JP2014015188A - Drive device for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a drive device for a vehicle capable of suppressing increase of drag loss while appropriately cooling an engagement device in the start of the vehicle in an electric travel mode, etc.SOLUTION: A drive device for a vehicle includes: a first engagement device CL1; a rotary electric machine MG; and a second engagement device CL2 in order on a power transmission path connecting an internal combustion engine with wheels. A first inner cylindrical part 46 of the first engagement device CL1 is arranged outside in a radial direction than a second outer cylindrical part 72 of the second engagement device CL2. A second inner cylindrical part 66, the second outer cylindrical part 72 and a first outer cylindrical part 52 have: a first through hole 11; a second through hole 12; and a third through hole 13 in the radial direction, respectively. The first inner cylindrical part 46 has an opening end 48, and is arranged at a position where the opening end 48 overlaps with the third through hole 13 at a released state of the first engagement device CL1.

Description

  The present invention provides, in order from the input member side, a first engagement device, a rotating electrical machine, and a second engagement member in a power transmission path that connects an input member that is drivingly connected to an internal combustion engine and an output member that is drivingly connected to wheels. The present invention relates to a vehicle drive device including a combination device.

  As a vehicle drive device as described above, for example, one described in Japanese Patent Application Laid-Open No. 2010-196868 (Patent Document 1) is known. In the device of Patent Document 1, the first engagement device [first clutch CL1] and the second engagement device [second clutch CL2] are arranged in the axial direction radially inward of the stator of the rotating electrical machine [motor generator MG]. Is arranged in. The oil for cooling and the like passes through a common distribution path (circulation oil path 700), and the first engagement device having a relatively small heat generation amount and the second engagement unit having a relatively large heat generation amount. It is configured to circulate in series in the order of the combined device. Thereby, the flow rate of oil is reduced to improve fuel consumption, and the supply balance of oil to the two engagement devices is made constant to stabilize the cooling performance.

  By the way, for example, in a situation where a stopped vehicle starts with the torque of the rotating electrical machine, the oil pump may be driven using the torque of the rotating electrical machine to ensure a necessary hydraulic pressure. Under such circumstances, the first engagement device, which is generally released while the internal combustion engine is stopped, does not generate heat, whereas the second engagement device provided on the output member side of the rotating electrical machine slips. There is a case where heat is generated in the engaged state. In such a case, it is preferable to preferentially cool only the second engagement device that generates heat. However, in the device of Patent Document 1, oil is serially connected in the order of the first engagement device and the second engagement device. Since it circulates, oil will be supplied also to a 1st engagement apparatus (1st friction member). For this reason, in the apparatus of Patent Document 1, drag loss may increase due to a large amount of oil around the first friction member.

JP 2010-196868 A

  Therefore, it is desired to realize a vehicle drive device that can suppress an increase in drag loss while appropriately cooling the engagement device when the vehicle starts using the torque of the rotating electrical machine.

  In order from the input member side to the power transmission path connecting the input member drivingly connected to the internal combustion engine and the output member drivingly connected to the wheels according to the present invention, in order from the input member side, The vehicle drive device including the two engagement devices is characterized in that the first engagement device includes a first friction member including a first inner friction member and a first outer friction member, and the first inner friction member. A first inner cylindrical portion that is arranged radially inside and supports the first inner friction member, and a first outer portion that is arranged radially outside the first outer friction member and supports the first outer friction member. A cylindrical member and a pressing member that presses the first friction member in the axial direction, and the second engagement device includes a second friction member including a second inner friction member and a second outer friction member; The second inner friction member is disposed radially inside the second friction member and supports the second inner friction member A second inner cylindrical portion that is disposed radially outside the second outer friction member and supports the second outer friction member, and the first inner cylindrical portion. Is disposed radially outside the second outer cylindrical portion, and the second inner cylindrical portion penetrates in the radial direction at a position overlapping the second friction member in the axial direction when viewed in the radial direction. The second outer cylindrical portion has a second through hole penetrating in the radial direction at a position overlapping with the second friction member in the axial direction when viewed in the radial direction, The first outer cylindrical portion has a third through hole penetrating in the radial direction, and the first inner cylindrical portion is counter-pressing in a direction opposite to the pressing direction of the first friction member by the pressing member. An opening end portion that opens in the direction, and the opening end portion and the third through hole overlap in the axial direction when viewed in the radial direction. In that it is disposed.

In the present application, “drive connection” means a state in which two rotating elements are connected so as to be able to transmit a driving force (synonymous with torque). This concept includes a state in which the two rotating elements are connected so as to rotate integrally, and a state in which the driving force is transmitted through one or more transmission members. Such transmission members include various members (shafts, gear mechanisms, belts, etc.) that transmit rotation at the same speed or at different speeds, and engaging devices (frictions) that selectively transmit rotation and driving force. Engagement devices, meshing engagement devices, etc.).
The “rotary electric machine” is used as a concept including a motor (electric motor), a generator (generator), and a motor / generator that performs both functions of the motor and the generator as necessary.
In addition, regarding the arrangement of two members (here, a concept including intangibles such as holes), “overlapping in the axial direction when viewed in the radial direction” means that in at least a partial region in the circumferential direction When an imaginary straight line parallel to the radial direction is moved in the axial direction, it represents that there is an axial region where the imaginary straight line intersects both of the two members.

  According to this characteristic configuration, the second inner cylindrical portion having the first through hole, the second outer cylindrical portion having the second through hole, the first inner cylindrical portion having the open end, and the third through hole The first outer cylindrical portion having the is arranged in the order described from the radially inner side to the radially outer side. For example, oil supplied from the radially inner side of the second inner cylindrical portion reaches the second friction member through the first through hole and cools the second friction member. Thereafter, the oil is discharged from the second through hole and reaches the space between the second outer cylindrical portion and the first inner cylindrical portion in the radial direction. At least in the released state of the first engagement device, this oil passes through the third through hole disposed at a position overlapping with the axial direction when viewed from the opening end of the first inner cylindrical portion, It is smoothly guided to the radially outer side of the first outer cylindrical portion. That is, oil that is supplied from the radially inner side of the second inner cylindrical portion to the second friction member through the first through hole and then discharged radially outward from the second through hole of the second outer cylindrical portion. Most of them are smoothly guided from the opening end portion to the third through hole, bypassing the first inner cylindrical portion and the first friction member. Therefore, for example, the amount of oil supplied to the second engagement device (second friction member) when the vehicle is started using the torque of the rotating electrical machine while the first engagement device is released while the internal combustion engine is stopped. Compared to the above, the amount of oil supplied to the first engagement device (first friction member) can be reduced. Thereby, drag loss that can occur in the first engagement device (first friction member) can be reduced while appropriately cooling the second engagement device (second friction member).

  Here, at least one of the pressing member and the pressed member that is directly pressed by the pressing member has a radial communication portion that communicates in the radial direction, and at least the first engagement device is released. Thus, it is preferable that the opening end portion and the radial direction communication portion are arranged at positions overlapping in the axial direction when viewed in the radial direction.

  According to this configuration, in the released state of the first engagement device, the oil from the opening end is smoothly guided to the third through hole through the radial communication portion. Therefore, the oil from the opening end can be smoothly discharged through the third through hole to the radially outer side of the first outer cylindrical portion. As a result, drag loss that can occur in the first engagement device can be suppressed while the second engagement device is appropriately cooled.

  Further, it is preferable that at least in the released state of the first engagement device, the radial communication portion and the third through hole are arranged at positions overlapping in the axial direction when viewed in the radial direction. .

  According to this structure, the oil which passed through the radial direction communication part is appropriately guide | induced to the 3rd through-hole, and is discharged | emitted smoothly to the radial direction outer side of a 1st outer side cylindrical part.

  In addition, it is preferable that the area of the third through hole is set larger than the cross-sectional area of the radial communication portion.

  According to this configuration, the oil that has reached the third through hole from the opening end through the radial communication portion can be smoothly discharged to the radially outer side of the first outer cylindrical portion without stagnation. it can.

  Further, it is preferable that the positions of the third through hole and the radial communication portion are set so that the circumferential center of the third through hole is in phase with the circumferential center of the radial communication portion. is there.

  According to this structure, the structure arrange | positioned in the position which a 3rd through-hole and a radial direction communication part overlap in a radial direction can be implement | achieved reliably.

  Further, the rotation direction of the first outer cylindrical portion for rotating the wheel in the forward direction of the vehicle is a normal rotation direction, and the circumferential center of the third through hole is the circumferential center of the radial communication portion. On the other hand, it is preferable that the positions of the third through hole and the radial direction communication portion are set so that the phase is shifted in the direction opposite to the normal rotation direction.

  According to this configuration, when the first outer cylindrical portion rotates in the forward rotation direction, oil that flows radially outward through the radial communication portion can be smoothly guided to the third through hole. Therefore, the oil from the opening end is smoothly discharged to the radially outer side of the first outer cylindrical portion through the radial communication portion and the third through hole.

  In addition, it is preferable that the pressing member includes a pressing cylindrical portion extending in the axial direction, and the radial communication portion includes a fourth through hole penetrating the pressing cylindrical portion in the radial direction.

  According to this configuration, the first friction member can be appropriately pressed in the axial direction from the opening end side of the first inner cylindrical portion by the pressing cylindrical portion of the pressing member. Moreover, when a press member has such a press cylindrical part, the radial direction communication part connected to radial direction can be appropriately comprised by the 4th through-hole which penetrates the said press cylindrical part to radial direction. And the oil from an opening edge part is smoothly guide | induced to a 3rd through-hole through a 4th through-hole.

  Further, the radial communication portion is formed to extend in a radial direction on at least one of a contact surface of the pressing member with the pressed member and a contact surface of the pressed member with the pressing member. It is preferable that a radial groove is included.

  According to this configuration, the structure of the pressing member and the pressed member generally used in the vehicle drive device is not significantly changed, and the radial communication is performed in the radial direction by the radial groove formed in at least one of them. It is possible to appropriately configure the radial communication portion. And the oil from an opening edge part is smoothly guide | induced to a 3rd through-hole through a radial direction groove part.

  In addition, the first engagement device and the second engagement device overlap each other in the axial direction when viewed in the radial direction, and are radially inward of the stator of the rotating electrical machine and viewed in the radial direction. It is preferable that they are arranged at positions overlapping with the stator in the axial direction.

  According to this configuration, the first engagement device and the second engagement device that overlap in the axial direction when viewed in the radial direction further overlap in the axial direction with the stator of the rotating electrical machine when viewed in the radial direction. Thereby, compared with the structure arrange | positioned along with an axial direction, arrange | positioning two engaging devices in the radial inside of a stator, the axial direction length which those whole occupies can be restrained short. Therefore, the entire apparatus can be effectively downsized with respect to the axial dimension.

  The first inner cylindrical portion and the input member are connected to the first friction member on the pressing direction side, and the second inner cylindrical portion and the output member are connected to the second friction member. The first outer cylindrical portion and the second outer cylindrical portion are connected to the member on the pressing direction side, and the reaction between the second inner cylindrical portion and the output member is opposite to the connection portion between the second inner cylindrical portion and the output member. It is preferable that the first outer cylindrical portion and the rotor of the rotating electrical machine are connected on the pressing direction side and are connected on the radially outer side of the first outer cylindrical portion.

  According to this configuration, a configuration in which the first engagement device, the rotating electrical machine, and the second engagement device are provided in this order on the power transmission path connecting the input member and the output member can be realized in a compact manner.

  The rotor support member includes a rotor support member that supports the rotor of the rotating electrical machine, and the rotor support member includes a cylindrical support portion that supports the rotor from a radially inner side, and the cylindrical support portion includes the cylindrical support portion. The outer periphery of the first outer cylindrical portion protrudes radially inward from the inner peripheral surface of the other part of the portion and does not overlap in the axial direction with the third through hole when viewed in the radial direction. The cylindrical support portion is further supplied from the radially inner side to the side opposite to the third through hole side sandwiching the raised engagement portion in the axial direction. It is preferable to provide an inlet for a cooling oil passage that guides the oil to be supplied to the coil end portion of the stator of the rotating electrical machine.

  According to this configuration, the oil supplied from the radially inner side is guided to the coil end portion of the stator by the cooling oil passage formed in the cylindrical support portion of the rotor support member, and the coil end portion can be cooled. it can. In addition, by realizing the drive connection between the rotating electrical machine (cylindrical support portion) and the first engagement device (first outer cylindrical portion) by the bulge engagement portion, the bulge engagement portion is connected to the cylindrical support portion. It can be made to function also as a weir which regulates oil circulation along. Therefore, the oil supplied from the radially inner side on the side opposite to the third through hole side with respect to the raised engagement portion is efficiently guided to the cooling oil passage through the inlet formed in the cylindrical support portion. be able to. Thereby, a coil end part can be cooled efficiently. Moreover, although the oil after cooling of a 2nd engagement apparatus (2nd friction member) may be comparatively high temperature, the comparatively high temperature oil which flows through the 3rd through-hole side with respect to a protruding engagement part Can be prevented from being supplied to the coil end portion through the cooling oil passage.

  The rotating electrical machine, the first engagement device, and the second engagement device include a case having a case wall that extends in a radial direction adjacent to the axial direction, and the cylindrical support portion has an axial direction. A support opening end portion that opens toward the case wall side, and the support opening end portion is arranged at a position overlapping with the coil end portion in the axial direction when viewed in the radial direction, and the case wall is It is preferable that a shielding protrusion that protrudes at least to a position overlapping with the support opening end portion in the axial direction when viewed in the radial direction is provided between the support opening end portion and the coil end portion in the radial direction.

  The oil after cooling of the second engagement device (second friction member) may be at a relatively high temperature. For this reason, when the oil discharged from the third through hole flows toward the support opening end along the first outer cylindrical portion and the cylindrical support portion, and further reaches the coil end portion from the support opening end portion. The cooling effect of the coil end portion may be attenuated. Therefore, as described above, the case wall has a configuration including the shielding protrusion, so that relatively high temperature oil can be prevented from reaching the coil end portion. Therefore, the cooling performance of the coil end part by the oil supplied through the cooling oil passage can be ensured.

The schematic diagram which shows schematic structure of the vehicle drive device which concerns on embodiment. Partial cross-sectional view of a vehicle drive device Cross-sectional view of the main part of the vehicle drive device Cross-sectional view of the main part of the vehicle drive device VV sectional view in FIG. The figure which shows the other form of the positional relationship of a 3rd through-hole and a 4th through-hole. Sectional drawing of the principal part of the vehicle drive device which concerns on other embodiment. VIII-VIII sectional view in FIG. The figure which shows the other form of the positional relationship of a 3rd through-hole and radial direction groove part.

  An embodiment of a vehicle drive device according to the present invention will be described with reference to the drawings. The vehicle drive device 1 according to this embodiment is a vehicle drive device (hybrid vehicle drive) for driving a vehicle (hybrid vehicle) provided with both the internal combustion engine E and the rotating electrical machine MG as a driving force source for the wheels W. Device). Specifically, the vehicle drive device 1 is configured as a drive device for a 1-motor parallel type hybrid vehicle.

  In the following description, unless otherwise specified, “axial direction L”, “radial direction”, and “circumferential direction” are based on the rotational axis (axial center X shown in FIG. 2) of rotating electrical machine MG. Defined. Further, the internal combustion engine E side (the right side in FIG. 2) that is one side in the axial direction L is defined as the first axial direction L1 side, and the opposite side (the other side in the axial direction L) is relatively. The speed change mechanism TM side (left side in FIG. 2) is defined as the second axial direction L2 side. In addition, the direction about each member represents the direction in the state in which they were assembled | attached to the vehicle drive device 1. FIG. 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.

1. Schematic Configuration of Vehicle Drive Device A schematic configuration of the vehicle drive device 1 according to the present embodiment will be described. As shown in FIG. 1, the vehicle drive device 1 includes an input shaft I that is drivingly connected to the internal combustion engine E, an intermediate shaft M that is drivingly connected to the wheels W, a rotating electrical machine MG, and a first engagement device CL1. And a second engagement device CL2. The first engagement device CL1, the rotating electrical machine MG, and the second engagement device CL2 are provided in the power transmission path T connecting the input shaft I and the intermediate shaft M in the order described from the input shaft I side. As shown in FIG. 1, the vehicle drive device 1 includes a speed change mechanism TM, a counter gear mechanism C, and a differential gear device DF. These are accommodated in a case (drive device case) 2.

  The internal combustion engine E is a prime mover (such as a gasoline engine or a diesel engine) that is driven by combustion of fuel inside the engine to extract power. In the present embodiment, the input shaft I is drivingly connected to the output shaft (crankshaft or the like) of the internal combustion engine E via a damper DA (see FIG. 2). The input shaft I may be drivingly connected to the output shaft of the internal combustion engine E without passing through the damper DA. In the present embodiment, the input shaft I corresponds to the “input member” in the present invention.

  The first engagement device CL1 is provided between the input shaft I and the rotating electrical machine MG in the power transmission path T. The first engagement device CL1 selectively drives and connects the input shaft I and the rotating electrical machine MG that are drivingly connected to the internal combustion engine E. The first engagement device CL1 functions as an internal combustion engine separation engagement device that separates the internal combustion engine E from the wheel W. The first engagement device CL1 is configured as a hydraulically driven friction engagement device. The first engagement device CL1 is controlled in its engagement state (direct engagement state / slip engagement state / release state) based on the hydraulic pressure supplied to the first engagement device CL1.

  The rotating electrical machine MG can perform a function as a motor (electric motor) that generates power upon receiving power supply and a function as a generator (generator) that generates power upon receiving power supply. ing. Therefore, the rotating electrical machine MG is electrically connected to a power storage device (battery, capacitor, etc.). The rotating electrical machine MG is powered by receiving power from the power storage device, or supplies the power storage device with power generated by the torque of the internal combustion engine E or the inertial force of the vehicle.

  The second engagement device CL2 is provided between the rotating electrical machine MG and the speed change mechanism TM in the power transmission path T. The second engagement device CL2 selectively connects the rotating electrical machine MG and the intermediate shaft M that is drivingly connected to the speed change mechanism TM. The second engagement device CL2 is configured as a hydraulically driven friction engagement device. The engagement state (direct engagement state / slip engagement state / release state) of the second engagement device CL2 is controlled based on the hydraulic pressure supplied to the second engagement device CL2. In the present embodiment, the intermediate shaft M corresponds to the “output member” in the present invention. The intermediate shaft M is an input shaft (transmission input shaft) of the speed change mechanism TM.

  In this embodiment, the speed change mechanism TM is an automatic stepped speed change mechanism that includes a plurality of speed change engagement devices and is capable of switching a plurality of speed stages having different speed ratios. As the speed change mechanism TM, an automatic continuously variable speed change mechanism that can change the speed ratio steplessly, a manual stepped speed change mechanism that is capable of switching a plurality of speed stages having different speed ratios, or the like may be used. The speed change mechanism TM changes the rotation and torque input to the intermediate shaft M in accordance with the speed change ratio at each time point, converts the torque, and transmits it to the speed change output gear G.

  The transmission output gear G is drivingly connected to the differential gear unit DF via the counter gear mechanism C. The differential gear unit DF is drivably coupled to the wheel W via the axle A. The differential gear device DF distributes and transmits the rotation and torque input to the differential gear device DF to the two left and right wheels W. Accordingly, the vehicle drive device 1 can cause the vehicle to travel by transmitting the torque of one or both of the internal combustion engine E and the rotating electrical machine MG to the wheels W.

  In the vehicle drive device 1 according to the present embodiment, the input shaft I and the intermediate shaft M are arranged coaxially, and the axle A is parallel to each other on an axis different from the input shaft I and the intermediate shaft M. The arrangement is a multi-axis arrangement. Such a configuration is suitable as a configuration of the vehicle drive device 1 mounted on, for example, an FF (Front Engine Front Drive) vehicle.

2. Configuration of Each Part of Vehicle Drive Device A configuration of each part of the vehicle drive device 1 according to the present embodiment will be described. As shown in FIG. 2, the case 2 includes a peripheral wall 21 that covers the outer periphery of each housing component such as the rotating electrical machine MG, the first engagement device CL1, and the second engagement device CL2, and the axial first direction of the peripheral wall 21. A first support wall 22 that closes the opening on the L1 side, and a second support wall 25 disposed between the rotating electrical machine MG and the speed change mechanism TM on the second axial direction L2 side of the first support wall 22. ing. The case 2 includes an end support wall (not shown) that closes the end of the peripheral wall 21 on the second axial direction L2 side.

  The first support wall 22 extends in the radial direction and the circumferential direction on the first axial direction L1 side of the rotating electrical machine MG, the first engagement device CL1, and the second engagement device CL2. The first support wall 22 is disposed adjacent to the rotating electrical machine MG or the like at a predetermined interval on the first axial direction L1 side. The first support wall 22 has a through hole in the axial direction L, and the input shaft I is inserted through the through hole. As a result, the input shaft I passes through the first support wall 22 and is inserted into the case 2. The first support wall 22 has a cylindrical inner end protruding portion 23 that protrudes in the axial direction L toward the second axial direction L2 at the radially inner end thereof. The first support wall 22 rotatably supports the rotor support member 30 on the first axial direction L1 side of the rotating electrical machine MG via the input bearing 81 by the inner end protruding portion 23.

  The second support wall 25 extends in the radial direction and the circumferential direction on the second axial direction L2 side of the rotating electrical machine MG, the first engagement device CL1, and the second engagement device CL2. The second support wall 25 is disposed adjacent to the rotating electrical machine MG or the like at a predetermined interval on the second axial direction L2 side. The second support wall 25 has a cylindrical sleeve portion 26 that protrudes in the axial direction L toward the axial first direction L1 at the radially inner end thereof. An intermediate shaft M is inserted through the sleeve portion 26. Thereby, the intermediate shaft M is disposed in the case 2 so as to penetrate the second support wall 25. In the present embodiment, the second support wall 25 corresponds to the “case wall” in the present invention.

  The rotating electrical machine MG includes a stator St fixed to the case 2 and a rotor Ro supported to be rotatable with respect to the case 2. The stator St includes coil end portions Ce on both sides in the axial direction L. The rotor Ro is disposed on the radially inner side of the stator St. The rotor Ro is rotatably supported with respect to the case 2 via a rotor support member 30 extending radially inward from the rotor Ro.

  As shown in FIG. 3, the rotor support member 30 that supports the rotor Ro includes a cylindrical support portion 31 that extends in the axial direction L and a plate-like support portion 35 that extends in the radial direction. The cylindrical support part 31 is formed in a substantially cylindrical shape having a main body part in contact with the inner peripheral surface of the rotor Ro and a flange part in contact with the side surface of the rotor Ro. The cylindrical support portion 31 supports the rotor Ro in a state of being in contact with the radially inner side and the first axial direction L1 side. The rotor Ro is held from the second axial direction L2 side by the locking holding portion 34. Moreover, the cylindrical support part 31 has the protruding engaging part 32 which protrudes toward the radial inner side from the inner peripheral surface of the other site | part of the said cylindrical support part 31 in the inner peripheral side. The rotating electrical machine MG and the first outer support member 51 of the first engagement device CL1 are drivingly connected via the raised engagement portion 32 so as to rotate integrally. Moreover, the cylindrical support part 31 is formed so that it may open toward the axial 2nd direction L2 side (2nd support wall 25 side). The support opening end portion 33 in the cylindrical support portion 31 is disposed at a position overlapping the coil end portion Ce and the axial direction L when viewed in the radial direction. In this example, it arrange | positions in the position which overlaps with the coil end part Ce of the axial 2nd direction L2 side (2nd support wall 25 side).

  The plate-like support portion 35 is formed in an annular plate shape extending radially inward from the end portion of the cylindrical support portion 31 on the first axial direction L1 side. The plate-like support part 35 is provided with a cylindrical first protruding part 36 that protrudes toward the first axial direction L1 side at the radially inner end. Further, the plate-like support portion 35 includes a cylindrical second protruding portion 37 that protrudes toward the first axial direction L1 side at the radial intermediate portion. The second protrusion 37 is formed with a larger diameter than the first protrusion 36.

  The rotor support member 30 is supported in the radial direction by the case 2 (first support wall 22) by an input bearing 81 disposed between the first protrusion 36 and the inner end protrusion 23. In the present embodiment, in response to the rotor support member 30 being cantilevered on the first axial direction L1 side, the input bearing 81 has two groups of balls composed of a plurality of balls in the axial direction L. A continuous bearing (double ball bearing) is used. A seal member 82 that restricts oil leakage to the internal combustion engine E (damper DA) side is disposed between the inner end protruding portion 23 and the input shaft I.

  A rotation sensor 18 is provided between the rotor support member 30 (plate-like support portion 35) and the first support wall 22 in the axial direction L. The rotation sensor 18 is a sensor for detecting the rotational position of the rotor Ro relative to the stator St of the rotating electrical machine MG. In this example, a resolver is used as such a rotation sensor 18. The sensor rotor of the rotation sensor 18 is fixed to the outer peripheral surface of the second protrusion 37. The sensor stator of the rotation sensor 18 is fixed to the first support wall 22 in a state of being arranged on the radially outer side of the sensor rotor.

  As shown in FIGS. 2 to 4, the first engagement device CL <b> 1 includes a first friction member 41, a first inner support member 45, a first outer support member 51, and a first pressing member 57. This is a friction engagement device. Each member constituting the first engagement device CL1 is arranged coaxially with the input shaft I and the intermediate shaft M. The first engagement device CL1 is disposed at a position that is radially inward of the stator St of the rotating electrical machine MG and overlaps the stator St and the axial direction L when viewed in the radial direction.

  The first friction member 41 includes a pair of first inner friction member 42 and first outer friction member 43 (see FIG. 4). The first inner friction member 42 and the first outer friction member 43 are both formed in an annular plate shape and are arranged with their rotation axes coinciding with each other. A plurality of first inner friction members 42 and first outer friction members 43 are provided, and these members are alternately arranged along the axial direction L. One of the first inner friction member 42 and the first outer friction member 43 can be a friction plate and the other can be a separate plate.

  The first inner support member 45 includes a first inner cylindrical portion 46 that supports the first inner friction member 42 from the radially inner side, and a first inner plate-shaped portion that extends radially inward from the first inner cylindrical portion 46. 47. The first inner cylindrical portion 46 is formed in a cylindrical shape extending along the axial direction L. The first inner cylindrical portion 46 is formed so as to open toward the side opposite to the internal combustion engine E side (the second axial direction L2 side). That is, the first inner cylindrical portion 46 has an opening end portion 48 that opens toward the second axial direction L2 side. A plurality of spline teeth extending in the axial direction L are formed on the outer peripheral portion of the first inner cylindrical portion 46 so as to be dispersed in the circumferential direction. Similar spline teeth are formed on the inner peripheral portion of the first inner friction member 42, and the first inner friction member 42 is radially inward by the first inner support member 45 with both spline teeth engaged. It is supported from. Accordingly, the first inner friction member 42 is supported so as to be slidable in the axial direction L in a state where relative rotation is restricted with respect to the first inner support member 45. In the present embodiment, the first inner cylindrical portion 46 is different from the first outer cylindrical portion 52, the second inner cylindrical portion 66, and the second outer cylindrical portion 72, which will be described later. A through hole penetrating the shape portion 46 in the radial direction is not formed. That is, the first inner cylindrical portion 46 is a non-porous cylindrical portion (continuous cylindrical portion) that does not have a radial through hole.

  The first inner plate-like portion 47 is an annular plate-like member extending radially inward from the end portion on the first axial direction L1 side of the first inner cylindrical portion 46. The first inner cylindrical portion 46 and the first inner plate-like portion 47 are integrally formed. The first inner plate-like portion 47 is connected to the flange portion of the input shaft I at the radially inner end thereof. Thus, the first inner cylindrical portion 46 and the input shaft I are integrally connected to the first friction member 41 on the first axial direction L1 side via the first inner plate-like portion 47. .

  The first outer support member 51 includes a first outer cylindrical portion 52 that supports the first outer friction member 43 from the radially outer side, and a first outer plate-shaped portion that extends radially inward from the first outer cylindrical portion 52. 53 and a first cylindrical connecting portion 54 connected to the second outer support member 71 of the second engagement device CL2. The first outer cylindrical portion 52 is formed in a cylindrical shape extending along the axial direction L. The first outer cylindrical portion 52 is formed so as to open toward the internal combustion engine E side (the first axial direction L1 side). A plurality of spline teeth extending in the axial direction L are formed on the inner peripheral portion of the first outer cylindrical portion 52 so as to be dispersed in the circumferential direction. Similar spline teeth are formed on the outer peripheral portion of the first outer friction member 43, and the first outer friction member 43 is moved from the radially outer side by the first outer support member 51 in a state where both spline teeth are engaged. It is supported. Accordingly, the first outer friction member 43 is supported so as to be slidable in the axial direction L in a state where relative rotation is restricted with respect to the first outer support member 51.

  Further, the first outer cylindrical portion 52 is driven to rotate integrally with the rotor Ro by engaging with a raised engagement portion 32 provided on the cylindrical support portion 31 of the rotor support member 30 at the outer peripheral portion thereof. It is connected. That is, the first outer cylindrical portion 52 and the cylindrical support portion 31 are connected via the raised engagement portion 32 on the radially outer side of the first outer cylindrical portion 52. The engaging portion between the first outer cylindrical portion 52 and the raised engaging portion 32 can be configured as, for example, a spline engaging portion in which a plurality of spline teeth extending in the axial direction L mesh with each other. The first outer cylindrical portion 52 is formed with a third through-hole 13 that penetrates the first outer cylindrical portion 52 in the radial direction (communication between the inner peripheral surface and the outer peripheral surface).

  The first outer plate-like portion 53 is an annular plate-like member that extends radially inward from the end portion of the first outer tubular portion 52 on the second axial direction L2 side. The first outer cylindrical portion 52 and the first outer plate-like portion 53 are integrally formed. The first cylindrical connecting portion 54 is formed in a cylindrical shape extending along the axial direction L. The first cylindrical connecting portion 54 is connected to the first outer plate-like portion 53 at the radially inner end of the first outer plate-like portion 53. The first cylindrical connecting portion 54 is mainly formed so as to extend from the first outer plate-like portion 53 toward the first axial direction L1 side. The 1st cylindrical connection part 54 is connected with the 2nd cylindrical connection part 74 which comprises the 2nd outer side support member 71 of 2nd engagement apparatus CL2 in the inner peripheral part. Further, as shown in FIG. 2, the first cylindrical connecting portion 54 is drivingly connected to the pump rotor of the oil pump OP.

  The first pressing member 57 slides in the axial direction L according to the hydraulic pressure when oil of a predetermined hydraulic pressure is supplied from the hydraulic control device (not shown) to the first hydraulic oil chamber H1. 41 is a member that presses 41 (first piston). The first pressing member 57 presses the first friction member 41 toward the first axial direction L1. In the present embodiment, the first pressing member 57 corresponds to a “pressing member” in the present invention. The first axial direction L1 coincides with the “pressing direction” in the present invention, and the second axial direction L2 coincides with the “counterpressing direction” in the present invention. As shown in FIGS. 3 and 4, the first pressing member 57 includes a cylindrical pressing cylindrical portion 58 extending in the axial direction L. When the first pressing member 57 slides in the axial direction L, the first friction member 41 is pressed by the contact surface of the end portion of the pressing cylindrical portion 58 on the axial first direction L1 side. A fourth through hole 14 is formed in the pressing cylindrical portion 58 so as to penetrate the pressing cylindrical portion 58 in the radial direction (communication between the inner peripheral surface and the outer peripheral surface). In the present embodiment, the fourth through hole 14 corresponds to the “radial communication portion” in the present invention.

  As shown in FIGS. 2 to 4, the second engagement device CL <b> 2 includes a second friction member 61, a second inner support member 65, a second outer support member 71, and a second pressing member 77. This is a friction engagement device. Each member constituting the second engagement device CL2 is arranged coaxially with the input shaft I and the intermediate shaft M. The second engagement device CL2 is disposed at a position that is radially inward of the stator St of the rotating electrical machine MG and overlaps the stator St and the axial direction L when viewed in the radial direction.

  The second friction member 61 includes a pair of second inner friction member 62 and second outer friction member 63 (see FIG. 4). The configurations of the second inner friction member 62 and the second outer friction member 63 can be the same as the configurations of the first inner friction member 42 and the first outer friction member 43 described above.

  The second inner support member 65 includes a second inner cylindrical portion 66 that supports the second inner friction member 62 from the radially inner side, and a second inner plate-shaped portion that extends radially inward from the second inner cylindrical portion 66. 67. The second inner cylindrical portion 66 is formed in a cylindrical shape extending along the axial direction L. Similar to the first inner cylindrical portion 46, the second inner cylindrical portion 66 is formed so as to open toward the side opposite to the internal combustion engine E side (the axial second direction L2 side). A plurality of spline teeth extending in the axial direction L are formed on the outer peripheral portion of the second inner cylindrical portion 66 so as to be dispersed in the circumferential direction. Similar spline teeth are formed on the inner peripheral portion of the second inner friction member 62, and the second inner friction member 62 is radially inward by the second inner support member 65 with both the spline teeth engaged. It is supported from. Accordingly, the second inner friction member 62 is supported so as to be slidable in the axial direction L in a state where relative rotation is restricted with respect to the second inner support member 65. The second inner cylindrical portion 66 is formed with a first through hole 11 that penetrates the second inner cylindrical portion 66 in the radial direction (communication between the inner peripheral surface and the outer peripheral surface).

  The second inner plate-shaped portion 67 is an annular plate-shaped member extending radially inward from the end portion of the second inner cylindrical portion 66 on the first axial direction L1 side. The second inner cylindrical portion 66 and the second inner plate-shaped portion 67 are integrally formed. The second inner plate-like portion 67 is connected to a flange member 84 that is drivingly connected to the intermediate shaft M at the radially inner end thereof. Accordingly, the second inner cylindrical portion 66 and the intermediate shaft M (flange member 84) are coupled to the second friction member 61 on the first axial direction L1 side via the second inner plate-shaped portion 67. ing.

  The second outer support member 71 includes a second outer cylindrical portion 72 that supports the second outer friction member 63 from the radially outer side, and a second outer plate-shaped portion that extends radially inward from the second outer cylindrical portion 72. 73 and a second cylindrical connecting portion 74 connected to the first outer support member 51 of the first engagement device CL1. The second outer cylindrical portion 72 is formed in a cylindrical shape extending along the axial direction L. Similar to the first outer cylindrical portion 52, the second outer cylindrical portion 72 is formed so as to open toward the internal combustion engine E side (the axial first direction L1 side). A plurality of spline teeth extending in the axial direction L are formed on the inner peripheral portion of the second outer cylindrical portion 72 so as to be dispersed in the circumferential direction. Similar spline teeth are formed on the outer peripheral portion of the second outer friction member 63, and the second outer friction member 63 is moved from the radially outer side by the second outer support member 71 in a state where both the spline teeth are engaged. It is supported. Thus, the second outer friction member 63 is supported so as to be slidable in the axial direction L in a state where relative rotation is restricted with respect to the second outer support member 71. The second outer cylindrical portion 72 is formed with a second through-hole 12 that penetrates the second outer cylindrical portion 72 in the radial direction (communication between the inner peripheral surface and the outer peripheral surface).

  The second outer plate-like portion 73 is an annular deformed plate-like member that extends radially inward from the end portion on the second axial direction L2 side of the second outer tubular portion 72. The second cylindrical connecting portion 74 is formed in a cylindrical shape extending along the axial direction L. The second cylindrical connecting portion 74 is connected to the second outer plate-shaped portion 73 at the radially inner end of the second outer plate-shaped portion 73. The second outer cylindrical portion 72, the second outer plate-shaped portion 73, and the second cylindrical connecting portion 74 are integrally formed. The second cylindrical connecting portion 74 is formed to extend from the radially inner end of the second outer plate-like portion 73 toward the first axial direction L1 side. The 2nd cylindrical connection part 74 is connected in the inner peripheral part to the 1st cylindrical connection part 54 which comprises the 1st outer side support member 51 of 1st engagement apparatus CL1. The first outer support member 51 having the first outer cylindrical part 52 and the second outer support member 71 having the second outer cylindrical part 72 are the second inner cylindrical part via the second inner plate-like part 67. 66 and the intermediate shaft M are integrally connected on the second axial direction L2 side. In the present embodiment, the two outer support members 51 and 71 are integrally connected to the first friction member 41 and the second friction member 61 at positions overlapping in the axial direction L when viewed in the radial direction.

  The second pressing member 77 slides in the axial direction L according to the hydraulic pressure when oil of a predetermined hydraulic pressure is supplied from the hydraulic control device (not shown) to the second hydraulic oil chamber H2, and the second friction member. A member (second piston) that presses 61 toward the first axial direction L1. Unlike the first pressing member 57, the second pressing member 77 is not formed with a through hole that penetrates the first pressing member 57 in the radial direction.

  In the present embodiment, the first inner cylindrical portion 46 is disposed on the radially outer side than the second outer cylindrical portion 72 (the second outer cylindrical portion 72 is more than the first inner cylindrical portion 46. Arranged radially inward). Therefore, the second inner cylindrical portion 66, the second outer cylindrical portion 72, the first inner cylindrical portion 46, and the first outer cylindrical portion 52 are arranged in the order described from the radially inner side to the radially outer side. Has been. These are arranged at positions overlapping each other in the axial direction L when viewed in the radial direction. Thereby, the positional relationship between the first friction member 41 and the second friction member 61 is also a positional relationship overlapping each other in the axial direction L when viewed in the radial direction. As described above, in the present embodiment, the first friction member 41 and the second friction member 61 are arranged at positions overlapping with the stator St in a state where they overlap each other in the axial direction L when viewed in the radial direction. . As a result, with respect to the dimension in the axial direction L, the entire vehicle drive device 1 is effectively downsized.

3. Cooling structure of each engaging device and rotating electrical machine The cooling structure of each engaging device CL1, CL2 and rotating electrical machine MG in the vehicle drive device 1 according to the present embodiment will be described. In the present embodiment, as an example, a description will be given on the assumption that a stopped vehicle starts with the torque of the rotating electrical machine MG in the electric travel mode. At the time of such a start, in a state where the rotating electrical machine MG is outputting torque, oil of a predetermined hydraulic pressure is supplied to at least the second engagement device CL2 provided on the downstream side thereof, and the second engagement device CL2 is Must be engaged. Further, when the speed change mechanism TM is an automatic stepped speed change mechanism as in the present embodiment, oil of a predetermined hydraulic pressure is supplied to one or more of the plurality of speed change engagement devices provided in the speed change mechanism TM. There is a need to feed and engage them.

  In the present embodiment, the oil pump OP is drivably coupled to the first outer support member 51 of the first engagement device CL1 that is drivably coupled to the rotating electrical machine MG (see FIG. 2). When the vehicle starts, the oil pump OP is driven using the torque of the rotating electrical machine MG output for driving the wheels W. The oil discharged from the oil pump OP is supplied to the second engagement device CL2 and the shift engagement device in the transmission mechanism TM to engage them. Thereby, it is possible to appropriately start in the electric travel mode. Note that the vehicle drive device 1 is not provided with a pump (electric pump) having a dedicated drive motor different from the oil pump OP. By omitting the installation of such an electric pump, cost reduction of the vehicle drive device 1 is achieved. However, it is not limited to such a configuration, and an electric pump may be provided.

  By the way, in order to increase the hydraulic pressure of the oil discharged from the oil pump OP to the hydraulic pressure necessary to engage each engagement device, the rotating electrical machine MG rotates at a rotational speed equal to or higher than a predetermined reference rotational speed. There is a need to. On the other hand, the rotational speed of the intermediate shaft M determined according to the vehicle speed when the specific gear stage is formed by the speed change mechanism TM is less than the reference rotational speed when the vehicle speed is low to some extent. Therefore, in order to absorb these rotational speed differences (differential rotations), it is necessary to engage the second engagement device CL2 while slipping (to set the slip engagement state). In the slip engagement state of the second engagement device CL2, the second friction member 61 of the second engagement device CL2 generates heat due to friction or the like, and thus it is necessary to cool it effectively. In the rotating electrical machine MG, when a current is passed through the coil of the stator St, the coil generates heat due to the generation of Joule heat. Therefore, there is a need to effectively cool the coil (for example, the coil end portion Ce that is a portion protruding in the axial direction L from the stator core).

  Therefore, as shown in FIGS. 2 to 4, the vehicle drive device 1 according to the present embodiment mainly includes a first cooling oil passage P <b> 1 for cooling the second friction member 61 of the second engagement device CL <b> 2. The second cooling oil passage P2 is mainly provided for cooling the coil end portion Ce of the rotating electrical machine MG. These are two independent oil passages. The oil discharged from the oil pump OP passes through an oil flow passage formed in the case 2 and a shaft peripheral oil passage 91 formed between the inner peripheral surface of the sleeve portion 26 and the outer peripheral surface of the intermediate shaft M. The second outer cylindrical portion 72 (second friction member 61) is supplied to the space inside in the radial direction. Further, an oil flow passage formed in the case 2, an in-shaft oil passage 92 formed in the intermediate shaft M, and the first inner plate-like portion 47 of the first engagement device CL <b> 1 and the plate of the rotor support member 30. It is also supplied to the radially inner space of the cylindrical support portion 31 of the rotor support member 30 through a communication oil passage 93 formed between the cylindrical support portion 35 and the cylindrical support portion 35. 2 to 4, main oil flows are indicated by broken-line arrows.

  The first cooling oil passage P1 supplies the oil supplied to the radially inner space of the second outer cylindrical portion 72 to the second friction member 61 to cool the second friction member 61, and It is an oil passage for guiding the cylindrical portion 52 to the outside in the radial direction. In order to form such a first cooling oil passage P1, the second inner cylindrical portion 66, the second outer cylindrical portion 72, and the first outer cylindrical portion 52 are respectively formed in the first through hole 11 and the second through hole. It is a perforated cylindrical portion having a hole 12 and a third through hole 13.

  Specifically, the second inner cylindrical portion 66 has the first through hole 11 that penetrates in the radial direction at a position overlapping with the second friction member 61 in the axial direction L when viewed in the radial direction. The first through hole 11 is an elongated through hole formed with a predetermined width in the axial direction L and the circumferential direction. The 1st through-hole 11 is formed in the part of the some spline teeth which the 2nd inner side cylindrical part 66 has. The second outer cylindrical portion 72 has a second through hole 12 that penetrates in the radial direction at a position overlapping with the second friction member 61 in the axial direction L when viewed in the radial direction. The second through-hole 12 is an elongated through-hole formed with a predetermined width in the axial direction L and the circumferential direction. The second through hole 12 is formed in a plurality of spline tooth portions of the second outer cylindrical portion 72.

  The first outer cylindrical portion 52 has a third through hole 13 penetrating in the radial direction at a position not overlapping with the first friction member 41 in the axial direction L when viewed in the radial direction. The third through hole 13 is formed in a portion on the second axial direction L2 side which is the first pressing member 57 side of at least the first friction member 41 in the first outer cylindrical portion 52. In the present embodiment, the first friction member 41 is disposed close to the portion on the first axial direction L1 side in the first outer cylindrical portion 52, and the third through hole 13 is the shaft in the first outer cylindrical portion 52. It is formed in a portion on the second direction L2 side. The third through-hole 13 is an elongated through-hole formed with a predetermined width in the axial direction L and the circumferential direction (see FIG. 5). The third through hole 13 is formed in a plurality of spline tooth portions of the first outer cylindrical portion 52.

  Each of the first through hole 11, the second through hole 12, and the third through hole 13 can be provided in the circumferential direction. In addition, one or more rows can be provided in the axial direction L, respectively. In the present embodiment, a plurality of first through holes 11 are distributed in the circumferential direction and two rows are provided in the axial direction L, and a plurality of second through holes 12 and third through holes 13 are distributed in the circumferential direction. In addition, one row is provided in the axial direction L. Note that the number, the number of rows, the shape, and the like can be appropriately set and changed according to various purposes.

  In the present embodiment, the pressing cylindrical portion 58 of the first pressing member 57 is at least first when viewed in the radial direction between the first inner cylindrical portion 46 and the first outer cylindrical portion 52 in the radial direction. The inner cylindrical portion 46 is disposed at a position overlapping the opening end 48 in the axial direction L. In the present embodiment, the pressing cylindrical portion 58 is a perforated cylindrical portion having the fourth through hole 14 penetrating in the radial direction. The fourth through hole 14 is a round hole-like through hole formed in a dot shape in this example (see FIG. 5). One or more fourth through holes 14 may be provided in the circumferential direction. Further, one or more rows can be provided in the axial direction L. In the present embodiment, a plurality of fourth through holes 14 are dispersedly arranged in the circumferential direction and provided in a row in the axial direction L. Note that the number, the number of rows, the shape, and the like can be appropriately set and changed according to various purposes.

  Here, the positional relationship in the axial direction L of the opening end portion 48 of the first inner cylindrical portion 46, the fourth through hole 14 of the pressing cylindrical portion 58, and the third through hole 13 of the first outer cylindrical portion 52. Focus on it. Here, in view of the situation where the stopped vehicle is assumed to start in the electric travel mode, attention is paid to the positional relationship in the released state of the first engagement device CL1. Then, the 4th through-hole 14 is arrange | positioned in the position which includes the position of the both sides with respect to the position of the opening edge part 48 in the axial direction L. As shown in FIG. Thereby, the opening edge part 48 and the 4th through-hole 14 are arrange | positioned in the position which overlaps with the axial direction L seeing in radial direction. Further, the third through hole 13 is arranged at a position including the entirety of the region occupied by the fourth through hole 14 in the axial direction L. Thereby, the 4th through-hole 14 and the 3rd through-hole 13 are arrange | positioned in the position which overlaps with the axial direction L seeing in radial direction. In such a positional relationship, the opening end 48, the fourth through hole 14, and the third through hole 13 are arranged at positions that overlap each other in the axial direction L when viewed in the radial direction.

  Further, in the circumferential direction, as shown in FIG. 5, the third through hole 13 and the fourth through hole so that the circumferential center of the third through hole 13 is in phase with the circumferential center of the fourth through hole 14. 14 positions are set. 5A is a cross-sectional view seen in the axial direction L, and FIG. 5B is a diagram showing a positional relationship when seen in the radial direction. In the present embodiment, with respect to the set of third through holes 13 and fourth through holes 14 that overlap in the axial direction L when viewed in the radial direction, the third through holes 13 and A fourth through hole 14 is arranged. At this time, as can be understood from FIG. 5B, the area of the third through hole 13 is set larger than the area of the fourth through hole 14. The area of the third through hole 13 can be, for example, about 1.1 to 4 times the area of the fourth through hole 14. In the example shown in the figure, it is approximately doubled.

  The opening end 48 of the first inner cylindrical portion 46 is formed continuously in the circumferential direction. The opening end portion 48 is arranged so as to occupy the same position in the axial direction L over the entire circumference.

  As shown in FIG. 4, the oil supplied to the radially inner side of the second inner cylindrical portion 66 through the axial circumferential oil passage 91 flows along the first cooling oil passage P1. Specifically, the oil reaches the second friction member 61 through the first through hole 11 formed in the second inner cylindrical portion 66 and cools the second friction member 61. Thereafter, the oil is discharged radially outward from the second through-hole 12 formed in the second outer cylindrical portion 72 and reaches the space between the second outer cylindrical portion 72 and the first inner cylindrical portion 46. To do. At this time, in the present embodiment, since the first inner cylindrical portion 46 has a non-porous structure, the oil that has reached the space bypasses the first inner cylindrical portion 46 and the first friction member 41 and opens. It flows toward the end 48 side (second axial direction L2 side). The oil that has reached the opening end 48 passes through the fourth through hole 14 and the third through hole 13 that are arranged in a position overlapping with the opening end 48 in the axial direction L when viewed in the radial direction, and passes through the first outer side. It is smoothly guided to the radially outer side of the cylindrical portion 52.

  Thus, the first cooling oil passage P1 is supplied from the radially inner side of the second inner cylindrical portion 66 to the second friction member 61 through the first through hole 11, and then the second outer cylindrical portion 72. The oil that is discharged radially outward from the second through hole 12 is guided to the third through hole 13 of the first outer cylindrical portion 52. The first cooling oil passage P1 includes an inter-friction member oil passage P1a extending along the second friction member 61 between the second inner tubular portion 66 and the second outer tubular portion 72, and the inter-friction member oil passage. A bypass oil passage P1b extending along the first inner cylindrical portion 46 from the outlet (second through hole 12) of P1a, and a derivation extending along the radial direction so as to connect the bypass oil passage P1b and the third through hole 13 And an oil passage P1c. The lead-out oil passage P1c is formed to extend linearly along the radial direction through the fourth through hole 14.

  In the present embodiment, the first cooling oil passage P1 has a bypass oil passage P1b, and the oil bypasses the first friction member 41 when flowing through the bypass oil passage P1b. The amount of oil supplied to the one friction member 41 can be reduced. Therefore, even when the second friction member 61 is in the slip engagement state at the start of the vehicle in the electric travel mode, a sufficient amount of oil is supplied to the second friction member 61, This can be cooled effectively. On the other hand, only the minimum necessary oil is supplied to the first friction member 41 via the lead-out oil passage P1c and the communication oil passage 93, so that the drag loss that may occur in the first friction member 41 is kept small. it can. In the electric travel mode in which the internal combustion engine E is stopped, the first engagement device CL1 is generally in a released state, so the first friction member 41 of the first engagement device CL1 does not generate heat. Further, the first engagement device CL1 slips only in a short time such as when the internal combustion engine E is started. Therefore, even if the amount of oil supplied to the first friction member 41 is reduced to suppress drag loss, there is no particular problem from the viewpoint of thermal protection of the first engagement device CL1.

  In this embodiment, the support opening end portion 33 of the cylindrical support portion 31 of the rotor support member 30 is axially aligned with the coil end portion Ce on the second axial direction L2 side (second support wall 25 side) when viewed in the radial direction. It is arranged at a position overlapping L. Therefore, the oil guided to the radially outer side of the first outer cylindrical portion 52 through the third through hole 13 flows from the support opening end portion 33 toward the radially outer side, and is normally a coil end portion. Reach Ce. However, in the present embodiment, the second support wall 25 adjacent to the support opening end portion 33 in the axial direction L has a first axial direction between the support opening end portion 33 and the coil end portion Ce in the radial direction. It has the shielding protrusion 27 which protrudes toward the L1 side. The shielding protrusion 27 protrudes at least to a position overlapping with the support opening end 33 in the axial direction L when viewed in the radial direction. The shielding protrusion 27 may be formed so as to be continuous over the entire circumferential direction, or may be formed so as to be discontinuous in a partial region in the circumferential direction (for example, a region on the vertically upper side). . In this embodiment, since it has such a shielding protrusion part 27, it can prevent that the comparatively high temperature oil after cooling the 2nd friction member 61 arrives at the coil end part Ce.

  As shown in FIGS. 2 to 4, the second cooling oil passage P <b> 2 supplies oil supplied to the space on the radially inner side of the cylindrical support portion 31 to the coil end portions Ce on both sides in the axial direction L. It is an oil passage for cooling both coil end parts Ce. The second cooling oil passage P <b> 2 is formed in at least one of the cylindrical support portion 31, the core (rotor core) that constitutes the rotor Ro, and the locking holding portion 34. In the present embodiment, the second cooling oil passage P2 is an oil passage that extends in the radial direction from the flange portion of the cylindrical support portion 31 and communicates with the space inside the coil end portion Ce on the first axial direction L1 side in the radial direction. Included (see FIG. 2). The second cooling oil passage P2 is formed on the inner peripheral surface of the rotor core and the side surface on the rotor core side of the locking holding portion 34, and communicates with the space on the radially inner side of the coil end portion Ce on the second axial direction L2 side. Includes oilway. In the present embodiment, the second cooling oil passage P2 corresponds to the “cooling oil passage” in the present invention.

  In the present embodiment, the raised engagement portion 32 formed in the cylindrical support portion 31 is an outer peripheral portion of the first outer cylindrical portion 52 at a position that does not overlap with the third through hole 13 and the axial direction L when viewed in the radial direction. Is engaged. In this example, the first friction member 41 is engaged with the first through-hole 13 at a position overlapping with the first friction member 41 in the axial direction L as viewed in the radial direction, on the axial first direction L1 side. And the inlet In of the 2nd cooling oil path P2 provided in the cylindrical support part 31 is on the opposite side to the 3rd through-hole 13 side which pinched | interposed the protrusion engagement part 32 in the axial direction L (from the protrusion engagement part 32). Is further arranged on the first axial direction L1 side).

  In such a configuration, the oil supplied from the communication oil passage 93 flows through the raised engagement portion 32 along the cylindrical support portion 31 to the third through hole 13 side (second axial direction L2 side). It can function as a regulating weir. Therefore, the oil supplied from the communication oil passage 93 can be efficiently guided to the second cooling oil passage P <b> 2 through the inlet In formed in the cylindrical support portion 31. As a result, the coil end portion Ce can be efficiently cooled. In addition, the oil supplied from the third through hole 13 flows through the raised engagement portion 32 along the cylindrical support portion 31 to the inlet In side (the first axial direction L1 side) of the second cooling oil passage P2. It can also function as a weir that regulates Therefore, it can suppress that the comparatively high temperature oil which flows into the 3rd through-hole 13 side with respect to the protrusion engagement part 32 is supplied to the coil end part Ce through the 2nd cooling oil path P2. As described above, since the coil end portion Ce is shielded from the relatively high temperature oil discharged from the first cooling oil passage P1 by the shielding protrusion 27, the coil protrusion portion Ce is supplied through the second cooling oil passage P2. The cooling performance of the coil end portion Ce by the oil is appropriately ensured.

4). Other Embodiments Finally, other embodiments of the vehicle drive device according to the present invention will be described. Note that the configurations disclosed in the following embodiments can be applied in combination with the configurations disclosed in other embodiments as long as no contradiction arises.

(1) In the above embodiment, the configuration in which the circumferential center of the third through hole 13 and the circumferential center of the fourth through hole 14 are in phase has been described as an example. However, the embodiment of the present invention is not limited to this. While the fourth through hole 14 and the third through hole 13 are arranged at positions overlapping in the axial direction L when viewed in the radial direction, their circumferential centers may be in different phases. For example, as shown in FIG. 6, the circumferential center of the third through-hole 13 is shifted in the negative rotation direction of the first outer cylindrical portion 52 with respect to the circumferential center of the fourth through-hole 14. The positions of the third through hole 13 and the fourth through hole 14 may be set. Here, the rotation direction of the first outer cylindrical portion 52 for rotating the wheel W in the forward direction of the vehicle is defined as the “forward rotation direction”. The “negative rotation direction” of the first outer cylindrical portion 52 is a direction opposite to the positive rotation direction, and is a rotation direction for rotating the wheel W in the reverse direction of the vehicle. Considering the relationship between the time required for oil circulation and the rotation of the first outer cylindrical portion 52, the fourth through hole 14 and the third through hole 13 are provided in this positional relationship, so that the vehicle advances. During traveling, the oil flowing through the fourth through hole 14 can be more smoothly guided to the third through hole.

(2) In the above embodiment, the fourth through hole 14 (one form of “radial communication portion”) is formed in the pressing cylindrical portion 58 of the first pressing member 57, and the derived oil of the first cooling oil passage P1. The configuration in which the path P1c is formed to extend in the radial direction through the fourth through hole 14 has been described as an example. However, the embodiment of the present invention is not limited to this. An example of this case will be described with reference to FIG. In this example, the first engagement device CL1 includes a first sliding holding portion 44 that is slidably provided between the first pressing member 57 and the first friction member 41 and holds them. Yes. The first sliding holding portion 44 is a member that is directly pressed by the first pressing member 57 and corresponds to a “pressed member” in the present invention. The first sliding holding portion 44 has a radial groove portion 16 communicating in the radial direction on the side surface (contact surface 44e with the first pressing member 57) on the second axial direction L2 side. In this example, the radial groove 16 corresponds to the “radial communication portion” in the present invention. The radial groove 16 is a groove having a rectangular cross section formed with a predetermined width in the axial direction L and the circumferential direction (see FIG. 8). In this example, the shapes of the third through hole 13 and the radial groove portion 16 are set so that the longitudinal direction of the third through hole 13 and the longitudinal direction of the radial groove portion 16 intersect (orthogonal in this example). Yes.

  The open end 48, the radial groove 16, and the third through-hole 13 are arranged at positions overlapping each other in the axial direction L when viewed in the radial direction. An outlet oil passage P1c of the first cooling oil passage P1 is formed so as to extend linearly along the radial direction through the radial groove portion 16. In this example, as shown in FIG. 8, the positions of the third through hole 13 and the radial groove portion 16 are such that the circumferential center of the third through hole 13 is in phase with the circumferential center of the radial groove portion 16. Is set. The area of the third through-hole 13 is set larger than the area of the radial groove 16 (about 3 times in the illustrated example). Even if it is such a structure, the effect similar to said embodiment can be acquired.

  It should be noted that various modifications can be made to the configuration having such a radial groove portion 16. For example, the radial groove portion 16 may be formed inside the first sliding holding portion 44 or may be formed on the contact surface 57 e of the first pressing member 57 with the first sliding holding portion 44. . When the first sliding holding portion 44 is not provided, the radial groove portion 16 is formed on the contact surface of the first inner friction member 42 or the first outer friction member 43 with the first pressing member 57. May be. In this case, the first inner friction member 42 or the first outer friction member 43 corresponds to the “pressed member” in the present invention. The radial groove 16 may be simultaneously formed in two or more of the first pressing member 57, the first sliding holding portion 44, and the first inner friction member 42 or the first outer friction member 43. . For example, as shown in FIG. 9, the circumferential center of the third through-hole 13 is shifted in the negative rotation direction of the first outer cylindrical portion 52 with respect to the circumferential center of the radial groove portion 16. In addition, the positions of the third through hole 13 and the radial groove 16 may be set. Or the 4th through-hole 14 and the radial direction groove part 16 may be formed simultaneously.

(3) In the above embodiment, the configuration in which the area of the third through hole 13 is set larger than the area of the fourth through hole 14 has been described as an example. However, the embodiment of the present invention is not limited to this. For example, the area of the third through hole 13 may be set equal to the area of the fourth through hole 14. Alternatively, a configuration in which the area of the third through hole 13 is set to be smaller than the area of the fourth through hole 14 is also possible.

(4) In the above embodiment, at least in the released state of the first engagement device CL1, the opening end 48, the fourth through hole 14, and the third through hole 13 are axially L with respect to each other when viewed in the radial direction. The configuration arranged at the overlapping position has been described as an example. However, the embodiment of the present invention is not limited to this. For example, even in the engaged state of the first engagement device CL1, they may overlap with each other in the axial direction L when viewed in the radial direction.

(5) In the above embodiment, the configuration in which the shielding protrusion 27 that protrudes toward the first axial direction L1 side is provided on the second support wall 25 has been described as an example. However, the embodiment of the present invention is not limited to this. For example, the support opening end portion 33 of the cylindrical support portion 31 does not overlap in the axial direction L with the coil end portion Ce on the axial second direction L2 side when viewed in the radial direction. It may be arranged at a position on the L2 side. Alternatively, the locking holding portion 34 provided on the radially outer side of the cylindrical support portion 31 does not overlap with the coil end portion Ce on the second axial direction L2 side in the radial direction when viewed in the radial direction. Furthermore, you may have the 2nd shielding protrusion part which protrudes to the position of the axial second direction L2 side. It is also possible to use the shielding protrusion 27 of the second support wall 25 and the second shielding protrusion of the locking holding part 34 in combination. In this case, from the viewpoint of preventing the oil from the first cooling oil passage P1 from reaching the coil end portion Ce, the second shielding projection of the latch holding portion 34 is at least a shielding projection as viewed in the radial direction. 27 may be formed so as to protrude to a position overlapping with 27 in the axial direction L.

(6) In the above-described embodiment, the configuration in which the first inner cylindrical portion 46 is a non-porous cylindrical portion (continuous cylindrical portion) that does not have a radial through hole has been described as an example. However, the embodiment of the present invention is not limited to this. The first inner cylindrical portion 46 may have a through hole that penetrates in the radial direction at a position overlapping with the first friction member 41 in the axial direction L when viewed in the radial direction. Such through-holes only need to have a cross-sectional area capable of supplying a minimum amount of oil required for cooling the first friction member 41. The through hole is a small hole having a small (for example, negligibly small) cross-sectional area as compared with the first through hole 11, the second through hole 12, the third through hole 13, and the fourth through hole 14. It can be.

(7) In the above embodiment, the first inner cylindrical portion 46, the first outer cylindrical portion 52, the second inner cylindrical portion 66, the second outer cylindrical portion 72, the input shaft I, and the intermediate shaft M. The connection relationship with the rotating electrical machine MG has been described with a specific structure. However, the embodiment of the present invention is not limited to this. If the structure in which the first engagement device CL1, the rotating electrical machine MG, and the second engagement device CL2 are provided in this order on the power transmission path T that connects the input shaft I and the intermediate shaft M is possible, It is also possible to adopt a connecting structure other than the above. For example, the first outer cylindrical portion 52 and the input shaft I are connected, the first inner cylindrical portion 46 and the second inner cylindrical portion 66 are connected, and the first inner cylindrical portion 46 and the second inner cylindrical portion are connected. The rotary electric machine MG may be connected to the shape portion 66, and the second outer cylindrical portion 72 and the intermediate shaft M may be connected.

(8) In the above embodiment, the case where the vehicle drive device 1 has a multi-axis configuration suitable for being mounted on an FF (Front Engine Front Drive) vehicle has been described as an example. However, the embodiment of the present invention is not limited to this. That is, for example, the output shaft of the speed change mechanism TM may be arranged on the same axis as the input shaft I and the intermediate shaft M, and may be a single-shaft vehicle drive device 1 that is directly connected to the differential gear device DF. The vehicle drive device 1 having such a configuration is suitable when mounted on an FR (Front Engine Rear Drive) vehicle.

(9) Regarding other configurations as well, the embodiments disclosed herein are illustrative in all respects, and embodiments of the present invention are not limited thereto. In other words, configurations that are not described in the claims of the present application can be modified as appropriate without departing from the object of the present invention.

  The present invention can be used in a drive device for a so-called one-motor parallel type hybrid vehicle.

1: Vehicle drive device 2: Case 11: First through hole 12: Second through hole 13: Third through hole 14: Fourth through hole (radial direction communication portion)
16: Radial groove (radial communication part)
25: Second support wall (case wall)
27: Shielding protrusion 30: Rotor support member 31: Cylindrical support portion 32: Raised engagement portion 33: Support opening end portion 41: First friction member 42: First inner friction member 43: First outer friction member 44: First sliding holding part (member to be pressed)
46: First inner cylindrical portion 48: Open end 52: First outer cylindrical portion 57: First pressing member (pressing member)
58: Pressing cylindrical part 61: Second friction member 62: Second inner friction member 63: Second outer friction member 66: Second inner cylindrical part 72: Second outer cylindrical part E: Internal combustion engine MG: Rotating electric machine Ro: Rotor Ce: Coil end I: Input shaft (input member)
M: Intermediate shaft (output member)
CL1: First engaging device CL2: Second engaging device W: Wheel P2: Second cooling oil passage (cooling oil passage)

Claims (12)

In order from the input member side, a first engagement device, a rotating electrical machine, and a second engagement device are connected to a power transmission path that connects an input member that is drivingly connected to the internal combustion engine and an output member that is drivingly connected to the wheels. A vehicle drive device comprising:
The first engagement device is disposed on the radially inner side of the first friction member including a first inner friction member and a first outer friction member, and supports the first inner friction member. A first inner cylindrical portion, a first outer cylindrical portion that is disposed radially outside the first outer friction member and supports the first outer friction member, and presses the first friction member in the axial direction. A pressing member,
The second engagement device is disposed on the radially inner side of the second friction member including a second inner friction member and a second outer friction member, and supports the second inner friction member. A second inner cylindrical portion, and a second outer cylindrical portion disposed on the radially outer side of the second outer friction member and supporting the second outer friction member,
The first inner cylindrical portion is disposed on a radially outer side than the second outer cylindrical portion,
The second inner cylindrical portion has a first through hole penetrating in the radial direction at a position overlapping with the second friction member in the axial direction when viewed in the radial direction,
The second outer cylindrical portion has a second through hole penetrating in the radial direction at a position overlapping with the second friction member in the axial direction when viewed in the radial direction,
The first outer cylindrical portion has a third through hole penetrating in the radial direction,
The first inner cylindrical portion has an opening end that opens in a counter-pressing direction that is opposite to the pressing direction of the first friction member by the pressing member;
The vehicle drive device in which the opening end portion and the third through hole are arranged at positions overlapping in the axial direction when viewed in the radial direction. At least one of the pressing member and a member to be pressed that is directly pressed by the pressing member has a radial communication portion that communicates in the radial direction,
2. The vehicle drive according to claim 1, wherein the opening end portion and the radial direction communication portion are arranged at positions overlapping in the axial direction when viewed in the radial direction at least in a released state of the first engagement device. apparatus.   3. The apparatus according to claim 2, wherein at least in the released state of the first engagement device, the radial communication portion and the third through hole are arranged at positions overlapping in the axial direction when viewed in the radial direction. Vehicle drive device.   The vehicle drive device according to claim 2 or 3, wherein an area of the third through hole is set to be larger than a cross-sectional area of the radial communication portion.   The position of the said 3rd through-hole and the said radial direction communication part is set so that the circumferential direction center of the said 3rd through-hole may become the same phase as the circumferential direction center of the said radial direction communication part. The vehicle drive device according to any one of the above. The rotation direction of the first outer cylindrical portion for rotating the wheel in the forward direction of the vehicle is a normal rotation direction,
The third through hole and the radial communication so that the circumferential center of the third through hole is in a phase shifted in a direction opposite to the normal rotation direction with respect to the circumferential center of the radial communication portion. The vehicle drive device according to any one of claims 2 to 4, wherein the position of the portion is set. The pressing member has a pressing cylindrical portion extending in the axial direction,
The vehicle drive device according to any one of claims 2 to 6, wherein the radial communication portion includes a fourth through hole penetrating the pressing cylindrical portion in the radial direction.   A diameter formed so that the radial communication portion extends in a radial direction on at least one of a contact surface of the pressing member with the pressed member and a contact surface of the pressed member with the pressing member. The vehicle drive device according to any one of claims 2 to 7, including a directional groove.   With the first engagement device and the second engagement device overlapping each other in the axial direction when viewed in the radial direction, the stator and the stator when viewed in the radial direction inside the stator of the rotating electrical machine The vehicle drive device according to any one of claims 1 to 8, wherein the vehicle drive device is disposed at a position overlapping in an axial direction. The first inner cylindrical portion and the input member are connected to the first friction member on the pressing direction side,
The second inner cylindrical portion and the output member are connected to the second friction member on the pressing direction side,
The first outer cylindrical portion and the second outer cylindrical portion are connected to the connecting portion between the second inner cylindrical portion and the output member on the side opposite to the pressing direction,
The vehicular drive apparatus according to any one of claims 1 to 9, wherein the first outer cylindrical portion and the rotor of the rotating electrical machine are coupled to each other on the radially outer side of the first outer cylindrical portion. A rotor support member that supports the rotor of the rotating electrical machine, and the rotor support member includes a cylindrical support portion that supports the rotor from a radially inner side;
The cylindrical support portion protrudes radially inward from the inner peripheral surface of another portion of the cylindrical support portion and does not overlap with the third through hole in the axial direction when viewed in the radial direction. A raised engagement portion that engages with the outer periphery of the first outer tubular portion at a position;
The cylindrical support portion further supplies oil supplied from the radially inner side to the side opposite to the third through hole side sandwiching the raised engagement portion in the axial direction, and the coil end portion of the stator of the rotating electrical machine The vehicle drive device according to claim 1, further comprising an inlet of a cooling oil passage that leads to the vehicle. A case having a case wall extending in the radial direction adjacent to the rotating electrical machine, the first engagement device, and the second engagement device in the axial direction;
The cylindrical support portion has a support opening end portion that opens toward the case wall side in the axial direction,
The support opening end is disposed at a position overlapping the coil end portion in the axial direction when viewed in the radial direction,
The said case wall has the shielding protrusion part which protrudes to the position which overlaps at least the said support opening end part and an axial direction seeing in a radial direction between the said support opening end part and the said coil end part in radial direction. Item 12. The vehicle drive device according to Item 11.

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