JP7270460B2 - Rotary electric machine rotor and vehicle drive device provided with the rotary electric machine rotor - Google Patents

Description

TECHNICAL FIELD The present invention relates to a rotating electric machine rotor and a vehicle drive device including the rotating electric machine rotor.

Conventionally, an inner peripheral portion formed radially inward of a cylindrical rotor shaft penetrating a rotor of a rotary electric machine is used as an oil passage through which oil is supplied. A structure that guides oil to a rotor core through an oil passage is known. For example, Japanese Patent Application Laid-Open No. 2014-239627 describes an inner peripheral portion (90) formed radially inside a cylindrical rotor shaft (3), and an outer peripheral portion of the inner peripheral portion (90) and the rotor shaft (3). A rotor (2) for a rotary electric machine is disclosed that includes a radial oil passage (91) penetrating the surface along the radial direction (R) and communicating with a rotor core (10). (See FIG. 2, etc. Reference numerals in parentheses in the background art refer to documents.). The oil supplied to the inner peripheral portion (90) flows through the radial oil passage (91) due to the centrifugal force associated with the rotation of the rotor shaft (3), and is supplied to the rotor core (10). The oil supplied to the rotor core (10) cools the permanent magnets (5) embedded in the rotor core (10) through heat exchange with the rotor core (10).

JP 2014-239627 A

Here, in order to guide a sufficient amount of oil to cool the permanent magnets (5) from the inner peripheral portion (90) to the rotor core (10) through the radial oil passage (91), for example, the inner peripheral It is conceivable to provide a weir portion in the portion (90) to dam up the oil so that the oil is retained in the inner peripheral portion (90). However, the oil in the inner peripheral portion (90) is used not only for cooling the permanent magnet (5), but also for lubricating the lubricated portion. For example, oil in the inner circumference (90) flows axially (L) along the inner circumference (90) to lubricate the bearings supporting the rotor shaft (3) at the axial (L) ends. It is sometimes used as an oil. In such a case, if a dam portion is provided in the inner peripheral portion (90) to restrict the flow of oil along the axial direction (L), the oil will not flow to the bearing as the lubricated portion, and lubrication at this point will not be possible. Sometimes you can't do enough.

In view of the above-mentioned actual situation, a rotor for a rotating electric machine capable of appropriately performing both cooling of a rotor core arranged radially outside of a rotor shaft and lubrication of a lubricated part to be lubricated, and a rotor for the rotating electric machine. It would be desirable to have a vehicle drive system with a rotor.

In view of the above, a rotor for a rotary electric machine is characterized by: a rotor core; a cylindrical rotor shaft connected to the rotor core through a radially inner side of the rotor core and extending along the axial direction; and a lubricating device arranged on the first axial side with respect to the rotor core, with the one axial side as the axial first side and the other axial side as the axial second side. The rotor shaft includes a target lubricated portion and a lubricating oil passage for supplying oil to the lubricated portion. a radial oil passage that extends along the radial direction and has an opening that opens to a radial direction oil passage; An annular weir arranged to extend in the circumferential direction along the inner peripheral surface and an axial communication passage are provided, and the oil supply portion is arranged to extend in the inner peripheral portion more than the weir in the inner peripheral portion. Oil is supplied to the second side in the axial direction, the lubricating oil passage is arranged on the first side in the axial direction with respect to the dam portion, and the axial communication passage is provided on the inner peripheral surface or the dam portion. a portion of the inner peripheral portion located on the first axial side of the weir and a portion of the inner peripheral portion located on the second axial side of the weir, and communicating with the lubricating oil passage; be.

According to this configuration, the oil supplied to the inner peripheral portion of the rotor shaft can be retained in the inner peripheral portion by the weir. Therefore, it is possible to appropriately supply oil to the radial oil passage through the opening opening on the inner peripheral surface of the rotor shaft, and to appropriately cool the rotor core disposed radially outside the rotor shaft. . Further, according to this configuration, the weir in the inner peripheral portion is formed by the axial communication passage that communicates the portion on the first side in the axial direction of the weir portion in the inner peripheral portion and the portion on the second side in the axial direction of the weir in the inner peripheral portion. Oil can be supplied from the region on the second side in the axial direction of the portion to the lubricating oil passage on the first side in the axial direction of the weir portion. Therefore, oil can be appropriately supplied to the lubricated portion arranged on the first side in the axial direction with respect to the rotor core, and the lubricated portion can be appropriately lubricated.

Further features and advantages of the technology according to the present disclosure will become clearer from the following description of exemplary and non-limiting embodiments described with reference to the drawings.

Sectional view of the vehicle drive system according to the embodiment Partially enlarged view of Fig. 1 1 is a skeleton diagram of a vehicle drive system according to an embodiment; FIG. 2 is a diagram showing the positional relationship of each component of the vehicle drive system according to the embodiment as viewed in the axial direction; A simplified diagram of a hydraulic circuit according to an embodiment Partially enlarged view of Fig. 1 Axis-perpendicular sectional view of the rotor shaft according to the embodiment Schematic diagram of the rotor shaft developed in the circumferential direction Schematic diagram of the development of the rotor shaft according to the second embodiment in the circumferential direction. Schematic diagram of development of a rotor shaft in a circumferential direction according to another embodiment. Axial cross-sectional view of a main part of a rotor for a rotary electric machine according to another embodiment Axial cross-sectional view of a main part of a rotor for a rotary electric machine according to another embodiment Axis-perpendicular sectional view of a rotor shaft according to another embodiment Axis-perpendicular sectional view of a rotor shaft according to another embodiment Axis-perpendicular sectional view of a rotor shaft according to another embodiment Axis-perpendicular sectional view of a rotor shaft according to another embodiment

1. First Embodiment A first embodiment of a rotor for a rotating electrical machine will be described by taking as an example a case where the rotor for a rotating electrical machine is applied to a vehicle drive device. In the following embodiments, the second rotor 24 provided in the second rotating electric machine MG2 corresponds to the "rotating electric machine rotor". Therefore, hereinafter, the second rotor core 24A corresponds to the "rotor core", and the second rotor shaft 26 corresponds to the "rotor shaft".

In the following description, the vertical direction V (see FIG. 4) means the vertical direction when the rotating electrical machine is in use, that is, the vertical direction when the rotating electrical machine is arranged in the direction in which it is used. In the present embodiment, since the rotating electric machine is provided in the vehicle drive device, the vertical direction V coincides with the vertical direction when the vehicle drive device is mounted on the vehicle. "Upper" and "lower" mean the upper and lower sides in the vertical direction V, respectively. In addition, the direction of each member in the following description represents the direction when they are assembled in a device in which the rotating electric machine is provided (in this embodiment, a vehicle drive device). It should be noted that terms relating to the dimensions, arrangement direction, arrangement position, etc. of each member are concepts that include the state of having differences due to errors (errors to the extent allowable in manufacturing).

As used herein, "driving connection" means a state in which two rotating elements are connected so as to be able to transmit driving force (synonymous with torque). This concept includes a state in which two rotating elements are connected so as to rotate together, and a state in which two rotating elements are connected so as to be able to transmit driving force via one or more transmission members. . Such transmission members include various members (shafts, gear mechanisms, belts, chains, etc.) that transmit rotation at the same speed or at different speeds, and engagement devices that selectively transmit rotation and driving force. (friction engagement device, interlocking engagement device, etc.) may be included. However, when each rotating element of the planetary gear mechanism is referred to as "driving connection", it refers to a state in which the three rotating elements of the planetary gear mechanism are drivingly connected to each other without intervening other rotating elements. .

In this specification, the term "rotary electric machine" is used as a concept including motors (electric motors), generators (generators), and motor generators that function as both motors and generators as necessary. . Further, in this specification, regarding the arrangement of two members, "overlapping in a particular direction view" means that when a virtual straight line parallel to the viewing direction is moved in each direction orthogonal to the virtual straight line, It means that there is at least a part of the area where the virtual straight line intersects both of the two members.

[Schematic Configuration of Vehicle Drive System]
A schematic configuration of the vehicle drive system 1 will be described. The vehicle driving device 1 is a device that transmits the driving force of a driving force source (a driving force source for the wheels W) to an output member 4 that is drivingly connected to the wheels W to drive the vehicle. The vehicle drive device 1 includes rotating electrical machines (here, a first rotating electrical machine MG1 and a second rotating electrical machine MG2) as driving force sources for the wheels W. As shown in FIG. Further, as shown in FIG. 3, in this embodiment, the vehicle drive system 1 includes an input member 3 that is drivingly connected to the internal combustion engine EG as a driving force source for the wheels W. As shown in FIG. That is, the vehicle drive system 1 is a drive system (hybrid vehicle drive system) for driving a vehicle (hybrid vehicle) including both the internal combustion engine EG and the rotating electrical machines (MG1, MG2). Specifically, the vehicle drive system 1 is a so-called two-motor split type hybrid vehicle drive system. The internal combustion engine EG is a prime mover (gasoline engine, diesel engine, etc.) that is driven by combustion of fuel inside the engine to generate power.

The vehicle drive device 1 includes a first rotating electrical machine MG1 and a second rotating electrical machine MG2. In this embodiment, as shown in FIG. 1, the first rotating electrical machine MG1 and the second rotating electrical machine MG2 are housed in a case 30. As shown in FIG. The case 30 also accommodates other devices or mechanisms included in the vehicle drive device 1 . In this embodiment, as shown in FIG. 3, the vehicle drive device 1 includes, in addition to the first rotating electric machine MG1 and the second rotating electric machine MG2, an input member 3, an output member 4, a planetary gear mechanism PG, and a counter gear mechanism. CG, an output differential gear device DF, a first oil pump OP1, and a second oil pump OP2. The dynamic gear device DF, the first oil pump OP1 and the second oil pump OP2 are also housed in the case 30 .

As shown in FIGS. 3 and 4, the first rotating electrical machine MG1, the input member 3, the planetary gear mechanism PG, and the second oil pump OP2 are arranged on the first axis A1, and the second rotating electrical machine MG2 is arranged on the second axis. A2, the output member 4 and the output differential gear device DF are arranged on the third axis A3, the counter gear mechanism CG is arranged on the fourth axis A4, and the first oil pump OP1 is arranged on the fifth axis A4. Placed on A5. These first axis A1, second axis A2, third axis A3, fourth axis A4, and fifth axis A5 are different axes (virtual axes) that are arranged in parallel to each other. Hereinafter, a direction parallel to each of these axes (A1 to A5) (that is, an axial direction common to each axis) is referred to as "axial direction L". One side in the axial direction L is referred to as the "first axial side L1", and the other side in the axial direction L (that is, the side opposite to the first axial side L1 in the axial direction L) is referred to as the "second axial side." L2”. In this embodiment, the vehicle drive device 1 is mounted on the vehicle with the axial direction L along the horizontal plane. Further, in the present embodiment, the vehicle drive device 1 is mounted on the vehicle such that the axial direction L extends along the lateral direction of the vehicle.

As shown in FIG. 1 , the first rotating electric machine MG1 includes a first stator 11 and a first rotor 14 rotatably supported with respect to the first stator 11 . The first stator 11 includes a first stator core 12 fixed to the case 30 and first coil end portions 13 . A coil is wound around the first stator core 12 , and the first coil end portion 13 is a portion of the coil that protrudes in the axial direction L from the first stator core 12 . The first stator 11 includes first coil end portions 13 on both sides in the axial direction L of the first stator core 12 . The first rotor 14 is fixed to a first rotor shaft 16 and rotates integrally with the first rotor shaft 16 . In this embodiment, the first rotating electrical machine MG1 is a permanent magnet rotating electrical machine (here, an embedded permanent magnet synchronous motor), and the first rotor 14 includes a first rotor core 14A and a and an embedded first permanent magnet M1. In addition, in the present embodiment, the first rotating electric machine MG1 is an inner rotor type rotating electric machine, and the first rotor 14 is positioned radially inside the first stator core 12 (in the radial direction with respect to the first axis A1). are placed in

As shown in FIG. 1 , the second rotating electrical machine MG2 includes a second stator 21 and a second rotor 24 rotatably supported with respect to the second stator 21 . The second stator 21 includes a second stator core 22 fixed to the case 30 and second coil end portions 23 . A coil is wound around the second stator core 22 , and the second coil end portion 23 is a portion of the coil that protrudes in the axial direction L from the second stator core 22 . The second stator 21 has second coil end portions 23 on both sides in the axial direction L of the second stator core 22 . The second rotor 24 includes a second rotor core 24A, and a tubular second rotor shaft 26 extending along the axial direction L, which is connected to the second rotor core 24A through the radially inner side of the second rotor core 24A. I have. The second rotor 24 is fixed to a second rotor shaft 26 and rotates together with the second rotor shaft 26 . In this embodiment, the second rotating electrical machine MG2 is a permanent magnet rotating electrical machine (here, an embedded permanent magnet synchronous motor), and the second rotor 24 is a second permanent magnet embedded inside the second rotor core 24A. It has a magnet M2. In addition, in the present embodiment, the second rotating electric machine MG2 is an inner rotor type rotating electric machine, and the second rotor 24 is positioned radially inside the second stator core 22 (in the radial direction with respect to the second axis A2). are placed in

The planetary gear mechanism PG includes a first rotating element 67 drivingly connected to the first rotating electric machine MG1, a second rotating element 68 drivingly connected to the output member 4, and a third rotating element drivingly connected to the input member 3. 69 and . In the present embodiment, the first rotating element 67 is coupled to rotate integrally with the first rotary electric machine MG1 (first rotor shaft 16), and the second rotating element 68 is a second rotating element of the counter gear mechanism CG, which will be described later. It is connected to the distribution output gear 64 meshing with the 1 gear 61 so as to rotate integrally, and the third rotating element 69 is connected to the input member 3 so as to rotate integrally. Here, the input member 3 is a member (a shaft member in this embodiment) that is drivingly connected to the internal combustion engine EG (an output shaft such as a crankshaft). The input member 3 is connected to rotate integrally with the internal combustion engine EG, or connected to the internal combustion engine EG via other members such as dampers and clutches. Moreover, the output member 4 is a member drivingly connected to the wheel W. As shown in FIG. In this embodiment, the output member 4 is a member that rotates integrally with the wheels W. As shown in FIG. That is, a member (e.g., side gear) that rotates integrally with the wheels W in the output differential gear device DF, or a member that constitutes a drive shaft that connects the output differential gear device DF and the wheels W, is used as an output A member 4 is used.

In this embodiment, the planetary gear mechanism PG is a single pinion type planetary gear mechanism. In this embodiment, the first rotating element 67 is a sun gear, the second rotating element 68 is a ring gear, and the third rotating element 69 is a carrier. Therefore, the planetary gear mechanism PG distributes the torque of the internal combustion engine EG transmitted to the third rotating element 69 to the first rotating element 67 and the second rotating element 68 (that is, the first rotating electric machine MG1 and the output member 4). and distributed).

The counter gear mechanism CG includes a first gear 61 meshing with the distribution output gear 64, a second gear 62 meshing with the differential input gear 65 of the output differential gear device DF, the first gear 61 and the second gear 62. and a connecting shaft 63 that connects the In this embodiment, the first gear 61 is also meshed with the output gear 60 of the second rotating electric machine MG2. The output gear 60 is a gear for outputting the torque of the second rotating electric machine MG2, and is connected to the second rotor shaft 26 so as to rotate integrally.

The output differential gear device DF distributes the torque input to the differential input gear 65 to the pair of left and right output members 4 (that is, distributes to the pair of left and right wheels W) and transmits the torque. The output differential gear device DF is configured using, for example, a bevel gear type or planetary gear type differential gear mechanism.

Since the vehicle drive system 1 according to the present embodiment is configured as described above, during execution of the continuously variable speed driving mode in which the vehicle is driven by transmitting the torque of the internal combustion engine EG to the wheels W, MG1 outputs reaction torque with respect to torque distributed to the first rotating element 67 . At this time, the first rotating electric machine MG1 basically functions as a generator and generates power by the torque distributed to the first rotating element 67 . Further, during execution of the continuously variable speed traveling mode, torque attenuated with respect to the torque of the internal combustion engine EG is distributed to the second rotating element 68 as torque for driving the wheels W, and the second rotating electric machine MG2 is , if necessary, torque is output so as to make up for the shortage of the wheel demand torque (torque demanded to be transmitted to the wheels W). Further, during execution of the electric drive mode in which only the torque of the second rotary electric machine MG2 is transmitted to the wheels W to drive the vehicle, the internal combustion engine EG is basically stopped, in which the supply of fuel is stopped. The single-rotation electric machine MG1 is basically in a state of idling (a state in which the output torque is controlled to be zero by zero torque control).

The vehicle drive device 1 includes a drive transmission mechanism 2 that transmits the driving force of the second rotating electric machine MG2 to the output member 4 . In this embodiment, the drive transmission mechanism 2 includes a counter gear mechanism CG and an output differential gear device DF. In this embodiment, as shown in FIG. 4, the second rotating electric machine MG2 is arranged so as to overlap the counter gear mechanism CG when viewed in the axial direction L along the axial direction L. As shown in FIG. Here, the second rotating electric machine MG2 is arranged so as to overlap the fourth axis A4 on which the counter gear mechanism CG is arranged when viewed in the axial direction L. Note that FIG. 4 shows the reference pitch circle for each gear, the outer shape of the first stator 11 (outer shape of the first stator core 12) for the first rotating electrical machine MG1, and the second stator for the second rotating electrical machine MG2. 21 (the outer shape of the second stator core 22).

In the present embodiment, as shown in FIG. 1, the counter gear mechanism CG is arranged on the opposite side (axial second side L2) of the second rotary electric machine MG2 from the axial first side L1 in the axial direction L. It is Specifically, the case 30 includes a first wall portion 31 arranged on the first side L1 in the axial direction with respect to the second rotating electric machine MG2, and a second wall portion 31 arranged on the second side L2 in the axial direction with respect to the second rotating electric machine MG2. and a second wall portion 32 that is Both the first wall portion 31 and the second wall portion 32 are support walls that support the second rotor shaft 26 . The counter gear mechanism CG is arranged on the second side L2 in the axial direction with respect to the second wall portion 32 . Here, the first wall portion 31 is arranged adjacent to the second rotating electric machine MG2 on the first side L1 in the axial direction, and the second wall portion 32 is arranged on the second axial side with respect to the second rotating electric machine MG2. It is arranged adjacent to side L2. In the present embodiment, the first wall portion 31 is a separate member from the peripheral wall portion of the case 30 (the tubular wall portion surrounding the second rotating electric machine MG2 and the like when viewed in the axial direction L). It is joined from the first axial side L1 so as to cover the opening on the first axial side L1. That is, in the present embodiment, the first wall portion 31 is a cover member (specifically, a rear cover that covers the opening of the peripheral wall portion on the side opposite to the side on which the internal combustion engine EG is arranged).

As shown in FIG. 3, the vehicle drive system 1 includes a first oil pump OP1 arranged on a separate axis from the second rotating electric machine MG2. Although not shown, an oil reservoir for storing oil is formed inside the case 30, and as shown in FIG. of oil. As shown in FIG. 3, in this embodiment, the vehicle drive system 1 further includes a second oil pump OP2. In this embodiment, the second oil pump OP2 is arranged coaxially with the first rotating electric machine MG1. As shown in FIG. 5, the second oil pump OP2 sucks the oil in the oil reservoir through the second strainer ST2. The first strainer ST1 and the second strainer ST2 are filters for removing foreign substances contained in the oil.

In this embodiment, the first oil pump OP1 is driven by the rotation of the drive transmission mechanism 2. As shown in FIG. Specifically, the first oil pump OP1 is a rotating member provided in the drive transmission mechanism 2, and is a rotating member that is drivingly connected to the wheels W inseparably (i.e., a rotating member that always rotates in conjunction with the wheels W). member) is configured to be driven by rotation. Therefore, while the vehicle is running, regardless of whether the continuously variable speed driving mode is being executed or the electric driving mode is being executed (that is, even when the internal combustion engine EG is stopped), the second 1 oil pump OP1 can be driven. Here, the drive transmission mechanism 2 is a mechanism that transmits the driving force of the second rotating electric machine MG2 to the output member 4. As shown in FIG. Therefore, the second rotor shaft 26 and the first oil pump OP1 are drive-coupled via the drive transmission mechanism 2 so as to always rotate synchronously at a prescribed rotational speed ratio. Therefore, it can be said that the first oil pump OP<b>1 is drivingly connected to the second rotor shaft 26 and driven by the rotation of the second rotor shaft 26 . In this embodiment, as shown in FIG. 3, the first oil pump OP1 is configured to be driven by rotation of the differential input gear 65 of the output differential gear device DF. Specifically, a pump drive gear 66 is provided on the first pump drive shaft 53a, which is the drive shaft of the first oil pump OP1. Then, the pump drive gear 66 meshes with the differential input gear 65, so that the rotation of the differential input gear 65 drives the first oil pump OP1. However, without being limited to such a configuration, the pump driving gear 66 is a gear other than the differential input gear 65 provided in the drive transmission mechanism 2 (in this embodiment, the output gear 60, the first gear 61, or the second gear). 2 gear 62) may be meshed.

In this embodiment, the second oil pump OP2 is driven by the rotation of the input member 3. As shown in FIG. In other words, the second oil pump OP2 is drivingly connected to the internal combustion engine EG and driven by the driving force of the internal combustion engine EG. Specifically, the second pump drive shaft 53b, which is the drive shaft of the second oil pump OP2, is connected to the input member 3 so as to rotate integrally therewith. In addition, as shown in FIG. 2, the second pump drive shaft 53b is connected to rotate integrally with the pump rotor 54 of the second oil pump OP2. Therefore, regardless of whether the vehicle is running or not, the driving force (torque) of the internal combustion engine EG can drive the second oil pump OP2 while the internal combustion engine EG is rotating. At least one of the first oil pump OP1 and the second oil pump OP2 may be an electric oil pump driven by a dedicated electric motor for driving the pump.

[Oil distribution structure]
Next, a structure for circulating oil flowing inside the vehicle drive system 1 will be described. The vehicle drive system 1 is provided with an oil flow structure described below, so that the oil is supplied to the inner peripheral portion 26I surrounded by the cylindrical inner peripheral surface F of the second rotor shaft 26, and the inner peripheral portion Oil can be supplied from 26I to the second rotor core 24A arranged radially outwardly of the second rotor shaft 26 and the lubricated portion H to be lubricated. In this embodiment, the vehicle drive system 1 includes an oil pump OP that supplies oil to the oil supply portion S. As shown in FIG. In this embodiment, the oil pump OP includes a first oil pump OP1 that is drivingly connected to the rotor shaft 26 and driven by the rotation of the rotor shaft 26, and a first oil pump OP1 that is drivingly connected to the internal combustion engine EG and is driven by the internal combustion engine EG. and a second oil pump OP2. Further, in the present embodiment, the lubricated portion H is a bearing B (first bearing B1 described later) that rotatably supports the second rotor shaft 26 . That is, as will be described below, the vehicle drive system 1 includes a first oil pump OP1, a supply oil passage 90, a first oil passage 91, and a second oil passage 92 constituted by the inner peripheral portion 26I. , and the third oil passage 93, cooling of the second rotary electric machine MG2 and lubrication of the bearing B are enabled by the oil discharged from the first oil pump OP1. Further, in the present embodiment, the vehicle drive device 1 further includes the fourth oil passage 94, so that the oil discharged from the first oil pump OP1 can be used to supply oil to the first rotary electric machine MG1. In this embodiment, the vehicle drive system 1 further includes an oil cooler OC.

As shown in FIG. 5, the supply oil passage 90 is connected to the first discharge port 52a, which is the discharge port of the first oil pump OP1. In FIG. 5, the line segment indicating the supply oil passage 90 is made thicker than the line segments indicating the other oil passages. In FIG. 5, arrows indicate the direction in which oil flows in each oil passage. In this embodiment, the supply oil passage 90 includes a first discharge oil passage 81, a confluence oil passage 83, and a downstream oil passage 84 in order from the upstream side. Specifically, the upstream end of the first discharge oil passage 81 is connected to the first discharge port 52a, and the downstream end of the first discharge oil passage 81 is connected to the upstream end of the confluence oil passage 83. It is connected. The downstream end of the merged oil passage 83 is connected to the upstream end of the downstream oil passage 84, and the downstream end of the downstream oil passage 84 is connected to the upstream end of the first oil passage 91 ( It is connected to a first inflow portion 91a), which will be described later. Therefore, the oil discharged by the first oil pump OP<b>1 flows through the first discharge oil passage 81 , the junction oil passage 83 and the downstream oil passage 84 in order, and is supplied to the first oil passage 91 . The first discharge oil passage 81 is provided with a first check valve 51a that regulates the flow of oil toward the upstream side.

As described above, in the present embodiment, the vehicle drive system 1 includes the second oil pump OP2 in addition to the first oil pump OP1. In this embodiment, the upstream end of the second discharge oil passage 82 is connected to the second discharge port 52b, which is the discharge port of the second oil pump OP2. is connected to the upstream end of the confluence oil passage 83 . That is, the confluence oil passage 83 is an oil passage formed by the merging of the first discharge oil passage 81 and the second discharge oil passage 82 . The second discharge oil passage 82 is provided with a second check valve 51b that regulates the flow of oil toward the upstream side.

As shown in FIG. 5, in this embodiment, an oil cooler OC is provided in the supply oil passage 90 . The oil cooler OC is a heat exchanger that cools oil. The oil cooler OC is, for example, a water-cooled or air-cooled oil cooler. In this embodiment, the oil cooler OC is provided in the confluence oil passage 83 . In addition, a relief valve RV (this embodiment In form, two relief valves RV) are provided.

As shown in FIG. 2, the first oil passage 91 is arranged above the second stator 21 in the vertical direction V (see FIG. 4). The first oil passage 91 includes a first inflow portion 91a connected to the supply oil passage 90 (the downstream side oil passage 84 in this embodiment) and a first side L1 in the axial direction from the first inflow portion 91a. It has a first discharge hole 91b formed to discharge oil toward the second stator 21, and a discharge portion 91c formed on the first side L1 in the axial direction from the first discharge hole 91b. As a result, the oil supplied from the supply oil passage 90 to the first oil passage 91 can be discharged from the first discharge hole 91 b toward the second stator 21 to cool the second stator 21 . .

The first oil passage 91 is arranged so as to overlap the second stator 21 when viewed in the vertical direction V. As shown in FIG.
As shown in FIG. 2, in the present embodiment, the first oil passage 91 is a first discharge hole provided at a position overlapping the second coil end portion 23 on the first side L1 in the axial direction when viewed in the vertical direction V. 91b, a first discharge hole 91b provided at a position overlapping the second coil end portion 23 on the axial second side L2 when viewed in the vertical direction V, and a position overlapping the second stator core 22 when viewed in the vertical direction V. and a first discharge hole 91b. As a result, the oil discharged from the first discharge hole 91b can be supplied to the second stator 21 with a relatively simple structure that utilizes gravity.

The first oil passage 91 is an oil passage having a first inflow portion 91a and a discharge portion 91c at both ends, and the discharge portion 91c is arranged on the first side L1 in the axial direction from the first inflow portion 91a. The first oil passage 91 is formed to uniformly extend from the first inflow portion 91a to the discharge portion 91c toward the axial first side L1. That is, as the direction of oil flow in each oil passage is indicated by an arrow in FIG.

As shown in FIG. 1, the second oil passage 92 is an oil passage formed inside the second rotor shaft 26 to which the second rotor 24 of the second rotary electric machine MG2 is fixed. The second rotor shaft 26 is composed of a cylindrical member extending in the axial direction L, and a space surrounded by the inner peripheral surface F of the second rotor shaft 26 forms a second oil passage 92 extending in the axial direction L. ing. That is, as described above, the second oil passage 92 is configured by the inner peripheral portion 26I surrounded by the inner peripheral surface F of the second rotor shaft 26. As shown in FIG. Furthermore, in this embodiment, the second rotor shaft 26 includes a first tubular member 26A and a second tubular member 26B. The first tubular member 26A is arranged on the first axial side L1 with respect to the second tubular member 26B. As shown in FIG. 1, the end portion of the first tubular member 26A on the second axial side L2 and the end portion of the second tubular member 26B on the first axial side L1 are connected. In the present embodiment, the end portion of the second tubular member 26B on the axial first side L1 is located radially inside the end portion of the axial direction second side L2 of the first tubular member 26A. The first cylindrical member 26A and the second cylindrical member 26B are connected so as to rotate integrally by fitting (spline fitting) to the inner peripheral surface of the member 26A. In this embodiment, a second oil passage 92 (inner peripheral portion 26I) is formed inside the first tubular member 26A of the second rotor shaft 26, and a seventh oil passage described later is formed inside the second tubular member 26B. 97 is formed.

As shown in FIGS. 1 and 6, the second rotor shaft 26 has an opening 72A that opens in its tubular inner peripheral surface F, and along the radial direction (the radial direction with respect to the second axis A2) It has a radial oil passage 72 that extends along the length of the shaft. In this embodiment, the radial oil passage 72 is formed so as to radially penetrate the second rotor shaft 26 , and communicates the inner peripheral surface F and the outer peripheral surface of the second rotor shaft 26 .

A second in-rotor oil passage 25 is formed inside the second rotor core 24A. Although details are omitted, the second rotor internal oil passage 25 includes an axial oil passage extending in the axial direction L and a radial direction extending in the radial direction to communicate the inner peripheral surface of the second rotor core 24A and the axial oil passage. and an oil passage. As a result, the oil in the second oil passage 92 can be supplied from the radial oil passage 72 to the second in-rotor oil passage 25 to cool the second rotor core 24A. The second rotor core 24A, particularly the second permanent magnets M2 embedded in the second rotor core 24A, can be cooled by heat exchange between the oil supplied to the second internal rotor oil passage 25 and the second rotor core 24A. It is possible. In the present embodiment, the axial oil passages of the second internal rotor oil passage 25 are formed to open at both ends of the second rotor core 24A in the axial direction L, and cool the second rotor core 24A. It is also possible to cool the second coil end portion 23 by supplying subsequent oil to the second coil end portion 23 from the inside in the radial direction.

In this embodiment, the vehicle drive system 1 includes a third oil passage 93 that connects the discharge portion 91 c of the first oil passage 91 and the second oil passage 92 . The third oil passage 93 is provided along the first wall portion 31 arranged on the first side L1 in the axial direction with respect to the second rotating electric machine MG2 in the case 30 . That is, at least a portion of the third oil passage 93 is provided along the first wall portion 31, and in the present embodiment, a portion of the third oil passage 93 excluding the upstream end and the downstream end is the third oil passage. It is provided along one wall portion 31 . By providing the third oil passage 93 along the first wall portion 31 in this manner, the vehicle drive device 1 is located at the portion where the third oil passage 93 is provided (that is, the portion where the second rotating electric machine MG2 is arranged). It is possible to provide a third oil passage 93 for supplying oil discharged from the first oil pump OP1 to the second oil passage 92 while suppressing an increase in size in the axial direction L of the oil pump OP1.

In the present embodiment, as shown in FIGS. 1 and 2, a connecting portion 90a, which is a portion of the supply oil passage 90 connected to the first inflow portion 91a, is connected to the second rotating electric machine MG2 in the case 30. It is provided along the second wall portion 32 arranged on the axial second side L2. The connection portion 90 a is a portion including the downstream end of the supply oil passage 90 (the downstream oil passage 84 in this embodiment), and at least a portion of the connection portion 90 a is provided along the second wall portion 32 . It is

As shown in FIG. 1 , in this embodiment, the third oil passage 93 is formed inside the first wall portion 31 . At least part of the third oil passage 93 is formed outside the first wall portion 31 (for example, inside a tubular member attached to the first wall portion 31 from the axial second side L2). formed configuration). Further, in the present embodiment, the first wall portion 31 is formed in a cylindrical shape protruding to the second axial side L2, and the opening portion of the second axial side L2 is arranged inside the second rotor shaft 26. The downstream end of the third oil passage 93 is formed by the space surrounded by the inner peripheral surface of the second connection portion 34b. Thereby, the downstream end of the third oil passage 93 and the end of the second oil passage 92 on the axial first side L1 are connected.
A first supply portion S<b>1 for supplying oil to an inner peripheral portion 26</b>I (second oil passage 92 ), which will be described later, is formed at the downstream end of the third oil passage 93 .

In the present embodiment, the vehicle drive system 1 further includes a fourth oil passage 94 through which oil flows for cooling the first rotating electric machine MG1. As shown in FIG. 5, the fourth oil passage 94 is formed to branch from a portion of the supply oil passage 90 downstream of the oil cooler OC. This makes it possible to supply the oil cooled by the oil cooler OC not only to the first oil passage 91 and the second oil passage 92 but also to the fourth oil passage 94 .

As shown in FIG. 2, the fourth oil passage 94 is arranged above the first stator 11 in the vertical direction V (see FIG. 4). The fourth oil passage 94 is connected to an intermediate portion of the supply oil passage 90 (in this embodiment, the downstream end of the merged oil passage 83, in other words, the upstream end of the downstream oil passage 84). It has a second inflow portion 94a and a second discharge hole 94b that is formed on the first side L1 in the axial direction of the second inflow portion 94a and discharges oil toward the first stator 11 . As a result, the oil supplied from the supply oil passage 90 to the fourth oil passage 94 can be discharged from the second discharge hole 94b toward the first stator 11 to cool the first stator 11. .

The fourth oil passage 94 is arranged so as to overlap the first stator 11 when viewed in the vertical direction V. As shown in FIG.
As shown in FIG. 2, in the present embodiment, the fourth oil passage 94 is a second discharge hole provided at a position overlapping the first coil end portion 13 on the first side L1 in the axial direction when viewed in the vertical direction V. 94b, a second discharge hole 94b provided at a position overlapping the first coil end portion 13 on the axial second side L2 when viewed in the vertical direction V, and a second discharge hole 94b provided at a position overlapping the first stator core 12 when viewed in the vertical direction V. and a second discharge hole 94b. As a result, the oil discharged from the second discharge hole 94b can be supplied to the first stator 11 with a relatively simple structure that utilizes gravity.

As shown in FIGS. 2 and 5, the vehicle drive system 1 further includes a fifth oil passage 95 in this embodiment. As shown in FIG. 2, the fifth oil passage 95 is an oil passage formed inside the second pump drive shaft 53b. The second pump drive shaft 53b is composed of a tubular member extending in the axial direction L, and the space surrounded by the inner peripheral surface of the second pump drive shaft 53b forms a fifth oil passage 95 extending in the axial direction L. It is As shown in FIG. 5, the fifth oil passage 95 is formed to branch from a portion of the second discharge oil passage 82 upstream of the second check valve 51b. The amount of oil flowing from the second discharge oil passage 82 into the fifth oil passage 95 is controlled by the second orifice 50b.

A flow of oil is formed in the fifth oil passage 95 toward the axial second side L2. As shown in FIG. 5, the oil in the fifth oil passage 95 is supplied for cooling the first rotary electric machine MG1 (first rotor 14) and lubricates the planetary gear mechanism PG. supplied for Specifically, as shown in FIG. 2, the first rotor shaft 16 is configured by a tubular member extending in the axial direction L, and the second pump drive shaft 53b extends along the inner peripheral surface of the first rotor shaft 16. It is located in a space surrounded by The second pump drive shaft 53b has a second oil hole 73 that communicates the inner and outer peripheral surfaces of the second pump drive shaft 53b. The second oil hole 73 is formed so as to penetrate through the cylindrical portion of the second pump drive shaft 53b in the radial direction (the radial direction with respect to the first axis A1; hereinafter the same in this paragraph). Further, the first rotor shaft 16 is provided with a first oil hole 71 that communicates between the inner peripheral surface and the outer peripheral surface of the first rotor shaft 16 . The first oil hole 71 is formed so as to penetrate the tubular portion of the first rotor shaft 16 in the radial direction. A first internal rotor oil passage 15 is formed inside the first rotor core 14A. Although details are omitted, the first rotor internal oil passage 15 includes an axial oil passage extending in the axial direction L and a radial direction extending in the radial direction to communicate the inner peripheral surface of the first rotor core 14A and the axial oil passage. and an oil passage.

As a result, the oil in the fifth oil passage 95 is supplied from the second oil hole 73 to the inner peripheral surface of the first rotor shaft 16, and the oil supplied to the inner peripheral surface of the first rotor shaft 16 is supplied to the first oil. It is possible to cool the first rotor core 14A by supplying it from the hole 71 to the first internal rotor oil passage 15 . By heat exchange between the oil supplied to the first internal rotor oil passage 15 and the first rotor core 14A, it is possible to cool the first rotor core 14A, particularly the first permanent magnet M1 embedded in the first rotor core 14A. It is possible. Further, in the present embodiment, the axial oil passages of the first internal rotor oil passage 15 are formed to open at both ends in the axial direction L of the first rotor core 14A, and cool the first rotor 14. It is also possible to cool the first coil end portion 13 by supplying subsequent oil to the first coil end portion 13 from the inside in the radial direction (the radial direction with respect to the first axis A1). . Further, after the oil in the fifth oil passage 95 flows into the oil passage formed inside the input member 3, the oil flows from the fourth oil hole 74 (see FIGS. 1 and 2) formed in the input member 3 to It is supplied for lubrication to the planetary gear mechanism PG and the like.

As shown in FIG. 5 , in this embodiment, the vehicle drive system 1 further includes a sixth oil passage 96 . The sixth oil passage 96 is formed to branch from a portion of the first discharge oil passage 81 upstream of the first check valve 51a. The oil in the sixth oil passage 96 is supplied for lubrication to the counter gear mechanism CG and the output differential gear device DF. The amount of oil flowing from the first discharge oil passage 81 to the sixth oil passage 96 is controlled by the first orifice 50a.

As shown in FIGS. 1 and 5, the vehicle drive system 1 further includes a seventh oil passage 97 in this embodiment. The seventh oil passage 97 is formed inside the second tubular member 26B that constitutes the second rotor shaft 26 . A flow of oil is formed in the seventh oil passage 97 toward the first side L1 in the axial direction. In this embodiment, as shown in FIG. 4, the vehicle drive system 1 includes a catch tank that stores oil that is raked up by the output member 4 (see FIG. 3) (in this example, by the differential input gear 65). A CT is provided at the top inside the case 30 . When the oil stored in the catch tank CT flows into the seventh oil passage 97 from the axial second side L2, a flow of oil toward the axial first side L1 is formed in the seventh oil passage 97. . As illustrated, the downstream end of the seventh oil passage 97 and the end of the second oil passage 92 on the second side L2 in the axial direction are connected. Therefore, the oil flowing through the seventh oil passage 97 toward the first side L1 in the axial direction is supplied to the second oil passage 92 (the inner peripheral portion 26I). A second supply portion S<b>2 for supplying oil to an inner peripheral portion 26</b>I (second oil passage 92 ), which will be described later, is formed at the downstream end of the seventh oil passage 97 .

As shown in FIGS. 1 and 2, in the present embodiment, the vehicle drive system 1 includes a first tubular oil flow pipe 41, a second tubular oil flow pipe 42, and a third tubular oil flow pipe 43. I have. A fourth oil passage 94 is formed inside the first oil flow pipe 41 , a first oil passage 91 is formed inside the second oil flow pipe 42 , and a downstream oil flow path is formed inside the third oil flow pipe 43 . A path 84 is formed. As shown in FIG. 1, in the present embodiment, the first wall portion 31 has a tubular first connecting portion 34a that protrudes toward the second side L2 in the axial direction. The upstream end of the third oil passage 93 is formed by the space surrounded by the inner peripheral surface of 34a. The second oil flow pipe 42 is arranged such that the discharge portion 91c is connected to the first connection portion 34a, thereby connecting the downstream end (discharge portion 91c) of the first oil passage 91 and the first oil passage 91c to the first connection portion 34a. 3 is connected to the upstream end of the oil passage 93 at the first connection portion 34a. In addition, the second oil flow pipe 42 is arranged so that both end portions are arranged at different positions in the axial direction L (for example, along the axial direction L). A discharge portion 91c of the first oil passage 91 is formed by the opening on the 1 side L1. Further, the first discharge hole 91b described above is formed so as to pass through the tubular portion of the second oil flow pipe 42 .

As shown in FIG. 2, in the present embodiment, the second wall portion 32 includes a third connecting portion 34c formed in a cylindrical shape extending in the axial direction L. As shown in FIG. Then, the end portion of the second oil flow pipe 42 on the second axial side L2 is fitted to the inner peripheral surface of the third connecting portion 34c from the first axial side L1, and the end of the third oil flow pipe 43 The end portion is fitted to the inner peripheral surface of the third connecting portion 34c from the second axial side L2. Thereby, the downstream end of the downstream oil passage 84 and the upstream end of the first oil passage 91 (first inflow portion 91a) are connected at the third connecting portion 34c. A first inflow portion 91 a of the first oil passage 91 is formed by an opening portion of the second oil flow pipe 42 on the second axial side L<b>2 .

As shown in FIG. 2, in this embodiment, the second wall portion 32 includes a fourth connection portion 34d formed in a cylindrical shape extending in the axial direction L. As shown in FIG. Then, the end portion of the first oil flow pipe 41 on the second axial side L2 is fitted to the inner peripheral surface of the fourth connection portion 34d from the first axial side L1, and the end of the third oil flow pipe 43 The end portion (the end portion opposite to the side connected to the third connection portion 34c) is fitted to the inner peripheral surface of the fourth connection portion 34d from the second axial side L2. Further, the downstream end portion of the confluence oil passage 83 is formed so as to open to the inner peripheral surface of the fourth connection portion 34d. As a result, the downstream end of the confluence oil passage 83, the upstream end of the downstream oil passage 84, and the upstream end of the fourth oil passage 94 (second inflow portion 94a) are connected to the fourth connection portion. 34d. In addition, the first oil flow pipe 41 is arranged so that both ends are arranged at different positions in the axial direction L (for example, along the axial direction L). A second inflow portion 94a of the fourth oil passage 94 is formed by the opening on the second side L2. Further, the above-described second discharge hole 94b is formed so as to pass through the tubular portion of the first oil flow pipe 41 .

[Running mode and oil flow]
Next, the flow of oil in the vehicle drive system 1 when the vehicle drive system 1 is executing a plurality of driving modes will be described.

The vehicle drive system 1 has a hybrid running mode (HV running mode) in which the vehicle runs using at least the internal combustion engine EG as a power source, and a second rotating electric machine among the internal combustion engine EG, the first rotating electric machine MG1, and the second rotating electric machine MG2. An electric drive mode (EV drive mode) in which the vehicle is driven using only the MG2 as a power source can be executed.

As shown in FIG. 3, the second oil pump OP2 is connected via the input member 3 to the internal combustion engine EG. Therefore, while the vehicle drive system 1 is executing the HV traveling mode (the vehicle is traveling in the HV traveling mode), the second oil pump OP2 is driven by the driving of the internal combustion engine EG, and the output member 4 and the second oil pump OP2 are driven. The rotation of the rotary electric machine MG2 drives the first oil pump OP1. Here, the oil discharged by the first oil pump OP1 is supplied to the supply oil passage 90, and also passes through the sixth oil passage 96 to the counter gear mechanism CG and the output differential gear device DF for lubrication. supplied to Oil discharged by the second oil pump OP2 is supplied to the supply oil passage 90 via the second discharge oil passage 82 . Normally, during execution of the HV driving mode, the discharge pressure of the second oil pump OP2 is higher than the discharge pressure of the first oil pump OP1. It is supplied to the oil passage 96 .

Therefore, in the HV driving mode, mainly the oil discharged from the second oil pump OP2 is supplied from the axial first side L1 to the second oil passage 92 (the inner peripheral portion 26I) via the third oil passage 93. be done. Since the oil supplied to the second oil passage 92 (inner peripheral portion 26I) in this way is cooled by the oil cooler OC while flowing through the supply oil passage 90, the cooling for cooling the second rotating electrical machine MG2 is It can be suitably used as an oil. Furthermore, while the vehicle drive system 1 is executing the HV driving mode, the differential input gear 65 rakes up the oil as the output member 4 rotates. The oil thus raked up is stored in the catch tank CT, and is supplied to the second oil passage 92 (the inner peripheral portion 26I) from the second axial side L2 via the seventh oil passage 97 . Therefore, while the vehicle drive system 1 is executing the HV drive mode, oil is supplied from both sides in the axial direction L to the second oil passage 92 (the inner peripheral portion 26I). is supplied to the second oil passage 92 (inner peripheral portion 26I).

On the other hand, while the vehicle drive system 1 is executing the EV traveling mode (the vehicle is traveling in the EV traveling mode), the differential input gear 65 rakes up the oil as the output member 4 rotates. The oil thus raked up is stored in the catch tank CT, and is supplied to the second oil passage 92 (the inner peripheral portion 26I) from the second axial side L2 via the seventh oil passage 97 . Here, while the vehicle drive system 1 is executing the EV driving mode, the oil is scraped up by the differential input gear 65, and in addition, the rotation of the output member 4 and the second electric rotating machine MG2 causes the first oil to flow. Pump OP1 is driven. However, for example, when the vehicle is traveling at a low speed, the rotation speed of the output member 4 is also low, and the amount of oil discharged by the first oil pump OP1 is relatively small. Further, the oil discharged by the first oil pump OP1 is supplied through the sixth oil passage 96 to the counter gear mechanism CG and the output differential gear device DF for lubrication.

Therefore, in the EV traveling mode, oil is mainly supplied from the catch tank CT through the seventh oil passage 97 to the second oil passage 92 (the inner peripheral portion 26I) from the axial second side L2. That is, in the EV traveling mode, there is no (or little) supply of oil to the second oil passage 92 (inner peripheral portion 26I) from the axial first side L1, and the oil is mainly supplied from the axial second side L2. A relatively small amount of oil is supplied to the second oil passage 92 (inner peripheral portion 26I).

[Detailed configuration of rotor for rotary electric machine]
Next, the detailed configuration of the rotating electrical machine rotor, here, the second rotor 24 of the second rotating electrical machine MG2 will be described.

As described above, the second rotor 24 includes the second rotor core 24A and the tubular second rotor shaft 26. The second rotor shafts 26 are aligned along the axial direction L and connected to each other. It has a tubular member 26A and a second tubular member 26B. As shown in FIG. 1, in this embodiment, the second rotor shaft 26 is rotatably supported by four bearings B with respect to the case 30 . Further, in the present embodiment, the first bearing B1 is the lubricated portion H, which is the lubrication target and is arranged on the first side L1 in the axial direction with respect to the second rotor core 24A. The second bearing B2 is arranged on the second axial side L2 with respect to the second rotor core 24A. This second bearing B2 is also preferably lubricated. In the illustrated example, the first tubular member 26A is supported by the first bearing B1 on the axial first side L1 with respect to the second rotor core 24A, and is supported on the axial second side L2 with respect to the second rotor core 24A. is supported by the second bearing B2. The second tubular member 26B is supported by a third bearing B3 on the first side L1 in the axial direction with respect to the output gear 60, and is supported by a fourth bearing B4 on the second side L2 in the axial direction with respect to the output gear 60. Supported by

In this embodiment, the first wall portion 31 has a tubular first boss portion 31A protruding to the axial second side L2. The first bearing B1 is supported by the inner peripheral surface of the first boss portion 31A and supports the outer peripheral surface of the second rotor shaft 26 (here, the first cylindrical member 26A). As described above, the first bearing B1 rotatably supports the second rotor shaft 26 on the axial first side L1 with respect to the second rotor core 24A. In this embodiment, as described above, the first bearing B1 corresponds to the "part to be lubricated H".

In addition, in the present embodiment, the second wall portion 32 has a tubular second boss portion 32A that protrudes toward the first side L1 in the axial direction. The second bearing B2 is supported by the inner peripheral surface of the second boss portion 32A and also supports the outer peripheral surface of the second rotor shaft 26 (here, the first tubular member 26A).

In this embodiment, the second wall portion 32 has, in addition to the second boss portion 32A, a cylindrical third boss portion 32B that protrudes to the axial second side L2. In the illustrated example, the third boss portion 32B is integrally formed with the second boss portion 32A. Protruding. The third bearing B3 is supported by the inner peripheral surface of the third boss portion 32B and also supports the outer peripheral surface of the second rotor shaft 26 (here, the second cylindrical member 26B).

In this embodiment, the case 30 includes a third wall portion 33 in addition to the first wall portion 31 and the second wall portion 32 . The third wall portion 33 is arranged on the second side L2 in the axial direction with respect to the counter gear mechanism CG and the second rotor shaft 26 (second tubular member 26B) in the case 30 . In the illustrated example, most of the second tubular member 26B of the second rotor shaft 26 is accommodated between the second wall portion 32 and the third wall portion 33 in the axial direction L. The counter gear mechanism CG described above is also housed between the second wall portion 32 and the third wall portion 33 in the axial direction L. In this embodiment, the third wall portion 33 has a tubular fourth boss portion 33A that protrudes toward the axial first side L1.
The fourth bearing B4 is supported by the inner peripheral surface of the fourth boss portion 33A and also supports the outer peripheral surface of the second rotor shaft 26 (here, the second cylindrical member 26B).

As shown in FIGS. 1 and 6 , the second rotor 24 has an oil supply section S that supplies oil to the second rotor shaft 26 . As described above, the second rotor shaft 26 has the inner peripheral portion 26I surrounded by the tubular inner peripheral surface F, and the oil supply section S supplies oil to the inner peripheral portion 26I. In addition, as described above, the inner peripheral portion 26I constitutes the second oil passage 92 .

In this embodiment, the oil supply section S includes a first supply section S1 and a second supply section S2. The first supply portion S1 supplies oil from the end portion of the second rotor shaft 26 on the first side L1 in the axial direction to the inner peripheral portion 26I. The second supply portion S2 supplies oil from the end portion of the second rotor shaft 26 on the second side L2 in the axial direction to the inner peripheral portion 26I. Here, the first supply portion S1 is formed at the downstream end of the third oil passage 93, and as shown in FIG. 5, the oil discharged from the first oil pump OP1 and the second oil pump The oil discharged from OP2 is supplied from the first supply portion S1 to the inner peripheral portion 26I. Further, the second supply portion S2 is formed at the downstream end portion of the seventh oil passage 97, and as shown in FIG. oil) is supplied to the inner peripheral portion 26I from the second supply portion S2.

As shown in FIGS. 1 and 6, the second rotor 24 has a lubricating oil passage 75 that supplies oil to the first bearing B1. In the present embodiment, the lubricating oil passage 75 includes an opening at the end of the second rotor shaft 26 (first cylindrical member 26A) on the axial first side L1 and and an axial end outer space between the end portion of the side L1 and the surface of the first wall portion 31 of the case 30 on the second axial side L2. Here, the shaft end outer space is a space surrounded by the first wall portion 31, the second rotor shaft 26, and the first bearing B1. As will be described later, a dam portion D (first dam portion D1) is formed inside the second rotor shaft 26, and the lubricating oil passage 75 extends axially from the dam portion D (first dam portion D1). It is arranged on the first side L1. The oil flowing out from the weir D (first weir D1) of the second rotor shaft 26 to the first axial side L1 passes through the lubricating oil passage 75 and is guided to the first bearing B1 to lubricate the first bearing B1. do.

As shown in FIG. 6, the second rotor shaft 26 has an opening 72A that opens to the inner peripheral surface F, and is oriented in a radial direction (a radial direction with respect to the second shaft A2, hereinafter referred to as [details of rotor for rotating electric machine)]. Configuration], and a radial oil passage 72 extending along the same. The opening 72</b>A is formed at the radial inner end of the radial oil passage 72 . A radially outer end of the radial oil passage 72 is open to the outer peripheral surface of the second rotor shaft 26 . In this embodiment, the second rotor shaft 26 is provided with a plurality of radial oil passages 72 distributed in the circumferential direction, and a plurality of openings 72A are formed along the circumferential direction on the inner peripheral surface F. . In the illustrated example, the plurality of openings 72A are arranged in a line along the circumferential direction at the same position in the axial direction L. As shown in FIG. The oil supplied to the inner peripheral portion 26I enters the radial oil passage 72 through the opening 72A, passes through the radial oil passage 72, is guided to the second rotor core 24A, and cools the second rotor core 24A.

As shown in FIG. 6, the second rotor shaft 26 protrudes radially inward from the inner peripheral surface F and extends along the inner peripheral surface F in the circumferential direction. It has D1. The first dam portion D1 is arranged on the axial first side L1 relative to the opening portion 72A. The oil supply portion S (first supply portion S1) is configured to supply oil to the second side L2 in the axial direction from the first weir portion D1 in the inner peripheral portion 26I. Therefore, in the illustrated example, the first supply portion S1 is provided so as to open on the second side L2 in the axial direction from the first dam portion D1. In this embodiment, the first dam portion D1 is configured by a member separate from the second rotor shaft 26 (the first tubular member 26A), and is press-fitted radially inwardly of the second rotor shaft 26. It is mounted inside the second rotor shaft 26 . However, without being limited to such a configuration, the first dam portion D1 may be formed integrally with the second rotor shaft 26 (first cylindrical member 26A) by, for example, casting. good. Alternatively, the first dam portion D1 may be formed by cutting or the like.

In this embodiment, the second rotor shaft 26 is arranged on the second axial side L2 of the opening 72A, protrudes radially inward from the inner peripheral surface F, and extends circumferentially along the inner peripheral surface F. It further comprises an annular second weir portion D2 arranged to extend. A space between the first weir portion D1 and the second weir portion D2 in the axial direction L serves as an in-shaft storage portion for storing oil. The opening 72A is arranged so as to open to this in-shaft reservoir. Therefore, the oil stored in the in-shaft storage portion between the first weir portion D1 and the second weir portion D2 efficiently flows into the opening portion 72A due to the centrifugal force or the like caused by the rotation of the second rotor shaft 26. can be made Therefore, in a state in which oil is stored in the in-shaft reservoir, the amount of oil required for cooling the second rotor core 24A is supplied from the opening 72A through the radial oil passage 72 to the second rotor core. 24A can be supplied. In this embodiment, the second dam portion D2 is formed by a step portion provided in the spline fitting portion for spline fitting the first tubular member 26A and the second tubular member 26B as described above. ing. However, without being limited to such a configuration, the second dam portion D2 may be configured by a simple stepped portion unrelated to the spline fitting portion.
Alternatively, the second weir D2 may be an annular member attached to the inner peripheral surface F of the second rotor shaft 26, like the first weir D1.

With such a configuration, oil can be stored in the inner peripheral portion 26I, and a sufficient amount of oil can be supplied to the radial oil passage 72 to cool the second rotor core 24A. On the other hand, as described above, the lubricating oil passage 75 for supplying oil to the first bearing B1 is arranged on the first side L1 in the axial direction from the first dam D1. Therefore, the oil blocked by the first dam portion D1 is more difficult to flow toward the axial first side L1 than the first dam portion D1, and the first bearing B1 may not be sufficiently lubricated. .

Therefore, as shown in FIG. 6, the second rotor 24 is provided on the inner peripheral surface F or the weir D, and the portion of the inner peripheral portion 26I on the first side L1 in the axial direction from the weir D and the weir D. It also has an axial communication passage LGr that communicates with the portion on the second axial side L2. In this embodiment, the axial communication passage LGr is provided in the inner peripheral surface F, is recessed radially outward, and extends in the axial direction L through the weir portion D radially outward. ing. The axial communication passage LGr communicates with the lubricating oil passage 75 . In this embodiment, the axial communication path LGr extends from the axial second side L2 to the axial first side L1 with respect to the first dam portion D1 through the radially outer side of the first dam portion D1. and communicates with the lubricating oil passage 75 . As a result, the oil supplied to the inner peripheral portion 26I flows into the axial communication passage LGr on the axial second side L2 of the first weir portion D1, and the axial communication passage LGr flows into the axial direction first side L1. and flows into the lubricating oil passage 75 arranged on the first side L1 in the axial direction of the first weir portion D1. The oil that has flowed into the lubricating oil passage 75 is supplied to the first bearing B1 and lubricates the first bearing B1. Therefore, according to this configuration, oil can be supplied to both the radial oil passage 72 and the lubricating oil passage 75, and both the cooling of the second rotor core 24A and the lubrication of the first bearing B1 can be performed appropriately. . In this embodiment, the axial communication passage LGr is formed continuously from the portion on the second axial side L2 of the first dam portion D1 to the end portion on the first axial side L1 of the second rotor shaft 26. there is

In this embodiment, a plurality of axial communication passages LGr are arranged side by side in the circumferential direction of the inner peripheral surface F. As shown in FIG. In this example, as shown in FIG. 7, four axial communication paths LGr are arranged in the circumferential direction at regular intervals (90° intervals). In the illustrated example, each of the axial communication passages LGr is formed in a groove shape having a rectangular cross section when viewed in the axial direction L. Note that the cross-sectional shape of the axial communication passage LGr is not limited to this, and may be a groove shape of various shapes such as an arc shape and various polygonal shapes. As a result, regardless of the position of the second rotor shaft 26 in the rotational direction, the axial communication passage LGr can guide the oil to the first axial side L1 rather than the first weir portion D1. However, without being limited to the configuration described above, the plurality of axial communication paths LGr may be arranged such that the arrangement intervals in the circumferential direction are uneven. Further, the number of axial communication passages LGr is arbitrary, and may be 1 to 3, or may be 5 or more. FIG. 8 shows a developed view in which the inner peripheral portion 26I is developed in a range of 180° in the circumferential direction, and two axial communication passages LGr out of the four axial communication passages LGr are shown. there is

As shown in FIGS. 6 and 8, in the present embodiment, the end portion of the axial direction second side L2 of the axial communication passage LGr is arranged on the axial direction second side L2 relative to the opening 72A. This makes it easier for the oil on the axial second side L2 to enter the axial communication passage LGr before entering the opening 72A. Therefore, even when the amount of oil supplied to the inner peripheral portion 26I is small, such as when the vehicle drive system 1 is executing the EV driving mode, oil is preferentially supplied to the axial communication passage LGr. It will be. Therefore, even when the amount of oil supplied to the inner peripheral portion 26I is small, the first bearing B1 can be properly lubricated. The end portion of the axial direction second side L2 of the axial communication passage LGr is arranged on the axial direction first side L1 relative to the second dam portion D2.

As shown in FIGS. 6 and 8, in the present embodiment, the axial communication path LGr and the opening 72A are arranged such that, at the same position in the axial direction L, the axial communication path LGr and the opening 72A are located at different circumferential positions. A portion 72A is arranged. Specifically, the plurality of axial communication passages LGr and the plurality of openings 72A are arranged such that the axial communication passages LGr are arranged between a pair of openings 72A adjacent in the circumferential direction. With this configuration, the oil that has once entered the axial communication passage LGr does not flow into the opening 72A. can. Therefore, it is possible to appropriately perform both cooling of the second rotor core 24A and lubrication of the first bearing B1.

As described above, according to the configuration of the present embodiment, from the first supply portion S1 (the third oil passage 93) or the second supply portion S2 (the seventh oil passage 97) to the inner peripheral portion 26I (the second oil passage 92 ) can be retained in the inner peripheral portion 26I between the first weir portion D1 and the second weir portion D2. For example, while the vehicle drive system 1 is executing the EV driving mode, oil is supplied to the inner peripheral portion 26I from the second supply portion S2 (seventh oil passage 97) as described above. will account for the majority, and the amount of oil supplied to the inner peripheral portion 26I will be relatively small. Even in such a case, the oil can preferentially flow through the lubricating oil path 75 via the axial communication path LGr, and the oil for lubricating the first bearing B1 can be appropriately secured. On the other hand, for example, while the vehicle drive system 1 is executing the HV driving mode, the supply of oil to the inner peripheral portion 26I is performed by the first supply portion S1 (the third oil passage 93) and the second The oil is supplied from both of the supply portion S2 (seventh oil passage 97), and the amount of oil supplied to the inner peripheral portion 26I is relatively large. In this case, the amount of oil supplied to the inner peripheral portion 26I is greater than the amount of oil flowing through the axial communication passage LGr at the inner peripheral portion 26I, and as a result, the oil flows through the first weir portion D1 and the second weir. It is stored in the inner peripheral portion 26I between the portion D2. The oil stored in this manner is efficiently supplied to the radial oil passage 72 by centrifugal force or the like that accompanies the rotation of the second rotor shaft 26 . Therefore, in such a case, both the lubrication of the first bearing B1 and the cooling of the second rotor core 24A can be performed appropriately.

2. 2nd Embodiment Next, 2nd Embodiment of the rotor for rotary electric machines is described. Differences from the above-described first embodiment will be mainly described below. Points that are not particularly described are the same as those of the first embodiment.

FIG. 9 shows a developed view in which the inner peripheral portion 26I of the rotor for a rotary electric machine (second rotor 24) according to this embodiment is developed in the circumferential direction within a range of 180°.

As shown in FIG. 9, in this embodiment, the second rotor 24 has a circumferential groove CGr provided in the inner peripheral surface F and extending in the circumferential direction. In the illustrated example, the circumferential groove CGr extends in the circumferential direction so as to be orthogonal to the axial direction L. As shown in FIG. In this embodiment, the circumferential groove CGr is provided continuously over the entire inner circumferential surface F in the circumferential direction. However, without being limited to such a configuration, the circumferential groove CGr may be provided in a partial region in the circumferential direction of the inner peripheral surface F, or may be intermittently provided.

In this embodiment, the circumferential groove CGr is arranged on the axial second side L2 of the opening 72A and is connected to the axial communication path LGr. The oil guided to the circumferential groove CGr is guided to the axial communication passage LGr. Therefore, according to this configuration, the oil supplied to the second axial side L2 of the circumferential groove CGr enters the circumferential groove CGr before entering the opening 72A, and is guided from there to the axial communication passage LGr. be killed. Therefore, the oil on the second axial side L2 of the circumferential groove CGr can be guided to the axial communication passage LGr with priority over the radial oil passage 72 . Therefore, even when the amount of oil supplied to the inner peripheral portion 26I is small, such as when the vehicle drive system 1 is executing the EV driving mode, the first bearing B1 can be properly lubricated.

Here, it is preferable that the circumferential groove CGr is connected to at least two axial communication passages LGr. In this embodiment, all the axial communication paths LGr (four axial communication paths LGr) are connected to the circumferential grooves CGr. Accordingly, even when the amount of oil supplied to the inner peripheral portion 26I is small, the oil can be easily supplied to the axial communication passage LGr, and the first bearing B1 can be lubricated more reliably.

3. Other Embodiments Next, other embodiments of the rotor for rotary electric machine will be described.

(1) In each of the embodiments described above, the configuration in which the end portion of the axial direction second side L2 of the axial communication passage LGr is arranged on the axial direction second side L2 relative to the opening 72A has been described as an example. However, without being limited to such a configuration, for example, as shown in FIG. Alternatively, it may be arranged at the same position as the opening 72A in the axial direction L (not shown).

(2) In each of the above embodiments, the axial communication path LGr continues from the portion on the second axial side L2 of the first dam portion D1 to the end of the second rotor shaft 26 on the first axial side L1. An example of a configuration that is formed in a uniform manner has been described. However, without being limited to such a configuration, the axial communication path LGr extends from the first dam portion D1 to the axial first side L1 and from the first dam portion D1 to the axial second side L2. For example, as shown in FIG. 11, it may be formed only in a region that overlaps with the first dam portion D1 when viewed in the radial direction and regions on both sides in the axial direction L thereof. In this case, a lubricating oil passage 75 is formed from the axial first side L1 end of the axial communication passage LGr to the first bearing B1 (see FIG. 6).

(3) In each of the above embodiments, the axial communication path LGr extends straight along the axial direction L, and the axial communication path LGr and the opening 72A are positioned at the same position in the axial direction L in the circumferential direction. The configuration in which the plurality of axial communication passages LGr and the plurality of openings 72A are arranged such that the distances are different has been described as an example. However, the axial communication passage LGr may extend in a direction inclined with respect to the axial direction L, without being limited to such a configuration. In this case, at different positions in the axial direction L (positions separated in the axial direction L), the axial communication passages LGr and the opening 72A are arranged at the same circumferential position. A plurality of openings 72A may be arranged.

(4) In each of the above embodiments, the axial communication passage LGr is provided in the inner peripheral surface F of the second rotor shaft 26, is recessed radially outward, and extends in the axial direction L. explained. However, without being limited to such a configuration, the axial communication passage LGr may be provided in the dam portion D (first dam portion D1) as shown in FIGS. 12 to 16, for example. In this case, the axial communication passage LGr is preferably formed in a groove shape or a hole shape so as to pass through the dam portion D (the first dam portion D1) in the axial direction L. Here, FIGS. 13 to 16 show cross-sectional views perpendicular to the axis when the rotor shaft 26 is cut along a plane perpendicular to the axial direction L. FIG. For example, as shown in FIGS. 12 and 13, the axial communication passage LGr is provided on the outer peripheral surface of the dam portion D (first dam portion D1) so as to be recessed radially inward and extend in the axial direction L. It can be formed in a groove shape. In the illustrated example, the axial communication passage LGr is formed in a groove shape having an arc-shaped cross section with an open radially outer side when viewed in the axial direction L. As shown in FIG. Further, as shown in FIG. 14, the axial communication passage LGr may be formed in a groove shape having a rectangular cross section with an open radially outer side when viewed in the axial direction L. As shown in FIG. Alternatively, as shown in FIG. 15, the axial communication passage LGr can be formed in the shape of a through hole penetrating in the axial direction L at a radially intermediate portion of the dam portion D (first dam portion D1). In the illustrated example, the axial communication passage LGr is formed in the shape of a hole having a circular cross section when viewed in the axial direction L. As shown in FIG. Note that the cross-sectional shape of the through-hole-shaped axial communication path LGr is not limited to this, and may be various shapes such as various polygonal shapes (triangle, square, etc.) and elliptical shapes (not shown). ). 13 to 15 exemplify a configuration in which two axial communication paths LGr are provided in the dam portion D (first dam portion D1) at intervals in the circumferential direction. However, without being limited to such a configuration, as shown in FIG. It's okay to be. Alternatively, only one dam portion D (first dam portion D1) may be provided (not shown).

(5) In each of the above-described embodiments, the configuration in which the lubricated portion H is the bearing B (first bearing B) that rotatably supports the rotor shaft 26 has been described as an example. However, without being limited to such a configuration, various parts to be lubricated in the vehicle drive device can serve as the lubricated portion H. Preferably, the lubricated portion H is a portion where members slide against each other, such as a meshing portion of a gear mechanism, a bearing, or the like.

(6) In each of the embodiments described above, the second rotor shaft 26 has been described as an example having both the first dam portion D1 and the second dam portion D2. However, without being limited to such a configuration, the second rotor shaft 26 may be provided with at least the first dam portion D1.

(7) It should be noted that the configurations disclosed in the respective embodiments described above can be applied in combination with configurations disclosed in other embodiments as long as there is no contradiction. Regarding other configurations, the embodiments disclosed in this specification are merely examples in all respects. Therefore, various modifications can be made as appropriate without departing from the scope of the present disclosure.

4. Overview of the above-described embodiment An overview of the above-described rotor for a rotating electrical machine and a vehicle drive device including the rotor for a rotating electrical machine will be described below.

The rotary electric machine rotor (24) is a cylindrical rotor that penetrates a rotor core (24A) and is connected to the rotor core (24A) through a radially inner side of the rotor core (24A) and extends along the axial direction (L). A shaft (26), an oil supply section (S) that supplies oil to the rotor shaft (26), one side of the axial direction (L) defined as an axial direction first side (L1), and the axial direction (L ) is the second axial side (L2), a lubricated portion (H) to be lubricated, which is arranged on the axial first side (L1) with respect to the rotor core (24A), and the lubricated portion ( H), the rotor shaft (26) includes an inner peripheral portion (26I) surrounded by a tubular inner peripheral surface (F) thereof, and the inner peripheral portion (26I) surrounded by the cylindrical inner peripheral surface (F) A radial oil passage (72) having an opening (72A) open to a peripheral surface (F) and extending along the radial direction, and a first axial side (L1) of the opening (72A). an annular weir portion (D) arranged so as to protrude radially inward from the inner peripheral surface (F) and extend in the circumferential direction along the inner peripheral surface (F); and an axial communication passage (LGr), wherein the oil supply portion (S) supplies oil to the second axial side (L2) of the inner peripheral portion (26I) from the weir portion (D). The lubricating oil passage (75) is arranged on the first side (L1) in the axial direction from the weir (D), and the axial communication passage (LGr) is located on the inner peripheral surface (F) or A portion of the inner peripheral portion (26I) on the axial first side (L1) of the weir portion (D) and a portion of the weir portion (D) on the axial first side (L1) of the weir portion (D). It communicates with the 2 side (L2) portion and communicates with the lubricating oil passage (75).

According to this configuration, the oil supplied to the inner peripheral portion (26I) of the rotor shaft (26) can be retained in the inner peripheral portion (26I) by the weir portion (D). Therefore, the oil can be appropriately supplied to the radial oil passage (72) through the opening (72A) opening in the inner peripheral surface (F) of the rotor shaft (26). It becomes possible to properly cool the arranged rotor core (24A). Further, according to this configuration, the portion of the inner peripheral portion (26I) on the first side (L1) in the axial direction from the weir portion (D) and the portion on the second side (L2) in the axial direction from the weir portion (D) from the region on the second side (L2) in the axial direction of the weir (D) in the inner peripheral portion (26I) to the first side in the axial direction of the weir (D). Oil can be supplied to the lubricating oil passage (75) of (L1). Therefore, the lubricated portion (H) arranged on the first side (L1) in the axial direction with respect to the rotor core (24A) can also be appropriately supplied with oil, and the lubricated portion (H) can be properly lubricated. becomes possible.

Here, it is preferable that the lubricated portion (H) is a bearing (B) that rotatably supports the rotor shaft (26).

According to this configuration, the oil supplied to the lubricating oil passage (75) can appropriately lubricate the bearing (B) that supports the rotor shaft (26).

In addition, it is preferable that the end portion of the axial direction second side (L2) of the axial communication passage (LGr) is disposed closer to the axial direction second side (L2) than the opening portion (72A). be.

According to this configuration, it is easier to supply the oil on the axial second side (L2) to the axial communication passage (LGr) than the opening (72A). Therefore, even if the amount of oil supplied to the inner peripheral portion (26I) is small, the oil can be supplied to the axial communication passage (LGr), and the lubricated portion (H) can be properly lubricated.

Further, it is preferable that the axial communication passage (LGr) and the opening (72A) are different in circumferential position at the same position in the axial direction (L).

According to this configuration, oil flowing through the axial communication passage (LGr) does not flow into the radial oil passage (72) through the opening (72A). Therefore, the oil flowing through the axial communication passage (LGr) can be separated from the oil flowing through the radial oil passage (72). Therefore, both the oil supply to the radial oil passage (72) through the opening (72A) and the oil supply to the lubricating oil passage (75) through the axial communication passage (LGr) can be properly controlled. can be done.

Here, the axial communication passage (LGr) is provided in the inner peripheral surface (F), is recessed radially outward, and passes radially outward with respect to the weir portion (D) to extend in the axial direction. It is preferable that it is formed so as to extend to (L).

According to this configuration, the axial communication passage (LGr) provides a portion of the inner peripheral portion (26I) on the first side (L1) of the weir portion (D) in the axial direction and a portion on the first axial side (L1) of the weir portion (D). 2 side (L2) can be communicated appropriately. Therefore, from the region on the second axial side (L2) of the weir (D) in the inner peripheral portion (26I) to the lubricating oil passage (75) on the first axial side (L1) of the weir (D). can supply oil.

Further, a circumferential groove (CGr) provided in the inner peripheral surface (F) and extending in the circumferential direction is further provided, and the circumferential groove (CGr) is located in the second axial direction relative to the opening (72A). It is preferably arranged on the side (L2) and connected to the axial communication passage (LGr).

According to this configuration, it is easier to supply the oil on the axial second side (L2) to the axial communication passage (LGr) than the opening (72A). Therefore, even if the amount of oil supplied to the inner peripheral portion (26I) is small, the oil can be supplied to the axial communication passage (LGr), and the lubricated portion (H) can be properly lubricated.

Further, a plurality of the axial communication passages (LGr) are arranged side by side in the circumferential direction of the inner peripheral surface (F), and the circumferential groove (CGr) is formed in at least two of the axial communication passages (LGr). ).

According to this configuration, it becomes easier to supply the oil on the axial second side (L2) of the opening (72A) to the axial communication passage (LGr). Therefore, even if the amount of oil supplied to the inner peripheral portion (26I) is small, a sufficient amount of oil can be supplied to the axial communication passage (LGr), and the lubricated portion (H) can be properly lubricated. can be done.

Here, it is preferable that the axial communication passage (LGr) is formed so as to pass through the dam portion (D) in the axial direction (L).

According to this configuration, the axial communication passage (LGr) provides a portion of the inner peripheral portion (26I) on the first side (L1) of the weir portion (D) in the axial direction and a portion on the first axial side (L1) of the weir portion (D). 2 side (L2) can be communicated appropriately. Therefore, from the region on the second axial side (L2) of the weir (D) in the inner peripheral portion (26I) to the lubricating oil passage (75) on the first axial side (L1) of the weir (D). can supply oil.

Further, the oil supply section (S) includes a first supply section (S1) and a second supply section (S2), and the first supply section (S1) extends along the axial direction of the rotor shaft (26). Oil is supplied from the end of the first side (L1) to the inner peripheral portion (26I), and the second supply portion (S2) is provided on the axial second side (L2) of the rotor shaft (26). It is preferable to supply oil to the inner peripheral portion (26I) from the end portion.

According to this configuration, it becomes easier to appropriately supply oil to the inner peripheral portion (26I). In addition, by configuring the first supply section (S1) and the second supply section (S2) to be connected to different hydraulic circuits, the pressure to the inner peripheral portion (26I) can be adjusted according to the operating state of the rotating electric machine. It is also possible to make the supply state of the oil different.

Further, the dam portion (D) is a first dam portion (D1), and is arranged on the second side (L2) in the axial direction from the opening (72A). It is preferable to further include an annular second dam portion (D2) arranged so as to protrude radially inward and extend in the circumferential direction along the inner peripheral surface (F).

According to this configuration, the oil can be appropriately stored in the inner peripheral portion (26I). Therefore, it is possible to appropriately supply both the oil to the radial oil passage (72) and the lubricating oil passage (75).

Here, the vehicle driving device (1) is
A rotary electric machine (MG2) including the rotary electric machine rotor (24) having the above configuration, and an oil pump (OP) for supplying oil to the oil supply section (S), wherein the oil pump (OP) A first oil pump (OP1) is drivingly connected to the rotor shaft (26) and driven by the rotation of the rotor shaft (26).

According to this configuration, the oil is supplied to the oil supply portion (S) by rotating the rotor shaft (26). Therefore, according to this configuration, it is possible to appropriately supply oil as lubricating oil to the lubricated portion (H) that needs to be lubricated with oil as the rotor shaft (26) rotates. Therefore, when the vehicle travels by rotating the wheels (W) using the rotary electric machine (MG2) as a power source, the oil pump (OP) is driven during travel to supply oil to the inner peripheral portion (26I). can do.

Further, the vehicle drive device (1) configured as described above includes:
Equipped with an internal combustion engine (EG) and the rotating electric machine (MG2) as a driving force source for the wheels (W),
Preferably, the oil pump (OP) includes a second oil pump (OP2) that is drivingly connected to the internal combustion engine (EG) and driven by the internal combustion engine (EG).

According to this configuration, the second oil pump (OP2) can be driven when the vehicle travels by rotating the wheels (W) using at least the internal combustion engine (EG) as a power source. Oil can be supplied to the inner peripheral portion (26I) by (OP2). Further, in the case where the rotor shaft (26) is configured to rotate while the vehicle using the internal combustion engine (EG) as a power source is running, the vehicle using at least the internal combustion engine (EG) as the power source as described above. , both the first oil pump (OP1) and the second oil pump (OP2) can be driven, and the amount of oil supplied to the inner peripheral portion (26I) can be increased. Become.

The technology according to the present disclosure can be used in a rotating electric machine rotor and a vehicle drive device including the rotating electric machine rotor.

1: Vehicle Drive Device EG: Internal Combustion Engine MG2: Second Rotating Electric Machine (Rotating Electric Machine)
OP: oil pump OP1: first oil pump OP2: second oil pump 24: second rotor (rotor for rotary electric machine)
24A: Second rotor core (rotor core)
26: Second rotor shaft (rotor shaft)
26I: inner peripheral portion 72: radial oil passage 72A: opening 75: lubricating oil passage B1: first bearing (bearing)
CGr: Circumferential groove LGr: Axial communication path D: Dam portion D1: First dam portion D2: Second dam portion F: Inner peripheral surface H: Lubricated portion L: Axial direction L1: Axial direction first side L2: Axial direction second side S: oil supply part S1: first supply part S2: second supply part

Claims (12)

a rotor core;
a cylindrical rotor shaft that penetrates the radially inner side of the rotor core and is connected to the rotor core and extends along the axial direction;
an oil supply unit that supplies oil to the rotor shaft;
a lubricated portion to be lubricated disposed on the first side in the axial direction with respect to the rotor core, with the one side in the axial direction as the first side in the axial direction and the other side in the axial direction as the second side in the axial direction;
a lubricating oil passage that supplies oil to the lubricated portion,
The rotor shaft is
an inner peripheral portion surrounded by the cylindrical inner peripheral surface;
a radial oil passage having an opening opening in the inner peripheral surface and extending along the radial direction;
An annular weir disposed on the first side in the axial direction of the opening, projecting radially inward from the inner peripheral surface and extending in the circumferential direction along the inner peripheral surface. and,
an axial communication passage,
The oil supply portion supplies oil to the second side in the axial direction of the weir portion in the inner peripheral portion,
The lubricating oil passage is arranged on the first side in the axial direction with respect to the weir,
The axial communication passage is provided in the inner peripheral surface or the dam portion, and is provided in a portion of the inner peripheral portion on the axial first side of the dam portion and on the axial second side of the dam portion. a rotor for a rotary electric machine, communicating with a portion and communicating with the lubricating oil passage. 2. The rotor for a rotary electric machine according to claim 1, wherein said lubricated portion is a bearing that rotatably supports said rotor shaft. 3. The apparatus according to claim 1, wherein an end portion of the axial communication passage provided in the inner peripheral surface on the second side in the axial direction is arranged on the second side in the axial direction with respect to the opening portion. Rotor for rotary electric machine. 4. The rotor for a rotary electric machine according to claim 3, wherein, at the same position in the axial direction, the axial communication passage provided in the inner peripheral surface and the opening are different in position in the circumferential direction. 2. The axial communication passage provided in the inner peripheral surface is formed so as to be recessed radially outward and extend in the axial direction through the weir portion radially outwardly. 5. The rotor for rotary electric machine according to any one of 4 to 4. Further comprising a circumferential groove provided on the inner peripheral surface and extending in the circumferential direction,
6. The rotor for a rotary electric machine according to claim 5, wherein said circumferential groove is arranged on the second axial side of said opening and is connected to said axial communication passage provided in said inner peripheral surface. . A plurality of the axial communication passages provided on the inner peripheral surface are arranged side by side in the circumferential direction of the inner peripheral surface,
7. The rotor for a rotary electric machine according to claim 6, wherein said circumferential groove is connected to at least two of said axial communicating passages provided in said inner peripheral surface . The rotor for a rotary electric machine according to any one of claims 1 to 4, wherein the axial communication passage provided in the dam portion is formed so as to penetrate the dam portion in the axial direction. The oil supply unit includes a first supply unit and a second supply unit,
The first supply portion supplies oil from an end portion of the rotor shaft on the first side in the axial direction to the inner peripheral portion,
The rotor for a rotary electric machine according to any one of claims 1 to 8, wherein the second supply portion supplies oil to the inner peripheral portion from an end portion of the rotor shaft on the second side in the axial direction. The weir portion is a first weir portion,
An annular second ring disposed on the second side in the axial direction of the opening, protruding radially inward from the inner peripheral surface and extending in the circumferential direction along the inner peripheral surface. The rotor for rotary electric machine according to any one of claims 1 to 9, further comprising a weir. A rotary electric machine comprising the rotor for rotary electric machine according to any one of claims 1 to 10;
and an oil pump that supplies oil to the oil supply unit,
The vehicle driving device, wherein the oil pump includes a first oil pump that is drivingly connected to the rotor shaft and driven by rotation of the rotor shaft. Equipped with an internal combustion engine and the rotating electric machine as a driving force source for the wheels,
12. The vehicle drive system according to claim 11, wherein said oil pump includes a second oil pump that is drivingly connected to said internal combustion engine and driven by the driving force of said internal combustion engine.

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