Vehicle drive unit

Abstract

To provide a vehicle drive device capable of supplying oil properly to a lubrication object part, even in a state in which an output member does not rotate.SOLUTION: A vehicle drive device 100 comprises: an input member which is provided on a first axis A1; an output member; first rotary electrical machinery 1; second rotary electrical machinery 2; and a power transmission mechanism for transmitting power between the pieces of rotary electrical machinery. An object rotary electrical machinery being any one of the pieces of first and second rotary electrical machinery 1, 2, is arranged on a second axis A2 which is parallel to the first axis A1 and is above V1 of the first axis A1. The vehicle drive device 100 has: a first oil reception part 7 which is arranged below V2 of the object rotary electrical machine, and receives oil falling from the object rotary electrical machine; and a first oil supply path 70 for supplying the oil accumulated on the first oil reception part 7 to a first bearing which supports the input member and an input gear G10 which integrally rotates with the input member.SELECTED DRAWING: Figure 3

Description

[Technical Field]

[0001] The present invention relates to a vehicle drive device including an input member drivingly connected to an internal combustion engine, two rotating electric machines, an output member, and a power transmission mechanism that transmits power among them. [Background technology]

[0002] Japanese Patent Application Laid-Open Publication No. 2017-114477 (Patent Document 1) discloses a technology for lubrication of a vehicle drive system in a hybrid vehicle equipped with an internal combustion engine and two rotating electric machines. This vehicle is equipped with an oil pump (electric oil pump) driven by a drive power source separate from the drive power source for the wheels, and some mechanisms of the vehicle drive system are lubricated by oil supplied from this oil pump. This also includes the case where oil lubricating one gear is used to lubricate other parts to be lubricated, such as other gears. For example, it is possible to configure the system so that oil scooped up by the rotating gears lubricates other parts to be lubricated. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Laid-Open No. 2017-114477 Summary of the Invention [Problem to be solved by the invention]

[0004] In hybrid vehicles equipped with an internal combustion engine and a rotating electric machine, the internal combustion engine may rotate the rotating electric machine to generate electricity while the wheels are stopped. In this case, the power transmission mechanism is controlled so that the gears that drive the wheels do not rotate. As a result, oil is not supplied to the lubrication target areas that are supplied with lubricating oil by the oil pump, which may result in insufficient lubrication. Providing a separate oil supply path from the oil pump would complicate the structure of the vehicle drive system and may also require a higher oil pump discharge capacity.

[0005] In view of the above background, it is desirable to realize a vehicle drive device that can appropriately supply oil to parts to be lubricated even when the output member is not rotating. [Means for solving the problem]

[0006] In view of the above, a vehicle drive device includes an input member drivingly connected to an internal combustion engine, an output member drivingly connected to wheels, a first rotating electric machine, a second rotating electric machine, and a power transmission mechanism that changes a power transmission state between the input member, the output member, the first rotating electric machine, and the second rotating electric machine to transmit power therebetween, wherein an operating mode in which a driving force is transmitted between the input member and the first rotating electric machine and between the second rotating electric machine and the output member is defined as a series mode, and an operating mode in which a driving force is transmitted between the input member, the second rotating electric machine, and the output member is defined as a parallel mode, and the power transmission mechanism is configured to switch between at least the series mode and the parallel mode. a first oil receiving portion disposed below the target rotating electric machine so as to receive cooling oil that is supplied to the target rotating electric machine from an oil pump that operates independently of the wheels and that drops from the target rotating electric machine; and a first oil supply passage that supplies the oil that has accumulated in the first oil receiving portion to a first bearing that supports the input member and an input gear that rotates integrally with the input member.

[0007] According to this configuration, the provision of the first oil receiving portion allows for effective collection of oil that flows down after being supplied from the oil pump and cooling the target rotating electric machine. Furthermore, the provision of the first oil supply passage allows for the oil stored in the first oil receiving portion to be supplied to the lubrication target parts. Since power generation can be performed even when the wheels are stopped, some gears constituting the power transmission mechanism do not rotate. However, the input member and input gear drivingly connected to the internal combustion engine rotate to supply mechanical energy to the rotating electric machine, for example, when the rotating electric machine is operated as a generator. As described above, by enabling the supply of oil to the first bearing and input gear supporting the input member, these can be appropriately lubricated. In other words, this configuration allows for the realization of a vehicle drive device that can appropriately supply oil to the first bearing and input gear, which are the lubrication target parts, even when the output member is not rotating.

[0008] Further features and advantages of the vehicle drive device will become apparent from the following description of exemplary, non-limiting embodiments which are given with reference to the drawings. [Brief explanation of the drawings]

[0009] [Figure 1] Skeleton diagram of a vehicle drive system [Figure 2] Partial cross-sectional view of a vehicle drive device [Figure 3] Schematic cross-sectional view of the first chamber viewed from the side facing the partition wall along the axial direction [Figure 4] Schematic cross-sectional view of the second chamber viewed from the side facing the partition wall along the axial direction [Figure 5] Partially enlarged perspective view of the first oil receiving portion in the main body case [Figure 6] Partially enlarged perspective view of the second oil receiving portion in the main body case [Figure 7] Partially enlarged perspective view of the second oil receiving portion in the transmission mechanism side cover case [Figure 8] 10 is a schematic cross-sectional view showing another example of the configuration of the first oil receiving portion, as viewed from the side facing the partition wall along the axial direction of the first chamber. DETAILED DESCRIPTION OF THE INVENTION

[0010] Hereinafter, an embodiment of a vehicle drive device will be described with reference to the drawings. Note that the directions of each component in the following description refer to the direction when the component is assembled in the vehicle drive device. Furthermore, terms relating to the dimensions, arrangement direction, arrangement position, etc. of each component are concepts that include differences due to errors (errors within the tolerances of manufacturing).

[0011] In this specification, "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 includes a state in which the two rotating elements are connected so as to rotate integrally, or a state in which the two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members. Such transmission members include various members (e.g., shafts, gear mechanisms, belts, chains, etc.) that transmit rotation at the same speed or at variable speeds, and may also include engagement devices (e.g., friction engagement devices, meshing engagement devices, etc.) that selectively transmit rotation and driving force.

[0012] In this specification, the term "rotating electric machine" is used to refer to a motor (electric motor), a generator (electric generator), and a motor-generator that functions as both a motor and a generator as needed. In this specification, the phrase "overlaps when viewed from a specific direction" in relation to the arrangement of two components means that when an imaginary line parallel to the line of sight is moved in directions perpendicular to the imaginary line, there is at least a portion of an area where the imaginary line intersects with both of the two components. In this specification, the phrase "axial arrangement areas overlap" in relation to the arrangement of two components means that the axial arrangement area of ​​one component includes at least a portion of the axial arrangement area of ​​the other component.

[0013] As shown in Fig. 1, a vehicle drive device 100 includes a first rotating electric machine 1, a second rotating electric machine 2, a first input member 11 drivingly connected to an internal combustion engine 3, an output member 5 drivingly connected to wheels 4, a second input member 12 drivingly connected to the second rotating electric machine 2, and a third input member 13 drivingly connected to the first rotating electric machine 1. The internal combustion engine 3 is a prime mover (e.g., a gasoline engine, a diesel engine, etc.) that is driven by combustion of fuel inside the engine to extract power. The first rotating electric machine 1 and the second rotating electric machine 2 are electrically connected to an electric storage device (not shown), such as a battery or a capacitor, and are powered by receiving a supply of electric power from the electric storage device, or are supplied with electric power generated by the inertial force of the vehicle or the driving force of the internal combustion engine 3, and stored in the electric storage device. The first rotating electric machine 1 and the second rotating electric machine 2 are electrically connected to a common power storage device, and the second rotating electric machine 2 can be powered by the electric power generated by the first rotating electric machine 1.

[0014] In this embodiment, the third input member 13 is connected to the first rotating electric machine 1 (specifically, a rotor included in the first rotating electric machine 1; the same applies hereinafter) so as to rotate integrally therewith, and the second input member 12 is connected to the second rotating electric machine 2 (specifically, a rotor included in the second rotating electric machine 2; the same applies hereinafter) so as to rotate integrally therewith. Also, in this embodiment, the first input member 11 is connected to the internal combustion engine 3 (specifically, an output member such as a crankshaft included in the internal combustion engine 3; the same applies hereinafter) via a torque limiter TL (see FIG. 2). The torque limiter TL limits the magnitude of torque transmitted between the first input member 11 and the internal combustion engine 3 to prevent excessive torque from being transmitted. When a damper device with a torque limiter TL (a damper device including a damper mechanism and the torque limiter TL) is used, the first input member 11 is connected to the internal combustion engine 3 via the torque limiter TL and the damper mechanism.

[0015] As shown in FIG. 2, the vehicle drive device 100 includes a case 9, and a first input member 11, a second input member 12, and a third input member 13 are housed in the case 9. Here, "house" means to house at least a portion of an object to be housed. Each of the first input member 11, the second input member 12, and the third input member 13 is supported by the case 9 so as to be rotatable relative to the case 9. The case 9 also houses a differential gear unit 6, a first counter gear mechanism 31, and a second counter gear mechanism 32, which will be described later.

[0016] 2, the case 9 includes a first chamber 91 that houses the first rotating electric machine 1 and the second rotating electric machine 2, and a second chamber 92 that houses the power transmission mechanism 20. The first chamber 91 and the second chamber 92 are separated by a partition wall 95. The case 9 includes a main body case 97 on which the partition wall 95 is formed, a rotating electric machine side cover case (not shown) that abuts against the main body case 97 from a first axial side L1 to form the first chamber 91 together with the main body case 97, and a transmission mechanism side cover case 96 that abuts against the main body case 97 from a second axial side L2 to form the second chamber 92 together with the main body case 97.

[0017] The vehicle drive device 100 includes a differential gear device 6. As shown in FIG. 1 , the differential gear device 6 includes a differential input gear GD, and distributes rotation of the differential input gear GD to a pair of output members 5 that are drivingly connected to wheels 4, respectively. If the wheel 4 to which one output member 5 is drivingly connected is defined as a first wheel, and the wheel 4 to which the other output member 5 is drivingly connected is defined as a second wheel, the first wheel and the second wheel are a pair of left and right wheels 4 (for example, a pair of left and right front wheels, or a pair of left and right rear wheels). In this embodiment, the output members 5 are drive shafts, and each output member 5 is connected to the wheel 4 to be connected so as to rotate at the same speed as the wheel 4. The output member 5 is connected to the wheel 4 to be connected via, for example, a constant velocity joint (not shown). The wheel 4 is driven by torque transmitted via the output member 5, causing the vehicle (a vehicle on which the vehicle drive device 100 is mounted; the same applies hereinafter) to run.

[0018] 2, in this embodiment, the differential gear device 6 includes a bevel gear type differential gear mechanism 40 and a differential case 41 that houses the differential gear mechanism 40. The differential case 41 is supported on the case 9 so as to be rotatable relative to the case 9. The differential input gear GD is connected to the differential case 41 so as to rotate integrally with the differential case 41. Specifically, the differential input gear GD is attached to the differential case 41 so as to protrude outward from the differential case 41 in the radial direction (the radial direction based on a fourth axis A4 described later).

[0019] The differential gear mechanism 40 includes a pinion gear 43 and a pair of side gears 44 that mesh with the pinion gear 43. The pinion gears 43 (for example, two pinion gears 43) are supported on a pinion shaft 42 that is held in a differential case 41 so as to be rotatable relative to the pinion shaft 42. The differential gear mechanism 40 distributes the rotation of the differential input gear GD to the pair of side gears 44. Each of the side gears 44 is coupled (spline-coupled in this case) to the output member 5 to be coupled thereto so as to rotate integrally with the output member 5.

[0020] As shown in FIGS. 1 and 2, the first input member 11 is disposed on the first axis A1, the second input member 12 is disposed on the second axis A2, the third input member 13 is disposed on the third axis A3, the differential gear unit 6 is disposed on the fourth axis A4, a first counter gear mechanism 31 (described later) is disposed on the fifth axis A5, and a second counter gear mechanism 32 (described later) is disposed on the sixth axis A6. The first axis A1, the second axis A2, the third axis A3, the fourth axis A4, the fifth axis A5, and the sixth axis A6 are different axes (virtual axes) and disposed parallel to one another. The direction parallel to each of these axes (A1 to A6) (i.e., the axial direction common to each axis) is defined as the axial direction L. One side of the axial direction L is defined as the first axial side L1, and the other side of the axial direction L (the opposite side of the first axial side L1 in the axial direction L) is defined as the second axial side L2.

[0021] 1, the first input member 11 is disposed on a first axial side L1 relative to the internal combustion engine 3. The third input member 13 is disposed on a second axial side L2 relative to the first rotating electric machine 1, and the second input member 12 is disposed on the second axial side L2 relative to the second rotating electric machine 2.

[0022] As shown in FIG. 1 , the vehicle drive device 100 includes a first gear mechanism 21 that drivingly couples a first input member 11 and a third input member 13 and also couples the first input member 11 and a differential input gear GD. The first gear mechanism 21 drivingly couples the third input member 13 and the differential input gear GD via the first input member 11. That is, the first gear mechanism 21 transmits driving force between the first input member 11, which is drivingly coupled to the internal combustion engine 3, and the first rotating electric machine 1. The first gear mechanism 21 can connect a first power transmission path, which is a power transmission path between the third input member 13 and the first input member 11, and a third power transmission path, which is a power transmission path between the first input member 11 and the differential input gear GD. The third power transmission path is selectively connected (i.e., connected or disconnected) by a first switching mechanism 51, which will be described later. On the other hand, in this embodiment, the first power transmission path is always connected.

[0023] The vehicle drive device 100 also includes a second gear mechanism 22 that drivingly couples the second input member 12 and the differential input gear GD. The second gear mechanism 22 drivingly couples the second input member 12 and the differential input gear GD without the first gear mechanism 21. A second power transmission path, which is a power transmission path between the second input member 12 and the differential input gear GD, can be connected using the second gear mechanism 22. That is, the second gear mechanism 22 transmits driving force between the second rotating electric machine 2 and the output member 5. In this embodiment, the second power transmission path is selectively connected by a second switching mechanism 52, which will be described later.

[0024] With the third power transmission path disconnected and the second power transmission path connected, the vehicle drive device 100 can achieve an electric driving mode and a series mode. The electric driving mode is a driving mode in which the output member 5 is driven by the driving force of the second rotating electric machine 2 to drive the vehicle. The series mode is a driving mode in which the first rotating electric machine 1 generates electricity by the driving force of the internal combustion engine 3 and the output member 5 is driven by the driving force of the second rotating electric machine 2 to drive the vehicle. In the electric driving mode and the series mode, the third power transmission path is disconnected and the first rotating electric machine 1 and the internal combustion engine 3 are separated from the output member 5.

[0025] Furthermore, with the second power transmission path and the third power transmission path connected, the vehicle drive device 100 can achieve a parallel mode. The parallel mode is a driving mode in which the output member 5 is driven by at least the driving force of the internal combustion engine 3 to drive the vehicle. In the parallel mode, the driving force of the second rotating electric machine 2 is transmitted to the output member 5 as needed to supplement the driving force of the internal combustion engine 3. When the second rotating electric machine 2 is stopped in the parallel mode (for example, when the vehicle is traveling at high speed), the second rotating electric machine 2, which is drivingly connected to the differential input gear GD without passing through the first input member 11, can be disconnected from the differential input gear GD by interrupting the second power transmission path. Therefore, when the second rotating electric machine 2 is stopped in the parallel mode, co-rotation of the second rotating electric machine 2 can be avoided, and as a result, energy loss due to dragging of the second rotating electric machine 2 can be suppressed. In addition, in the parallel mode, the driving force of the first rotating electric machine 1 may be transmitted to the output member 5 in addition to or instead of the driving force of the second rotating electric machine 2, thereby assisting the driving force of the internal combustion engine 3.

[0026] The first gear mechanism 21 and the second gear mechanism 22 correspond to the power transmission mechanism 20 that changes the power transmission state between the third input member 13, the output member 5, the first rotating electric machine 1, and the second rotating electric machine 2, and transmits power therebetween. As described above, the series mode is an operation mode in which a driving force is transmitted between the first input member 11 and the first rotating electric machine 1, and a driving force is transmitted between the second rotating electric machine 2 and the output member 5. The parallel mode is an operation mode in which a driving force is transmitted between the first input member 11, the second rotating electric machine 2, and the output member 5. The power transmission mechanism 20 is capable of operating in at least two operation modes: the series mode and the parallel mode.

[0027] 1, the first gear mechanism 21 includes a third input gear G9 (ninth gear) arranged coaxially with the third input member 13, and a first input gear G10 (tenth gear) arranged coaxially with the first input member 11 and meshing with the third input gear G9. In this embodiment, the third input gear G9 is connected to the third input member 13 so as to rotate integrally therewith, and the first input gear G10 is connected to the first input member 11 so as to rotate integrally therewith. That is, in this embodiment, the third input member 13 and the first input member 11 are constantly connected to each other via the gear pair of the third input gear G9 and the first input gear G10, and therefore the first power transmission path between the third input member 13 and the first input member 11 is constantly connected.

[0028] 1 and 2, in this embodiment, the third input gear G9 is formed to have a smaller diameter than the first input gear G10. That is, the gear ratio between the third input gear G9 and the first input gear G10 is set so that the rotation of the third input member 13 is decelerated before being transmitted to the first input member 11 (in other words, so that the rotation of the first input member 11 is accelerated before being transmitted to the third input member 13).

[0029] The first gear mechanism 21 further includes a first gear G1 and a second gear G2, each of which is coaxially disposed with the first input member 11, and a first counter gear mechanism 31. The first gear G1 is disposed on a first axial side L1 relative to the second gear G2. The first counter gear mechanism 31 includes a first counter shaft 31a, a third gear G3 meshing with the first gear G1, a fourth gear G4 meshing with the second gear G2, and a fifth gear G5 rotating integrally with the first counter shaft 31a and meshing with the differential input gear GD. The third gear G3 is disposed on the first axial side L1 relative to the fourth gear G4. In this embodiment, the fifth gear G5 is disposed between the third gear G3 and the fourth gear G4 in the axial direction L.

[0030] 1 and 2, in this embodiment, the fifth gear G5 is formed to have a smaller diameter than the differential input gear GD. That is, the gear ratio between the fifth gear G5 and the differential input gear GD is set so that the rotation of the first counter shaft 31a is decelerated and transmitted to the differential gear device 6 (specifically, the differential input gear GD).

[0031] The first gear mechanism 21 is provided with a first switching mechanism 51 that switches between a state in which driving force is transmitted between the first input member 11 and the first countershaft 31a via a first gear pair GP1 consisting of a first gear G1 and a third gear G3, a state in which driving force is transmitted between the first input member 11 and the first countershaft 31a via a second gear pair GP2 consisting of a second gear G2 and a fourth gear G4, and a state in which driving force is not transmitted between the first input member 11 and the first countershaft 31a.

[0032] Hereinafter, the state in which a driving force is transmitted between the first input member 11 and the first countershaft 31a via the first gear pair GP1 (i.e., the state in which the first input member 11 and the first countershaft 31a are connected via the first gear pair GP1) will be referred to as the "first connected state." Furthermore, the state in which a driving force is transmitted between the first input member 11 and the first countershaft 31a via the second gear pair GP2 (i.e., the state in which the first input member 11 and the first countershaft 31a are connected via the second gear pair GP2) will be referred to as the "second connected state." Furthermore, the state in which a driving force is not transmitted between the first input member 11 and the first countershaft 31a will be referred to as the "disconnected state." The fifth gear G5, which meshes with the differential input gear GD, is connected to the first countershaft 31a so as to rotate integrally with the first countershaft 31a. Therefore, in the first connected state and the second connected state, a driving force is transmitted between the first input member 11 and the differential input gear GD (i.e., the third power transmission path is connected), and in the unconnected state, a driving force is not transmitted between the first input member 11 and the differential input gear GD (i.e., the third power transmission path is disconnected). In this embodiment, the first switching mechanism 51 corresponds to the "switching mechanism."

[0033] In this embodiment, the third gear G3 and the fourth gear G4 are connected to the first counter shaft 31a so as to rotate integrally with the first counter shaft 31a. The first switching mechanism 51 is configured to switch between a state in which only the first gear G1 of the first gear G1 and the second gear G2 is connected to the first input member 11, a state in which only the second gear G2 of the first gear G1 and the second gear G2 is connected to the first input member 11, and a state in which both the first gear G1 and the second gear G2 are disconnected from the first input member 11. In other words, the first gear G1 and the second gear G2 are selectively connected to the first input member 11 by the first switching mechanism 51.

[0034] A first connected state is achieved when only the first gear G1 of the first gear G1 and the second gear G2 is connected to the first input member 11. A second connected state is achieved when only the second gear G2 of the first gear G1 and the second gear G2 is connected to the first input member 11. A non-connected state is achieved when both the first gear G1 and the second gear G2 are disconnected from the first input member 11. In the first connected state, the second gear G2 is supported by the first input member 11 so as to be rotatable relative to the first input member 11. In the second connected state, the first gear G1 is supported by the first input member 11 so as to be rotatable relative to the first input member 11. In the non-connected state, the first gear G1 and the second gear G2 are supported by the first input member 11 so as to be rotatable relative to the first input member 11.

[0035] The rotational speed ratio between the first input member 11 and the first countershaft 31a is determined according to the gear ratio between the first gear G1 and the third gear G3 in the first connected state, and is determined according to the gear ratio between the second gear G2 and the fourth gear G4 in the second connected state. The gear ratio between the first gear G1 and the third gear G3 is set to be different from the gear ratio between the second gear G2 and the fourth gear G4. Therefore, by switching between the first connected state and the second connected state using the first switching mechanism 51, the rotational speed ratio between the first input member 11 and the first countershaft 31a can be switched to a different value.

[0036] The ratio of the rotational speed of the first input member 11 to the rotational speed of the differential input gear GD is defined as the gear ratio. In this embodiment, the gear ratio between the first gear G1 and the third gear G3 and the gear ratio between the second gear G2 and the fourth gear G4 are set so that the gear ratio in the first connected state is larger than the gear ratio in the second connected state. Therefore, a low gear is formed in the first connected state, and a high gear is formed in the second connected state. Because the gear ratio between the first gear G1 and the third gear G3 and the gear ratio between the second gear G2 and the fourth gear G4 are set in this manner, in this embodiment, the first gear G1 is formed with a smaller diameter than the second gear G2, and the third gear G3 is formed with a larger diameter than the fourth gear G4.

[0037] In this embodiment, the first gear G1 has a smaller diameter than the third gear G3. That is, the gear ratio between the first gear G1 and the third gear G3 is set so that the rotation of the first input member 11 is reduced in speed before being transmitted to the first countershaft 31a. In addition, in this embodiment, the second gear G2 has a larger diameter than the fourth gear G4. That is, the gear ratio between the second gear G2 and the fourth gear G4 is set so that the rotation of the first input member 11 is increased in speed before being transmitted to the first countershaft 31a.

[0038] In this embodiment, the first switching mechanism 51 is configured using a meshing engagement device (dog clutch). Specifically, the first switching mechanism 51 includes a first sleeve member 51a movable in the axial direction L, a first engagement portion E1 that rotates integrally with the first input member 11, a second engagement portion E2 that rotates integrally with the first gear G1, and a third engagement portion E3 that rotates integrally with the second gear G2. The first sleeve member 51a, the first engagement portion E1, the second engagement portion E2, and the third engagement portion E3 are disposed on the first axis A1. That is, the first switching mechanism 51 (specifically, at least the first sleeve member 51a, the first engagement portion E1, the second engagement portion E2, and the third engagement portion E3) are disposed coaxially with the first input member 11.

[0039] The position of the first sleeve member 51a in the axial direction L is changed by a first shift fork 51b (see FIG. 2) supported on the case 9 so as to be movable in the axial direction L. The first shift fork 51b is engaged with the first sleeve member 51a (specifically, a groove formed in the outer peripheral surface of the first sleeve member 51a) so as to move integrally with the first sleeve member 51a in the axial direction L while allowing rotation of the first sleeve member 51a (rotation about the first axis A1). The first shift fork 51b is moved in the axial direction L by the driving force of an actuator such as an electric actuator or a hydraulic actuator.

[0040] In this embodiment, internal teeth are formed on the inner peripheral surface of the first sleeve member 51a, and external teeth are formed on the outer peripheral surfaces of each of the first engagement portion E1, the second engagement portion E2, and the third engagement portion E3. The first sleeve member 51a is arranged to fit over the first engagement portion E1 and is connected to the first engagement portion E1 so as to be non-rotatable relative to the first engagement portion E1 and movable relative to the first engagement portion E1 in the axial direction L. The first engagement portion E1 (specifically, the external teeth formed on the first engagement portion E1) engages with the first sleeve member 51a (specifically, the internal teeth formed on the first sleeve member 51a) regardless of the position of the first sleeve member 51a in the axial direction L. On the other hand, the second engagement portion E2 (specifically, the external teeth formed on the second engagement portion E2) and the third engagement portion E3 (specifically, the external teeth formed on the third engagement portion E3) selectively engage with the first sleeve member 51a (specifically, the internal teeth formed on the first sleeve member 51a) depending on the axial position L of the first sleeve member 51a.

[0041] The first switching mechanism 51 is configured to switch between a first connected state, a second connected state, and a non-connected state depending on the position of the first sleeve member 51a in the axial direction L. Specifically, the non-connected state is achieved when the first sleeve member 51a moves to a position in the axial direction L where it engages with the first engagement portion E1 but does not engage with the second engagement portion E2 or the third engagement portion E3 (see FIGS. 1 and 2). The first connected state is achieved when the first sleeve member 51a moves to a position in the axial direction L where it engages with the first engagement portion E1 or the second engagement portion E2 but does not engage with the third engagement portion E3 (a position on the first axial side L1 from the position of the first sleeve member 51a shown in FIGS. 1 and 2). In addition, the second connection state is realized when the first sleeve member 51a moves to a position in the axial direction L where it engages with the first engagement portion E1 and the third engagement portion E3 but does not engage with the second engagement portion E2 (a position on the second axial side L2 from the position of the first sleeve member 51a shown in Figures 1 and 2).

[0042] 2, in this embodiment, the first input member 11 is supported by the case 9 at two locations in the axial direction L by a pair of first bearings B1. As described above, the second chamber 92 is formed by the main body case 97 and the transmission mechanism side cover case 96 that abuts against the main body case 97 from the second axial side L2. One of the pair of first bearings B1 is supported by a partition wall 95 formed on the main body case 97, and the other is supported by the transmission mechanism side cover case 96. The first input gear G10, the first gear G1, and the second gear G2 housed in the second chamber 92 are disposed between the pair of first bearings B1 in the axial direction L.

[0043] Similarly, the third input member 13 is supported by the case 9 at two locations in the axial direction L by a pair of second bearings B2. One of the pair of second bearings B2 is supported by a partition wall 95 formed on the main body case 97, and the other is supported by the transmission mechanism side cover case 96. The third input gear G9 housed in the second chamber 92 is disposed between the pair of first bearings B1 in the axial direction L.

[0044] In this embodiment, the first countershaft 31a is supported by the case 9 at two locations in the axial direction L by a pair of third bearings B3. Similar to the first bearing B1 and the second bearing B2, one of the pair of third bearings B3 is supported by a partition wall 95 formed on the main body case 97, and the other is supported by the transmission mechanism side cover case 96. The third gear G3, the fourth gear G4, and the fifth gear G5 are disposed between the pair of third bearings B3.

[0045] As shown in FIG. 1, the second gear mechanism 22 includes a sixth gear G6 (second input gear) arranged coaxially with the second input member 12, and a second counter gear mechanism 32. The second counter gear mechanism 32 includes a second counter shaft 32a, a seventh gear G7 meshing with the sixth gear G6, and an eighth gear G8 rotating integrally with the second counter shaft 32a and meshing with the differential input gear GD. In this embodiment, the sixth gear G6 has a smaller diameter than the seventh gear G7. That is, the gear ratio between the sixth gear G6 and the seventh gear G7 is set so that the rotation of the second input member 12 is decelerated and transmitted to the second counter shaft 32a. In addition, in this embodiment, the eighth gear G8 has a smaller diameter than the differential input gear GD. That is, the gear ratio between the eighth gear G8 and the differential input gear GD is set so that the rotation of the second countershaft 32a is reduced in speed and transmitted to the differential gear device 6 (specifically, the differential input gear GD). In this embodiment, the seventh gear G7 has a larger diameter than the eighth gear G8.

[0046] The second gear mechanism 22 is provided with a second switching mechanism 52 that switches between a transmission state in which driving force is transmitted between the second input member 12 and the second countershaft 32a via the gear pair of the sixth gear G6 and the seventh gear G7, and a non-transmission state in which driving force is not transmitted between the second input member 12 and the second countershaft 32a. The eighth gear G8, which meshes with the differential input gear GD, is connected to the second countershaft 32a so as to rotate integrally with the second countershaft 32a. Therefore, in the transmission state, driving force is transmitted between the second input member 12 and the differential input gear GD (i.e., the second power transmission path is connected), and in the non-transmission state, driving force is not transmitted between the second input member 12 and the differential input gear GD (i.e., the second power transmission path is disconnected).

[0047] In this embodiment, the sixth gear G6 is connected to the second input member 12 so as to rotate integrally with the second input member 12. The second switching mechanism 52 is configured to switch between a state in which the seventh gear G7 is connected to the second countershaft 32a and a state in which the seventh gear G7 is disconnected from the second countershaft 32a. That is, the seventh gear G7 is selectively connected to the second countershaft 32a by the second switching mechanism 52. When the seventh gear G7 is connected to the second countershaft 32a, a transmission state is established. When the seventh gear G7 is disconnected from the second countershaft 32a, a non-transmission state is established. In the non-transmission state, the seventh gear G7 is supported by the second countershaft 32a so as to be rotatable relative to the second countershaft 32a.

[0048] In this embodiment, the second switching mechanism 52 is configured using a mesh-type engagement device (dog clutch). Specifically, the second switching mechanism 52 includes a second sleeve member 52a that is movable in the axial direction L, a fourth engagement portion E4 that rotates integrally with the second counter shaft 32a, and a fifth engagement portion E5 that rotates integrally with the seventh gear G7. The second sleeve member 52a, the fourth engagement portion E4, and the fifth engagement portion E5 are disposed on the sixth axis A6. That is, the second switching mechanism 52 (specifically, at least the second sleeve member 52a, the fourth engagement portion E4, and the fifth engagement portion E5) are disposed coaxially with the second counter gear mechanism 32. In this manner, the second switching mechanism 52 includes the second sleeve member 52a that is coaxial with the second counter gear mechanism 32. As will be described later, the second sleeve member 52a moves in the axial direction L to switch between a transmission state and a non-transmission state.

[0049] The position of the second sleeve member 52a in the axial direction L is changed by a second shift fork 52b (see FIGS. 2 and 3) supported on the case 9 so as to be movable in the axial direction L. The second shift fork 52b is engaged with the second sleeve member 52a (specifically, a groove formed in the outer peripheral surface of the second sleeve member 52a) so as to move integrally with the second sleeve member 52a in the axial direction L while allowing rotation of the second sleeve member 52a (rotation about the sixth axis A6). As will be described in detail later, a drive mechanism that drives the second sleeve member 52a in the axial direction L is configured using the second shift fork 52b.

[0050] In this embodiment, internal teeth are formed on the inner peripheral surface of the second sleeve member 52a, and external teeth are formed on the outer peripheral surfaces of the fourth engagement portion E4 and the fifth engagement portion E5. The second sleeve member 52a is arranged to fit over the fourth engagement portion E4 and is coupled to the fourth engagement portion E4 so as to be non-rotatable relative to the fourth engagement portion E4 and movable in the axial direction L relative to the fourth engagement portion E4. The fourth engagement portion E4 (specifically, the external teeth formed on the fourth engagement portion E4) engages with the second sleeve member 52a (specifically, the internal teeth formed on the second sleeve member 52a) regardless of the position of the second sleeve member 52a in the axial direction L. On the other hand, the fifth engagement portion E5 (specifically, the external teeth formed on the fifth engagement portion E5) selectively engages with the second sleeve member 52a (specifically, the internal teeth formed on the second sleeve member 52a) depending on the position of the second sleeve member 52a in the axial direction L.

[0051] The second switching mechanism 52 is configured to switch between a power transmission state and a non-power transmission state depending on the position of the second sleeve member 52a in the axial direction L. Specifically, the non-power transmission state is achieved when the second sleeve member 52a moves to a position in the axial direction L where it engages with the fourth engagement portion E4 but does not engage with the fifth engagement portion E5 (see FIGS. 1 and 2). The power transmission state is achieved when the second sleeve member 52a moves to a position in the axial direction L where it engages with the fourth engagement portion E4 and the fifth engagement portion E5 (a position on the first axial side L1 from the position of the second sleeve member 52a shown in FIGS. 1 and 2).

[0052] 2, in this embodiment, the second input member 12 is supported by the case 9 at two locations in the axial direction L by a pair of fourth bearings B4. Similar to the first bearing B1, one of the pair of fourth bearings B4 is supported by a partition wall 95 formed on the main body case 97, and the other is supported by the transmission mechanism side cover case 96. The sixth gear G6 housed in the second chamber 92 is disposed between the pair of fourth bearings B4 in the axial direction L.

[0053] The first rotating electric machine 1, the second rotating electric machine 2, the power transmission mechanism 20, and the differential gear unit 6 that constitute the vehicle drive device 100 are lubricated with oil. The lubricating oil is supplied to the vehicle drive device 100 from at least one of a mechanical oil pump (not shown) that is driven by one or more of the internal combustion engine 3, the first rotating electric machine 1, and the second rotating electric machine 2, which are the driving power sources for the wheels 4, as a driving power source, and an electric oil pump (not shown) that is driven by a driving power source other than the driving power source for the wheels 4 (for example, a rotating electric machine (motor) other than the first rotating electric machine 1 and the second rotating electric machine 2). In this embodiment, the oil pump that supplies cooling oil to the target rotating electric machine (the second rotating electric machine 2) and operates independently of the wheels is an electric oil pump. Note that the oil pump that operates independently of the wheels may also be, for example, a mechanical oil pump that is driven by at least one of the first rotating electric machine 1 and the internal combustion engine 3 that rotates to generate electricity while the wheels are stopped. In the vehicle drive system 100, oil passages are formed to each mechanical part, and oil is supplied from these oil pumps. However, forming oil passages to all mechanical parts may result in the oil passages becoming complicated and the vehicle drive system 100 becoming larger. Furthermore, if the number of oil passages increases, it may become necessary to increase the discharge capacity of the oil pump.

[0054] Therefore, instead of forming an oil passage and directly supplying oil from the oil pump, it is often the case that oil is supplied to one mechanism of the vehicle drive system 100 and the oil used to lubricate that mechanism is then used to lubricate another mechanism. For example, the vehicle drive system 100 may be configured so that the other mechanism is lubricated by using rotating members such as various gears provided in the vehicle drive system 100 to scoop up the oil or by using centrifugal force to splash the oil. Note that a differential input gear GD, for example, is commonly used as such a rotating member.

[0055] When the rotating members rotate, oil can be supplied to the lubrication target locations by the rotating members. However, when the rotating members do not rotate, sufficient oil cannot be supplied. As described above, the vehicle drive system 100 can operate in at least two operating modes, a series mode and a parallel mode, depending on the state of the power transmission mechanism 20. In the series mode, for example, while the wheels are stopped, the internal combustion engine 3 is driven, the first rotating electric machine 1 is operated in regenerative mode to generate electricity, and the electricity storage device can be charged. At this time, the first gear mechanism 21 is controlled so that the driving force from the internal combustion engine 3 is not transmitted to the wheels 4. The second gear mechanism 22 is also controlled so that the driving force of the second rotating electric machine 2 is not transmitted to the wheels 4. In other words, when generating electricity while the wheels are stopped, many of the rotating members constituting the power transmission mechanism 20 are not rotating, and there is a possibility that oil will not be sufficiently supplied due to oil being scooped up or the like.

[0056] During power generation while the wheels are stopped, at least the first input member 11, the first rotating electric machine 1, the third input gear G9, and the first input gear G10 are rotating, and it is preferable that these and the bearings that support them are appropriately lubricated. The vehicle drive device 100 according to this embodiment is configured so that these are appropriately lubricated even in such a case.

[0057] As described above, the case 9 includes a first chamber 91 that houses the first rotating electric machine 1 and the second rotating electric machine 2, a second chamber 92 that houses the power transmission mechanism 20, and a partition wall 95 that separates the first chamber 91 from the second chamber 92. FIG. 3 shows a schematic cross-sectional view of the first chamber 91 viewed from the side facing the partition wall 95 along the axial direction L, and FIG. 4 shows a schematic cross-sectional view of the second chamber 92 viewed from the side facing the partition wall 95 along the axial direction L. In the following description, when the vehicle drive device 100 is mounted on a vehicle, the axial direction L is assumed to be horizontal, and a direction perpendicular to the horizontal direction is assumed to be the up-down direction V. Furthermore, a direction perpendicular to the axial direction L and the up-down direction V is assumed to be the width direction H, and one side of the width direction H is referred to as the first width direction side H1, and the other side is assumed to be the second width direction side H2. The width direction H is a direction that runs horizontally.

[0058] As will be described in detail later, as shown in FIG. 3 , the vehicle drive device 100 includes a first oil receiving portion 7 disposed below the second rotating electric machine 2 in a position V2 and configured to receive oil dropping from the second rotating electric machine 2. The first oil receiving portion 7 is disposed in the first chamber 91. Specifically, the first oil receiving portion 7 is formed in the first chamber 91 by a rib (first main body-side rib 75) protruding from a partition wall 95 of the main body case 97 toward the rotating electric machine-side cover case and a rib (first cover-side rib: not shown) protruding from a wall surface of the rotating electric machine-side cover case toward the main body case 97. The first oil receiving portion 7 is formed in a bowl shape so as to be able to store oil. In this embodiment, the "ribs" forming the first oil receiving portion 7, the second oil receiving portion 8, the third oil receiving portion 73, etc., include not only protruding walls protruding from the inner surface of the case 9 but also portions constituting the outer wall of the case 9. 3 and 4, the vehicle drive device 100 is provided with a first oil passage 71 (first oil supply passage 70) that supplies oil collected in the first oil receiving portion 7 to the first bearing B1 that supports the first input member 11 and the first input gear G10 that rotates integrally with the first input member 11. The first oil passage 71 is provided to penetrate the partition wall 95 and communicate between the first chamber 91 and the second chamber 92.

[0059] 4, the second chamber 92 is formed with a second oil receiving portion 8, an oil guide passage 88 that guides the oil supplied from the first oil passage 71 (first oil supply passage 70) to the first input gear G10 and scooped up by the first input gear G10 to the second oil receiving portion 8, and a second oil passage 81 (second oil supply passage 80) that supplies the oil collected in the second oil receiving portion 8 to a second bearing B2 that supports the third input member 13, which is the rotating shaft of the first rotating electrical machine 1. The second oil receiving portion 8 is formed in the second chamber 92 by a rib (second body-side rib 85a) that protrudes from the partition wall 95 of the main body case 97 toward the transmission mechanism-side cover case 96 and a rib (second cover-side rib 85b; see FIG. 7) that protrudes from the wall surface of the transmission mechanism-side cover case 96 toward the main body case 97. The second oil receiving portion 8 is formed in a bowl shape so as to be able to store oil. The bottom 89 of the second oil receiving portion 8 is located at a position V2 below the upper end of the first input gear G10.

[0060] The flow of oil will be described below with reference to the schematic perspective views of Figures 5 to 7. Figure 5 is a partially enlarged perspective view of the first oil receiving portion 7 in the main body case 97. Figure 6 is a partially enlarged perspective view of the second oil receiving portion 8 in the main body case 97. Figure 7 is a partially enlarged perspective view of the second oil receiving portion 8 in the transmission mechanism side cover case 96.

[0061] For example, oil supplied from an electric oil pump is supplied from above V1 of the second rotating electric machine 2 toward the second rotating electric machine 2 to cool the second rotating electric machine 2. More specifically, the oil is supplied toward the stator coil of the second rotating electric machine 2. After cooling the second rotating electric machine 2, the oil flows downward V2 due to gravity. As shown in FIGS. 3 and 5 , the oil that drops from the second rotating electric machine 2 is received by a first oil receiving portion 7 disposed below V2 of the second rotating electric machine 2 and stored in the first oil receiving portion 7. A first oil passage 71 (first oil supply passage 70) is formed in the first oil receiving portion 7 so as to penetrate the partition wall 95 and communicate between the first chamber 91 and the second chamber 92, and supplies the oil stored in the first oil receiving portion 7 to the second chamber 92. In this embodiment, when the first rotating electric machine 1 is generating electricity while the wheels 4 are stopped, the second rotating electric machine 2 is not driven, but due to the configuration of the oil passage, cooling oil is supplied to both the first rotating electric machine 1 and the second rotating electric machine 2.

[0062] A branch oil passage 72 is formed in the rib (first body-side rib 75) that forms the first oil receiving portion 7, at the same position as the first oil passage 71 in the vertical direction V, so as to be adjacent to the first oil passage 71. Because the first oil passage 71 and the branch oil passage 72 are formed at the same position in the vertical direction V, oil that accumulates in the first oil receiving portion 7 flows through both oil passages at approximately the same rate. The branch oil passage 72 may be formed in the first cover-side rib that abuts against the first body-side rib 75, or may be formed in both the first body-side rib 75 and the first cover-side rib. A third oil receiving portion 73 that receives oil from the branch oil passage 72 is formed below V2 of the first oil receiving portion 7. Like the first oil receiving portion 7, the third oil receiving portion 73 is also formed by abutment between a rib (third body-side rib 76) formed on the main body case 97 and a rib (third cover-side rib; not shown) formed on the rotating electrical machine cover case. The third oil receiving portion 73 is provided with a third oil passage 74 that penetrates the partition wall 95 and connects the first chamber 91 and the second chamber 92. The oil that passes through the third oil passage 74 lubricates the first bearing B1 of the first input member 11, as described below. Because the oil stored in the third oil receiving portion 73 is supplied from the first oil receiving portion 7, the third oil passage 74 supplies the oil stored in the first oil receiving portion 7 to the first bearing B1 that supports the input member. In other words, the third oil passage 74, together with the first oil passage 71, constitutes the first oil supply passage 70. As shown in FIG. 2, the oil that passes through the third oil passage 74 lubricates the first bearing B1 (reference symbol B1a) on the left side of the figure, and is then supplied to the shaft space 11e of the first input member 11. This oil not only provides shaft lubrication, but is also used to lubricate other parts via oil passages provided radially from the shaft space 11e.

[0063] The oil supplied to the second chamber 92 through the first oil passage 71 lubricates the first input gear G10. As shown in FIGS. 4 and 6, the oil supplied through the first oil passage 71 is scooped up by the rotation of the first input gear G10. The oil is carried by centrifugal force to the radially outer side of a guide rib 86 formed along the outer periphery of the first input gear G10, and flows through the radially outer side of the guide rib 86 to the second oil receiving portion 8. That is, an oil guide passage 88 is formed radially outward of the guide rib 86 to guide the oil supplied from the first oil passage 71 to the first input gear G10 and scooped up by the first input gear G10 to the second oil receiving portion 8.

[0064] As shown in FIGS. 4, 6, and 7, the second oil receiving portion 8 is connected to a second oil passage 81 that supplies oil collected in the second oil receiving portion 8 to a second bearing B2 (see FIG. 2) that supports the third input member 13, which is the rotating shaft of the first rotating electrical machine 1. As described above, the second oil receiving portion 8 is formed in the second chamber 92 by abutting a second body-side rib 85a that protrudes from the partition wall 95 of the main body case 97 toward the transmission mechanism-side cover case 96 and a second cover-side rib 85b that protrudes from the wall surface of the transmission mechanism-side cover case 96 toward the main body case 97. One second oil passage 81 is formed in each of the second body-side rib 85a and the second cover-side rib 85b. As shown in FIGS. 4 and 6, a second body-side oil passage 81a is formed in the second body-side rib 85a, and as shown in FIG. 7, a second cover-side oil passage 81b is formed in the second cover-side rib 85b. As shown in Figures 4 and 6, the second oil receiving portion 8 is positioned V1 above the third axis A3 on which the first rotating electric machine 1 is positioned, and can appropriately supply oil to the second bearing B2 of the first rotating electric machine 1.

[0065] As described above, the pair of second bearings B2 are supported by the partition wall 95 and the transmission mechanism side cover case 96. The second oil passages 81 are formed on the partition wall 95 side and the transmission mechanism side cover case 96 side, respectively, so that each of the pair of second bearings B2 can be appropriately lubricated.

[0066] Additionally, the guide rib 86 on the transmission mechanism side cover case 96 side also has a fourth oil passage 83 formed therein, which supplies oil collected in the second oil receiving portion 8 to the first input gear G10 and the first bearing B1. Additionally, the above-mentioned third oil passage 74 opens radially inward of the first bearing B1, as shown in Figures 2, 4, and 6, and the oil supplied through the third oil passage 74 lubricates the first bearing B1. As described above, the third oil passage 74, together with the first oil passage 71, constitutes the first oil supply passage 70.

[0067] 5 and 6, the second oil receiving portion 8 is disposed so as to overlap with the first input gear G10 and the second bearing B2 when viewed in the up-down direction V. The bottom 89 of the second oil receiving portion 8 is disposed at a position V2 below the upper end of the first input gear G10. This allows the oil scooped up by the first input gear G10 to be appropriately received by the second oil receiving portion 8 and stored in the second oil receiving portion 8.

[0068] In the above description, an example has been given in which oil supplied from the electric oil pump to the second rotating electric machine 2 is received in the first oil receiving portion 7, stored, and circulated. That is, an example has been given in which oil is supplied from the electric oil pump to the second rotating electric machine 2 disposed on a second axis A2 that is separate from the first axis A1 on which the first input member 11 is disposed, is parallel to the first axis A1, and is disposed above the first axis A1 at a position V1. However, the arrangement of the mechanisms in the vehicle drive device 100 is not limited to the example described above. For example, if the first rotating electric machine 1 is disposed on the second axis A2 above the first axis A1 at a position V1, the target rotating electric machine may be the first rotating electric machine 1, and the first oil receiving portion 7 may be disposed below the first rotating electric machine 1 so that the oil supplied from the electric oil pump to the first rotating electric machine 1 is received in the first oil receiving portion 7.

[0069] That is, it is sufficient that either the first rotating electric machine 1 or the second rotating electric machine 2 is set as the target rotating electric machine, and that the target rotating electric machine is arranged on a second axis A2 that is separate from the first axis A1 on which the first input member 11 is arranged, is parallel to the first axis A1, and is arranged on a position V1 above the first axis A1. The vehicle drive device 100 is further provided with a first oil receiving portion 7 arranged on a position V2 below the target rotating electric machine so as to receive cooling oil that is supplied to the target rotating electric machine from an oil pump that operates independently of the wheels 4 and drops from the target rotating electric machine, and a first oil supply passage 70 that supplies the oil collected in the first oil receiving portion 7 to the first bearing B1 that supports the first input member 11 and to the first input gear G10 that rotates integrally with the first input member 11.

[0070] In the embodiment exemplified above, the target rotating electric machine is the second rotating electric machine 2. The first rotating electric machine 1 is arranged on a third axis A3 that is separate from and parallel to the first axis A1 and the second axis A2. The second chamber 92 is further provided with a second oil receiving portion 8 arranged at a position V1 above the third axis A3, an oil guide passage 88 that guides oil supplied from the first oil supply passage 70 (first oil passage 71) to the first input gear G10 and scooped up by the first input gear G10 to the second oil receiving portion 8, and a second oil passage 81 (second oil supply passage 80) that supplies the oil collected in the second oil receiving portion 8 to a second bearing B2 that supports the rotating shaft of the first rotating electric machine 1.

[0071] The oil supplied from the first oil supply passage 70 not only lubricates the first bearing B1 and the first input gear G10, but is also supplied to and lubricates the second bearing B2 via the oil guide passage 88, the second oil receiver 8, and the second oil passage 81. In other words, oil can be supplied to more locations that need to be lubricated. However, the oil guide passage 88, the second oil receiver 8, and the second oil passage 81 (the second oil supply passage 80) do not necessarily have to be provided.

[0072] Naturally, the target rotating electric machine may be the first rotating electric machine 1. In the above embodiment, the first rotating electric machine 1 and the first input member 11 are always connected to each other. However, this does not preclude a configuration in which the first rotating electric machine 1 and the first input member 11 are separably connected to each other.

[0073] 3 and 4, in the embodiment exemplified above, the third axis A3 is disposed adjacent to the first axis A1 on the opposite side of the second axis A2 in the width direction H (horizontal direction) with respect to the first axis A1 when viewed in the axial direction L. The second oil receiving portion 8 is disposed so as to overlap with the first input gear G10 and the second bearing B2 when viewed in the up-down direction V, and the bottom 89 of the second oil receiving portion 8 is disposed at V2 below the upper end of the first input gear G10.

[0074] Since the first shaft A1 and the third shaft A3 are arranged adjacent to each other, oil that lubricates the first input gear G10 arranged on the first shaft A1 can efficiently flow toward the third shaft A3. Furthermore, since the bottom 89 of the second oil receiving portion 8 is arranged at V2 below the upper end of the first input gear G10, oil scooped up by the first input gear G10 can be easily guided to the second oil receiving portion 8. Furthermore, since the second oil receiving portion 8 is arranged to overlap the first input gear G10 and the second bearing B2 when viewed in the vertical direction V, oil stored in the second oil receiving portion 8 is appropriately supplied to the second bearing B2 by gravity. Since the first input gear G10 rotates, centrifugal force causes the oil that lubricates the first input gear G10 to fly radially outward beyond the outer periphery of the first input gear G10. Therefore, the second oil receiving portion 8 can be arranged at V1 above the upper end of the first input gear G10.

[0075] In the above, an example has been given in which the case 9 accommodating the first rotating electric machine 1, the second rotating electric machine 2, and the power transmission mechanism 20 has a partition wall 95 that separates the first chamber 91 accommodating the first rotating electric machine 1 and the second rotating electric machine 2 from the second chamber 92 accommodating the power transmission mechanism 20, the first oil receiving portion 7 is arranged in the first chamber 91, and the first oil supply passage 70 is arranged to pass through the partition wall 95 and connect the first chamber 91 and the second chamber 92.

[0076] In order to reduce the size of the case 9 while providing rigidity to the case 9, it is preferable to configure the case 9 with the partition wall 95 in this manner. Even when such a partition wall 95 is provided, the first oil supply passage 70 penetrates the partition wall 95 to communicate between the first chamber 91 and the second chamber 92, thereby enabling oil to circulate effectively. Naturally, when the case 9 is not partitioned in this manner and no partition wall 95 or the like is provided, the first oil supply passage 70 may be formed without penetrating any member inside the case 9.

[0077] Furthermore, as described above, when the power transmission mechanism 20 includes two counter gear mechanisms, the first counter gear mechanism 31 and the second counter gear mechanism 32, it is possible to supply lubricating oil to at least one of them. As shown in FIG. 4 , the fifth shaft A5 on which the first counter gear mechanism 31 is disposed is disposed below the first shaft A1. Furthermore, the fifth gear G5 of the first counter gear mechanism 31 overlaps with the first input gear G10 in the width direction H. Therefore, the oil that has lubricated the first input gear G10 drops downward, thereby efficiently lubricating the fifth gear G5, the first counter shaft 31a, and the third bearing B3 that rotatably supports the first counter shaft 31a.

[0078] Furthermore, in the above description, with reference to Figures 3, 5, etc., an example has been described in which two oil receiving portions, the first oil receiving portion 7 and the third oil receiving portion 73, are used as oil receiving portions for storing oil supplied from the first oil supply passage 70 (first oil passage 71, third oil passage 74). However, the oil receiving portion for storing oil supplied from the first oil supply passage 70 may be only the first oil receiving portion 7, as shown in Figure 8. In Figure 8, in order to distinguish it from the first oil receiving portion 7 illustrated in Figures 3 and 5, a different reference symbol "7A" is used, and it will be described as a second first oil receiving portion 7A.

[0079] As shown in FIG. 8, in this embodiment, the first body-side rib 75 extends further toward the first widthwise side H1 than in the embodiment illustrated in FIG. 3, and the second first oil receiving portion 7A is formed to extend further toward the first widthwise side H1 than the opening of the first oil passage 71. A fifth oil passage 77 is provided on the first widthwise side H1 of the first oil passage 71 at approximately the same position (height) in the up-down direction V as the first oil passage 71. Like the first oil passage 71 and the third oil passage 74, the fifth oil passage 77 also penetrates the partition wall 95 to communicate between the first chamber 91 and the second chamber 92. The oil that passes through the fifth oil passage 77 lubricates the second bearing B2 and the third input gear G9 arranged on the third shaft A3. The oil that has passed through the fifth oil passage 77 may be supplied to the first bearing B1 or the first input gear G10. In this case, the fifth oil passage 77 is also included in the first oil supply passage .

[0080] Preferably, the first oil passage 71 and the fifth oil passage 77 are disposed at approximately the same position in the vertical direction V and formed as machined holes in the partition wall 95. The sizes of the first oil passage 71 and the fifth oil passage 77 can be easily adjusted during machining, and the flow rates of oil flowing through the first oil passage 71 and the fifth oil passage 77 can also be easily adjusted. [Explanation of symbols]

[0081] 1: first rotating electric machine, 2: second rotating electric machine, 3: internal combustion engine, 4: wheel, 5: output member, 6: differential gear device, 7: first oil receiving portion, 7A: second first oil receiving portion (first oil receiving portion), 8: second oil receiving portion, 9: case, 11: first input member (input member drivingly connected to internal combustion engine), 20: power transmission mechanism, 21: first gear mechanism, 22: second gear mechanism, 31: first counter gear mechanism, 31a : 1st counter shaft, 32: 2nd counter gear mechanism, 32a: 2nd counter shaft, 70: 1st oil supply path, 71: 1st oil path (1st oil supply path), 74: 3rd oil path (1st oil supply path), 80: 2nd oil Supply path, 81: Second oil path (second oil supply path), 88: Oil guide path, 89: Bottom, 91: First chamber, 92: Second chamber, 95: Partition wall, 100: Vehicle drive device, A1: First shaft, A2: Second shaft, A3: Second shaft. 3 axes, B1: 1st bearing, B2: 2nd bearing, G1: 1st gear, G10: 1st input gear (input gear that rotates integrally with the input member), G2: 2nd gear, G3: 3rd gear, G4: 4th gear, G5: 5th gear, G6: 6th gear, G7: 7th gear, G8: 8th gear, GD: Differential input gear, GP1: 1st gear pair, GP2: 2nd gear pair, H: Horizontal direction, L: Axial direction, V: Up and down direction

Claims

1. an input member drivingly connected to the internal combustion engine; an output member drivingly connected to the wheels; a first rotating electric machine; a second rotating electric machine; a power transmission mechanism that changes a power transmission state between the input member, the output member, the first rotating electric machine, and the second rotating electric machine to transmit power therebetween, an operation mode in which a driving force is transmitted between the input member and the first rotating electric machine and a driving force is transmitted between the second rotating electric machine and the output member is defined as a series mode; an operation mode in which a driving force is transmitted between the input member, the second rotating electric machine, and the output member is defined as a parallel mode; The power transmission mechanism is capable of executing at least two operation modes, namely, the series mode and the parallel mode, one of the first rotating electric machine and the second rotating electric machine is a target rotating electric machine, the target rotating electric machine is disposed on a second axis that is separate from a first axis on which the input member is disposed and that is parallel to the first axis, the second shaft is disposed above the first shaft, a first oil receiving portion disposed below the target rotating electric machine and above the first shaft so as to receive cooling oil supplied to the target rotating electric machine from an oil pump that operates independently of the wheels and drops from the target rotating electric machine; a first oil supply passage that supplies oil accumulated in the first oil receiving portion to a first bearing that supports the input member and an input gear that rotates integrally with the input member.

2. the target rotating electric machine is the second rotating electric machine, the first rotating electric machine is disposed on a third axis separate from the first axis and the second axis and parallel to these axes, a second oil receiving portion disposed above the third shaft; an oil guide passage that guides the oil supplied from the first oil supply passage to the input gear and scooped up by the input gear to the second oil receiving portion; The vehicle drive device according to claim 1 , further comprising: a second oil supply passage that supplies oil collected in the second oil receiving portion to a second bearing that supports the rotating shaft of the first rotating electric machine.

3. When viewed in the axial direction along the axial direction, the third axis is disposed adjacent to the first axis on the opposite side to the second axis in the horizontal direction, the second oil receiving portion is disposed so as to overlap with the input gear and the second bearing when viewed in the up-down direction, The vehicle drive device according to claim 2 , wherein a bottom portion of the second oil receiving portion is disposed below an upper end of the input gear.

4. a case that accommodates the first rotating electric machine, the second rotating electric machine, and the power transmission mechanism; the case includes a partition wall that separates a first chamber that houses the first rotating electric machine and the second rotating electric machine from a second chamber that houses the power transmission mechanism, The first oil receiving portion is disposed in the first chamber, The vehicle drive device according to claim 1 , wherein the first oil supply passage is provided so as to penetrate the partition wall and connect the first chamber and the second chamber.

5. a differential gear device that distributes rotation of a differential input gear to the pair of output members, the power transmission mechanism includes a first gear mechanism that drivingly connects the first rotating electric machine and the input member, and that drivingly connects the input member and the differential input gear; a second gear mechanism that drivingly connects the second rotating electric machine and the differential input gear, the first gear mechanism includes a first gear and a second gear, each of which is disposed coaxially with the input member, and a first counter gear mechanism; the first counter gear mechanism includes a first counter shaft, a third gear meshing with the first gear, a fourth gear meshing with the second gear, and a fifth gear rotating integrally with the first counter shaft and meshing with the differential input gear; a gear ratio between the first gear and the third gear is different from a gear ratio between the second gear and the fourth gear; the second gear mechanism includes a sixth gear arranged coaxially with the second rotating electric machine and a second counter gear mechanism, the second counter gear mechanism includes a second counter shaft, a seventh gear that meshes with the sixth gear, and an eighth gear that rotates integrally with the second counter shaft and meshes with the differential input gear, 5. The vehicle drive device according to claim 1, wherein the first gear mechanism is provided with a switching mechanism that switches between a state in which driving force is transmitted between the input member and the first countershaft via a first gear pair of the first gear and the third gear, a state in which driving force is transmitted between the input member and the first countershaft via a second gear pair of the second gear and the fourth gear, and a state in which driving force is not transmitted between the input member and the first countershaft.

6. An input member drivingly connected to an internal combustion engine; an output member drivingly connected to the wheels; a first rotating electric machine; a second rotating electric machine; a power transmission mechanism that changes a power transmission state between the input member, the output member, the first rotating electric machine, and the second rotating electric machine to transmit power therebetween, an operation mode in which a driving force is transmitted between the input member and the first rotating electric machine and a driving force is transmitted between the second rotating electric machine and the output member is defined as a series mode; an operation mode in which a driving force is transmitted between the input member, the second rotating electric machine, and the output member is defined as a parallel mode; The power transmission mechanism is capable of executing at least two operation modes, namely, the series mode and the parallel mode, one of the first rotating electric machine and the second rotating electric machine is a target rotating electric machine, the target rotating electric machine is disposed on a second axis that is separate from a first axis on which the input member is disposed and that is parallel to the first axis, the second shaft is disposed above the first shaft, a first oil receiving portion disposed below the target rotating electric machine to receive cooling oil supplied to the target rotating electric machine from an oil pump that operates independently of the wheels and drops from the target rotating electric machine; a first oil supply passage that supplies oil collected in the first oil receiving portion to a first bearing that supports the input member and an input gear that rotates integrally with the input member, the target rotating electric machine is the second rotating electric machine, the first rotating electric machine is disposed on a third axis separate from the first axis and the second axis and parallel to these axes, a second oil receiving portion disposed above the third shaft; an oil guide passage that guides the oil supplied from the first oil supply passage to the input gear and scooped up by the input gear to the second oil receiving portion; a second oil supply passage that supplies oil collected in the second oil receiving portion to a second bearing that supports the rotating shaft of the first rotating electric machine.

7. An input member drivingly connected to an internal combustion engine; an output member drivingly connected to the wheels; a first rotating electric machine; a second rotating electric machine; a power transmission mechanism that changes a power transmission state between the input member, the output member, the first rotating electric machine, and the second rotating electric machine to transmit power therebetween, an operation mode in which a driving force is transmitted between the input member and the first rotating electric machine and a driving force is transmitted between the second rotating electric machine and the output member is defined as a series mode; an operation mode in which a driving force is transmitted between the input member, the second rotating electric machine, and the output member is defined as a parallel mode; The power transmission mechanism is capable of executing at least two operation modes, namely, the series mode and the parallel mode, one of the first rotating electric machine and the second rotating electric machine is a target rotating electric machine, the target rotating electric machine is disposed on a second axis that is separate from a first axis on which the input member is disposed and that is parallel to the first axis, the second shaft is disposed above the first shaft, a first oil receiving portion disposed below the target rotating electric machine to receive cooling oil supplied to the target rotating electric machine from an oil pump that operates independently of the wheels and drops from the target rotating electric machine; a first oil supply passage that supplies the oil collected in the first oil receiving portion to a first bearing that supports the input member and an input gear that rotates integrally with the input member; a case that houses the first rotating electric machine, the second rotating electric machine, and the power transmission mechanism, the case includes a partition wall that separates a first chamber that houses the first rotating electric machine and the second rotating electric machine from a second chamber that houses the power transmission mechanism, The first oil receiving portion is disposed in the first chamber, The first oil supply passage is provided to pass through the partition wall and communicate the first chamber with the second chamber.

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