other. The first friction engagement device of the first transmission is shared with the first friction engagement device of the second transmission. The second friction engagement device of the first transmission is shared by the second friction engagement device of the second transmission.

4. A drive transmission device for a vehicle, wherein: The driving source is a rotating electric machine having a rotor, The vehicle drive transmission device comprises: a rotor shaft, rotating integrally with the rotor; A first output member drivingly connected to a first wheel as the wheel; A second output member drivingly connected to the wheel and a second wheel different from the first wheel; the transmission according to claim 1; as well as The differential gear mechanism includes a differential input element, a first differential output element, and a second differential output element, and 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 to rotate integrally with the rotor shaft, The output element of the transmission is connected to the externally toothed drive gear so as to rotate integrally. The differential input element is connected to rotate integrally with a driven gear having external teeth meshing with the driving gear, The first differential output element is coupled to rotate integrally with the first output member, The second differential output element is coupled to rotate integrally with the second output member, The shaft on which the rotor shaft and the planetary gear mechanism of the transmission are arranged is set as a first shaft, the shaft on which the first fixed gear of the transmission is arranged is set as a second shaft, the shaft on which the second fixed gear of the transmission is arranged is set as a third shaft, and the shaft on which the differential gear mechanism is arranged is set as a fourth shaft, The first axis, the second axis, the third axis, and the fourth axis are arranged parallel to each other. The second axis, the third axis, and the fourth axis are arranged to surround the first axis.

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