JP6848824B2 - Vehicle drive - Google Patents

Description

The present invention relates to a vehicle drive device.

The torque of the first rotary electric machine, the second rotary electric machine, the first connecting member that is driven and connected to the first wheel, the second connecting member that is driven and connected to the second wheel, and the torque of the first rotary electric machine are first connected. A transmission device that transmits the torque of the second rotary electric machine to at least the first connecting member of the members and the second connecting member, and also transmits the torque of the second rotating electric machine to at least the second connecting member of the first connecting member and the second connecting member. Vehicle drive devices equipped with the above are known. An example of a vehicle drive device having such a configuration is disclosed in Japanese Patent Application Laid-Open No. 2017-141889 (Patent Document 1). Hereinafter, the reference numerals shown in parentheses in the description of the background technology are those of Patent Document 1.

As shown in FIGS. 1 and 7 of Patent Document 1, the vehicle drive device (1) of Patent Document 1 is driven and connected to two electric motors (2L, 2R) and left and right drive wheels (61L, 61R). A gear device (30) configured by using two output gear shafts (14L, 14R), two planetary gear mechanisms (30L, 30R), and a reduction gear housing (9) accommodating the gear device (30). ) And. This gear device (30) has an input side external gear (13a) that meshes with an input gear (12a) to which power is transmitted from an electric motor (2L, 2R), and an output gear (14L, 14R) having an output gear shaft (14L, 14R). It is provided with an output side small diameter gear (13b) that meshes with 14a). The gear mechanism (30) is configured as described in paragraph 0110 of Patent Document 1, so that the torque input to the input side external gear (13a) from the side of the electric motor (2L, 2R) can be applied. When outputting from the output side small diameter gear (13b) to the drive wheel (61L, 61R) side, the torque difference between the two electric motors (2L, 2R) is amplified and distributed to the left and right drive wheels (61L, 61R). It is configured so that it can be done (paragraphs 0108,0166).

By the way, in the vehicle drive device (1) of Patent Document 1, as described in paragraph 0118 and FIG. 2 of Patent Document 1, the output side small diameter gear (13b) that meshes with the output gear (14a) is a carrier flange (34a). It is formed on the outer peripheral surface of the hollow shaft portion (35) formed so as to project in the axial direction from the hollow shaft portion (35). Then, as described in paragraph 0116 of Patent Document 1, the hollow shaft portion (35) is supported by the reduction gear housing (9) only at one end in the axial direction. Therefore, in a state where the gear device (30) is transmitting torque, load output side small-diameter gear (13b) receives from the output gear (14a) (load due to the meshing force) is the planet carrier _(C L, _{C R)} in Easy to communicate. Further, in the vehicle drive device (1) of Patent Document 1, as described in paragraph 0121 and FIG. 2 of Patent Document 1, the input side external gear (13a) that meshes with the input gear (12a) is an internal gear ( _RL). are formed on the outer peripheral surface of the _{R R),} the internal gear _(R L, R R) is supported from the radially inner side by the carrier flange (34a, 34b). Therefore, in a state where the gear device (30) is transmitting torque, load input side external gear (13a) is received from input gear (12a) is likely to be transmitted planet carrier _(C L, _{C R)} to. Thus, in the vehicle drive device of Patent Document 1 (1), since the output-side small-diameter gear (13b) and the input-side external gear (13a) is load undergoes easily transmitted planet carrier _(C L, _{C R),} the the planet carrier _(C L, C _R) stiffness is increased correspondingly required for the planetary gear mechanism constituting the gearing (30) (30L, 30R) is likely to increase in size.

Japanese Unexamined Patent Publication No. 2017-141889

Therefore, it is desired to realize a vehicle drive device capable of downsizing the planetary gear device constituting the transmission device.

In view of the above, the first characteristic configuration of the vehicle drive device is that the first rotary electric machine, the second rotary electric machine, the first connecting member that is driven and connected to the first wheel, and the second wheel are driven and connected. The torque of the second connecting member and the first rotating electric machine is transmitted to at least the first connecting member of the first connecting member and the second connecting member, and the torque of the second rotating electric machine is transmitted to the first connecting member. A transmission device that transmits to at least the second connecting member of the connecting member and the second connecting member, the first rotating electric machine, the second rotating electric machine, the first connecting member, the second connecting member, and the said. A case for accommodating a transmission device is provided, the transmission device is arranged on a first axis, and the first connecting member and the second connecting member are arranged on a second axis parallel to the first axis. The transmission device is driven and connected to the first rotary electric machine, a first rotating element, a second rotating element that is driven and connected to the first connecting member, and a third rotation that is driven and connected to the second connecting member. A planetary gear device having at least an element and a fourth rotating element that is driven and connected to the second rotating electric machine, a first input member connected to the first rotating element, and connected to the second rotating element. A first output member, a second output member connected to the third rotating element, and a second input member connected to the fourth rotating element are provided, and the first output member is the first connected. The second output member includes a first output gear that meshes with the first driven gear included in the member, and the second output member includes a second output gear that meshes with the second driven gear included in the second connecting member. Each of the two output members is rotatably supported at two points in the axial direction by the case or a support member fixed to the case.

According to the first characteristic configuration, the first output member connected to the second rotating element of the planetary gear device is rotatably supported at two points in the axial direction by the case or the support member fixed to the case. To. That is, since the first output member can be supported by the non-rotating member at each of the two axial directions, the first output member may be supported by the non-rotating member only at one axial direction, or the first The support rigidity of the first output member can be increased as compared with the case where the output member is not supported by the non-rotating member. Therefore, the load received by the first output gear from the first driven gear can be appropriately supported, and the influence of the load on the planetary gear device can be reduced. Similarly, the second output member connected to the third rotating element of the planetary gear device is rotatably supported at two points in the axial direction by the case or the support member fixed to the case, so that the second output gear Can appropriately support the load received from the second driven gear, and can reduce the influence of the load on the planetary gear device.
As described above, according to the first characteristic configuration, the load received by the first output gear and the second output gear can be appropriately supported, and the influence of the load on the planetary gear device can be reduced. it can. Therefore, it becomes easy to secure the rigidity required for the planetary gear device, and the planetary gear device can be miniaturized.

In view of the above, the second characteristic configuration of the vehicle drive device is that the first rotary electric machine, the second rotary electric machine, the first connecting member that is driven and connected to the first wheel, and the second wheel are driven and connected. The torque of the second connecting member and the first rotating electric machine is transmitted to at least the first connecting member of the first connecting member and the second connecting member, and the torque of the second rotating electric machine is transmitted to the first connecting member. A transmission device that transmits to at least the second connecting member of the connecting member and the second connecting member, the first rotating electric machine, the second rotating electric machine, the first connecting member, the second connecting member, and the said. A case for accommodating the transmission device is provided, the transmission device is arranged on the first axis, and the first rotary electric machine and the second rotary electric machine are arranged on the third axis parallel to the first axis. The transmission device is driven and connected to the first rotary electric machine, a first rotating element, a second rotating element that is driven and connected to the first connecting member, and a third rotation that is driven and connected to the second connecting member. A planetary gear device having at least an element and a fourth rotating element that is driven and connected to the second rotating electric machine, a first input member connected to the first rotating element, and connected to the second rotating element. A first output member, a second output member connected to the third rotating element, and a second input member connected to the fourth rotating element are provided, and the first input member is the first rotation. The second input member includes a first input gear that meshes with a first drive gear that is driven and connected to an electric machine, and the second input member includes a second input gear that meshes with a second drive gear that is driven and connected to the second rotary electric machine. Each of the 1 input member and the 2nd input member is rotatably supported at two points in the axial direction by the case or the support member fixed to the case.

According to the second characteristic configuration, the first input member connected to the first rotating element of the planetary gear device is rotatably supported at two points in the axial direction by the case or the support member fixed to the case. To. That is, since the first input member can be supported by the non-rotating member at each of the two axial directions, the first input member may be supported by the non-rotating member only at one axial direction, or the first The support rigidity of the first input member can be increased as compared with the case where the input member is not supported by the non-rotating member. Therefore, the load received by the first input gear from the first drive gear can be appropriately supported, and the influence of the load on the planetary gear device can be reduced. Similarly, the second input member connected to the fourth rotating element of the planetary gear device is rotatably supported at two points in the axial direction by the case or the support member fixed to the case, so that the second input gear Can appropriately support the load received from the second drive gear, and can reduce the influence of the load on the planetary gear device.
As described above, according to the second characteristic configuration, the load received by the first input gear and the second input gear can be appropriately supported, and the influence of the load on the planetary gear device can be reduced. it can. Therefore, it becomes easy to secure the rigidity required for the planetary gear device, and the planetary gear device can be miniaturized.

Further features and advantages of the vehicle drive will be clarified from the following description of embodiments described with reference to the drawings.

Sectional drawing of the drive device for a vehicle which concerns on embodiment Partially enlarged view of FIG. Skeleton diagram of the vehicle drive device according to the embodiment Speed diagram of the planetary gear device according to the embodiment

An embodiment of a vehicle drive device will be described with reference to the drawings. In the present embodiment, the sixth bearing B6 corresponds to the "bearing arranged between the first support member and the first output member" and the "first output bearing", and the seventh bearing B7 is the "second support member". Corresponds to the "bearing placed between the first output member and the second output member" and the "second output bearing", and the ninth bearing B9 becomes the "bearing placed between the first support member and the first input member". The 12th bearing B12 corresponds to the "bearing arranged between the 2nd support member and the 2nd input member", the 13th bearing B13 corresponds to the "1st pinion bearing", and the 14th bearing B14. Corresponds to the "second pinion bearing". Further, in the present embodiment, the seventh support portion 41b corresponds to the "support portion of the first output member", the eighth support portion 42b corresponds to the "support portion of the second output member", and the ninth support portion 41c. Corresponds to the "support portion of the first input member", and the tenth support portion 42c corresponds to the "support portion of the second input member". Then, in the present embodiment, the first oil passage 91 corresponds to the "oil passage for supplying oil to the first pinion bearing", and the second oil passage 92 "for supplying oil to the first output bearing". The third oil passage 93 corresponds to the "oil passage", the third oil passage 93 corresponds to the "oil passage for supplying oil to the second pinion bearing", and the fourth oil passage 94 corresponds to "the oil passage for supplying oil to the second output bearing". Corresponds to "oil channel".

As used herein, the term "driving connection" means a state in which two rotating elements are connected so as to be able to transmit a driving force. This concept includes a state in which two rotating elements are connected so as to rotate integrally, and a state in which two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members. .. Such transmission members include various members (shafts, gear mechanisms, belts, chains, etc.) that transmit rotation at the same speed or at different speeds, and are engaging devices that selectively transmit rotation and driving force. (Friction engagement device, meshing engagement device, etc.) may be included. However, when the term "drive connection" is used for each rotating element of the differential gear device or the differential gear mechanism, the other rotating elements of the differential gear device or the differential gear mechanism have three or more rotating elements. It shall refer to the state of being driven and connected without going through.

Further, in the present specification, "rotary electric machine" is used as a concept including any of a motor (electric motor), a generator (generator), and, if necessary, a motor / generator that functions as both a motor and a generator. There is. Further, in the present specification, with respect to the arrangement of the two members, "overlapping in a specific direction" means that a virtual straight line parallel to the line-of-sight direction is moved in each direction orthogonal to the virtual straight line. It means that there is at least a part of the region where the virtual straight line intersects both of the two members. For example, "overlapping in radial direction" means that a region where the virtual straight line intersects both of the two members exists in at least a part of the circumferential direction. The direction of each member in the following description represents the direction in which they are assembled to the vehicle drive device. In addition, terms related to the direction, position, etc. of each member are concepts that include a state in which there is a difference due to an error (an error that is acceptable in manufacturing).

As shown in FIGS. 1 and 3, the vehicle drive device 1 includes a first rotary electric machine 11, a second rotary electric machine 12, a first connecting member 51 that is driven and connected to the first wheel W1, and a second wheel. It includes a second connecting member 52 that is driven and connected to W2, and a transmission device 2. Further, as shown in FIG. 1, the vehicle drive device 1 includes a case 3 accommodating a first rotary electric machine 11, a second rotary electric machine 12, a first connecting member 51, a second connecting member 52, and a transmission device 2. I have. Here, "accommodating" means accommodating at least a part of the object to be accommodated. For example, as shown in FIG. 1, in the present embodiment, the entire first connecting member 51 is housed in the case 3 (that is, arranged inside the case 3), but a part of the first connecting member 51. It is also possible that only the case 3 is housed in the case 3.

The transmission device 2 transmits the torque of the first rotary electric machine 11 to at least the first connecting member 51 of the first connecting member 51 and the second connecting member 52, and transmits the torque of the second rotating electric machine 12 to the first connecting member. It is a device that transmits to at least the second connecting member 52 of the 51 and the second connecting member 52. The first wheel W1 is rotationally driven by the torque transmitted to the first connecting member 51, and the second wheel W2 is rotationally driven by the torque transmitted to the second connecting member 52, thereby driving the vehicle (vehicle drive). A vehicle equipped with the device 1 and the same shall apply hereinafter). As shown in FIG. 3, the vehicle is provided with a first shaft member 53 that rotates integrally with the first wheel W1 and a second shaft member 54 that rotates integrally with the second wheel W2. The first shaft member 53 constitutes at least a part of the drive shaft connected to the first wheel W1 (the end opposite to the first wheel W1), and the second shaft member 54 is attached to the second wheel W2. It constitutes at least a part of the drive shaft to be connected (the end opposite to the second wheel W2). In the present embodiment, the first connecting member 51 is arranged coaxially with the first shaft member 53, and the second connecting member 52 is arranged coaxially with the second shaft member 54. When the first wheel W1 is arranged coaxially with the first shaft member 53, the first connecting member 51 is arranged coaxially with the first wheel W1 and the second wheel W2 is coaxial with the second shaft member 54. When arranged in, the second connecting member 52 is arranged coaxially with the second wheel W2. Then, in the present embodiment, the first connecting member 51 is connected so as to rotate integrally with the first wheel W1, and the second connecting member 52 is connected so as to rotate integrally with the second wheel W2. ing. Specifically, as shown in FIG. 3, in the present embodiment, the first connecting member 51 is connected via the first shaft member 53 so as to rotate integrally with the first wheel W1, and the second connecting member 51 is connected. The member 52 is connected via the second shaft member 54 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 arranged coaxially with each other (on the second axis A2 described later in the present embodiment).

In this way, the vehicle drive device 1 is provided in the vehicle so as to drive a pair of left and right wheels. For example, when the vehicle includes a pair of left and right front wheels and a pair of left and right rear wheels, the vehicle drive device 1 is provided so as to drive the pair of left and right front wheels, or to drive the pair of left and right rear wheels. be able to. In the former case, the pair of left and right front wheels are the first wheel W1 and the second wheel W2, and in the latter case, the pair of left and right rear wheels are the first wheel W1 and the second wheel W2. When the vehicle includes a pair of left and right front wheels and a pair of left and right rear wheels in this way, the pair of left and right front wheels and the pair of left and right rear wheels that are not driven by the vehicle drive device 1 are different. It may be configured to be driven by a drive device (a drive device having the same configuration as that of the vehicle drive device 1).

As shown in FIGS. 1 and 3, the transmission device 2 is arranged on the first axis A1, and the first connecting member 51 and the second connecting member 52 are placed on the second axis A2 parallel to the first axis A1. Have been placed. Further, the first rotary electric machine 11 and the second rotary electric machine 12 are arranged on the third axis A3 parallel to the first axis A1 and the second axis A2. That is, the third axis A3 is an axis parallel to the first axis A1, and the second axis A2 is an axis parallel to the first axis A1 and the third axis A3. These first axis A1, second axis A2, and third axis A3 are axes (virtual axes) different from each other. In the following, the direction parallel to each of these axes (first axis A1, second axis A2, and third axis A3) (axial direction common to each axis) is referred to as "axial direction L". Then, one side of the axial direction L is defined as the "axial first side L1", and the other side of the axial direction L (the side opposite to the axial first side L1 in the axial direction L) is defined as the "axial second side L2". And. In the present embodiment, the side on which the first rotary electric machine 11 is arranged with respect to the second rotary electric machine 12 in the axial direction L is the first side L1 in the axial direction. Further, in the following, unless otherwise specified, the “diameter direction R” represents the radial direction with respect to the first axis A1 (see FIG. 2).

The first rotary electric machine 11 includes a first stator 11a fixed to a non-rotating member such as a case 3, and a first rotor 11b rotatably supported by the first stator 11a. The first rotor 11b is connected so as to rotate integrally with the first rotor shaft 11c. The second rotary electric machine 12 includes a second stator 12a fixed to a non-rotating member such as a case 3, and a second rotor 12b rotatably supported by the second stator 12a. The second rotor 12b is connected so as to rotate integrally with the second rotor shaft 12c. Each of the first rotary electric machine 11 and the second rotary electric machine 12 is electrically connected to a power storage device such as a battery or a capacitor, and is powered by receiving electric power from the power storage device, or the inertial force of the vehicle or the like. The power generated by the above is supplied to the power storage device to store the power.

In the present embodiment, the first rotary electric machine 11 is an inner rotor type rotary electric machine, and the first rotor 11b is inside the first stator 11a in the radial direction and overlaps with the first stator 11a in the radial direction. Is located in. Further, in the present embodiment, the second rotary electric machine 12 is an inner rotor type rotary electric machine, and the second rotor 12b is inside the second stator 12a in the radial direction and overlaps with the second stator 12a in the radial direction. It is placed in the position to do. The radial direction here is the radial direction with reference to the third axis A3.

As shown in FIGS. 2 and 3, the vehicle drive device 1 includes a first drive gear 21a that is driven and connected to the first rotary electric machine 11 and a second drive gear 22a that is driven and connected to the second rotary electric machine 12. It has. The first drive gear 21a is a gear for outputting the torque of the first rotary electric machine 11, and meshes with an input gear (first input gear 71a) included in the transmission device 2. The torque of the first rotary electric machine 11 is input to the transmission device 2 from the meshing portion between the first drive gear 21a and the first input gear 71a. The second drive gear 22a is a gear for outputting the torque of the second rotary electric machine 12, and meshes with the input gear (second input gear 72a) included in the transmission device 2. The torque of the second rotary electric machine 12 is input to the transmission device 2 from the meshing portion between the second drive gear 22a and the second input gear 72a. The transmission device 2 includes a first input member 71 and a second input member 72, and the first input member 71 includes a first input gear 71a that meshes with the first drive gear 21a, and the second input member 72. However, a second input gear 72a that meshes with the second drive gear 22a is provided.

In the present embodiment, the first drive gear 21a is connected so as to rotate integrally with the first rotary electric machine 11 (first rotor 11b). Specifically, the vehicle drive device 1 attaches a first drive member 21 (here, a shaft member) connected to the first rotor shaft 11c so as to rotate integrally with the first rotary electric machine 11. A first drive gear 21a is formed on the outer peripheral surface of the first drive member 21 so as to be provided on the second side L2 in the axial direction. Further, in the present embodiment, the second drive gear 22a is connected so as to rotate integrally with the second rotary electric machine 12 (second rotor 12b). Specifically, the vehicle drive device 1 attaches a second drive member 22 (here, a shaft member) connected to the second rotor shaft 12c so as to rotate integrally with the second rotary electric machine 12. A second drive gear 22a is formed on the outer peripheral surface of the second drive member 22 so as to be provided on the first side L1 in the axial direction.

As shown in FIGS. 1 and 3, each of the first connecting member 51 and the second connecting member 52 includes a driven gear that meshes with an output gear included in the transmission device 2. Specifically, the first connecting member 51 includes a first driven gear 51a that meshes with the first output gear 81a included in the transmission device 2, and the second connecting member 52 is attached to the second output gear 82a included in the transmission device 2. It is provided with a second driven gear 52a that meshes with the second driven gear 52a. The torque for rotationally driving the first wheel W1 is output to the first connecting member 51 from the meshing portion between the first output gear 81a and the first driven gear 51a, and the torque for rotationally driving the second wheel W2 is , The second output gear 82a and the second driven gear 52a are output from the meshing portion to the second connecting member 52. The transmission device 2 includes a first output member 81 and a second output member 82, and the first output member 81 includes a first output gear 81a that meshes with the first driven gear 51a, and the second output member 82. However, a second output gear 82a that meshes with the second driven gear 52a is provided.

In this embodiment, the transmission device 2 includes a differential gear device 6. Here, the differential gear device is a gear device having a plurality of rotating elements capable of differential rotation. That is, the differential gear device is configured by using a differential gear mechanism having a plurality of rotating elements capable of differential rotation. The differential gear device is, for example, a planetary gear type differential gear device (that is, a planetary gear device), and in this case, the differential gear device is a planet gear type differential gear mechanism (that is, a planetary gear mechanism). Is constructed using. Further, the differential gear device is, for example, a bevel gear type differential gear device, and in this case, the differential gear device is configured by using a bevel gear type differential gear mechanism. The plurality of rotating elements included in the differential gear device 6 may include a non-rotating element fixed to a non-rotating member such as the case 3, but in the present specification, the non-rotating element is also included. It is called a "rotating element".

The differential gear device 6 has a first rotating element E1, a second rotating element E2, a third rotating element E3, and a fourth rotating element E4 (see FIG. 4). By connecting the first input member 71 described above to the first rotating element E1, the first rotating electric machine 11 is driven and connected to the first rotating element E1, and the first output member 81 described above is connected to the second rotating element E2. By being connected, the first connecting member 51 is driven and connected to the second rotating element E2, and the second output member 82 described above is connected to the third rotating element E3, so that the second connecting member 52 is third. The second rotary electric machine 12 is drive-connected to the fourth rotary element E4 by being drive-connected to the rotary element E3 and the second input member 72 described above being connected to the fourth rotary element E4. In this embodiment, the differential gear device 6 is a planetary gear device 60. That is, the transmission device 2 is driven and connected to the first rotating element E1 that is driven and connected to the first rotating electric machine 11, the second rotating element E2 that is driven and connected to the first connecting member 51, and the second connecting member 52. It includes a planetary gear device 60 having at least a three-rotating element E3 and a fourth rotating element E4 that is driven and connected to the second rotating electric machine 12. In the present embodiment, the planetary gear device 60 has only the first rotating element E1, the second rotating element E2, the third rotating element E3, and the fourth rotating element E4 as rotating elements.

As shown in FIGS. 2 and 3, the planetary gear device 60 includes a first planetary gear mechanism 61 having a first sun gear S1, a first carrier C1, and a first ring gear R1, a second sun gear S2, and a second carrier C2. , And a second planetary gear mechanism 62 having a second ring gear R2. The first carrier C1 rotatably supports the first pinion gear P1 via the thirteenth bearing B13, and the second carrier C2 rotatably supports the second pinion gear P2 via the fourteenth bearing B14. The planetary gear device 60 is configured by connecting the first planetary gear mechanism 61 and the second planetary gear mechanism 62. Specifically, in the present embodiment, both the first planetary gear mechanism 61 and the second planetary gear mechanism 62 are single pinion type planetary gear mechanisms. The first carrier C1 and the second sun gear S2 are connected so as to rotate integrally, and the first sun gear S1 and the second carrier C2 are connected so as to rotate integrally. As described above, the first planetary gear mechanism 61 and the second planetary gear mechanism 62 are provided with four rotating elements as a whole by connecting two of the three rotating elements each of them to each other. It is configured to perform differential operation integrally. The first planetary gear mechanism 61 is arranged on the first side L1 in the axial direction with respect to the second planetary gear mechanism 62. Further, in the present embodiment, the first planetary gear mechanism 61 is arranged on the second side L2 in the axial direction with respect to the first rotary electric machine 11, and the second planetary gear mechanism 62 is a shaft with respect to the second rotary electric machine 12. It is arranged on the first side L1 in the direction.

As shown in FIG. 3, in the present embodiment, the first rotary electric machine 11 is drive-connected to the first ring gear R1, the second rotary electric machine 12 is drive-coupled to the second ring gear R2, and the first connecting member 51 is the first. The second connecting member 52 is driven and connected to the carrier C1 and the second connecting member 52 is driven and connected to the second carrier C2. Therefore, in the present embodiment, the first rotating element E1 to which the first rotating electric machine 11 is driven and connected is the first ring gear R1, and the second rotating element E2 to which the first connecting member 51 is driven and connected is integrally. The first carrier C1 and the second sun gear S2 that rotate in the same direction, and the third rotating element E3 to which the second connecting member 52 is driven and connected are the first sun gear S1 and the second carrier C2 that rotate integrally. The fourth rotating element E4 to which the two-rotating electric machine 12 is driven and connected is the second ring gear R2. Then, in the present embodiment, the order of the rotation speed is the order of the first rotation element E1, the second rotation element E2, the third rotation element E3, and the fourth rotation element E4.

The "order of rotation speeds" is the order of rotation speeds of each rotating element in the rotating state. The rotational speed of each rotating element changes depending on the rotational state of the differential gear device 6 (planetary gear device 60), but the order of the high and low rotational speeds of each rotating element is determined by the structure of the differential gear device 6. Therefore, it becomes constant. The "order of rotation speed of each rotating element" is the same as the order of arrangement in the speed diagram (collinear diagram, see FIG. 4) of each rotating element. Here, the "arrangement order of each rotating element in the speed diagram" is the order in which the axes corresponding to each rotating element in the speed diagram (collinear diagram) are arranged along the direction orthogonal to the axis. That is. The arrangement direction of the axes corresponding to each rotating element in the speed diagram (collinear diagram) differs depending on how the speed diagram is drawn, but the arrangement order is fixed because it is determined by the structure of the differential gear device 6. Become. In FIG. 4, "0" on the vertical axis indicates that the rotation speed is zero, and the upper side is positive and the lower side is negative.

In FIG. 4, "Ti1" represents the torque (first input torque Ti1) input to the first rotating element E1 from the side of the first rotating electric machine 11, and "Ti2" represents the second to the fourth rotating element E4. It represents the torque (second input torque Ti2) input from the rotary electric machine 12 side. The magnitude of the first input torque Ti1 is determined according to the magnitude of the output torque of the first rotary electric machine 11 and the gear ratio (first gear ratio) from the first rotary electric machine 11 to the first rotary element E1. The magnitude of the two input torque Ti2 is determined according to the magnitude of the output torque of the second rotary electric machine 12 and the gear ratio (second gear ratio) from the second rotary electric machine 12 to the fourth rotary element E4. In the present embodiment, the first drive gear 21a and the second drive gear 22a are formed to have the same diameter, and the first input gear 71a and the second input gear 72a are formed to have the same diameter. The first gear ratio and the second gear ratio are equal to each other. Here, the first gear ratio and the second gear ratio are larger than 1, the rotation of the first rotary electric machine 11 is decelerated and transmitted to the first rotation element E1, and the rotation of the second rotary electric machine 12 is decelerated to the fourth. It is transmitted to the rotating element E4.

Further, in FIG. 4, "To1" represents the torque output from the second rotating element E2 to the side of the first wheel W1 (first output torque To1), and "To2" represents the third rotating element E3 to the third. It represents the torque output to the side of the two wheels W2 (second output torque To2). The magnitude of the driving force of the first wheel W1 is determined according to the magnitude of the first output torque To1 and the gear ratio (third gear ratio) from the second rotating element E2 to the first wheel W1. The magnitude of the driving force of W2 is determined according to the magnitude of the second output torque To2 and the gear ratio (fourth gear ratio) from the third rotating element E3 to the second wheel W2. In the present embodiment, the first output gear 81a and the second output gear 82a are formed to have the same diameter, and the first driven gear 51a and the second driven gear 52a are formed to have the same diameter. The third gear ratio and the fourth gear ratio are equal to each other. Here, the third gear ratio and the fourth gear ratio are larger than 1, the rotation of the second rotating element E2 is decelerated and transmitted to the first wheel W1, and the rotation of the third rotating element E3 is decelerated to be the second wheel. It is transmitted to W2.

Since the third gear ratio and the fourth gear ratio are equal to each other as described above, when the vehicle goes straight, the rotation speed of the second rotation element E2 and the rotation speed of the third rotation element E3 become equal, and the planetary gear device 60 All the rotating elements of are rotated at the same speed. On the other hand, when the vehicle is turning, the rotation speed of the rotating element to which the outer wheels (wheels far from the turning center) of the first wheel W1 and the second wheel W2 are driven and connected is the first wheel W1 and the second wheel. The inner wheel (the wheel closer to the turning center) of the wheels W2 is in a state higher than the rotation speed of the driving and connected rotating elements. FIG. 4 shows the state of each rotating element of the planetary gear device 60 in a state where the vehicle is turning in the direction in which the first wheel W1 becomes the outer wheel.

From the balance of torque, the first output torque To1 and the second output torque To2 are the first input torque Ti1, the second input torque Ti2, and the first planet, respectively, as shown in the following equations (1) and (2). It is determined according to the gear ratio of the gear mechanism 61 (first gear ratio λ1) and the gear ratio of the second planetary gear mechanism 62 (second gear ratio λ2). Here, the first gear ratio λ1 is the ratio of the number of teeth of the first sun gear S1 to the number of teeth of the first ring gear R1, and the second gear ratio λ2 is the ratio of the number of teeth of the second sun gear S2 to the number of teeth of the second ring gear R2. It is the ratio of the number of teeth.
To1 = (1 + λ1) ・ Ti1-λ2 ・ Ti2 ・ ・ ・ (1)
To2 = (1 + λ2) ・ Ti2-λ1 ・ Ti1 ・ ・ ・ (2)

As described above, each of the first output torque To1 and the second output torque To2 is determined according to both the first input torque Ti1 and the second input torque Ti2. That is, in the present embodiment, the transmission device 2 transmits the torque of the first rotary electric machine 11 to both the first connecting member 51 and the second connecting member 52, and transfers the torque of the second rotating electric machine 12 to the first connecting member. It is configured to transmit to both the 51 and the second connecting member 52. In other words, the transmission device 2 is configured to distribute and transmit the torque of the first rotary electric machine 11 and the second rotary electric machine 12 to the first connecting member 51 and the second connecting member 52. By configuring the vehicle drive device 1 in this way, the power transmission path between the first rotary electric machine 11 and the first connecting member 51 and the power transmission between the second rotary electric machine 12 and the second connecting member 52 When a difference in driving force is provided between the first wheel W1 and the second wheel W2, the total driving force of the first wheel W1 and the second wheel W2 is increased as compared with the case where the path is separated. It is possible to secure and improve the running performance when the vehicle turns.

As a supplementary explanation, as an example, in a situation where the magnitude of the first input torque Ti1 is 200 [Nm], the difference between the first output torque To1 and the second output torque To2 is 160 [Nm]. Imagine a case. In this case, unlike the vehicle drive device 1 according to the present embodiment, in the configuration of the comparative example in which To1 = Ti1 and To2 = Ti2, the difference between the first output torque To1 and the second output torque To2 is 160 [N. The magnitude of the second input torque Ti2 for setting m] is 40 [Nm]. Therefore, in the case of this comparative example, the sum of the first input torque Ti1 and the second input torque Ti2 (equal to the sum of the first output torque To1 and the second output torque To2) is 240 [Nm]. It becomes. On the other hand, in the vehicle drive device 1 according to the present embodiment, the first output torque To1 and the second output torque To2 are combined in a situation where the magnitude of the first input torque Ti1 is 200 [Nm]. The magnitude of the second input torque Ti2 for setting the difference to 160 [Nm] is the above formula when both the first gear ratio λ1 and the second gear ratio λ2 are “0.4”. From (1) and (2), it becomes 111 [Nm]. Therefore, in this case, the sum of the first input torque Ti1 and the second input torque Ti2 (the sum of the first output torque To1 and the second output torque To2) is 311 [Nm], which is the above comparative example. Compared to the case of, the total driving force of the first wheel W1 and the second wheel W2 is equivalent to the torque difference of 71 [N ・ m] (= 311 [N ・ m] -240 [N ・ m]). Can be secured greatly.

Next, the configuration of the case 3 in the vehicle drive device 1 of the present embodiment will be described. The case 3 includes a plurality of case portions 30 that are joined via the sealing member 4. Each of the case portions 30 has a portion exposed on the outer surface of the case 3. That is, the joint portion between the case portions 30 is formed so as to be exposed on the outer surface of the case 3. The case portions 30 are joined to each other using, for example, bolts.

As shown in FIG. 1, the plurality of case portions 30 include a first case portion 31 and a second case portion 32. The first case portion 31 is joined to the second case portion 32 from the first side L1 in the axial direction. The first case portion 31 includes a first peripheral wall portion 31c formed in a tubular shape extending in the axial direction L, and is a space surrounded by the first peripheral wall portion 31c in the axial L view (first accommodation space H1). In addition, a part of the first rotary electric machine 11, the first drive member 21, the first connecting member 51, and the transmission device 2 (specifically, the first input member 71, the first output member 81, and the first planetary gear). The mechanism 61) is arranged. Further, the second case portion 32 includes a second peripheral wall portion 32c formed in a tubular shape extending in the axial direction L, and is a space surrounded by the second peripheral wall portion 32c in the axial L view (second accommodation space). H2), the second rotary electric machine 12, the second drive member 22, the second connecting member 52, and a part of the transmission device 2 (specifically, the second input member 72, the second output member 82, and the second A planetary gear mechanism 62) is arranged. In the present embodiment, the first accommodation space H1 and the second accommodation space H2 are partitioned in the axial direction L by a fifth case portion 35, which will be described later.

The plurality of case portions 30 further include a third case portion 33 and a fourth case portion 34. An opening is formed in the portion of the first accommodation space H1 where the first rotary electric machine 11 is arranged so that the first case portion 31 does not partition the first side L1 in the axial direction, and the opening is closed. The third case portion 33 is joined to the first case portion 31 from the first side L1 in the axial direction. Further, in the portion of the second accommodation space H2 where the second rotary electric machine 12 is arranged, an opening is formed without partitioning the second side L2 in the axial direction by the second case portion 32, and the opening is closed. As described above, the fourth case portion 34 is joined to the second case portion 32 from the second side L2 in the axial direction.

The plurality of case portions 30 further include a fifth case portion 35. The fifth case portion 35 is an internal space of the case 3 (accommodation space H for accommodating the first rotary electric machine 11, the second rotary electric machine 12, the first connecting member 51, the second connecting member 52, and the transmission device 2). Functions as an intermediate wall for partitioning in the axial direction L. Specifically, the fifth case portion 35 is formed in a shape extending in the radial direction R (for example, a plate shape), and a joint portion 36 between the first case portion 31 and the second case portion 32 is formed. It is arranged at the position L in the axial direction. The fifth case portion 35 is sandwiched between the first case portion 31 (first peripheral wall portion 31c) and the second case portion 32 (second peripheral wall portion 32c) from both sides in the axial direction L, and the first case portion 35 is first. It is joined to each of the case portion 31 and the second case portion 32. That is, in the present embodiment, the first case portion 31 and the second case portion 32 are joined at the joint portion 36 via the fifth case portion 35. Therefore, the joint portion 36 is formed with a joint portion between the first case portion 31 and the fifth case portion 35 and a joint portion between the second case portion 32 and the fifth case portion 35.

A sealing member 4 for preventing oil from leaking out of the case 3 in the case 3 is provided on the joint surface between different case portions in the joint portion 36 between the first case portion 31 and the second case portion 32. ing. That is, the first case portion 31 and the second case portion 32 are joined via the seal member 4. Here, "via the seal member 4" means that at least the seal member 4 is interposed between the first case portion 31 and the second case portion 32, and the seal is added to the seal member 4. It is a concept including the case where a member other than the member 4 is interposed. As described above, in the present embodiment, the first case portion 31 and the second case portion 32 are joined at the joint portion 36 via the fifth case portion 35. In the joint portion 36, the seal member 4 is provided on the joint surface (first joint surface 36a) between the first case portion 31 and the fifth case portion 35, and the second case portion 32 and the fifth case A sealing member 4 is provided on a joint surface (second joint surface 36b) with the portion 35. That is, the first case portion 31 and the second case portion 32 are joined via the seal member 4, but in the present embodiment, the first case portion 31 and the second case portion 32 are joined to each other through the first joint surface. The seal member 4 provided on the 36a, the seal member 4 provided on the second joint surface 36b, and the fifth case portion 35 are joined to each other. As the sealing member 4, for example, a liquid gasket can be used. In FIG. 1, the seal member 4 is simplified and shown by a thick line.

Next, the support structure of the first connecting member 51 and the second connecting member 52 in the vehicle drive device 1 of the present embodiment will be described. The radial direction in the following description of the support structure of the first connecting member 51 and the second connecting member 52 is the radial direction with respect to the second axis A2, unless otherwise specified.

As shown in FIG. 1, the vehicle drive device 1 includes a support member 40 fixed to the case 3. The support member 40 is arranged inside the case 3. Therefore, the fixing portion between the support member 40 and the case 3 (in the present embodiment, the first fixing portion 37a and the second fixing portion 37b, which will be described later) is different from the joint portion between the different case portions 30, and the outer surface of the case 3 is different. Not exposed to. In the present embodiment, the vehicle drive device 1 includes a first support member 41 and a second support member 42, which are support members 40 arranged inside the case 3, respectively. That is, the vehicle drive device 1 includes a first support member 41 arranged inside the case 3 and a second support member 42 arranged inside the case 3. The first support member 41 is arranged on the first side L1 in the axial direction with respect to the fifth case portion 35 (that is, arranged in the first accommodation space H1) and fixed to the first case portion 31. 1 Used to support a member arranged in the accommodation space H1. That is, the first support member 41 is fixed inside the first case portion 31, which is one of the plurality of case portions 30. Further, the second support member 42 is arranged on the second side L2 in the axial direction with respect to the fifth case portion 35 (that is, arranged in the second accommodation space H2) and fixed to the second case portion 32. , Used to support a member arranged in the second accommodation space H2. That is, the second support member 42 is fixed to the inside of the second case portion 32, which is one of the plurality of case portions 30 and is different from the first case portion 31. The first support member 41 and the second support member 42 are fixed to the case 3 using, for example, bolts.

The first connecting member 51 includes a first support portion 31a formed in the first case portion 31 and a first support member 41 (specifically, a fifth support portion 41a formed in the first support member 41). Therefore, it is rotatably supported at two locations in the axial direction L. In the present embodiment, the fifth support portion 41a is arranged on the second side L2 in the axial direction with respect to the first support portion 31a.

The first connecting member 51 is supported from the outside in the radial direction by the first supporting portion 31a. Specifically, the first bearing B1 (here, a radial type ball bearing) is arranged between the inner peripheral surface of the first support portion 31a and the outer peripheral surface of the first connecting member 51, and the first connecting is performed. The member 51 is supported from the outside in the radial direction by the first support portion 31a via the first bearing B1. Further, the first connecting member 51 is supported from the inside in the radial direction by the fifth supporting portion 41a. Specifically, the second bearing B2 (here, a radial type ball bearing) is arranged between the outer peripheral surface of the fifth support portion 41a and the inner peripheral surface of the first connecting member 51, and the first connecting is performed. The member 51 is supported from the inside in the radial direction by the fifth support portion 41a via the second bearing B2. The first driven gear 51a is formed on the outer peripheral surface of the portion of the first connecting member 51 that is radially outside the second bearing B2 and is arranged so as to overlap the second bearing B2 in the radial direction. There is. That is, the second bearing B2 is arranged so as to overlap the first driven gear 51a in the radial direction.

The second connecting member 52 includes a second support portion 32a formed on the second case portion 32 and a second support member 42 (specifically, a sixth support portion 42a formed on the second support member 42). Therefore, it is rotatably supported at two locations in the axial direction L. In the present embodiment, the sixth support portion 42a is arranged on the first side L1 in the axial direction with respect to the second support portion 32a.

The second connecting member 52 is supported from the outside in the radial direction by the second supporting portion 32a. Specifically, a fourth bearing B4 (here, a radial type ball bearing) is arranged between the inner peripheral surface of the second support portion 32a and the outer peripheral surface of the second connecting member 52, and the second connecting is performed. The member 52 is supported from the outside in the radial direction by the second support portion 32a via the fourth bearing B4. Further, the second connecting member 52 is supported from the inside in the radial direction by the sixth supporting portion 42a. Specifically, a third bearing B3 (here, a radial type ball bearing) is arranged between the outer peripheral surface of the sixth support portion 42a and the inner peripheral surface of the second connecting member 52, and the second connecting is performed. The member 52 is supported from the inside in the radial direction by the sixth support portion 42a via the third bearing B3. The second driven gear 52a is formed on the outer peripheral surface of the portion of the second connecting member 52 that is radially outside the third bearing B3 and is arranged so as to overlap the third bearing B3 in the radial direction. There is. That is, the third bearing B3 is arranged so as to overlap the second driven gear 52a in the radial direction.

As described above, the first connecting member 51 and the second connecting member 52 are rotatably and radially supported at two locations in the axial direction L by the case 3 and the support member 40. Therefore, both the first connecting member 51 and the second connecting member 52 can be supported by the non-rotating member at each of the two positions in the axial direction L, and each of the first connecting member 51 and the second connecting member 52 can be supported. It is possible to support it appropriately. On top of that, by adopting the support structure of the first connecting member 51 and the second connecting member 52 as described above, it is possible to appropriately maintain the sealing performance between the case portions 30 as described below. ing.

As described above, the first support member 41 that rotatably supports the first connecting member 51 at a position different from that of the first support portion 31a in the axial direction L is the first case portion in which the first support portion 31a is formed. Since it is fixed inside the 31, the first connecting member 51 can be supported by one case portion 30 and the support member 40 fixed inside the case portion 30. Unlike such a configuration, when the first connecting member 51 is supported by the first case portion 31 and another case portion 30 (for example, the fifth case portion 35) joined via the sealing member 4. Due to the load received by the first driven gear 51a from the first output gear 81a (load due to the meshing force), these two case portions 30 are attached to the joint portion between the first case portion 31 and the other case portion 30. A force in the direction of separating from each other (separation force) can act. On the other hand, in the vehicle drive device 1, the first connecting member 51 is formed by one case portion 30 (first case portion 31) and a support member 40 (first support member 41) fixed inside the case portion 30 (first case portion 31). Can be supported. Therefore, it is possible to suppress the action of the separation force as described above on the joint portion between the case portions 30, or to suppress the magnitude of the separation force to be small, and as a result, the sealing performance between the case portions 30 can be improved. It is possible to maintain it properly.

Similarly, in the vehicle drive device 1, the second connecting member 52 is supported by one case portion 30 (second case portion 32) and a support member 40 (second support member 42) fixed inside the case portion 30 (second case portion 32). be able to. Therefore, it is possible to prevent the above-mentioned separation force from acting on the joints between the case portions 30 due to the load (load due to the meshing force) received by the second driven gear 52a from the second output gear 82a, or The magnitude of the separation force can be suppressed to a small size, and as a result, the sealing performance between the case portions 30 can be appropriately maintained. The load due to the meshing force includes a radial load due to the pressure angle of the tooth and a thrust load due to the twist of the tooth. When a helical gear is used, the thrust load is dominant over the radial load.

Due to the load received by the first driven gear 51a from the first output gear 81a, the first support member 41 is attached to the fixing portion (first fixing portion 37a) between the first support member 41 and the first case portion 31. A force in a direction that separates the first case portion 31 from the first case portion 31 may act. Similarly, due to the load received by the second driven gear 52a from the second output gear 82a, the second support member is attached to the fixing portion (second fixing portion 37b) between the second support member 42 and the second case portion 32. A force in a direction that separates the 42 and the second case portion 32 from each other may act. However, as described above, the first fixing portion 37a and the second fixing portion 37b are not exposed to the outer surface of the case 3, unlike the joint portions between the different case portions 30, and therefore the first fixing portion 37a and the second fixing portion 37a and the second fixing portion 37b are not exposed. The influence of the above-mentioned force that can act on the fixed portion 37b on the sealing performance between the case portions (30) is limited.

As described above, in the present embodiment, the first connecting member 51 is connected so as to rotate integrally with the first wheel W1, and the second connecting member 52 is connected so as to rotate integrally with the second wheel W2. Will be done. Therefore, the first connecting member 51 is responsible for transmitting a relatively large torque (torque of the rotating electric machine (11, 12) after deceleration) equivalent to the driving torque of the first wheel W1, and the second connecting member 52 is responsible for transmitting the torque. , The configuration is such that a relatively large torque (torque of the rotating electric machine (11, 12) after deceleration) equivalent to the drive torque of the second wheel W2 is transmitted, and the first driven gear 51a is from the first output gear 81a. The load received and the load received by the second driven gear 52a from the second output gear 82a tend to be large. Regarding this point, as described above, in the vehicle drive device 1, the influence of the load received by the first driven gear 51a from the first output gear 81a on the sealing performance between the case portions 30 and the second driven gear 52a The influence of the load received from the second output gear 82a on the sealing performance between the case portions 30 can be suppressed to a small extent. Therefore, even in a configuration in which the first connecting member 51 is connected so as to rotate integrally with the first wheel W1 and the second connecting member 52 is connected so as to rotate integrally with the second wheel W2, the case portion It is possible to properly maintain the sealing performance between 30.

Next, the support structure of the first output member 81 and the second output member 82 in the vehicle drive device 1 of the present embodiment will be described.

The first output member 81 and the second output member 82 are rotatably supported by the case 3 or the support member 40. Specifically, each of the first output member 81 and the second output member 82 is rotatably supported by the case 3 or the support member 40 at two locations in the axial direction L. Here, "supported rotatably by the case 3 or the support member 40 at two places in the axial direction L" means that the case 3 is rotatably supported by the case 3 at both places in the axial direction L. It is rotatably supported by the support member 40 at both of the two locations in the direction L, and is rotatably supported by the case 3 at one location in the axial direction L and rotatably supported by the support member 40 at another location in the axial direction L. It is a concept that includes all of the things that are supported by.

As shown in FIG. 1, in the present embodiment, the first output member 81 is rotatably supported at two positions in the axial direction L by the case 3 and the first support member 41. Specifically, the first output member 81 is composed of a third support portion 31b formed on the first case portion 31 and a seventh support portion 41b formed on the first support member 41, so that the first output member 81 has an axial direction of 2 It is rotatably supported in several places. The seventh support portion 41b is arranged on the second side L2 in the axial direction with respect to the third support portion 31b.

The first output member 81 is supported from the outside in the radial direction R by the third support portion 31b. Specifically, a fifth bearing B5 (here, a radial type conical roller bearing) is arranged between the inner peripheral surface of the third support portion 31b and the outer peripheral surface of the first output member 81, and the first The output member 81 is supported from the outside in the radial direction R by the third support portion 31b via the fifth bearing B5. Further, the first output member 81 is supported from the outside in the radial direction R by the seventh support portion 41b. Specifically, a sixth bearing B6 (here, a radial type conical roller bearing) is arranged between the inner peripheral surface of the seventh support portion 41b and the outer peripheral surface of the first output member 81, and the first The output member 81 is supported from the outside in the radial direction R by the seventh support portion 41b via the sixth bearing B6. The first output gear 81a is formed on the outer peripheral surface of the portion of the first output member 81 that is arranged between the fifth bearing B5 and the sixth bearing B6 in the axial direction L.

As shown in FIG. 1, in the present embodiment, the second output member 82 is rotatably supported at two positions in the axial direction L by the case 3 and the second support member 42. Specifically, the second output member 82 has a fourth support portion 32b formed on the second case portion 32 and an eighth support portion 42b formed on the second support member 42, so that the second output member 82 has an axial direction of 2 It is rotatably supported in several places. The eighth support portion 42b is arranged on the first side L1 in the axial direction with respect to the fourth support portion 32b.

The second output member 82 is supported from the outside in the radial direction R by the fourth support portion 32b. Specifically, the eighth bearing B8 (here, a radial type conical roller bearing) is arranged between the inner peripheral surface of the fourth support portion 32b and the outer peripheral surface of the second output member 82, and the second bearing. The output member 82 is supported from the outside in the radial direction R by the fourth support portion 32b via the eighth bearing B8. Further, the second output member 82 is supported from the outside in the radial direction R by the eighth support portion 42b. Specifically, a seventh bearing B7 (here, a radial type conical roller bearing) is arranged between the inner peripheral surface of the eighth support portion 42b and the outer peripheral surface of the second output member 82, and the second bearing. The output member 82 is supported from the outside in the radial direction R by the eighth support portion 42b via the seventh bearing B7. The second output gear 82a is formed on the outer peripheral surface of the portion of the second output member 82 that is arranged between the seventh bearing B7 and the eighth bearing B8 in the axial direction L.

As described above, the first output member 81 and the second output member 82 are rotatably supported in the radial direction R at two locations in the axial direction L by the case 3 or the support member 40. Therefore, both the first output member 81 and the second output member 82 can be supported by the non-rotating member at each of the two positions in the axial direction L, and the first output member 81 and the second output member 82 are in the axial direction. Compared to the case where the first output member 81 and the second output member 82 are not supported by the non-rotating member (that is, the case where they are supported only by the rotating member) when they are supported by the non-rotating member only at one place of L. , It is possible to increase the support rigidity of the first output member 81 and the second output member 82. That is, the load received by the first output gear 81a from the first driven gear 51a (load due to the meshing force) and the load received by the second output gear 82a from the second driven gear 52a (load due to the meshing force) can be appropriately supported. Therefore, by reducing the influence of the load on the planetary gear device 60, it becomes easy to secure the rigidity required for the planetary gear device 60, and as a result, the planetary gear device 60 can be miniaturized. It is possible.

Specifically, in the present embodiment, as shown in FIGS. 2 and 3, the first output member 81 is connected to the first carrier C1, and the second output member 82 is connected to the second carrier C2. ing. Therefore, when the support rigidity of the first output member 81 is not sufficient, the load is transmitted from the first output member 81 to the first carrier C1 due to the load received by the first output gear 81a from the first driven gear 51a. It is easy, and the rigidity required for the first carrier C1 tends to be high. If the support rigidity of the second output member 82 is not sufficient, the load is transmitted from the second output member 82 to the second carrier C2 due to the load received by the second output gear 82a from the second driven gear 52a. It is easy, and the rigidity required for the second carrier C2 tends to be high. On the other hand, in the vehicle drive device 1 of the present embodiment, since the support rigidity of the first output member 81 and the second output member 82 can be increased as described above, the load received by the first output gear 81a can be increased. Due to this, the load transmitted from the first output member 81 to the first carrier C1 is reduced, and due to the load received by the second output gear 82a, the load is transmitted from the second output member 82 to the second carrier C2. The load can be reduced. As a result, it becomes easy to secure the rigidity required for the first carrier C1 and the second carrier C2, and it is possible to reduce the size of the first planetary gear mechanism 61 and the second planetary gear mechanism 62. ..

In the present embodiment, the first output member 81 is further movably connected to the first carrier C1 in the axial direction L, and the second output member 82 is axially L relative to the second carrier C2. They are connected so that they can move relative to each other. Specifically, as shown in FIG. 2, the first carrier C1 is arranged on the first side L1 in the axial direction with respect to the first pinion gear P1 and rotatably supports the first pinion gear P1. The shape portion 68a is provided. The first annular plate-shaped portion 68a holds the end portion of the first pinion shaft 64a in the axial direction L1 that supports the first pinion gear P1 from the inside in the radial direction R via the thirteenth bearing B13. There is. Then, the first axial extending portion 65a having a cylindrical outer peripheral surface and being formed so as to extend in the axial direction L protrudes to the first side L1 in the axial direction with respect to the first annular plate-shaped portion 68a. It is connected to the first annular plate-shaped portion 68a so as to be connected. In the present embodiment, the first axial extending portion 65a is integrally formed with the first annular plate-shaped portion 68a. The first output member 81 is formed in a cylindrical shape extending in the axial direction L, is outside the radial extending portion 65a of the first axial extending portion 65a, and is the first axial extending portion in the radial R view. It is arranged so as to overlap with 65a. That is, in the present embodiment, the first output member 81 is arranged on the first side L1 in the axial direction with respect to the first planetary gear mechanism 61 (the meshing portion of the first planetary gear mechanism 61). Then, the relative rotation of the first axial extension portion 65a and the first output member 81 in the circumferential direction (circumferential direction with respect to the first axis A1) is restricted, and the relative movement in the axial direction L is allowed. In addition, the engaging portion formed on the outer peripheral surface of the extending portion 65a in the first axial direction and the engaging portion formed on the inner peripheral surface of the first output member 81 are engaged in the third connecting portion 66a (this In the embodiment, the spline is engaged). As a result, the first output member 81 is movably connected to the first carrier C1 in the axial direction L.

Further, the second carrier C2 includes a second annular plate-shaped portion 68b that is arranged on the second side L2 in the axial direction with respect to the second pinion gear P2 and rotatably supports the second pinion gear P2. The second annular plate-shaped portion 68b holds the end portion of the second pinion shaft 64b in the axial direction L2 that supports the second pinion gear P2 from the inside in the radial direction R via the 14th bearing B14. There is. Then, the second axial extending portion 65b having a cylindrical outer peripheral surface and being formed so as to extend in the axial direction L protrudes to the second side L2 in the axial direction with respect to the second annular plate-shaped portion 68b. It is connected to the second annular plate-shaped portion 68b so as to be used. In the present embodiment, the second axial extending portion 65b is integrally formed with the second annular plate-shaped portion 68b. The second output member 82 is formed in a cylindrical shape extending in the axial direction L, is outside the radial extension portion 65b in the radial direction R, and is a second axial extension portion in the radial direction R view. It is arranged so as to overlap with 65b. That is, in the present embodiment, the second output member 82 is arranged on the second side L2 in the axial direction with respect to the second planetary gear mechanism 62 (the meshing portion of the second planetary gear mechanism 62). Then, the relative rotation of the second axial extension portion 65b and the second output member 82 in the circumferential direction (circumferential direction with respect to the first axis A1) is restricted, and the relative movement in the axial direction L is allowed. In addition, the engaging portion formed on the outer peripheral surface of the second axial extending portion 65b and the engaging portion formed on the inner peripheral surface of the second output member 82 are engaged in the fourth connecting portion 66b (this In the embodiment, the spline is engaged). As a result, the second output member 82 is movably connected to the second carrier C2 in the axial direction L.

As described above, in the present embodiment, the first output member 81 is connected so as to be movable relative to the first carrier C1 in the axial direction L, and the second output member 82 is axially movable with respect to the second carrier C2. It is connected to L so as to be relatively movable. Therefore, the load at the connecting portion (third connecting portion 66a) between the first output member 81 and the first carrier C1 is compared with the case where the first output member 81 and the first carrier C1 cannot move relative to each other in the axial direction L. The second output member 82 and the second carrier C2 cannot move relative to each other in the axial direction L, as compared with the case where the second output member 82 and the second carrier C2 cannot move relative to each other. It is possible to reduce the transmission of the load at the fourth connecting portion 66b). As a result, the load transmitted from the first output member 81 to the first carrier C1 due to the first output gear 81a receiving the load due to the meshing force from the first driven gear 51a is reduced, and the second output gear 82a is reduced. It is possible to further reduce the load transmitted from the second output member 82 to the second carrier C2 due to the load received from the second driven gear 52a due to the meshing force.

By the way, as described above, the first output member 81 is rotatably supported via the sixth bearing B6, and the second output member 82 is rotatably supported via the seventh bearing B7. Then, as described below, in the present embodiment, the first carrier C1 has a first oil passage 91 for supplying oil to the thirteenth bearing B13 and a second oil passage 91 for supplying oil to the sixth bearing B6. An oil passage 92 is formed, and the second carrier C2 has a third oil passage 93 for supplying oil to the 14th bearing B14 and a fourth oil passage 94 for supplying oil to the 7th bearing B7. It is formed.

As shown in FIG. 2, in the present embodiment, the first oil passage 91 and the second oil passage 92 are formed in the first annular plate-shaped portion 68a. The first oil passage 91 is formed so as to extend in the radial direction R, and the outer end portion of the first oil passage 91 in the radial direction R is oiled on a thirteenth bearing B13 formed on the first pinion shaft 64a. Is connected to the oil channel to supply. As a result, the oil supplied to the first oil passage 91 can be supplied to the thirteenth bearing B13 to lubricate the thirteenth bearing B13. The second oil passage 92 is formed so as to extend in the radial direction R, and the outer end portion of the second oil passage 92 in the radial direction R is relative to the sixth bearing B6 in the first annular plate-shaped portion 68a. It is open at a portion adjacent to the second side L2 in the axial direction. As a result, the oil supplied to the second oil passage 92 can be supplied to the sixth bearing B6 to lubricate the sixth bearing B6.

Further, in the present embodiment, the third oil passage 93 and the fourth oil passage 94 are formed in the second annular plate-shaped portion 68b. The third oil passage 93 is formed so as to extend in the radial direction R, and the outer end portion of the third oil passage 93 in the radial direction R is oiled on the 14th bearing B14 formed on the second pinion shaft 64b. Is connected to the oil channel to supply. As a result, the oil supplied to the third oil passage 93 can be supplied to the 14th bearing B14 to lubricate the 14th bearing B14. The fourth oil passage 94 is formed so as to extend in the radial direction R, and the outer end portion of the fourth oil passage 94 in the radial direction R is relative to the seventh bearing B7 in the second annular plate-shaped portion 68b. It is open at a portion adjacent to the first side L1 in the axial direction. As a result, the oil supplied to the fourth oil passage 94 can be supplied to the seventh bearing B7 to lubricate the seventh bearing B7.

As shown briefly in FIG. 2, the vehicle drive device 1 includes a hydraulic source 5, and the oil discharged from the hydraulic source 5 is discharged from the first oil passage 91, the second oil passage 92, and the third oil passage. It is configured to be supplied to each of 93 and the fourth oil passage 94. The hydraulic source 5 is, for example, an electric oil pump driven by an electric motor, or a machine driven by power transmitted through a power transmission path between the rotary electric machines (11, 12) and the wheels (W1, W2). It can be a type oil pump. As shown in FIG. 2, a third axial extending portion 65c formed so as to extend in the axial direction L is arranged inside the first sun gear S1 and the second sun gear S2 in the radial direction R. The third axial extending portion 65c is connected to the second annular plate-shaped portion 68b so as to project from the second annular plate-shaped portion 68b to the first side L1 in the axial direction. In the present embodiment, the third axial extending portion 65c is integrally formed with the second annular plate-shaped portion 68b and the second axial extending portion 65b. Then, the central portion of the second axial extending portion 65b in the radial direction R, the central portion of the second annular plate-shaped portion 68b in the radial direction R, and the central portion of the third axial extending portion 65c in the radial direction R. The in-shaft oil passage 95 is formed so as to extend continuously in the axial direction L. The oil discharged from the hydraulic source 5 is supplied to each of the above-mentioned oil passages (91 to 94) via the in-shaft oil passage 95.

Specifically, the end portion of the axial first side L1 in the third axial extending portion 65c is inserted into the hole portion 69 formed in the central portion of the first annular plate-shaped portion 68a in the radial direction R. The inner peripheral surface of the third axial extension portion 65c (the surface that partitions the outer side of the in-axis oil passage 95 in the radial direction R) is inserted into the hole portion 69 of the third axial extension portion 65c. ) And the outer peripheral surface are formed with an oil hole 96. Further, each of the first oil passage 91 and the second oil passage 92 is formed so as to open to the inner peripheral surface of the hole portion 69. As a result, the oil supplied from the hydraulic source 5 to the in-shaft oil passage 95 is supplied to the first oil passage 91 and the second oil passage 92 via the oil holes 96 by the action of centrifugal force or the like. In this way, by forming both the first oil passage 91 and the second oil passage 92 in the first carrier C1 (here, the first annular plate-shaped portion 68a), the first oil passage 91 and the second oil It is possible to simplify the oil channel configuration by standardizing the oil supply structure for the road 92.

Since both the first oil passage 91 and the second oil passage 92 are formed in the first annular plate-shaped portion 68a, the first oil passage 91 and the second oil passage 92 are positioned and peripherally aligned in the axial direction L. It is preferable that at least one of the positions in the direction (circumferential direction with respect to the first axis A1) is displaced from each other. As shown in FIG. 2, in the present embodiment, the first oil passage 91 is formed so as to extend parallel to the radial direction R, and the second oil passage 92 is inclined in the radial direction R (diameter direction). By forming so as to extend in the direction toward the first side L1 in the axial direction toward the outside of R), the position of the axial L is shifted between the first oil passage 91 and the second oil passage 92. .. In the example shown in FIG. 2, the positions of the first oil passage 91 and the second oil passage 92 in the axial direction L are set so that the first oil passage 91 and the second oil passage 92 do not have any portion arranged at the same position in the axial direction L. They are out of alignment with each other. Further, in the present embodiment, the first oil passage 91 and the second oil passage 92 are formed so as to be displaced from each other in the circumferential direction (circumferential direction with respect to the first axis A1). For convenience, both the first oil passage 91 and the second oil passage 92 are shown in the same cross section.

Further, each of the third oil passage 93 and the fourth oil passage 94 is opened on the inner peripheral surface of the second annular plate-shaped portion 68b (the surface that partitions the outer side of the in-shaft oil passage 95 in the radial direction R). Is formed in. Therefore, the oil supplied from the hydraulic source 5 to the in-shaft oil passage 95 is supplied to the third oil passage 93 and the fourth oil passage 94 by the action of centrifugal force or the like. In this way, by forming both the third oil passage 93 and the fourth oil passage 94 in the second carrier C2 (here, the second annular plate-shaped portion 68b), the third oil passage 93 and the fourth oil can be used. It is possible to simplify the oil channel configuration by standardizing the oil supply structure for the road 94.

Since both the third oil passage 93 and the fourth oil passage 94 are formed in the second annular plate-shaped portion 68b, the third oil passage 93 and the fourth oil passage 94 are positioned and peripherally aligned in the axial direction L. It is preferable to form at least one of the positions in the direction (circumferential direction with respect to the first axis A1) by shifting them from each other. As shown in FIG. 2, in the present embodiment, the third oil passage 93 is formed so as to extend parallel to the radial direction R, and the fourth oil passage 94 is inclined in the radial direction R (diameter direction). By forming so as to extend in the direction toward the second side L2 in the axial direction toward the outside of R), the position of the axial L is shifted between the third oil passage 93 and the fourth oil passage 94. .. In the example shown in FIG. 2, the third oil passage 93 and the fourth oil passage 94 are opened on the inner peripheral surface of the second annular plate-shaped portion 68b at the same position in the axial direction L. That is, the third oil passage 93 and the fourth oil passage 94 have a part that is arranged at the same position in the axial direction L, but the positions in the axial direction L are deviated from each other. Further, in the present embodiment, the third oil passage 93 and the fourth oil passage 94 are formed so as to be displaced from each other in the circumferential direction (circumferential direction with respect to the first axis A1). For convenience, both the third oil passage 93 and the fourth oil passage 94 are shown in the same cross section.

Next, the support structure of the first input member 71 and the second input member 72 in the vehicle drive device 1 of the present embodiment will be described.

The first input member 71 and the second input member 72 are rotatably supported by the case 3 or the support member 40. Specifically, each of the first input member 71 and the second input member 72 is rotatably supported by the case 3 or the support member 40 at two locations in the axial direction L.

As shown in FIG. 2, in the present embodiment, the first input member 71 is rotatably supported at two positions in the axial direction L by the case 3 and the first support member 41. Specifically, the first input member 71 is formed in the fifth case portion 35 by the thirteenth support portion 35a and the ninth support portion 41c formed in the first support member 41. It is rotatably supported in several places. The ninth support portion 41c is arranged on the first side L1 in the axial direction with respect to the thirteenth support portion 35a.

The first input member 71 is supported from the outside in the radial direction R by the thirteenth support portion 35a. Specifically, the tenth bearing B10 (here, a radial type ball bearing) is arranged between the inner peripheral surface of the thirteenth support portion 35a and the outer peripheral surface of the first input member 71, and the first input. The member 71 is supported from the outside in the radial direction R by the thirteenth support portion 35a via the tenth bearing B10. In the present embodiment, the first input member 71 includes a first ring gear R1. The first ring gear R1 is the inner circumference of the portion of the first input member 71 that is inside the radial direction R of the tenth bearing B10 and is arranged so as to overlap the tenth bearing B10 in the radial direction R. It is formed on the surface. That is, the tenth bearing B10 is arranged so as to overlap the first ring gear R1 in the radial R view. Further, the first input member 71 is supported from the inside in the radial direction R by the ninth support portion 41c. Specifically, the ninth bearing B9 (here, a radial type ball bearing) is arranged between the outer peripheral surface of the ninth support portion 41c and the inner peripheral surface of the first input member 71, and the first input The member 71 is supported from the inside in the radial direction R by the ninth support portion 41c via the ninth bearing B9. The first input gear 71a is located on the outer peripheral surface of the portion of the first input member 71 that is outside the ninth bearing B9 in the radial direction R and is arranged so as to overlap the ninth bearing B9 in the radial direction R. It is formed. That is, the ninth bearing B9 is arranged so as to overlap the first input gear 71a in the radial R view. Further, the ninth bearing B9 is arranged so as to overlap the sixth bearing B6 in the radial R view.

As shown in FIG. 2, in the present embodiment, the second input member 72 is rotatably supported at two positions in the axial direction L by the case 3 and the second support member 42. Specifically, the second input member 72 is formed in the fifth case portion 35 by the 14th support portion 35b and the tenth support portion 42c formed in the second support member 42, so that the second input member 72 is 2 in the axial direction L. It is rotatably supported in several places. The tenth support portion 42c is arranged on the second side L2 in the axial direction with respect to the fourteenth support portion 35b.

The second input member 72 is supported from the outside in the radial direction R by the 14th support portion 35b. Specifically, the eleventh bearing B11 (here, a radial type ball bearing) is arranged between the inner peripheral surface of the 14th support portion 35b and the outer peripheral surface of the second input member 72, and the second input The member 72 is supported from the outside in the radial direction R by the 14th support portion 35b via the 11th bearing B11. In the present embodiment, the second input member 72 includes a second ring gear R2. The second ring gear R2 is the inner circumference of the portion of the second input member 72 that is inside the radial direction R of the 11th bearing B11 and is arranged so as to overlap the 11th bearing B11 in the radial direction R. It is formed on the surface. That is, the eleventh bearing B11 is arranged so as to overlap the second ring gear R2 in the radial R view. Further, the second input member 72 is supported from the inside in the radial direction R by the tenth support portion 42c. Specifically, a twelfth bearing B12 (here, a radial type ball bearing) is arranged between the outer peripheral surface of the tenth support portion 42c and the inner peripheral surface of the second input member 72, and the second input The member 72 is supported from the inside in the radial direction R by the tenth support portion 42c via the twelfth bearing B12. The second input gear 72a is provided on the outer peripheral surface of the portion of the second input member 72 that is outside the 12th bearing B12 in the radial direction R and is arranged so as to overlap the 12th bearing B12 in the radial direction R. It is formed. That is, the twelfth bearing B12 is arranged so as to overlap the second input gear 72a in the radial R view. Further, the 12th bearing B12 is arranged so as to overlap the 7th bearing B7 in the radial R view.

As described above, the first input member 71 and the second input member 72 are rotatably supported in the radial direction R at two locations in the axial direction L by the case 3 or the support member 40. Therefore, both the first input member 71 and the second input member 72 can be supported by the non-rotating member at each of the two positions in the axial direction L, and the first input member 71 and the second input member 72 are in the axial direction. Compared to the case where the first input member 71 and the second input member 72 are not supported by the non-rotating member (that is, the case where they are supported only by the rotating member) when they are supported by the non-rotating member only at one place of L. , It is possible to increase the support rigidity of the first input member 71 and the second input member 72. That is, the load received by the first input gear 71a from the first drive gear 21a (load due to the meshing force) and the load received by the second input gear 72a from the second drive gear 22a (load due to the meshing force) can be appropriately supported. Therefore, by reducing the influence of the load on the planetary gear device 60, it becomes easy to secure the rigidity required for the planetary gear device 60, and as a result, the planetary gear device 60 can be miniaturized. It is possible.

Specifically, in the present embodiment, as shown in FIGS. 2 and 3, the first input member 71 includes the first ring gear R1, and the second input member 72 includes the second ring gear R2. .. Therefore, when the support rigidity of the first input member 71 is not sufficient, the first input member 71 via the first ring gear R1 from the first input member 71 due to the load received by the first input gear 71a from the first drive gear 21a. The load is easily transmitted to the carrier C1, and the rigidity required for the first carrier C1 tends to be high. If the support rigidity of the second input member 72 is not sufficient, the second input gear 72a is second from the second input member 72 via the second ring gear R2 due to the load received from the second drive gear 22a. The load is easily transmitted to the carrier C2, and the rigidity required for the second carrier C2 tends to be high. On the other hand, in the vehicle drive device 1 of the present embodiment, since the support rigidity of the first input member 71 and the second input member 72 can be increased as described above, the load received by the first input gear 71a is applied. Due to this, the load transmitted from the first input member 71 to the first carrier C1 is reduced, and due to the load received by the second input gear 72a, the load is transmitted from the second input member 72 to the second carrier C2. The load can be reduced. As a result, it becomes easy to secure the rigidity required for the first carrier C1 and the second carrier C2, and it is possible to reduce the size of the first planetary gear mechanism 61 and the second planetary gear mechanism 62. ..

Next, the support structure of the first drive member 21 and the second drive member 22 in the vehicle drive device 1 of the present embodiment will be described. The radial direction in the following description of the support structure of the first drive member 21 and the second drive member 22 is the radial direction with respect to the third axis A3, unless otherwise specified.

The first drive member 21 and the second drive member 22 are rotatably supported by the case 3 or the support member 40. Specifically, each of the first drive member 21 and the second drive member 22 is rotatably supported at two locations in the axial direction L by the case 3 or the support member 40.

As shown in FIGS. 1 and 2, in the present embodiment, the first driving member 21 is rotatably supported at two positions in the axial direction L by the case 3 and the first supporting member 41. Specifically, the first drive member 21 is formed in the fifth case portion 35 by the fifteenth support portion 35c and the eleventh support portion 41d formed in the first support member 41. It is rotatably supported in several places. The eleventh support portion 41d is arranged on the first side L1 in the axial direction with respect to the fifteenth support portion 35c.

The first driving member 21 is supported from the outside in the radial direction by the fifteenth supporting portion 35c. Specifically, the 16th bearing B16 (here, a radial type ball bearing) is arranged between the inner peripheral surface of the 15th support portion 35c and the outer peripheral surface of the first driving member 21, and the first driving The member 21 is supported from the outside in the radial direction by the 15th support portion 35c via the 16th bearing B16. The 16th bearing B16 is arranged so as to overlap the 10th bearing B10 in the radial direction (that is, the radial direction R view) with respect to the first axis A1. Further, the first driving member 21 is supported from the outside in the radial direction by the eleventh supporting portion 41d. Specifically, the 15th bearing B15 (here, a radial type ball bearing) is arranged between the inner peripheral surface of the 11th support portion 41d and the outer peripheral surface of the 1st drive member 21, and the 1st drive The member 21 is supported from the outside in the radial direction by the eleventh support portion 41d via the fifteenth bearing B15. The fifteenth bearing B15 is arranged so as to overlap the second bearing B2 in a radial direction with respect to the second axis A2. The first drive gear 21a is formed on the outer peripheral surface of a portion of the first drive member 21 arranged between the 15th bearing B15 and the 16th bearing B16 in the axial direction L.

As shown in FIGS. 1 and 2, in the present embodiment, the second driving member 22 is rotatably supported at two positions in the axial direction L by the case 3 and the second supporting member 42. Specifically, the second drive member 22 is formed in the fifth case portion 35 by the 16th support portion 35d and the 12th support portion 42d formed in the second support member 42, so that the second drive member 22 is 2 in the axial direction L. It is rotatably supported in several places. The 12th support portion 42d is arranged on the second side L2 in the axial direction with respect to the 16th support portion 35d.

The second driving member 22 is supported from the outside in the radial direction by the 16th support portion 35d. Specifically, the 17th bearing B17 (here, a radial type ball bearing) is arranged between the inner peripheral surface of the 16th support portion 35d and the outer peripheral surface of the 2nd drive member 22, and the 2nd drive The member 22 is supported from the outside in the radial direction by the 16th support portion 35d via the 17th bearing B17. The 17th bearing B17 is arranged so as to overlap the 11th bearing B11 in the radial direction (that is, the radial direction R view) with respect to the first axis A1. Further, the second driving member 22 is supported from the outside in the radial direction by the twelfth supporting portion 42d. Specifically, the 18th bearing B18 (here, a radial type ball bearing) is arranged between the inner peripheral surface of the 12th support portion 42d and the outer peripheral surface of the 2nd drive member 22, and the 2nd drive The member 22 is supported from the outside in the radial direction by the 12th support portion 42d via the 18th bearing B18. The 18th bearing B18 is arranged so as to overlap the 3rd bearing B3 in a radial direction with respect to the 2nd axis A2. The second drive gear 22a is formed on the outer peripheral surface of the portion of the second drive member 22 that is arranged between the 17th bearing B17 and the 18th bearing B18 in the axial direction L.

As described above, in the present embodiment, the first support member 41 is used to support the first input member 71 and the first output member 81, and further, the first connecting member 51 and the first driving member 21 are provided. It is also used to support. That is, the first support member 41 is formed with a support portion (9th support portion 41c) of the first input member 71 and a support portion (7th support portion 41b) of the first output member 81. A support portion (fifth support portion 41a) of the 1 connecting member 51 and a support portion (11th support portion 41d) of the first drive member 21 are formed. Further, in the present embodiment, the second support member 42 is used to support the second input member 72 and the second output member 82, and further supports the second connecting member 52 and the second driving member 22. It is also used in. That is, the second support member 42 is formed with a support portion (10th support portion 42c) of the second input member 72 and a support portion (8th support portion 42b) of the second output member 82. A support portion (sixth support portion 42a) of the two connecting members 52 and a support portion (12th support portion 42d) of the second drive member 22 are formed. In this way, by using the first support member 41 and the second support member 42 to support a plurality of rotating members, the number of parts can be suppressed to a small number, and the support accuracy of each rotating member (the same support member 40). It becomes easy to secure the accuracy of the relative position between the rotating members supported by the above.

In the present embodiment, each of the first input member 71, the second input member 72, the first output member 81, and the second output member 82 is rotatably supported by the case 3 or the support member 40. Therefore, the first rotating element E1 connected to the first input member 71, the fourth rotating element E4 connected to the second input member 72, the second rotating element E2 connected to the first output member 81, and the second It is possible to appropriately secure the support accuracy of each of the third rotating elements E3 connected to the two output members 82. On top of that, in the present embodiment, the connecting portion 63 between the rotating element of the first planetary gear mechanism 61 and the rotating element of the second planetary gear mechanism 62 has a connecting structure having a gap in the radial direction R. As a result, it is possible for the connecting portion 63 to absorb dimensional errors and assembly errors in the radial direction R of each component, and an excessive load is applied to the gear meshing portions of the first planetary gear mechanism 61 and the second planetary gear mechanism 62. It is possible to avoid the action of (uneven load, etc.).

Specifically, in the present embodiment, the first carrier C1 and the second sun gear S2 are connected so as to rotate integrally, and the first sun gear S1 and the second carrier C2 rotate integrally. It is connected like this. Then, the diameter of the second connecting portion 63b, which is the connecting portion 63 between the first carrier C1 and the second sun gear S2, and the first connecting portion 63a, which is the connecting portion 63 between the first sun gear S1 and the second carrier C2, is formed. It has a connecting structure with a gap in the direction R.

As shown in FIG. 2, the first carrier C1 includes a third annular plate-shaped portion 68c that is arranged on the second side L2 in the axial direction with respect to the first pinion gear P1 and rotatably supports the first pinion gear P1. ing. A cylindrical third tubular portion 67c extending in the axial direction L is connected to the inner end of the third annular plate-shaped portion 68c in the radial direction R. Here, the third tubular portion 67c is integrally formed with the third annular plate-shaped portion 68c. Further, a second cylindrical portion 67b formed in a cylindrical shape extending in the axial direction L is connected to the second sun gear S2 so as to project from the second sun gear S2 on the first side L1 in the axial direction. .. Here, the second tubular portion 67b is integrally formed with a cylindrical member on which the second sun gear S2 is formed on the outer peripheral surface. The outer peripheral surface of the second tubular portion 67b is formed to have a smaller diameter than the inner peripheral surface of the third tubular portion 67c. Then, the relative rotation of the second tubular portion 67b and the third tubular portion 67c in the circumferential direction (circumferential direction with respect to the first axis A1) is restricted, and the relative movement in the axial direction L is allowed. , The engaging portion formed on the outer peripheral surface of the second tubular portion 67b and the engaging portion formed on the inner peripheral surface of the third tubular portion 67c are engaged in the second connecting portion 63b (the present embodiment). Then, spline engagement). The second connecting portion 63b is formed with a gap in the radial direction R that enables relative movement of at least the second tubular portion 67b and the third tubular portion 67c in the axial direction L.

Further, as shown in FIG. 2, the first sun gear S1 is formed on the outer peripheral surface of the first tubular portion 67a formed in a tubular shape extending in the axial direction L. The inner peripheral surface of the first tubular portion 67a is formed to have a diameter larger than the outer peripheral surface of the extending portion 65c in the third axial direction. Then, the relative rotation of the first tubular portion 67a and the third axial extending portion 65c in the circumferential direction (circumferential direction with respect to the first axis A1) is restricted, and the relative movement in the axial direction L is allowed. As described above, the engaging portion formed on the inner peripheral surface of the first tubular portion 67a and the engaging portion formed on the outer peripheral surface of the third axial extending portion 65c are engaged in the first connecting portion 63a. (In this embodiment, the spline is engaged). The first connecting portion 63a is formed with a gap in the radial direction R that enables relative movement of at least the first tubular portion 67a and the third axial extending portion 65c in the axial direction L.

[Other Embodiments]
Next, other embodiments of the vehicle drive device will be described.

(1) In the above embodiment, the first carrier C1 and the second sun gear S2 are connected, and the first sun gear S1 and the second carrier C2 are connected to connect the first planetary gear mechanism 61 and the second sun gear S2. An example has been described in which the two planetary gear mechanisms 62 are provided with four rotating elements (E1 to E4) as a whole and integrally perform differential operation. However, the first planet is not limited to such a configuration, for example, by connecting the first carrier C1 and the second ring gear R2 and connecting the first ring gear R1 and the second carrier C2. The gear mechanism 61 and the second planetary gear mechanism 62 may be provided with four rotating elements (E1 to E4) as a whole to integrally perform differential operation. In this case, the first rotary electric machine 11 is driven and connected to the first sun gear S1, the first connecting member 51 is driven and connected to the first carrier C1 and the second ring gear R2 that rotate integrally, and the second connecting member 52 is integrated. By driving and connecting the first ring gear R1 and the second carrier C2 that rotate in a driven manner and driving and connecting the second rotating electric machine 12 to the second sun gear S2, the rotation speed can be increased as in the above embodiment. The order is the first rotating element E1 driven and connected to the first rotating electric machine 11, the second rotating element E2 driven and connected to the first connecting member 51, and the third rotating element E3 driven and connected to the second connecting member 52. , And the configuration in which the fourth rotating element E4 is driven and connected to the second rotating electric machine 12 can be realized.

(2) In the above embodiment, a configuration in which both the first planetary gear mechanism 61 and the second planetary gear mechanism 62 are single pinion type planetary gear mechanisms has been described as an example. However, without being limited to such a configuration, for example, both the first planetary gear mechanism 61 and the second planetary gear mechanism 62 may be configured to be a double pinion type planetary gear mechanism. In this case, the first carrier C1 and the second ring gear R2 are connected, and the first ring gear R1 and the second carrier C2 are connected, so that the first planetary gear mechanism 61 and the second planetary gear mechanism 62 are connected. As a whole, four rotating elements (E1 to E4) can be provided to integrally perform differential operation. In this case, the first rotary electric machine 11 is driven and connected to the first sun gear S1, the first connecting member 51 is driven and connected to the first ring gear R1 and the second carrier C2 that rotate integrally, and the second connecting member 52 is integrated. By driving and connecting the first carrier C1 and the second ring gear R2 that rotate in a driven manner and driving and connecting the second rotating electric machine 12 to the second sun gear S2, the rotation speed can be increased as in the above embodiment. The order is the first rotating element E1 that is driven and connected to the first rotating electric machine 11, the second rotating element E2 that is driven and connected to the first connecting member 51, and the third rotating element E3 that is driven and connected to the second connecting member 52. , And the configuration in which the fourth rotating element E4 is driven and connected to the second rotating electric machine 12 can be realized.

(3) In the above embodiment, the transmission device 2 transmits the torque of the first rotary electric machine 11 to both the first connecting member 51 and the second connecting member 52, and transfers the torque of the second rotary electric machine 12 to the first. The configuration of transmitting to both the connecting member 51 and the second connecting member 52 has been described as an example. However, without being limited to such a configuration, the transmission device 2 transmits the torque of the first rotary electric machine 11 only to the first connecting member 51 among the first connecting member 51 and the second connecting member 52. The torque of the second rotary electric machine 12 may be transmitted only to the second connecting member 52 of the first connecting member 51 and the second connecting member 52. That is, the power transmission path between the first rotary electric machine 11 and the first connecting member 51 and the power transmission path between the second rotary electric machine 12 and the second connecting member 52 may be separated. ..

For example, the first planetary gear mechanism 61 and the second planetary gear mechanism 62 operate independently of each other without connecting the first planetary gear mechanism 61 and the second planetary gear mechanism 62 as in the above embodiment. The power transmission path between the first rotary electric machine 11 and the first connecting member 51 and the power transmission path between the second rotary electric machine 12 and the second connecting member 52 are separated by the configuration. The configuration can be realized. In this case, the first planetary gear mechanism 61 includes a first rotating element E1 that is driven and connected to the first rotating electric machine 11, a second rotating element E2 that is driven and connected to the first connecting member 51, and a fifth rotating element. The second planetary gear mechanism 62 includes a third rotating element E3 that is driven and connected to the second connecting member 52, a fourth rotating element E4 that is driven and connected to the second rotating electric machine 12, and a sixth rotating element. And. That is, the differential gear device 6 (planetary gear device 60) has six rotating elements as a whole. In this case, for example, the fifth rotating element may be fixed to the non-rotating member, and the sixth rotating element may be fixed to the non-rotating member.

(4) In the above embodiment, a configuration in which each of the first output member 81 and the second output member 82 is rotatably supported by the case 3 or the support member 40 at two locations in the axial direction L will be described as an example. did. However, without being limited to such a configuration, one or both of the first output member 81 and the second output member 82 are rotatably supported by the case 3 or the support member 40 only at one position in the axial direction L. Or a configuration in which one or both of the first output member 81 and the second output member 82 are not supported by either the case 3 or the support member 40 (that is, a configuration in which only the rotating member is rotatably supported). You can also do it.

(5) In the above embodiment, a configuration in which each of the first input member 71 and the second input member 72 is rotatably supported by the case 3 or the support member 40 at two locations in the axial direction L will be described as an example. did. However, without being limited to such a configuration, one or both of the first input member 71 and the second input member 72 are rotatably supported by the case 3 or the support member 40 only at one position in the axial direction L. Or a configuration in which one or both of the first input member 71 and the second input member 72 are not supported by either the case 3 or the support member 40 (that is, a configuration in which only the rotating member is rotatably supported). You can also do it.

(6) In the above embodiment, a configuration in which the case 3 includes the fifth case portion 35 and the first case portion 31 and the second case portion 32 are joined via the fifth case portion 35 has been described as an example. .. However, without being limited to such a configuration, the case 3 does not include the fifth case portion 35, and the first case portion 31 and the second case portion 32 are joined without passing through the fifth case portion 35. It is also possible to have a configuration (that is, a configuration in which the seal member 4 is joined only through the seal member 4). In this case, for example, a support member 40 having the same support function of the rotating member as the fifth case portion 35 may be provided instead of the fifth case portion 35.

(7) In the above embodiment, the first oil passage 91 and the second oil passage 92 are formed in the first carrier C1, and the third oil passage 93 and the fourth oil passage 94 are formed in the second carrier C2. The configuration was described as an example. However, the configuration is not limited to such a configuration, and for example, the second oil passage 92 may not be formed in the first carrier C1 and the fourth oil passage 94 may not be formed in the second carrier C2.

(8) In the above embodiment, the ninth bearing B9 is arranged so as to overlap the sixth bearing B6 in the radial R view, and the twelfth bearing B12 overlaps the seventh bearing B7 in the radial R view. The configuration in which they are arranged is described as an example. However, without being limited to such a configuration, the ninth bearing B9 is axially the first side L1 or the axial direction with respect to the sixth bearing B6 so that the ninth bearing B9 does not overlap with the sixth bearing B6 in the radial R view. Axial first side L1 or axial second with respect to the seventh bearing B7 so that the configuration arranged on the second side L2 and the twelfth bearing B12 do not overlap with the seventh bearing B7 in the radial R view. It can also be configured to be arranged on the side L2.

(9) In the above embodiment, the first support member 41 is formed with the fifth support portion 41a, the seventh support portion 41b, the ninth support portion 41c, and the eleventh support portion 41d, and the second support portion 41d is formed. The configuration in which the sixth support portion 42a, the eighth support portion 42b, the tenth support portion 42c, and the twelfth support portion 42d are formed on the member 42 has been described as an example. However, without being limited to such a configuration, only a part of the fifth support portion 41a, the seventh support portion 41b, the ninth support portion 41c, and the eleventh support portion 41d is formed on the first support member 41. The remaining support portion may be formed on the other support member 40 or the case 3. Further, only a part of the sixth support portion 42a, the eighth support portion 42b, the tenth support portion 42c, and the twelfth support portion 42d is formed on the second support member 42, and the remaining support portion is the other support member 40. Alternatively, the configuration may be formed in the case 3.

(10) In the above embodiment, the first output member 81 is connected so as to be movable relative to the first carrier C1 in the axial direction L, and the second output member 82 is axially movable with respect to the second carrier C2. The configuration which is connected to L so as to be relatively movable has been described as an example. However, without being limited to such a configuration, the first output member 81 is formed integrally with the first carrier C1 and the like, so that the first output member 81 cannot move relative to the first carrier C1 in the axial direction L. It can also be configured to be connected. Further, the second output member 82 may be integrally formed with the second carrier C2 so as to be integrally immovably connected to the second carrier C2 in the axial direction L.

(11) In the above embodiment, the first output member 81 is arranged on the first side L1 in the axial direction with respect to the first planetary gear mechanism 61 (the meshing portion of the first planetary gear mechanism 61), and the second output member The configuration in which the 82 is arranged on the second side L2 in the axial direction with respect to the second planetary gear mechanism 62 (the meshing portion of the second planetary gear mechanism 62) has been described as an example. However, without being limited to such a configuration, the first output member 81 is arranged on the second side L2 in the axial direction with respect to the first planetary gear mechanism 61 (the meshing portion of the first planetary gear mechanism 61). The second output member 82 may be arranged on the first side L1 in the axial direction with respect to the second planetary gear mechanism 62 (the meshing portion of the second planetary gear mechanism 62).

(12) In the above embodiment, the configuration in which the first drive gear 21a meshes with the first input gear 71a and the second drive gear 22a meshes with the second input gear 72a has been described as an example. However, without being limited to such a configuration, the first drive gear 21a and the first input gear 71a are connected via another gear or a gear mechanism, and the second drive gear 22a and the second input gear 72a Can also be configured to be connected via another gear or gear mechanism.

(13) In the above embodiment, the configuration in which the first output gear 81a meshes with the first driven gear 51a and the second output gear 82a meshes with the second driven gear 52a has been described as an example. However, without being limited to such a configuration, the first output gear 81a and the first driven gear 51a are connected via another gear or a gear mechanism, and the second output gear 82a and the second driven gear 52a Can also be configured to be connected via another gear or gear mechanism.

(14) In the above embodiment, the first connecting member 51 is connected so as to rotate integrally with the first wheel W1, and the second connecting member 52 is connected so as to rotate integrally with the second wheel W2. The configuration was described as an example. However, without being limited to such a configuration, the first connecting member 51 is arranged coaxially with the first shaft member 53 and is attached to the first wheel W1 via a gear mechanism (for example, a differential gear mechanism). The second connecting member 52 may be connected and arranged coaxially with the second shaft member 54 and connected to the second wheel W2 via a gear mechanism (for example, a differential gear mechanism). It is also possible that the first connecting member 51 is arranged on a different axis from the first shaft member 53, and the second connecting member 52 is arranged on a different axis from the second shaft member 54.

(15) In the above embodiment, the first connecting member 51 is rotatably supported at two positions in the axial direction L by the first support portion 31a formed in the case 3 and the first support member 41. The configuration in which the second connecting member 52 is rotatably supported at two positions in the axial direction L by the second supporting portion 32a formed in the case 3 and the second supporting member 42 has been described as an example. However, without being limited to such a configuration, for example, the first connecting member 51 is rotatably supported by the case 3 at each of the two positions in the axial direction L, and the second connecting member 52 is supported in the axial direction L. It is also possible to rotatably support the case 3 at each of the two locations.

(16) In the above embodiment, the configuration in which the first rotary electric machine 11 and the second rotary electric machine 12 are arranged on the third axis A3 has been described as an example. However, the configuration is not limited to such a configuration, and one or both of the first rotary electric machine 11 and the second rotary electric machine 12 is arranged on the first axis A1 or on the second axis A2. You can also. Further, in the above embodiment, the configuration in which the first connecting member 51 and the second connecting member 52 are arranged on the second axis A2 has been described as an example. However, without being limited to such a configuration, the first connecting member 51 and the second connecting member 52 may be arranged on the first axis A1 or on the third axis A3.

(17) The configurations disclosed in each of the above-described embodiments shall be applied in combination with the configurations disclosed in other embodiments as long as there is no contradiction between the embodiments described as the other embodiments. (Including combinations) is also possible. With respect to other configurations, the embodiments disclosed herein are merely exemplary in all respects. Therefore, various modifications can be made as appropriate without departing from the gist of the present disclosure.

[Outline of the above-described embodiment]
Hereinafter, the outline of the vehicle drive device described above will be described.

The first rotary electric machine (11), the second rotary electric machine (12), the first connecting member (51) which is driven and connected to the first wheel (W1), and the second wheel (W2) which is driven and connected. The torque of the two connecting members (52) and the first rotary electric machine (11) is transmitted to at least the first connecting member (51) of the first connecting member (51) and the second connecting member (52). At the same time, the transmission device (2) that transmits the torque of the second rotary electric machine (12) to at least the second connecting member (52) of the first connecting member (51) and the second connecting member (52). ), The first rotary electric machine (11), the second rotary electric machine (12), the first connecting member (51), the second connecting member (52), and the transmission device (2). (3), the transmission device (2) is arranged on the first shaft (A1), and the first connecting member (51) and the second connecting member (52) are the first shaft. The transmission device (2) is arranged on a second axis (A2) parallel to (A1), and the transmission device (2) is a first rotating element (E1) driven and connected to the first rotating electric machine (11), and the first connection. Driven by a second rotating element (E2) that is driven and connected to a member (51), a third rotating element (E3) that is driven and connected to the second connecting member (52), and a second rotating electric machine (12). A planetary gear device (60) having at least a fourth rotating element (E4) to be connected, a first input member (71) connected to the first rotating element (E1), and the second rotating element (E2). A first output member (81) connected to, a second output member (82) connected to the third rotating element (E3), and a second input member connected to the fourth rotating element (E4). The first output member (81) includes the first output gear (81a) that meshes with the first driven gear (51a) included in the first connecting member (51). The output member (82) includes a second output gear (82a) that meshes with a second driven gear (52a) included in the second connecting member (52), and the first output member (81) and the second output member. Each of (82) is rotatably supported at two points in the axial direction (L) by the case (3) or the support member (40) fixed to the case (3).

According to this configuration, the first output member (81) connected to the second rotating element (E2) of the planetary gear device (60) is fixed to the case (3) or the case (3), and the support member (40). ), It is rotatably supported at two points in the axial direction (L). That is, since the first output member (81) can be supported by the non-rotating member at each of the two positions in the axial direction (L), the first output member (81) is supported at one place in the axial direction (L). The support rigidity of the first output member (81) can be increased as compared with the case where only the first output member (81) is supported by the non-rotating member or the first output member (81) is not supported by the non-rotating member. Therefore, the load received by the first output gear (81a) from the first driven gear (51a) can be appropriately supported, and the influence of the load on the planetary gear device (60) can be reduced. Similarly, the second output member (82) connected to the third rotating element (E3) of the planetary gear device (60) is formed by the case (3) or the support member (40) fixed to the case (3). Since it is rotatably supported at two points in the axial direction (L), the load received by the second output gear (82a) from the second driven gear (52a) can be appropriately supported, and the load can be appropriately supported by the planetary gear device. The influence on (60) can be reduced.
As described above, according to the above configuration, the load received by the first output gear (81a) and the second output gear (82a) can be appropriately supported, and the load is applied to the planetary gear device (60). The impact can be reduced. Therefore, it becomes easy to secure the rigidity required for the planetary gear device (60), and the planetary gear device (60) can be miniaturized.

Here, the first rotary electric machine (11) and the second rotary electric machine (12) are arranged on the third axis (A3) parallel to the first axis (A1) and the second axis (A2). It is preferable to have.

According to this configuration, the first rotary electric machine (11) and the second rotary electric machine (12) are arranged on the first axis (A1) or the second axis (A2) as compared with the case where the first rotary electric machine (11) and the second rotary electric machine (12) are arranged on the first axis (A1) or the second axis (A2). ) And the second rotary electric machine (12) are arranged closer to the center side of the axial direction (L) of the transmission device (2), and as a result, the size of the entire device in the axial direction (L) can be reduced. It will be easier to plan.

The first rotary electric machine (11), the second rotary electric machine (12), the first connecting member (51) which is driven and connected to the first wheel (W1), and the second wheel (W2) which is driven and connected. The torque of the two connecting members (52) and the first rotary electric machine (11) is transmitted to at least the first connecting member (51) of the first connecting member (51) and the second connecting member (52). At the same time, the transmission device (2) that transmits the torque of the second rotary electric machine (12) to at least the second connecting member (52) of the first connecting member (51) and the second connecting member (52). ), The first rotary electric machine (11), the second rotary electric machine (12), the first connecting member (51), the second connecting member (52), and the transmission device (2). (3), the transmission device (2) is arranged on the first shaft (A1), and the first rotary electric machine (11) and the second rotary electric machine (12) are the first shaft. The transmission device (2) is arranged on a third axis (A3) parallel to (A1), and the transmission device (2) is a first rotating element (E1) driven and connected to the first rotating electric machine (11), and the first connection. Driven by a second rotating element (E2) that is driven and connected to a member (51), a third rotating element (E3) that is driven and connected to the second connecting member (52), and a second rotating electric machine (12). A planetary gear device (60) having at least a fourth rotating element (E4) to be connected, a first input member (71) connected to the first rotating element (E1), and the second rotating element (E2). A first output member (81) connected to, a second output member (82) connected to the third rotating element (E3), and a second input member connected to the fourth rotating element (E4). The first input member (71) includes a first input gear (71a) that meshes with a first drive gear (21a) that is driven and connected to the first rotary electric machine (11). The second input member (72) includes a second input gear (72a) that meshes with a second drive gear (22a) that is driven and connected to the second rotary electric machine (12), and the first input member (71). And each of the second input member (72) is rotatably supported at two points in the axial direction (L) by the case (3) or the support member (40) fixed to the case (3). There is.

According to this configuration, the first input member (71) connected to the first rotating element (E1) of the planetary gear device (60) is fixed to the case (3) or the case (3), and the support member (40). ), It is rotatably supported at two points in the axial direction (L). That is, since the first input member (71) can be supported by the non-rotating member at each of the two positions in the axial direction (L), the first input member (71) is supported at one place in the axial direction (L). The support rigidity of the first input member (71) can be increased as compared with the case where only the first input member (71) is supported by the non-rotating member or the first input member (71) is not supported by the non-rotating member. Therefore, the load received by the first input gear (71a) from the first drive gear (21a) can be appropriately supported, and the influence of the load on the planetary gear device (60) can be reduced. Similarly, the second input member (72) connected to the fourth rotating element (E4) of the planetary gear device (60) is formed by the case (3) or the support member (40) fixed to the case (3). Since it is rotatably supported at two points in the axial direction (L), the load received by the second input gear (72a) from the second drive gear (22a) can be appropriately supported, and the load can be appropriately supported by the planetary gear device. The influence on (60) can be reduced.
As described above, according to the above configuration, the load received by the first input gear (71a) and the second input gear (72a) can be appropriately supported, and the load is applied to the planetary gear device (60). The impact can be reduced. Therefore, it becomes easy to secure the rigidity required for the planetary gear device (60), and the planetary gear device (60) can be miniaturized.

Here, the first connecting member (51) and the second connecting member (52) are arranged on the second axis (A2) parallel to the first axis (A1) and the third axis (A3). It is preferable to have.

According to this configuration, the first connecting member (51) and the second connecting member (52) are arranged on the first axis (A1) or the third axis (A3) as compared with the case where the first connecting member (51) and the second connecting member (52) are arranged on the first axis (A1) or the third axis (A3). ) And the second connecting member (52) are closer to the center side of the axial direction (L) of the transmission device (2), and as a result, the size of the entire device in the axial direction (L) can be reduced. It will be easier to plan.

Here, the planetary gear device (6) includes a first planetary gear mechanism (61) having a first sun gear (S1), a first carrier (C1), and a first ring gear (R1), and a second sun gear (S2). ), A second carrier (C2), and a second planetary gear mechanism (62) having a second ring gear (R2), and the first rotating element (E1) is the first ring gear (R1). The second rotating element (E2) is the first carrier (C1) and the second sun gear (S2) that rotate integrally, and the third rotating element (E3) rotates integrally. It is preferable that the first sun gear (S1) and the second carrier (C2), and the fourth rotating element (E4) is the second ring gear (R2).

According to this configuration, the order of rotation speed is the first rotating element (E1) that is driven and connected to the first rotating electric machine (11), and the second rotating element (E2) that is driven and connected to the first connecting member (51). ), The third rotating element (E3) that is driven and connected to the second connecting member (52), and the fourth rotating element (E4) that is driven and connected to the second rotating electric machine (12). The torque of the electric machine (11) and the second rotary electric machine (12) can be distributed and transmitted to the first connecting member (51) and the second connecting member (52) by the transmission device (2). Therefore, the power transmission path between the first rotary electric machine (11) and the first connecting member (51) and the power transmission path between the second rotating electric machine (12) and the second connecting member (52) are separated. It is possible to improve the running performance when the vehicle turns, as compared with the case where the vehicle is turned.

As described above, in the configuration in which the planetary gear device (60) includes the first planetary gear mechanism (61) and the second planetary gear mechanism (62), the first planetary gear mechanism (61) is the first planetary gear mechanism (61). 2 The first output member (81) is arranged on the first side (L1) in the axial direction, which is one side of the axial direction (L) with respect to the planetary gear mechanism (62), and the first output member (81) is the first planetary gear mechanism (L). The second output member (82) is arranged on the first side (L1) in the axial direction with respect to 61), and the second output member (82) has the axial direction in the axial direction (L) with respect to the second planetary gear mechanism (62). The first output member (81) is arranged on the second side (L2) in the axial direction opposite to the first side (L1), and the first output member (81) is in the axial direction (L) with respect to the first carrier (C1). The second output member (82) is preferably connected so as to be relatively movable in the axial direction (L) with respect to the second carrier (C2).

According to this configuration, the first output member (81) is connected so as to be movable relative to the first carrier (C1) in the axial direction (L), so that the first output member (81) and the first carrier (81) are connected. Compared with the case where the first output member (81) and the first carrier (C1) cannot move relative to each other in the axial direction (L), such as when the C1) is integrally formed, the first output member (81) ) And the first carrier (C1) at the connecting portion (66a), the load transmission can be reduced. As a result, the load transmitted from the first output member (81) to the first carrier (C1) due to the load received from the first driven gear (51a) by the first output gear (81a) is reduced. Can be done. Similarly, according to the above configuration, the second output member (82) is connected so as to be relatively movable in the axial direction (L) with respect to the second carrier (C2), so that the second output gear (82a) is connected. The load transmitted from the second output member (82) to the second carrier (C2) due to receiving the load from the second driven gear (52a) can be reduced. As a result, it becomes easy to secure the rigidity required for the first carrier (C1) and the second carrier (C2), and the first planetary gear mechanism (61) and the second planetary gear mechanism (62) can be downsized. Can be planned.

In the vehicle drive device (1) having each of the above configurations, the first support member (41) and the second support member (42), which are the support members (40) arranged inside the case (3), respectively. A support portion (41c) of the first input member (71) and a support portion (41b) of the first output member (81) are formed on the first support member (41), and the second support member is provided. It is preferable that the support portion (42c) of the second input member (72) and the support portion (42b) of the second output member (82) are formed in (42).

According to this configuration, both the support portion (41c) of the first input member (71) and the support portion (41b) of the first output member (81) are formed on the first support member (41). Compared with the case where these support portions (41c and 41b) are formed on different support members, the number of parts can be reduced, and the first input member (71) and the first output member (81) can be combined. It becomes easy to secure the accuracy of the relative position. Similarly, according to the above configuration, both the support portion (42c) of the second input member (72) and the support portion (42b) of the second output member (82) are formed on the second support member (42). Therefore, the number of parts can be reduced as compared with the case where these support portions (42c, 42b) are formed on different support members, and the second input member (72) and the second output member ( It becomes easy to secure the accuracy of the position relative to 82).

As described above, in the configuration in which the vehicle drive device (1) includes the first support member (41) and the second support member (42), the first support member (41) and the first input member ( The bearing (B9) arranged between the first support member (41) and the bearing (B6) arranged between the first support member (41) and the first output member (81) is the first shaft. Bearings (B12) arranged so as to overlap each other in the radial (R) view with reference to (A1) and arranged between the second support member (42) and the second input member (72). And the bearing (B7) arranged between the second support member (42) and the second output member (82) are arranged so as to overlap each other in the radial (R) view. Is suitable.

According to this configuration, the bearing (B9) arranged between the first support member (41) and the first input member (71), the first support member (41), and the first output member (81) Since the bearing (B6) arranged between the bearings (B6) overlaps in the radial direction (R), the space occupied by the transmission device (2) can be reduced in the axial direction (L). Further, according to the above configuration, the bearing (B12) arranged between the second support member (42) and the second input member (72), the second support member (42), and the second output member ( Since the bearing (B7) arranged between the bearing (B7) and the bearing (B7) overlaps in the radial direction (R), the space occupied by the transmission device (2) can be reduced in the axial direction (L).

In the vehicle drive device (1) having each of the above configurations, the planetary gear device (60) is configured by connecting the first planetary gear mechanism (61) and the second planetary gear mechanism (62). Each of the 1 input member (71), the 2nd input member (72), the 1st output member (81), and the 2nd output member (82) is the case (3) or the support member (40). The connecting portion (63) between the rotating element of the first planetary gear mechanism (61) and the rotating element of the second planetary gear mechanism (62) is rotatably supported by the first axis (A1). It is preferable that the connection structure has a gap in the radial direction (R).

According to this configuration, each of the first input member (71), the second input member (72), the first output member (81), and the second output member (82) is a case (3) or a support member ( Since it is rotatably supported by the first input member (71), the first rotating element (E1) connected to the first input member (71), the fourth rotating element (E4) connected to the second input member (72), and the second It is possible to appropriately secure the support accuracy of each of the second rotating element (E2) connected to the first output member (81) and the third rotating element (E3) connected to the second output member (82). it can. On top of that, according to the above configuration, the connecting portion (63) between the rotating element of the first planetary gear mechanism (61) and the rotating element of the second planetary gear mechanism (62) has a gap (R) in the radial direction (R). Since it has a connecting structure having the above, the dimensional error and the assembling error in the radial direction (R) of each part can be absorbed by the connecting portion (63), and the first planetary gear mechanism (61) and the second planet can be absorbed. It becomes easy to avoid an excessive load (uneven load, etc.) acting on the meshing portion of the gear in the gear mechanism (62).

Further, the planetary gear device (60) has a first planetary gear mechanism (61) having a first carrier (C1) that rotatably supports the first pinion gear (P1) via a first pinion bearing (B13). A second planetary gear mechanism (62) having a second carrier (C2) that rotatably supports the second pinion gear (P2) via a second pinion bearing (B14), and the first output member ( The 81) is connected to the first carrier (C1) and rotatably supported via the first output bearing (B6), and the second output member (82) is attached to the second carrier (C2). Connected and rotatably supported via a second output bearing (B7), the first carrier (C1) and an oil passage (91) for supplying oil to the first pinion bearing (B13). An oil passage (92) for supplying oil to the first output bearing (B6) is formed, and the second carrier (C2) is used to supply oil to the second pinion bearing (B14). It is preferable that the oil passage (93) and the oil passage (94) for supplying oil to the second output bearing (B7) are formed.

According to this configuration, the oil passage (92) for supplying oil to the first output bearing (B6) is the same as the oil passage (91) for supplying oil to the first pinion bearing (B13). Since it is formed in one carrier (C1), the oil supply structure for these oil passages (91, 92) can be made common, and the oil passage configuration can be simplified. Similarly, according to the above configuration, the oil passage (94) for supplying oil to the second output bearing (B7) is the oil passage (93) for supplying oil to the second pinion bearing (B14). Since it is formed in the second carrier (C2) in the same manner as in the above, the oil supply structure for these oil passages (93, 94) can be made common, and the oil passage configuration can be simplified.

The vehicle drive device according to the present disclosure may be capable of exerting at least one of the above-mentioned effects.

1: Vehicle drive device 2: Transmission device 3: Case 11: First rotary electric machine 12: Second rotary electric machine 21a: First drive gear 22a: Second drive gear 40: Support member 41: First support member 41b: First 7 Support part (Support part of the first output member)
41c: Ninth support part (support part of the first input member)
42: Second support member 42b: Eighth support portion (support portion of the second output member)
42c: 10th support part (support part of the 2nd input member)
51: 1st connecting member 51a: 1st driven gear 52: 2nd connecting member 52a: 2nd driven gear 60: Planetary gear device 61: 1st planetary gear mechanism 62: 2nd planetary gear mechanism 63: Connecting portion 71: First 1 input member 71a: 1st input gear 72: 2nd input member 72a: 2nd input gear 81: 1st output member 81a: 1st output gear 82: 2nd output member 82a: 2nd output gear 91: 1st oil Road (oil path for supplying oil to the first pinion bearing)
92: 2nd oil passage (oil passage for supplying oil to the 1st output bearing)
93: Third oil passage (oil passage for supplying oil to the second pinion bearing)
94: Fourth oil passage (oil passage for supplying oil to the second output bearing)
A1: 1st axis A2: 2nd axis A3: 3rd axis B6: 6th bearing (bearing arranged between the 1st support member and the 1st output member, 1st output bearing)
B7: 7th bearing (bearing arranged between the 2nd support member and the 2nd output member, the 2nd output bearing)
B9: Ninth bearing (bearing placed between the first support member and the first input member)
B12: 12th bearing (bearing placed between the 2nd support member and the 2nd input member)
B13: 13th bearing (1st pinion bearing)
B14: 14th bearing (2nd pinion bearing)
C1: 1st carrier C2: 2nd carrier E1: 1st rotating element E2: 2nd rotating element E3: 3rd rotating element E4: 4th rotating element L: Axial direction L1: Axial direction 1st side L2: Axial direction first 2 side P1: 1st pinion gear P2: 2nd pinion gear R1: 1st ring gear R2: 2nd ring gear S1: 1st sun gear S2: 2nd sun gear W1: 1st wheel W2: 2nd wheel

Claims (10)

With the 1st rotary electric machine
2nd rotary electric machine and
The first connecting member that is driven and connected to the first wheel,
The second connecting member that is driven and connected to the second wheel,
The torque of the first rotary electric machine is transmitted to at least the first connecting member of the first connecting member and the second connecting member, and the torque of the second rotating electric machine is transmitted to the first connecting member and the second connecting member. A transmission device that transmits to at least the second connecting member among the connecting members,
The first rotary electric machine, the second rotary electric machine, the first connecting member, the second connecting member, and a case for accommodating the transmission device are provided.
The transmission device is arranged on the first axis and
The first connecting member and the second connecting member are arranged on a second axis parallel to the first axis.
The transmission device includes a first rotating element that is driven and connected to the first rotating electric machine, a second rotating element that is driven and connected to the first connecting member, and a third rotating element that is driven and connected to the second connecting member. A planetary gear device having at least a fourth rotating element that is driven and connected to the second rotating electric machine, a first input member that is connected to the first rotating element, and a first that is connected to the second rotating element. The output member, the second output member connected to the third rotating element, and the second input member connected to the fourth rotating element are provided.
The first output member includes a first output gear that meshes with a first driven gear included in the first connecting member.
The second output member includes a second output gear that meshes with a second driven gear included in the second connecting member.
A vehicle drive device in which each of the first output member and the second output member is rotatably supported at two points in the axial direction by the case or a support member fixed to the case. The vehicle drive device according to claim 1, wherein the first rotary electric machine and the second rotary electric machine are arranged on a third axis parallel to the first axis and the second axis. With the 1st rotary electric machine
2nd rotary electric machine and
The first connecting member that is driven and connected to the first wheel,
The second connecting member that is driven and connected to the second wheel,
The torque of the first rotary electric machine is transmitted to at least the first connecting member of the first connecting member and the second connecting member, and the torque of the second rotating electric machine is transmitted to the first connecting member and the second connecting member. A transmission device that transmits to at least the second connecting member among the connecting members,
The first rotary electric machine, the second rotary electric machine, the first connecting member, the second connecting member, and a case for accommodating the transmission device are provided.
The transmission device is arranged on the first axis and
The first rotary electric machine and the second rotary electric machine are arranged on a third axis parallel to the first axis.
The transmission device includes a first rotating element that is driven and connected to the first rotating electric machine, a second rotating element that is driven and connected to the first connecting member, and a third rotating element that is driven and connected to the second connecting member. A planetary gear device having at least a fourth rotating element that is driven and connected to the second rotating electric machine, a first input member that is connected to the first rotating element, and a first that is connected to the second rotating element. The output member, the second output member connected to the third rotating element, and the second input member connected to the fourth rotating element are provided.
The first input member includes a first input gear that meshes with a first drive gear that is driven and connected to the first rotary electric machine.
The second input member includes a second input gear that meshes with a second drive gear that is driven and connected to the second rotary electric machine.
A vehicle drive device in which each of the first input member and the second input member is rotatably supported at two points in the axial direction by the case or a support member fixed to the case. The vehicle drive device according to claim 3, wherein the first connecting member and the second connecting member are arranged on a second axis parallel to the first axis and the third axis. The planetary gear device includes a first planetary gear mechanism having a first sun gear, a first carrier, and a first ring gear, and a second planetary gear mechanism having a second sun gear, a second carrier, and a second ring gear. ,
The first rotating element is the first ring gear.
The second rotating element is the first carrier and the second sun gear that rotate integrally.
The third rotating element is the first sun gear and the second carrier that rotate integrally.
The vehicle drive device according to any one of claims 1 to 4, wherein the fourth rotating element is the second ring gear. The first planetary gear mechanism is arranged on the first side in the axial direction, which is one side in the axial direction with respect to the second planetary gear mechanism.
The first output member is arranged on the first side in the axial direction with respect to the first planetary gear mechanism.
The second output member is arranged on the second side in the axial direction, which is opposite to the first side in the axial direction in the axial direction with respect to the second planetary gear mechanism.
The first output member is connected to the first carrier so as to be relatively movable in the axial direction.
The vehicle drive device according to claim 5, wherein the second output member is connected to the second carrier so as to be relatively movable in the axial direction. A first support member and a second support member, which are the support members arranged inside the case, respectively, are provided.
A support portion of the first input member and a support portion of the first output member are formed on the first support member.
The vehicle drive device according to any one of claims 1 to 6, wherein a support portion of the second input member and a support portion of the second output member are formed on the second support member. The bearing arranged between the first support member and the first input member and the bearing arranged between the first support member and the first output member are based on the first axis. Arranged so that they overlap each other in the radial view
The bearing arranged between the second support member and the second input member and the bearing arranged between the second support member and the second output member overlap each other in the radial direction. The vehicle drive device according to claim 7, which is arranged so as to be used. The planetary gear device is configured by connecting a first planetary gear mechanism and a second planetary gear mechanism.
Each of the first input member, the second input member, the first output member, and the second output member is rotatably supported by the case or the support member.
Claims 1 to 8 in which the connecting portion between the rotating element of the first planetary gear mechanism and the rotating element of the second planetary gear mechanism has a connecting structure having a radial gap with respect to the first axis. The vehicle drive device according to any one of the above. The planetary gear device rotatably supports a first planetary gear mechanism having a first carrier that rotatably supports the first pinion gear via a first pinion bearing and a second pinion gear via a second pinion bearing. A second planetary gear mechanism having a second carrier, and
The first output member is connected to the first carrier and rotatably supported via the first output bearing.
The second output member is connected to the second carrier and rotatably supported via the second output bearing.
An oil passage for supplying oil to the first pinion bearing and an oil passage for supplying oil to the first output bearing are formed in the first carrier.
Any of claims 1 to 9, wherein the second carrier is formed with an oil passage for supplying oil to the second pinion bearing and an oil passage for supplying oil to the second output bearing. The vehicle drive device according to paragraph 1.

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