JP2012097842A - Vehicle driving apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve a vehicle driving apparatus with which a partial engagement state of an engagement device can be easily achieved and the responsiveness of the engagement device can be maintained favorably.SOLUTION: The vehicle driving apparatus includes a rotating electrical machine MG and the engagement device C1 on a power transmission path which links an input member drive-coupled to an internal combustion engine and an output member drive-coupled to vehicle wheels. The engagement device C1 includes an engagement input side member 31 coupled to the input member, an engagement output side member 32 which forms a pair with the engagement input side member 31 and is coupled to the rotating electrical machine MG, a friction member 33 disposed between the engagement input side member 31 and the engagement output side member 32, and a pressing member 34 for pressing the friction member 33 in the pressing direction A2. A working oil pressure chamber H1 is formed between the engagement output side member 32 and the pressing member 34, and a biasing spring 35 for biasing the pressing member 34 in the pressing direction A2 when no working oil pressure is supplied to the working oil pressure chamber H1 is disposed on the exterior of the working oil pressure chamber H1.

Description

  The present invention relates to a vehicle drive device including a rotating electrical machine and an engagement device on 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 a wheel.

  As the above vehicle drive device, for example, a device described in Patent Document 1 below is already known. As shown in FIGS. 2 and 3 of Patent Document 1, in this vehicle drive device, an engagement output side member provided in an engagement device (first clutch CL1 in Patent Document 1; the same applies hereinafter). Between the (first member M11) and the pressing member (piston P), an operating hydraulic chamber (first hydraulic chamber r1) to which hydraulic pressure for operating the pressing member is supplied is formed, and the operating hydraulic chamber has an operating hydraulic chamber. An urging spring (coil spring SPRING) that urges the pressing member toward the friction member (first friction plate F1) in a state where the hydraulic pressure is not supplied is disposed in the working hydraulic pressure chamber. In the apparatus of Patent Document 1, both the hydraulic pressure supplied to the hydraulic pressure chamber and the hydraulic pressure supplied to the oil-tight second hydraulic chamber r2 formed on the opposite side of the hydraulic pressure chamber with respect to the pressing member are used. By setting it to zero, the friction member is frictionally engaged with a predetermined engagement pressure by the biasing force (elastic force) of the biasing spring, and a partial engagement state (so-called half-clutch state) can be easily realized.

  However, in the configuration in which the urging spring is arranged in the working hydraulic pressure chamber as in the device of Patent Document 1, the working hydraulic pressure is equal to the length in the pressing direction of the region occupied by the urging spring in the maximum compression state of the urging spring. The chamber volume needs to be increased. When the volume of the hydraulic oil pressure chamber increases, the time until the hydraulic oil pressure chamber is filled with the hydraulic oil increases accordingly. For this reason, the apparatus of Patent Document 1 has a problem that the responsiveness related to the engagement and release of the engagement apparatus decreases.

JP 2009-1165 A

  Therefore, it is desired to realize a vehicle drive device that can easily realize the partial engagement state of the engagement device and that can maintain good response of the engagement device.

  According to the present invention, a vehicle drive device having a rotating electrical machine and an engagement device on 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 a wheel. The engagement device includes an engagement input side member connected to the input member, an engagement output side member paired with the engagement input side member and connected to the rotating electrical machine, and the engagement input. A friction member disposed between the side member and the engagement output side member; and a pressing member that presses the friction member in a pressing direction; and the engagement input side member or the engagement output side member An operating hydraulic chamber is formed between the pressing member and an operating hydraulic pressure for supplying the operating hydraulic pressure to press the pressing member in the pressing direction, and the operating hydraulic chamber is not supplied with the operating hydraulic pressure. An urging spring for urging the pressing member in the pressing direction includes In that it is arranged outside the hydraulic chamber.

The “drive connection” means a state in which two rotating elements are connected so as to be able to transmit a driving force, and the two rotating elements are connected so as to rotate integrally, or the two The rotating element is used as a concept including a state in which the driving force is connected to be transmitted through one or more transmission members. Examples of such a transmission member include various members that transmit rotation at the same speed or a variable speed, and include, for example, a shaft, a gear mechanism, a belt, a chain, and the like. Further, as such a transmission member, an engagement device that selectively transmits rotation and driving force, for example, a friction clutch or a meshing clutch may be included.
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.

According to the above characteristic configuration, the pressing member can be operated according to the hydraulic pressure supplied to the working hydraulic chamber, and the input member and the rotating electrical machine can be selectively driven and connected by the engagement device. At this time, the pressing member is biased in the pressing direction by the biasing spring regardless of the hydraulic pressure for operation, and therefore the friction member is biased by the biasing force of the biasing spring even when the hydraulic pressure for operation is not supplied to the hydraulic pressure chamber. Can be frictionally engaged with each other with a predetermined engagement pressure, and the partial engagement state of the engagement device can be easily realized.
Further, in the above characteristic configuration, since such an urging spring is disposed outside the working hydraulic chamber, the volume of the working hydraulic chamber can be determined without considering the presence of the urging spring. That is, since it is not necessary to increase the volume of the working hydraulic chamber by providing an urging spring, the time until the working hydraulic chamber is filled with the working oil is not increased, and the engagement of the engaging device is prevented. In addition, the responsiveness related to release can be maintained well.
Therefore, it is possible to easily realize the partial engagement state of the engagement device and further to realize a vehicle drive device that can maintain the responsiveness of the engagement device well.

  Here, the engagement output side member includes an axially extending portion that extends in the axial direction so as to cover at least a radially outer side of the friction member, and an opposite direction to the pressing direction with respect to the friction member. A radially extending portion extending in the radial direction on the pressing direction side, and the working hydraulic chamber is formed on a radially inner side of the friction member, and the pressing member extends from the radially extending portion side. The urging spring is provided so as to press the friction member, and the urging spring is radially inward of the axially extending portion and radially outward of the working hydraulic chamber, and the radially extending portion and the pressing member Is preferably arranged between the two.

  According to this configuration, the pressing member provided so as to press the friction member from the radially extending portion side of the engagement output side member is biased between the radially extending portion and the pressing member. The spring can be appropriately biased in the pressing direction. Further, in this configuration, the urging spring presses the pressing member on the outer side in the radial direction of the working hydraulic chamber, so that the friction member disposed on the outer side in the radial direction of the working hydraulic chamber is also efficiently from a relatively close position. The biasing force of the biasing spring can be applied

  In addition, the engagement output side member has a fastening attachment portion formed thickly for bolting the rotor member of the rotating electrical machine integrally with the radially extending portion, and the biasing spring includes It is preferable to adopt a configuration in which the fastening mounting portion is disposed in contact with a step portion formed on the surface facing the pressing direction.

  According to this configuration, since the biasing spring is disposed in contact with the fastening attachment portion formed to be thick, the one end of the biasing spring can be stably supported by the fastening attachment portion. At this time, the biasing spring can be stably supported without adding any special parts by using a portion for fastening the rotor member of the rotating electrical machine with a bolt. Further, in this configuration, since the urging spring is disposed in contact with the step portion formed on the surface facing the pressing direction of the fastening mounting portion, when the urging spring is formed in an annular shape as a whole There is an advantage that the radial positioning of the biasing spring can be appropriately performed by the step portion.

  In addition, the pressing member has a projecting portion having an arcuate cross section that protrudes in the opposite pressing direction that is opposite to the pressing direction, and the biasing spring is disposed in contact with the projecting portion. A configuration is preferable.

  According to this configuration, the pressing member can receive the urging force of the urging spring at the projecting portion having an arcuate cross section. Therefore, the pressing member can be smoothly pressed regardless of the displacement of the contact portion between the urging spring and the pressing member accompanying the elastic deformation of the urging spring. Such a configuration is particularly effective when the urging spring has a flat side surface and is formed in a cross-sectional plate shape.

It is a schematic diagram which shows schematic structure of the drive device which concerns on embodiment. It is a fragmentary sectional view of a drive device. It is principal part sectional drawing of a drive device. It is principal part sectional drawing of a drive device. It is a principal part enlarged view in FIG.

  Embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a schematic diagram illustrating a schematic configuration of a drive device 1 according to the present embodiment. The driving device 1 is a driving device (hybrid driving device) for a hybrid vehicle that uses one or both of the internal combustion engine E and the rotating electrical machine MG as a driving force source of the vehicle. The drive device 1 is configured as a drive device for a so-called 1-motor parallel type hybrid vehicle. Hereinafter, the drive device 1 according to the present embodiment will be described in detail.

1. Overall Configuration of Drive Device First, the overall configuration of the drive device 1 according to the present embodiment will be described. As shown in FIG. 1, the driving device 1 includes an input shaft I that is drivingly connected to an internal combustion engine E as a first driving force source of the vehicle, an output shaft O that is drivingly connected to wheels W, And a rotating electrical machine MG as a second driving force source. Further, the drive device 1 includes an input clutch C1, a torque converter TC, and a speed change mechanism TM. These are arranged in the order of the input clutch C1, the rotating electrical machine MG, the torque converter TC, and the speed change mechanism TM from the input shaft I side on the power transmission path connecting the input shaft I and the output shaft O. Each of these components is housed in a case (drive device case) 3 except for a part of the input shaft I and a part of the output shaft O. In the present embodiment, the input shaft I corresponds to the “input member” in the present invention, and the output shaft O corresponds to the “output member” in the present invention.

  In the present embodiment, the input shaft I, the rotating electrical machine MG, the torque converter TC, and the output shaft O are all disposed on the axis X (see FIG. 2), and the drive device 1 according to the present embodiment. Is a uniaxial configuration suitable for mounting on an FR (Front Engine Rear Drive) type vehicle. In the following description, the directions of “axial direction”, “radial direction”, and “circumferential direction” are defined based on the axis X unless otherwise specified. Furthermore, regarding the directionality along the axial direction when paying attention to a specific part in the driving device 1, the direction toward the internal combustion engine E side (the left side in FIG. 2) which is one side in the axial direction is referred to as “first axial direction A1. The direction toward the output shaft O side (the right side in FIG. 2), which is the other side in the axial direction, is referred to as the “second axial direction A2”.

  The internal combustion engine E is a device that extracts power by being driven by combustion of fuel inside the engine. For example, various known engines such as a gasoline engine and a diesel engine can be used. In this example, an output rotation shaft such as a crankshaft of the internal combustion engine E is drivingly connected to the input shaft I via a damper device (not shown). Further, the input shaft I is drivingly connected to the rotating electrical machine MG via the input clutch C1. In the engaged state of the input clutch C1, the internal combustion engine E and the rotating electrical machine MG are drivingly connected via the input shaft I so as to rotate integrally, and in the released state of the input clutch C1, the internal combustion engine E and the rotating electrical machine MG are separated. Is done. That is, the input clutch C1 selectively drives and connects the internal combustion engine E and the rotating electrical machine MG. In the present embodiment, the input clutch C1 corresponds to the “engagement device” in the present invention.

  The rotating electrical machine MG includes a stator St and a rotor Ro, and functions as a motor (electric motor) that generates power by receiving power supply, and a generator (power generation) that generates power by receiving power supply. Function). Therefore, rotating electrical machine MG is electrically connected to a power storage device (not shown). In this example, a battery is used as the power storage device. Note that it is also preferable to use a capacitor or the like as the power storage device. The rotating electrical machine MG is powered by receiving power supplied from the battery, or supplies the battery with electric power generated by torque (driving force) output from the internal combustion engine E or the inertial force of the vehicle. The rotor Ro of the rotating electrical machine MG is drivingly connected to the pump impeller 41 of the torque converter TC via the power transmission member T.

  The torque converter TC is a device that converts the torque of one or both of the internal combustion engine E and the rotating electrical machine MG and transmits it to the intermediate shaft M. The torque converter TC includes a pump impeller 41 that is drivingly connected to the rotor Ro of the rotating electrical machine MG via the power transmission member T, a turbine runner 45 that is drivingly connected so as to rotate integrally with the intermediate shaft M, and a gap between them. Provided with a stator 48 (see FIG. 2). The torque converter TC is a kind of fluid coupling, and can transmit torque between the pump impeller 41 and the turbine runner 45 through oil (an example of fluid) filled therein. At that time, when a rotational speed difference is generated between the pump impeller 41 and the turbine runner 45, torque converted according to the rotational speed ratio is transmitted.

  The torque converter TC includes a lockup clutch C2. The lockup clutch C2 selectively drives and connects the pump impeller 41 and the turbine runner 45. In the engaged state of the lock-up clutch C2, the torque converter TC transmits the torque of one or both of the internal combustion engine E and the rotating electrical machine MG to the intermediate shaft M without passing through the internal oil. The intermediate shaft M is an input shaft (transmission input shaft) of the speed change mechanism TM.

  The speed change mechanism TM is a device that changes the rotational speed of the intermediate shaft M at a predetermined speed ratio and transmits it to the output shaft O. In this embodiment, an automatic stepped transmission mechanism that is capable of switching between a plurality of shift stages having different gear ratios is used as such a transmission mechanism TM. 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, and the like may be used. The speed change mechanism TM changes the rotational speed of the intermediate shaft M at a predetermined speed change ratio at each time point, converts torque, and transmits it to the output shaft O. The rotation and torque transmitted to the output shaft O are distributed and transmitted to the two left and right wheels W via the output differential gear unit DF. Thereby, the drive device 1 can drive the vehicle by transmitting the torque of one or both of the internal combustion engine E and the rotating electrical machine MG to the wheels W.

2. Next, the configuration of each part of the drive device 1 according to the present embodiment will be described with reference to FIGS. 3 is a partially enlarged view of the cross-sectional view of FIG. 2, and FIG. 4 is a cross-sectional view at a position different from the circumferential direction of FIG. FIG. 5 is an enlarged view of a main part in FIG.

2-1. Case As shown in FIG. 2, the case 3 is formed in a substantially cylindrical shape. In the present embodiment, the case 3 is substantially cylindrical and has a peripheral wall 4 that covers the outer side in the radial direction of the rotary electric machine MG, the input clutch C1, the torque converter TC, and the first axial direction A1 of the rotary electric machine MG and the input clutch C1. And an intermediate support wall 6 covering the second axial direction A2 side of the torque converter TC. The rotating electrical machine MG, the input clutch C1, and the torque converter TC are accommodated in the space between the end support wall 5 and the intermediate support wall 6 in the case 3. Although not shown, the speed change mechanism TM is accommodated in a space closer to the second axial direction A2 than the intermediate support wall 6.

  The end support wall 5 has a shape extending at least in the radial direction, and here is a substantially disc-shaped wall portion extending in the radial direction and the circumferential direction. A cylindrical projecting portion 11 is provided at the radial center of the end support wall 5. The cylindrical protruding portion 11 is a cylindrical protruding portion that is disposed coaxially with the axis X and is formed so as to protrude from the end support wall 5 toward the second axial direction A2. The cylindrical protrusion 11 is formed integrally with the end support wall 5. The cylindrical protrusion 11 has an axial length that is longer than the axial length of the rotor Ro. An axial center through-hole 11a (see FIG. 3 and the like) penetrating in the axial direction is formed at the central portion in the radial direction of the cylindrical protrusion 11. The input shaft I is inserted through the axial through hole 11a. Thus, the input shaft I is disposed so as to penetrate the radially inner side of the cylindrical projecting portion 11, penetrates the end support wall 5, and is inserted into the case 3.

  In the present embodiment, as shown in FIGS. 3 and 4, the first oil passage L <b> 1, the second oil passage L <b> 2, and the third oil passage L <b> 3 are formed in the cylindrical protruding portion 11. The first oil passage L1 is an oil supply passage for supplying oil to a later-described working hydraulic chamber H1 of the input clutch C1 (see FIG. 4). The second oil passage L2 is an oil supply passage for supplying oil to a circulating hydraulic chamber H2 (described later) of the input clutch C1 (see FIG. 3). The third oil passage L3 is an oil discharge passage for returning the oil discharged from the circulation hydraulic chamber H2 to an oil pan (not shown) (see FIG. 3).

  The intermediate support wall 6 has a shape extending at least in the radial direction, and here is a substantially disk-shaped wall portion extending in the radial direction and the circumferential direction. In the present embodiment, the intermediate support wall 6 is configured as a separate member from the peripheral wall 4, and is fastened and fixed to a step portion formed on the inner peripheral surface of the peripheral wall 4 by a fastening member such as a bolt. An oil pump 9 is provided on the intermediate support wall 6. The pump rotor of the oil pump 9 is drivingly connected so as to rotate integrally with the pump impeller 41 via a pump driving shaft 43. As the pump impeller 41 rotates, the oil pump 9 discharges oil and generates hydraulic pressure for supplying the oil to each part of the drive device 1.

2-2. Rotating electrical machine As shown in FIG. 2, the rotating electrical machine MG is disposed closer to the second axial direction A2 than the end support wall 5 and closer to the first axial direction A1 than the torque converter TC. The rotating electrical machine MG is disposed on the radially outer side with respect to the input shaft I and the input clutch C1. The rotating electrical machine MG and the input clutch C1 are arranged at positions having overlapping portions when viewed in the radial direction. Regarding the arrangement of the two members, “having overlapping portions when seen in a certain direction” means that the two members when the viewpoint is moved in each direction orthogonal to the line-of-sight direction with the direction as the line-of-sight direction. This means that the viewpoints that appear to overlap each other exist in at least some areas. The stator St of the rotating electrical machine MG is fixed to the case 3. A rotor Ro is arranged on the radially inner side of the stator St. The rotor Ro is opposed to the stator St with a small gap in the radial direction, and is supported by the case 3 in a rotatable state. Specifically, the rotor support member 22 that supports the rotor Ro and rotates integrally with the rotor Ro is rotatably supported with respect to the cylindrical protrusion 11 of the case 3 via the first bearing 61. Yes. In the present embodiment, the rotor Ro and the rotor support member 22 that rotate integrally constitute a “rotor member” in the present invention.

  As shown in FIGS. 2 to 4, the rotor support member 22 is a member that supports the rotor Ro of the rotating electrical machine MG from the inside in the radial direction. The rotor support member 22 is disposed on the first axial direction A1 side with respect to the input clutch C1. The rotor support member 22 is formed in a shape extending at least in the radial direction so as to support the rotor Ro with respect to the first bearing 61 disposed on the radially inner side of the rotor Ro. In the present embodiment, the rotor support member 22 includes a rotor holding portion 23, a radially extending portion 24, and a support cylindrical portion 25.

  The rotor holding part 23 is a part that holds the rotor Ro. The rotor holding part 23 is disposed coaxially with the axis X, and is formed in a substantially cylindrical shape so as to be in contact with the inner peripheral surface and both axial side surfaces of the rotor Ro. The radially extending portion 24 is formed integrally with the rotor holding portion 23 and is formed to extend radially inward from the vicinity of the central portion of the rotor holding portion 23 in the axial direction. In this example, the radially extending portion 24 is an annular plate-like portion extending in the radial direction and the circumferential direction. In addition, first bolt insertion holes 24 a are provided at a plurality of locations in the circumferential direction of the radially extending portion 24. A first bolt 71 for fastening the rotor support member 22 and the cylindrical connecting member 32 is inserted through the first bolt insertion hole 24a.

  A support cylindrical portion 25 is integrally provided at the radially inner end of the radially extending portion 24. The support cylindrical portion 25 is a cylindrical portion that is arranged coaxially with the axis X and is formed so as to extend on both sides in the axial direction with respect to the radially extending portion 24. In the present embodiment, the first bearing 61 is disposed in contact with the inner peripheral surface of the support cylindrical portion 25, and is disposed between the inner peripheral surface of the support cylindrical portion 25 and the outer peripheral surface of the cylindrical protruding portion 11. The rotor support member 22 is supported by the first bearing 61. Thereby, the rotor support member 22 is supported on the outer peripheral surface of the cylindrical protrusion 11 in a rotatable state via the first bearing 61. In the present embodiment, a seal member is disposed between the support cylindrical portion 25 and the cylindrical protrusion 11 on the first axial direction A1 side with respect to the first bearing 61. Thereby, between the support cylindrical part 25 and the cylindrical protrusion part 11 is sealed.

  In the present embodiment, the rotation sensor 13 that detects the rotational position of the rotor Ro relative to the stator St of the rotating electrical machine MG is provided on the outer peripheral surface of the support cylindrical portion 25. The rotation sensor 13 is disposed between the end support wall 5 and the rotor support member 22 (here, mainly the radially extending portion 24) in the axial direction. In other words, the end support wall 5 is disposed on the opposite side of the rotation sensor 13 from the rotor support member 22 in the axial direction. As the rotation sensor 13, a resolver is used in this example.

2-3. Input clutch The input clutch C1 is a friction engagement device that selectively drives and connects the input shaft I to the rotating electrical machine MG and the torque converter TC. The input clutch C1 is configured as a wet multi-plate clutch mechanism. As shown in FIG. 2, the input clutch C <b> 1 is disposed between the rotor support member 22 and the torque converter TC in the axial direction. Further, the input clutch C1 is disposed between the cylindrical protrusion 11 and the rotor Ro of the rotating electrical machine MG in the radial direction. The cylindrical projecting portion 11, the input clutch C1, and the rotor Ro are arranged so as to have portions that overlap each other when viewed in the radial direction. The input clutch C1 includes a clutch hub 31, a cylindrical connecting member 32, a friction member 33, a piston 34, and a working hydraulic pressure chamber H1.

  The input clutch C <b> 1 has a pair of input side friction member and output side friction member as the friction member 33. Here, the input clutch C1 has a plurality of input side friction members and a plurality of output side friction members, which are alternately arranged in the axial direction. The plurality of friction members 33 are all formed in an annular plate shape, and are arranged between the clutch hub 31 and the cylindrical connecting member 32.

  The clutch hub 31 is an annular plate-like member extending in the radial direction so as to support a plurality of input-side friction members (in this example, the hub-side friction member) from the radially inner side. The clutch hub 31 is formed so as to extend in the radial direction between the piston 34 and a cover portion 42 described later of the torque converter TC in the axial direction, and a radially inner end portion of the clutch hub 31 is an input shaft. I. Thereby, the input shaft I and the clutch hub 31 are connected so as to rotate integrally. The clutch hub 31 is a member to which the rotation and torque of the internal combustion engine E are transmitted via the input shaft I, and is an input side rotation member of the input clutch C1. In the present embodiment, the clutch hub 31 corresponds to the “engagement input side member” in the present invention.

  The cylindrical connecting member 32 covers at least the radially outer side of the plurality of friction members 33 and has a substantially cylindrical shape formed so as to support the output-side friction member (in this example, the drum-side friction member) from the radially outer side. It is a member. The cylindrical connecting member 32 is configured to function as a clutch drum of the input clutch C1. Moreover, the cylindrical connection member 32 has a part formed in a bowl shape as a whole so as to further cover the first axial direction A1 side of the piston 34 and the radially outer side of the piston 34. The cylindrical connecting member 32 is connected to the rotor support member 22 of the rotating electrical machine MG and is connected to the cover portion 42. The cylindrical connecting member 32 is paired with the clutch hub 31 and transmits the rotation and torque input to the clutch hub 31 in the engaged state of the input clutch C1 to the torque converter TC on the output shaft O side. It is an output side rotation member. In the present embodiment, the cylindrical connecting member 32 corresponds to the “engagement output side member” in the present invention.

  As shown in FIGS. 3 and 4, the cylindrical connecting member 32 as a clutch drum includes an axially extending portion 32a, a radially extending portion 32b, a cylindrical extending portion 32d, a cylindrical protruding portion 32e, and a diameter. A direction extending portion 32f is provided. The axially extending portion 32 a is formed in a cylindrical shape and is disposed coaxially with the axis X. The axially extending portion 32 a is formed in a cylindrical shape extending in the axial direction so as to cover at least the radially outer side of the friction member 33. The axially extending portion 32a is in contact with the radially extending portion 24 of the rotor support member 22 on the first axial direction A1 side and is in contact with the cover portion 42 of the torque converter TC on the second axial direction A2 side. The cover portion 42 is fitted to the axially extending portion 32a while abutting in the radial direction. The radially extending portion 32f is formed integrally with the axially extending portion 32a, and extends in the radially outward direction from the end of the axially extending portion 32a on the second axial direction A2 side. It is formed in a plate shape.

  The radially extending portion 32b is formed integrally with the axially extending portion 32a, and is substantially circular so as to extend radially inward from the end portion on the axial first direction A1 side of the axially extending portion 32a. It is formed in an annular plate shape. The radially extending portion 32 b is disposed on the first axial direction A1 side with respect to the friction member 33. An attachment portion 32c is formed integrally with the axially extending portion 32a and the radially extending portion 32b at the connecting portion between the axially extending portion 32a and the radially extending portion 32b. The attachment portion 32 c is formed as a thick portion having a predetermined thickness in the axial direction and the radial direction, and serves as a portion for attaching the cylindrical coupling member 32 and the rotor support member 22. First bolt fastening holes to which the first bolts 71 are fastened are provided at a plurality of locations in the circumferential direction of the mounting portion 32c. In the present embodiment, the attachment portion 32c corresponds to the “fastening attachment portion” in the present invention. Further, the radially extending portion 32b includes a cylindrical tubular extending portion 32d that is integrally formed with the radially extending portion 32b and extends in the axial direction on the radially inner side of the mounting portion 32c. Have. That is, the radially extending portion 32b is formed such that the radially inner portion is offset from the radially extending portion toward the second axial direction A2 side with respect to the radially extending portion 32d. The cylindrical extending portion 32d is fitted to the support cylindrical portion 25 of the rotor support member 22 while abutting in the radial direction.

  The cylindrical projecting portion 32e is formed integrally with the radially extending portion 32b, and is formed in a cylindrical shape so as to extend from the radially inner end of the radially extending portion 32b to both sides in the axial direction. . The cylindrical protrusion 32e is disposed on the radially inner side of the friction member 33 at a position having a portion overlapping with the friction member 33 when viewed in the radial direction. Further, the cylindrical protrusion 32e has a diameter in a state of being spaced apart from the cylindrical protrusion 11 on the radial outside of the end of the cylindrical protrusion 11 of the case 3 on the second axial direction A2 side. It is arranged facing the direction. A sleeve 56 is disposed between the cylindrical protrusion 32 e and the cylindrical protrusion 11 of the case 3. That is, the sleeve 56 is disposed so as to contact the inner peripheral surface of the cylindrical projecting portion 32 e and the outer peripheral surface of the cylindrical projecting portion 11 of the case 3.

  The piston 34 that presses the friction member 33 along the pressing direction is disposed so as to be slidable along the axial direction with respect to the outer peripheral surface of the cylindrical extending portion 32d and the outer peripheral surface of the cylindrical protruding portion 32e. In the present embodiment, the piston 34 corresponds to the “pressing member” in the present invention. In the present embodiment, the piston 34 is provided so as to press the friction member 33 from the axial first direction A1 side, which is the radially extending portion 32b side. Accordingly, in this example, the second axial direction A2 coincides with the “pressing direction”, and the first axial direction A1 coincides with the “counterpressing direction”. In the present embodiment, the piston 34 has a cylindrical cylindrical extending portion 34a extending in the axial direction at a predetermined radial position. The piston 34 is formed such that the outer position on the radial direction side of the cylindrical extending portion 34a is offset to the first axial direction A1 side with respect to the radially inner portion.

  Here, the outer side in the radial direction of the cylindrical extension part 34 a of the piston 34 is a contact pressing part 34 b provided so as to be able to press the friction member 33 in contact with the friction member 33. . The contact pressing portion 34b is provided between the attachment portion 32c of the cylindrical coupling member 32 and the friction member 33 in the axial direction and at a position overlapping with these when viewed in the axial direction. Further, as shown in FIG. 5, the piston 34 has a protrusion 34 c that protrudes toward the first axial direction A <b> 1. The projecting portion 34c is formed integrally with the piston 34 in a circular arc shape in cross section. In the present embodiment, the protruding portion 34c is located at a position having a portion overlapping the cylindrical extending portion 34a when viewed in the axial direction of the connecting portion between the cylindrical extending portion 34a and the contact pressing portion 34b of the piston 34. Is formed.

  An O-ring is provided between the cylindrical extending portion 32 d of the cylindrical connecting member 32 and the cylindrical extending portion 34 a of the piston 34 and between the cylindrical protruding portion 32 e and the radially inner end of the piston 34. Etc. are arranged. As a result, the hydraulic hydraulic chamber H1 is formed as a space that is partitioned and sealed by the radially extending portion 32b, the cylindrical extending portion 32d, the cylindrical protruding portion 32e, and the piston 34. In this example, in particular, a working hydraulic chamber H1 is formed between the radially extending portion 32b and the radially inner portion of the piston 34 from the cylindrical extending portion 34a. In the present embodiment, the working hydraulic chamber H <b> 1 is formed at a position having a portion overlapping the friction member 33 on the radially inner side of the friction member 33. Oil for operating the piston 34 is supplied to the operating hydraulic chamber H1 via the first oil passage L1.

  As shown in FIG. 5, a disc spring 35 is disposed on the working hydraulic chamber H <b> 1 side (the first axial direction A <b> 1 side) with respect to the piston 34. In the present embodiment, a disc spring 35 is disposed outside the hydraulic operating chamber H1. The disc spring 35 is formed in an annular shape as a whole, and has a radially inner end positioned on the second axial direction A2 side with respect to the radially outer end. The disc spring 35 has a flat side surface and is formed in a cross-sectional plate shape. The disc spring 35 urges the piston 34 in the second axial direction A2, which is the pressing direction, regardless of the hydraulic pressure for operation supplied to the hydraulic pressure chamber H1. That is, in the present example, the disc spring 35 is disposed between the radially extending portion 32b of the cylindrical connecting member 32 and the piston 34, and the radially extending portion 32b disposed on the axial first direction A1 side. In a state where the reaction force is supported, the disc spring 35 biases the piston 34 in the second axial direction A2. Thereby, even if the hydraulic pressure is not supplied to the working hydraulic chamber H1, the disc spring 35 biases the piston 34 in the second axial direction A2. In the present embodiment, the disc spring 35 corresponds to the “biasing spring” in the present invention.

  In this embodiment, the disc spring 35 is arrange | positioned at the radial direction outer side of the working hydraulic chamber H1. The disc spring 35 is disposed on the radially inner side of the axially extending portion 32a and on the radially outer side of the working hydraulic chamber H1. Further, in this example, the disc spring 35 is configured such that the mounting portion 32c formed integrally with the radially extending portion 32b and the piston 34 are located at a position shifted to the first axial direction A1 side with respect to the working hydraulic chamber H1. It arrange | positions between the contact press parts 34b. More specifically, as shown in FIG. 5, a stepped portion 32 h is formed on a friction facing surface 32 g that faces the friction member 33 on the surface in the second axial direction A2 side of the mounting portion 32 c. . In this example, the step 32h is formed at the corner of the radially inner end of the mounting portion 32c so as to be slightly recessed toward the first axial direction A1 side with respect to the friction facing surface 32g.

  In the present embodiment, a disc spring 35 is disposed in contact with the stepped portion 32h. Here, a cylindrical inner peripheral surface continuously extending in the axial direction and the circumferential direction from the friction facing surface 32g, and a radial extension extending continuously in the radial direction and the circumferential direction from the cylindrical inner peripheral surface. Are generally referred to as a “step 32 h” in the friction facing surface 32 g. In the illustrated example, the radially extending surface is formed in a stepped shape in which the radially inner portion slightly protrudes toward the second axial direction A2. In this example, the disc spring 35 is disposed in a state where the radially outer end thereof is in contact with the stepped portion 32h. Specifically, the disc spring 35 is disposed in a state in which its radially outer end is in contact with the cylindrical inner peripheral surface and the radially inner portion of the radially extending surface. The disc spring 35 is disposed in contact with the protrusion 34 c of the piston 34. In this example, the disc spring 35 is disposed in a state in which the side surface on the axial second direction A2 side at the radially inner end thereof is in contact with the protrusion 34c.

  Further, a circulating hydraulic chamber H2 is formed on the opposite side of the piston 34 from the operating hydraulic chamber H1 (here, the second axial direction A2 side). The circulating hydraulic chamber H2 is formed as a space mainly defined by the piston 34, the axially extending portion 32a, the cover portion 42 of the torque converter TC, the cylindrical protruding portion 11, the input shaft I, and the clutch hub 31. Yes. In this embodiment, between the cylindrical protrusion part 11 and the input shaft I and between the axial direction extension part 32a and the cover part 42 are each sealed with the sealing member. Thereby, the circulating hydraulic chamber H2 is formed as a sealed space. The circulating hydraulic chamber H2 is supplied with pressure oil discharged by the oil pump 9 and adjusted to a predetermined hydraulic pressure level by a hydraulic control device (not shown) via the second oil passage L2. The oil from the circulation hydraulic chamber H2 is supplied from the third oil passage L3 via a communication oil passage formed inside the input shaft I.

2-4. Torque Converter As shown in FIG. 2, the torque converter TC is arranged on the second axial direction A2 side with respect to the rotating electrical machine MG and the input clutch C1 and on the first axial direction A1 side with respect to the intermediate support wall 6 and the speed change mechanism TM. Has been. The torque converter TC includes a pump impeller 41, a turbine runner 45, a stator 48, and a cover portion 42 that accommodates them.

  The cover part 42 is configured to rotate integrally with the pump impeller 41. Here, the pump impeller 41 is integrally provided inside the cover portion 42. Further, the cover part 42 is connected to the cylindrical connecting member 32. The cover portion 42 is drivingly connected to the rotor Ro of the rotating electrical machine MG via the cylindrical connecting member 32 and the rotor support member 22 so as to rotate integrally. Therefore, the pump impeller 41 and the cover portion 42 that rotate integrally are members to which the rotation and torque of one or both of the internal combustion engine E and the rotating electrical machine MG are transmitted, and the input side rotation member (joint input side member) of the torque converter TC. ). Further, the cover part 42 is connected to the pump drive shaft 43. The cover part 42 is drivingly connected to the pump rotor of the oil pump 9 via the pump drive shaft 43 so as to rotate integrally.

  The turbine runner 45 is disposed on the first axial direction A1 side of the pump impeller 41 so as to face the pump impeller 41. The turbine runner 45 is paired with the pump impeller 41, and transmits the rotation and torque input to the pump impeller 41 to the intermediate shaft M on the output shaft O side. ). The turbine runner 45 has a radially extending portion 46 extending in the radial direction. In the present embodiment, the radially extending portion 46 and the intermediate shaft M disposed so as to penetrate the radially extending portion 46 are spline-connected. The stator 48 is disposed between the pump impeller 41 and the turbine runner 45 in the axial direction. The stator 48 is supported on the intermediate support wall 6 via a one-way clutch 49 and a fixed shaft.

  In the present embodiment, the pump impeller 41 and the turbine runner 45 that are arranged to face each other constitute a main body of the torque converter TC. And the cover part 42 which hold | maintains the pump impeller 41 from the outside is arrange | positioned so that the turbine runner 45 may also be accommodated. That is, the cover part 42 is arrange | positioned so that the main-body part of the torque converter TC may be accommodated. In the present embodiment, the lock-up clutch C2 and the like disposed on the first axial direction A1 side with respect to the main body of the torque converter TC are also accommodated in the cover 42.

2-5. Power transmission member The power transmission member T is a member that transmits the power (torque) of the rotating electrical machine MG to the speed change mechanism TM on the wheel W side. In the present embodiment, the rotation and torque of the rotating electrical machine MG are transmitted to the pump impeller 41 of the torque converter TC, so that the rotation and torque are transmitted to the transmission mechanism TM via the torque converter TC. Therefore, the power transmission member T is connected so as to rotate integrally with the rotor support member 22 and the pump impeller 41 of the rotating electrical machine MG. The power transmission member T according to the present embodiment is configured by integrally connecting a cylindrical coupling member 32 as an output side rotation member of the input clutch C1 and a cover portion 42 of the torque converter TC. In the engaged state of the input clutch C1, the power transmission member T can transmit the power (torque) of both the internal combustion engine E and the rotating electrical machine MG to the wheel W side.

  The rotor support member 22 and the power transmission member T are connected by a first fastening and fixing portion F1. The first fastening and fixing portion F1 is a portion for fastening and fixing the rotor support member 22 and the cylindrical connecting member 32. In the present embodiment, the radially extending portion 24 of the rotor support member 22 and the mounting portion 32c of the cylindrical connecting member 32 are disposed in contact with each other in the axial direction. In this example, the attachment portion 32c is disposed in contact with the radially extending portion 24 from the second axial direction A2 side. These are arranged in a state where the axes of the plurality of first bolt insertion holes 24a provided in the radially extending portion 24 and the axes of the plurality of first bolt fastening holes provided in the mounting portion 32c all coincide. Has been. The first bolts 71 are inserted into the first bolt insertion holes 24a and fastened to the first bolt fastening holes. Thereby, the radial direction extension part 24 and the attachment part 32c are mutually fastened and fixed by the 1st volt | bolt 71, and the 1st fastening fixing part F1 is comprised by the fastening site | part between the radial direction extension part 24 and the attachment part 32c. Is done. In this example, the first bolt 71, the first bolt insertion hole 24a, and the first bolt fastening hole are arranged in a distributed manner in the circumferential direction at the same radial position. Therefore, the “first fastening and fixing portion F1” is used as a term that collectively refers to the plurality of sets.

  In the present embodiment, the outer peripheral surface of the support cylindrical portion 25 and the inner peripheral surface of the cylindrical extending portion 32d are fitted while being in contact with each other over the entire circumferential direction. Thereby, the mutual positioning of the radial direction of the rotor support member 22 and the cylindrical connection member 32 is performed.

  The cylindrical connecting member 32 and the cover part 42 constituting the power transmission member T are connected by a second fastening and fixing part F2. The second fastening and fixing portion F2 is a portion for fastening and fixing the cylindrical connecting member 32 and the cover portion 42. In the present embodiment, the radially extending portion 32 f of the cylindrical connecting member 32 and the portion extending in the radial direction of the cover portion 42 are fastened and fixed to each other by the second bolt 72. Thereby, the 2nd fastening fixing | fixed part F2 is comprised by the fastening site | part between the radial direction extension part 32f and the cover part 42. FIG.

  As shown in FIG. 2 and the like, the rotor support member 22 and the power transmission member T (that is, the rotor support member 22 that rotates integrally, the cylindrical connecting member 32, and the cover portion 42) rotate integrally. Then, in the state which can rotate via the 1st bearing 61, it is supported by the outer peripheral surface of the cylindrical protrusion part 11 formed integrally with the edge part support wall 5 in radial direction. As the first bearing 61, a bearing capable of receiving a relatively large radial load is used, and in this example, a ball bearing is used. On the other hand, the rotor support member 22 and the power transmission member T, which rotate integrally, have a diameter on the inner peripheral surface of the through hole of the intermediate support wall 6 in a state where the rotor support member 22 and the power transmission member T can rotate via the second bearing 62 on the second axial direction A2 side. Supported in the direction. As the second bearing 62, a bearing capable of receiving a radial load is used, and in this example, a needle bearing is used.

  Further, the input shaft I arranged in a state of penetrating the cylindrical protruding portion 11 of the end support wall 5 is in a state that it can be rotated via the third bearing 63 and has a diameter on the inner peripheral surface of the cylindrical protruding portion 11. Supported in the direction. As the third bearing 63, a bearing capable of receiving a radial load is used, and in this example, a needle bearing is used. In the present embodiment, the input shaft I is connected to the cylindrical projecting portion 11 via two third bearings 63 that are separated from each other by a predetermined distance in the axial direction along the inner peripheral surface of the cylindrical projecting portion 11. It is supported by the inner peripheral surface of.

3. Torque transmission mode in the input clutch C1 Next, a torque transmission mode in the input clutch C1 according to the present embodiment will be described. Here, when the pump is in a state where the oil pump 9 is stopped, and when the oil pump 9 is driven by one or both of the internal combustion engine E and the rotating electrical machine MG as a driving force source. It will be described separately.

3-1. When the pump is stopped When both the internal combustion engine E and the rotating electrical machine MG are stopped, the oil pump 9 is also stopped, and the oil pump 9 does not discharge oil. In this state, the hydraulic pressure supplied to both the working hydraulic chamber H1 and the circulating hydraulic chamber H2 of the input clutch C1 is substantially zero. Therefore, the hydraulic pressure hardly acts on the piston 34 from both sides in the axial direction. However, in the present embodiment, the disc spring 35 is disposed between the radially extending portion 32b (attachment portion 32c) of the cylindrical coupling member 32 and the piston 34 as described above, and the disc spring 35 is a piston. 34 is urged in the second axial direction A2. Therefore, even when the oil pump 9 is stopped, the piston 34 can frictionally engage the plurality of friction members 33 with a predetermined engagement pressure by the biasing force of the disc spring 35. Therefore, the input clutch C1 is connected to the input shaft I and the power transmission member T by the biasing force of the disc spring 35 even when the oil pump 9 is stopped and no oil is supplied to both the working hydraulic chamber H1 and the circulating hydraulic chamber H2. Torque transmission between the two is possible. That is, the input clutch C1 according to the present embodiment is configured as a kind of so-called normal close type friction engagement device.

  As shown in FIG. 5, in the present embodiment, the disc spring 35 is in contact with the stepped portion 32 h provided on the mounting portion 32 c at the radially outer end, and at the axial second end A2 side at the radially inner end. The side surface is disposed in contact with the protrusion 34 c of the piston 34. Thus, in this embodiment, since the disc spring 35 is disposed in contact with a part of the attachment portion 32c formed thick, one end of the disc spring 35 (in this example, the radial direction) is arranged by the attachment portion 32c. The outer end portion) can be stably supported. At this time, using the mounting portion 32c, which is a part for fastening and fixing the rotor support member 22 and the cylindrical connecting member 32 of the rotating electrical machine MG with the first bolt 71, the dish is added without adding any special parts. The spring 35 can be stably supported. Further, in the present embodiment, since the disc spring 35 is disposed in contact with the stepped portion 32h formed on the friction facing surface 32g of the mounting portion 32c, the radial direction of the disc spring 35 formed in an annular shape as a whole is arranged. Positioning can be performed appropriately.

  In the present embodiment, the protrusion 34c formed in the piston 34 is disposed in a state in which the side surface on the axial second direction A2 side at the radially inner end of the disc spring 35 is in contact with the protrusion 34c. The disc spring 35 is elastically deformed or the piston 34 moves in the axial direction by the action of the hydraulic pressure supplied to the working hydraulic chamber H1, regardless of the displacement of the contact portion between the disc spring 35 and the piston 34. The piston 34 can be smoothly pressed. Furthermore, in the present embodiment, the protrusion 34c is formed at a radial position equal to the cylindrical extending portion 34a of the piston 34 on the radially outer side of the working hydraulic chamber H1, and therefore, more than the contact pressing portion 34b. The biasing force of the disc spring 35 can be applied to the piston 34 at a close radial position. Therefore, the urging force of the disc spring 35 can be efficiently applied to the friction member 33 arranged on the radially outer side of the hydraulic operating chamber H1.

  In the present embodiment, the magnitude of the urging force of the disc spring 35 is predetermined in a state where no oil is supplied to the working hydraulic chamber H1 of the input clutch C1 and no oil is supplied to the circulating hydraulic chamber H2. It is set in advance so that the size is within the range. Here, the “size within a predetermined range” is a range that is equal to or greater than a first limit threshold T1 described below and equal to or less than a second limit threshold T2. The first limit threshold T1 is a state in which the torque of the internal combustion engine E is transmitted to the oil pump 9 via the input clutch C1 in a state where the oil is not supplied to both the working hydraulic chamber H1 and the circulating hydraulic chamber H2. The lower limit value of the urging force (load) is set such that the pump 9 can be driven from a stopped state. Further, the second limit threshold T2 is assumed that the torque of the rotating electrical machine MG is transmitted to the internal combustion engine E via the input clutch C1 in a state in which no oil is supplied to both the working hydraulic pressure chamber H1 and the circulating hydraulic pressure chamber H2. Also, the upper limit value of the urging force (load) is set such that the internal combustion engine E in the stopped state can be maintained in the stopped state as it is.

  In this embodiment, since the magnitude of the biasing force of the disc spring 35 is set as described above, not only the torque of the rotating electrical machine MG but also the torque of the internal combustion engine E can be transmitted to the oil pump 9. . Therefore, the oil pump 9 can be driven using the torque of the internal combustion engine E to obtain a predetermined oil pressure, and the input clutch C1 can be engaged. Therefore, for example, even when the rotating electrical machine MG is out of order, the vehicle can be appropriately driven by the torque of the internal combustion engine E. Further, during normal operation of the rotating electrical machine MG, even when a part of the torque of the rotating electrical machine MG is transmitted to the internal combustion engine E by the biasing force of the disc spring 35 when the rotating electrical machine MG outputs torque, basically, The internal combustion engine E can be maintained in a stopped state as it is.

3-2. When the pump is driven In a state where at least one of the internal combustion engine E and the rotating electrical machine MG is driven, the oil pump 9 is also in a driving state, and the oil pump 9 discharges oil. In this state, the hydraulic pressure supplied to the working hydraulic chamber H1 and the circulating hydraulic chamber H2 of the input clutch C1 can be controlled to a predetermined magnitude via a hydraulic control device (not shown). In this example, the hydraulic pressure supplied to the circulating hydraulic chamber H2 is basically maintained at a substantially constant level regardless of the situation (hereinafter referred to as “circulating pressure Pc”) and supplied to the working hydraulic chamber H1. The hydraulic pressure is controlled based on a command value or the like from a control unit (not shown) so as to have a desired magnitude according to the situation. More specifically, the hydraulic pressure supplied to the working hydraulic chamber H1 is normally zero, and when necessary, a predetermined complete engagement pressure (the input clutch C1 is transmitted to the input clutch C1). The pressure is such that the pressure is constantly in a direct engagement state regardless of torque fluctuations.

  For example, in the state where the hydraulic pressure supplied to the working hydraulic chamber H1 remains zero and the hydraulic pressure supplied to the circulating hydraulic chamber H2 becomes the circulating pressure Pc when the vehicle travels, the piston from the second shaft direction A2 side is The circulation pressure Pc acts on the cylinder 34. Thereby, the urging force of the disc springs 35 arranged so as to press the friction members 33 against each other with a predetermined engagement pressure can be offset by the circulation pressure Pc supplied to the circulation hydraulic chamber H2. As a result, the input clutch C1 can be released. Therefore, for example, after a sufficient circulation pressure Pc is obtained after the vehicle starts, the vehicle is only driven by the torque of the rotating electrical machine MG in the so-called electric travel mode in a state where the input clutch C1 is released and the drag of the internal combustion engine E is suppressed. Can be run. In addition, a preliminary operation for starting the vehicle by the driver is detected, and based on the detection result, the oil pump 9 is driven by the torque of the rotating electrical machine MG before starting the vehicle to release the input clutch C1. A configuration in which the vehicle is actually started with the input clutch C1 released is also suitable.

  Further, for example, when the hydraulic pressure supplied to the hydraulic pressure chamber H1 rises and becomes larger than a predetermined pressure when the vehicle is traveling, for example, the hydraulic pressure supplied to the hydraulic pressure chamber H1 causes the shaft 34 By canceling the circulating pressure Pc acting from the two-direction A2 side, the piston 34 can be further pressed toward the second axial direction A2 side, and the plurality of friction members 33 can be pressed together. As a result, the input clutch C1 can be engaged. Therefore, the torque of the internal combustion engine E is transmitted to the wheels W with the input clutch C1 engaged in a situation where the driving force required to drive the vehicle becomes very large, for example, when traveling on an uphill. In a possible state, the vehicle can be appropriately driven by the torque of both the internal combustion engine E and the rotating electrical machine MG in a so-called parallel running mode.

  Note that when the mode is switched from the electric travel mode to the parallel travel mode, internal combustion engine start control is performed in which the internal combustion engine E is cranked and started by the torque of the rotating electrical machine MG transmitted via the input clutch C1. In this internal combustion engine start control, in order to start the internal combustion engine E quickly at a desired timing, a high control response is required with respect to the engagement and release of the input clutch C1.

  By the way, if the disc spring 35 is disposed in the working hydraulic chamber H1, it is necessary to increase the volume of the working hydraulic chamber H1 by the axial length of the region occupied by the disc spring 35. As the volume of the hydraulic oil pressure chamber H1 increases, the time required for the hydraulic oil pressure chamber H1 to be filled with oil increases accordingly, so that the responsiveness related to the engagement and release of the input clutch C1 decreases. In this regard, in the present embodiment, the disc spring 35 is arranged outside the working hydraulic chamber H1 instead of inside the working hydraulic chamber H1. Therefore, the volume of the working hydraulic chamber H1 can be determined without considering the presence of the disc spring 35. That is, even when the disc spring 35 is provided to urge the piston 34 in the second axial direction A2, which is the pressing direction, there is no need to increase the volume of the working hydraulic chamber H1. Therefore, in the drive device 1 according to the present embodiment, it is possible to satisfactorily maintain the responsiveness related to the engagement and release of the input clutch C1.

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 are not applied only in the embodiments, and can be applied in combination with the configurations disclosed in other embodiments as long as no contradiction arises. It is.

(1) In the above-described embodiment, the friction facing surface 32g of the mounting portion 32c abuts on the stepped portion 32h formed so as to be recessed toward the first axial direction A1 side with respect to the friction facing surface 32g. The case where 35 is arranged has been described as an example. However, the embodiment of the present invention is not limited to this. That is, for example, a protruding portion that protrudes toward the second axial direction A2 with respect to the friction facing surface 32g of the mounting portion 32c is formed, and the disc spring 35 is disposed in contact with the protruding portion and the friction facing surface 32g. This is also a preferred embodiment of the present invention. In this case, the disc spring 35 is positioned in the radial direction by the protrusion. Alternatively, a configuration in which the disc spring 35 is disposed in contact with the axially extending portion 32a and the friction facing surface 32g without providing such a protruding portion is also one preferred embodiment of the present invention. One. In this case, the disk spring 35 is positioned in the radial direction by the axially extending portion 32a.

(2) In the above embodiment, the attachment portion 32c formed as a thick portion having a predetermined thickness in the axial direction and the radial direction integrally with the axial extension portion 32a and the radial extension portion 32b. The case where the disc springs 35 are disposed in contact with each other has been described as an example. However, the embodiment of the present invention is not limited to this. That is, without providing the attachment portion 32c having such a thickness, for example, the disc spring 35 may be disposed in contact with the side surface of the radially extending portion 32b formed in a substantially flat plate shape. This is one of the preferred embodiments of the present invention. In this case, it is preferable that the first fastening and fixing portion F1 between the rotor support member 22 and the cylindrical connecting member 32 is configured as a joint portion by welding or the like, for example.

(3) In the above embodiment, the disc spring 35 is disposed in contact with the projecting portion 34c formed integrally with the piston 34 and projecting from the piston 34 in the first axial direction A1 side. The case has been described as an example. However, the embodiment of the present invention is not limited to this. That is, it is also a preferred embodiment of the present invention that the disc spring 35 is disposed in contact with the protrusion 34c of the piston 34 having an arbitrary cross-sectional shape. Alternatively, without having such a protruding portion 34c, the piston 34 (for example, a connecting portion between the cylindrical extending portion 34a and the contact pressing portion 34b) contacts the substantially flat side surface on the first axial direction A1 side. It is also one of preferred embodiments of the present invention that the disc spring 35 is arranged. Furthermore, the disc spring 35 is arranged in contact with a concave portion having an arbitrary cross-sectional shape recessed in the second axial direction A2 side with respect to the substantially flat side surface on the first axial direction A1 side of the piston 34. Is also one preferred embodiment of the present invention.

(4) In the above embodiment, the disc spring 35 formed in an annular shape as a whole is arranged in a state where the radially inner end is positioned on the second axial direction A2 side with respect to the radially outer end. An example has been described. However, the embodiment of the present invention is not limited to this. That is, it is also preferable that the disc spring 35 has a configuration in which the radially outer end portion is disposed in the axial second direction A2 side with respect to the radially inner end portion. One of the forms. In this case, it is preferable that the shape of the radially extending portion 32b (including the attachment portion 32c) and the piston 34 is set so as to be adapted to the disc spring 35 according to the arrangement state thereof.

(5) In the above embodiment, the input clutch C1 includes the disc spring 35 to urge the piston 34 in the second axial direction A2, which is the pressing direction, even when no oil is supplied to the working hydraulic chamber H1. The case has been described as an example. However, the embodiment of the present invention is not limited to this. That is, as long as the same function as the disc spring 35 in the above-described embodiment is provided, the input clutch C1 may be provided with another biasing spring such as a coil spring. one of.

(6) In the above embodiment, the clutch hub 31 is drivingly connected so as to rotate integrally with the input shaft I, and the cylindrical connecting member 32 constituting the power transmission member T is paired with the clutch hub 31. The case where the hydraulic oil pressure chamber H1 functions as a clutch drum and is formed between the cylindrical connecting member 32 and the piston 34 has been described as an example. However, the embodiment of the present invention is not limited to this. That is, for example, the clutch drum is drivingly connected so as to rotate integrally with the input shaft I, and the clutch hub paired with the clutch drum is driven and connected so as to rotate integrally with the rotating electrical machine MG, etc. In another preferred embodiment of the present invention, the hydraulic oil pressure chamber H1 is formed between the piston 34 and the clutch drum (corresponding to the “engagement input side member”) that rotates integrally with I. is there.

(7) In the above embodiment, the case where the torque converter TC including the pump impeller 41, the turbine runner 45, and the stator 48 is provided in the drive device 1 as a fluid coupling has been described as an example. However, the embodiment of the present invention is not limited to this. That is, for example, a configuration in which the fluid coupling having only the pump impeller 41 and the turbine runner 45 without including the stator 48 is provided in the drive device 1 as a fluid coupling is also one preferred embodiment of the present invention. One. Or it is also one of the suitable embodiments of the present invention that such a fluid coupling is not provided in the drive device 1 at all.

(8) In the above-described embodiment, the case where the driving device 1 has a uniaxial configuration suitable for mounting on an FR (Front Engine Rear Drive) vehicle has been described as an example. However, the embodiment of the present invention is not limited to this. That is, for example, a drive device having a multi-shaft configuration in which a counter gear mechanism and the like are provided and an axle is arranged with a shaft center different from the common shaft center X for the input shaft I and the intermediate shaft M may be used. This is one of the preferred embodiments. The drive device having such a configuration is suitable when mounted on an FF (Front Engine Front 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. That is, as long as the configuration described in the claims of the present application and a configuration equivalent thereto are provided, a configuration obtained by appropriately modifying a part of the configuration not described in the claims is naturally also included in the present invention. Belongs to the technical scope.

  INDUSTRIAL APPLICABILITY The present invention is suitably used for a vehicle drive device including a rotating electrical machine and an engagement device on 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 a wheel. be able to.

1 Drive device (vehicle drive device)
22 Rotor support member 31 Clutch hub (engagement input side member)
32 Cylindrical connecting member (engagement output side member)
32a Axial extending portion 32b Radial extending portion 32c Mounting portion (fastening mounting portion)
32g Friction facing surface 32h Stepped portion 33 Friction member 34 Piston (pressing member)
34c Projection 35 Disc spring (biasing spring)
E Internal combustion engine MG Rotating electrical machine Ro Rotor W Wheel I Input shaft (input member)
O Output shaft (output member)
C1 input clutch (engagement device)

Claims (4)

A vehicle drive device comprising a rotating electrical machine and an engagement device on a power transmission path connecting an input member that is drivingly connected to an internal combustion engine and an output member that is drivingly connected to a wheel,
The engagement device includes an engagement input side member coupled to the input member, an engagement output side member paired with the engagement input side member and coupled to the rotating electrical machine, and the engagement input side A friction member disposed between a member and the engagement output side member; and a pressing member that presses the friction member in a pressing direction.
Between the engagement input side member or the engagement output side member and the pressing member, an operating hydraulic pressure chamber is formed to which hydraulic pressure for operation for pressing the pressing member in the pressing direction is supplied.
A vehicle drive device in which an urging spring that urges the pressing member in the pressing direction in a state where no operating hydraulic pressure is supplied to the operating hydraulic chamber is disposed outside the operating hydraulic chamber. The engagement output side member includes an axially extending portion extending in the axial direction so as to cover at least a radially outer side of the friction member, and a counter-pressing direction side opposite to the pressing direction with respect to the friction member. A radially extending portion extending in the radial direction,
The working hydraulic chamber is formed on the radially inner side of the friction member,
The pressing member is provided so as to press the friction member from the radially extending portion side,
The biasing spring is disposed between the radially extending portion and the pressing member on the radially inner side of the axially extending portion and on the radially outer side of the working hydraulic chamber. The vehicle drive device according to claim 1. The engagement output side member integrally has a fastening attachment portion formed to be thick in order to bolt the rotor member of the rotating electrical machine with the radially extending portion,
The vehicle drive device according to claim 2, wherein the urging spring is disposed in contact with a step portion formed on a surface of the fastening attachment portion facing the pressing direction. The pressing member has a projecting portion having an arc-shaped cross section that protrudes toward the opposite pressing direction that is opposite to the pressing direction.
The vehicle drive device according to any one of claims 1 to 3, wherein the biasing spring is disposed in contact with the protrusion.

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