JP2024043033A - Vehicle drive transmission device - Google Patents

Abstract

[Problem] To provide a drive transmission device for a vehicle that has a simplified and compact configuration and can prevent differences in torque transmitted to a first output member and a second output member caused by variations in the engagement force of a friction engagement device. [Solution] The first reduction gear 3A is a planetary gear mechanism including an input element 31A that rotates integrally with the first differential output element 22, an output element 32A that rotates integrally with the first output member 4A, and a fixed element 33A that rotates integrally with the first fixed gear 5A, and the second reduction gear 3B is a planetary gear mechanism including an input element 31B that rotates integrally with the second differential output element 23, an output element 32B that rotates integrally with the second output member 4B, and a fixed element 33B that rotates integrally with the second fixed gear 5B, and a first fixed gear 6A that meshes with the first fixed gear 5A and a second fixed gear 6B that meshes with the second fixed gear 5B rotate integrally with each other and are engaged with a non-rotating member NR via a friction engagement device 7. [Selected Figure] Figure 1

Description

The present invention includes an input member drivingly connected to a drive source, a first output member drivingly connected to a first wheel, a second output member drivingly connected to a second wheel, and a differential input element from the input member. a differential gear mechanism that distributes the torque transmitted to the first differential output element and the second differential output element, and a first differential gear mechanism that decelerates the rotation of the first differential output element and transmits it to the first output member. The present invention relates to a vehicle drive transmission device including a reduction gear and a second reduction gear that reduces rotation of a second differential output element and transmits the rotation to a second output member.

An example of such a vehicle drive transmission device is disclosed in Patent Document 1 below. Hereinafter, in the description of the background art, the reference numerals in Patent Document 1 will be cited in parentheses.

In the vehicle drive transmission device of Patent Document 1, the first reduction gear (205) includes a first sun gear connected to rotate integrally with the first differential output element of the differential gear mechanism (201); It includes a first carrier connected to rotate integrally with a first output member drivingly connected to the first wheel, and a first ring gear connected to a non-rotating member (221). The second reduction gear (207) also includes a second sun gear connected to rotate integrally with the second differential output element of the differential gear mechanism (201), and a second sun gear drivingly connected to the second wheel. The second carrier is connected to rotate integrally with the second output member, and the second ring gear (223) is connected to a non-rotating member (221).

In the vehicle drive transmission device of Patent Document 1, a friction engagement device (219) is provided in the second reduction gear (207). Specifically, the second ring gear (223) of the second reduction gear (207) is engaged with the non-rotating member (221) via a friction engagement device (219). This frictional engagement device (219) is configured as a torque limiter. Therefore, under normal conditions when a torque lower than the allowable transmission torque of the frictional engagement device (219) acts on the second ring gear (223), the frictional engagement device (219) causes the second ring gear (223) to connect to the non-rotating member (221). It is connected to. On the other hand, when a torque exceeding the allowable transmission torque of the friction engagement device (219) acts on the second ring gear (223), the friction engagement device (219) connects the second ring gear (223) with the non-rotating member (221). ) is disconnected. The second ring gear (223) rotates relative to the non-rotating member (221), thereby restricting torque transmission between the second ring gear (223) and the non-rotating member (221).

JP2020-67182A

As mentioned above, in the vehicle drive transmission device of Patent Document 1, the friction engagement device (219) is provided in the second reduction gear (207), whereas the friction engagement device (219) is provided in the first reduction gear (205). It has not been done. Therefore, when the friction engagement device (219) is slipping, the first output member connected to rotate integrally with the first carrier, which is the output element of the first reduction gear (205), and the second reduction gear (207) The problem has arisen in that the torque balance between the second carrier, which is the output element, and the second output member, which is connected to rotate integrally, is likely to be disturbed, and the stability of the vehicle may be reduced. .

As a means to solve the above problems, it is possible to provide a frictional engagement device in the first reduction gear (205) in addition to the second reduction gear (207). However, in that case, it is disadvantageous in that the structure of the vehicle drive transmission device becomes complicated and larger. Further, due to variations in the engagement force between the pair of frictional engagement devices, a difference may occur in the torque transmitted to the first output member and the second output member. Such a torque difference is disadvantageous in that it may reduce the stability of the vehicle.

Therefore, in addition to simplifying and downsizing the configuration of the vehicle drive transmission device, the difference in the torque transmitted to the first output member and the second output member due to the variation in the engagement force of the friction engagement device. It is desired to realize a vehicle drive transmission device that can avoid this occurrence.

In view of the above, the characteristic configuration of the vehicle drive transmission device is as follows:
an input member drivingly connected to a driving source;
a first output member drivingly connected to the first wheel;
a second output member drivingly connected to the second wheel;
A differential input element, a first differential output element, and a second differential output element are connected to the input member so as to rotate integrally with the input member, and the torque is transmitted from the input member to the differential input element. a differential gear mechanism that distributes the output to the first differential output element and the second differential output element;
a first speed reducer that reduces rotation of the first differential output element and transmits it to the first output member;
A vehicular drive transmission device comprising: a second reduction gear that decelerates rotation of the second differential output element and transmits the rotation to the second output member,
The first reduction gear includes a first reduction input element connected to rotate integrally with the first differential output element, and a first reduction input element connected to rotate integrally with the first output member. A planetary gear mechanism comprising a deceleration output element and a first deceleration fixing element connected to rotate integrally with the first fixed gear,
The second reduction gear includes a second reduction input element connected to rotate integrally with the second differential output element, and a second reduction input element connected to rotate integrally with the second output member. A planetary gear mechanism comprising a deceleration output element and a second deceleration fixing element connected to rotate integrally with the second fixed gear,
A first fixed gear that meshes with the first fixed gear and a second fixed gear that meshes with the second fixed gear are connected to each other so as to rotate integrally with each other, and via a friction engagement device. in that it is engaged with a non-rotating member.

According to this characteristic configuration, in a configuration including a differential gear mechanism that distributes the driving force of a driving source to a first differential output element and a second differential output element, a first reduction gear that reduces the rotation of the first differential output element and transmits it to a first output member, and a second reduction gear that reduces the rotation of the second differential output element and transmits it to a second output member, it is possible to share the friction engagement devices for engaging the reduction-reduction fixed elements of the pair of reduction gears with the non-rotating members. Therefore, it is easier to simplify and miniaturize the configuration of the vehicle drive transmission device compared to a case in which friction engagement devices are provided corresponding to the reduction-reduction fixed elements of the pair of reduction gears.
Furthermore, when a friction engagement device is provided corresponding to each of the reduction-reduction fixed elements of a pair of speed reducers, a difference may occur between the torque transmitted to the first output member and the torque transmitted to the second output member due to variation in the engagement force of the pair of friction engagement devices. Such a torque difference may be a factor in reducing the stability of the vehicle. According to this characteristic configuration, the pair of reduction-reduction fixed elements are engaged with the non-rotating member via a common friction engagement device. Therefore, it is possible to avoid a difference occurring between the torque transmitted to the first output member and the torque transmitted to the second output member due to variation in the engagement force of the friction engagement device.

A cross-sectional view along the axial direction of the vehicle drive transmission device according to the first embodiment Skeleton diagram of the vehicle drive transmission device according to the first embodiment A partially enlarged view of a cross-sectional view along the axial direction of the vehicle drive transmission device according to the first embodiment FIG. 13 is a partially enlarged cross-sectional view of a vehicle drive transmission device according to a second embodiment taken along an axial direction; FIG. 11 is a cross-sectional view taken along an axial direction of a vehicle drive transmission device according to a third embodiment; Skeleton diagram of a vehicle drive transmission device according to a third embodiment

1. First Embodiment Below, a vehicle drive transmission device 100 according to a first embodiment will be described with reference to FIGS. 1 to 3.

As shown in FIGS. 1 and 2, the vehicle drive transmission device 100 includes an input member 1, a differential gear mechanism 2, a first reduction gear 3A, a second reduction gear 3B, and a first output member 4A. , a second output member 4B.

The input member 1 is drivingly connected to a driving source D. In this embodiment, a rotating electric machine MG including a stator ST and a rotor RT corresponds to the drive source D. Note that in this application, the term "rotating electric machine" is used as a concept that includes a motor (electric motor), a generator (generator), and, if necessary, a motor/generator that functions as both a motor and a generator.

Here, in this application, "drive connection" refers to a state in which two rotating elements are connected so that driving force can be transmitted, and a state in which the two rotating elements are connected so that they rotate integrally, or This includes a state in which two rotating elements are connected so that driving force can be transmitted via one or more transmission members. Such transmission members include various members that transmit rotation at the same speed or at variable speeds, such as shafts, gear mechanisms, belts, chains, and the like. Note that the transmission member may include an engagement device that selectively transmits rotation and driving force, such as a friction engagement device, a meshing engagement device, and the like. However, when each rotating element of a planetary gear mechanism is referred to as "drive connection", it refers to a state in which the rotating elements are connected to each other without intervening other rotating elements.

In this embodiment, the input member 1 is a rotor shaft 10 that rotates integrally with the rotor RT of the rotating electric machine MG. In the following description, the direction along the first axis X1, which is the rotation axis of the rotor shaft 10, is referred to as the "axial direction L". One side of the axial direction L is referred to as the "axial first side L1", and the other side of the axial direction L is referred to as the "axial second side L2". The direction perpendicular to the first axis X1 is referred to as the "radial direction R". Note that the direction perpendicular to the rotation axis of a rotating member other than the rotor shaft 10 is also referred to as the "radial direction R". In other words, the radial direction R is defined based on the rotation axis of each rotating member including the rotor shaft 10. Note that when it is not necessary to distinguish which rotation axis is the reference or when it is clear which rotation axis is the reference, it may simply be referred to as the "radial direction R".

The differential gear mechanism 2 includes a differential input element 21, a first differential output element 22, and a second differential output element 23. The differential gear mechanism 2 distributes the torque transmitted from the input member 1 to the differential input element 21 to the first differential output element 22 and the second differential output element 23. The differential input element 21 is an input element of the differential gear mechanism 2. The differential input element 21 is connected to the input member 1 so as to rotate integrally therewith. The first differential output element 22 and the second differential output element 23 are output elements of the differential gear mechanism 2.

The first reduction gear 3A reduces the rotation of the first differential output element 22 of the differential gear mechanism 2 and transmits the reduced rotation to the first output member 4A. The second reducer 3B reduces the rotation of the second differential output element 23 of the differential gear mechanism 2 and transmits the reduced rotation to the second output member 4B.

The first output member 4A is drivingly connected to the first wheel W1 (see FIG. 2). The second output member 4B is drivingly connected to the second wheel W2 (see FIG. 2). In this embodiment, the first output member 4A is connected to the first wheel W1 via the first drive shaft DS1 (see FIG. 2) so as to rotate integrally with the first wheel W1. The second output member 4B is connected to the second wheel W2 via the second drive shaft DS2 (see FIG. 2) so as to rotate integrally with the second wheel W2. 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).

In this embodiment, the differential gear mechanism 2, the first reducer 3A, and the second reducer 3B are arranged on the first axis X1. That is, in this embodiment, the rotor shaft 10, the differential gear mechanism 2, the first reducer 3A, and the second reducer 3B are arranged coaxially with each other. In the illustrated example, the rotating electric machine MG, the first output member 4A, and the second output member 4B are also arranged on the first axis X1.

In addition, in this embodiment, the first reducer 3A, the differential gear mechanism 2, the rotating electric machine MG, and the second reducer 3B are arranged on the first axis X1 in the order described from the first axial side L1 to the second axial side L2. In other words, in this embodiment, the first reducer 3A and the second reducer 3B are arranged separately on both sides of the rotating electric machine MG and the differential gear mechanism 2 in the axial direction L.

As shown in FIG. 1, in this embodiment, the rotating electric machine MG, the input member 1, the differential gear mechanism 2, the first reduction gear 3A, the second reduction gear 3B, the first output member 4A, and the second output member 4B are housed in a case 9 serving as a non-rotating member NR. Note that a portion of the first output member 4A and the second output member 4B are exposed to the outside of the case 9.

The case 9 includes a peripheral wall 91 , a first side wall 92 , a second side wall 93 , a first partition 94 , and a second partition 95 .

The peripheral wall portion 91 is formed into a cylindrical shape having an axis along the axial direction L. In this embodiment, the peripheral wall portion 91 includes a stator support portion 911 that supports the stator ST of the rotating electric machine MG. The stator support portion 911 is formed to protrude inward in the radial direction R from the inner peripheral surface of the portion of the peripheral wall portion 91 where the stator support portion 911 is not provided.

The first side wall portion 92 and the second side wall portion 93 are formed to extend along the radial direction R. The first side wall portion 92 is joined to the peripheral wall portion 91 from the first axial side L1 so as to close the opening on the first axial side L1 of the peripheral wall portion 91 formed in a cylindrical shape. The second side wall portion 93 is joined to the peripheral wall portion 91 from the second axial side L2 so as to close the opening on the second axial side L2 of the peripheral wall portion 91 formed in a cylindrical shape.

The first partition wall portion 94 and the second partition wall portion 95 are formed to extend along the radial direction R. The first partition wall part 94 and the second partition wall part 95 are arranged so as to partition the internal space of the case 9 in the axial direction L. In the present embodiment, the first partition wall portion 94 is arranged to extend inward in the radial direction R from the end of the stator support portion 911 of the peripheral wall portion 91 on the first axial side L1. Further, the second partition wall portion 95 is arranged to extend inward in the radial direction R from the end of the stator support portion 911 of the peripheral wall portion 91 on the second axial side L2.

In this embodiment, the rotating electric machine MG and the differential gear mechanism 2 are arranged between the first partition wall part 94 and the second partition wall part 95 in the axial direction L. Moreover, the first speed reducer 3A and the first output member 4A are arranged between the first side wall portion 92 and the first partition wall portion 94 in the axial direction L. The second speed reducer 3B and the second output member 4B are arranged between the second side wall portion 93 and the second partition wall portion 95 in the axial direction L.

The stator ST of the rotating electric machine MG is fixed to a non-rotating member NR. In this embodiment, the stator ST is fixed to a stator support portion 911 of the case 9 as a non-rotating member NR. The rotor RT of the rotating electric machine MG is rotatably supported by the stator ST. In this embodiment, the rotor RT is arranged inside the stator ST in the radial direction R.

In this embodiment, the rotor shaft 10 is formed in a cylindrical shape extending along the axial direction L. The rotor shaft 10 is arranged to support the rotor RT from the inside in the radial direction R.

In this embodiment, the differential gear mechanism 2 is a planetary gear type differential gear mechanism equipped with a differential sun gear SG, a differential carrier CR, and a differential ring gear RG. Here, the differential gear mechanism 2 is a double-pinion type planetary gear mechanism. Therefore, the differential carrier CR rotatably supports an inner pinion gear PG1 that meshes with the differential sun gear SG, and an outer pinion gear PG2 that meshes with the inner pinion gear PG1 and the differential ring gear RG.

In this embodiment, the differential ring gear RG is connected to the rotor shaft 10 so as to rotate integrally therewith. That is, in this embodiment, the differential ring gear RG functions as the differential input element 21. In the example shown in FIG. 1, the end of the rotor shaft 10 on the first axial side L1 extends outward in the radial direction R along the end surface of the first axial side L1 of the rotor RT, and the differential ring gear Connected to RG.

In this embodiment, the differential carrier CR functions as the first differential output element 22. The differential sun gear SG functions as the second differential output element 23.

In the present embodiment, the differential gear mechanism 2 is disposed inside the stator ST in the radial direction R and at a position that overlaps with the stator ST when viewed in the radial direction along the radial direction R. Here, regarding the arrangement of two elements, "overlapping when viewed in a specific direction" means that when a virtual straight line parallel to the line of sight is moved in each direction orthogonal to the virtual straight line, the virtual straight line becomes two Refers to the existence of at least a part of the area that intersects both of the two elements.

According to this configuration, the size of the vehicle drive transmission device 100 in the axial direction L can be easily kept small compared to a configuration in which the differential gear mechanism 2 is disposed at a position shifted in the axial direction L from the stator ST.

In addition, in this embodiment, the differential gear mechanism 2 is arranged at a position overlapping with the rotor RT when viewed in the axial direction along the axial direction L. In the example shown in FIG. 1, the differential gear mechanism 2 is arranged on the first axial side L1 with respect to the rotor RT. Note that the differential gear mechanism 2 may also be arranged inward in the radial direction R from the rotor RT at a position overlapping with the rotor RT when viewed in the radial direction along the radial direction R.

The first reduction gear 3A is a planetary gear mechanism including a first reduction input element 31A, a first reduction output element 32A, and a first reduction fixing element 33A.

The first deceleration input element 31A is connected to the first differential output element 22 so as to rotate integrally therewith. In this embodiment, the first deceleration input element 31A is the first sun gear S1. The first deceleration output element 32A is connected to rotate integrally with the first output member 4A. In this embodiment, the first deceleration output element 32A is the first carrier C1. The first deceleration fixing element 33A is connected to rotate integrally with a first fixed gear 5A, which will be described later. In this embodiment, the first deceleration fixing element 33A includes a first annular portion A1 formed in an annular shape and a first ring gear R1 having internal teeth provided on the inner peripheral surface of the first annular portion A1. ing.

The first sun gear S1 is connected to a differential carrier CR as the first differential output element 22 so as to rotate integrally therewith. In this embodiment, the first sun gear S1 is connected to the differential carrier CR via the first connection shaft J1 so as to rotate integrally with the differential carrier CR. The first connecting shaft J1 is a shaft member extending along the axial direction L so as to connect the first sun gear S1 and the differential carrier CR. In this embodiment, the first connecting shaft J1 is arranged to penetrate the first partition wall portion 94 of the case 9 in the axial direction L.

The first carrier C1 rotatably supports a first large-diameter pinion gear P11 and a first small-diameter pinion gear P12, which rotate integrally with each other. Each of the first large-diameter pinion gear P11 and the first small-diameter pinion gear P12 rotates (rotates) around its own axis, and also rotates (revolutions) about the first sun gear S1 together with the first carrier C1. A plurality of the first large-diameter pinion gears P11 and the first small-diameter pinion gears P12 are provided at intervals along their own orbits.

The first large diameter pinion gear P11 meshes with the first sun gear S1. In this embodiment, the first large diameter pinion gear P11 is formed to have a larger diameter than the first sun gear S1. The first small diameter pinion gear P12 meshes with the first ring gear R1. The first small diameter pinion gear P12 is formed to have a smaller diameter than the first large diameter pinion gear P11. In this embodiment, the first small-diameter pinion gear P12 is disposed on the first side L1 in the axial direction than the first large-diameter pinion gear P11.

The second speed reducer 3B is a planetary gear mechanism including a second speed reduction input element 31B, a second speed reduction output element 32B, and a second speed reduction fixing element 33B.

The second deceleration input element 31B is connected to the second differential output element 23 so as to rotate integrally therewith. In this embodiment, the second deceleration input element 31B is the second sun gear S2. The second deceleration output element 32B is connected to rotate integrally with the second output member 4B. In this embodiment, the second deceleration output element 32B is the second carrier C2. The second deceleration fixing element 33B is connected to rotate integrally with a second fixed gear 5B, which will be described later. In this embodiment, the second deceleration fixing element 33B includes a second annular portion A2 formed in an annular shape and a second ring gear R2 having internal teeth provided on the inner peripheral surface of the second annular portion A2. ing.

The second sun gear S2 is connected to rotate integrally with the differential sun gear SG as the second differential output element 23. In this embodiment, the second sun gear S2 is connected to rotate integrally with the differential sun gear SG via the second connecting shaft J2. The second connecting shaft J2 is a shaft member extending along the axial direction L so as to connect the second sun gear S2 and the differential sun gear SG. In this embodiment, the second connecting shaft J2 is arranged to penetrate the inside of the radial direction R with respect to the rotor shaft 10 in the axial direction L. The second connecting shaft J2 is also arranged to penetrate the second partition wall portion 95 of the case 9 in the axial direction L.

The second carrier C2 rotatably supports a second large-diameter pinion gear P21 and a second small-diameter pinion gear P22, which rotate integrally with each other. Each of the second large-diameter pinion gear P21 and the second small-diameter pinion gear P22 rotates (rotates) around its own axis, and also rotates (revolutions) about the second sun gear S2 together with the second carrier C2. A plurality of second large-diameter pinion gears P21 and second small-diameter pinion gears P22 are provided at intervals along their own orbits.

The second large diameter pinion gear P21 meshes with the second sun gear S2. In this embodiment, the second large diameter pinion gear P21 is formed to have a larger diameter than the second sun gear S2. The second small diameter pinion gear P22 meshes with the second ring gear R2. The second small diameter pinion gear P22 is formed to have a smaller diameter than the second large diameter pinion gear P21. In this embodiment, the second small diameter pinion gear P22 is arranged on the second axial side L2 than the second large diameter pinion gear P21.

In this embodiment, the first output member 4A is formed in a cylindrical shape extending along the axial direction L. The first output member 4A is arranged to penetrate the first side wall portion 92 of the case 9 in the axial direction L. Further, in the present embodiment, the first output member 4A is located inside in the radial direction R with respect to the orbit of the first small diameter pinion gear P12 of the first reduction gear 3A, and is the first output member when viewed in the radial direction along the radial direction R. It is arranged at a position that overlaps with the revolution locus of the first small diameter pinion gear P12.

In this embodiment, the second output member 4B is formed in a cylindrical shape extending along the axial direction L. The second output member 4B is arranged to penetrate the second side wall portion 93 of the case 9 in the axial direction L. Further, in the present embodiment, the second output member 4B is located inside in the radial direction R with respect to the orbit of the second small diameter pinion gear P22 of the second reduction gear 3B, and is the second output member 4B when viewed in the radial direction along the radial direction R. It is arranged at a position that overlaps with the orbit of the second small diameter pinion gear P22.

As shown in FIGS. 1 and 2, the vehicle drive transmission device 100 includes the first fixed gear 5A, the second fixed gear 5B, the first fixed gear 6A, and the second fixed gear 6B. and a frictional engagement device 7.

The first fixed gear 5A and the first fixed gear 6A are arranged to mesh with each other. The second fixed gear 5B and the second fixed gear 6B are arranged to mesh with each other. In this embodiment, the first fixed gear 5A is an externally toothed gear provided on the outer circumferential surface of the first annular part A1. And the second fixed gear 5B is an externally toothed gear provided on the outer circumferential surface of the second annular part A2. Also, in this embodiment, the first fixed gear 5A is formed with a larger diameter than the first large diameter pinion gear P11, and the second fixed gear 5B is formed with a larger diameter than the second large diameter pinion gear P21. Also, in this embodiment, the first fixed gear 6A is formed with a smaller diameter than the first fixed gear 5A. And the second fixed gear 6B is formed with a smaller diameter than the second fixed gear 5B.

In this embodiment, the first fixed gear 5A and the second fixed gear 5B are arranged on the first axis X1. That is, in this embodiment, the first fixed gear 5A and the second fixed gear 5B are arranged coaxially with each other. Further, in this embodiment, the first fixed gear 6A and the second fixed gear 6B are arranged on a second axis X2 that is parallel to the first axis X1 and different from the first axis X1. That is, in this embodiment, the first fixed gear 6A and the second fixed gear 6B are arranged on separate axes parallel to the rotational axis of the rotor shaft 10.

As shown in FIG. 1, the first fixed gear 6A and the second fixed gear 6B are connected to rotate integrally with each other. Further, the first fixed gear 6A and the second fixed gear 6B are engaged with the non-rotating member NR via a friction engagement device 7. In this embodiment, the first fixed gear 6A and the second fixed gear 6B are connected via the first connecting member 61 so as to rotate integrally with each other. Further, the first fixed gear 6A and the second fixed gear 6B are connected to the frictional engagement device 7 via the first connecting member 61. The first connecting member 61 is a shaft member formed to extend along the axial direction L. In this embodiment, the first connecting member 61 is arranged on the second axis X2. Further, in the present embodiment, the first connecting member 61 is arranged so as to penetrate the stator support portion 911 of the case 9 in the axial direction L, and also to penetrate the first side wall portion 92 of the case 9 in the axial direction L. There is.

In this embodiment, the second reducer 3B has the same configuration as the first reducer 3A and is arranged in mirror symmetry with the first reducer 3A with respect to a plane perpendicular to the axial direction L. Therefore, the second sun gear S2 is formed to have the same diameter as the first sun gear S1, the second large diameter pinion gear P21 is formed to have the same diameter as the first large diameter pinion gear P11, the second small diameter pinion gear P22 is formed to have the same diameter as the first small diameter pinion gear P12, the second ring gear R2 is formed to have the same diameter as the first ring gear R1, and the second fixed gear 5B is formed to have the same diameter as the first fixed gear 5A.

In this embodiment, the frictional engagement device 7 is arranged on the second axis X2. Further, the frictional engagement device 7 is disposed on the first side L1 in the axial direction with respect to the first side wall portion 92 of the case 9.

In this embodiment, the case 9 further includes a first cylindrical wall portion 96 and a first support wall portion 97.

The first cylindrical wall portion 96 is formed into a cylindrical shape having the second axis X2 as its axis. The first cylindrical wall portion 96 is arranged to cover the frictional engagement device 7 from the outside in the radial direction R. In this embodiment, the first cylindrical wall portion 96 is joined to the first side wall portion 92 so as to extend from the first side wall portion 92 toward the first axial side L1.

The first support wall portion 97 is formed to extend along the radial direction R. The first support wall 97 is joined to the first cylindrical wall 96 so as to close the opening on the first axial side L1 of the first cylindrical wall 96 formed in a cylindrical shape. In this embodiment, the first support wall portion 97 is arranged to cover the first friction member 71 and the second friction member 72 of the friction engagement device 7 from the first axial side L1.

As shown in FIG. 3, in this embodiment, the friction engagement device 7 includes a first friction member 71, a second friction member 72, a first support member 73, a second support member 74, and a pressing device 75.

The first friction member 71 and the second friction member 72 are arranged to face each other in the axial direction L. In this embodiment, a plurality of first friction members 71 and a plurality of second friction members 72 are provided, and these are arranged alternately along the axial direction L. One of the first friction member 71 and the second friction member 72 can be a friction plate, and the other can be a separate plate.

The first support member 73 is a member that supports the outer peripheral portion of the first friction member 71 while restricting relative rotation of the first friction member 71. The first support member 73 is formed into a cylindrical shape extending along the axial direction L. The first support member 73 rotates integrally with the first fixed gear 6A and the second fixed gear 6B. In this embodiment, the first support member 73 is connected to the first connection member 61 so as to rotate integrally therewith. In the example shown in FIG. 3, the end of the first supporting member 73 on the second axial side L2 extends inward in the radial direction R, and the end of the first connecting member 61 on the first axial side L1 extends inward in the radial direction R. is connected to.

The second support member 74 is a member that supports the inner peripheral portion of the second friction member 72 while restricting relative rotation of the second friction member 72. The second support member 74 is formed into a cylindrical shape extending along the axial direction L. The second support member 74 functions as a non-rotating member NR. In this embodiment, the second support member 74 is fixed to the case 9 as a non-rotating member NR. In the example shown in FIG. 3, the second support member 74 is integrally formed with the first support wall 97 so as to protrude from the first support wall 97 of the case 9 toward the second axial side L2. .

The pressing device 75 is a device that presses the first friction member 71 and the second friction member 72 in the axial direction L. In this embodiment, the pressing device 75 includes a pressing member 76 that applies a pressing force to the first friction member 71 and the second friction member 72, and a biasing mechanism 77 that biases the pressing member 76 in the axial direction L. It is equipped with

The pressing member 76 is disposed on the inside of the first support member 73 in the radial direction R, and is positioned so as to overlap with the first support member 73 when viewed radially along the radial direction R. Furthermore, the pressing member 76 is disposed so as to overlap with the first friction member 71 and the second friction member 72 when viewed axially along the axial direction L. In this embodiment, the pressing member 76 is formed in a plate shape extending along the radial direction R.

The biasing mechanism 77 is arranged to penetrate in the axial direction L inside the second support member 74 in the radial direction R. In this embodiment, the biasing mechanism 77 includes a linear motion conversion mechanism 81 and a fixing member 82.

The linear motion conversion mechanism 81 includes a screw shaft member 811, a nut member 812, a connecting member 813, and a support member 814.

The screw shaft member 811 is formed to extend along the axial direction L. The nut member 812 is formed into an annular shape that covers the screw shaft member 811 from the outside in the radial direction R. The screw shaft member 811 and the nut member 812 are configured to be screwed together. Specifically, a male thread is formed on the outer circumference of the screw shaft member 811, and a female thread is formed on the inner circumference of the nut member 812 to be screwed into the male thread of the screw shaft member 811. Therefore, as the screw shaft member 811 rotates, the nut member 812 performs a linear motion along the axial direction L depending on the rotation direction and the directions of the male thread and the female thread.

The nut member 812 cannot rotate relative to the non-rotating member NR and is supported movably in the axial direction L. In this embodiment, the nut member 812 is arranged inside in the radial direction R with respect to the second support member 74 as the non-rotating member NR. The nut member 812 is non-rotatable relative to the second support member 74 via an annular rotation prevention member 81a disposed between the nut member 812 and the second support member 74 in the radial direction R. They are connected so as to be relatively movable in the axial direction L. In the example shown in FIG. 3, a plurality of spline teeth extending in the axial direction L are formed on the outer peripheral portion of the nut member 812 and are distributed in the circumferential direction. A plurality of spline teeth that engage with a plurality of spline teeth formed on the outer circumference of the nut member 812 are distributed in the circumferential direction so as to extend in the axial direction L on the inner circumferential portion of the detent member 81a. It is formed as follows. Furthermore, a plurality of spline teeth extending in the axial direction L are formed on the inner peripheral portion of the second support member 74 and are distributed in the circumferential direction. A plurality of spline teeth that engage with a plurality of spline teeth formed on the inner circumference of the second support member 74 are provided on the outer circumference of the detent member 81a in a circumferential direction so as to extend in the axial direction L. It is formed in a dispersed manner.

The nut member 812 is connected to the pressing member 76 so that it moves in the axial direction L together with the pressing member 76. In the example shown in FIG. 3, the nut member 812 is formed integrally with the pressing member 76. Therefore, as the screw shaft member 811 rotates, the pressing member 76 moves in the axial direction L via the nut member 812.

In this embodiment, the connecting member 813 connects the screw shaft member 811 and the fixing member 82. Further, the connecting member 813 is formed in a cylindrical shape extending from the screw shaft member 811 to the first axial side L1.

The support member 814 is supported in the axial direction L with respect to the non-rotating member NR. In this embodiment, the support member 814 is formed to protrude outward in the radial direction R from the connection member 813. The support member 814 is supported from the second axial side L2 by a support portion 74a formed to protrude inward in the radial direction R from the second support member 74 serving as the non-rotating member NR.

The fixing member 82 is a member for fixing the screw shaft member 811 to the non-rotating member NR. In this embodiment, the fixed member 82 cannot rotate relative to the fixed part 821 fixed to the first support wall part 97 of the case 9 as the non-rotating member NR and the connecting member 813 of the linear motion conversion mechanism 81. A connecting portion 822 to be connected is provided. In the example shown in FIG. 3, the fixing portion 821 is formed in a plate shape extending along the radial direction R, and is configured to close a through hole formed to penetrate the first support wall portion 97 in the axial direction L. It is located in The connecting portion 822 is formed to protrude from the fixed portion 821 toward the second axial side L2 and engage with the connecting member 813.

In addition, in this embodiment, it is possible to use a hexagon socket head bolt as the screw shaft member 811, the connection member 813, and the support member 814, for example. In this case, the threaded portion of the hexagonal socket bolt functions as a screw shaft member 811, the outer peripheral portion of the head functions as a support member 814, and the portion of the head in which the hexagonal hole is formed functions as a connecting member 813.

In this embodiment, when the pressing member 76 presses the first friction member 71 and the second friction member 72 from the second axial side L2, the first support wall portion 97 of the case 9 causes the first friction member 71 and the second friction member 72 to Movement of the second friction member 72 toward the first side L1 in the axial direction is restricted. As a result, the first friction member 71 and the second friction member 72 are connected to each other so that they cannot rotate relative to each other, and the friction engagement device 7 is brought into an engaged state. As described above, the second support member 74 that supports the second friction member 72 functions as a non-rotating member NR. Therefore, when the friction engagement device 7 is in the engaged state, the first support member 73 that supports the first friction member 71 is fixed to the second support member 74 as the non-rotating member NR. Become.

In this embodiment, the rotational position of the screw shaft member 811 is adjusted so that the friction engagement device 7 is in an engaged state. Therefore, in this embodiment, in normal times when a torque equal to or less than the allowable transmission torque of the friction engagement device 7 acts on the first support member 73, the first support member 73 is connected to the second support member 74 as the non-rotating member NR. At this time, the first fixed gear 6A and the second fixed gear 6B connected to the first support member 73 are fixed to the non-rotating member NR. Therefore, the first reduction fixed element 33A connected to the first fixed gear 5A meshed with the first fixed gear 6A so as to rotate integrally, and the second reduction fixed element 33B connected to the second fixed gear 5B meshed with the second fixed gear 6B so as to rotate integrally are fixed to the non-rotating member NR. As a result, the power transmission between the drive source D and the first output member 4A and the second output member 4B is possible.

On the other hand, when a torque exceeding the allowable transmission torque of the friction engagement device 7 acts on the first support member 73, the connection between the first support member 73 and the second support member 74 is released. As a result, the first support member 73 rotates relative to the second support member 74, thereby restricting torque transmission between the first support member 73 and the second support member 74. At this time, the first fixed gear 6A and the second fixed gear 6B connected to the first support member 73 are rotatable relative to the non-rotating member NR. Therefore, the first reduction fixing element 33A is connected to rotate integrally with the first fixed gear 5A that meshes with the first fixed gear 6A, and the second fixed gear 5B that meshes with the second fixed gear 6B. The second deceleration fixing element 33B, which is connected to rotate with the first fixed gear 6A and the second fixed gear 6B, becomes rotatable. As a result, power transmission between the drive source D and the first output member 4A and second output member 4B is cut off.

Thus, in this embodiment, the frictional engagement device 7 functions as a torque limiter.

As described above, the vehicle drive transmission device 100 is
an input member 1 drivingly connected to a driving source D;
a first output member 4A drivingly connected to the first wheel W1;
a second output member 4B drivingly connected to the second wheel W2;
A differential input element 21, a first differential output element 22, and a second differential output element 23 are connected to rotate integrally with the input member 1, and transmission from the input member 1 to the differential input element 21 is provided. a differential gear mechanism 2 that distributes the torque generated between the first differential output element 22 and the second differential output element 23;
a first reducer 3A that decelerates the rotation of the first differential output element 22 and transmits it to the first output member 4A;
A vehicular drive transmission device 100 comprising a second reducer 3B that reduces the rotation of the second differential output element 23 and transmits it to the second output member 4B,
The first reduction gear 3A includes a first reduction input element 31A connected to rotate integrally with the first differential output element 22, and a first reduction input element 31A connected to rotate integrally with the first output member 4A. A planetary gear mechanism including a first deceleration output element 32A and a first deceleration fixing element 33A connected to rotate integrally with the first fixed gear 5A,
The second reduction gear 3B includes a second reduction input element 31B connected to rotate integrally with the second differential output element 23, and a second reduction input element 31B connected to rotate integrally with the second output member 4B. A planetary gear mechanism including a second reduction output element 32B and a second reduction fixing element 33B connected to rotate integrally with the second fixed gear 5B,
A first fixed gear 6A that meshes with the first fixed gear 5A and a second fixed gear 6B that meshes with the second fixed gear 5B are connected to rotate integrally with each other, and the friction engagement device 7 It is engaged with the non-rotating member NR via.

According to this configuration, the differential gear mechanism 2 distributes the driving force of the drive source D to the first differential output element 22 and the second differential output element 23, and the rotation of the first differential output element 22 is decelerated. In a configuration including a first reducer 3A that reduces the rotation of the second differential output element 23 and transmits the rotation to the first output member 4A, and a second reducer 3B that reduces the rotation of the second differential output element 23 and transmits the rotation to the second output member 4B, The frictional engagement device 7 for engaging each deceleration fixing element of the pair of reducers 3A, 3B with the non-rotating member NR can be shared. Therefore, compared to the case where the frictional engagement device 7 is provided corresponding to each deceleration fixing element of the pair of reducers 3A and 3B, it is easier to simplify and downsize the configuration of the vehicle drive transmission device 100.
Further, when the frictional engagement device 7 is provided corresponding to each reduction fixing element of the pair of reduction gears 3A, 3B, due to variations in the engagement force of the pair of frictional engagement devices 7, the first output member There may be a difference between the torque transmitted to the output member 4A and the torque transmitted to the second output member 4B. Such a difference in torque can be a factor that reduces the stability of the vehicle. According to this configuration, the pair of deceleration fixing elements 33A, 33B are engaged with the non-rotating member NR via the common frictional engagement device 7. Therefore, it is possible to avoid a difference between the torque transmitted to the first output member 4A and the torque transmitted to the second output member 4B due to variations in the engagement force of the frictional engagement device 7.

As described above, in this embodiment, the driving source D is a rotating electric machine MG including a stator ST and a rotor RT.
The input member 1 is a rotor shaft 10 that rotates integrally with the rotor RT.
The rotor shaft 10, the differential gear mechanism 2, the first reduction gear 3A, and the second reduction gear 3B are arranged coaxially with each other,
The first reduction gear 3A and the second reduction gear 3B are arranged separately on both sides in the axial direction L with respect to the rotating electric machine MG and the differential gear mechanism 2,
The first fixed gear 5A and the second fixed gear 5B are arranged coaxially with each other,
The first fixed gear 6A and the second fixed gear 6B are arranged on separate axes parallel to the rotation axis of the rotor shaft 10.

According to this configuration, in a configuration in which the rotor shaft 10, the differential gear mechanism 2, the first reduction gear 3A, and the second reduction gear 3B are arranged coaxially, the first reduction fixing element of the first reduction gear 3A 33A and the second reduction fixing element 33B of the second reduction gear 3B can be appropriately realized to be engaged with the non-rotating member NR via the frictional engagement device 7.

As described above, in this embodiment, the first reduction fixed element 33A includes the first annular portion A1 formed in an annular shape, and the first ring gear R1 having internal teeth provided on the inner circumferential surface of the first annular portion A1.
The second reduction fixed element 33B includes a second annular portion A2 formed in an annular shape, and a second ring gear R2 having internal teeth provided on an inner circumferential surface of the second annular portion A2.
The first fixed gear 5A is an externally toothed gear provided on the outer circumferential surface of the first annular portion A1.
The second fixed gear 5B is an externally toothed gear provided on the outer circumferential surface of the second annular portion A2.

According to this configuration, it is easy to arrange the first fixed gear 5A in the outer region in the radial direction R with respect to the first reducer 3A, and the second fixed gear 5B with respect to the second reducer 3B in the radial direction. It is easy to arrange it in the area outside R. Therefore, in the configuration in which the first fixed gear 5A and the first fixed gear 6A mesh with each other, and the second fixed gear 5B and the second fixed gear 6B mesh with each other, it is easy to reduce the size of the vehicle drive transmission device 100.

2. Second Embodiment Below, a vehicle drive transmission device 100 according to a second embodiment will be described with reference to FIG. 4. In this embodiment, the configuration of the frictional engagement device 7 is different from that of the vehicle drive transmission device 100 according to the first embodiment. Below, the explanation will focus on the differences from the first embodiment. Note that points not particularly described are the same as those in the first embodiment.

As shown in FIG. 4, in this embodiment, the biasing mechanism 77 of the friction engagement device 7 includes a pressure transmission mechanism 83 and a pressure drive source 84 instead of the fixing member 82. The pressing drive source 84 is configured to generate a driving force for driving the pressing member 76. In this embodiment, the pressing drive source 84 is an electric motor. The pressure transmission mechanism 83 is configured to transmit the driving force of the pressure drive source 84 to the linear motion conversion mechanism 81. In this embodiment, the pressure transmission mechanism 83 reduces the rotation speed of the pressure drive source 84 and transmits the rotation to the linear motion conversion mechanism 81 . The linear motion conversion mechanism 81 converts the rotation of the pressure drive source 84 transmitted via the pressure transmission mechanism 83 into a driving force in the axial direction L, and transmits it to the pressing member 76 .

In this embodiment, the pressure transmission mechanism 83 includes a first gear 831, a second gear 832, a third gear 833, and a fourth gear 834.

The first gear 831 is connected to the output shaft of the pressing drive source 84 so as to rotate together with the output shaft. In this embodiment, the first gear 831 is arranged on a third axis X3, which is a separate axis parallel to the first axis X1 and the second axis X2. Further, in this embodiment, the first gear 831 is arranged on the first axial side L1 with respect to the pressing drive source 84.

The second gear 832 meshes with the first gear 831. The second gear 832 is formed to have a larger diameter than the first gear 831. In this embodiment, the second gear 832 is arranged on a fourth axis X4, which is another axis parallel to the first axis X1, the second axis X2, and the third axis X3.

The third gear 833 is connected to the second gear 832 so as to rotate integrally with the second gear 832. The third gear 833 is formed with a smaller diameter than the second gear 832. In this embodiment, the third gear 833 is disposed on the second axial side L2 relative to the second gear 832.

The fourth gear 834 meshes with the third gear 833. The fourth gear 834 is formed to have a larger diameter than the third gear 833. The fourth gear 834 is connected to the screw shaft member 811 of the linear motion conversion mechanism 81 so as to rotate integrally therewith. In this embodiment, the fourth gear 834 is arranged on the first axial side L1 with respect to the linear motion conversion mechanism 81. Further, the fourth gear 834 is arranged on the second axis X2.

The number of teeth of the second gear 832 is greater than the number of teeth of the first gear 831. The number of teeth of the fourth gear 834 is greater than the number of teeth of the third gear 833, which rotates integrally with the second gear 832. Therefore, the rotation transmitted from the pressing drive source 84 to the first gear 831 is decelerated between the first gear 831 and the second gear 832, and then transmitted to the third gear 833. The rotation of the third gear 833 is then decelerated between the third gear 833 and the fourth gear 834 and transmitted to the linear motion conversion mechanism 81.

In this embodiment, the connecting member 813 of the linear motion conversion mechanism 81 connects the screw shaft member 811 and the fourth gear 834. Specifically, the gear connecting portion 835 extending from the fourth gear 834 to the second axial side L2 is connected to rotate integrally with the connecting member 813 in a state in which it is disposed inside the connecting member 813 in the radial direction R. In the example shown in FIG. 4, a plurality of spline teeth extending in the axial direction L are formed in a circumferentially distributed manner on the inner peripheral portion of the connecting member 813. And, a plurality of spline teeth that engage with a plurality of spline teeth formed on the inner peripheral portion of the connecting member 813 are formed in a circumferentially distributed manner so as to extend in the axial direction L on the outer peripheral portion of the gear connecting portion 835.

In this embodiment, the support member 814 of the linear motion conversion mechanism 81 is supported from the second axial side L2 via the thrust bearing B on the support portion 74a of the second support member 74 as the non-rotating member NR.

In this embodiment, when the pressing member 76 moves to the first side L1 in the axial direction and presses the first friction member 71 and the second friction member 72, the first support wall portion 97 of the case 9 71 and the second friction member 72 are restricted from moving toward the first axial side L1. As a result, the first friction member 71 and the second friction member 72 are connected to each other so that they cannot rotate relative to each other, and the friction engagement device 7 is brought into an engaged state. As described above, the second support member 74 that supports the second friction member 72 is a non-rotating member NR. Therefore, when the friction engagement device 7 is in the engaged state, the first support member 73 that supports the first friction member 71 is fixed to the second support member 74 as the non-rotating member NR. Become. At this time, the first fixed gear 6A and the second fixed gear 6B connected to the first support member 73 are fixed to the non-rotating member NR. Therefore, the first reduction fixing element 33A is connected to rotate integrally with the first fixed gear 5A that meshes with the first fixed gear 6A, and the second fixed gear 5B that meshes with the second fixed gear 6B. The second deceleration fixing element 33B, which is rotatably coupled to the non-rotating member NR, is fixed to the non-rotating member NR. As a result, the driving force of the driving source D can be transmitted to the first output member 4A and the second output member 4B.

On the other hand, when the pressing member 76 moves to the second axial side L2 and the pressing of the first friction member 71 and the second friction member 72 by the pressing member 76 is released, the first friction member 71 and the second friction member 72 are in a state where they can rotate relative to each other, and the frictional engagement device 7 is in a released state. When the friction engagement device 7 is in the released state, the first support member 73 that supports the first friction member 71 is able to rotate relative to the second support member 74 as the non-rotating member NR. At this time, the first deceleration fixing element 33A interlocks with the first support member 73 via the first fixed gear 6A and the first fixed gear 5A, and the The second deceleration fixing element 33B interlocked with the first support member 73 is not fixed to the non-rotating member NR. As a result, the driving force of the driving source D becomes unable to be transmitted to the first output member 4A and the second output member 4B (neutral state).

Thus, in this embodiment, the frictional engagement device 7 functions as a brake that selectively fixes the first support member 73 to the second support member 74 as the non-rotating member NR.

As described above, in this embodiment, as the pressing drive source 84 operates and the screw shaft member 811 rotates, the pressing member 76 rotates through the nut member 812 that is screwed into the screw shaft member 811. Move in direction L. Since the nut member 812 is screwed into the screw shaft member 811, when the pressing drive source 84 stops, the pressing member 76 connected to move integrally with the nut member 812 in the axial direction L position is maintained. Therefore, in this embodiment, each of the engaged state and released state of the frictional engagement device 7 can be maintained appropriately without operating the pressing drive source 84. In other words, the frictional engagement device 7 is configured to be self-lockable.

3. Third Embodiment Below, a vehicle drive transmission device 100 according to a third embodiment will be described with reference to FIGS. 5 and 6. The vehicle drive transmission device 100 according to the present embodiment includes a first fixed gear 5A, a second fixed gear 5B, a first fixed gear 6A, a second fixed gear 6B, and a friction engagement device 7 (hereinafter referred to as , "first frictional engagement device 7A"), a third fixed gear 5C, a fourth fixed gear 5D, a third fixed gear 6C, a fourth fixed gear 6D, and a second fixed gear 5C. This differs from the vehicle drive transmission device 100 according to the second embodiment in that it further includes a frictional engagement device 7B. Below, the explanation will focus on the differences from the second embodiment. Note that the points not particularly described are the same as those in the second embodiment.

As shown in Figures 5 and 6, in this embodiment, the first reducer 3A further includes a third reduction fixed element 33C. The third reduction fixed element 33C is connected to the third fixed gear 5C so as to rotate integrally with it. In this embodiment, the third reduction fixed element 33C includes a third annular portion A3 formed in an annular shape and a third ring gear R3 with internal teeth provided on the inner peripheral surface of the third annular portion A3. The third ring gear R3 meshes with the first large diameter pinion gear P11.

In this embodiment, the second reducer 3B further includes a fourth reduction fixed element 33D. The fourth reduction fixed element 33D is connected to the fourth fixed gear 5D so as to rotate integrally with it. In this embodiment, the fourth reduction fixed element 33D includes a fourth annular portion A4 formed in an annular shape, and a fourth ring gear R4 with internal teeth provided on the inner peripheral surface of the fourth annular portion A4. The fourth ring gear R4 meshes with the second large diameter pinion gear P21.

The third fixed gear 5C and the third fixed gear 6C are arranged to mesh with each other. The fourth fixed gear 5D and the fourth fixed gear 6D are arranged to mesh with each other. In this embodiment, the third fixed gear 5C is an externally toothed gear provided on the outer peripheral surface of the third annular portion A3. The fourth fixed gear 5D is an externally toothed gear provided on the outer peripheral surface of the fourth annular portion A4. Further, in this embodiment, the third fixed gear 6C is formed to have a smaller diameter than the third fixed gear 5C. The fourth fixed gear 6D is formed to have a smaller diameter than the fourth fixed gear 5D.

In this embodiment, the third fixed gear 5C and the fourth fixed gear 5D are arranged on the first axis X1. Further, in this embodiment, the third fixed gear 6C and the fourth fixed gear 6D are connected to a fifth fixed gear 6C that is parallel to the first axis X1 to the fourth axis X4 and that is different from the first axis X1 to the fourth axis X4. It is arranged on the axis X5.

As shown in FIG. 5, the third fixed gear 6C and the fourth fixed gear 6D are connected to rotate integrally with each other. Further, the third fixed gear 6C and the fourth fixed gear 6D are engaged with the non-rotating member NR via the second frictional engagement device 7B. In this embodiment, the third fixed gear 6C and the fourth fixed gear 6D are connected via the second connecting member 62 so as to rotate integrally with each other. Further, the third fixed gear 6C and the fourth fixed gear 6D are connected to the second frictional engagement device 7B via the second connecting member 62. The second connecting member 62 is a shaft member formed to extend along the axial direction L. In this embodiment, the second connecting member 62 is arranged on the fifth axis X5. Further, in the present embodiment, the second connecting member 62 is arranged to penetrate the stator support portion 911 of the case 9 in the axial direction L, and to penetrate the first side wall portion 92 of the case 9 in the axial direction L. There is.

In this embodiment, the second friction engagement device 7B is disposed on the fifth axis X5. The second friction engagement device 7B is disposed on the first axial side L1 relative to the first side wall portion 92 of the case 9. The second friction engagement device 7B is disposed such that the arrangement area of the second friction engagement device 7B in the axial direction L overlaps with the arrangement area of the first friction engagement device 7A in the axial direction L. In this embodiment, the second friction engagement device 7B is configured similarly to the first friction engagement device 7A except for the points that will be specifically described below.

In this embodiment, the case 9 further includes a second cylindrical wall portion 98 and a second support wall portion 99.

The second cylindrical wall portion 98 is formed into a cylindrical shape having the fifth axis X5 as its axis. The second cylindrical wall portion 98 is arranged to cover the second frictional engagement device 7B from the outside in the radial direction R. In this embodiment, the second cylindrical wall portion 98 is joined to the first side wall portion 92 so as to extend from the first side wall portion 92 toward the first side L1 in the axial direction.

The second support wall portion 99 is formed to extend along the radial direction R. The second support wall portion 99 is joined to the second cylinder wall portion 98 so as to close an opening on the first axial side L1 of the second cylinder wall portion 98 formed in a cylindrical shape. In this embodiment, the second support wall portion 99 is arranged to cover the first friction member 71 and the second friction member 72 of the second friction engagement device 7B from the first axial side L1.

The first support member 73 of the second frictional engagement device 7B rotates integrally with the third fixed gear 6C and the fourth fixed gear 6D. In this embodiment, the first support member 73 of the second frictional engagement device 7B is connected to the second connection member 62 so as to rotate integrally therewith. In the example shown in FIG. 5, the end of the first support member 73 of the second frictional engagement device 7B on the second axial side L2 extends inward in the radial direction R, and It is connected to the end of the first side L1 in the direction.

In this embodiment, the second support member 74 of the second frictional engagement device 7B is fixed to the case 9 as a non-rotating member NR. In the example shown in FIG. 5, the second support member 74 of the second frictional engagement device 7B extends from the second support wall portion 99 of the case 9 so as to protrude from the second support wall portion 99 toward the second axial side L2. is integrally formed with.

When the second friction engagement device 7B is in the engaged state, the first support member 73 that supports the first friction member 71 in the second friction engagement device 7B is a second support member serving as a non-rotating member NR. 74. At this time, the third fixed gear 6C and fourth fixed gear 6D connected to the first support member 73 of the second frictional engagement device 7B are fixed to the non-rotating member NR. Therefore, the third reduction fixing element 33C is connected to rotate integrally with the third fixed gear 5C that meshes with the third fixed gear 6C, and the fourth fixed gear 5D that meshes with the fourth fixed gear 6D. The fourth deceleration fixing element 33D, which is rotatably connected to the rotation member NR, is in a fixed state with respect to the non-rotating member NR.

On the other hand, when the second frictional engagement device 7B is in the released state, in the second frictional engagement device 7B, the first support member 73 that supports the first friction member 71 is used as a second support member as a non-rotating member NR. It becomes possible to rotate relative to the member 74. At this time, the third deceleration fixing element 33C interlocks with the first support member 73 via the third fixed gear 6C and the third fixed gear 5C, and the The fourth deceleration fixing element 33D interlocked with the first support member 73 is not fixed to the non-rotating member NR.

In this embodiment, when the first friction engagement device 7A is in an engaged state, the first ring gear R1, which has a relatively small diameter and meshes with the first small diameter pinion gear P12, and the second ring gear R2, which has a relatively small diameter and meshes with the second small diameter pinion gear P22, are fixed relative to the non-rotating member NR.

In the present embodiment, when the second frictional engagement device 7B is in the engaged state, the third ring gear R3, which has a relatively large diameter and meshes with the first large-diameter pinion gear P11, and the second large-diameter pinion gear P21 are connected to each other. The meshing fourth ring gear R4, which has a relatively large diameter, is fixed to the non-rotating member NR.

Therefore, in this embodiment, when the first frictional engagement device 7A is in the engaged state and the second frictional engagement device 7B is in the released state, the gear stage (low gear stage) with a relatively large gear ratio is The first speed reducer 3A and the second speed reducer 3B are formed. Further, when the first frictional engagement device 7A is in the released state and the second frictional engagement device 7B is in the engaged state, the gear stage (high speed stage) with a relatively small gear ratio is the first reducer 3A and the second frictional engagement device 7B. It is formed in the second speed reducer 3B.

Further, when both the first frictional engagement device 7A and the second frictional engagement device 7B are in the engaged state, the first carrier C1 as the first deceleration output element 32A and the first carrier C1 as the second deceleration output element 32B 2 carrier C2 is fixed relative to non-rotating member NR. As a result, the first output member 4A and the second output member 4B are locked. In this way, in this embodiment, the first frictional engagement device 7A and the second frictional engagement device 7B can function as a parking brake.

In addition, when both the first frictional engagement device 7A and the second frictional engagement device 7B are in the released state, the first ring gear R1 as the first reduction fixing element 33A and the second ring gear R1 as the second reduction fixing element 33B Ring gear R2, third ring gear R3 as third reduction fixing element 33C, and fourth ring gear R4 as fourth reduction fixing element 33D are not fixed to non-rotating member NR. As a result, the driving force of the driving source D becomes unable to be transmitted to the first output member 4A and the second output member 4B (neutral state).

Thus, in this embodiment, the first reduction gear 3A further includes a third reduction fixing element 33C connected to rotate integrally with the third fixed gear 5C,
The second reduction gear 3B further includes a fourth reduction fixing element 33D connected to rotate integrally with the fourth fixed gear 5D,
A third fixed gear 6C that meshes with the third fixed gear 5C and a fourth fixed gear 6D that meshes with the fourth fixed gear 5D are connected so as to rotate integrally with each other, and are engaged in a second frictional engagement. engaged with non-rotating member NR via device 7B;
The first speed reducer 3A has two states: the first speed reduction fixing element 33A is fixed to the non-rotating member NR, and the third reducing speed fixing element 33C is fixed to the non-rotating member NR. The speed ratio between the deceleration input element 31A and the first deceleration output element 32A is configured to be different,
The second speed reducer 3B has a state in which the second speed reduction fixed element 33B is fixed to the non-rotating member NR, and a state in which the fourth speed reduction fixed element 33D is fixed to the non-rotating member NR. The speed ratio between the deceleration input element 31B and the second deceleration output element 32B is configured to be different.

According to this configuration, the first fixed gear 6A and the second fixed gear 6B are fixed to the non-rotating member NR with the first frictional engagement device 7A in the engaged state, and the second frictional engagement device 7B is fixed to the non-rotating member NR. A state where the third fixed gear 6C and the fourth fixed gear 6D are freely rotatable in a released state, and a state where the first fixed gear 6A and the second fixed gear 6B are freely rotatable with the first frictional engagement device 7A in a released state. In addition, the first reduction gear 3A and the second reduction gear The gear ratio in 3B can be made different. That is, a plurality of gear stages can be formed in the first reduction gear 3A and the second reduction gear 3B.
Further, according to this configuration, by bringing both the first frictional engagement device 7A and the second frictional engagement device 7B into the engaged state, the first fixed gear 6A, the second fixed gear 6B, and the third fixed gear 6C and the fourth fixed gear 6D can be fixed to the non-rotating member NR to lock the first deceleration output element 32A and the second deceleration output element 32B from rotating. Therefore, it is possible to eliminate the need to separately provide a parking brake.

4. Other Embodiments (1) In the above embodiments, the configuration in which the differential gear mechanism 2 is a double pinion type planetary gear mechanism has been described as an example. However, the configuration is not limited to such a configuration, and, for example, the differential gear mechanism 2 may be a Ravigneau type planetary gear mechanism. Alternatively, the differential gear mechanism 2 may be a bevel gear type differential gear mechanism instead of a planetary gear type differential gear mechanism.

(2) In the above embodiment, the first fixed gear 5A is an externally toothed gear provided on the outer peripheral surface of the first annular portion A1. However, without being limited to such a configuration, for example, the first fixed gear 5A may be an internally toothed gear provided on the inner peripheral surface of an annular portion different from the first annular portion A1. good. In this configuration, it is preferable to provide a member for connecting the annular portion provided with the first fixed gear 5A and the first annular portion A1 provided with the first ring gear R1 in the radial direction R.

(3) In the first and second embodiments, each of the first reducer 3A and the second reducer 3B includes a carrier that rotatably supports the large-diameter pinion gear and the small-diameter pinion gear that rotate integrally with each other; An example of a planetary gear mechanism that includes a sun gear that meshes with a large-diameter pinion gear and a ring gear that meshes with a small-diameter pinion gear, where the reduction input element is the sun gear, the reduction output element is the carrier, and the reduction fixing element is the ring gear. It was explained as follows. However, without being limited to such a configuration, for example, each of the first reducer 3A and the second reducer 3B may include a carrier that rotatably supports a large-diameter pinion gear and a small-diameter pinion gear that rotate integrally with each other. , a planetary gear mechanism that includes a sun gear that meshes with a large-diameter pinion gear, a large-diameter ring gear that meshes with the large-diameter pinion gear, and a small-diameter ring gear that meshes with a small-diameter pinion gear, in which the reduction input element is the sun gear, and the reduction output element is the small-diameter ring gear. The reduction fixing element may be a large-diameter ring gear. Alternatively, each of the first reducer 3A and the second reducer 3B is a single pinion type planetary gear mechanism including a sun gear, a ring gear, and a carrier that rotatably supports a pinion gear that meshes with the sun gear and the ring gear. , the input element may be a sun gear, the output element may be a carrier, and the fixed element may be a ring gear.

(4) The configurations disclosed in each of the above-described embodiments may be combined with configurations disclosed in other embodiments, provided no contradictions arise. With respect to other configurations, the embodiments disclosed in this specification are merely examples in all respects. Therefore, various modifications may be made as appropriate within the scope of the spirit of this disclosure.

The technology according to the present disclosure includes an input member that is drivingly connected to a drive source, a first output member that is drivingly connected to a first wheel, a second output member that is drivingly connected to a second wheel, and a difference from the input member. a differential gear mechanism that distributes the torque transmitted to the dynamic input element to the first differential output element and the second differential output element; and a differential gear mechanism that decelerates the rotation of the first differential output element and transmits it to the first output member. The present invention can be used in a vehicle drive transmission device including a first reduction gear that reduces rotation of the second differential output element and a second reduction gear that reduces rotation of the second differential output element and transmits the rotation to the second output member.

100: Vehicle drive transmission device, 1: Input member, 10: Rotor shaft, 2: Differential gear mechanism, 21: Differential input element, 22: First differential output element, 23: Second differential output element, 3A: First reduction gear, 3B: Second reduction gear, 31A: First reduction input element, 31B: Second reduction input element, 32A: First reduction output element, 32B: Second reduction output element, 33A: First reduction fixed element, 33B: Second reduction fixed element, 33C: Third reduction fixed element, 33D: Fourth reduction fixed element, 4A: First output member, 4B: Second output member, 5A: Third 1 fixed gear, 5B: second fixed gear, 5C: third fixed gear, 5D: fourth fixed gear, 6A: first fixed gear, 6B: second fixed gear, 6C: third fixed gear, 6D: fourth fixed gear, 7: friction engagement device, 7A: first friction engagement device, 7B: second friction engagement device, D: drive source, MG: rotating electric machine, ST: stator, RT: rotor, A1: first annular part, A2: second annular part, R1: first ring gear, R2: second ring gear, NR: non-rotating member, W1: first wheel, W2: second wheel, L: axial direction, R: radial direction

Claims (5)

an input member drivingly connected to a driving source;
a first output member drivingly connected to the first wheel;
a second output member drivingly connected to the second wheel;
A differential input element, a first differential output element, and a second differential output element are connected to the input member so as to rotate integrally with the input member, and the torque is transmitted from the input member to the differential input element. a differential gear mechanism that distributes the output to the first differential output element and the second differential output element;
a first speed reducer that reduces rotation of the first differential output element and transmits it to the first output member;
A vehicular drive transmission device comprising: a second reduction gear that decelerates rotation of the second differential output element and transmits the rotation to the second output member,
The first reduction gear includes a first reduction input element connected to rotate integrally with the first differential output element, and a first reduction input element connected to rotate integrally with the first output member. A planetary gear mechanism comprising a deceleration output element and a first deceleration fixing element connected to rotate integrally with the first fixed gear,
The second reduction gear includes a second reduction input element connected to rotate integrally with the second differential output element, and a second reduction input element connected to rotate integrally with the second output member. A planetary gear mechanism comprising a deceleration output element and a second deceleration fixing element connected to rotate integrally with the second fixed gear,
A first fixed gear that meshes with the first fixed gear and a second fixed gear that meshes with the second fixed gear are connected to each other so as to rotate integrally with each other, and via a friction engagement device. A vehicle drive transmission device engaged with a non-rotating member. The drive source is a rotating electric machine including a stator and a rotor,
The input member is a rotor shaft that rotates integrally with the rotor,
The rotor shaft, the differential gear mechanism, the first reduction gear, and the second reduction gear are arranged coaxially with each other,
The direction along the rotational axis of the rotor shaft is defined as the axial direction,
The first speed reducer and the second speed reducer are arranged separately on both sides in the axial direction with respect to the rotating electric machine and the differential gear mechanism,
the first fixed gear and the second fixed gear are arranged coaxially with each other,
The vehicle drive transmission device according to claim 1, wherein the first fixed gear and the second fixed gear are arranged on separate axes parallel to the rotation axis. The first deceleration fixing element includes a first annular portion formed in an annular shape, and a first ring gear with internal teeth provided on an inner circumferential surface of the first annular portion,
The second deceleration fixing element includes a second annular portion formed in an annular shape, and a second ring gear with internal teeth provided on an inner circumferential surface of the second annular portion,
The first fixed gear is an externally toothed gear provided on the outer peripheral surface of the first annular portion,
The vehicle drive transmission device according to claim 2, wherein the second fixed gear is an externally toothed gear provided on the outer peripheral surface of the second annular portion. The direction perpendicular to the rotational axis is defined as the radial direction,
The vehicle according to claim 2 or 3, wherein the differential gear mechanism is disposed inside the stator in the radial direction and at a position overlapping the stator when viewed in the radial direction along the radial direction. drive transmission device. The first speed reducer further includes a third speed reduction fixing element connected to rotate integrally with the third fixed gear,
The second speed reducer further includes a fourth speed reduction fixing element connected to rotate integrally with the fourth fixed gear,
The frictional engagement device is a first frictional engagement device,
A third fixed gear that meshes with the third fixed gear and a fourth fixed gear that meshes with the fourth fixed gear are connected to rotate integrally with each other, and a second frictional engagement device is provided. engaged with the non-rotating member through the
The first speed reducer has a state in which the first speed reduction fixing element is fixed to the non-rotating member and a state in which the third speed reducing fixing element is fixed to the non-rotating member. The gear ratio between the first deceleration input element and the first deceleration output element is configured to be different,
The second speed reducer is configured such that the second speed reduction fixing element is fixed to the non-rotating member and the fourth speed reducing fixing element is fixed to the non-rotating member. The vehicle drive transmission device according to claim 1, wherein the speed ratio between the two deceleration input elements and the second deceleration output element is different.

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