JP2020028213A - Rotor for rotary electric machine and vehicle drive device including the rotor for rotary electric machine - Google Patents

Abstract

To provide: a rotor for a rotary electric machine, capable of both cooling a rotor core disposed on the radially outer side of a rotor shaft and lubricating a bearing supporting the rotor shaft, appropriately; and a vehicle drive device including the rotor for the rotary electric machine.SOLUTION: A rotor 24 for a rotary electric machine includes a rotor shaft 26, an oil supply part S, a portion H to be lubricated, and a lubrication oil path 75. The rotor shaft 26 includes: an inner peripheral portion 26I surrounded by an inner peripheral surface F; radial oil paths 72 having openings 72A that open in the inner peripheral surface F; an annular weir portion D disposed so as to project radially inward from the inner peripheral surface F and extend in the circumferential direction; and axial communication paths LGr. The axial communication paths LGr are provided in the inner peripheral surface F or the weir portion D, and communicate between a portion of the inner peripheral portion 26I on a first axial side L1 with respect to the weir portion D and a portion thereof on a second axial side L2 with respect to the weir portion D, and also communicate with the lubrication oil path 75.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a rotating electric machine rotor and a vehicle drive device provided with the rotating electric machine rotor.

  Conventionally, an inner peripheral portion formed radially inside a cylindrical rotor shaft that penetrates a rotor of a rotating electric machine is used as an oil passage to which oil is supplied, and a radial direction from the inner peripheral portion along a radial direction is used. There is known a structure for guiding oil to a rotor core through an oil passage. For example, Japanese Patent Application Laid-Open No. 2014-239627 discloses an inner peripheral portion (90) formed radially inside a cylindrical rotor shaft (3), and an inner peripheral portion (90) and an outer periphery of the rotor shaft (3). A rotary electric machine rotor (2) including a radial oil passage (91) penetrating through a surface along a radial direction (R) and communicating with a rotor core (10) is disclosed. (See FIG. 2 etc. In the background art, reference numerals in parentheses are those of the referenced document.) The oil supplied to the inner peripheral portion (90) flows through the radial oil passage (91) by centrifugal force caused by 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 magnet (5) embedded in the rotor core (10) by heat exchange with the rotor core (10).

JP 2014-239627 A

  Here, in order to guide a sufficient amount of oil for cooling the permanent magnet (5) from the inner peripheral portion (90) to the rotor core (10) via the radial oil passage (91), for example, It is conceivable to provide a weir section for blocking oil in the section (90) and store the oil in the inner peripheral section (90). However, the oil in the inner peripheral portion (90) is used not only for cooling the permanent magnet (5) but also for lubricating a lubricated portion to be lubricated. For example, the oil in the inner peripheral portion (90) flows along the inner peripheral portion (90) in the axial direction (L), and lubricates the bearing that supports the rotor shaft (3) at the end in the axial direction (L). Sometimes used as oil. In such a case, if a weir is provided in the inner peripheral part (90) to restrict the oil flow along the axial direction (L), the oil does not flow to the bearing as the part to be lubricated, and lubrication here is prevented. In some cases, it cannot be performed sufficiently.

  In view of the above situation, a rotor for a rotating electric machine and a rotor for a rotating electric machine capable of appropriately performing both cooling of a rotor core arranged radially outside a rotor shaft and lubrication of a lubricated portion to be lubricated. It is desired to realize a vehicle drive device having a rotor.

  In view of the above, the characteristic configuration of the rotor for a rotating electrical machine includes a rotor core, a cylindrical rotor shaft penetrating radially inside of the rotor core, connected to the rotor core, and extending along the axial direction, and oil on the rotor shaft. And a lubrication unit disposed on the first axial side with respect to the rotor core, with one side in the axial direction being the first axial side and the other side in the axial direction being the second axial side. A lubricating portion to be lubricated, and a lubricating oil passage for supplying oil to the lubricated portion, wherein the rotor shaft has an inner peripheral portion surrounded by a cylindrical inner peripheral surface, and the inner peripheral surface. A radial oil passage having an opening that opens in the radial direction and extending along the radial direction, and disposed on the first axial side with respect to the opening, and protruding radially inward from the inner peripheral surface; An annular arrangement arranged circumferentially along the inner peripheral surface A dam portion, and an axial communication passage, wherein the oil supply portion supplies oil to the second axial side of the inner peripheral portion with respect to the dam portion, and the lubricating oil passage comprises the dam portion. And the axial communication passage is provided on the inner peripheral surface or the weir portion, and a portion of the inner peripheral portion on the axial first side than the weir portion. It is in communication with the portion on the second axial side of the weir and at the same time as communicating with the lubricating oil passage.

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

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

Sectional view of the vehicle drive device according to the embodiment. Partial enlarged view of FIG. Skeleton diagram of the vehicle drive device according to the embodiment The figure which shows the arrangement | positioning relationship in the axial direction view of each component of the vehicle drive device which concerns on embodiment. Simplified diagram of a hydraulic circuit according to an embodiment Partial enlarged view of FIG. Cross-section orthogonal to the axis of the rotor shaft according to the embodiment Exploded schematic diagram with the rotor shaft expanded in the circumferential direction FIG. 2 is a development schematic diagram in which a rotor shaft according to a second embodiment is developed in a circumferential direction. Exploded schematic diagram in which a rotor shaft according to another embodiment is developed in a circumferential direction. Axial sectional view of a main part of a rotor for a rotating electrical machine according to another embodiment. Axial sectional view of a main part of a rotor for a rotating electrical machine according to another embodiment. Cross-sectional view orthogonal to the axis of the rotor shaft according to another embodiment Cross-sectional view orthogonal to the axis of the rotor shaft according to another embodiment Cross-sectional view orthogonal to the axis of the rotor shaft according to another embodiment Cross-sectional view orthogonal to the axis of the rotor shaft according to another embodiment

1. First Embodiment A first embodiment of a rotor for a rotating electrical machine will be described by way of an example in which the rotor for a rotating electrical machine is applied to a vehicle drive device. In the following embodiment, the second rotor 24 provided in the second rotating electrical machine MG2 corresponds to a “rotating electrical machine rotor”. Accordingly, hereinafter, the second rotor core 24A corresponds to a “rotor core”, and the second rotor shaft 26 corresponds to a “rotor shaft”.

  In the following description, the vertical direction V (see FIG. 4) refers to the vertical direction in the use state of the rotary electric machine, that is, the vertical direction when the rotary electric machine is arranged in the direction in the use state. 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. The terms “upper” and “lower” mean the upper and lower sides in the vertical direction V. In addition, the directions of the respective members in the following description represent directions in a state where they are assembled to a device (in the present embodiment, a vehicle driving device) provided with a rotating electric machine. Note that terms relating to dimensions, arrangement directions, arrangement positions, and the like of the respective members are concepts including a state in which there is a difference due to an error (an error that is allowable in manufacturing).

  In this specification, “drive 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 integrally, and a state in which two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members. . Such transmission members include various members (shafts, gear mechanisms, belts, chains, etc.) that transmit rotation at the same speed or at a variable speed, and an engagement device that selectively transmits rotation and driving force. (A friction engagement device, a meshing engagement device, etc.) may be included. However, the term "drive connection" for each rotating element of the planetary gear mechanism means a state in which three rotating elements included in the planetary gear mechanism are drivingly connected to each other without passing through another rotating element. .

  Further, in this specification, the “rotary electric machine” is used as a concept including any of a motor (electric motor), a generator (generator), and a motor generator that performs both functions of a motor and a generator as necessary. . Further, in the present specification, regarding the arrangement of two members, “overlap in a specific direction” means that when a virtual straight line parallel to the line of sight is moved in each direction orthogonal to the virtual line, This means that at least a region where the virtual straight line intersects both of the two members exists.

(Schematic configuration of vehicle drive device)
A schematic configuration of the vehicle drive device 1 will be described. The vehicle drive device 1 is a device that transmits a driving force of a driving force source (a driving force source of the wheels W) to an output member 4 that is drivingly connected to the wheels W, and causes the vehicle to travel. The vehicle drive device 1 includes a rotating electric machine (here, a first rotating electric machine MG1 and a second rotating electric machine MG2) as a driving force source for the wheels W. Further, as shown in FIG. 3, in the present embodiment, the vehicle drive device 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. That is, the vehicle drive device 1 is a drive device (hybrid vehicle drive device) for driving a vehicle (hybrid vehicle) including both the internal combustion engine EG and the rotary electric machines (MG1, MG2). Specifically, the vehicle drive device 1 is a so-called two-motor split type hybrid vehicle drive device. The internal combustion engine EG is a prime mover (a gasoline engine, a diesel engine, or the like) driven by combustion of fuel inside the engine to extract power.

  The vehicle drive device 1 includes a first rotating electrical machine MG1 and a second rotating electrical machine MG2. In the present 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. The case 30 also houses other devices or mechanisms included in the vehicle drive device 1. In the present embodiment, as shown in FIG. 3, the vehicle drive device 1 includes an input member 3, an output member 4, a planetary gear mechanism PG, a counter gear mechanism, in addition to the first rotary electric machine MG1 and the second rotary electric machine MG2. CG, an output differential gear device DF, a first oil pump OP1, and a second oil pump OP2. These input member 3, output member 4, planetary gear mechanism PG, counter gear mechanism CG, output differential The dynamic gear unit 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 electric machine MG1, the input member 3, the planetary gear mechanism PG, and the second oil pump OP2 are arranged on the first shaft A1, and the second rotating electric machine MG2 is connected to the second shaft. A2, the output member 4 and the output differential gear unit DF are disposed on the third shaft A3, the counter gear mechanism CG is disposed on the fourth shaft A4, and the first oil pump OP1 is disposed on the fifth shaft A4. It is arranged on A5. The first axis A1, the second axis A2, the third axis A3, the fourth axis A4, and the fifth axis A5 are different axes from each other, and are axes (virtual axes) arranged in parallel with each other. Hereinafter, a direction parallel to each of the axes (A1 to A5) (that is, an axis direction common to the axes) is referred to as “axial direction L”. One side in the axial direction L is referred to as an “axial first side L1”, and the other side in the axial direction L (that is, the side opposite to the axial first side L1 in the axial direction L) is referred to as the “axial second side”. L2 ". In the present embodiment, the vehicle drive device 1 is mounted on the vehicle with the axial direction L oriented along a horizontal plane. Further, in the present embodiment, the vehicle drive device 1 is mounted on the vehicle such that the axial direction L is along the left-right 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 by the first stator 11. The first stator 11 includes a first stator core 12 fixed to the case 30 and a first coil end 13. A coil is wound around the first stator core 12, and the first coil end portion 13 is a portion of the coil projecting in the axial direction L from the first stator core 12. The first stator 11 includes first coil end portions 13 on both sides of the first stator core 12 in the axial direction L. The first rotor 14 is fixed to the first rotor shaft 16 and rotates integrally with the first rotor shaft 16. In the present embodiment, the first rotating electric machine MG1 is a permanent magnet type rotating electric machine (here, an embedded permanent magnet synchronous motor), and the first rotor 14 has a first rotor core 14A and an inside of the first rotor core 14A. And an embedded first permanent magnet M1. Further, in the present embodiment, the first rotating electric machine MG1 is an inner-rotor-type rotating electric machine, and the first rotor 14 is located radially inward of the first stator core 12 (a radial direction based on the first axis A1). Are located in

  As shown in FIG. 1, the second rotating electrical machine MG2 includes a second stator 21 and a second rotor 24 rotatably supported by the second stator 21. The second stator 21 includes a second stator core 22 fixed to the case 30 and a second coil end portion 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 projects from the second stator core 22 in the axial direction L. The second stator 21 includes second coil end portions 23 on both sides of the second stator core 22 in the axial direction L. The second rotor 24 includes a second rotor core 24A, and a cylindrical second rotor shaft 26 that penetrates radially inside the second rotor core 24A, is connected to the second rotor core 24A, and extends along the axial direction L. Have. The second rotor 24 is fixed to the second rotor shaft 26 and rotates integrally with the second rotor shaft 26. In the present embodiment, the second rotating electric machine MG2 is a permanent magnet type rotating electric machine (here, an embedded permanent magnet synchronous motor), and the second rotor 24 is a second permanent electric machine embedded in the second rotor core 24A. It has a magnet M2. In the present embodiment, the second rotating electric machine MG2 is an inner-rotor-type rotating electric machine, and the second rotor 24 is located radially inward of the second stator core 22 (a radial direction based on the second axis A2). Are located in

  The planetary gear mechanism PG includes a first rotating element 67 that is drivingly connected to the first rotating electric machine MG1, a second rotating element 68 that is drivingly connected to the output member 4, and a third rotating element that is drivingly connected to the input member 3. 69. In the present embodiment, the first rotating element 67 is connected so as to rotate integrally with the first rotating electric machine MG1 (the first rotor shaft 16), and the second rotating element 68 is connected to a counter gear mechanism CG, which will be described later. The distribution output gear 64 meshing with the first gear 61 is connected so as to rotate integrally, and the third rotating element 69 is connected so as to rotate integrally with the input member 3. Here, the input member 3 is a member (a shaft member in the present 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 is connected to the internal combustion engine EG via another member such as a damper or a clutch. The output member 4 is a member that is drivingly connected to the wheel W. In the present embodiment, the output member 4 is a member that rotates integrally with the wheel W. That is, a member (for example, a side gear) that rotates integrally with the wheel W in the output differential gear device DF, or a member that forms a drive shaft that connects the output differential gear device DF and the wheel W is output. Member 4.

  In the present embodiment, the planetary gear mechanism PG is a single pinion type planetary gear mechanism. In the present 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 rotary element 69 to the first rotary element 67 and the second rotary element 68 (that is, the first rotary electric machine MG1 and the output member 4). To be distributed).

  The counter gear mechanism CG includes a first gear 61 that meshes with the distribution output gear 64 described above, a second gear 62 that meshes with the differential input gear 65 of the output differential gear device DF, and a first gear 61 and a second gear 62. And a connection shaft 63 that connects the two. In the present embodiment, the output gear 60 of the second rotating electrical machine MG2 is also meshed with the first gear 61. The output gear 60 is a gear for outputting the torque of the second rotating electric machine MG <b> 2, and is connected to rotate integrally with the second rotor shaft 26.

  The output differential gear device DF distributes and transmits the torque input to the differential input gear 65 to the pair of left and right output members 4 (that is, distributes the torque to the pair of left and right wheels W). 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 device 1 according to the present embodiment is configured as described above, the first rotary electric machine is in operation during the continuously variable speed travel mode in which the vehicle travels by transmitting the torque of the internal combustion engine EG to the wheels W. MG1 outputs a reaction torque corresponding to the torque distributed to 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 the execution of the continuously variable transmission mode, the torque attenuated with respect to the torque of the internal combustion engine EG is distributed to the second rotating element 68 as the torque for driving the wheels W, and the second rotating electric machine MG2 is If necessary, a torque is output so as to compensate for a shortfall in the wheel required torque (torque required to be transmitted to the wheel W). Further, during the execution of the electric traveling mode in which the vehicle travels by transmitting only the torque of the second rotating electrical machine MG2 to the wheels W, the internal combustion engine EG is basically in a stopped state in which fuel supply is stopped. Basically, single-rotation electric machine MG1 is in a state of idling (a state in which 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 drive force of the second rotary electric machine MG2 to the output member 4. In the present embodiment, the drive transmission mechanism 2 includes a counter gear mechanism CG and an output differential gear device DF. In the present embodiment, as shown in FIG. 4, the second rotating electrical machine MG2 is disposed so as to overlap with the counter gear mechanism CG when viewed in the axial direction L along the axial direction L. Here, the second rotating electrical machine MG2 is arranged so as to overlap with the fourth shaft A4 on which the counter gear mechanism CG is arranged as viewed in the axial direction L. In FIG. 4, the reference pitch circle is shown for each gear, the outer shape of the first stator 11 (the 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 shows the outer shape of 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 disposed on the side opposite to the first axial side L1 in the axial direction L (second axial side L2) with respect to the second rotary electric machine MG2. Have been. Specifically, case 30 is arranged on first axial side L1 with respect to second rotating electrical machine MG2, and on first axial wall L2 with respect to second rotating electrical machine MG2. And a second wall portion 32 to be formed. The first wall portion 31 and the second wall portion 32 are both support walls that support the second rotor shaft 26. The counter gear mechanism CG is disposed on the second axial side L2 with respect to the second wall 32. Here, the first wall portion 31 is disposed adjacent to the second rotating electrical machine MG2 on the first axial side L1, and the second wall portion 32 is arranged in the second rotating electrical machine MG2 in the axial second direction. It is arranged adjacent to the side L2. In the present embodiment, the first wall 31 is a member separate from the peripheral wall of the case 30 (a cylindrical wall surrounding the second rotary electric machine MG2 and the like in the axial direction L). 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 31 is a cover member (specifically, a rear cover that covers an opening of the peripheral wall opposite to the side where the internal combustion engine EG is arranged).

  As shown in FIG. 3, the vehicle drive device 1 includes a first oil pump OP1 arranged on a different shaft 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. 5, the first oil pump OP1 is connected to the oil reservoir via a first strainer ST1. Aspirate the oil. As shown in FIG. 3, in the present embodiment, the vehicle drive device 1 further includes a second oil pump OP2. In the present 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 storage unit via the second strainer ST2. The first strainer ST1 and the second strainer ST2 are filters for removing foreign matter contained in oil.

  In the present embodiment, the first oil pump OP1 is driven by rotation of the drive transmission mechanism 2. Specifically, the first oil pump OP1 is a rotating member included in the drive transmission mechanism 2, and is a rotating member that is inseparably connected to the wheel W (ie, a rotating member that always rotates in conjunction with the wheel W). ) Is configured to be driven by rotation of the member. Therefore, when the vehicle is traveling, regardless of whether the continuously variable transmission traveling mode or the electric traveling mode is being executed (that is, even if the internal combustion engine EG is stopped), One oil pump OP1 can be driven. Here, the drive transmission mechanism 2 is a mechanism that transmits the driving force of the second rotating electrical machine MG2 to the output member 4. Therefore, the second rotor shaft 26 and the first oil pump OP <b> 1 are drivingly connected via the drive transmission mechanism 2 so as to always rotate synchronously at a specified rotation speed ratio. Therefore, it can be said that the first oil pump OP1 is drivingly connected to the second rotor shaft 26 and is driven by the rotation of the second rotor shaft 26. In the present 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 a first pump drive shaft 53a that is a drive shaft of the first oil pump OP1. Then, as the pump drive gear 66 meshes with the differential input gear 65, the first oil pump OP1 is driven by the rotation of the differential input gear 65. However, without being limited to such a configuration, the pump drive gear 66 may be a gear other than the differential input gear 65 provided in the drive transmission mechanism 2 (in the present embodiment, the output gear 60, the first gear 61, or the first gear 61). It may be configured to mesh with the second gear 62).

  In the present embodiment, the second oil pump OP2 is driven by the rotation of the input member 3. In other words, the second oil pump OP2 is drivingly connected to the internal combustion engine EG and is driven by the driving force of the internal combustion engine EG. Specifically, a second pump drive shaft 53b, which is a drive shaft of the second oil pump OP2, is connected to rotate integrally with the input member 3. 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 traveling or not, the second oil pump OP2 can be driven by the driving force (torque) of the internal combustion engine EG while the internal combustion engine EG is rotating. In addition, at least one of the first oil pump OP1 and the second oil pump OP2 can be an electric oil pump driven by a dedicated electric motor for driving the pump.

[Oil distribution structure]
Next, the flow structure of the oil flowing inside the vehicle drive device 1 will be described. The vehicle drive device 1 is provided with an oil circulation structure described below to supply oil to an inner peripheral portion 26I surrounded by a cylindrical inner peripheral surface F of the second rotor shaft 26, and to supply the oil to the inner peripheral portion 26I. From 26I, it is possible to supply oil to the second rotor core 24A arranged radially outward with respect to the second rotor shaft 26 and the lubricated portion H to be lubricated. In the present embodiment, the vehicle drive device 1 includes an oil pump OP that supplies oil to the oil supply unit S. In this example, the oil pump OP is drivingly connected to the rotor shaft 26 and driven by rotation of the rotor shaft 26, and is drivingly connected to the internal combustion engine EG and driven by the driving of the internal combustion engine EG. A second oil pump OP2. In the present embodiment, the lubricated portion H is a bearing B (a first bearing B1 described later) that rotatably supports the second rotor shaft 26. That is, as described below, the vehicle drive device 1 includes the first oil pump OP1, the supply oil passage 90, the first oil passage 91, and the second oil passage 92 configured by the above-described 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. 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 supply oil to the first rotary electric machine MG1. In the present embodiment, the vehicle drive device 1 further includes an oil cooler OC.

  As shown in FIG. 5, the supply oil passage 90 is connected to a first discharge port 52a that is a discharge port of the first oil pump OP1. In FIG. 5, the line segment indicating the supply oil passage 90 is thicker than the line segments indicating the other oil passages. In FIG. 5, the direction in which oil flows in each oil passage is indicated by an arrow. In the present embodiment, the supply oil passage 90 includes a first discharge oil passage 81, a merge oil passage 83, and a downstream oil passage 84 in this 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 merged oil passage 83. It is connected. The downstream end of the joining 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) described later. Therefore, the oil discharged from the first oil pump OP1 flows through the first discharge oil passage 81, the merge oil passage 83, and the downstream oil passage 84 in this 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 device 1 includes the second oil pump OP2 in addition to the first oil pump OP1. In the present 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, and the downstream end of the second discharge oil passage 82. The portion is connected to the upstream end of the junction oil passage 83. That is, the joining oil passage 83 is an oil passage formed by joining 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 the present embodiment, the oil cooler OC is provided in the junction oil passage 83. In addition, a relief valve RV (in this embodiment) that discharges a part of the oil and adjusts the oil pressure of the joining oil passage 83 when the oil pressure becomes excessive in the portion of the joining oil passage 83 upstream of the oil cooler OC. In the embodiment, two relief valves RV) are provided.

  As shown in FIG. 2, the first oil passage 91 is disposed above the second stator 21 in the vertical direction V (see FIG. 4). The first oil passage 91 is located closer to the first inflow portion 91a connected to the supply oil passage 90 (in the present embodiment, the downstream oil passage 84) and to the first side L1 in the axial direction than 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 axial side L1 with respect to the first discharge hole 91b. This allows the oil supplied from the supply oil passage 90 to the first oil passage 91 to be discharged from the first discharge holes 91b toward the second stator 21, thereby cooling the second stator 21. .

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

  The first oil passage 91 is an oil passage having both ends of the first inflow portion 91a and the discharge portion 91c, and the discharge portion 91c is disposed on the first axial side L1 with respect to the first inflow portion 91a. The first oil passage 91 is formed so as to uniformly extend from the first inflow portion 91a to the discharge portion 91c toward the first axial side L1. That is, as shown by arrows in FIG. 1, the direction in which the oil flows in each oil passage, an oil flow is formed in the first oil passage 91 toward the first axial side L1.

  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 formed 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 constituted by the inner peripheral portion 26I surrounded by the inner peripheral surface F of the second rotor shaft 26. Further, in the present embodiment, the second rotor shaft 26 includes a first tubular member 26A and a second tubular member 26B. The first cylindrical member 26A is disposed on the first axial side L1 with respect to the second cylindrical member 26B. As shown in FIG. 1, the end of the first cylindrical member 26A on the second axial side L2 and the end of the second cylindrical member 26B on the first axial side L1 are connected. In the present embodiment, the end of the second cylindrical member 26B on the first axial side L1 is radially inward of the end of the first cylindrical member 26A on the second axial side L2. By fitting (spline fitting) to the inner peripheral surface of the member 26A, the first tubular member 26A and the second tubular member 26B are connected so as to rotate integrally. In the present embodiment, a second oil passage 92 (inner peripheral portion 26I) is formed inside the first cylindrical member 26A of the second rotor shaft 26, and a seventh oil passage described below is formed inside the second cylindrical member 26B. 97 are formed.

  As shown in FIGS. 1 and 6, the second rotor shaft 26 has an opening 72 </ b> A that opens on its cylindrical inner peripheral surface F, and extends in a radial direction (a radial direction based on the second axis A <b> 2). And a radial oil passage 72 extending therefrom. In the present embodiment, the radial oil passage 72 is formed so as to penetrate the second rotor shaft 26 in the radial direction, and communicates the inner peripheral surface F and the outer peripheral surface of the second rotor shaft 26.

  A second rotor oil passage 25 is formed inside the second rotor core 24A. Although not described in detail, the second rotor oil passage 25 includes an axial oil passage extending in the axial direction L and a radial direction extending in the radial direction and communicating the inner peripheral surface of the second rotor core 24A with the axial oil passage. And an oil passage. This makes it possible to supply the oil in the second oil passage 92 from the radial oil passage 72 to the second rotor oil passage 25 to cool the second rotor core 24A. Then, the second rotor core 24A, in particular, the second permanent magnet M2 embedded in the second rotor core 24A is cooled by heat exchange between the oil supplied to the second rotor oil passage 25 and the second rotor core 24A. It is possible. Further, in the present embodiment, the axial oil passage of the second rotor internal oil passage 25 is formed to open at both ends in the axial direction L of the second rotor core 24A, and cools the second rotor core 24A. It is also possible to supply the latter oil to the second coil end portion 23 from inside in the radial direction to cool the second coil end portion 23.

  In the present embodiment, the vehicle drive device 1 includes a third oil passage 93 that connects the discharge portion 91c 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 axial side L1 with respect to the second rotating electric machine MG2 in the case 30. That is, at least a part of the third oil passage 93 is provided along the first wall portion 31, and in the present embodiment, the portion of the third oil passage 93 except the upstream end and the downstream end is the third oil passage 93. 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 in a portion where the third oil passage 93 is provided (that is, a portion where the second rotary electric machine MG2 is disposed). 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.

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

As shown in FIG. 1, in the present embodiment, the third oil passage 93 is formed inside the first wall 31. Note that at least a portion 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 second axial side L2). Formed). Further, in the present embodiment, the first wall portion 31 is formed in a cylindrical shape protruding toward the second axial side L2, and the opening of the second axial side L2 is disposed inside the second rotor shaft 26. A second end portion of the third oil passage 93 is formed by a space surrounded by an 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 first side L1 in the axial direction are connected.
Note that a first supply unit S1 for supplying oil to an inner peripheral portion 26I (second oil passage 92) described later is formed at a downstream end of the third oil passage 93.

  In the present embodiment, the vehicle drive device 1 further includes a fourth oil passage 94 through which oil for cooling the first rotary electric machine MG1 flows. As shown in FIG. 5, the fourth oil passage 94 is formed so as 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 disposed 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 the present embodiment, a downstream end of the merge oil passage 83, in other words, an upstream end of the downstream oil passage 84). It has a second inflow portion 94a and a second discharge hole 94b formed on the first side L1 in the axial direction with respect to the second inflow portion 94a and discharging oil toward the first stator 11. Thus, the oil supplied from the supply oil passage 90 to the fourth oil passage 94 is discharged from the second discharge hole 94b toward the first stator 11, and the first stator 11 can be cooled. .

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

  As shown in FIGS. 2 and 5, in the present embodiment, the vehicle drive device 1 further includes a fifth oil passage 95. 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 formed of a tubular member extending in the axial direction L, and a 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. Have been. As shown in FIG. 5, the fifth oil passage 95 is formed so as 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 to the fifth oil passage 95 is controlled by the second orifice 50b.

  In the fifth oil passage 95, a flow of oil toward the second axial side L2 is formed. Then, as shown in FIG. 5, the oil in the fifth oil passage 95 is supplied to the first rotating electric machine MG1 (first rotor 14) for cooling, and lubricates the planetary gear mechanism PG. Supplied for Specifically, as shown in FIG. 2, the first rotor shaft 16 is formed of a cylindrical member extending in the axial direction L, and the second pump drive shaft 53 b is formed on the inner peripheral surface of the first rotor shaft 16. It is arranged in the space surrounded by. The second pump drive shaft 53b has a second oil hole 73 that connects the inner peripheral surface and the outer peripheral surface of the second pump drive shaft 53b. The second oil hole 73 is formed so as to penetrate the cylindrical portion of the second pump drive shaft 53b in a radial direction (a radial direction based on the first axis A1; the same applies hereinafter in this paragraph). Further, the first rotor shaft 16 has a first oil hole 71 that connects 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 cylindrical portion of the first rotor shaft 16 in the radial direction. A first rotor oil passage 15 is formed inside the first rotor core 14A. Although not described in detail, the first rotor oil passage 15 has an axial oil passage extending in the axial direction L and a radial direction extending in the radial direction and communicating the inner peripheral surface of the first rotor core 14A with the axial oil passage. And an oil passage.

  Thus, 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 The first rotor core 14A can be cooled by supplying the oil from the hole 71 to the first rotor oil passage 15. Then, the first rotor core 14A, in particular, the first permanent magnet M1 embedded in the first rotor core 14A can be cooled by heat exchange between the oil supplied to the first rotor oil passage 15 and the first rotor core 14A. It is possible. In the present embodiment, the axial oil passage of the first rotor oil passage 15 is formed so as to open at both ends in the axial direction L of the first rotor core 14A, and cools the first rotor 14. The subsequent oil can be supplied to the first coil end portion 13 from the radially inner side (radial direction with reference to the first axis A1) to cool the first coil end portion 13. . Further, the oil in the fifth oil passage 95 flows into an oil passage formed inside the input member 3 and then flows through a fourth oil hole 74 (see FIGS. 1 and 2) formed in the input member 3. It is supplied for lubrication to the planetary gear mechanism PG and the like.

  As shown in FIG. 5, in the present embodiment, the vehicle drive device 1 further includes a sixth oil passage 96. The sixth oil passage 96 is formed so as 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 to the counter gear mechanism CG and the output differential gear device DF for lubrication. 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, in the present embodiment, the vehicle drive device 1 further includes a seventh oil passage 97. The seventh oil passage 97 is formed inside a second cylindrical member 26B constituting the second rotor shaft 26. In the seventh oil passage 97, an oil flow is formed toward the first side L1 in the axial direction. In the present embodiment, as shown in FIG. 4, the vehicle drive device 1 is a catch tank that stores oil scooped up by the output member 4 (see FIG. 3, in this example, by the differential input gear 65). The CT is provided in the upper part in the case 30. Then, the oil stored in the catch tank CT flows into the seventh oil passage 97 from the second axial side L2, so that an oil flow toward the first axial side L1 is formed in the seventh oil passage 97. . As shown in the figure, the downstream end of the seventh oil passage 97 and the end of the second oil passage 92 on the second axial side L2 are connected. Therefore, the oil flowing through the seventh oil passage 97 toward the first axial side L1 is supplied to the second oil passage 92 (the inner peripheral portion 26I). The second supply portion S2 for supplying oil to an inner peripheral portion 26I (second oil passage 92) described later is formed at a downstream end of the seventh oil passage 97.

  As shown in FIGS. 1 and 2, in the present embodiment, the vehicle drive device 1 includes a tubular first oil circulation pipe 41, a tubular second oil circulation pipe 42, and a tubular third oil circulation pipe 43. Have. A fourth oil passage 94 is formed inside the first oil circulation pipe 41, a first oil passage 91 is formed inside the second oil circulation pipe 42, and a downstream oil is formed inside the third oil circulation pipe 43. A passage 84 is formed. As shown in FIG. 1, in the present embodiment, the first wall portion 31 has a first connection portion 34a formed in a cylindrical shape and protruding toward the second axial side L2. The upstream end of the third oil passage 93 is formed by the space surrounded by the inner peripheral surface of the groove 34a. The second oil flow pipe 42 is disposed such that the discharge portion 91c is connected to the first connection portion 34a, whereby the downstream end (discharge portion 91c) of the first oil passage 91 and the second oil flow pipe 42 are connected to each other. The upstream end of the three oil passages 93 is connected at the first connection portion 34a. The second oil flow pipe 42 is disposed such that both ends are disposed at different positions in the axial direction L (for example, along the axial direction L). The discharge portion 91c of the first oil passage 91 is formed by the opening on the first side L1. Further, the above-described first discharge hole 91b is formed so as to penetrate the cylindrical 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 connection portion 34c formed in a cylindrical shape extending in the axial direction L. Then, the end of the second oil flow pipe 42 on the second axial side L2 is fitted to the inner peripheral surface of the third connection portion 34c from the first axial side L1. The end is fitted to the inner peripheral surface of the third connection portion 34c from the second axial side L2. Thereby, the downstream end of the downstream oil passage 84 and the upstream end (first inflow portion 91a) of the first oil passage 91 are connected at the third connection portion 34c. Note that the first inflow portion 91a of the first oil passage 91 is formed by an opening on the second axial side L2 of the second oil flow pipe 42.

  As shown in FIG. 2, in the present embodiment, the second wall portion 32 includes a fourth connection portion 34 d formed in a cylindrical shape extending in the axial direction L. Then, the end 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 direction L1. The end (the end 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. The downstream end of the joining oil passage 83 is formed so as to open to the inner peripheral surface of the fourth connection portion 34d. Thereby, the downstream end of the joining oil passage 83, the upstream end of the downstream oil passage 84, and the upstream end (the second inflow portion 94a) of the fourth oil passage 94 are connected to the fourth connection portion. 34d. The first oil flow pipe 41 is disposed such that both ends are disposed at different positions in the axial direction L (for example, along the axial direction L). The second inflow portion 94a of the fourth oil passage 94 is formed by the opening on the second side L2. Further, the above-mentioned second discharge hole 94b is formed so as to penetrate the cylindrical portion of the first oil flow pipe 41.

[Driving mode and oil flow]
Next, the flow of oil in the vehicle drive device 1 in each case where the vehicle drive device 1 is executing a plurality of traveling modes will be described.

  The vehicle drive device 1 includes a hybrid traveling mode (HV traveling mode) in which at least the internal combustion engine EG is used 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 traveling mode (EV traveling mode) in which the vehicle travels using only the MG2 as a power source is configured to be executable.

  As shown in FIG. 3, the second oil pump OP2 is connected to the internal combustion engine EG via the input member 3. Accordingly, while the vehicle drive device 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 first oil pump OP1 is driven by the rotation of the rotary electric machine MG2. Here, the oil discharged by the first oil pump OP1 is supplied to the supply oil passage 90 and lubricated to the counter gear mechanism CG and the output differential gear device DF via the sixth oil passage 96. Supplied to The 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 traveling mode, the discharge pressure of the second oil pump OP2 is higher than the discharge pressure of the first oil pump OP1, so that the oil discharged by the first oil pump OP1 is mainly The oil is supplied to an oil passage 96.

  Therefore, in the HV traveling mode, the oil mainly discharged from the second oil pump OP2 is supplied to the second oil passage 92 (the inner peripheral portion 26I) from the first axial side L1 via the third oil passage 93. Is done. In this way, the oil supplied to the second oil passage 92 (the inner peripheral portion 26I) is cooled by the oil cooler OC in the process of flowing through the supply oil passage 90, so that the cooling for cooling the second rotary electric machine MG2 is performed. It can be suitably used as oil. Further, while the vehicle drive device 1 is executing the HV traveling mode, the oil is scraped up by the differential input gear 65 as the output member 4 rotates. The oil thus scooped 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 device 1 is executing the HV traveling mode, oil is supplied to the second oil passage 92 (the inner peripheral portion 26I) from both sides in the axial direction L, so that a relatively large amount of oil is supplied. Is supplied to the second oil passage 92 (the inner peripheral portion 26I).

  On the other hand, while the vehicle drive device 1 is executing the EV traveling mode (the vehicle is traveling in the EV traveling mode), the oil is scraped up by the differential input gear 65 as the output member 4 rotates. The oil thus scooped 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 device 1 is executing the EV traveling mode, in addition to the oil being scraped up by the differential input gear 65, the first oil is rotated by the rotation of the output member 4 and the second rotary electric machine MG2. The 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 to the counter gear mechanism CG and the output differential gear unit DF via the sixth oil passage 96 for lubrication.

  Therefore, in the EV traveling mode, oil is mainly supplied from the catch tank CT to the second oil passage 92 (the inner peripheral portion 26I) from the second axial side L2 via the seventh oil passage 97. That is, in the EV traveling mode, the supply of the oil from the first axial side L1 to the second oil passage 92 (the inner peripheral portion 26I) is not (or less), and the comparison is mainly performed from the second axial side L2. A very small amount of oil is supplied to the second oil passage 92 (the inner peripheral portion 26I).

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

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

  In the present embodiment, the first wall portion 31 has a cylindrical first boss portion 31A protruding on the second axial 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 first axial side L1 with respect to the second rotor core 24A. In the present embodiment, as described above, the first bearing B1 corresponds to the “lubricated portion H”.

  In the present embodiment, the second wall portion 32 has a cylindrical second boss portion 32A protruding on the first axial side L1. The second bearing B2 is supported by the inner peripheral surface of the second boss 32A and also supports the outer peripheral surface of the second rotor shaft 26 (here, the first cylindrical member 26A).

  In the present embodiment, the second wall portion 32 has, in addition to the second boss portion 32A, a cylindrical third boss portion 32B protruding on the second axial side L2. In the illustrated example, the third boss portion 32B is formed integrally with the second boss portion 32A, and the second boss portion 32A and the third boss portion 32B are located on opposite sides along the axial direction L. It is protruding. The third bearing B3 is supported by the inner peripheral surface of the third boss 32B and also supports the outer peripheral surface of the second rotor shaft 26 (here, the second cylindrical member 26B).

In the present embodiment, the case 30 includes a third wall 33 in addition to the first wall 31 and the second wall 32. The third wall portion 33 is disposed on the second axial side L2 with respect to the counter gear mechanism CG and the second rotor shaft 26 (the second cylindrical member 26B) in the case 30. In the illustrated example, most of the second cylindrical 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 above-described counter gear mechanism CG is also accommodated between the second wall portion 32 and the third wall portion 33 in the axial direction L. And in this embodiment, the 3rd wall part 33 has the cylindrical 4th boss part 33A which protrudes in the axial direction 1st side L1.
The fourth bearing B4 is supported by the inner peripheral surface of the fourth boss 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 includes an oil supply unit 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 cylindrical 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 forms the second oil passage 92.

  In the present embodiment, the oil supply unit S includes a first supply unit S1 and a second supply unit S2. The first supply unit S1 supplies oil from the end of the second rotor shaft 26 on the first axial side L1 to the inner peripheral portion 26I. The second supply part S2 supplies oil to the inner peripheral part 26I from the end on the second axial side L2 of the second rotor shaft 26. Here, the first supply section 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 part S1 to the inner peripheral part 26I. The second supply portion S2 is formed at the downstream end of the seventh oil passage 97, and as shown in FIG. 5, oil from the catch tank CT (which is scraped up with the rotation of the output member 4). Oil) is supplied from the second supply section S2 to the inner peripheral section 26I.

  As shown in FIGS. 1 and 6, the second rotor 24 includes 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 portion at an end of the second rotor shaft 26 (the first cylindrical member 26A) on the first axial side L1 and a first axial portion of the second rotor shaft 26 in the axial direction. It is formed by a space outside the shaft end between the end of the side L1 and the surface of the first wall 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 weir portion D (first weir portion D1) is formed inside the second rotor shaft 26, and the lubricating oil passage 75 is more axially located than the weir portion D (first weir portion D1). It is arranged on the first side L1. The oil that has flowed out of the weir portion D (the first weir portion D1) of the second rotor shaft 26 to the first axial side L1 passes through the lubricating oil passage 75 to the first bearing B1, and lubricates the first bearing B1. I do.

  As shown in FIG. 6, the second rotor shaft 26 has an opening 72 </ b> A opened on the inner peripheral surface F and has a radial direction (a radial direction based on the second shaft A <b> 2, hereinafter referred to as “Details of Rotor for Rotating Electric Machine” Configuration], the radial oil passage 72 extends along the same line. The opening 72A is formed at a radially inner end of the radial oil passage 72. The radially outer end of the radial oil passage 72 is open to the outer peripheral surface of the second rotor shaft 26. In the present embodiment, the second rotor shaft 26 is provided with a plurality of radial oil passages 72 dispersed in the circumferential direction, and a plurality of openings 72A are formed in the inner circumferential surface F along the circumferential direction. . 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. The oil supplied to the inner peripheral portion 26I enters the radial oil passage 72 from the opening 72A, is guided to the second rotor core 24A through the radial oil passage 72, and cools the second rotor core 24A.

  As shown in FIG. 6, the second rotor shaft 26 projects radially inward from the inner peripheral surface F and is arranged so as to extend in the circumferential direction along the inner peripheral surface F. D1 is provided. The first dam D1 is disposed on the first axial side L1 with respect to the opening 72A. And the oil supply part S (1st supply part S1) is comprised so that oil may be supplied to the 2nd axial side L2 rather than the 1st dam part D1 in the inner peripheral part 26I. For this reason, in the illustrated example, the first supply unit S1 is provided so as to be open on the second axial side L2 with respect to the first dam D1. In the present embodiment, the first dam portion D1 is formed by a member different from the second rotor shaft 26 (the first cylindrical member 26A), and is press-fitted radially inward to 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 or the like. Good. Alternatively, the first dam portion D1 may be formed by cutting or the like.

In the present embodiment, the second rotor shaft 26 is disposed on the second axial side L2 with respect to the opening 72A, protrudes radially inward from the inner peripheral surface F, and extends circumferentially along the inner peripheral surface F. It further includes an annular second weir portion D2 arranged to extend. The first weir portion D1 and the second weir portion D2 constitute an in-axial storage portion for storing oil between the two in the axial direction L. And the opening part 72A is arrange | positioned so that it may open to this axial storage part. Therefore, the oil stored in the axial storage portion between the first dam portion D1 and the second dam portion D2 efficiently flows into the opening 72A due to the centrifugal force and the like caused by the rotation of the second rotor shaft 26. Can be done. Therefore, in a state where oil is stored in the in-shaft storage portion, an 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. 24A. In the present embodiment, the second dam portion D2 is configured by the step portion provided in the spline fitting portion for fitting the first tubular member 26A and the second tubular member 26B into splines as described above. ing. However, without being limited to such a configuration, the second dam portion D2 may be configured by a simple step portion that is not related to the spline fitting portion.
Alternatively, the second dam portion D2 may be an annular member attached to the inner peripheral surface F of the second rotor shaft 26, similarly to the first dam portion D1.

  With such a configuration, oil can be stored in the inner peripheral portion 26I, and a sufficient amount of oil for cooling the second rotor core 24A can be supplied to the radial oil passage 72. On the other hand, as described above, the lubricating oil passage 75 for supplying oil to the first bearing B1 is disposed on the first axial side L1 with respect to the first dam D1. Therefore, the oil blocked by the first dam D1 is less likely to flow to the first axial side L1 than the first dam 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 portion D, and the portion of the inner peripheral portion 26I on the first side L1 in the axial direction and the weir portion D than the weir portion D. Also has an axial communication passage LGr that communicates with the portion on the second axial side L2. In the present embodiment, the axial communication passage LGr is provided on the inner peripheral surface F, is formed so as to be depressed radially outward, and to extend in the axial direction L through the radial outside with respect to the weir portion D. ing. The axial communication passage LGr communicates with the lubricating oil passage 75. In the present embodiment, the axial communication passage LGr extends from the second axial side L2 to the first axial side L1 with respect to the first weir D1 through the radial outside of the first weir 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 second axial side L2 from the first dam portion D1, and flows through the axial communication passage LGr along the first axial side L1. , And flows into the lubricating oil passage 75 disposed on the first axial side L1 with respect to the first dam D1. Then, the oil flowing 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 appropriately performed. . In the present embodiment, the axial communication passage LGr is formed continuously from the portion on the second axial side L2 to the end of the second rotor shaft 26 on the first axial side L1 with respect to the first dam D1. I have.

  In the present embodiment, a plurality of axial communication passages LGr are arranged in the circumferential direction of the inner peripheral surface F. In this example, as shown in FIG. 7, four axial communication passages LGr are arranged at equal intervals (90 ° intervals) in the circumferential direction. 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. The cross-sectional shape of the axial communication passage LGr is not limited to this, and may be a groove having various shapes such as an arc shape or various polygonal shapes. Thus, regardless of the position of the second rotor shaft 26 in the rotation direction, the oil can be guided to the first axial side L1 from the first dam D1 by the axial communication passage LGr. However, without being limited to the above-described configuration, the plurality of axial communication passages LGr may be arranged such that the circumferential arrangement intervals are unequal. Further, the number of the axial communication passages LGr is arbitrary, and may be 1 to 3 or 5 or more. FIG. 8 is a development view in which the inner peripheral portion 26I is developed in the circumferential direction within a range of 180 °, and two of the four axial communication passages LGr are illustrated. I have.

  As shown in FIGS. 6 and 8, in the present embodiment, the end of the axial communication path LGr on the second axial side L2 is disposed closer to the second axial side L2 than the opening 72A. This makes it easier for the oil on the second axial side L2 to enter the axial communication passage LGr before entering the opening 72A than 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 device 1 is executing the EV traveling mode, the oil is preferentially supplied to the axial communication passage LGr. Will be. Therefore, even when the amount of oil supplied to the inner peripheral portion 26I is small, the first bearing B1 can be appropriately lubricated. The end of the axial communication passage LGr on the second axial side L2 is located closer to the first axial side L1 than the second dam D2.

  As shown in FIGS. 6 and 8, in the present embodiment, the axial communication passage LGr and the opening are arranged such that, at the same position in the axial direction L, the circumferential communication passage LGr and the opening 72 </ b> A have different circumferential positions. The part 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. According to this configuration, since the oil once entering the axial communication passage LGr does not flow into the opening 72A, it is possible to appropriately distribute the oil to the axial communication passage LGr and the radial oil passage 72. it 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, the inner peripheral portion 26I (the second oil passage 92) from the first supply portion S1 (the third oil passage 93) or the second supply portion S2 (the seventh oil passage 97). ) Can be retained in the inner peripheral portion 26I between the first dam portion D1 and the second dam portion D2 in a certain amount. For example, while the vehicle drive device 1 is executing the EV traveling mode, the supply of oil to the inner peripheral portion 26I is supplied from the second supply portion S2 (the seventh oil passage 97) as described above. Occupies the majority, and the supply amount of oil to the inner peripheral portion 26I is relatively small. Even in such a case, the oil can be preferentially supplied to the lubricating oil passage 75 via the axial communication passage LGr, and the oil for lubricating the first bearing B1 can be appropriately secured. On the other hand, for example, while the vehicle drive device 1 is executing the HV traveling mode, the supply of the oil to the inner peripheral portion 26I is performed by the first supply portion S1 (the third oil passage 93) and the second supply portion as described above. The oil supply is performed from both the supply section S2 (the seventh oil passage 97) and the amount of oil supply to the inner peripheral portion 26I is relatively large. In this case, the amount of oil supplied to the inner peripheral portion 26I is larger than the amount of oil flowing through the axial communication passage LGr in the inner peripheral portion 26I. As a result, the oil is supplied to the first dam portion D1 and the second dam portion. It is stored in the inner peripheral part 26I between the part D2. The oil thus stored is efficiently supplied to the radial oil passage 72 by centrifugal force or the like accompanying 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 appropriately performed.

2. Second Embodiment Next, a second embodiment of the rotating electrical machine rotor will be described. Hereinafter, points different from the first embodiment will be mainly described. The points that are not particularly described are the same as those in the first embodiment.

  FIG. 9 is a development view in which the inner peripheral portion 26I of the rotating electrical machine rotor (second rotor 24) according to the present embodiment is developed in a circumferential direction within a range of 180 °.

  As shown in FIG. 9, in the present embodiment, the second rotor 24 includes a circumferential groove CGr provided on the inner circumferential 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. In the present embodiment, the circumferential grooves CGr are provided continuously over the entire area of the 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 part of the inner circumferential surface F in the circumferential direction or may be provided intermittently.

  In the present embodiment, the circumferential groove CGr is arranged on the second axial side L2 with respect to the opening 72A, and is connected to the axial communication passage LGr. The oil guided to the circumferential groove CGr is guided to the axial communication passage LGr. Therefore, according to this configuration, oil supplied to the second axial side L2 rather than 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. I will Therefore, the oil on the second side L2 in the axial direction can be guided to the axial communication passage LGr more preferentially than the radial oil passage 72 than the circumferential groove CGr. Therefore, the first bearing B1 can be appropriately lubricated even when the amount of oil supplied to the inner peripheral portion 26I is small, such as when the vehicle drive device 1 is executing the EV traveling mode.

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

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

(1) In each of the above embodiments, the configuration in which the end of the second axial direction L2 of the axial communication passage LGr is disposed on the second axial side L2 with respect to the opening 72A has been described as an example. However, without being limited to such a configuration, for example, as shown in FIG. 10, the end of the axial communication passage LGr on the second axial side L2 is closer to the first axial side L1 than the opening 72A. It may be arranged, or 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 passage LGr is continuous from the portion on the second axial side L2 to the end of the second rotor shaft 26 on the first axial side L1 with respect to the first dam portion D1. The configuration that has been formed is described as an example. However, without being limited to such a configuration, the axial communication passage LGr extends between the first weir D1 in the axial first side L1 and the first weir D1 in the axial second side L2. For example, as shown in FIG. 11, it may be formed only in a region overlapping the first dam portion D1 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 end of the axial communication passage LGr on the first axial side L1 to the first bearing B1 (see FIG. 6).

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

(4) In each of the above embodiments, the axial communication passage LGr is provided on the inner peripheral surface F of the second rotor shaft 26, is recessed radially outward, and extends in the axial direction L as an example. explained. However, without being limited to such a configuration, the axial communication passage LGr may be provided in the weir D (first weir D1), for example, as shown in FIGS. In this case, the axial communication passage LGr may be formed in a groove shape or a hole shape so as to penetrate the weir portion D (the first weir portion D1) in the axial direction L. Here, FIGS. 13 to 16 are cross-sectional views orthogonal to the axis when the rotor shaft 26 is cut along a plane orthogonal to the axial direction L. For example, as shown in FIGS. 12 and 13, the axial communication passage LGr is provided on the outer peripheral surface of the weir D (first weir D1), and is recessed radially inward and extends in the axial direction L. The groove may be formed. In the illustrated example, the axial communication passage LGr is formed in a groove shape having an arc-shaped cross section whose radial outside is open when viewed in the axial direction L. Further, as shown in FIG. 14, the axial communication passage LGr may be formed in a groove shape having a rectangular cross section whose radial outside is open when viewed in the axial direction L. Alternatively, as shown in FIG. 15, the axial communication passage LGr may be formed in a through-hole shape penetrating in the axial direction L at a radially intermediate portion of the weir D (first weir D1). In the illustrated example, the axial communication passage LGr is formed in a hole shape having a circular cross section when viewed in the axial direction L. The cross-sectional shape of the through-hole-shaped axial communication passage LGr is not limited to this, and may be various shapes such as various polygonal shapes (triangular shape, square shape, etc.) and elliptical shapes (not shown). ). 13 to 15 illustrate a configuration in which two axial communication passages LGr are provided in the weir D (first weir D1) at intervals in the circumferential direction. However, without being limited to such a configuration, as shown in FIG. 16, three or more axial communication passages LGr are provided in the weir portion D (first weir portion D1) at intervals in the circumferential direction. It may be. Alternatively, only one dam D (first dam D1) may be provided (not shown).

(5) In each of the above embodiments, the configuration in which the lubricated portion H is the bearing B (the 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 portions to be lubricated in the vehicle drive device can be the lubricated portions H. Preferably, the lubricated portion H is a portion where each member slides, and is, for example, a meshing portion of a gear mechanism, a bearing, or the like.

(6) In each of the above embodiments, the configuration in which the second rotor shaft 26 includes both the first dam portion D1 and the second dam portion D2 has been described as an example. However, without being limited to such a configuration, the second rotor shaft 26 only needs to include at least the first dam portion D1.

(7) The configurations disclosed in the above embodiments can be applied in combination with the configurations disclosed in other embodiments as long as no contradiction occurs. Regarding other configurations, the embodiments disclosed in this specification are merely examples in all respects. Therefore, various modifications can be appropriately made without departing from the spirit of the present disclosure.

4. Hereinafter, an outline of the above-described rotary electric machine rotor and a vehicle drive device including the rotary electric machine rotor will be described.

  The rotor for a rotating electrical machine (24) includes a rotor core (24A), a cylindrical rotor penetrating radially inside the rotor core (24A), being connected to the rotor core (24A), and extending along the axial direction (L). A shaft (26), an oil supply unit (S) for supplying oil to the rotor shaft (26), and one side in the axial direction (L) as a first axial side (L1). ) Is defined as the second axial side (L2), the lubricated part (H) to be lubricated disposed on the first axial side (L1) with respect to the rotor core (24A), and the lubricated part (L). H), a lubricating oil passage (75) for supplying oil to the rotor shaft (26), wherein the rotor shaft (26) has an inner peripheral portion (26I) surrounded by a cylindrical inner peripheral surface (F); Radial oil having an opening (72A) opening in the peripheral surface (F) and extending along the radial direction And (72), disposed on the first side (L1) in the axial direction with respect to the opening (72A), protruding radially inward from the inner peripheral surface (F), and at the inner peripheral surface (F). An annular weir (D) disposed so as to extend in the circumferential direction along the axis, and an axial communication path (LGr). The oil supply unit (S) includes the inner peripheral portion (26I). The oil is supplied to the second axial side (L2) from the weir (D) in the above, and the lubricating oil passage (75) is more axially to the first axial side (L1) than the weir (D). And the axial communication path (LGr) is provided on the inner peripheral surface (F) or the weir portion (D), and the axial communication passage (LGr) is more axially disposed than the weir portion (D) in the inner peripheral portion (26I). A portion on the first side (L1) in the direction and a portion on the second side (L2) in the axial direction relative to the weir portion (D) communicate with each other, and the lubricating oil passage (75 And communicates with.

  According to this configuration, the oil supplied to the inner peripheral portion (26I) of the rotor shaft (26) can be retained on 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) opened on the inner peripheral surface (F) of the rotor shaft (26), and the oil can be supplied to the radial outside of the rotor shaft (26). It is possible to appropriately cool the disposed rotor core (24A). Further, according to this configuration, the portion of the inner peripheral portion (26I) on the first axial side (L1) than the weir portion (D) and the portion on the second axial side (L2) than the weir portion (D). And an axial communication path (LGr) that communicates between the inner peripheral portion (26 </ b> I) and a region on the second axial side (L <b> 2) than the weir (D) in the inner peripheral portion (26 </ b> I). Oil can be supplied to the lubricating oil passage (75) of (L1). Therefore, it is possible to appropriately supply oil to the lubricated portion (H) disposed on the first axial side (L1) with respect to the rotor core (24A), and to appropriately lubricate the lubricated portion (H). It 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 bearing (B) supporting the rotor shaft (26) can be appropriately lubricated by the oil supplied to the lubricating oil passage (75).

  In addition, it is preferable that an end of the axial communication path (LGr) on the second axial side (L2) is disposed closer to the second axial direction (L2) than the opening (72A). is there.

  According to this configuration, the oil on the second axial side (L2) is more easily supplied to the axial communication passage (LGr) than the opening (72A). Therefore, even when the amount of oil supplied to the inner peripheral portion (261) is small, oil can be supplied to the axial communication passage (LGr), and the lubricated portion (H) can be appropriately lubricated.

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

  According to this configuration, the oil flowing in the axial communication passage (LGr) does not flow to the radial oil passage (72) via the opening (72A). Therefore, the oil flowing in the axial communication passage (LGr) and the oil flowing in the radial oil passage (72) can be separated. Therefore, both the supply of oil to the radial oil passage (72) through the opening (72A) and the supply of oil to the lubricating oil passage (75) through the axial communication passage (LGr) can be appropriately performed. Can be done.

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

  According to this configuration, due to the axial communication passage (LGr), the portion of the inner peripheral portion (26I) on the first side (L1) in the axial direction with respect to the weir (D) and the axial direction with respect to the weir (D). The portion on the second side (L2) can be appropriately communicated. Therefore, the lubricating oil passage (75) on the axially first side (L1) from the weir (D) from the area on the second axial side (L2) than the weir (D) in the inner peripheral portion (26I). Oil can be supplied.

  Further, a circumferential groove (CGr) provided on the inner peripheral surface (F) and extending in the circumferential direction is further provided, and the circumferential groove (CGr) is more axially second than the opening (72A). It is preferable to be disposed on the side (L2) and connected to the axial communication path (LGr).

  According to this configuration, the oil on the second axial side (L2) is more easily supplied to the axial communication passage (LGr) than the opening (72A). Therefore, even when the amount of oil supplied to the inner peripheral portion (261) is small, oil can be supplied to the axial communication passage (LGr), and the lubricated portion (H) can be appropriately lubricated.

  In addition, 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) includes at least two of the axial communication passages (LGr). ) Is preferably connected.

  According to this configuration, the oil on the second axial side (L2) is more easily supplied to the axial communication passage (LGr) than the opening (72A). Therefore, even when 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 appropriately lubricated. Can be.

  Here, it is preferable that the axial communication passage (LGr) is formed so as to penetrate the weir (D) in the axial direction (L).

  According to this configuration, due to the axial communication passage (LGr), the portion of the inner peripheral portion (26I) on the first side (L1) in the axial direction with respect to the weir (D) and the axial direction with respect to the weir (D). The portion on the second side (L2) can be appropriately communicated. Therefore, the lubricating oil passage (75) on the axially first side (L1) from the weir (D) from the area on the second axial side (L2) than the weir (D) in the inner peripheral portion (26I). Oil can be supplied.

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

  According to this configuration, it becomes easier to more appropriately supply the oil to the inner peripheral portion (26I). In addition, since the first supply unit (S1) and the second supply unit (S2) are connected to different hydraulic circuits, the first supply unit (S1) and the second supply unit (S2) are connected to the inner peripheral portion (26I) according to the operation state of the rotating electric machine. It is also possible to make the supply state of the oil different.

  The weir portion (D) is a first weir portion (D1), and is disposed on the second axial side (L2) with respect to the opening (72A), from the inner peripheral surface (F). It is preferable to further include an annular second weir portion (D2) that protrudes radially inward and extends in the circumferential direction along the inner peripheral surface (F).

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

Here, the vehicle drive device (1)
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 unit (S), wherein the oil pump (OP) includes: A first oil pump (OP1) is drivingly connected to the rotor shaft (26) and driven by rotation of the rotor shaft (26).

  According to this configuration, the rotation of the rotor shaft (26) supplies oil to the oil supply unit (S). Therefore, according to this configuration, it is possible to appropriately supply the lubricating oil to the lubricated portion (H) that requires lubrication with the oil as the rotor shaft (26) rotates. Therefore, when the vehicle travels while rotating the wheels (W) using the rotating electric machine (MG2) as a power source, the oil pump (OP) is driven during the traveling to supply oil to the inner peripheral portion (261). can do.

In addition, the vehicle drive device (1) having the above configuration includes:
An internal combustion engine (EG) and the rotary electric machine (MG2) as driving power sources for the wheels (W);
The oil pump (OP) preferably includes a second oil pump (OP2) that is drivingly connected to the internal combustion engine (EG) and driven by driving the internal combustion engine (EG).

  According to this configuration, the second oil pump (OP2) can be driven when the vehicle travels while rotating the wheels (W) using at least the internal combustion engine (EG) as a power source, and the second oil pump can be driven. Oil can be supplied to the inner peripheral portion (26I) by (OP2). Further, when the rotor shaft (26) is configured to rotate during traveling of the vehicle using the internal combustion engine (EG) as a power source, the vehicle uses at least the internal combustion engine (EG) as a power source as described above. When the vehicle travels, both the first oil pump (OP1) and the second oil pump (OP2) can be driven, and the supply amount of oil to the inner peripheral portion (261) can be increased. Become.

  The technology according to the present disclosure can be used for 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 rotating electric machine)
24A: 2nd rotor core (rotor core)
26: 2nd 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 part D1: first dam part D2: second dam part F: inner peripheral surface H: lubricated part L: axial direction L1: axial first side L2: Axial second side S: oil supply unit S1: first supply unit S2: second supply unit

Claims (12)

A rotor core,
A cylindrical rotor shaft penetrating the rotor core radially inward and connected to the rotor core, and extending along the axial direction;
An oil supply unit for supplying oil to the rotor shaft,
A lubricated part to be lubricated disposed on the first axial side with respect to the rotor core, with one side in the axial direction being a first axial side and the other side in the axial direction being a second axial side;
A lubricating oil passage for supplying oil to the lubricated portion,
The rotor shaft,
An inner peripheral portion surrounded by the cylindrical inner peripheral surface,
A radial oil passage having an opening that opens to the inner peripheral surface and extending along the radial direction,
An annular weir portion that is arranged on the first side in the axial direction with respect to the opening, protrudes radially inward from the inner peripheral surface, and is arranged so as to extend circumferentially along the inner peripheral surface; When,
An axial communication passage,
The oil supply unit supplies oil to the second axial side from the weir portion in the inner peripheral portion,
The lubricating oil passage is disposed on the first axial side with respect to the weir portion,
The axial communication path is provided on the inner peripheral surface or the weir portion, and a portion of the inner peripheral portion on the axial first side than the weir portion and on the axial second side than the weir portion. A rotor for a rotating electrical machine, wherein the rotor is in communication with a portion and in communication with the lubricating oil passage.   The rotor for a rotating electric machine according to claim 1, wherein the lubricated portion is a bearing that rotatably supports the rotor shaft.   3. The rotor for a rotating electrical machine according to claim 1, wherein an end of the axial communication path on the second axial direction is located closer to the second axial direction than the opening. 4.   The rotor for a rotating electrical machine according to claim 3, wherein circumferential positions of the axial communication passage and the opening are different at the same axial position.   The said axial direction communication path is provided in the said inner peripheral surface, and it is formed so that it may be depressed radially outward and may extend in the axial direction through the radial outside with respect to the weir portion. The rotor for a rotating electrical machine according to any one of claims 1 to 4. A circumferential groove provided on the inner peripheral surface and extending in a circumferential direction,
The rotor for a rotating electrical machine according to claim 5, wherein the circumferential groove is disposed on the second axial side with respect to the opening, and is connected to the axial communication passage. A plurality of the axial communication paths are arranged side by side in the circumferential direction of the inner peripheral surface,
The rotor for a rotating electrical machine according to claim 6, wherein the circumferential groove is connected to at least two of the axial communication passages.   The rotary electric machine rotor according to any one of claims 1 to 4, wherein the axial communication passage is formed to penetrate the weir portion in the axial direction. The oil supply unit includes a first supply unit and a second supply unit,
The first supply unit supplies oil to the inner peripheral portion from an end of the rotor shaft on the first side in the axial direction,
The rotary electric machine rotor according to any one of claims 1 to 8, wherein the second supply unit supplies oil to the inner peripheral portion from an end of the rotor shaft on the second axial side. The weir is a first weir,
An annular second member that is disposed on the second axial side with respect to the opening, protrudes radially inward from the inner peripheral surface, and is disposed so as to extend in the circumferential direction along the inner peripheral surface. The rotating electric machine rotor according to any one of claims 1 to 9, further comprising a weir portion. A rotating electric machine comprising the rotating electric machine rotor according to any one of claims 1 to 10,
An oil pump that supplies oil to the oil supply unit,
The vehicle drive device includes a first oil pump that is drivingly connected to the rotor shaft and driven by rotation of the rotor shaft. An internal combustion engine and the rotating electric machine are provided as driving power sources for wheels,
The vehicle drive device according to claim 11, wherein the oil pump includes a second oil pump that is drivingly connected to the internal combustion engine and driven by a driving force of the internal combustion engine.

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