JP2018057243A - Vehicle drive device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a vehicle drive device which can properly cool both of a rotor and a stator of a first rotary electric machine included as a driving power source of a wheel regardless of a vehicle speed.SOLUTION: A vehicle drive device 1 includes: a first oil passage 91 which supplies an oil discharged by a first hydraulic pump 51 to a rotor 14 as a cooling oil and supplies the oil to a power transmission mechanism 3 as a lubrication oil; and a second oil passage 92 which supplies an oil discharged by a second hydraulic pump 52 to a stator 11 as a cooling oil.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a vehicle drive device.

  A vehicle drive device including a rotating electrical machine as a wheel driving force source may be provided with a cooling structure for cooling the rotating electrical machine with oil. Japanese Patent Application Laid-Open No. 6-98417 (Patent Document 1) describes an example of such a cooling structure. Specifically, oil discharged by an electric oil pump (105) is supplied to a stator (27, 28). ) To cool the coils (31, 32) directly. In the configuration described in Patent Document 1, a mechanical oil pump (91) driven in conjunction with the rotation of the torque transmission system between the rotating electrical machine and the wheels is provided in addition to the electric oil pump (105). . In the configuration described in Patent Document 1, a cooling circuit (109) for supplying oil discharged from the electric oil pump (105) to the stator (27, 28) and a mechanical oil pump (91) are discharged. A lubrication circuit (104) for supplying the oil to the lubrication site is connected to each other via an oil passage (110). Thus, when the amount of oil discharged from the mechanical oil pump (91) is large, such as when the vehicle is traveling at high speed, an amount of oil necessary for cooling the coils (31, 32) is transferred from the lubrication circuit (104) to the oil passage. (110) can be supplied to the cooling circuit (109), during which the operation of the electric oil pump (105) can be stopped. Further, when the amount of oil discharged from the mechanical oil pump (91) is small, such as when the vehicle is stopped or running at a low speed, the electric oil pump (105) is operated to supply oil for lubricating the lubrication site. The cooling circuit (109) can supply the lubricating circuit (104) via the oil passage (110). As a result, it is possible to prevent heat generation in the torque transmission system due to insufficient lubrication, It is possible to eliminate the start.

  By the way, in the configuration described in Patent Document 1, when the electric oil pump (105) is operated to cool the stator (27, 28) while the vehicle is stopped (vehicle stopped state), the electric oil pump is used. A certain proportion of the oil discharged from (105) is not supplied to the stators (27, 28), and is supplied to the lubrication site that does not require much oil when the vehicle is stopped. Therefore, the cooling efficiency of the stator (27, 28) is reduced by the amount of oil supplied to the lubrication site, and electric power corresponding to the amount of oil supplied excessively to the lubrication site is converted to electric oil. The pump (105) is wasted. In the configuration described in Patent Document 1, the rotor (41, 42) including the permanent magnets (43, 44) generates heat due to iron loss when the motor (24, 25) is driven. Therefore, depending on the degree of heat generation of the rotor (41, 42), it is necessary to effectively cool the rotor (41, 42) in addition to the stator (27, 28). There is no description about the cooling of 42).

JP-A-6-98417 (paragraphs 0032 to 0035, etc.)

  Therefore, it is desired to realize a vehicle drive device capable of appropriately cooling both the rotor and the stator of the first rotating electrical machine provided as a wheel driving force source regardless of the vehicle speed.

  In view of the above, a first rotating electrical machine having a rotor and a stator, a power transmission mechanism for transmitting a rotational driving force between the first rotating electrical machine and wheels, and a first hydraulic pressure driven by the first rotating electrical machine A pump and a second hydraulic pump driven by a second rotating electrical machine different from the first rotating electrical machine, wherein the second rotating electrical machine is separated from a transmission path of rotational driving force by the power transmission mechanism. The vehicular drive device is provided with a first oil passage that supplies oil discharged from the first hydraulic pump as cooling oil to the rotor and as lubricating oil to the power transmission mechanism; And a second oil passage that supplies oil discharged from the hydraulic pump to the stator as cooling oil.

Since the rotor of the first rotating electrical machine provided as a driving force source for the wheel rotates at a rotational speed according to the vehicle speed, the amount of heat generated by the rotor due to iron loss increases as the frequency of the alternating magnetic field increases (that is, the vehicle speed increases). Grows) In this regard, according to the above characteristic configuration, the oil discharged by the first hydraulic pump driven by the first rotating electrical machine (that is, the first hydraulic pump that increases the amount of oil discharged as the vehicle speed increases) is cooled. Since it can be supplied to the rotor as oil, more cooling oil can be supplied to the rotor whose calorific value increases as the vehicle speed increases, as the vehicle speed increases. That is, when the amount of cooling oil supplied to the rotor is too small, the rotor cannot be cooled appropriately, and when the amount of cooling oil supplied to the rotor is excessive, However, according to the above-described characteristic configuration, it is possible to supply the cooling oil having an oil amount corresponding to the heat generation amount of the rotor to the rotor so that the rotor can be appropriately cooled. Become. Note that the oil discharged by the first hydraulic pump that increases in volume as the vehicle speed increases is also supplied to the power transmission mechanism as lubricating oil, so that each part of the power transmission mechanism is properly lubricated while the vehicle is running. You can also
On the other hand, when the stator of the first rotating electrical machine provided as a wheel driving force source is an armature around which a coil is wound, the amount of heat generated by the stator does not depend directly on the vehicle speed, and the current flowing in the coil Increases as becomes larger. In this regard, according to the above characteristic configuration, the second hydraulic pump driven by the second rotating electrical machine provided separately from the transmission path of the rotational driving force by the power transmission mechanism (that is, discharge regardless of the vehicle speed). The oil discharged by the second hydraulic pump capable of adjusting the oil amount can be supplied to the stator as cooling oil. Therefore, it becomes possible to cool the stator appropriately by supplying the stator with an amount of cooling oil corresponding to the amount of heat generated by the stator.
As described above, according to the above characteristic configuration, the rotor of the first rotating electrical machine is cooled by the oil discharged from the first hydraulic pump, and the stator of the first rotating electrical machine is cooled by the oil discharged by the second hydraulic pump. With the configuration, both the rotor and the stator can be appropriately cooled regardless of the vehicle speed. In addition, compared with the case where the rotor of the first rotating electrical machine is cooled by the oil discharged from the second hydraulic pump, the second hydraulic pump is reduced in size by reducing the maximum amount of discharged oil required for the second hydraulic pump. There is also an advantage of being able to.

Partial sectional drawing of the vehicle drive device which concerns on embodiment Partial enlarged view of FIG. Another partially enlarged view of FIG. Sectional drawing of the differential gear mechanism which concerns on embodiment The figure which shows the 1st oil level and 2nd oil level which concern on embodiment Simplified diagram of hydraulic circuit according to the embodiment

  An embodiment of a vehicle drive device will be described with reference to the drawings. In the embodiment described below, the first oil passage hole 61 corresponds to the “communication hole”, the first insertion hole 44 corresponds to the “insertion hole”, and the first wall portion 41 corresponds to the “target wall portion”. It corresponds to.

  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 functioning as both a motor and a generator as necessary. Further, in the present specification, regarding the arrangement of the two members, “overlapping when viewed in a certain direction” means that when a virtual straight line parallel to the visual line direction is moved in each direction orthogonal to the virtual straight line, It means that the region where the virtual straight line intersects both of the two members exists at least in part. In this specification, regarding the shape of a member, “extends in a certain direction” means that the direction in which the member extends is not limited to a shape parallel to the reference direction, with the direction as the reference direction. Is used as a concept including a shape whose crossing angle is within a predetermined range (for example, less than 45 degrees) even if the direction intersects the reference direction.

  In the following description, unless otherwise specified, the “axial direction L” is defined with reference to the rotation axis A (see FIGS. 4 and 5) of the differential gear mechanism 30. The rotation axis A is a virtual axis, and the differential input gear 31 and the differential case 33 of the differential gear mechanism 30 rotate around the rotation axis A. One side of the axial direction L is referred to as “axial first side L1”, and the other side of the axial direction L (opposite side to the axial first side L1) is referred to as “axial second side L2.” In the following description, unless otherwise specified, the “radial direction R” is defined with reference to the rotation axis (virtual axis) of the first rotating electrical machine 10. The rotor 14 of the first rotating electrical machine 10 rotates around this rotation axis. The direction about each member in the following description represents the direction in the state in which they were assembled to the vehicle drive device 1. Further, “upper” and “lower” are defined with reference to a vertical direction (vertical direction Z in FIGS. 4 and 5) in a state where the vehicle drive device 1 is mounted on the vehicle. Moreover, the term regarding the direction, position, etc. about each member is a concept including the state which has the difference by the error which can be accept | permitted on manufacture.

  As shown in FIG. 1, the vehicle drive device 1 includes a first rotating electrical machine 10 and a rotational driving force between the first rotating electrical machine 10 and a plurality of wheels W (two left and right wheels W in the present embodiment). And a power transmission mechanism 3 for transmitting the power. The plurality of wheels W include the first wheel W1, and in the present embodiment, the first wheel W1 and the second wheel W2 are included in the plurality of wheels W. The vehicle (the vehicle on which the vehicle drive device 1 is mounted) travels by the torque of the first rotating electrical machine 10 transmitted to each wheel W via the power transmission mechanism 3. The power transmission mechanism 3 includes a differential gear mechanism 30 that distributes torque input from the first rotating electrical machine 10 side to a plurality of wheels W. In the present embodiment, the power transmission mechanism 3 includes a counter gear mechanism 20 that transmits a rotational driving force between the first rotating electrical machine 10 and the differential gear mechanism 30, and the differential gear mechanism 30 includes a counter gear mechanism 30. Torque of the first rotating electrical machine 10 is input via the gear mechanism 20. The vehicle drive device 1 according to the present embodiment is a drive device for driving a wheel W (rear wheel) on the rear side of the vehicle. The vehicle drive device 1 according to the present embodiment is disposed, for example, under a vehicle floor.

  The first rotating electrical machine 10 is electrically connected to a power storage device (not shown) provided in the vehicle, and receives power supplied from the power storage device to generate power. At this time, the power generated by the first rotating electrical machine 10 is transmitted to the wheels W via the power transmission mechanism 3. Further, when the first rotating electrical machine 10 applies a braking force by regeneration to the wheels W, the electric power generated by the first rotating electrical machine 10 is supplied to the power storage device. A second rotating electrical machine 2 (see FIG. 6), which will be described later, also receives power from a power storage device (not shown) provided in the vehicle to generate power.

  The vehicle drive device 1 includes a case 40 that houses the first rotating electrical machine 10. The case 40 also houses at least a part of the power transmission mechanism 3. In the present embodiment, most of the power transmission mechanism 3 is accommodated inside the case 40, but as shown in FIG. 4, a part of the output shaft 4 provided in the power transmission mechanism 3 is outside the case 40. Be placed. As shown in FIGS. 1 and 4, a first space S <b> 1 that houses the differential gear mechanism 30 and a second space S <b> 2 that houses the first rotating electrical machine 10 are formed inside the case 40. In the present embodiment, the counter gear mechanism 20 is also accommodated in the first space S1.

  In the present embodiment, the first rotating electrical machine 10 is disposed on another axis parallel to the rotation axis A (see FIGS. 4 and 5) of the differential gear mechanism 30. Therefore, in the present embodiment, the axial direction of the first rotating electrical machine 10 (hereinafter referred to as “rotating electrical machine axial direction”) coincides with the axial direction L. As shown in FIG. 2, the first rotating electrical machine 10 includes a rotor 14 and a stator 11. The stator 11 includes a stator core 12 that is fixed to the case 40. In the present embodiment, the first rotating electrical machine 10 is a rotating field type rotating electrical machine, and a coil is wound around the stator core 12. Coil end portions 13, which are coil portions protruding from the stator core 12 in the rotating electrical machine axial direction (axial direction L in the present embodiment), are formed on both sides of the rotating electrical machine axial direction from the stator core 12.

  The rotor 14 is supported by the case 40 so as to be rotatable with respect to the stator 11. As shown in FIG. 2, the rotor 14 includes a rotor core 15 that is disposed inside the stator core 12 in the radial direction R so as to overlap the stator core 12 when viewed in the radial direction R. That is, in the present embodiment, the first rotating electrical machine 10 is an inner rotor type rotating electrical machine. As described above, the first rotating electrical machine 10 includes the rotor core 15 and the stator core 12 that is disposed outside the rotor core 15 in the radial direction R. The stator core 12 has a cylindrical inner peripheral surface 12 a that faces the outer peripheral surface 15 a of the rotor core 15 in the radial direction R. The outer peripheral surface 15a of the rotor core 15 is formed in a cylindrical shape extending in the axial direction of the rotating electrical machine (in the present embodiment, the axial direction L). In the present embodiment, the inner peripheral surface 12 a of the stator core 12 is formed by the end surfaces on the inner sides in the radial direction R of the plurality of teeth formed on the stator core 12.

  As shown in FIG. 2, the rotor core 15 is fixed to the outer peripheral surface of the rotor shaft 16 that is rotatably supported with respect to the case 40. That is, the rotor 14 includes a rotor shaft 16 that is rotatably supported with respect to the case 40, and a rotor core 15 that is fixed to the outer peripheral surface of the rotor shaft 16. The inner peripheral surface of the rotor core 15 is in contact with the rotor shaft 16 so that heat can be transferred. In the present embodiment, the first rotating electrical machine 10 is a rotating electrical machine having an embedded magnet structure (for example, a synchronous motor), and a permanent magnet is embedded in the rotor core 15.

  As shown in FIGS. 1 to 3, the case 40 includes a first wall portion 41 disposed on one side of the rotating electrical machine in the axial direction of the rotor core 15 (the first axial direction side L <b> 1 in this embodiment), and the rotor core 15. 2nd wall part 42 arrange | positioned in the other side (this embodiment axial direction 2nd side L2 in this embodiment) rather than a rotary electric machine axial direction. In the present embodiment, the case 40 further includes a third wall portion 43 disposed between the first wall portion 41 and the rotor core 15 in the rotating electrical machine axial direction (the axial direction L in the present embodiment). The first space S1 described above is formed between the first wall portion 41 and the third wall portion 43 in the rotary electric machine axial direction, and the second space S2 described above is formed with the second wall portion 42 in the rotary electric machine axial direction. It is formed between the third wall 43. Therefore, the first space S <b> 1 and the second space S <b> 2 are partitioned by the third wall portion 43 in the rotating electric machine axial direction.

  The rotor shaft 16 is rotatably supported with respect to the case 40 by the second wall portion 42 and the third wall portion 43. Specifically, as shown in FIG. 2, the first bearing B <b> 1 that rotatably supports the rotor shaft 16 with respect to the third wall portion 43 is disposed on the first axial side L <b> 1 from the rotor core 15. A second bearing B <b> 2 that rotatably supports the rotor shaft 16 with respect to the second wall portion 42 is disposed on the second axial side L <b> 2 from 15.

  The rotor shaft 16 is connected to an output gear 17 for outputting torque of the first rotating electrical machine 10. In this embodiment, as shown in FIGS. 1 and 3, the output gear 17 connected to the rotor shaft 16 of the first rotating electrical machine 10 is a first wall in the rotating electrical machine axial direction (axial direction L in the present embodiment). It is arranged between the part 41 and the third wall part 43. In the present embodiment, the output gear 17 is arranged on the first axial side L1 with respect to the rotor shaft 16 so as to be coaxial with the rotor shaft 16 and rotate integrally with the rotor shaft 16. The output gear 17 is rotatably supported with respect to the case 40 by the first wall portion 41 and the third wall portion 43. Specifically, as shown in FIG. 3, the intermediate shaft 8 formed with the output gear 17 is rotatably supported with respect to the first wall portion 41 on the first axial side L1 from the output gear 17. Three bearings B <b> 3 are disposed, and a fourth bearing B <b> 4 that rotatably supports the intermediate shaft 8 with respect to the third wall portion 43 is disposed on the second axial side L <b> 2 from the output gear 17. As shown in FIG. 2, the end of the intermediate shaft 8 on the second axial side L2 is connected to the end of the rotor shaft 16 on the first axial side L1 by spline engagement. As a result, the rotor shaft 16 is coupled to rotate integrally with the output gear 17.

  As shown in FIGS. 1 and 3, the counter gear mechanism 20 includes a first gear 21 that meshes with the output gear 17 of the first rotating electrical machine 10 and a second gear 22 that meshes with the differential input gear 31 of the differential gear mechanism 30. And a connecting shaft 23 that connects the first gear 21 and the second gear 22. The counter gear mechanism 20 is disposed between the first wall portion 41 and the third wall portion 43 in the rotating electrical machine axial direction (the axial direction L in the present embodiment), and the connecting shaft 23 is connected to the first wall portion 41. And the third wall 43 are rotatably supported with respect to the case 40. Specifically, as shown in FIG. 3, a fifth shaft that rotatably supports the connecting shaft 23 with respect to the first wall portion 41 on the first axial side L1 relative to the first gear 21 and the second gear 22. A bearing B5 is disposed, and a sixth bearing B6 that rotatably supports the coupling shaft 23 with respect to the third wall portion 43 is disposed on the second axial side L2 relative to the first gear 21 and the second gear 22. Yes.

  As shown in FIG. 4, the differential gear mechanism 30 includes a differential input gear 31, a differential output gear 32 (side gear), a differential output gear 32, and a differential rotation that integrally rotates with the differential input gear 31. A moving case 33. In this specification, the rotational axis of the differential input gear 31 and the differential case 33 that rotate integrally with each other is used as the rotational axis A of the differential gear mechanism 30. In the present embodiment, at least a part of the differential gear mechanism 30 is disposed at a height between the uppermost part and the lowermost part of the rotor 14 of the first rotating electrical machine 10. In other words, the differential gear mechanism 30 and the rotor 14 have overlapping arrangement areas in the vertical direction Z. Specifically, as is apparent from the positional relationship in the vertical direction Z between the outer peripheral surface 15a of the rotor core 15 and the rotation axis A of the differential gear mechanism 30 shown in FIG. The rotation axis A is arranged at a height between the uppermost part and the lowermost part of the rotor core 15 of the first rotating electrical machine 10. The outer peripheral surface 15a of the rotor core 15 is disposed slightly inward in the radial direction R from the inner peripheral surface 12a of the stator core 12, but in FIG. 5, for the sake of simplicity, the outer peripheral surface 15a and the inner peripheral surface 12a Are indicated by the same line segment.

  The differential input gear 31 is a gear that meshes with a gear for inputting the torque of the first rotating electrical machine 10 to the differential gear mechanism 30. In the present embodiment, the differential input gear 31 meshes with the second gear 22 of the counter gear mechanism 20. As shown in FIG. 4, a pinion shaft 37 that rotates integrally with the differential case 33 and a plurality of pinion gears 36 that are rotatably supported by the pinion shaft 37 are disposed inside the differential case 33. . A pair of differential output gears 32 is provided so as to be arranged separately on both sides in the axial direction L with respect to the pinion shaft 37, and each of the pair of differential output gears 32 meshes with the plurality of pinion gears 36. Is arranged.

  As shown in FIG.1 and FIG.4, each of a pair of differential output gear 32 is connected with the wheel W by the output shaft 4 (drive shaft). That is, the power transmission mechanism 3 includes an output shaft 4 that connects the differential gear mechanism 30 and the wheels W. When one of the two left and right wheels W is a first wheel W1, and the other of the two left and right wheels W is a second wheel W2, the power transmission mechanism 3 is a differential gear mechanism 30 (specifically, a pair of differential wheels The output shaft 4 that connects one of the output gears 32 and the first wheel W1, the differential gear mechanism 30 (specifically, the other of the pair of differential output gears 32) and the second wheel W2 are connected. And an output shaft 4. Each of the differential output gears 32 is connected so as to rotate integrally with the output shaft 4 (for example, connected by spline engagement). When torque is input to the differential input gear 31, the pair of differential output gears 32 (the pair of output shafts 4) are rotationally driven by the rotation of the plurality of pinion gears 36 as the differential case 33 rotates. . At this time, if a difference in rotational resistance occurs between the first wheel W1 and the second wheel W2 due to the vehicle traveling on a curved road or the like, the plurality of pinion gears 36 rotate, thereby a pair of differential output gears. 32 rotate at different speeds.

  As shown in FIG. 4, the output shaft 4 is rotatably supported with respect to the case 40 while being inserted into an insertion hole 46 that communicates the inside and the outside of the case 40. And the sealing member 5 which has the contact surface 5a which contacts in the state which slides with respect to the outer peripheral surface of the output shaft 4 is arrange | positioned at the inner peripheral surface of the insertion hole 46. FIG. The seal member 5 is provided to prevent oil inside the case 40 from leaking out of the case 40 through the insertion hole 46. In this embodiment, the seal member 5 includes an annular fixed portion that is press-fitted into the inner peripheral surface of the insertion hole 46, and an annular seal portion that contacts the outer peripheral surface of the output shaft 4 while being supported by the fixed portion. The contact surface 5a is formed by the inner peripheral surface of the seal portion. A member (cylindrical member) that rotates integrally with the output shaft 4 is disposed in a radial direction (with reference to the rotation axis A) at a portion arranged at the same position in the axial direction L as the insertion hole 46 in the output shaft 4. When arranged on the outer side in the radial direction, the contact surface 5a of the seal member 5 can be configured to come into contact with the outer peripheral surface of the member rotating integrally with the output shaft 4 in a sliding state. .

  As shown in FIG. 4, the differential gear mechanism 30 includes washers (34, 35) disposed between the differential case 33 and the differential output gear 32 in the axial direction of the output shaft 4. Since the output shaft 4 is arranged coaxially with the rotation axis A, the axial direction of the output shaft 4 coincides with the axial direction L. The washers (34, 35) are arranged so as to come into contact with the end surface of the differential output gear 32 opposite to the pinion shaft 37 in the axial direction L. In the present embodiment, the differential gear mechanism 30 includes two washers (34, 35) of a conical washer 34 and a side washer 35 between one of the pair of differential output gears 32 and the differential case 33. Between the other of the pair of differential output gears 32 and the differential case 33, two washers (34, 35) of a conical washer 34 and a side washer 35 are provided. The side washer 35 is a thrust washer formed in an annular plate shape, and is used to reduce the frictional resistance between the differential output gear 32 and the differential case 33. The conical washer 34 is a disc spring and is used to bias the differential output gear 32 toward the pinion gear 36 by an elastic restoring force.

  As shown in FIG. 6, the vehicle drive device 1 includes hydraulic pumps (51, 52). As shown in FIGS. 5 and 6, in the case 40, a first reservoir 70 that stores oil sucked by the hydraulic pump (51, 52) and an upper side of the first reservoir 70 are arranged. And a second reservoir 80 for storing oil is formed. The second storage unit 80 functions as a catch tank that stores oil in order to lower the oil level of the first storage unit 70. The second reservoir 80 is fixed to the inner surface of the case 40 with fastening bolts or the like.

  In the present embodiment, the vehicle drive device 1 includes two hydraulic pumps (51, 52), a first hydraulic pump 51 and a second hydraulic pump 52. The first hydraulic pump 51 is a pump that is connected to the differential gear mechanism 30 in an inseparable manner and is always driven in conjunction with the rotation of the differential gear mechanism 30. In other words, the first hydraulic pump 51 is a pump that is driven in conjunction with the rotation of the plurality of wheels W. That is, the first hydraulic pump 51 is a pump driven by the first rotating electrical machine 10. Therefore, the amount of oil discharged from the first hydraulic pump 51 increases as the vehicle speed increases. As shown in FIG. 3, in this embodiment, the pump drive shaft 53 that is connected to the pump rotor of the first hydraulic pump 51 and drives the first hydraulic pump 51 rotates integrally with the connection shaft 23 of the counter gear mechanism 20. So that they are connected. That is, in the present embodiment, the first hydraulic pump 51 (pump drive shaft 53) is connected to the differential gear mechanism 30 through the counter gear mechanism 20 so as not to be separated. In the present embodiment, the first hydraulic pump 51 is provided on the first wall portion 41. Specifically, a pump chamber that houses the pump rotor is formed between the first wall portion 41 and the pump cover 54 attached to the end surface of the first wall portion 41 on the first axial side L1. . In the present embodiment, at least the former state of the state where the plurality of wheels W are rotating in the forward direction of the vehicle and the state where the plurality of wheels W are rotating in the backward direction of the vehicle, The hydraulic pump 51 is configured to be driven in conjunction with the rotation of the differential gear mechanism 30 (in conjunction with the rotation of the plurality of wheels W).

  As shown in FIG. 6, the second hydraulic pump 52 is a pump driven by a second rotating electrical machine 2 different from the first rotating electrical machine 10. The second rotating electrical machine 2 is provided separately from the rotational driving force transmission path by the power transmission mechanism 3. That is, the second hydraulic pump 52 is a pump driven by a dedicated rotating electrical machine, and the amount of oil discharged from the second hydraulic pump 52 can be adjusted independently of the vehicle speed, unlike the first hydraulic pump 51. . As the first hydraulic pump 51 and the second hydraulic pump 52, for example, an internal gear pump, an external gear pump, a vane pump, or the like can be used. In FIG. 6, the first hydraulic pump 51 is expressed as MOP (Mechanical Oil Pump), the second hydraulic pump 52 is expressed as EOP (Electric Oil Pump), and the second rotating electrical machine 2 is expressed as M (Motor). The counter gear mechanism 20 is expressed as CG (Counter Gear), and the oil cooler 7 described later is expressed as O / C (Oil Cooler).

  As shown in FIGS. 5 and 6, the first reservoir 70 is formed in a lower portion (the bottom of the case 40) inside the case 40. The height of the oil level of the first reservoir 70 varies depending on the amount of oil present in each oil path and the second reservoir 80 provided in the vehicle drive device 1. Here, the height of the oil level of the first reservoir 70 in a state where the rotation of the plurality of wheels W is stopped is referred to as a “first height H1”. That is, the first height H1 is the height of the oil level of the first reservoir 70 when the vehicle is stopped. In the present embodiment, the first height H1 is the height of the oil level of the first reservoir 70 when the vehicle is stopped on a flat road.

  In addition, the height of the oil level of the first reservoir 70 in a state where the plurality of wheels W are rotating is referred to as “second height H2”. That is, the second height H2 is the height of the oil level of the first reservoir 70 when the vehicle is running. In the present embodiment, the second height H2 is the height of the oil level of the first reservoir 70 when the plurality of wheels W are rotating in the forward direction of the vehicle (the state where the vehicle is traveling forward). To do. Hereinafter, unless otherwise specified, the “vehicle traveling state” refers to a state in which the vehicle is traveling forward. In the present embodiment, the second height H2 is the first storage in a state where the vehicle is traveling straight on a flat road at a constant speed (that is, a state where no inertial force is applied to the first storage unit 70). The height of the oil level of the portion 70 is assumed.

  As described above, in the present embodiment, the first space S1 that houses the differential gear mechanism 30 and the second space S2 that houses the first rotating electrical machine 10 are formed inside the case 40 ( (See FIG. 1). In this embodiment, the 1st storage part 70 is formed over the lower part in 1st space S1, and the lower part in 2nd space S2. In the present embodiment, as shown in FIG. 6, the first space S1 and the first space S1 are located at positions lower than the second height H2 in the third wall portion 43 that divides the first space S1 and the second space S2. A communication portion 45 that communicates with the two spaces S2 is formed. Therefore, the oil level in the second space S2 rises or falls according to the height of the oil level in the first space S1. In a static state where no oil moves inside the case 40, the oil level in the second space S2 matches the oil level in the first space S1.

  As shown in FIGS. 1 and 6, in the present embodiment, the discharge port 51 a of the first hydraulic pump 51 communicates with a supply unit 96 that supplies oil to the second storage unit 80. Therefore, in the vehicle running state, the first hydraulic pump 51 is driven to suck the oil in the first reservoir 70, and at least a part of the oil sucked from the first reservoir 70 is the second reservoir 80. To be stored. Therefore, the second height H2 is not less than the height corresponding to the amount of oil stored in the second reservoir 80 and lower than the first height H1. As shown in FIG. 1, in the present embodiment, a reservoir oil passage 97 that connects the discharge port 51 a (see FIG. 3) of the first hydraulic pump 51 and the supply unit 96 is formed in the first wall portion 41. . As shown in FIGS. 1 and 5, the supply unit 96 is formed above the second storage unit 80, and in this embodiment, the inner surface of the case 40 (above the second storage unit 80 ( It is formed so as to open in the inner surface of the first wall portion 41. The second reservoir 80 is formed in a tank shape that opens upward, and the oil that has flowed out of the supply unit 96 is supplied into the second reservoir 80 from the upper opening of the second reservoir 80.

  In the present embodiment, as shown in FIGS. 5 and 6, the second height H <b> 2 is a height at which a part of the lower side of the differential input gear 31 is immersed in the oil in the first reservoir 70. Moreover, as shown in FIG. 1, the 2nd storage part 80 and the differential input gear 31 are arrange | positioned so that the arrangement | positioning area | region of the axial direction L of the differential input gear 31 may mutually overlap. Then, as shown in FIG. 5, the oil in the first reservoir 70 raked up by the differential input gear 31 that rotates forward (the differential input gear 31 that rotates in the direction indicated by the solid thick arrow in FIG. 5). A supply oil passage 94 for supplying the second reservoir 80 is formed inside the case 40. The supply oil passage 94 is formed in a gap between the outer peripheral portion of the differential input gear 31 and the inner surface of the case 40. The normal rotation is a rotation direction for rotating the wheel W in the forward direction of the vehicle. Therefore, in the vehicle running state, the oil in the first reservoir 70 that is scooped up by the differential input gear 31 moves to the space above the second reservoir 80 in the case 40 through the supply oil passage 94. After that, the second reservoir 80 is supplied to the inside of the second reservoir 80 from the upper opening of the second reservoir 80.

  Thus, in this embodiment, the supply of oil from the first storage unit 70 to the second storage unit 80 in the vehicle traveling state is both the driving of the first hydraulic pump 51 and the scraping by the differential input gear 31. Is done by. Therefore, compared with the case where oil is supplied from the first reservoir 70 to the second reservoir 80 only by driving either the first hydraulic pump 51 or scraping by the differential input gear 31, the vehicle It is possible to increase the rate of decrease in the oil level of the first reservoir 70 after starting forward travel.

  As shown in FIG. 5, in the present embodiment, the second storage portion 80 includes two chambers arranged in a horizontal direction (left-right direction in FIG. 5) orthogonal to the axial direction L (axial direction of the differential input gear 31). 81, 82). Each of the two chambers (81, 82) is formed in a tank shape opening upward. Here, the chamber close to the supply oil passage 94 of the two chambers (81, 82) is referred to as a first chamber 81, and the remaining chambers are referred to as second chambers 82. In the present embodiment, the supply unit 96 that supplies oil to the second storage unit 80 is provided at a position where oil can be supplied to the second chamber 82. In other words, in the present embodiment, the discharge port 51 a of the first hydraulic pump 51 communicates with the supply unit 96 that supplies oil to the second chamber 82.

  In the present embodiment, the upper end of the peripheral wall portion (first peripheral wall portion 81a) that partitions the first chamber 81 is lower than the upper end of the peripheral wall portion (second peripheral wall portion 82a) that partitions the second chamber 82. Is arranged. In addition, although the partition 83 which divides the 1st chamber 81 and the 2nd chamber 82 is contained in each of the 1st surrounding wall part 81a and the 2nd surrounding wall part 82a, the height of the upper end of the 1st surrounding wall part 81a is It is set as the height of the upper end of the part except the partition 83 in the 1st surrounding wall part 81a. Thus, by arranging the upper end of the first peripheral wall portion 81a at a position lower than the upper end of the second peripheral wall portion 82a, the first peripheral wall is compared with the case where these upper ends are arranged at the same height. It is possible to secure a large space above the portion 81 a and improve the efficiency of supplying oil from the supply oil passage 94 to the first chamber 81. In the present embodiment, the volume of the first chamber 81 is smaller than the volume of the second chamber 82. That is, the second chamber 82 to which oil is supplied from the supply unit 96 is formed to have a larger volume than the first chamber 81, and it is possible to appropriately secure the storable capacity of the second storage unit 80. ing.

  As shown in FIG. 5, in the present embodiment, the second reservoir 80 includes a discharge portion 84 that supplies the oil in the second reservoir 80 to at least one of the output gear 17 and the first gear 21. . In the present embodiment, the discharge portion 84 is formed at a position above the output gear 17 and overlapping the output gear 17 when viewed in the vertical direction Z. Therefore, in the present embodiment, the discharge unit 84 is configured to supply oil directly to the output gear 17. In addition, the structure in which the discharge part 84 is formed in the position which supplies oil directly with respect to the meshing part of the output gear 17 and the first gear 21, or the discharge part 84 supplies oil to the first gear 21 directly. It can also be set as the structure formed in a position. In the present embodiment, the discharge part 84 is formed at the lowermost part of the second chamber 82. Further, in the present embodiment, the discharge part 84 is formed by a through-hole that penetrates the bottom part of the second storage part 80 in the vertical direction Z. Although not shown in the drawings, a discharge portion that supplies oil in the second storage portion 80 to a gear (for example, the differential input gear 31) included in the power transmission mechanism 3 is also formed in the lowermost portion of the first chamber 81. Yes. Therefore, when the vehicle stops from the state where the vehicle is running, the oil is discharged from the discharge unit 84 in a state where the supply of oil to the second storage unit 80 is stopped. The amount of oil stored is returned to the state before the vehicle started to travel. Along with this, the height of the oil level of the first reservoir 70 increases from the second height H2 to the first height H1.

  Here, from the oil amount of the first reservoir 70 when the oil level of the first reservoir 70 is the first height H1, the height of the oil level of the first reservoir 70 is the second height. If the value obtained by subtracting the amount of oil in the first reservoir 70 in the case of H2 is “difference oil amount”, the first reservoir in the vehicle traveling state in order to set the second height H2 to a desired height. The amount of oil existing in a place other than 70 needs to be the difference oil amount. And in order to make oil quantity which exists in places other than the 1st storage part 70 into the above-mentioned differential oil quantity, the sum total of the volume of each place where oil can exist other than the 1st storage part 70 is the above-mentioned It must be greater than the differential oil amount. In places other than the first reservoir 70 where oil can exist, the second reservoir 80 and the oil in the first reservoir 70 are guided to the oil supply target by driving the first hydraulic pump 51. For example, the oil storage capacity of the second storage unit 80 and the oil path for guiding the oil of the first storage unit 70 to the oil supply target by driving the first hydraulic pump 51 are included. It can be set as the structure whose sum with a volume becomes more than the said difference oil amount. The volume of the oil passage here does not include the volume of oil remaining in the oil passage when the vehicle is stopped. In the present embodiment, the oil passage for guiding the oil in the first reservoir 70 to the oil supply target by driving the first hydraulic pump 51 includes a first oil passage 91 described later and the above-described reservoir oil passage 97. included. Suction oil for connecting the first reservoir 70 and the suction port of the first hydraulic pump 51 to an oil passage for guiding the oil of the first reservoir 70 to the oil supply target by driving the first hydraulic pump 51. A road may be included.

  In the present embodiment, a second hydraulic pump 52 is provided in addition to the first hydraulic pump 51, and the second hydraulic pump 52 also sucks oil in the first reservoir 70. Therefore, when the oil level of the first reservoir 70 in the vehicle running state and the second hydraulic pump 52 operating is set to the second height H2, the oil is stored in the second reservoir 80. The possible capacity, the volume of the oil passage for guiding the oil in the first reservoir 70 to the oil supply target by driving the first hydraulic pump 51, and the oil in the first reservoir 70 by driving the second hydraulic pump 52 The sum with the volume of the oil path for leading to the oil supply target may be the difference oil amount or more. The volume of the oil passage here does not include the volume of oil remaining in the oil passage when the vehicle is stopped. In the present embodiment, the oil passage for guiding the oil in the first reservoir 70 to the oil supply target by driving the second hydraulic pump 52 includes a second oil passage 92 described later. Suction oil for connecting the first reservoir 70 and the suction port of the second hydraulic pump 52 to an oil passage for guiding the oil of the first reservoir 70 to the oil supply target by driving the second hydraulic pump 52 A road may be included.

  In the present embodiment, as shown in FIGS. 4 and 5, the first height H <b> 1 is at least a part of the differential gear mechanism 30 (the lower part in the present embodiment). It will be soaked in height. Thereby, the state of the differential gear mechanism 30 at the time of starting rotation with the start of the vehicle can be set to a state in which at least a part is immersed in oil. As a result, the differential gear mechanism 30 is set when the vehicle starts. It is possible to reduce the possibility of occurrence of insufficient lubrication.

  Specifically, in the present embodiment, the first height H <b> 1 is a height above the lowermost portion of the contact surface 5 a of the seal member 5. In the present embodiment, the first height H1 is lower than the rotation axis A. In the present embodiment, the first height H <b> 1 is a height at which at least a part of the washers (34, 35) (a part of the lower side in the present embodiment) is immersed in the oil in the first reservoir 70. Specifically, the first height H <b> 1 is a height at which a part of the lower side of the conical washer 34 and a part of the lower side of the side washer 35 are immersed in the oil in the first reservoir 70. As shown in FIG. 4, in this embodiment, the contact surface 5a (the seal member 5 on the second axial side L2) that contacts the outer peripheral surface of the output shaft 4 connected to the first wheel W1 (see FIG. 1). The lowermost part of the contact surface 5a) is a contact surface 5a (contact surface 5a of the seal member 5 on the first axial side L1) that contacts the outer peripheral surface of the output shaft 4 connected to the second wheel W2 (see FIG. 1). ) Above the lowermost part. In such a case, it is preferable that the first height H1 is a height that is higher than the lowest portions of both of the seal members 5 on both sides in the axial direction L. In other words, the wheel W on the side where the lowermost seal member 5 of the pair of seal members 5 is provided is the first wheel W1, and the first height H1 is the first wheel W1. It is preferable that the height is higher than the lowermost portion of the contact surface 5a that contacts the outer peripheral surface of the output shaft 4 to be connected.

  The first height H <b> 1 can vary depending on the operating state of the second hydraulic pump 52. Considering this point, for example, the first height H1 can be the height of the oil level of the first reservoir 70 when the vehicle is stopped and the second hydraulic pump 52 is not operating. . Note that the first height H1 may be the oil level of the first reservoir 70 when the vehicle is stopped and the second hydraulic pump 52 is operating.

  In the present embodiment, as shown in FIGS. 5 and 6, the second height H <b> 2 is lower than the lowermost portion (lowermost portion of the outer peripheral surface 15 a) of the rotor core 15 of the first rotating electrical machine 10. That is, in the present embodiment, the first height H1 is a height at which at least a part of the rotor core 15 (a part of the lower side in the present embodiment) is immersed in the oil in the first reservoir 70 (see FIG. 5), the second height H2 is lower than the lowermost portion of the rotor core 15 of the first rotating electrical machine 10. Thereby, in the vehicle running state, it is possible to prevent the rotor core 15 from being immersed in the oil in the first reservoir 70 and to reduce the oil stirring loss due to the rotation of the rotor core 15. Further, according to the decrease in the oil level of the first reservoir 70, it is possible to reduce oil agitation loss due to the rotation of the differential gear mechanism 30 (differential input gear 31 and the like) while the vehicle is traveling.

  In the present embodiment, the second height H <b> 2 is lower than the lowermost portion of the inner peripheral surface 12 a of the stator core 12. That is, in the present embodiment, the first height H1 is higher than the lowermost portion of the inner peripheral surface 12a of the stator core 12 (see FIG. 5), whereas the second height H2 is the stator core 12. It becomes the height below the lowest part in the inner peripheral surface 12a. This makes it possible to suppress the shear loss of oil due to the rotation of the rotor 14 by setting the oil level of the first reservoir 70 to be low enough to prevent oil from entering the air gap in the vehicle running state. It has become. As shown in FIG. 6, in the present embodiment, the second height H2 is a height at which a part of the coil end portion 13 is immersed in the oil in the first storage portion 70. It is also possible to cool the stator 11 with the oil in the reservoir 70.

  The second height H2 can vary depending on the operating state of the second hydraulic pump 52, as with the first height H1. Further, the second height H2 can also change depending on the vehicle speed. For example, the second height H2 can be the height of the oil level of the first reservoir 70 when the vehicle is running and the second hydraulic pump 52 is not operating. Note that the second height H2 may be the height of the oil level of the first reservoir 70 when the vehicle is running and the second hydraulic pump 52 is operating. The “vehicle running state” here can be a state where the vehicle speed is equal to or higher than a predetermined speed threshold. This speed threshold is, for example, a speed range in which the amount of oil stored in the second reservoir 80 is equal to the storable capacity of the second reservoir 80, that is, the oil overflows from the opening above the second reservoir 80. It can be set as the speed contained in the speed range used as a state. For example, the speed threshold can be set to a speed included in the range of 15 km / h to 30 km / h.

  As described above, in the present embodiment, the discharge port 51 a of the first hydraulic pump 51 communicates with the supply unit 96 that supplies oil to the second storage unit 80. As shown in FIG. 6, in the present embodiment, the discharge port 51 a of the first hydraulic pump 51 further passes through the second reservoir 80 to the cooling oil passage 93 for cooling the first rotating electrical machine 10. It communicates without any problems. As will be described below, the discharge port 51 a of the first hydraulic pump 51 is connected to the cooling oil passage 93 by the first oil passage 91. Further, in the present embodiment, the discharge port 51 a of the first hydraulic pump 51 further communicates with the bearing B disposed inside the case 40 without passing through the second reservoir 80. As will be described below, the discharge port 51a of the first hydraulic pump 51 is connected to an oil supply portion (a second oil passage hole 62, which will be described later) by a first oil passage 91 with respect to a bearing B arranged inside the case 40. The third oil passage hole 63 and the fourth oil passage hole 64) are connected. The bearings B disposed inside the case 40 include the first bearing B1, the second bearing B2, the third bearing B3, the fourth bearing B4, the fifth bearing B5, and the sixth bearing B6 described above. The discharge port 51a of one hydraulic pump 51 communicates with at least one of these six bearings B without the second reservoir 80.

  As shown in FIG. 6, in the present embodiment, the vehicle drive device 1 includes a first oil passage 91 and a second oil passage 92. The first oil passage 91 is an oil passage that supplies oil discharged from the first hydraulic pump 51 to the rotor 14 as cooling oil and supplies it to the power transmission mechanism 3 as lubricating oil. The second oil passage 92 is an oil passage that supplies oil discharged from the second hydraulic pump 52 to the stator 11 as cooling oil. By providing the first oil passage 91 and the second oil passage 92 as described above, both the rotor 14 and the stator 11 can be appropriately cooled regardless of the vehicle speed.

  Supplementally, since the rotor 14 rotates at a rotational speed corresponding to the vehicle speed, the amount of heat generated by the rotor 14 due to iron loss increases as the frequency of the alternating magnetic field increases (that is, as the vehicle speed increases). In the present embodiment, permanent magnets are embedded in the rotor core 15. As the vehicle speed increases, hysteresis loss and eddy current loss, that is, iron loss increases, and the permanent magnets easily generate heat. In this regard, by providing the first oil passage 91 in the vehicle drive device 1, the oil discharged from the first hydraulic pump 51 whose discharge oil amount increases as the vehicle speed increases, and the heat generation amount increases as the vehicle speed increases. It can be supplied as cooling oil to the rotor 14 which becomes larger. That is, when the amount of cooling oil supplied to the rotor 14 is too small, the rotor 14 cannot be cooled appropriately, and when the amount of cooling oil supplied to the rotor 14 is excessive. The oil drag loss may increase unnecessarily. However, by configuring the rotor 14 to be cooled by the oil discharged from the first hydraulic pump 51, the amount of cooling oil corresponding to the amount of heat generated by the rotor 14 is reduced. Can be supplied to the rotor 14 to cool the rotor 14 appropriately. As shown in FIGS. 1 and 3, the first hydraulic pump 51 is provided with a relief valve 55, and the vehicle speed is high and the amount of oil discharged from the first hydraulic pump 51 becomes excessive. In other words, when the hydraulic pressure becomes abnormally high due to, for example, a part of the oil discharged from the first hydraulic pump 51 is discharged from the relief valve 55 and returned to the first reservoir 70. . In this way, by limiting the amount of oil supplied from the first hydraulic pump 51 to the first oil passage 91 to a predetermined value or less, it is possible to optimize the drag loss of oil. Since the oil discharged from the first hydraulic pump 51 is also supplied to the power transmission mechanism 3 as lubricating oil through the first oil passage 91, each part of the power transmission mechanism 3 can be appropriately lubricated while the vehicle is traveling. .

  In the present embodiment, since the stator 11 is an armature around which a coil is wound, the amount of heat generated by the stator 11 does not depend directly on the vehicle speed, and increases as the current flowing through the coil increases. . In this regard, by providing the second oil passage 92 in the vehicle drive device 1, the oil discharged by the second hydraulic pump 52 that can adjust the amount of discharged oil regardless of the vehicle speed is supplied to the stator 11 as cooling oil. can do. Therefore, it is possible to cool the stator 11 appropriately by supplying the stator 11 with an amount of cooling oil corresponding to the amount of heat generated by the stator 11. For example, when the first rotating electrical machine 10 outputs a high torque when the vehicle speed is low, such as when traveling on an uphill, the amount of heat generated by the stator 11 tends to increase, but the amount of oil discharged depends on the vehicle speed. The stator 11 can be appropriately cooled by supplying oil to the stator 11 from the second hydraulic pump 52 that can adjust the discharge oil amount regardless of the vehicle speed instead of the first hydraulic pump 51. Note that when the vehicle speed is low in this manner, the amount of heat generated by the rotor 14 is small, and if a large amount of cooling oil is supplied to the rotor 14, there is a possibility that the dragging loss of the oil becomes unnecessarily large. In the vehicle drive device 1, since the cooling oil is supplied to the rotor 14 from the first hydraulic pump 51, such a problem can be avoided. Since it is not necessary for the second hydraulic pump 52 to discharge the oil for cooling the rotor 14, the maximum hydraulic oil amount required for the second hydraulic pump 52 is reduced by a corresponding amount, and the second hydraulic pump 52 can be downsized. There is also an advantage that can be achieved. In the present embodiment, as shown in FIG. 6, the second oil passage 92 is provided with an oil cooler 7 (heat exchanger) for cooling the oil, and the oil cooled by the oil cooler 7 is supplied to the stator 11. Supplied.

  As shown in FIG. 2, in the present embodiment, the cooling oil passage 93 is configured to cool the rotor core 15 from the inside in the radial direction R. That is, in the present embodiment, the first oil passage 91 communicates with the cooling oil passage 93 that cools the rotor core 15 from the inside in the radial direction R. Specifically, the rotor shaft 16 is formed in a cylindrical shape extending in the axial direction L, and a cooling oil passage 93 is formed inside the rotor shaft 16. The cooling oil passage 93 is formed to extend in the axial direction L. Since the rotor core 15 is fixed to the outer peripheral surface of the rotor shaft 16, the rotor core 15 is cooled from the inner side in the radial direction R by heat exchange between the oil flowing through the cooling oil passage 93 and the rotor shaft 16.

  In order to intensively cool the central portion of the rotor core 15 that tends to accumulate heat, it is possible to supply relatively low temperature oil to a position in the cooling oil passage 93 that can exchange heat with the central portion in the axial direction L of the rotor core 15. Is desirable. In view of this point, in the present embodiment, by using the oil passage forming member 60 disposed on the inner side in the radial direction R than the rotor shaft 16, cooling capable of heat exchange with the central portion in the axial direction L of the rotor core 15. A relatively low temperature oil can be supplied to a position in the oil passage 93. Specifically, as shown in FIGS. 1 to 3, the oil passage forming member 60 is formed in a cylindrical shape having a smaller diameter than the rotor shaft 16 and extending in the axial direction L. In the present embodiment, the oil passage forming member 60 is disposed coaxially with the rotor shaft 16. A cooling oil passage 93 is formed between the outer peripheral surface of the oil passage forming member 60 and the inner peripheral surface of the rotor shaft 16. An internal oil passage 91 b is formed in a space surrounded by the inner peripheral surface of the oil passage forming member 60. The internal oil passage 91b is formed to extend in the axial direction L. The internal oil passage 91 b is an oil passage included in the first oil passage 91, and is an oil passage connecting the upstream portion of the first oil passage 91 and the cooling oil passage 93. In the present embodiment, the intermediate shaft 8 formed in a cylindrical shape extending in the axial direction L on the first axial side L1 from the rotor shaft 16 is coaxial with the rotor shaft 16 and rotates integrally with the rotor shaft 16. Are arranged to be. The oil passage forming member 60 is formed to have a smaller diameter than the intermediate shaft 8, and the portion of the oil passage forming member 60 on the first axial side L <b> 1 is disposed on the inner side in the radial direction R from the intermediate shaft 8. ing.

  In the present embodiment, the end portion on the first axial side L1 of the oil passage forming member 60 is held by the first wall portion 41, and the end portion on the second axial side L2 of the oil passage forming member 60 is the second wall portion. 42. And in this embodiment, as shown in FIG. 3, the connection part 91c of the discharge oil path 91a from the 1st hydraulic pump 51 in the 1st oil path 91 and the internal oil path 91b is formed in the 1st wall part 41. As shown in FIG. Has been. That is, in the present embodiment, the connection portion 91 c is formed on the first wall portion 41 or the second wall portion 42, specifically, formed on the first wall portion 41. If the wall part in which the connection part 91c of the 1st wall part 41 and the 2nd wall part 42 is formed is made into the "target wall part", in this embodiment, the 1st wall part 41 is a target wall part. Here, the discharge oil passage 91 a is an oil passage whose upstream end is connected to the discharge port 51 a of the first hydraulic pump 51. The oil discharged from the first hydraulic pump 51 flows through the discharge oil passage 91a and the connection portion 91c, and then flows into the internal oil passage 91b. And the oil which flowed into the internal oil path 91b distribute | circulates the internal oil path 91b toward the axial direction 2nd side L2.

  As shown in FIG. 2, the oil passage forming member 60 includes a first oil passage hole 61 that allows the internal oil passage 91 b and the cooling oil passage 93 to communicate with each other. The first oil passage hole 61 is formed so as to penetrate the oil passage forming member 60 from the inner side in the radial direction R to the outer side. In the present embodiment, the first oil passage hole 61 is formed so as to penetrate the oil passage forming member 60 in parallel to the radial direction R. Part of the oil flowing through the internal oil passage 91 b flows through the first oil passage hole 61 toward the outside in the radial direction R and flows into the cooling oil passage 93. In the present embodiment, the plurality of first oil passage holes 61 are formed at different positions in the circumferential direction (the circumferential direction of the first rotating electrical machine 10) at the same position in the axial direction L.

  The oil that has flowed into the cooling oil passage 93 from the internal oil passage 91 b flows in the axial direction L through the cooling oil passage 93 in a state of being in close contact with the inner peripheral surface of the rotor shaft 16 due to the centrifugal force accompanying the rotation of the rotor shaft 16. In the present embodiment, the opening on the outer side in the radial direction R of the first oil passage hole 61 is arranged in the arrangement region of the rotor core 15 in the axial direction L. Specifically, the opening on the outer side in the radial direction R of the first oil passage hole 61 is disposed in the central portion of the rotor core 15 in the axial direction L. Therefore, oil having a temperature similar to that of the oil in the internal oil passage 91b can be supplied to a position in the cooling oil passage 93 that can exchange heat with the central portion of the rotor core 15 in the axial direction L. It is possible to intensively cool the central portion in the axial direction L of the rotor core 15 that tends to be trapped.

  In the present embodiment, as shown in FIG. 2, the discharge oil passage for discharging the oil in the cooling oil passage 93 to the space outside the rotor shaft 16 on both sides in the axial direction L with respect to the first oil passage hole 61. 16a is formed. The drain oil passage 16a is formed so as to penetrate the rotor shaft 16 from the inside in the radial direction R to the outside. Therefore, the oil flowing into the cooling oil passage 93 from the internal oil passage 91b flows from the central portion of the rotor core 15 in the axial direction L toward both sides in the axial direction L, as shown by the broken line arrows in FIG. After that, due to the centrifugal force accompanying the rotation of the rotor shaft 16, the oil is discharged from each of the discharge oil passages 16 a into a space outside the rotor shaft 16 in the radial direction R. In the present embodiment, the oil discharged to the outside in the radial direction R from the discharged oil passage 16a is supplied to the coil end portion 13 by centrifugal force. That is, it is possible to cool the coil end portions 13 on both sides in the axial direction L using the oil after cooling the rotor core 15.

  As described above, in the present embodiment, the discharge port 51a of the first hydraulic pump 51 passes through the discharge oil passage 91a, the connection portion 91c, and the internal oil passage 91b, that is, through the first oil passage 91. And communicated with the cooling oil passage 93. As shown in FIGS. 2 and 3, the oil passage forming member 60 has a plurality of oil passage holes (through the oil passage forming member 60 from the inner side to the outer side in the radial direction R) in addition to the first oil passage hole 61 ( A second oil passage hole 62, a third oil passage hole 63, and a fourth oil passage hole 64) are formed. Therefore, a part of the oil in the internal oil passage 91b is supplied as the lubricating oil to the third bearing B3 through the second oil passage hole 62. Part of the oil in the internal oil passage 91b is supplied as lubricating oil to the first bearing B1 and the fourth bearing B4 through the third oil passage hole 63. The intermediate shaft 8 is formed with a communication oil passage 8a penetrating the intermediate shaft 8 from the inside in the radial direction R to the outside, and the oil that has flowed out from the third oil passage hole 63 to the outside in the radial direction R It is supplied to the first bearing B1 and the fourth bearing B4 through the spline engaging portion between the rotor shaft 16 and the intermediate shaft 8 and the communication oil passage 8a. Part of the oil in the internal oil passage 91b is supplied as lubricating oil to the second bearing B2 through the fourth oil passage hole 64. As described above, the discharge port 51a of the first hydraulic pump 51 passes through the discharge oil passage 91a, the connection portion 91c, and the internal oil passage 91b, that is, through the first oil passage 91, to the inside of the case 40. Is communicated with the bearing B disposed in the. As described above, the first oil passage 91 supplies the oil discharged from the first hydraulic pump 51 to the rotor 14 as cooling oil and also uses the power transmission mechanism 3 as the lubricating oil (here, the bearing B provided in the power transmission mechanism 3). It is an oil passage to supply to.

  In the present embodiment, the first oil passage 91 is configured to supply oil discharged from the first hydraulic pump 51 to the counter gear mechanism 20 as lubricating oil. That is, the power transmission mechanism 3 to which the lubricant is supplied by the first oil passage 91 includes the counter gear mechanism 20 in addition to the bearing B. Specifically, as shown in FIG. 3, the first oil passage 91 is an oil passage (this embodiment) that connects the discharge port 51 a of the first hydraulic pump 51 and the hollow portion of the connecting shaft 23 of the counter gear mechanism 20. In the embodiment, an in-shaft oil passage 91d) formed inside the pump drive shaft 53 is provided. The oil that has flowed into the hollow portion of the connecting shaft 23 from the in-shaft oil passage 91d is supplied as, for example, lubricating oil to the first gear 21, the second gear 22, the fifth bearing B5, or the sixth bearing B6.

  As shown in FIG. 3, in this embodiment, the connection part 91c of the 1st oil path 91 is formed in the inside of the 1st wall part 41 (target wall part). Specifically, the first wall portion 41 includes a first insertion hole 44 into which an end portion on the first axial side L1 of the oil passage forming member 60 is inserted. The connection portion 91 c is provided so as to open to the inner peripheral surface of the first insertion hole 44 on the first axial side L <b> 1 (the back side of the first insertion hole 44) from the oil passage forming member 60. Therefore, the oil supplied from the discharge oil passage 91a to the connection portion 91c flows into the first insertion hole 44 and then enters the shaft from the opening at the end on the first axial side L1 of the oil passage forming member 60. It flows into the oil passage 91d. Thus, in the present embodiment, the end of the oil passage forming member 60 on the first axial side L1 is inserted into the first insertion hole 44 formed in the first wall 41 from the second axial side L2. In this state, the first wall 41 is held. Similarly, in the present embodiment, as shown in FIG. 2, the end portion of the oil passage forming member 60 on the second axial side L2 is axially inserted into the second insertion hole 47 formed in the second wall portion 42. In the state inserted from the one side L1, it is hold | maintained at the 2nd wall part 42. FIG. In the example illustrated in FIG. 2, a second insertion hole 47 is formed in a member that is fixed to the second wall portion 42 with a fastening member.

  As shown in FIG. 3, in the present embodiment, in order to appropriately secure the amount of oil flowing from the discharge oil passage 91a to the internal oil passage 91b, the oil passage with respect to the first wall portion 41 (target wall portion). A step portion 6 is provided for restricting the formation member 60 from moving to the first axial side L1 (the back side of the first insertion hole 44). The step portion 6 is formed on at least one of the outer peripheral surface of the oil passage forming member 60 and the inner peripheral surface of the first insertion hole 44, and is formed on the outer peripheral surface of the oil passage forming member 60 in this embodiment. Specifically, a protruding portion that is formed on the outer peripheral surface of the oil passage forming member 60 and protrudes outward in the radial direction R as compared with the portion on the first axial side L1 is the stepped portion 6. A surface of the step portion 6 that faces the first axial direction L1 (in this embodiment, a surface in which the normal direction is inclined with respect to the axial direction L) faces the second axial direction L2 of the first wall portion 41. , The movement of the oil passage forming member 60 to the first axial direction L1 is limited. In other words, by providing such a stepped portion 6, even if an external force on the side toward the first wall portion 41 acts on the oil passage forming member 60, the first axial direction of the oil passage forming member 60 is provided. Movement to the side L1 can be restricted. As a result, it is possible to avoid the portion of the connecting portion 91c that opens to the inner peripheral surface of the first insertion hole 44 from being blocked by the end portion of the oil passage forming member 60 on the first axial side L1. ing.

  As shown in FIGS. 2 and 6, in the present embodiment, the stator 11 is cooled by supplying oil discharged from the second hydraulic pump 52 to the stator 11 from above. Specifically, an oil supply portion 65 that supplies oil supplied from the second oil passage 92 to the stator 11 is provided between the second wall portion 42 and the third wall portion 43 in the axial direction L. . The oil supply unit 65 is disposed above the stator 11. A connection oil passage 95 that connects the second oil passage 92 and the oil supply portion 65 is formed in the second wall portion 42. Therefore, the oil discharged from the second hydraulic pump 52 flows through the second oil passage 92 and the connection oil passage 95 and then flows into the oil supply unit 65. Then, the stator 11 is cooled by the oil supplied to the stator 11 from the oil supply unit 65.

  In the present embodiment, the oil supply unit 65 is formed in a cylindrical shape extending in the axial direction L, and an oil passage extending in the axial direction L is formed inside the oil supply unit 65. And the oil supply part 65 is provided with the oil supply hole (66a, 66b) formed so that the oil supply part 65 might be penetrated from the inner side of radial direction R to the outer side. The oil supply holes (66a, 66b) are provided at positions overlapping the stator 11 when viewed in the vertical direction Z. The oil supplied to the oil supply unit 65 is subjected to the action of gravity and drops from the oil supply holes (66a, 66b) onto the stator 11, whereby the stator 11 is cooled. In the present embodiment, the oil supply unit 65 corresponds to each of the coil end portions 13 on both sides in the axial direction L with the first oil supply holes 66a arranged at positions overlapping with the coil end portions 13 when viewed in the vertical direction Z. In addition, a second oil supply hole 66b disposed at a position overlapping the stator core 12 when viewed in the vertical direction Z is provided in the central portion of the stator core 12 in the axial direction L.

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

(1) In the above embodiment, the configuration in which the second storage unit 80 is partitioned into two chambers (81, 82) has been described as an example. However, the configuration is not limited to such a configuration, and the second storage unit 80 may have only one chamber, or the second storage unit 80 may be partitioned into three or more chambers.

(2) In the above embodiment, the configuration in which the discharge port 51a of the first hydraulic pump 51 communicates with the supply unit 96 that supplies oil to the second storage unit 80 has been described as an example. However, the present invention is not limited to such a configuration, and the discharge port 51 a of the first hydraulic pump 51 may be configured not to communicate with the supply unit 96.

(3) In the above embodiment, the discharge port 51 a of the first hydraulic pump 51 is provided both on the bearing B disposed inside the case 40 and the cooling oil passage 93 for cooling the first rotating electrical machine 10. The configuration that communicates without going through the second reservoir 80 has been described as an example. However, without being limited to such a configuration, the discharge port 51 a of the first hydraulic pump 51 communicates with only one of the bearing B and the cooling oil passage 93 without passing through the second reservoir 80. The discharge port 51 a of the first hydraulic pump 51 can be configured to be able to communicate only with the bearing B and the cooling oil passage 93 only via the second storage portion 80. .

(4) In the above embodiment, the configuration in which the discharge port 52a of the second hydraulic pump 52 does not communicate with the supply unit 96 has been described as an example. However, the present invention is not limited to such a configuration, and the discharge port 52 a of the second hydraulic pump 52 may be configured to communicate with the supply unit 96.

(5) In the above embodiment, the configuration in which the oil passage forming member 60 is held by the case 40 has been described as an example. That is, the configuration in which the oil passage forming member 60 is a non-rotating member has been described as an example. However, without being limited to such a configuration, a cylindrical member that rotates in conjunction with the rotating member of the power transmission mechanism 3 can also be used as the oil passage forming member 60. For example, the pump drive shaft 53 of the first hydraulic pump 51 is arranged coaxially with the first rotating electrical machine 10, and the oil passage forming member 60 is connected to the pump drive shaft 53, or one of the pump drive shafts 53. The part may be configured to function as the oil passage forming member 60.

(6) In the above embodiment, the oil passage forming member 60 is disposed on the inner side in the radial direction R from the rotor shaft 16, and the cooling oil passage 93 is changed from the internal oil passage 91 b formed inside the oil passage forming member 60. The configuration in which oil is supplied, that is, the configuration in which oil is supplied from the inside in the radial direction R to the cooling oil passage 93 has been described as an example. However, without being limited to such a configuration, the oil supply portion for the cooling oil passage 93 is disposed on the first axial side L1 or the second axial side L2 with respect to the cooling oil passage 93, and the cooling oil passage 93 is provided. On the other hand, the oil may be supplied from the outside in the axial direction L.

(7) In the above embodiment, the configuration in which the cooling oil passage 93 is formed inside the rotor shaft 16 has been described as an example. However, without being limited to such a configuration, the cooling oil passage 93 includes an axial oil passage that penetrates the portion between the inner peripheral surface and the outer peripheral surface 15a of the rotor core 15 in the axial direction L, The cooling oil passage 93 may be configured to include both such an axial oil passage and an oil passage formed inside the rotor shaft 16.

(8) In the above embodiment, the step portion 6 for restricting the oil passage forming member 60 from moving to the first axial direction L1 relative to the first wall portion 41 is the outer periphery of the oil passage forming member 60. The structure formed only on the outer peripheral surface of the oil passage forming member 60 among the surface and the inner peripheral surface of the first insertion hole 44 has been described as an example. However, without being limited to such a configuration, the stepped portion 6 is formed only on the inner peripheral surface of the first insertion hole 44, or the outer peripheral surface of the oil passage forming member 60 and the first insertion hole 44. It can also be set as the structure formed in both inner peripheral surfaces. When the step portion 6 is formed on the inner peripheral surface of the first insertion hole 44, the inner side in the radial direction R is formed on the inner peripheral surface of the first insertion hole 44 compared to the portion on the second axial side L <b> 2. The protruding portion that protrudes can be the stepped portion 6.

(9) In the above embodiment, the connection portion 91c of the first oil passage 91 is formed in the first wall portion 41, and the connection oil passage 95 that connects the second oil passage 92 and the oil supply portion 65 is the second wall. The configuration formed in the portion 42 has been described as an example. However, the configuration is not limited to such a configuration, and the connection portion 91 c is formed in a portion other than the first wall portion 41 in the case 40, or the connection oil passage 95 is other than the second wall portion 42 in the case 40. It can also be set as the structure formed in a part (for example, 3rd wall part 43). For example, the connection portion 91c can be configured to be formed on the second wall portion 42 (that is, a configuration in which the second wall portion 42 is the target wall portion). In this case, it is preferable to provide the connection portion 91c so as to open to the inner peripheral surface of the second insertion hole 47 on the second axial side L2 (the back side of the second insertion hole 47) from the oil passage forming member 60. is there. In this case, the step portion 6 is provided so as to restrict the oil passage forming member 60 from moving to the second axial side L2 (the back side of the second insertion hole 47) with respect to the second wall portion 42. It is preferable. Thus, in the configuration in which the connection portion 91 c is formed on the second wall portion 42, the first hydraulic pump 51 may be provided on the second wall portion 42, unlike the above embodiment.

(10) In the above embodiment, the configuration in which the rotation axis A of the differential gear mechanism 30 is disposed at a height between the uppermost part and the lowermost part of the rotor core 15 of the first rotating electrical machine 10 has been described as an example. . However, without being limited to such a configuration, the configuration in which the rotational axis A of the differential gear mechanism 30 is disposed above the uppermost portion of the rotor core 15, or the rotational axis A of the differential gear mechanism 30 is It can also be set as the structure arrange | positioned below the lowest part of the rotor core 15. FIG.

(11) In the above embodiment, the configuration in which the power transmission mechanism 3 includes the counter gear mechanism 20 has been described as an example. However, the configuration is not limited to such a configuration, and the power transmission mechanism 3 may be configured not to include the counter gear mechanism 20. For example, the output gear 17 can be configured to mesh with the differential input gear 31. Further, in a configuration in which the power transmission mechanism 3 includes the counter gear mechanism 20 or a configuration in which the power transmission mechanism 3 does not include the counter gear mechanism 20, the power transmission mechanism 3 has a power between the output gear 17 and the differential input gear 31. It can also be set as the structure provided with other mechanisms or apparatuses, such as a planetary gear mechanism, in a transmission path.

(12) In the above embodiment, the configuration in which the second reservoir 80 is formed inside the case 40 has been described as an example. However, the configuration is not limited to such a configuration, and the second storage portion 80 may not be formed inside the case 40.

(13) It should be noted that the configuration disclosed in each of the above-described embodiments may be applied in combination with the configuration disclosed in the other embodiment unless there is a contradiction (between the embodiments described as other embodiments. (Including combinations) is also possible. Regarding other configurations, the embodiments disclosed herein are merely examples in all respects. Accordingly, various modifications can be made as appropriate without departing from the spirit of the present disclosure.

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

  A first rotating electrical machine (10) having a rotor (14) and a stator (11), and a power transmission mechanism (3) for transmitting a rotational driving force between the first rotating electrical machine (10) and a wheel (W). The first hydraulic pump (51) driven by the first rotary electric machine (10) and the second hydraulic pump (52) driven by a second rotary electric machine (2) different from the first rotary electric machine (10). ), Wherein the second rotating electrical machine (2) is provided separately from the transmission path of the rotational driving force by the power transmission mechanism (3), A first oil passage (91) for supplying oil discharged from one hydraulic pump (51) as cooling oil to the rotor (14) and as lubricating oil to the power transmission mechanism (3); and the second hydraulic pump The oil discharged by (52) is used as cooling oil for the stator (11 Comprising second oil passage (92) and supplying, to the.

Since the rotor (14) of the first rotating electrical machine (10) provided as a driving force source for the wheels (W) rotates at a rotational speed corresponding to the vehicle speed, the amount of heat generated by the rotor (14) due to iron loss is an alternating magnetic field. Increases as the frequency increases (that is, as the vehicle speed increases). In this regard, according to the above configuration, the first hydraulic pump (51) driven by the first rotating electrical machine (10) (that is, the first hydraulic pump (51) in which the discharge oil amount increases as the vehicle speed increases). ) Can be supplied to the rotor (14) as cooling oil, so that the amount of cooling oil increases as the vehicle speed increases with respect to the rotor (14) whose calorific value increases as the vehicle speed increases. Can be supplied. That is, when the amount of cooling oil supplied to the rotor (14) is too small, the rotor (14) cannot be cooled appropriately, and the cooling oil supplied to the rotor (14) If the amount is excessive, the dragging loss of oil may become unnecessarily large. However, according to the above configuration, the amount of cooling oil corresponding to the amount of heat generated by the rotor (14) is supplied to the rotor (14). Supplying it makes it possible to cool the rotor (14) appropriately. The oil discharged from the first hydraulic pump (51) whose amount of discharged oil increases as the vehicle speed increases is also supplied to the power transmission mechanism (3) as lubricating oil. Each part of (3) can also be lubricated appropriately.
On the other hand, when the stator (11) of the first rotating electrical machine (10) provided as a driving force source for the wheels is an armature around which a coil is wound, the amount of heat generated by the stator (11) is directly related to the vehicle speed. The current increases as the current flowing in the coil increases. In this regard, according to the configuration described above, the second hydraulic pump (52) (52) driven by the second rotating electrical machine (2) provided separately from the transmission path of the rotational driving force by the power transmission mechanism (3) ( That is, the oil discharged by the second hydraulic pump (52) whose discharge oil amount can be adjusted regardless of the vehicle speed can be supplied to the stator (11) as cooling oil. Therefore, it becomes possible to cool the stator (11) appropriately by supplying the stator (11) with an amount of cooling oil corresponding to the amount of heat generated by the stator (11).
As described above, according to the above configuration, the rotor (14) of the first rotating electrical machine (10) is cooled by the oil discharged from the first hydraulic pump (51) and discharged from the second hydraulic pump (52). By adopting a configuration in which the stator (11) of the first rotating electrical machine (10) is cooled by oil, both the rotor (14) and the stator (11) can be appropriately cooled regardless of the vehicle speed. . Further, the maximum discharge oil amount required for the second hydraulic pump (52) is larger than that in the case where the rotor (14) of the first rotating electrical machine (10) is cooled by the oil discharged by the second hydraulic pump (52). There is also an advantage that the size of the second hydraulic pump (52) can be reduced with a small amount.

  Here, the rotor (14) is located on the inner side in the radial direction (R) than the stator core (12) of the stator (11), and overlaps with the stator core (12) when viewed in the radial direction (R). The first oil passage (91) communicates with a cooling oil passage (93) that cools the rotor core (15) from the inside in the radial direction (R). It is preferable.

According to this configuration, the oil in the cooling oil passage (93) after cooling the rotor core (15) is discharged from the cooling oil passage (93) to the outside in the radial direction (R). Using the centrifugal force accompanying the rotation of the rotor (14), the oil after cooling the rotor core (15) can be discharged from the cooling oil passage (93). Therefore, it is possible to improve the cooling efficiency of the rotor core (15) by smoothing the oil flow in the cooling oil passage (93).
Note that the amount of oil supplied from the first oil passage (91) to the cooling oil passage (93) increases as the vehicle speed increases, but the centrifugal force increases as the rotational speed of the rotor (14) increases. (Ie as the vehicle speed increases). Therefore, even when the amount of oil supplied to the cooling oil passage (93) is large, it is possible to ensure smooth circulation of the oil in the cooling oil passage (93) by the centrifugal force. Further, when the amount of oil supplied to the cooling oil passage (93) is large, drag loss due to oil existing around the rotor core (15) is likely to occur, but the oil is supplied to the cooling oil passage (93). When the amount of oil is large, the centrifugal force is also increased, so that excessive oil can be prevented from staying around the rotor core (15).

  In the configuration in which the first oil passage (91) communicates with the cooling oil passage (93) as described above, the case includes a case (40) for housing the first rotating electrical machine (10), and the rotor core (15 ) Is fixed to the outer peripheral surface of the rotor shaft (16) supported rotatably with respect to the case (40), and the rotor shaft (16) is formed in a cylindrical shape extending in the axial direction (L), An oil passage forming member (60) having a smaller diameter than the rotor shaft (16) and extending in the axial direction (L) inside the radial direction (R) from the rotor shaft (16). ) Is disposed, and the cooling oil passage (93) is formed between the outer peripheral surface of the oil passage forming member (60) and the inner peripheral surface of the rotor shaft (16), and the oil passage forming member (60 ), An internal oil passage (91b) is formed in the space surrounded by the inner peripheral surface, and the oil passage The component member (60) is formed so as to penetrate the oil passage forming member (60) from the inside in the radial direction (R) to the outside, and the internal oil passage (91b), the cooling oil passage (93), A communication hole (61) that communicates with each other, and an opening portion on the outer side in the radial direction (R) of the communication hole (61) is disposed in an arrangement region of the rotor core (15) in the axial direction (L). The case (40) includes a first wall (41) disposed on an axial first side (L1), which is one side in the axial direction (L) relative to the rotor core (15), and the rotor core ( 15), and a second wall (42) disposed on the second axial side (L2) opposite to the first axial side (L1), and the oil passage forming member (60). ) Of the first axial side (L1) is held by the first wall (41), and An end of the path forming member (60) on the second axial side (L2) is held by the second wall (42), and the first hydraulic pump (51) in the first oil path (91) It is preferable that the connection portion (91c) between the discharge oil passage (91a) and the internal oil passage (91b) is formed in the first wall portion (41) or the second wall portion (42). .

According to this configuration, the rotor core (15) fixed to the outer peripheral surface of the rotor shaft (16) is radially (by the heat exchange between the oil flowing through the cooling oil passage (93) and the rotor shaft (16) ( R) can be cooled from the inside. At this time, the internal oil passage (91b) through which the oil supplied to the cooling oil passage (93) flows is the oil passage forming member (60) disposed inside the radial direction (R) with respect to the rotor shaft (16). Since it is formed inside, the oil passage forming member (60) is provided with a communication hole (61), and the oil in the internal oil passage (91b) can be supplied even while the rotor (14) is rotating. The structure which can be appropriately supplied to a cooling oil path (93) is realizable. Moreover, the opening part of the radial direction (R) outer side of this communicating hole (61) is arrange | positioned in the arrangement | positioning area | region of the rotor core (15) in an axial direction (L). Therefore, oil having the same temperature as the oil in the internal oil passage (91b) is supplied to the position in the cooling oil passage (93) that can exchange heat with the central portion in the axial direction (L) of the rotor core (15). As a result, the central portion of the rotor core (15) where heat tends to be trapped can be intensively cooled.
Moreover, according to said structure, the axis | shaft of the 1st wall part (41) by which the edge part of the axial direction 1st side (L1) of an oil path formation member (60) is hold | maintained, or an oil path formation member (60) A discharge oil passage (91a) and an internal oil passage from the first hydraulic pump (51) in the first oil passage (91) to the second wall portion (42) where the end portion on the second direction side (L2) is held. A connecting portion (91c) with (91b) is formed. Therefore, it becomes possible to ensure the oil tightness in the connection portion (91c) using the first wall portion (41) or the second wall portion (42), and the configuration of the connection portion (91c) is simplified. be able to.

  As described above, the connection portion (91c) between the discharge oil passage (91a) and the internal oil passage (91b) in the first oil passage (91) is the first wall portion (41) or the second wall portion. (42) WHEREIN: The wall part in which the said connection part (91c) of said 1st wall part (41) and said 2nd wall part (42) is formed is made into object wall part (41,42). ), The target wall (41, 42) includes an insertion hole (44, 47) into which an end in the axial direction (L) of the oil passage forming member (60) is inserted, and the connection portion ( 91c) is provided so as to open to the inner peripheral surface of the insertion hole (44, 47) on the deeper side of the insertion hole (44, 47) than the oil passage forming member (60), and the target wall portion The oil passage forming member (60) moves to the back side of the insertion hole (44, 47) with respect to (41, 42). It is preferable that the step portion (6) for restricting this is formed on at least one of the outer peripheral surface of the oil passage forming member (60) and the inner peripheral surface of the insertion hole (44, 47). is there.

  According to this structure, even if it is a case where the external force of the side which goes to an object wall part (41, 42) acts with respect to an oil path formation member (60), the insertion hole (44 of an oil path formation member (60)) , 47) to the back side is limited, and the portion opened to the inner peripheral surface of the insertion hole (44) in the connection portion (91c) is in the axial direction (L) of the oil passage forming member (60). It is possible to avoid being blocked by the end portion. Therefore, it is possible to appropriately secure the amount of oil flowing from the discharge oil passage (91a) to the internal oil passage (91b).

  The rotor (14) includes a rotor shaft (16) that is rotatably supported with respect to the case (40), and a case (40) that houses the first rotating electrical machine (10). A rotor core (15) fixed to the outer peripheral surface of the shaft (16), and the case (40) is closer to one side in the axial direction (L) of the rotor shaft (16) than the rotor core (15). A first wall portion (41) arranged on a certain first axial direction side (L1) and an axial second side (L1) opposite to the first axial side (L1) with respect to the rotor core (15) ( A second wall portion (42) arranged in L2) and a third wall portion (43) arranged between the first wall portion (41) and the rotor core (15) in the axial direction (L). And an output connected to the rotor shaft (16) of the first rotating electrical machine (10). Ya (17) is arranged between the first wall (41) and the third wall (43) in the axial direction (L), the rotor shaft (16) is the second wall (42) and the third wall (43) are rotatably supported with respect to the case (40), and the output gear (17) includes the first wall (41) and the third wall. (43) and an oil supply section (65) that is rotatably supported by the case (40) and supplies oil supplied from the second oil passage (92) to the stator (11). It is provided between the second wall part (42) and the third wall part (43) in the axial direction (L), and connects the second oil passage (92) and the oil supply part (65). It is preferable that the connection oil passage (95) is formed in the second wall portion (42).

  According to this structure, compared with the case where a connection oil path (95) is formed in a 1st wall part (41), the wall part in which a connection oil path (95) is formed, and an oil supply part (65) The distance can be reduced, and the configuration of the connection oil passage (95) can be simplified. Further, in terms of the distance between the wall portion where the connection oil passage (95) is formed and the oil supply portion (65), the connection oil passage (95) is not the second wall portion (42) but the third wall portion (43). However, the connecting oil passage (95) is not connected to the second wall portion (42) but to the third wall portion (43) dividing the space inside the case (40) in the axial direction (L). The advantage that the processing for forming the connection oil passage (95) is facilitated and that the arrangement position of the connection oil passage (95) is not easily restricted are formed.

  The vehicle drive device according to the present disclosure only needs to exhibit at least one of the effects described above.

1: vehicle drive device 2: second rotating electrical machine 3: power transmission mechanism 6: step 10: first rotating electrical machine 11: stator 12: stator core 14: rotor 15: rotor core 16: rotor shaft 17: output gear 40: case 41: 1st wall part (target wall part)
42: second wall 43: third wall 44: first insertion hole (insertion hole)
51: First hydraulic pump 52: Second hydraulic pump 60: Oil passage forming member 61: First oil passage hole (communication hole)
65: Oil supply portion 91: First oil passage 91a: Discharge oil passage 91b: Internal oil passage 91c: Connection portion 92: Second oil passage 93: Cooling oil passage 95: Connection oil passage 96: Supply portion 97: Storage oil passage 98: In-shaft oil passage L: Axial direction L1: Axial direction first side L2: Axial direction second side R: Radial direction W: Wheel

Claims (5)

A first rotating electrical machine having a rotor and a stator; a power transmission mechanism for transmitting rotational driving force between the first rotating electrical machine and wheels; a first hydraulic pump driven by the first rotating electrical machine; A second hydraulic pump driven by a second rotating electrical machine different from the one rotating electrical machine, wherein the second rotating electrical machine is provided separately from a rotational drive force transmission path by the power transmission mechanism A driving device comprising:
A first oil passage for supplying oil discharged from the first hydraulic pump to the rotor as cooling oil and supplying to the power transmission mechanism as lubricating oil;
And a second oil passage that supplies oil discharged from the second hydraulic pump as cooling oil to the stator. The rotor includes a rotor core that is disposed radially inward of the stator core of the stator and overlaps the stator core when viewed in the radial direction,
2. The vehicle drive device according to claim 1, wherein the first oil passage communicates with a cooling oil passage that cools the rotor core from the inside in the radial direction. A case for housing the first rotating electrical machine;
The rotor core is fixed to an outer peripheral surface of a rotor shaft that is rotatably supported with respect to the case,
The rotor shaft is formed in a cylindrical shape extending in the axial direction,
An oil passage forming member formed in a cylindrical shape having a smaller diameter than the rotor shaft and extending in the axial direction is disposed inside the radial direction from the rotor shaft,
The cooling oil passage is formed between the outer peripheral surface of the oil passage forming member and the inner peripheral surface of the rotor shaft,
An internal oil passage is formed in a space surrounded by the inner peripheral surface of the oil passage forming member,
The oil passage forming member includes a communication hole that is formed so as to penetrate the oil passage forming member from the inside in the radial direction to the outside and communicates the internal oil passage and the cooling oil passage.
The radially outer opening of the communication hole is disposed in an arrangement region of the rotor core in the axial direction,
The case includes a first wall portion disposed on an axial first side which is one axial side of the rotor core, and an axial first side which is opposite to the axial first side than the rotor core. A second wall portion disposed on two sides,
The end portion on the first axial direction side of the oil passage forming member is held by the first wall portion, and the end portion on the second axial direction side of the oil passage forming member is held on the second wall portion. And
The vehicle according to claim 2, wherein a connection portion between the discharge oil passage from the first hydraulic pump and the internal oil passage in the first oil passage is formed in the first wall portion or the second wall portion. Drive device. Of the first wall portion and the second wall portion, the wall portion where the connecting portion is formed is the target wall portion, and the target wall portion is inserted with the axial end of the oil passage forming member. With an insertion hole
The connecting portion is provided so as to open to the inner peripheral surface of the insertion hole on the deeper side of the insertion hole than the oil passage forming member,
A stepped portion for restricting the oil passage forming member from moving toward the back side of the insertion hole with respect to the target wall portion is formed between an outer peripheral surface of the oil passage forming member and an inner peripheral surface of the insertion hole. The vehicle drive device according to claim 3, wherein the vehicle drive device is formed on at least one side. A case for housing the first rotating electrical machine;
The rotor includes a rotor shaft that is rotatably supported with respect to the case, and a rotor core that is fixed to an outer peripheral surface of the rotor shaft,
The case is a first wall portion disposed on the first axial side which is one axial side of the rotor shaft with respect to the rotor core, and is opposite to the first axial side with respect to the rotor core. A second wall portion disposed on the second axial side, and a third wall portion disposed between the first wall portion and the rotor core in the axial direction,
An output gear coupled to the rotor shaft of the first rotating electrical machine is disposed between the first wall portion and the third wall portion in the axial direction,
The rotor shaft is rotatably supported with respect to the case by the second wall portion and the third wall portion,
The output gear is rotatably supported with respect to the case by the first wall portion and the third wall portion,
An oil supply portion for supplying oil supplied from the second oil passage to the stator is provided between the second wall portion and the third wall portion in the axial direction;
The vehicle drive device according to any one of claims 1 to 4, wherein a connection oil passage that connects the second oil passage and the oil supply portion is formed in the second wall portion.

Images