JP2020193699A - Drive unit for vehicle - Google Patents

Abstract

To obtain a drive unit for a vehicle which can be reduced in a size of the unit as a whole.SOLUTION: A first planetary gear mechanism 31 comprises: a first rotation element E1 engaged with, and connected to a fourth gear G4; a second rotation element E2 integrally rotating together with a first output member 3; and a third rotation element E3. A second planetary gear mechanism 32 comprises: a fourth rotation element E4 engaged with, and connected to a sixth gear G6; a fifth rotation element E5 integrally rotating together with a second output member 4; and a sixth rotation element E6. The first rotation element E1 and the sixth rotation element E6 are connected to each other so as to integrally rotate, and the third rotation element E3 and the fourth rotation element E4 are connected to each other so as to integrally rotate. A first gear G1 and a second gear G2 are arranged between a first drive source 10 and a second drive source 20 in an axial direction L in an order from a first side L1 in the axial direction, a fourth gear G4 is arranged at the first side L1 in the axial direction with respect to a third gear G3, and the sixth gear G6 is arranged at a second side L2 in the axial direction with respect to a fifth gear G5.SELECTED DRAWING: Figure 2

Description

The present invention comprises a first drive source, a second drive source, a first output member that is driven and connected to the first wheel, a second output member that is driven and connected to the second wheel, and a power transmission device. Regarding the vehicle drive device provided.

An example of the vehicle drive device as described above is disclosed in Japanese Patent Application Laid-Open No. 2017-141889 (Patent Document 1) and Japanese Patent Application Laid-Open No. 2015-21594 (Patent Document 2). Hereinafter, the reference numerals shown in parentheses in the explanation of background techniques and problems are those of the references.

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 drive sources (2L, 2R) and left and right drive wheels (61L, 61R). It is provided with two output gear shafts (14L, 14R) and a gear device (30) configured by using two planetary gear mechanisms (30L, 30R). This gear device (30) includes an input side external gear (13a) that meshes with an input gear (12a) to which power is transmitted from a drive source (2L, 2R), and an output gear (14L, 14R) included in the output gear shaft (14L, 14R). It is provided with an output side small diameter gear (13b) that meshes with 14a). Then, this gear device (30) is configured as described in paragraph 0110 of Patent Document 1, so that the torque input from the drive source (2L, 2R) side to the input side external gear (13a) can be obtained. When outputting from the output side small diameter gear (13b) to the drive wheel (61L, 61R) side, the output torque of the two drive sources (2L, 2R) is applied to the left and right drive wheels (61L, 61R) while amplifying the torque difference. It is configured so that it can be distributed to 61R) (paragraphs 0108,0166). The gear device (5) provided in the left and right wheel drive devices (1) of Patent Document 2 also applies the output torques of the two drive sources (2, 3) to the left and right drive wheels (4L, 4R) while amplifying the torque difference. It is configured so that it can be distributed.

Japanese Unexamined Patent Publication No. 2017-141889 Japanese Unexamined Patent Publication No. 2015-21594

By the way, in the vehicle drive device (1) of Patent Document 1, as shown in FIG. 2 of Patent Document 1, four planetary gear mechanisms (30L, 30R) constituting the gear device (30) are each provided with four. Bearings (20a, 20b, 39a, 39b) are arranged in an axially dispersed manner. That is, since the eight bearings are distributed and arranged in the axial direction in the entire gear device (30), the gear device (30) tends to be large in the axial direction. Then, as shown in FIG. 1 of Patent Document 1, in this vehicle drive device (1), a gear device (30) is arranged between two drive sources (2L, 2R) in the axial direction. Therefore, as the distance between the two drive sources (2L, 2R) in the axial direction increases, the vehicle drive device (1) tends to increase in the axial direction. On the other hand, although Patent Document 2 discloses a schematic configuration of the left and right wheel drive device (1) using a skeleton diagram, the size of the entire device in the axial direction and the radial direction (direction orthogonal to the axial direction). There is no specific disclosure of.

Therefore, it is desired to realize a vehicle drive device that can reduce the size of the entire device.

The vehicle drive device according to the present disclosure includes a first drive source, a second drive source, a first output member that is driven and connected to the first wheel, and a second output member that is driven and connected to the second wheel. A vehicle drive device including a power transmission device, wherein the first drive source and the second drive source are arranged on a first shaft, and the first output member and the second output member are The first counter gear mechanism and the second are arranged on a second axis different from the first axis, and the power transmission device is arranged on the first axis and the third axis different from the second axis, respectively. A counter gear mechanism and a first planetary gear mechanism and a second planetary gear mechanism arranged on the second shaft, respectively, are provided, and the first counter gear mechanism rotates integrally with the first drive source. A second gear that includes a third gear that meshes with the first gear and a fourth gear that rotates integrally with the third gear, and the second counter gear mechanism rotates integrally with the second drive source. A fifth gear that meshes with the fifth gear and a sixth gear that rotates integrally with the fifth gear are provided, and the first planetary gear mechanism includes a first rotating element that meshes with and is connected to the fourth gear, and the first A second rotating element that rotates integrally with the output member, a third rotating element, and the second planetary gear mechanism include a fourth rotating element that is meshed with and connected to the sixth gear, and the second. A fifth rotating element and a sixth rotating element that rotate integrally with the output member are provided, and the first rotating element and the sixth rotating element are connected so as to rotate integrally, and the third rotation. The element and the fourth rotating element are connected so as to rotate integrally, and the side on which the first drive source is arranged with respect to the second drive source in the axial direction is defined as the first side in the axial direction, and the shaft. The side opposite to the first side in the axial direction in the direction is set as the second side in the axial direction, and the first side in the axial direction is placed between the first drive source and the second drive source in the axial direction in order from the first side in the axial direction. The first gear and the second gear are arranged, the fourth gear is arranged on the first side in the axial direction with respect to the third gear, and the sixth gear is the shaft with respect to the fifth gear. It is arranged on the second side of the direction.

According to this configuration, the first planetary gear mechanism and the second planetary gear mechanism are connected to form a planetary gear device having four rotating elements as a whole, and the planetary gear device is used via the first counter gear mechanism. The output torque of the first drive source input and the output torque of the second drive source input via the second counter gear mechanism can be distributed to the first output member and the second output member. .. Then, in the above configuration, the power transmission between the first axis in which the first drive source and the second drive source are arranged and the second axis in which the planetary gear device is arranged is transmitted to these first axes. And it can be done via a third axis that is different from the second axis. Therefore, as compared with the case where the power is transmitted between the first axis and the second axis without going through the other axes, the first drive source and the second drive source are avoided while avoiding interference with the planetary gear device. It becomes easy to arrange the and the device close to the axial direction, and as a result, the entire device can be miniaturized in the axial direction.

Further, in the above configuration, the first gear and the second gear are arranged in order from the first side in the axial direction between the first drive source and the second drive source in the axial direction, and the fourth gear is the first gear. Since the sixth gear is arranged on the first side in the axial direction with respect to the third gear that meshes with the gear and the sixth gear is arranged on the second side in the axial direction with respect to the fifth gear that meshes with the second gear, the axial direction of the entire device It is possible to further reduce the size of the gear. To supplement this point, the limit position on the second side in the axial direction in which the first drive source can be arranged is generally the position on the first side in the axial direction as the first gear is arranged on the first side in the axial direction. .. For example, when a support structure such as a bearing is provided between the first drive source and the first gear on the first shaft, the limit position on the second side in the axial direction in which the first drive source can be arranged is the first. The position is separated from one gear by at least the arrangement space of the support structure on the first side in the axial direction. Similarly, the limit position on the first side in the axial direction in which the second drive source can be arranged generally becomes the position on the second side in the axial direction as the second gear is arranged on the second side in the axial direction.

In the above configuration, since the fourth gear is arranged on the first side in the axial direction with respect to the third gear, as compared with the case where the fourth gear is arranged on the second side in the axial direction with respect to the third gear, The first gear can be arranged closer to the second side in the axial direction, and as a result, the first drive source can be easily arranged closer to the second side in the axial direction. Further, in the above configuration, since the sixth gear is arranged on the second side in the axial direction with respect to the fifth gear, compared with the case where the sixth gear is arranged on the first side in the axial direction with respect to the fifth gear. Therefore, the second gear can be arranged closer to the first side in the axial direction, and as a result, the second drive source can be easily arranged closer to the first side in the axial direction. As described above, as a result of facilitating the arrangement of the first drive source and the second drive source closer to each other in the axial direction, it is possible to further reduce the size of the entire device in the axial direction. ing.

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

Cross-sectional view of the vehicle drive device according to the 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 The figure which shows the arrangement relation of each component of the vehicle drive device which concerns on embodiment in the axial direction.

An embodiment of a vehicle drive device will be described with reference to the drawings. 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 dimensions, placement directions, placement positions, etc. of each member are concepts including a state in which there is a difference due to an error (an error that is acceptable in manufacturing).

As used herein, the term "driving connection" refers to a state in which two rotating elements are connected so as to be able to transmit a driving force (synonymous with torque), and the two rotating elements are connected so as to rotate integrally. This includes a state in which the 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 (for example, shafts, gear mechanisms, belts, chains, etc.) that transmit rotation at the same speed or at different speeds, and are responsible for selectively transmitting rotation and driving force. A mating device (eg, friction engaging device, meshing engaging device, etc.) may be included. However, when the term "drive connection" is used for each rotating element of the planetary gear mechanism, it means a state in which the three rotating elements included in the planetary gear mechanism are driven and connected to each other without interposing other rotating elements. ..

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.

As shown in FIGS. 1 and 3, the vehicle drive device 1 includes a first drive source 10, a second drive source 20, a first output member 3, a second output member 4, and a power transmission device 2. , Is equipped. As shown in FIG. 1, the vehicle drive device 1 further includes a case 60. The case 60 houses a first drive source 10, a second drive source 20, a first output member 3, a second output member 4, and a power transmission device 2. Here, "accommodating" means accommodating at least a part of the object to be accommodated. Each storage object housed in the case 60 is fixed to the case 60 or rotatably supported by the case 60 via bearings or the like.

As shown in FIG. 3, the first output member 3 is drive-connected to the first wheel W1, and the second output member 4 is drive-connected to the second wheel W2. Here, the first wheel W1 and the second wheel W2 are a pair of left and right wheels (for example, a pair of left and right front wheels or a pair of left and right rear wheels). In the present embodiment, the first output member 3 is connected so as to rotate integrally with the first wheel W1, and the second output member 4 is connected so as to rotate integrally with the second wheel W2. Then, the power transmission device 2 is configured to transmit the output torques of the first drive source 10 and the second drive source 20 to the first output member 3 and the second output member 4. The vehicle drive device 1 transmits the output torques of the first drive source 10 and the second drive source 20 to the first wheel W1 and the second wheel W2, and the vehicle (vehicle on which the vehicle drive device 1 is mounted, hereinafter The same) is run. That is, the first drive source 10 and the second drive source 20 are used as drive force sources for the first wheel W1 and the second wheel W2.

As shown in FIGS. 1 and 3, the first drive source 10 and the second drive source 20 are arranged on the first axis A1, and the first output member 3 and the second output member 4 are arranged with the first axis A1. Are located on different second axes A2. The power transmission device 2 is on the first counter gear mechanism 41 and the second counter gear mechanism 42, which are arranged on the third axis A3 different from the first axis A1 and the second axis A2, and on the second axis A2, respectively. The first planetary gear mechanism 31 and the second planetary gear mechanism 32, which are arranged in the above, are provided. The first planetary gear mechanism 31 and the second planetary gear mechanism 32 are arranged between the first output member 3 and the second output member 4 in the axial direction L. As will be described later, the planetary gear device 30 is configured by connecting the first planetary gear mechanism 31 and the second planetary gear mechanism 32. The second axis A2 is an axis parallel to the first axis A1, and the third axis A3 is an axis parallel to the first axis A1 and the second axis A2. These first axis A1, second axis A2, and third axis A3 are virtual axes.

In the following, the direction parallel to the first axis A1, the second axis A2, and the third axis A3 (that is, the axial direction common among these axes) is referred to as the axial direction L. Then, the side where the first drive source 10 is arranged with respect to the second drive source 20 in the axial direction L is set as the first side L1 in the axial direction, and the side opposite to the first side L1 in the axial direction in the axial direction L is the axial direction. Let it be the second side L2. The first output member 3 is arranged on the first side L1 in the axial direction with respect to the second output member 4. The first counter gear mechanism 41 is arranged on the first side L1 in the axial direction with respect to the second counter gear mechanism 42. The first planetary gear mechanism 31 is arranged on the first side L1 in the axial direction with respect to the second planetary gear mechanism 32. Further, as shown in FIGS. 1 and 5, the radial direction based on the first axis A1 is defined as the first radial direction K1, and the radial direction based on the second axis A2 is defined as the second radial direction K2. The radial direction with respect to the axis A3 is defined as the third radial direction K3.

As shown in FIGS. 1 and 3, in the present embodiment, the first drive source 10 is a rotary electric machine. That is, the first drive source 10 includes a first stator 12 fixed to the case 60 and a first rotor 11 rotatably supported by the case 60 with respect to the first stator 12. In the present embodiment, the first drive source 10 is an inner rotor type rotary electric machine, and the first rotor 11 is inside the first radial direction K1 with respect to the first stator 12, and is in the first radial direction K1. It is arranged so as to overlap the first stator 12 in the radial direction along the line. The first stator 12 includes a first stator core 12a fixed to the case 60 and a coil wound around the first stator core 12a, and a portion of the coil protruding from the first stator core 12a in the axial direction L. The first coil end portion 12b is formed on both sides in the axial direction L with respect to the first stator core 12a.

As shown in FIGS. 1 and 3, in the present embodiment, the second drive source 20 is a rotary electric machine. That is, the second drive source 20 includes a second stator 22 fixed to the case 60 and a second rotor 21 rotatably supported by the case 60 with respect to the second stator 22. In the present embodiment, the second drive source 20 is an inner rotor type rotary electric machine, and the second rotor 21 is inside the first radial direction K1 with respect to the second stator 22 and is in the first radial direction K1. It is arranged so as to overlap the second stator 22 in the radial direction along the line. The second stator 22 includes a second stator core 22a fixed to the case 60 and a coil wound around the second stator core 22a, and a portion of the coil that protrudes in the axial direction L from the second stator core 22a. The second coil end portion 22b is formed on both sides in the axial direction L with respect to the second stator core 22a.

The second drive source 20 is rotatably provided independently of the first drive source 10. That is, the second rotor 21 is not connected so as to rotate integrally with the first rotor 11, but is connected to the rotation speed of the first drive source 10 (specifically, the rotation speed of the first rotor 11). The ratio with the rotation speed of the second drive source 20 (specifically, the rotation speed of the second rotor 21) changes according to the state of the vehicle drive device 1. For example, as the first drive source 10 and the second drive source 20, two rotary electric machines having the same output characteristics can be used.

As shown in FIGS. 1 and 3, the vehicle drive device 1 includes a first transmission shaft 71 that transmits a driving force between the first drive source 10 and the power transmission device 2, and a second drive source 20 and power. A second transmission shaft 72 that transmits a driving force to and from the transmission device 2 is provided on the first shaft A1. That is, the output torque of the first drive source 10 is input to the power transmission device 2 via the first transmission shaft 71, and the output torque of the second drive source 20 is input to the power transmission device 2 via the second transmission shaft 72. Is entered in. The first transmission shaft 71 and the second transmission shaft 72 are arranged along the axial direction L. The first transmission shaft 71 is arranged on the first side L1 in the axial direction with respect to the second transmission shaft 72.

The first drive source 10 (specifically, the first rotor 11) is connected so as to rotate integrally with the first transmission shaft 71. The first transmission shaft 71 includes a first gear G1. That is, the first gear G1 is a gear that rotates integrally with the first drive source 10. In the present embodiment, the first gear G1 is a helical gear (cylindrical gear having spiral tooth streaks). Further, the second drive source 20 (specifically, the second rotor 21) is connected so as to rotate integrally with the second transmission shaft 72. The second transmission shaft 72 includes a second gear G2. That is, the second gear G2 is a gear that rotates integrally with the second drive source 20. In this embodiment, the second gear G2 is a helical gear.

As shown in FIG. 2, in the present embodiment, the first transmission shaft 71 includes a first shaft member 71a and a second shaft member 71b, which are two shaft members connected so as to rotate integrally with each other. There is. The first shaft member 71a is arranged on the first side L1 in the axial direction with respect to the second shaft member 71b. The first rotor 11 is fixed to the outer peripheral surface of the first shaft member 71a, and the first gear G1 is formed on the outer peripheral portion of the second shaft member 71b. Further, in the present embodiment, the second transmission shaft 72 includes a third shaft member 72a and a fourth shaft member 72b, which are two shaft members connected so as to rotate integrally with each other. The third shaft member 72a is arranged on the second side L2 in the axial direction with respect to the fourth shaft member 72b. The second rotor 21 is fixed to the outer peripheral surface of the third shaft member 72a, and the second gear G2 is formed on the outer peripheral portion of the fourth shaft member 72b.

The rotation of the first transmission shaft 71 is input to the planetary gear device 30 via the first counter gear mechanism 41. As shown in FIGS. 2 and 3, the first counter gear mechanism 41 rotates integrally with the third gear G3 and the third gear G3 that mesh with the first gear G1 that rotates integrally with the first drive source 10. It is provided with a fourth gear G4. The first counter gear mechanism 41 is further provided with a first counter shaft 41a which is arranged along the axial direction L and connects the third gear G3 and the fourth gear G4. In the present embodiment, the third gear G3 is formed to have a larger diameter than the first gear G1, and the fourth gear G4 is formed to have a smaller diameter than the seventh gear G7 described later. Therefore, the rotation of the first transmission shaft 71 is decelerated according to the gear ratio between the first gear G1 and the third gear G3, and also according to the gear ratio between the fourth gear G4 and the seventh gear G7. It is further decelerated (that is, decelerated by two steps) and input to the planetary gear device 30 (specifically, the first rotating element E1 described later). In the present embodiment, the third gear G3 and the fourth gear G4 are helical gears.

Further, the rotation of the second transmission shaft 72 is input to the planetary gear device 30 via the second counter gear mechanism 42. As shown in FIG. 2, the second counter gear mechanism 42 has a fifth gear G5 that meshes with a second gear G2 that rotates integrally with the second drive source 20, and a sixth gear that rotates integrally with the fifth gear G5. It is equipped with a gear G6. The second counter gear mechanism 42 further includes a second counter shaft 42a that is arranged along the axial direction L and connects the fifth gear G5 and the sixth gear G6. In the present embodiment, the fifth gear G5 is formed to have a larger diameter than the second gear G2, and the sixth gear G6 is formed to have a smaller diameter than the eighth gear G8 described later. Therefore, the rotation of the second transmission shaft 72 is decelerated according to the gear ratio between the second gear G2 and the fifth gear G5, and also according to the gear ratio between the sixth gear G6 and the eighth gear G8. It is further decelerated (that is, decelerated by two steps) and input to the planetary gear device 30 (specifically, the fourth rotating element E4 described later). In the present embodiment, the fifth gear G5 and the sixth gear G6 are helical gears.

As shown in FIGS. 2 and 3, the first planetary gear mechanism 31 has a first rotating element E1 meshed with and connected to a fourth gear G4 and a second rotating element E2 that rotates integrally with the first output member 3. And a third rotating element E3. The fourth gear G4 is arranged so as to mesh with the seventh gear G7 that rotates integrally with the first rotating element E1. In the present embodiment, the vehicle drive device 1 includes a first connecting member 51 connected so as to rotate integrally with the first rotating element E1, and a fourth connecting member 51 is provided on the outer peripheral portion of the first connecting member 51. A seventh gear G7 that meshes with the gear G4 is formed. That is, the first rotating element E1 is meshed and connected to the fourth gear G4 via the first connecting member 51. In the present embodiment, since the seventh gear G7 that meshes with the fourth gear G4 is formed on the outer peripheral portion of the first connecting member 51, which is a member different from the member constituting the first rotating element E1, the first rotating element Compared to the case where the seventh gear G7 is formed on the member constituting the E1, the load (radial load, thrust load, etc.) received by the seventh gear G7 from the fourth gear G4 is the first including the first rotating element E1. It is possible to reduce the influence on the planetary gear mechanism 31. As a result, it becomes easy to secure the rigidity required for the first planetary gear mechanism 31, and it is possible to reduce the size of the first planetary gear mechanism 31.

Further, the second planetary gear mechanism 32 includes a fourth rotating element E4 meshed with and connected to the sixth gear G6, a fifth rotating element E5 that rotates integrally with the second output member 4, and a sixth rotating element E6. , Is equipped. The sixth gear G6 is arranged so as to mesh with the eighth gear G8 that rotates integrally with the fourth rotating element E4. In the present embodiment, the vehicle drive device 1 includes a second connecting member 52 connected so as to rotate integrally with the fourth rotating element E4, and a sixth connecting member 52 is provided on the outer peripheral portion of the second connecting member 52. An eighth gear G8 that meshes with the gear G6 is formed. That is, the fourth rotating element E4 is meshed and connected to the sixth gear G6 via the second connecting member 52. In the present embodiment, since the eighth gear G8 that meshes with the sixth gear G6 is formed on the outer peripheral portion of the second connecting member 52 which is a member different from the member constituting the fourth rotating element E4, the fourth rotating element Compared to the case where the eighth gear G8 is formed on the member constituting the E4, the load (radial load, thrust load, etc.) received by the eighth gear G8 from the sixth gear G6 is the second including the fourth rotating element E4. It is possible to reduce the influence on the planetary gear mechanism 32. As a result, it becomes easy to secure the rigidity required for the second planetary gear mechanism 32, and it is possible to reduce the size of the second planetary gear mechanism 32.

In the present embodiment, the first planetary gear mechanism 31 includes a carrier (first carrier C1) which is a first rotating element E1, a ring gear (first ring gear R1) which is a second rotating element E2, and a third rotating element E3. This is a double pinion type planetary gear mechanism equipped with a sun gear (first sun gear S1). The first carrier C1 rotatably supports a first pinion gear set, which is a set of two first pinion gears P1 that mesh with each other. The first planetary gear mechanism 31 includes a first pinion shaft 81 that rotatably supports the first pinion gear P1 from the inside in the radial direction (diameter direction with respect to the first pinion gear P1), and the first carrier C1 , Holds the first pinion shaft 81. One of the two first pinion gears P1 constituting one first pinion gear set is arranged so as to mesh with the first sun gear S1, and the other of the two first pinion gears P1 is arranged so as to mesh with the first ring gear R1. There is. In the example shown in FIG. 5, the first carrier C1 rotatably supports four sets of first pinion gear sets. In the present embodiment, the first ring gear R1, the first sun gear S1, and the first pinion gear P1 are spur gears (cylindrical gears having linear tooth streaks).

Further, in the present embodiment, the second planetary gear mechanism 32 includes a carrier (second carrier C2) which is a fourth rotating element E4, a ring gear (second ring gear R2) which is a fifth rotating element E5, and a sixth rotation. It is a double pinion type planetary gear mechanism including a sun gear (second sun gear S2) which is an element E6. The second carrier C2 rotatably supports a second pinion gear set, which is a set of two second pinion gears P2 that mesh with each other. The second planetary gear mechanism 32 includes a second pinion shaft 82 that rotatably supports the second pinion gear P2 from the inside in the radial direction (diameter direction with respect to the second pinion gear P2), and the second carrier C2 , Holds the second pinion shaft 82. One of the two second pinion gears P2 constituting one second pinion gear set is arranged so as to mesh with the second sun gear S2, and the other of the two second pinion gears P2 is arranged so as to mesh with the second ring gear R2. There is. In the example shown in FIG. 5, the second carrier C2 rotatably supports four sets of second pinion gear sets. In the present embodiment, the second ring gear R2, the second sun gear S2, and the second pinion gear P2 are spur gears.

Then, as shown in FIGS. 2 and 3, the first rotating element E1 and the sixth rotating element E6 are connected so as to rotate integrally, and the third rotating element E3 and the fourth rotating element E4 are integrally rotated. It is connected so as to rotate. That is, 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. The first planetary gear mechanism 31 and the second planetary gear mechanism 32 are integrally 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. That is, as shown in the speed diagram (co-line diagram) in FIG. 4, the planetary gear device 30 configured by connecting the first planetary gear mechanism 31 and the second planetary gear mechanism 32 rotates integrally with each other. A rotating element composed of the first rotating element E1 and the sixth rotating element E6, a rotating element composed of the second rotating element E2, a rotating element composed of the fifth rotating element E5, and a second rotating element that rotates integrally with each other. It includes four rotating elements, which are rotating elements composed of the three rotating elements E3 and the fourth rotating element E4.

In FIG. 4, "Ti1" represents the torque (first input torque Ti1) input to the first rotating element E1 and the sixth rotating element E6 from the side of the first drive source 10, and "Ti2" is the third. The torque (second input torque Ti2) input to the rotating element E3 and the fourth rotating element E4 from the side of the second drive source 20 is represented, and "To1" represents the side from the second rotating element E2 to the first output member 3. Represents the torque output to (first output torque To1), and “To2” represents the torque output from the fifth rotating element E5 to the side of the second output member 4 (second output torque To2). In the present embodiment, the gear ratio of the first planetary gear mechanism 31 (that 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 gear ratio of the second planetary gear mechanism 32 (that is, the first The ratio of the number of teeth of the second sun gear S2 to the number of teeth of the two ring gear R2) is equal to each other, and in FIG. 4, the gear ratio of the first planetary gear mechanism 31 and the second planetary gear mechanism 32 is “λ”. In the present embodiment, the first ring gear R1 and the second ring gear R2 are formed to have the same diameter, and the first sun gear S1 and the second sun gear S2 are formed to have the same diameter.

The magnitude of the first input torque Ti1 is the magnitude of the output torque of the first drive source 10 and the reduction ratio (first reduction ratio) from the first drive source 10 to the first rotation element E1 and the sixth rotation element E6. The magnitude of the second input torque Ti2 is determined according to the magnitude of the output torque of the second drive source 20 and the reduction ratio from the second drive source 20 to the third rotation element E3 and the fourth rotation element E4 (the first). 2 reduction ratio) and determined. In the present embodiment, the first gear G1 and the second gear G2 are formed to have the same diameter, the third gear G3 and the fifth gear G5 are formed to have the same diameter, and the fourth gear G4 and the sixth gear G6. Are formed to have the same diameter as each other, and the seventh gear G7 and the eighth gear G8 are formed to have the same diameter. Therefore, in the present embodiment, the first reduction ratio and the second reduction ratio are equal to each other. In the present embodiment, the seventh gear G7 is formed to have a diameter larger than that of the first ring gear R1, and the eighth gear G8 is formed to have a diameter larger than that of the second ring gear R2.

As described above, the first output member 3 is connected so as to rotate integrally with the first wheel W1, and the second output member 4 is connected so as to rotate integrally with the second wheel W2. Then, the second rotating element E2 is connected so as to rotate integrally with the first output member 3, and the fifth rotating element E5 is connected so as to rotate integrally with the second output member 4. Therefore, when the vehicle goes straight, the rotation speed of the second rotation element E2 and the rotation speed of the fifth rotation element E5 become equal, and the four rotation elements included in the planetary gear device 30 rotate at the same speed (that is, the planet). The gear device 30 does not perform differential operation). On the other hand, when the vehicle turns, as shown by an example in FIG. 4, four rotating elements included in the planetary gear device 30 rotate at different rotational speeds (that is, a state in which the planetary gear device 30 performs differential operation). It becomes. FIG. 4 shows a state in which the vehicle is turning in the direction in which the first wheel W1 becomes the inner wheel (the wheel on the side closer to the turning center).

As described above, the scene in which the planetary gear device 30 performs the differential operation (specifically, the scene in which the first planetary gear mechanism 31 and the second planetary gear mechanism 32 perform the differential operation) is limited to the time when the vehicle turns. To. As described above, in the present embodiment, the gears (R1, R2, S1, S2, P1, P2) constituting the first planetary gear mechanism 31 and the second planetary gear mechanism 32 are spur gears, but are planets. Since the scene where the gear device 30 performs the differential operation is limited to the time when the vehicle turns, it is possible to minimize the influence of gear noise that may occur when the planetary gear device 30 performs the differential operation. Further, by making each gear (R1, R2, S1, S2, P1, P2) constituting the first planetary gear mechanism 31 and the second planetary gear mechanism 32 a spur gear, the load received by each of these gears can be applied. It is also possible to simplify the configuration for supporting each of these gears in the axial direction L, mainly as a radial load. Further, in the vehicle drive device 1, two rotating elements (specifically, the second rotating element E2 and the fifth rotating element E5) are driven and connected to the output members (3, 4) in the planetary gear device 30. Is connected so as to rotate integrally with the output members (3, 4), so that the planetary gears are compared with the configuration in which the rotation of these two rotating elements is decelerated and transmitted to the output members (3, 4). The upper limit of the rotation speed of each rotating element of the device 30 can be kept low. This makes it easier to secure the performance (for example, durability, lubrication performance, etc.) required for the first planetary gear mechanism 31 and the second planetary gear mechanism 32.

Although details are omitted, in the example shown in FIG. 4, the first output torque To1 and the second output torque To2 are the first input torque Ti1 and the second, respectively, as shown in the following equations (1) and (2). 2 Determined according to the input torque Ti2.
To1 = Ti1 × (1-λ) / (1-2λ) -Ti2 × λ / (1-2λ) ... (1)
To2 = Ti2 × (1-λ) / (1-2λ) -Ti1 × λ / (1-2λ) ... (2)
From these equations (1) and (2), the following equation (3) can be obtained.
To1-To2 = {1 / (1-2λ)} × (Ti1-Ti2) ... (3)
As represented by this equation (3), the planetary gear device 30 amplifies the torque difference (Ti1-Ti2) of the input torque with the amplification factor of the value of {1 / (1-2λ)} to obtain the output torque. It is configured so that a torque difference (To1-To2) can be provided, which makes it possible to improve the running performance when the vehicle turns.

Next, the support configuration of each member of the vehicle drive device 1 of the present embodiment with respect to the case 60 will be described. As shown in FIG. 1, in the present embodiment, the case 60 includes a case portion having a portion exposed on the outer surface of the case 60, and a support member arranged inside the case 60. Specifically, the case 60 includes a plurality of case portions including a first case portion 61, a second case portion 62, a third case portion 63, a fourth case portion 64, and a fifth case portion 65, and a first case portion. It includes a plurality of support members including a support member 66 and a second support member 67.

As shown in FIG. 1, the first case portion 61 is joined to the second case portion 62 from the first side L1 in the axial direction. The first case portion 61 includes a peripheral wall portion formed in a tubular shape extending in the axial direction L, and in a space surrounded by the peripheral wall portion, a first drive source 10, a first transmission shaft 71, and a first counter gear mechanism are provided. 41, the first planetary gear mechanism 31, and the first output member 3 are housed. Then, the third case portion 63 is joined to the first case portion 61 from the axial first side L1 so as to close at least a part of this space from the axial first side L1. Further, the second case portion 62 includes a peripheral wall portion formed in a tubular shape extending in the axial direction L, and in a space surrounded by the peripheral wall portion, the second drive source 20, the second transmission shaft 72, and the second counter The gear mechanism 42, the second planetary gear mechanism 32, and the second output member 4 are housed. Then, the fourth case portion 64 is joined to the second case portion 62 from the axial second side L2 so as to close at least a part of this space from the axial second side L2.

The fifth case portion 65 is joined to each of the first case portion 61 and the second case portion 62 in a state of being sandwiched between the first case portion 61 and the second case portion 62 from both sides in the axial direction L. .. That is, the first case portion 61 and the second case portion 62 are joined to each other via the fifth case portion 65. The fifth case portion 65 is formed in a shape extending in a direction orthogonal to the axial direction L, and functions as an intermediate wall for partitioning the internal space of the case 60 in the axial direction L. The first drive source 10, the first transmission shaft 71, the first counter gear mechanism 41, the first planetary gear mechanism 31, and the first output member 3 are arranged on the first side L1 in the axial direction with respect to the fifth case portion 65. The second drive source 20, the second transmission shaft 72, the second counter gear mechanism 42, the second planetary gear mechanism 32, and the second output member 4 are arranged on the second side L2 in the axial direction with respect to the fifth case portion 65. It is located in.

The first support member 66 is fixed inside the first case portion 61, and the second support member 67 is fixed inside the second case portion 62. The first support member 66 is arranged on the first side L1 in the axial direction with respect to the fifth case portion 65, and the second support member 67 is arranged on the second side L2 in the axial direction with respect to the fifth case portion 65. There is.

In the present embodiment, regarding the arrangement position and shape of each member included in the vehicle drive device 1, the portion L1 on the first side in the axial direction with respect to the fifth case portion 65 in the vehicle drive device 1 and the vehicle drive device 1 The portion of the second side L2 in the axial direction with respect to the fifth case portion 65 in the above is a plane orthogonal to the axial direction L (specifically, the axial direction L in which the fifth case portion 65 is arranged). The plane orthogonal to the axial direction L at the position of) is set as a plane of symmetry, and is configured to have a mirror image symmetric relationship with each other.

As shown in FIGS. 1 and 2, the vehicle drive device 1 of the present embodiment has the first bearing B1, the second bearing B2, and the third bearing B3 as bearings for supporting each rotating member housed in the case 60. , 4th bearing B4, 5th bearing B5, 6th bearing B6, 7th bearing B7, 8th bearing B8, 9th bearing B9, 10th bearing B10, 11th bearing B11, 12th bearing B12, 13th bearing B13 , 14th bearing B14, 15th bearing B15, 16th bearing B16, 17th bearing B17, 18th bearing B18, 19th bearing B19, and 20th bearing B20. As described below, the first bearing B1 is a bearing arranged on the first side L1 in the axial direction with respect to the first gear G1 to support the first gear G1, and the second bearing B2 is the second gear G2. It is a bearing that is arranged on the second side L2 in the axial direction and supports the second gear G2. Further, the third bearing B3 is a bearing that supports the first connecting member 51, and the fourth bearing B4 is a bearing that supports the second connecting member 52.

As shown in FIGS. 1 and 2, the first shaft member 71a to which the first rotor 11 is fixed is the thirteenth bearing B13 and the fifteenth member arranged on the second side L2 in the axial direction with respect to the thirteenth bearing B13. It is rotatably supported at two locations in the axial direction L by the bearing B15. Here, the thirteenth bearing B13 is arranged on the first side L1 in the axial direction with respect to the first rotor 11, and the fifteenth bearing B15 is arranged on the second side L2 in the axial direction with respect to the first rotor 11. .. The first shaft member 71a is supported by the case 60 (here, the third case portion 63) via the thirteenth bearing B13, and the case 60 (here, the first case 60) is supported via the fifteenth bearing B15. It is supported by the case portion 61).

Further, the third shaft member 72a to which the second rotor 21 is fixed is provided with the 14th bearing B14 and the 16th bearing B16 arranged on the first side L1 in the axial direction with respect to the 14th bearing B14 in the axial direction L. It is rotatably supported in two places. Here, the 14th bearing B14 is arranged on the second side L2 in the axial direction with respect to the second rotor 21, and the 16th bearing B16 is arranged on the first side L1 in the axial direction with respect to the second rotor 21. .. The third shaft member 72a is supported by the case 60 (here, the fourth case portion 64) via the 14th bearing B14, and is supported by the case 60 (here, the second case portion 64) via the 16th bearing B16. It is supported by the case portion 62).

As shown in FIGS. 1 and 2, the second shaft member 71b on which the first gear G1 is formed is arranged on the first bearing B1 and the fifth side L2 in the axial direction with respect to the first bearing B1. It is rotatably supported at two locations in the axial direction L by the bearing B5. Here, the first bearing B1 is arranged on the first side L1 in the axial direction with respect to the first gear G1, and the fifth bearing B5 is arranged on the second side L2 in the axial direction with respect to the first gear G1. .. The second shaft member 71b is supported by the case 60 (here, the first case portion 61) via the first bearing B1 and the case 60 (here, the fifth case portion 61) via the fifth bearing B5. It is supported by the case portion 65). The first bearing B1 is formed on the outer peripheral surface of a portion of the second shaft member 71b that is arranged on the first side L1 in the axial direction with respect to the first gear G1 and on the case 60 (here, the first case portion 61). It is arranged between the inner peripheral surface of the bearing support. The first bearing B1 is arranged on the second side L2 in the axial direction with respect to the fifteenth bearing B15.

Further, the fourth shaft member 72b on which the second gear G2 is formed is formed by the second bearing B2 and the sixth bearing B6 arranged on the first side L1 in the axial direction with respect to the second bearing B2. It is rotatably supported in two places. Here, the second bearing B2 is arranged on the second side L2 in the axial direction with respect to the second gear G2, and the sixth bearing B6 is arranged on the first side L1 in the axial direction with respect to the second gear G2. .. The fourth shaft member 72b is supported by the case 60 (here, the second case portion 62) via the second bearing B2, and the case 60 (here, the fifth case portion 62) is supported via the sixth bearing B6. It is supported by the case portion 65). The second bearing B2 is formed on the outer peripheral surface of a portion of the fourth shaft member 72b that is arranged on the second side L2 in the axial direction with respect to the second gear G2, and on the case 60 (here, the second case portion 62). It is arranged between the inner peripheral surface of the bearing support. The second bearing B2 is arranged on the first side L1 in the axial direction with respect to the 16th bearing B16.

As shown in FIG. 2, the first counter shaft 41a connecting the third gear G3 and the fourth gear G4 is arranged on the 17th bearing B17 and the second side L2 in the axial direction with respect to the 17th bearing B17. It is rotatably supported at two locations in the axial direction L by the 19th bearing B19. Here, the 17th bearing B17 is arranged on the first side L1 in the axial direction with respect to the 3rd gear G3 and the 4th gear G4, and the 19th bearing B19 is a shaft with respect to the 3rd gear G3 and the 4th gear G4. It is arranged on the second side L2 in the direction. The first counter shaft 41a is supported by the case 60 (here, the first case portion 61) via the 17th bearing B17, and is supported by the case 60 (here, the fifth case portion 61) via the 19th bearing B19. It is supported by the case portion 65).

Further, the second counter shaft 42a connecting the fifth gear G5 and the sixth gear G6 includes the 18th bearing B18 and the 20th bearing B20 arranged on the first side L1 in the axial direction with respect to the 18th bearing B18. Therefore, it is rotatably supported at two points in the axial direction L. Here, the 18th bearing B18 is arranged on the second side L2 in the axial direction with respect to the 5th gear G5 and the 6th gear G6, and the 20th bearing B20 is a shaft with respect to the 5th gear G5 and the 6th gear G6. It is arranged on the first side L1 in the direction. The second counter shaft 42a is supported by the case 60 (here, the second case portion 62) via the 18th bearing B18, and is supported by the case 60 (here, the fifth case portion 62) via the 20th bearing B20. It is supported by the case portion 65).

As shown in FIG. 1, the first output member 3 is provided at two locations in the axial direction L by the ninth bearing B9 and the eleventh bearing B11 arranged on the second side L2 in the axial direction with respect to the ninth bearing B9. It is rotatably supported by. The first output member 3 is supported by the case 60 (here, the third case portion 63) via the ninth bearing B9, and is supported by the case 60 (here, the first case portion 63) via the eleventh bearing B11. It is supported by 61). Further, the second output member 4 is rotatably supported at two locations in the axial direction L by the tenth bearing B10 and the twelfth bearing B12 arranged on the first side L1 in the axial direction with respect to the tenth bearing B10. Has been done. The second output member 4 is supported by the case 60 (here, the fourth case portion 64) via the tenth bearing B10, and is supported by the case 60 (here, the second case portion 64) via the twelfth bearing B12. It is supported by 62).

As shown in FIG. 2, the first connecting member 51 is provided at two locations in the axial direction L by the third bearing B3 and the seventh bearing B7 arranged on the second side L2 in the axial direction with respect to the third bearing B3. It is rotatably supported by. The first connecting member 51 is supported by the case 60 (here, the first support member 66) via the third bearing B3, and the case 60 (here, the fifth case portion) via the seventh bearing B7. It is supported by 65). Further, the second connecting member 52 is rotatably supported at two locations in the axial direction L by the fourth bearing B4 and the eighth bearing B8 arranged on the first side L1 in the axial direction with respect to the fourth bearing B4. Has been done. The second connecting member 52 is supported by the case 60 (here, the second support member 67) via the fourth bearing B4, and is supported by the case 60 (here, the fifth case portion) via the eighth bearing B8. It is supported by 65).

As shown in FIG. 2, the first ring gear R1 rotates integrally with the first output member 3 via a third connecting member 53 arranged on the first side L1 in the axial direction with respect to the first carrier C1. Is connected to. Further, the second ring gear R2 is connected to the second carrier C2 via a fourth connecting member 54 arranged on the second side L2 in the axial direction so as to rotate integrally with the second output member 4. There is. In the present embodiment, the bearing that directly supports the first ring gear R1 is not provided, and the first ring gear R1 is indirectly supported by the case 60 via the first output member 3. Further, in the present embodiment, the bearing that directly supports the second ring gear R2 is not provided, and the second ring gear R2 is indirectly supported by the case 60 via the second output member 4. In the present embodiment, the first rotating element E1 meshed with and connected to the fourth gear G4 is the first carrier C1, and the first ring gear R1 is connected so as to rotate integrally with the first output member 3. A large load (load due to the meshing force of the gears) does not act on the first ring gear R1. Further, in the present embodiment, the fourth rotating element E4 meshed with and connected to the sixth gear G6 is the second carrier C2, and the second ring gear R2 is connected so as to rotate integrally with the second output member 4. Therefore, a large load (load due to the meshing force of the gears) does not act on the second ring gear R2. Therefore, it is possible to appropriately support the first ring gear R1 and the second ring gear R2 without providing a bearing that directly supports the first ring gear R1 and the second ring gear R2.

Next, the arrangement relationship of each member in the vehicle drive device 1 of the present embodiment will be described. As shown in FIGS. 1 and 2, the first gear G1 and the second gear G2 are arranged between the first drive source 10 and the second drive source 20 in the axial direction L in order from the first side L1 in the axial direction. Has been done. The fourth gear G4 is arranged on the first side L1 in the axial direction with respect to the third gear G3, and the sixth gear G6 is arranged on the second side L2 in the axial direction with respect to the fifth gear G5. As a result, it is easier to arrange the first drive source 10 closer to the second side L2 in the axial direction than when the fourth gear G4 is arranged on the second side L2 in the axial direction with respect to the third gear G3. At the same time, the second drive source 20 can be arranged closer to the first side L1 in the axial direction than when the sixth gear G6 is arranged on the first side L1 in the axial direction with respect to the fifth gear G5. It's easy. As a supplementary explanation, as an example of the case where the fourth gear G4 is arranged on the second side L2 in the axial direction with respect to the third gear G3, the first counter gear mechanism 41 of the present embodiment is inverted in the axial direction L. think of. In this case, as is clear from FIGS. 1 and 2, it is not easy to maintain the position of the first drive source 10 at the positions shown in FIGS. 1 and 2. For example, the first bearing B1 and its peripheral structure When the first drive source 10 is shifted to the first side L1 in the axial direction to a position where it does not interfere with the first counter gear mechanism 41, the entire device becomes larger in the axial direction L by that amount. On the other hand, in the vehicle drive device 1, since the fourth gear G4 is arranged on the first side L1 in the axial direction with respect to the third gear G3, the fourth gear G4 is an axis with respect to the third gear G3. Compared with the case where the first drive source 10 is arranged on the second side L2 in the direction, it is easier to arrange the first drive source 10 closer to the second side L2 in the axial direction. For the same reason, in this vehicle drive device 1, since the sixth gear G6 is arranged on the second side L2 in the axial direction with respect to the fifth gear G5, the sixth gear G6 is an axis with respect to the fifth gear G5. Compared with the case where the second drive source 20 is arranged on the first side L1 in the direction, it is easier to arrange the second drive source 20 closer to the first side L1 in the axial direction.

As shown in FIG. 2, in the present embodiment, the arrangement region of the first bearing B1 in the axial direction L and the arrangement region of the fourth gear G4 in the axial direction L overlap, and the arrangement region of the second bearing B2 in the axial direction L The arrangement area and the arrangement area of the sixth gear G6 in the axial direction L overlap. In the present embodiment, the fourth gear G4 is formed to have a smaller diameter than the third gear G3. Then, a space formed outside the third radial direction K3 (see FIG. 1) of the fourth gear G4 (in the axial direction along the axial direction L, the outer peripheral portion of the fourth gear G4 and the outer peripheral portion of the third gear G3 The first bearing B1 is arranged so that the arrangement areas of the fourth gear G4 and the axial direction L overlap each other by utilizing the space between them. Further, in the present embodiment, the sixth gear G6 is formed to have a smaller diameter than the fifth gear G5. Then, a space formed outside the third radial direction K3 of the sixth gear G6 (a space between the outer peripheral portion of the sixth gear G6 and the outer peripheral portion of the fifth gear G5 in the axial direction along the axial direction L). The second gear B2 is arranged so that the arrangement areas of the sixth gear G6 and the axial direction L overlap with each other.

Further, in the present embodiment, the arrangement area in the axial direction L of the 15th bearing B15 and the arrangement area in the axial direction L of the first counter shaft 41a overlap, and the arrangement area in the axial direction L of the 16th bearing B16 and The arrangement area of the second counter shaft 42a in the axial direction L overlaps. Here, the arrangement area of the 15th bearing B15 in the axial direction L and the arrangement area of the 17th bearing B17 in the axial direction L overlap, and the arrangement area of the 16th bearing B16 in the axial direction L and the 18th bearing B18 The arrangement area in the axial direction L overlaps.

As shown in FIG. 2, in the present embodiment, the first planetary gear mechanism 31 is arranged on the first side L1 in the axial direction with respect to the third gear G3, and the second planetary gear mechanism 32 is on the fifth gear G5. On the other hand, it is arranged on the second side L2 in the axial direction. The first connecting member 51 is arranged between the first planetary gear mechanism 31 and the third gear G3 in the axial direction L, and the second connecting member 51 is connected between the second planetary gear mechanism 32 and the fifth gear G5 in the axial direction L. The member 52 is arranged. Then, in the present embodiment, as shown in FIG. 5, the first planetary gear mechanism 31 is arranged so as to overlap the third gear G3 in the axial direction, and the second planetary gear mechanism 32 is arranged so as to overlap the third gear G3 in the axial direction. It is arranged so as to overlap with the fifth gear G5. Further, the first connecting member 51 having the seventh gear G7 formed on the outer peripheral portion is arranged so as to overlap the third gear G3 in the axial direction, and the second connecting member 51 having the eighth gear G8 formed on the outer peripheral portion. The 52 is arranged so as to overlap the fifth gear G5 in the axial direction. In FIG. 5, the reference pitch circle is shown by a chain double-dashed line for each gear, the outer shape of the first stator 12 is shown by a solid line for the first drive source 10, and the second stator 22 is shown for the second drive source 20. The outer shape is shown by a solid line.

In the present embodiment, the outer edge of the arrangement region of the first planetary gear mechanism 31 in the axial direction is defined so as to follow the reference pitch circle of the first ring gear R1, and the second planetary gear mechanism in the axial direction is defined. The outer edge of the arrangement region of 32 is defined to be along the reference pitch circle of the second ring gear R2. Not limited to this, for example, the outer edge of the arrangement region of the first planetary gear mechanism 31 in the axial direction is defined so that the first ring gear R1 is along the outer edge of the cylindrical member formed on the inner peripheral portion. The outer edge of the arrangement region of the second planetary gear mechanism 32 in the axial direction may be defined so that the second ring gear R2 is along the outer edge of the cylindrical member formed on the inner peripheral portion. Further, in the present embodiment, since the first drive source 10 and the second drive source 20 are inner rotor type rotary electric machines, the outer edge of the arrangement region of the first drive source 10 in the axial direction is the first stator 12 The outer edge of the arrangement region of the second drive source 20 in the axial direction is defined to be along the outer edge of the second stator 22.

In the present embodiment, all the bearings that support the rotating members arranged on the second axis A2 are arranged so as not to overlap with either the first drive source 10 or the second drive source 20 in the axial direction. .. In the present embodiment, the bearings that support the rotating member arranged on the second shaft A2 include the third bearing B3, the fourth bearing B4, the seventh bearing B7, the eighth bearing B8, the ninth bearing B9, and the tenth bearing. Eight bearings of bearing B10, eleventh bearing B11, and twelfth bearing B12 are included. All of these eight bearings are arranged so as not to overlap with any of the first drive source 10 and the second drive source 20 in the axial direction. That is, all the diameters of these eight bearings are set so as not to overlap with any of the first drive source 10 and the second drive source 20 in the axial direction. As described above, in the present embodiment, the bearing that supports the rotating member arranged on the second shaft A2 and in which the seventh gear G7 that meshes with the fourth gear G4 is formed (in this example, the first bearing). Supports the third bearing B3 and the seventh bearing B7) that support the connecting member 51, and the rotating member that is arranged on the second shaft A2 and has the eighth gear G8 that meshes with the sixth gear G6. The bearings (in this example, the fourth bearing B4 and the eighth bearing B8 that support the second connecting member 52) do not overlap with either the first drive source 10 or the second drive source 20 in the axial direction. Have been placed.

As shown in FIG. 5, in the present embodiment, the first planetary gear mechanism 31 is arranged so as not to overlap with the first drive source 10 in the axial direction, and the second planetary gear mechanism 32 is the second in the axial direction. 2 It is arranged so as not to overlap with the drive source 20. Then, as shown in FIG. 2, in the present embodiment, the arrangement region of the first drive source 10 in the axial direction L and the meshing of the gears in the first planetary gear mechanism 31 (specifically, the first planetary gear mechanism 31). The axial direction L arrangement area of the second drive source 20 overlaps with the axial direction L arrangement area of the second drive source 20, and the meshing of the gears in the second planetary gear mechanism 32 (specifically, the second planetary gear mechanism 32). Part) overlaps with the arrangement area in the axial direction L. Here, the first coil end portion 12b projecting to the second side L2 in the axial direction with respect to the first stator core 12a overlaps the meshing portion of the gear in the first planetary gear mechanism 31 and the arrangement region in the axial direction L. The second coil end portion 22b that is arranged and projects to the first side L1 in the axial direction with respect to the second stator core 22a overlaps the gear meshing portion and the arrangement region in the axial direction L in the second planetary gear mechanism 32. Have been placed.

In FIG. 5, the first drive source 10 is arranged so as to overlap the seventh gear G7 in the axial view, and the second drive source 20 is arranged so as to overlap the eighth gear G8 in the axial view. The first drive source 10 is arranged so as not to overlap with the seventh gear G7 in the axial view, and the second drive source 20 overlaps with the eighth gear G8 in the axial view. It may be configured so as not to be arranged.

As shown in FIG. 2, in the present embodiment, the first connecting member 51 is arranged on the second side L2 in the axial direction with respect to the first planetary gear mechanism 31. Then, the first connecting member 51 holds a portion (an end portion of the first pinion shaft 81 on the second side L2 in the axial direction) arranged on the second side L2 in the axial direction with respect to the first pinion gear P1 in the first carrier C1. It is connected to (in this example, spline connection). On the other hand, the portion of the first carrier C1 that is arranged on the first side L1 in the axial direction with respect to the first pinion gear P1 (the portion that holds the end of the first side L1 in the axial direction of the first pinion shaft 81) is the fifth. It is connected to the second sun gear S2 via a first connecting shaft 91 arranged so as to penetrate the case portion 65 in the axial direction L. The first connecting shaft 91 is located inside the second radial direction K2 (see FIG. 1) with respect to the first sun gear S1, the second sun gear S2, the first connecting member 51, and the second connecting member 52, in the axial direction L. It is arranged along. Here, the first connecting shaft 91 is integrally formed with the first carrier C1, and the second sun gear S2 is connected so as to rotate integrally with the first connecting shaft 91 (in this example, a spline connection). ) Has been.

In the present embodiment, the third bearing B3 is located inside the second radial direction K2 with respect to the seventh gear G7 in the radial direction (diametrical view along the second radial direction K2, the same applies hereinafter) to the seventh gear G7. It is arranged so as to overlap with. Specifically, in the portion of the first connecting member 51 extending in the second radial direction K2, the outer portion (outer portion) of the second radial direction K2 is relative to the inner portion (inner portion) of the second radial direction K2. It is formed so as to project toward the first side L1 in the axial direction, and at the boundary between these outer and inner portions on the end surface of the first side L1 in the axial direction of the first connecting member 51, the second radial direction K2 A stepped surface facing the inside of the surface is formed. The third bearing B3 is arranged between the stepped surface and the outer peripheral surface of the bearing support portion formed on the case 60 (here, the first support member 66). On the other hand, the seventh bearing B7 is arranged on the second side L2 in the axial direction with respect to the seventh gear G7.

Further, as shown in FIG. 2, in the present embodiment, the second connecting member 52 is arranged on the first side L1 in the axial direction with respect to the second planetary gear mechanism 32. Then, the second connecting member 52 holds a portion (an end portion of the second pinion shaft 82 on the first side L1 in the axial direction) arranged on the first side L1 in the axial direction with respect to the second pinion gear P2 in the second carrier C2. It is connected to (in this example, spline connection). Further, the second connecting member 52 is connected to the first sun gear S1 via a second connecting shaft 92 arranged so as to penetrate the fifth case portion 65 in the axial direction L. The second connecting shaft 92 is arranged along the axial direction L between the first connecting shaft 91 and the first connecting member 51 in the second radial direction K2 (see FIG. 1). Here, the second connecting shaft 92 is integrally formed with the first sun gear S1, and the second connecting member 52 is connected so as to rotate integrally with the second connecting shaft 92 (in this example, a spline). (Concatenated).

In the present embodiment, the fourth bearing B4 is inside the second radial direction K2 with respect to the eighth gear G8 in the radial direction (diametrical view along the second radial direction K2, the same applies hereinafter) to the eighth gear G8. It is arranged so as to overlap with. Specifically, in the portion of the second connecting member 52 extending in the second radial direction K2, the outer portion (outer portion) of the second radial direction K2 is relative to the inner portion (inner portion) of the second radial direction K2. The second connecting member 52 is formed so as to project toward the second side L2 in the axial direction, and the second radial direction K2 is formed at the boundary between the outer portion and the inner portion on the end surface of the second side L2 in the axial direction of the second connecting member 52. A stepped surface facing the inside of the surface is formed. The fourth bearing B4 is arranged between the stepped surface and the outer peripheral surface of the bearing support portion formed on the case 60 (here, the second support member 67). On the other hand, the eighth bearing B8 is arranged on the first side L1 in the axial direction with respect to the eighth gear G8.

By the way, as shown in FIGS. 1 and 2, in the present embodiment, the first counter gear mechanism 41 and the second counter gear mechanism 42 are located between the first drive source 10 and the second drive source 20 in the axial direction L. Is placed. The bearings that support the first counter gear mechanism 41 and the second counter gear mechanism 42 are arranged so as to overlap the first drive source 10 and the second drive source 20 in the axial direction. That is, the bearings that support the rotating members arranged on the third axis A3 are arranged so as to overlap the first drive source 10 and the second drive source 20 in the axial direction. In this regard, in the present embodiment, there are four bearings supporting the rotating member arranged on the third axis A3: the 17th bearing B17, the 18th bearing B18, the 19th bearing B19, and the 20th bearing B20. Only bearings. Therefore, the space in which the first counter gear mechanism 41, the second counter gear mechanism 42, and the bearings supporting them are arranged is kept small in the axial direction L, and the first drive source 10 and the second drive source 20 are pivoted. It is possible to arrange it close to the direction L.

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

(1) In the above embodiment, the third bearing B3 is located inside the second radial direction K2 with respect to the seventh gear G7 in a radial direction (a radial direction along the second radial direction K2, the same applies hereinafter). It is arranged so as to overlap the 7th gear G7, and the 4th bearing B4 is arranged inside the 2nd radial direction K2 with respect to the 8th gear G8 so as to overlap the 8th gear G8 in the radial direction. Was described as an example. However, without being limited to such a configuration, the third bearing B3 is arranged on the first side L1 in the axial direction with respect to the seventh gear G7 so as not to overlap with the seventh gear G7 in the radial direction. It can also be configured. Further, the fourth bearing B4 may be arranged on the second side L2 in the axial direction with respect to the eighth gear G8 so as not to overlap with the eighth gear G8 in the radial direction.

(2) In the above embodiment, the arrangement area of the first bearing B1 in the axial direction L and the arrangement area of the fourth gear G4 in the axial direction L overlap, and the arrangement area of the second bearing B2 in the axial direction L , The configuration in which the arrangement region of the sixth gear G6 in the axial direction L overlaps with each other has been described as an example. However, the configuration is not limited to such a configuration, and a configuration in which the arrangement region of the first bearing B1 in the axial direction L and the arrangement region of the fourth gear G4 in the axial direction L do not overlap, for example, the first bearing B1. It may be configured to be arranged on the first side L1 in the axial direction with respect to the fourth gear G4. Further, the arrangement region of the second bearing B2 in the axial direction L and the arrangement region of the sixth gear G6 in the axial direction L do not overlap, for example, the second bearing B2 is the second in the axial direction with respect to the sixth gear G6. It can also be configured to be arranged on the side L2.

(3) In the above embodiment, the first planetary gear mechanism 31 is arranged so as to overlap the third gear G3 in the axial direction, and the second planetary gear mechanism 32 is arranged with the fifth gear G5 in the axial direction. The configuration in which they are arranged so as to overlap is described as an example. However, without being limited to such a configuration, the first planetary gear mechanism 31 is arranged in a region different from the third gear G3 in the axial direction so as not to overlap with the third gear G3 in the axial direction. It can also be configured as such. Further, the second planetary gear mechanism 32 may be arranged in a region different from that of the fifth gear G5 in the axial direction so as not to overlap with the fifth gear G5 in the axial direction.

(4) In the above embodiment, the arrangement region of the first drive source 10 in the axial direction L and the arrangement region of the first planetary gear mechanism 31 in the axial direction L overlap, and the arrangement region of the second drive source 20 in the axial direction L The configuration in which the arrangement region of the second planetary gear mechanism 32 and the arrangement region of the second planetary gear mechanism 32 in the axial direction L overlap has been described as an example. However, the configuration is not limited to such a configuration, and the arrangement region of the first drive source 10 in the axial direction L and the arrangement region of the first planetary gear mechanism 31 in the axial direction L do not overlap, for example, the first configuration. The drive source 10 may be arranged on the first side L1 in the axial direction with respect to the first planetary gear mechanism 31. Further, the arrangement region of the second drive source 20 in the axial direction L and the arrangement region of the second planetary gear mechanism 32 in the axial direction L do not overlap, for example, the second drive source 20 is attached to the second planetary gear mechanism 32. On the other hand, it may be configured to be arranged on the second side L2 in the axial direction.

(5) In the above embodiment, the first planetary gear mechanism 31 is arranged so as not to overlap with the first drive source 10 in the axial direction, and the second planetary gear mechanism 32 is the second drive source in the axial direction. An example of a configuration in which the components are arranged so as not to overlap with 20 has been described. However, the configuration is not limited to such a configuration, and the first planetary gear mechanism 31 may be arranged so as to overlap with the first drive source 10 in the axial direction. Further, the second planetary gear mechanism 32 may be arranged so as to overlap with the second drive source 20 in the axial direction.

(6) In the above embodiment, all the bearings supporting the rotating member arranged on the second shaft A2 should not overlap with either the first drive source 10 or the second drive source 20 in the axial direction. The configuration to be arranged has been described as an example. However, without being limited to such a configuration, at least one of the bearings supporting the rotating member arranged on the second axis A2 may be the first drive source 10 and the second drive source 20 in the axial direction. It can also be configured so that it overlaps with at least one of them.

(7) In the above embodiment, the vehicle drive device 1 includes a first connecting member 51 that is connected so as to rotate integrally with the first rotating element E1, and a first connecting member 51 is provided on the outer peripheral portion of the first connecting member 51. The configuration in which the 7-gear G7 is formed has been described as an example. However, the configuration is not limited to such a configuration, and for example, the seventh gear G7 may be formed on the outer peripheral portion of the member constituting the first rotating element E1. In this case, it is preferable that the bearings supporting the members constituting the first rotating element E1 are arranged so as not to overlap with either the first drive source 10 or the second drive source 20 in the axial direction. Further, in the above embodiment, the vehicle drive device 1 is provided with a second connecting member 52 that is connected so as to rotate integrally with the fourth rotating element E4, and an eighth is provided on the outer peripheral portion of the second connecting member 52. The configuration in which the gear G8 is formed has been described as an example. However, the configuration is not limited to such a configuration, and for example, the eighth gear G8 may be formed on the outer peripheral portion of the member constituting the fourth rotating element E4. In this case, it is preferable that the bearings supporting the members constituting the fourth rotating element E4 are arranged so as not to overlap with either the first drive source 10 or the second drive source 20 in the axial direction.

(8) In the above embodiment, the first transmission shaft 71 includes a first shaft member 71a to which the first rotor 11 is fixed and a second shaft member 71b to which the first gear G1 is formed. It was explained as. However, without being limited to such a configuration, for example, the first transmission shaft 71 has the first rotor 11 fixed to the portion of the first side L1 in the axial direction and the first rotor 11 is fixed to the portion of the second side L2 in the axial direction. It is also possible to have a configuration including one shaft member on which one gear G1 is formed. In this case, for example, the first transmission shaft 71 is rotatably supported by the first bearing B1 and the thirteenth bearing B13 at two locations in the axial direction L, or the first transmission shaft 71 is the fifth. The bearing B5 and the thirteenth bearing B13 can be rotatably supported at two locations in the axial direction L.

Further, in the above embodiment, as an example, the second transmission shaft 72 includes a third shaft member 72a to which the second rotor 21 is fixed and a fourth shaft member 72b to which the second gear G2 is formed. explained. However, without being limited to such a configuration, for example, the second transmission shaft 72 has the second rotor 21 fixed to the portion of the second side L2 in the axial direction and the second rotor 21 is fixed to the portion of the first side L1 in the axial direction. It is also possible to have a configuration including one shaft member on which the two gears G2 are formed. In this case, for example, the second transmission shaft 72 is rotatably supported by the second bearing B2 and the 14th bearing B14 at two locations in the axial direction L, or the second transmission shaft 72 is the sixth. The bearing B6 and the 14th bearing B14 can be rotatably supported at two locations in the axial direction L.

(9) In the above embodiment, a configuration in which both the first drive source 10 and the second drive source 20 are rotary electric machines has been described as an example. However, without being limited to such a configuration, a drive source other than the rotary electric machine can be used as one or both of the first drive source 10 and the second drive source 20. As a drive source used in place of the rotary electric machine, for example, an internal combustion engine can be exemplified. An internal combustion engine is a prime mover (gasoline engine, diesel engine, etc.) that is driven by combustion of fuel inside the engine to extract power.

(10) The configurations disclosed in each of the above-described embodiments shall be applied in combination with the configurations disclosed in the other embodiments as long as there is no contradiction (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 embodiment]
Hereinafter, the outline of the vehicle drive device described above will be described.

A first drive source (10), a second drive source (20), a first output member (3) driven and connected to the first wheel (W1), and a second drive connected to the second wheel (W2). A vehicle drive device (1) including a two-output member (4) and a power transmission device (2), wherein the first drive source (10) and the second drive source (20) are second. The first output member (3) and the second output member (4) are arranged on one axis (A1), and are arranged on a second axis (A2) different from the first axis (A1). The power transmission device (2) has a first counter gear mechanism (41) and a second counter gear mechanism (41) arranged on a third axis (A3) different from the first axis (A1) and the second axis (A2), respectively. The first counter gear mechanism (42) is provided with a first planetary gear mechanism (31) and a second planetary gear mechanism (32) arranged on the second shaft (A2), respectively. 41) is a third gear (G3) that meshes with a first gear (G1) that rotates integrally with the first drive source (10), and a fourth gear that rotates integrally with the third gear (G3). The second counter gear mechanism (42) includes the second gear (G4), and the second counter gear mechanism (42) has a fifth gear (G5) that meshes with a second gear (G2) that rotates integrally with the second drive source (20). A first rotating element including a sixth gear (G6) that rotates integrally with the fifth gear (G5), and the first planetary gear mechanism (31) is meshed with and connected to the fourth gear (G4). The second planetary gear mechanism (32) includes (E1), a second rotating element (E2) that rotates integrally with the first output member (3), and a third rotating element (E3). , A fourth rotating element (E4) meshed with and connected to the sixth gear (G6), a fifth rotating element (E5) that rotates integrally with the second output member (4), and a sixth rotating element ( E6), and the first rotating element (E1) and the sixth rotating element (E6) are connected so as to rotate integrally, and the third rotating element (E3) and the fourth rotating element are connected. (E4) is connected so as to rotate integrally, and the side on which the first drive source (10) is arranged with respect to the second drive source (20) in the axial direction (L) is the first in the axial direction. The first drive source (L1) in the axial direction (L) is defined as the side (L1) and the side opposite to the first axial side (L1) in the axial direction (L) is defined as the second axial side (L2). The first gear (G1) and the second gear (G2) are arranged in this order from the first side (L1) in the axial direction between the second drive source (20) and the fourth gear. Gear (G4 ) Is arranged on the first side (L1) in the axial direction with respect to the third gear (G3), and the sixth gear (G6) is the second in the axial direction with respect to the fifth gear (G5). It is arranged on the side (L2).

According to this configuration, the first planetary gear mechanism (31) and the second planetary gear mechanism (32) are connected to form a planetary gear device (30) having four rotating elements as a whole, and the planetary gear device is formed. According to (30), the output torque of the first drive source (10) input via the first counter gear mechanism (41) and the second drive source (input via the second counter gear mechanism (42)). The output torque of 20) can be distributed to the first output member (3) and the second output member (4). Then, in the above configuration, the first axis (A1) in which the first drive source (10) and the second drive source (20) are arranged and the second axis (A2) in which the planetary gear device (30) is arranged. Power can be transmitted to and from the third axis (A3), which is different from the first axis (A1) and the second axis (A2). Therefore, while avoiding interference with the planetary gear device (30), as compared with the case where the power is transmitted between the first axis (A1) and the second axis (A2) without going through the other axes. It becomes easy to arrange the first drive source (10) and the second drive source (20) close to the axial direction (L), and as a result, it is possible to reduce the size of the entire device in the axial direction (L). it can.

Further, in the above configuration, between the first drive source (10) and the second drive source (20) in the axial direction (L), the first gear (G1) is sequentially arranged from the first side (L1) in the axial direction. The second gear (G2) is arranged, and the fourth gear (G4) is arranged on the first side (L1) in the axial direction with respect to the third gear (G3) that meshes with the first gear (G1). Since the gear (G6) is arranged on the second side (L2) in the axial direction with respect to the fifth gear (G5) that meshes with the second gear (G2), the size of the entire device in the axial direction (L) can be further reduced. You can do more. To give a supplementary explanation of this point, the limit position of the second side (L2) in the axial direction in which the first drive source (10) can be arranged is generally such that the first gear (G1) is arranged on the first side (L1) in the axial direction. As the result is increased, the position becomes the first side (L1) in the axial direction. For example, when a support structure such as a bearing is provided between the first drive source (10) and the first gear (G1) on the first shaft (A1), the first drive source (10) can be arranged. The limit position on the second side (L2) in the axial direction is a position separated from the first gear (G1) by at least the arrangement space of the support structure on the first side (L1) in the axial direction. Similarly, the limit position of the first side (L1) in the axial direction in which the second drive source (20) can be arranged is generally the axis as the second gear (G2) is arranged in the second side (L2) in the axial direction. It is the position on the second side (L2) of the direction.

In the above configuration, since the fourth gear (G4) is arranged on the first side (L1) in the axial direction with respect to the third gear (G3), the fourth gear (G4) is arranged with respect to the third gear (G3). The first gear (G1) can be arranged closer to the second side (L2) in the axial direction as compared with the case where it is arranged on the second side (L2) in the axial direction, and as a result, the first drive source (L2) It becomes easy to arrange 10) closer to the second side (L2) in the axial direction. Further, in the above configuration, since the sixth gear (G6) is arranged on the second side (L2) in the axial direction with respect to the fifth gear (G5), the sixth gear (G6) is the fifth gear (G5). The second gear (G2) can be arranged closer to the first side (L1) in the axial direction as compared with the case where it is arranged on the first side (L1) in the axial direction, and as a result, the second drive can be arranged. It becomes easy to arrange the source (20) closer to the first side (L1) in the axial direction. As described above, as a result of facilitating the arrangement of the first drive source (10) and the second drive source (20) closer to each other in the axial direction (L), the axial direction (L) of the entire apparatus is obtained. It is possible to further reduce the size of the product.

Here, the first planetary gear mechanism (31) is on the first side (L1) in the axial direction with respect to the third gear (G3), and the third in the axial direction along the axial direction (L). Arranged so as to overlap the gear (G3), the second planetary gear mechanism (32) is on the second side (L2) in the axial direction with respect to the fifth gear (G5), and is said in the axial view. It is preferable that the gears are arranged so as to overlap with the fifth gear (G5).

According to this configuration, the first planetary planet avoids interference between the first planetary gear mechanism (31) and the third gear (G3) and interference between the second planetary gear mechanism (32) and the fifth gear (G5). The second axis (A2) overlaps the third gear (G3) in the axial direction and the second planetary gear mechanism (32) overlaps the fifth gear (G5) in the axial direction. ) And the third axis (A3) can be arranged close to each other. Therefore, it is possible to reduce the size of the entire device in the direction (diameter direction) orthogonal to the axial direction (L).

Further, with bearings (B3, B7) that support the rotating member arranged on the second shaft (A2) and on which the seventh gear (G7) meshing with the fourth gear (G4) is formed. , The bearings (B4, B8) that support the rotating member arranged on the second shaft (A2) and on which the eighth gear (G8) meshing with the sixth gear (G6) is formed. It is preferable that the first drive source (10) and the second drive source (20) are arranged so as not to overlap each other in the axial direction along the axial direction (L).

According to this configuration, the first drive source (10) and the second drive source (20) are axially (20) while avoiding interference with the bearing supporting the rotating member arranged on the second axis (A2). It can be placed close to L). Therefore, it is possible to reduce the size of the entire device in the axial direction (L) while appropriately supporting the rotating member arranged on the second axis (A2).

Further, the first planetary gear mechanism (31) is arranged so as not to overlap with the first drive source (10) in an axial direction along the axial direction (L), and the second planetary gear mechanism (32) Is preferably arranged so as not to overlap with the second drive source (20) in the axial view.

According to this configuration, while avoiding interference between the first drive source (10) and the first planetary gear mechanism (31) and interference between the second drive source (20) and the second planetary gear mechanism (32), the first The first drive source (10) and the second drive source (20) can be arranged close to each other in the axial direction (L). Therefore, it is possible to reduce the size of the entire device in the axial direction (L).

As described above, the first planetary gear mechanism (31) is arranged so as not to overlap with the first drive source (10) in the axial view, and the second planetary gear mechanism (32) is arranged in the axial view. In a configuration in which the first drive source (20) is arranged so as not to overlap with the second drive source (20), the arrangement region of the first drive source (10) in the axial direction (L) and the first planetary gear mechanism (31). The axial direction (L) arrangement area overlaps, and the axial direction (L) arrangement area of the second drive source (20) and the axial direction (L) of the second planetary gear mechanism (32) It is preferable that the arrangement area of the above overlaps.

According to this configuration, the first drive is such that the axial direction (L) arrangement area of the first drive source (10) and the axial (L) arrangement area of the first planetary gear mechanism (31) overlap. The source (10) can be arranged closer to the second side (L2) in the axial direction, and the arrangement area in the axial direction (L) of the second drive source (20) and the axis of the second planetary gear mechanism (32). The second drive source (20) can be arranged closer to the first side (L1) in the axial direction so as to overlap the arrangement area in the direction (L). Therefore, the size of the entire device in the axial direction (L) can be further reduced.

In the vehicle drive device (1) having each of the above configurations, the first bearing is arranged on the first side (L1) in the axial direction with respect to the first gear (G1) and supports the first gear (G1). (B1) and a second bearing (B2) arranged on the second side (L2) in the axial direction with respect to the second gear (G2) to support the second gear (G2). The axial (L) arrangement area of the first bearing (B1) and the axial (L) arrangement area of the fourth gear (G4) overlap, and the shaft of the second bearing (B2) It is preferable that the arrangement area in the direction (L) and the arrangement area in the axial direction (L) of the sixth gear (G6) overlap.

According to this configuration, the first bearing (B1) overlaps the axial direction (L) arrangement area of the first bearing (B1) and the axial (L) arrangement area of the fourth gear (G4). Can be arranged closer to the second side (L2) in the axial direction, and accordingly, the first drive source (10) can be arranged closer to the second side (L2) in the axial direction. Further, the second bearing (B2) is placed in the axial direction so that the arrangement area of the second bearing (B2) in the axial direction (L) and the arrangement area of the sixth gear (G6) in the axial direction (L) overlap each other. It can be arranged closer to the 1 side (L1), and accordingly, the second drive source (20) can be arranged closer to the first side (L1) in the axial direction. Therefore, the size of the entire device in the axial direction (L) can be further reduced.

Further, the first connecting member (51) connected so as to rotate integrally with the first rotating element (E1) and the first connecting member (51) connected so as to rotate integrally with the fourth rotating element (E4). The two connecting members (52), the third bearing (B3) supporting the first connecting member (51), and the fourth bearing (B4) supporting the second connecting member (52) are provided. A seventh gear (G7) that meshes with the fourth gear (G4) is formed on the outer peripheral portion of the first connecting member (51), and the sixth gear (G6) is formed on the outer peripheral portion of the second connecting member (52). The eighth gear (G8) is formed so as to mesh with the seventh gear (G8), and the third bearing (B3) is radially inside the seventh gear (G7) in the radial direction along the radial direction. The fourth bearing (B4) is arranged so as to overlap the gear (G7), and the fourth bearing (B4) is inside the eighth gear (G8) in the radial direction, and the eighth gear (G8) in the radial view. It is preferable that they are arranged so as to overlap with.

According to this configuration, the output torque of the first drive source (10) transmitted via the first counter gear mechanism (41) is transmitted to the first rotating element (E1) via the first connecting member (51). Input and input the output torque of the second drive source (20) transmitted via the second counter gear mechanism (42) to the fourth rotating element (E4) via the second connecting member (52). Can be done. Then, in the above configuration, the third bearing (B3) supporting the first connecting member (51) is radially inward with respect to the seventh gear (G7) as the seventh gear (G7). The fourth bearing (B4), which is arranged so as to overlap and supports the second connecting member (52), is radially inward with respect to the eighth gear (G8) with the eighth gear (G8). Arranged so that they overlap. Therefore, the first connecting member (51) is arranged so as to be supported by the third bearing (B3) while reducing the size of the entire device in the axial direction (L), and is supported by the fourth bearing (B4). The second connecting member (52) can be arranged so as to be.

Further, in the above configuration, the object to be supported by the third bearing (B3) is the first connecting member (51) which is a separate member from the member constituting the first rotating element (E1). The third bearing (B3) has a shape that allows the diameter of the third bearing (B3) to be kept smaller than when the object to be supported by the bearing (B3) is a member constituting the first rotating element (E1). It is easy to form the support object of B3). Further, in the above configuration, the object to be supported by the fourth bearing (B4) is the second connecting member (52), which is a separate member from the member constituting the fourth rotating element (E4). The fourth bearing (B4) has a shape that can reduce the diameter of the fourth bearing (B4) as compared with the case where the supporting object of the bearing (B4) is a member constituting the fourth rotating element (E4). It is easy to form the support object of B4). Therefore, according to the above configuration, it is possible to reduce the cost by keeping the diameters of the third bearing (B3) and the fourth bearing (B4) small.

Further, the first planetary gear mechanism (31) includes a carrier (C1) which is the first rotating element (E1), a ring gear (R1) which is the second rotating element (E2), and the third rotating element. It is a double pinion type planetary gear mechanism including a sun gear (S1) which is (E3), and the second planetary gear mechanism (32) is a carrier (C2) which is the fourth rotating element (E4). A double pinion type planetary gear mechanism including the ring gear (R2) which is the fifth rotating element (E5) and the sun gear (S2) which is the sixth rotating element (E6) is preferable.

In this configuration, the first rotating element (E1) meshed with and connected to the fourth gear (G4) is the carrier (C1) of the first planetary gear mechanism (31), so that the first rotating element (E1) is Compared to the case where the ring gear (R1) of the first planetary gear mechanism (31) is used, a member forming a gear that meshes with the fourth gear (G4) (a member constituting the first rotating element (E1), or the member thereof. It becomes easy to keep the diameter of the bearing that supports the member) to be small. Further, in the above configuration, the fourth rotating element (E4) meshed with and connected to the sixth gear (G6) is used as the carrier (C2) of the second planetary gear mechanism (32), so that the fourth rotating element ( Compared to the case where E4) is the ring gear (R2) of the second planetary gear mechanism (32), a member (a member constituting the fourth rotating element (E4)) in which a gear meshing with the sixth gear (G6) is formed. , Or a member connected to the member), and the diameter of the bearing supporting the member) can be easily suppressed to a small size. As a result, the cost can be reduced.

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: Power transmission device 3: First output member 4: Second output member 10: First drive source 20: Second drive source 31: First planetary gear mechanism 32: Second planetary gear mechanism 41 : 1st counter gear mechanism 42: 2nd counter gear mechanism 51: 1st connecting member 52: 2nd connecting member A1: 1st axis A2: 2nd axis A3: 3rd axis B1: 1st bearing B2: 2nd bearing B3: 3rd gear B4: 4th gear E1: 1st rotating element E2: 2nd rotating element E3: 3rd rotating element E4: 4th rotating element E5: 5th rotating element E6: 6th rotating element G1: 1st Gear G2: 2nd gear G3: 3rd gear G4: 4th gear G5: 5th gear G6: 6th gear G7: 7th gear G8: 8th gear L: Axial direction L1: Axial direction 1st side L2: Shaft Direction 2nd side W1: 1st wheel W2: 2nd wheel

Claims (8)

For vehicles including a first drive source, a second drive source, a first output member that is driven and connected to the first wheel, a second output member that is driven and connected to the second wheel, and a power transmission device. It ’s a drive device,
The first drive source and the second drive source are arranged on the first axis.
The first output member and the second output member are arranged on a second axis different from the first axis.
The power transmission device is arranged on a first counter gear mechanism and a second counter gear mechanism, which are arranged on the first axis and a third axis different from the second axis, and on the second axis, respectively. It is equipped with a first planetary gear mechanism and a second planetary gear mechanism.
The first counter gear mechanism includes a third gear that meshes with a first gear that rotates integrally with the first drive source, and a fourth gear that rotates integrally with the third gear.
The second counter gear mechanism includes a fifth gear that meshes with a second gear that rotates integrally with the second drive source, and a sixth gear that rotates integrally with the fifth gear.
The first planetary gear mechanism includes a first rotating element meshed with and connected to the fourth gear, a second rotating element that rotates integrally with the first output member, and a third rotating element.
The second planetary gear mechanism includes a fourth rotating element meshed with and connected to the sixth gear, a fifth rotating element that rotates integrally with the second output member, and a sixth rotating element.
The first rotating element and the sixth rotating element are connected so as to rotate integrally.
The third rotating element and the fourth rotating element are connected so as to rotate integrally.
The side where the first drive source is arranged with respect to the second drive source in the axial direction is defined as the first side in the axial direction, and the side opposite to the first side in the axial direction in the axial direction is defined as the second side in the axial direction. ,
The first gear and the second gear are arranged in order from the first side in the axial direction between the first drive source and the second drive source in the axial direction.
The fourth gear is arranged on the first side in the axial direction with respect to the third gear.
The sixth gear is a vehicle drive device arranged on the second side in the axial direction with respect to the fifth gear. The first planetary gear mechanism is arranged on the first side in the axial direction with respect to the third gear so as to overlap the third gear in an axial view along the axial direction.
The vehicle according to claim 1, wherein the second planetary gear mechanism is arranged on the second side in the axial direction with respect to the fifth gear so as to overlap the fifth gear in the axial direction. Drive device. A bearing that supports a rotating member that is arranged on the second shaft and has a seventh gear that meshes with the fourth gear, and a rotating member that is arranged on the second shaft. The bearing that supports the rotating member on which the eighth gear that meshes with the sixth gear is formed is arranged so as not to overlap with either the first drive source or the second drive source in the axial view along the axial direction. The vehicle drive device according to claim 1 or 2. The first planetary gear mechanism is arranged so as not to overlap with the first drive source in an axial view along the axial direction.
The vehicle drive device according to any one of claims 1 to 3, wherein the second planetary gear mechanism is arranged so as not to overlap with the second drive source in the axial direction. The axial arrangement area of the first drive source and the axial arrangement area of the first planetary gear mechanism overlap with each other.
The vehicle drive device according to claim 4, wherein the axial arrangement region of the second drive source and the axial arrangement region of the second planetary gear mechanism overlap. A first bearing arranged on the first side in the axial direction with respect to the first gear to support the first gear, and the second gear arranged on the second side in the axial direction with respect to the second gear. With a second bearing to support,
The axial arrangement area of the first bearing and the axial arrangement area of the fourth gear overlap with each other.
The vehicle drive device according to any one of claims 1 to 5, wherein the axially arranged area of the second bearing and the axially arranged area of the sixth gear overlap. A first connecting member connected so as to rotate integrally with the first rotating element, a second connecting member connected so as to rotate integrally with the fourth rotating element, and the first connecting member. A third bearing for supporting and a fourth bearing for supporting the second connecting member are provided.
A seventh gear that meshes with the fourth gear is formed on the outer peripheral portion of the first connecting member.
An eighth gear that meshes with the sixth gear is formed on the outer peripheral portion of the second connecting member.
The third bearing is arranged inside the seventh gear in the radial direction so as to overlap the seventh gear in a radial direction along the radial direction.
According to any one of claims 1 to 6, the fourth bearing is arranged inside the eighth gear in the radial direction so as to overlap the eighth gear in the radial direction. The vehicle drive device described. The first planetary gear mechanism is a double pinion type planetary gear mechanism including a carrier which is the first rotating element, a ring gear which is the second rotating element, and a sun gear which is the third rotating element. ,
The second planetary gear mechanism is a double pinion type planetary gear mechanism including the carrier which is the fourth rotating element, the ring gear which is the fifth rotating element, and the sun gear which is the sixth rotating element. , The vehicle drive device according to any one of claims 1 to 7.

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