Patent Description:
An example of the above vehicle drive device is disclosed in Patent Literature <NUM> below. The description below of the background art shows parentheses to indicate the reference signs used in Patent Literature <NUM>.

Patent Literature <NUM> discloses a device (<NUM>) including a friction clutch device (CL1) with friction members (<NUM>) and also including an outer support (<NUM>) supporting the friction members (<NUM>) from the outer side (R2) in a radial direction (R). The friction clutch device (CL1) includes a press member (<NUM>) supported by the outer support (<NUM>) in such a manner as to rotate integrally with the outer support (<NUM>). Specifically, the outer support (<NUM>) includes at an inner circumferential portion thereof a plurality of splines extending in an axial direction (L) and separated from one another in a circumferential direction (C). The press member (<NUM>) also each include similar splines at an outer circumferential portion thereof. The two sets of splines are engaged with each other, so that the press member (<NUM>) is restricted in its rotation relative to the outer support (<NUM>), and is supported by the outer support (<NUM>) in such a manner as to be slidable in the axial direction (L).

International Publication No. <CIT> (<FIG>).

<CIT> discloses an automatic transmission.

<CIT> discloses an automatic transmission and a method of providing the same.

<CIT> discloses a start-up clutch assembly.

The device (<NUM>) of Patent Literature <NUM> is configured such that the outer support (<NUM>) is open toward a first side (L1) in the axial direction (L). Producing the device (<NUM>) of Patent Literature <NUM> involves assembling the press member (<NUM>) to the outer support (<NUM>) through the opening thereof from the first side (L1) in the axial direction (L). This assembly work requires an assembler to engage the splines of the press member (<NUM>) with those of the outer support (<NUM>). If, for instance, the splines are so positioned as to be difficult to see, the assembler needs to press the press member (<NUM>) against the outer support (<NUM>) in the axial direction (L) and simultaneously rotate the press member (<NUM>) relative to the outer support (<NUM>) until the two sets of splines match in phase. This need to rotate the press member (<NUM>) to allow the two sets of splines to match in phase has made the assembly of the press member (<NUM>) troublesome.

The above circumstances have led to a demand for a vehicle drive transmission device including an easily assemblable press member and a vehicle drive device including the vehicle drive transmission device.

In view of the above, a vehicle drive transmission device characteristically includes:.

The above vehicle drive transmission device is characteristically configured such that the intermediate member includes a body and a protrusion protruding toward the first side of the body in the axial direction and that the press member has an insertion hole extending through the press member in the axial direction and configured to receive the protrusion. With the protrusion in the insertion hole, the press member is restricted in its rotation relative to the second support. The use of the protrusion and the insertion hole appropriately restricts rotation of the press member and the second support relative to each other. Further, when the press member is assembled to the intermediate member from the first side in the axial direction, the assembler is able to see, from the first side in the axial direction through the insertion hole in the press member, the protrusion to be inserted into the insertion hole. The above configuration thereby allows the assembler to easily adjust the rotation phase of the press member and insert the protrusion into the insertion hole, facilitating the assembly of the press member.

The above vehicle drive transmission device is characteristically configured such that the second support includes a cylindrical support section and a protrusion protruding from the cylindrical support section toward the first side in the axial direction and that the press member has an insertion hole extending through the press member in the axial direction and configured to receive the protrusion. With the protrusion in the insertion hole, the press member is restricted in its rotation relative to the second support. The use of the protrusion and the insertion hole appropriately restricts rotation of the press member and the second support relative to each other. Further, when the press member is assembled to the second support from the first side in the axial direction, the assembler is able to see, from the first side in the axial direction through the insertion hole in the press member, the protrusion to be inserted into the insertion hole. The above configuration thereby allows the assembler to easily adjust the rotation phase of the press member and insert the protrusion into the insertion hole, facilitating the assembly of the press member.

The description below deals with a vehicle drive device <NUM> as an embodiment with reference to drawings. As illustrated in <FIG>, the vehicle drive device <NUM> is for use to drive a vehicle including both an internal combustion engine EG and a rotary electric machine MG (that is, a hybrid vehicle). Specifically, the vehicle drive device <NUM> serves to drive a single-motor parallel hybrid vehicle.

The description below uses the terms "axial direction L", "radial direction R", and "circumferential direction C" relative to the rotation axis of the rotary electric machine MG unless otherwise specified. The description below also uses the term "radially inner side R1" to refer to that side in the radial direction R on which the rotation axis of the rotary electric machine MG is present and the term "radially outer side R2" to refer to that side in the radial direction R which is opposite to the above side.

The respective orientations of different parts described below are of those parts as assembled into the vehicle drive device <NUM>. Further, the terms related to, for example, the respective orientations and positions of different parts described below each cover in its conceptual scope a state involving a production tolerance.

As illustrated in <FIG>, the vehicle drive device <NUM> includes a vehicle drive transmission device <NUM> and a rotary electric machine MG. The vehicle drive transmission device <NUM> includes a first clutch device CL1. The vehicle drive transmission device <NUM> for the present embodiment further includes a second clutch device CL2, an input member I, a transmission TM, a counter gear mechanism CG, a differential gear mechanism DF. and a pair of output members O. The vehicle drive device <NUM> as the present embodiment includes a case <NUM> containing a portion of the input member I, a portion of each output member O, the first clutch device CL1, the second clutch device CL2, the rotary electric machine MG, the transmission TM, the counter gear mechanism CG, and the differential gear mechanism DF.

The rotary electric machine MG serves as a driving source for wheels W of the vehicle. The rotary electric machine MG serves as an electric motor configured to receive electric power and generate motive power and also as a generator configured to receive motive power and generate electric power. For that purpose, the rotary electric machine MG is electrically connected to an electricity storage device (such as a battery or capacitors). The rotary electric machine MG runs on electric power from the electricity storage device, and also supplies the electricity storage device with electric power for storage which is generated by the torque of the internal combustion engine EG or the inertial force of the vehicle.

The internal combustion engine EG serves as a driving source for the wheels W similarly to the rotary electric machine MG. The internal combustion engine EG is a prime mover drivable through fuel combustion to take out motive power (such as a gasoline engine or a diesel engine).

The input member I is drive-coupled to the internal combustion engine EG. The input member I for the present embodiment is drive-coupled to the output shaft (such as a crank shaft) of the internal combustion engine EG with a damper device (not illustrated in the drawings) therebetween that is configured to attenuate variation of torque being transmitted.

The expression "drive-coupled" as used herein refers to the state of two rotary elements being coupled to each other in such a manner as to allow transmission of driving force from one to the other. The state may be of two rotary elements being coupled to each other in such a manner as to rotate integrally or allow transmission of driving force from one to the other with one or more power transmission members therebetween. Such power transmission members are each any of various members configured to transmit rotation while keeping or varying its speed, such as a shaft, a gear mechanism, a belt, and a chain. The power transmission members may include a clutch device configured to selectively transmit rotation and driving force, such as a friction clutch device or an engaging clutch device.

The first clutch device CL1 and the second clutch device CL2 each serve to enable and disable transmission of motive power from one of two rotary elements to the other. As illustrated in <FIG>, the first clutch device CL1 and the second clutch device CL2 for the present embodiment are arranged in the axial direction L. The rotary electric machine MG and the transmission TM for the present embodiment are also arranged in the axial direction L. The second clutch device CL2 is on that side in the axial direction L on which the transmission TM is present relative to the first clutch device CL1.

The description below uses the term "axial-direction first side L1" to refer to that side in the axial direction L on which the first clutch device CL1 is present relative to the second clutch device CL2 and the term "axial-direction second side L2" to refer to that side in the axial direction L which is opposite to the axial-direction first side L1.

As illustrated in <FIG>, the first clutch device CL1 for the present embodiment is on a motive power transmission path between the input member I and the rotary electric machine MG. The first clutch device CL1 thus serves to couple the input member I and the rotary electric machine MG to each other or uncouple the input member I and the rotary electric machine MG from each other. The first clutch device CL1 for the present embodiment is controlled in terms of its engagement state (namely, direct engagement, slip engagement, or disengaged) in response to the hydraulic pressure applied to the first clutch device CL1.

The second clutch device CL2 for the present embodiment is on a motive power transmission path between the rotary electric machine MG and the transmission TM. The second clutch device CL2 serves to couple an input transmission shaft M, which is an input element of the transmission TM, and the rotary electric machine MG to each other or uncouple the input transmission shaft M and the rotary electric machine MG from each other. The second clutch device CL2 for the present embodiment is controlled in terms of its engagement state (namely, direct engagement, slip engagement, or disengaged) in response to the hydraulic pressure applied to the second clutch device CL2.

The transmission TM serves to change the speed of rotation transmitted from the rotary electric machine MG. Specifically, the transmission TM changes the speed of rotation inputted to the input transmission shaft M at the current speed-change ratio, and converts the torque inputted to the input transmission shaft M. The transmission TM then transmits the resulting rotation and torque to an output transmission gear G1, which is an output element of the transmission TM. The transmission TM for the present embodiment is an automatic stepped transmission that includes a plurality of transmission engagement devices and that is switchable between a plurality of gear positions with respective speed-change ratios different from each other. The transmission TM may alternatively be, for example, an automatic stepless transmission having a steplessly changeable speed-change ratio or a manual stepped transmission switchable between a plurality of gear positions with respective speed-change ratios different from each other.

The counter gear mechanism CG includes an input counter gear G2 and an output counter gear G3. The input counter gear G2 is an input element of the counter gear mechanism CG, and meshes with the output transmission gear G1. The output counter gear G3 is an output element of the counter gear mechanism CG, and is coupled to the input counter gear G2 in such a manner as to rotate integrally with the input counter gear G2. The output counter gear G3 for the present embodiment is coupled to the input counter gear G2 with a counter shaft S therebetween that extends in the axial direction L. The output counter gear G3 is on the axial-direction first side L1 of the input counter gear G2 as in the illustrated example.

The differential gear mechanism DF includes an input differential gear G4 that meshes with the output counter gear G3 of the counter gear mechanism CG. The differential gear mechanism DF The differential gear mechanism DF divides rotation of the input differential gear G4 and transmits the resulting rotations to the respective output members O, which are drive-coupled to the respective wheels W.

The vehicle drive device <NUM> configured as above allows the engagement state of each of the first clutch device CL1 and the second clutch device CL2 to be switched in order for either or both of the internal combustion engine EG and the rotary electric machine MG to transmit torque to the wheels W and thereby for the vehicle to travel. The vehicle drive device <NUM> as the present embodiment has a multi-axis configuration: The input member I is coaxial with the input transmission shaft M, and the pair of output members O are on a different axis and parallel to the input member I and the input transmission shaft M. The vehicle drive device <NUM> configured as such is suitable for an FF (front engine front drive) vehicle, for example.

The vehicle drive device <NUM> allows the internal combustion engine EG to be started with use of driving force of the rotary electric machine MG with the first clutch device CL1 directly engaged and the second clutch device CL2 slip-engaged to prevent the torque fluctuation at the start of the internal combustion engine EG from being transmitted to the wheels W. The expression "directly engaged" refers to an engagement state involving no rotation speed difference (slip) between a pair of friction plates of a friction clutch device. The expression "slip-engaged" refers to an engagement state involving a rotation speed difference (slip) between a pair of friction plates of a friction clutch device.

As illustrated in <FIG>, the case <NUM> for the present embodiment includes a first side wall <NUM>, a second side wall <NUM>, and a cylindrical protrusion <NUM>. The case <NUM> for the present embodiment also includes a round wall (not illustrated in the drawings) disposed between the first side wall <NUM> and the second side wall <NUM> in the axial direction L and covering the rotary electric machine MG from the radially outer side R2.

The first side wall <NUM> extends in the radial direction R, and is on the axial-direction first side L1 of the rotary electric machine MG and the first clutch device CL1. The input member I extends through the first side wall <NUM> in the axial direction L. The input member I includes on the axial-direction first side L1 of the first side wall <NUM> a portion coupled to the damper device mentioned above.

The second side wall <NUM> extends in the radial direction R, and is on the axial-direction second side L2 of the rotary electric machine MG and the second clutch device CL2. The input transmission shaft M extends through the second side wall <NUM> in the axial direction L.

The cylindrical protrusion <NUM> protrudes from the second side wall <NUM> in the axial direction L. The cylindrical protrusion <NUM> for the present embodiment protrudes from the second side wall <NUM> toward the axial-direction first side L1. Further, the cylindrical protrusion <NUM> covers the input transmission shaft M on the radially outer side R2. The cylindrical protrusion <NUM> for the present embodiment has on the axial-direction first side L1 an end portion that is on the axial-direction second side L2 of that end portion of the input member I which is on the axial-direction second side L2. The cylindrical protrusion <NUM> is, in other words, apart from the input member I in the axial direction L.

The input member I for the present embodiment includes a cylindrical input section Ia that is open toward one side in the axial direction L (for the present embodiment, the axial-direction second side L2). The input transmission shaft M includes an insert portion Ma inserted in the cylindrical input section Ia on the radially inner side R1. The input member I and the input transmission shaft M are rotatable relative to each other with the insert portion Ma in the cylindrical input section Ia.

As illustrated in <FIG>, the rotary electric machine MG includes a stator St and a rotor Ro on the radially inner side R1 of the stator St. The stator St is fixed to a non-rotatable member. The stator St for the present embodiment is fixed to the first side wall <NUM> of the case <NUM> with use of fixing members such as bolts. The stator St for the present embodiment includes a stator core Stc and a coil wound around the stator core Stc to form coil end portions Ce protruding from the stator core Stc on both sides in the axial direction L (namely, on the axial-direction first side L1 and the axial-direction second side L2). The rotor Ro is rotatable relative to the stator St. The rotor Ro for the present embodiment includes a rotor core Roc, a pair of holding members H holding the rotor core Roc on opposite sides in the axial direction L, and a permanent magnet PM inside the rotor core Roc. The stator core Stc and rotor core Roc for the present embodiment each include a plurality of ring-shaped magnetic plates (for example, electromagnetic steel plates) disposed on one another in the axial direction L.

The vehicle drive transmission device <NUM> for the present embodiment includes a rotor support <NUM> supporting the rotor Ro. The rotor support <NUM> includes a cylindrical portion <NUM> and a flange portion <NUM>.

The cylindrical portion <NUM> extends in the axial direction L, and is on the radially outer side R2 of the first clutch device CL1. The cylindrical portion <NUM> for the present embodiment is on the radially outer side R2 of the first clutch device CL1 and the second clutch device CL2. The cylindrical portion <NUM> supports the rotor Ro from the radially inner side R1, and is coupled to the rotor Ro in such a manner as to rotate integrally with the rotor Ro. The cylindrical portion <NUM> for the present embodiment has a peripheral surface to which the rotor Ro is attached. The rotor Ro is, for example, welded or swaged to the peripheral surface of the cylindrical portion <NUM> for attachment.

The flange portion <NUM> extends from the cylindrical portion <NUM> in the radial direction R toward the radially inner side R1. The flange portion <NUM> is on the axial-direction second side L2 of the first clutch device CL1. The flange portion <NUM> for the present embodiment is on the axial-direction second side L2 of the second clutch device CL2, and is adjacent to the second clutch device CL2. The flange portion <NUM> for the present embodiment is on the axial-direction first side L1 of the second side wall <NUM>. The flange portion <NUM> for the present embodiment is a ring-shaped plate extending in the radial direction R and the circumferential direction C.

The flange portion <NUM> is coupled to the cylindrical portion <NUM> in such a manner as to rotate integrally with the cylindrical portion <NUM>. The flange portion <NUM> for the present embodiment is a member separate from the cylindrical portion <NUM>, and is welded, swaged, or otherwise joined to the cylindrical portion <NUM>. The cylindrical portion <NUM> and the flange portion <NUM> are, in other words, separate members joined to each other. The flange portion <NUM> and the cylindrical portion <NUM> are, in the illustrated example, welded to each other in such a manner that the flange portion <NUM> includes on the radially outer side R2 an end portion coupled to that end portion of the cylindrical portion <NUM> which is on the axial-direction second side L2.

The first clutch device CL1 is on the radially inner side R1 of the cylindrical portion <NUM> and on the axial-direction first side L1 of the flange portion <NUM>. The rotor support <NUM> defines a space for the first clutch device CL1 on the radially inner side R1 of the cylindrical portion <NUM> and on the axial-direction first side L1 of the flange portion <NUM>. The rotor support <NUM> is thus in the shape of a bottomed cylinder that is open toward the axial-direction first side L1. The second clutch device CL2 for the present embodiment is between the first clutch device CL1 and the flange portion <NUM> in the axial direction L. The first clutch device CL1 and the second clutch device CL2 are, as mentioned above, arranged in the axial direction L. The second clutch device CL2 is thus on the axial-direction second side L2 of the first clutch device CL1, and is adjacent to the first clutch device CL1.

The first clutch device CL1 and second clutch device CL2 for the present embodiment are on the radially inner side R1 of the rotor Ro, and coincide with the rotor Ro as viewed in the radial direction R. The expression "on the radially inner side R1 of X" indicates that something is on the inner side of X in the radial direction R regardless of the position in the axial direction L. A similar definition applies to the expression "on the radially outer side R2 of X". Further, if two elements are described herein as coinciding with each other as viewed in a particular direction, it means that a virtual straight line in that direction remains through both of the two elements as it is moved in either direction orthogonal to the virtual straight line.

As illustrated in <FIG>, the first clutch device CL1 is a friction clutch device including first inner friction members <NUM> and first outer friction members <NUM> arranged in the axial direction L as well as a first piston <NUM> configured to press the first inner friction members <NUM> and the first outer friction members <NUM> in the axial direction L. The first clutch device CL1 for the present embodiment further includes a first operating oil chamber <NUM> configured to receive oil for operating the first piston <NUM> and an oil chamber forming member <NUM> extending from the input member I toward the radially outer side R2 and coupled to the input member I in such a manner as to rotate integrally with the input member I.

The first inner friction members <NUM> and the first outer friction members <NUM> are each in the shape of a ring-shaped plate, and share the same rotation axis. Further, the first inner friction members <NUM> and the first outer friction members <NUM> are arranged alternately in the axial direction L. The first inner friction members <NUM> and the first outer friction members <NUM> may be such that one of the former and the latter serves as friction plates while the other serves as separate plates. The description below may use the term "first friction members <NUM>" to collectively refer to the first inner friction members <NUM> and the first outer friction members <NUM>.

The first outer friction members <NUM> correspond to the "first friction plates". The first outer friction members <NUM> are supported by a first outer support <NUM>. The first outer support <NUM> corresponds to the "first support", which supports the first outer friction members <NUM> from the radially outer side R2. The first outer support <NUM> is open toward the axial-direction first side L1. The first outer support <NUM> is rotatable integrally with the cylindrical portion <NUM>. The first outer support <NUM> for the present embodiment is integral with the cylindrical portion <NUM>. The cylindrical portion <NUM> in the illustrated example includes at an inner circumferential portion thereof a plurality of splines extending in the axial direction L over the entire area in the axial direction L and separated from one another in the circumferential direction C. The first outer friction members <NUM> also each include similar splines at an outer circumferential portion thereof. The two sets of splines are engaged with each other, so that the first outer friction members <NUM> are supported by the cylindrical portion <NUM> from the radially outer side R2. The first outer friction members <NUM> are thus restricted in its rotation relative to the cylindrical portion <NUM>, and are supported by the cylindrical portion <NUM> in such a manner as to be slidable in the axial direction L.

The first inner friction members <NUM> correspond to the "second friction plates". The first inner friction members <NUM> are supported by a first inner support <NUM>. The first inner support <NUM> corresponds to the "second support", which supports the first inner friction members <NUM> from the radially inner side R1. The first inner support <NUM> includes a first cylindrical support section <NUM> and a first radial extension section <NUM>.

The first cylindrical support section <NUM> corresponds to the "cylindrical support section", which extends in the axial direction L and which supports the first inner friction members <NUM>. The first cylindrical support section <NUM> supports the first inner friction members <NUM> from the radially inner side R1. The first cylindrical support section <NUM> in the illustrated example includes at an outer circumferential portion thereof a plurality of splines extending in the axial direction L over the entire area in the axial direction L and separated from one another in the circumferential direction C. The first inner friction members <NUM> also each include similar splines at an inner circumferential portion thereof. The two sets of splines are engaged with each other, so that the first inner friction members <NUM> are supported by the first cylindrical support section <NUM> from the radially inner side R1. The first inner friction members <NUM> are thus restricted in its rotation relative to the first cylindrical support section <NUM>, and are supported by the first cylindrical support section <NUM> in such a manner as to be slidable in the axial direction L.

The first radial extension section <NUM> corresponds to the "radial extension section", which extends in the radial direction R on the radially inner side R1 of the first cylindrical support section <NUM> and which is coupled to the first cylindrical support section <NUM>. The first radial extension section <NUM> is coupled to the first cylindrical support section <NUM> in such a manner as to rotate integrally with the first cylindrical support section <NUM>. The first radial extension section <NUM> for the present embodiment is a member separate from the first cylindrical support section <NUM>, and is welded, swaged, or otherwise joined to the first cylindrical support section <NUM>. The first radial extension section <NUM> and first cylindrical support section <NUM> in the illustrated example are welded to each other with the first radial extension section <NUM> having on the axial-direction first side L1 a surface in contact with that surface of the first cylindrical support section <NUM> which is on the axial-direction second side L2. The first radial extension section <NUM> is coupled to the input member I in such a manner as to rotate integrally with the input member I. The first radial extension section <NUM> for the present embodiment includes on the radially inner side R1 an end portion coupled to the outer peripheral surface of the input member I. The first radial extension section <NUM> in the illustrated example includes on the radially inner side R1 an end portion welded to a flange-shaped protrusion at the outer peripheral surface of the input member I. The first radial extension section <NUM> for the present embodiment is a ring-shaped plate extending in the radial direction R and the circumferential direction C.

The first clutch device CL1 for the present embodiment includes a contact portion 442a in contact with a first friction member <NUM> from that side in the axial direction L which is opposite to the first piston <NUM> (for the present embodiment, from the axial-direction second side L2). The contact portion 442a in the illustrated example is integral with the first radial extension section <NUM>. Specifically, the contact portion 442a corresponds to a portion of the first radial extension section <NUM> which portion extends farther on the radially outer side R2 than the first cylindrical support section <NUM>. The contact portion 442a for the present embodiment is in contact, from the axial-direction second side L2, with a first inner friction member <NUM> furthermost on the axial-direction second side L2.

The first inner support <NUM> is coupled to an intermediate member <NUM>. The intermediate member <NUM> is coupled to the first inner support <NUM> in such a manner as to rotate integrally with the first inner support <NUM>. The intermediate member <NUM> for the present embodiment is on the radially inner side R1 of the first cylindrical support section <NUM>, and coincides with the first cylindrical support section <NUM> as viewed in the radial direction R.

The intermediate member <NUM> includes a body <NUM> and protrusions <NUM>. The intermediate member <NUM> for the present embodiment further includes a coupling portion <NUM>.

The body <NUM> is between the first piston <NUM> and the first inner support <NUM> in the axial direction L. The body <NUM> for the present embodiment extends in the radial direction R.

The body <NUM> for the present embodiment is in contact with the first radial extension section <NUM> of the first inner support <NUM> from the axial-direction first side L1. The body <NUM> has a surface in contact with the first radial extension section <NUM> which surface has radial grooves 45a extending in the radial direction R. The radial grooves 45a extend across that contact surface continuously in the radial direction R. The radial grooves 45a, in other words, extend through the portion of the contact between the body <NUM> and the first radial extension section <NUM> from the radially inner side R1 to the radially outer side R2. The radial grooves 45a for the present embodiment are separated from one another in the circumferential direction C.

The protrusions <NUM> protrude toward the axial-direction first side L1 of the body <NUM>. The protrusions <NUM> for the present embodiment protrude from the coupling portion <NUM> toward the axial-direction first side L1.

The coupling portion <NUM> is in the shape of a cylinder extending in the axial direction L. The coupling portion <NUM> is coupled to the first cylindrical support section <NUM> of the first inner support <NUM> in such a manner as to rotate integrally with the first cylindrical support section <NUM>. The coupling portion <NUM> for the present embodiment is on the radially inner side R1 of the first cylindrical support section <NUM>, adjacent to the first cylindrical support section <NUM>, and coupled to the first cylindrical support section <NUM>. Specifically, the first cylindrical support section <NUM> includes at an inner circumferential portion thereof a plurality of splines extending in the axial direction L and separated from one another in the circumferential direction C. The coupling portion <NUM> also includes similar splines at an outer circumferential portion thereof. The two sets of splines are engaged with each other, so that the coupling portion <NUM> is coupled to the first cylindrical support section <NUM> in such a manner as to rotate integrally with the first cylindrical support section <NUM>.

The coupling portion <NUM> for the present embodiment includes on the axial-direction second side L2 an end portion coupled to that end portion of the body <NUM> which is on the radially outer side R2. The coupling portion <NUM> includes on the axial-direction first side L1 an end portion from which the protrusions <NUM> protrude toward the axial-direction first side L1. In the illustrated example, the body <NUM>, the protrusions <NUM>, and the coupling portion <NUM> are integral with one another.

The first piston <NUM> corresponds to the "press member". The first piston <NUM> is so positioned as to press the first inner friction members <NUM> and the first outer friction members <NUM> from the axial-direction first side L1. The first piston <NUM> for the present embodiment is configured to press the first friction members <NUM> with a pressure corresponding to the pressure of oil supplied into the first operating oil chamber <NUM>. The first piston <NUM> for the present embodiment mainly includes an alloy containing iron.

The first piston <NUM> for the present embodiment includes a first slide section <NUM>, a first press section <NUM>, and a connection section <NUM>.

The first slide section <NUM> extends in the radial direction R. The first slide section <NUM> for the present embodiment is a ring-shaped plate extending in the radial direction R and the circumferential direction C. The first slide section <NUM> is slidable in the axial direction L inside a first cylinder C1. The first slide section <NUM> for the present embodiment is on the radially inner side R1 of the first friction members <NUM>, and coincides with the first friction members <NUM> as viewed in the radial direction R.

The first cylinder C1 extends in the axial direction L. The first cylinder C1 for the present embodiment is made up of the input member I and the intermediate member <NUM>. Specifically, the first slide section <NUM> includes at an end portion thereof on the radially inner side R1 an inner slide section 421A in the shape of a cylinder. The inner slide section 421A has an inner circumferential surface that defines a gap together with the outer peripheral surface of the cylindrical input section Ia. The gap contains a first seal member S1. Further, the first slide section <NUM> includes at an end portion thereof on the radially outer side R2 an outer slide section 421B in the shape of a cylinder. The outer slide section 421B has an outer peripheral surface that defines a gap together with the inner circumferential surface of the coupling portion <NUM>. The gap contains a second seal member S2. This allows the inner slide section 421A of the first piston <NUM> to slide in the axial direction L relative to the cylindrical input section Ia of the input member I, and also allows the outer slide section 421B of the first piston <NUM> to slide in the axial direction L relative to the coupling portion <NUM> of the intermediate member <NUM>. The first piston <NUM> is thus slidable in the axial direction L relative to slide reference members T, which are rotatable integrally with the first inner support <NUM>. The slide reference members T for the present embodiment are the input member I and the intermediate member <NUM>.

As described above, the present embodiment is arranged such that the first piston <NUM> is slidable on the slide reference members T at respective portions each with a gap filled with a seal member (namely, the first seal member S1 and the second seal member S2). The first seal member S1 for the present embodiment is attached to a groove extending in the outer peripheral surface of the cylindrical input section Ia continuously in the circumferential direction C. The second seal member S2 is attached to the outer peripheral surface of the outer slide section 421B. The first seal member S1 and the second seal member S2 are each made of an elastic material such as nitrile rubber (NBR) or styrene-butadiene rubber (SBR).

The first press section <NUM> is on the axial-direction first side L1 of the first friction members <NUM>, and is adjacent to the first friction members <NUM>. The first press section <NUM> for the present embodiment is a ring-shaped plate extending in the radial direction R and the circumferential direction C.

The connection section <NUM> connects the first slide section <NUM> with the first press section <NUM>. The connection section <NUM> for the present embodiment extends in the radial direction R in such a manner as to bypass the first cylindrical support section <NUM> of the first inner support <NUM> on the axial-direction first side L1. The connection section <NUM> thereby connects that end portion of the first slide section <NUM> which is on the radially outer side R2 with that end portion of the first press section <NUM> which is on the radially inner side R1. Specifically, the connection section <NUM> includes a first cylindrical connection section 423A, a second cylindrical connection section 423B, and an intermediate connection section 423C. The first cylindrical connection section 423A is connected with the outer slide section 421B, and protrudes from the outer slide section 421B toward the axial-direction first side L1. The second cylindrical connection section 423B is on the radially outer side R2 of the first cylindrical connection section 423A, is connected with that end portion of the first press section <NUM> which is on the radially inner side R1, and protrudes from that end portion toward the axial-direction first side L1. The intermediate connection section 423C is in the shape of a ring-shaped plate connecting the first cylindrical connection section 423A with the second cylindrical connection section 423B in the radial direction R.

The first piston <NUM> has insertion holes <NUM> extending through the first piston <NUM> in the axial direction L. The insertion holes <NUM> for the present embodiment extend through the connection section <NUM> in the axial direction L. Specifically, the insertion holes <NUM> are in the intermediate connection section 423C. The insertion holes <NUM> receive the respective protrusions <NUM> of the intermediate member <NUM> as inserted. The insertion holes <NUM>, with the respective protrusions <NUM> inserted therein, serve to restrict rotation of the first piston <NUM> relative to the first inner support <NUM>. This allows the first piston <NUM> to rotate integrally with the first inner support <NUM>. The insertion holes <NUM> and the protrusions <NUM> will be detailed later.

The first piston <NUM> for the present embodiment is urged by first urging members 42a toward the axial-direction first side L1. The first urging members 42a are between the first slide section <NUM> and the body <NUM> of the intermediate member <NUM> in the axial direction L. The first urging members 42a for the present embodiment are separated from one another in the circumferential direction C. The first urging members 42a may be, for example, a return spring. With the above arrangement, when the first operating oil chamber <NUM> has received oil with a predetermined pressure from a hydraulic pressure control device (not illustrated in the drawings), the first piston <NUM> responds to the pressure to slide toward the axial-direction second side L2 against the urging force of the first urging members 42a and press the first friction members <NUM> toward the axial-direction second side L2.

The first operating oil chamber <NUM> is adjacent to the first piston <NUM> in the axial direction L. The first operating oil chamber <NUM> for the present embodiment is between the first piston <NUM> and the oil chamber forming member <NUM>. Specifically, the first operating oil chamber <NUM> is between the first slide section <NUM> of the first piston <NUM> and the oil chamber forming member <NUM> in the axial direction L.

The first operating oil chamber <NUM> for the present embodiment coincides with the first friction members <NUM> as viewed in the radial direction R. The first operating oil chamber <NUM> for the present embodiment does not coincide with the first friction members <NUM> as viewed in the axial direction L.

The oil chamber forming member <NUM> for the present embodiment is in contact with the outer peripheral surface of the cylindrical input section Ia of the input member I. The oil chamber forming member <NUM> for the present embodiment is on the axial-direction first side L1 of the first piston <NUM>. The oil chamber forming member <NUM> for the present embodiment is on the axial-direction first side L1 of the first slide section <NUM> of the first piston <NUM>, and is adjacent to the first slide section <NUM>.

The present embodiment includes a first cancel oil chamber <NUM> and a lubricating oil path <NUM> between the first piston <NUM> and the first inner support <NUM> in the axial direction L. The first cancel oil chamber <NUM> is a space for creating a hydraulic pressure for counteracting a centrifugal hydraulic pressure created in the first operating oil chamber <NUM>. The first cancel oil chamber <NUM> for the present embodiment is between the first slide section <NUM> of the first piston <NUM> and the body <NUM> of the intermediate member <NUM> in the axial direction L. The lubricating oil path <NUM> serves to supply oil to an inner circumferential portion of the first inner support <NUM> (first cylindrical support section <NUM>) from the radially inner side R1.

The body <NUM> of the intermediate member <NUM> for the present embodiment separates the first cancel oil chamber <NUM> and the lubricating oil path <NUM> from each other. The body <NUM>, as described above, extends in the radial direction R. This means that the first cancel oil chamber <NUM> is on the axial-direction first side L1 of the body <NUM> and that the lubricating oil path <NUM> is on the axial-direction second side L2 of the body <NUM>.

As illustrated in <FIG>, the first cancel oil chamber <NUM> and lubricating oil path <NUM> for the present embodiment receive oil through a first oil path P1, a second oil path P2, and a third oil path P3.

The first oil path P1 extends from the inner circumferential surface of the cylindrical input section Ia of the input member I to the outer peripheral surface thereof. The first oil path P1 for the present embodiment connects with the space between the first piston <NUM> and the first inner support <NUM>. The second oil path P2 connects the first oil path P1 with the third oil path P3. The second oil path P2 is in the insert portion Ma of the input transmission shaft M. The second oil path P2 for the present embodiment extends through the insert portion Ma in the radial direction R from the third oil path P3 to the outer peripheral surface of the insert portion Ma. The third oil path P3 is in the input transmission shaft M. The third oil path P3 for the present embodiment extends in the axial direction L.

The present embodiment allows oil to flow sequentially through the third oil path P3, the second oil path P2, and the first oil path P1 into the space between the first piston <NUM> and the first inner support <NUM>. The oil having flown into the space then flows toward the radially outer side R2 into both the first cancel oil chamber <NUM> and the lubricating oil path <NUM>. The first cancel oil chamber <NUM> has a space that is closed except at a portion that communicates with the first oil path P1. After the first cancel oil chamber <NUM> has become filled with oil, the oil from the first oil path P1 flows mainly into the lubricating oil path <NUM>. The oil having flown into the lubricating oil path <NUM> then flows through the radial grooves 45a to reach an inner circumferential portion of the first cylindrical support section <NUM>. The oil having reached the inner circumferential portion of the first cylindrical support section <NUM> then flows through a communication hole 44a, which extends through the first cylindrical support section <NUM> in the radial direction R, to reach the first friction members <NUM>. The oil thus lubricates and cools the first friction members <NUM>.

As illustrated in <FIG>, the second clutch device CL2 for the present embodiment includes (i) second inner friction members <NUM> and second outer friction members <NUM> arranged in the axial direction L, (ii) a second piston <NUM> configured to press the second inner friction members <NUM> and the second outer friction members <NUM> in the axial direction L, and (iii) a second operating oil chamber <NUM> configured to receive oil for operating the second piston <NUM>.

The second inner friction members <NUM> and the second outer friction members <NUM> are each in the shape of a ring-shaped plate, and share the same rotation axis. Further, the second inner friction members <NUM> and the second outer friction members <NUM> are arranged alternately in the axial direction L. The second inner friction members <NUM> and the second outer friction members <NUM> may be such that one of the former and the latter serves as friction plates while the other serves as separate plates. The description below may use the term "second friction members <NUM>" to collectively refer to the second inner friction members <NUM> and the second outer friction members <NUM>.

The second inner friction members <NUM> are supported by a second inner support <NUM>. The second inner support <NUM> supports the second inner friction members <NUM> from the radially inner side R1. The second inner support <NUM> for the present embodiment includes a second cylindrical support section <NUM> extending in the axial direction L and a second radial extension section <NUM> extending in the radial direction R on the radially inner side R1 of the second cylindrical support section <NUM>.

The second cylindrical support section <NUM> supports the second inner friction members <NUM> from the radially inner side R1. The second cylindrical support section <NUM> in the illustrated example includes at an outer circumferential portion thereof a plurality of splines extending in the axial direction L over the entire area in the axial direction L and separated from one another in the circumferential direction C. The second inner friction members <NUM> also each include similar splines at an inner circumferential portion thereof. The two sets of splines are engaged with each other, so that the second inner friction members <NUM> are supported by the second cylindrical support section <NUM> from the radially inner side R1. The second inner friction members <NUM> are thus restricted in its rotation relative to the second cylindrical support section <NUM>, and are supported by the second cylindrical support section <NUM> in such a manner as to be slidable in the axial direction L.

The second radial extension section <NUM> is coupled to the second cylindrical support section <NUM> in such a manner as to rotate integrally with the second cylindrical support section <NUM>. The second radial extension section <NUM> for the present embodiment is a member separate from the second cylindrical support section <NUM>, and is welded, swaged, or otherwise joined to the second cylindrical support section <NUM>. The second radial extension section <NUM> and second cylindrical support section <NUM> in the illustrated example are welded to each other with the second radial extension section <NUM> having on the radially outer side R2 an end portion coupled to that end portion of the second cylindrical support section <NUM> which is on the axial-direction first side L1. The second radial extension section <NUM> for the present embodiment is a ring-shaped plate extending in the radial direction R and the circumferential direction C.

The second radial extension section <NUM> is coupled to the input transmission shaft M in such a manner as to rotate integrally with the input transmission shaft M. The second radial extension section <NUM> for the present embodiment includes on the radially inner side R1 an end portion coupled to the outer peripheral surface of the input transmission shaft M. The second radial extension section <NUM> in the illustrated example includes at an end portion thereof on the radially inner side R1 a cylindrical portion having an inner circumferential surface provided with a plurality of splines extending in the axial direction L and separated from one another in the circumferential direction C. The input transmission shaft M also includes similar splines on an outer circumferential surface thereof. The two sets of splines are engaged with each other, so that the second radial extension section <NUM> is coupled to the input transmission shaft M in such a manner as to rotate integrally with the input transmission shaft M.

The second outer friction members <NUM> are supported by a second outer support <NUM>. The second outer support <NUM> supports the second outer friction members <NUM> from the radially outer side R2. The second outer support <NUM> for the present embodiment is in the shape of a cylinder extending in the axial direction L. The second outer support <NUM> in the illustrated example includes at an inner circumferential portion thereof a plurality of splines extending in the axial direction L and separated from one another in the circumferential direction C. The second outer friction members <NUM> also each include similar splines at an outer circumferential portion thereof. The two sets of splines are engaged with each other, so that the second outer friction members <NUM> are supported by the second outer support <NUM> from the radially outer side R2. The second outer friction members <NUM> are thus restricted in its rotation relative to the second outer support <NUM>, and are supported by the second outer support <NUM> in such a manner as to be slidable in the axial direction L.

The second outer support <NUM> is rotatable integrally with the rotor support <NUM>. The second outer support <NUM> for the present embodiment is supported by the cylindrical portion <NUM> of the rotor support <NUM> from the radially outer side R2. The second outer support <NUM> in the illustrated example includes at an outer circumferential portion thereof a plurality of splines extending in the axial direction L and separated from one another in the circumferential direction C. The cylindrical portion <NUM>, as described above, also includes at an inner circumferential portion thereof a plurality of splines extending in the axial direction L and separated from one another in the circumferential direction C. The two sets of splines are engaged with each other, so that the second outer support <NUM> is supported by the cylindrical portion <NUM> from the radially outer side R2. The second outer friction members <NUM> are thus supported by the cylindrical portion <NUM> of the rotor support <NUM> with the second outer support <NUM> therebetween.

The second clutch device CL2 for the present embodiment includes a contact member <NUM> in contact with a second friction member <NUM>. The contact member <NUM> is in contact with a second friction member <NUM> from that side in the axial direction L which is opposite to the second piston <NUM> (for the present embodiment, from the axial-direction first side L1). The contact member <NUM> for the present embodiment is in contact, from the axial-direction first side L1, with a second outer friction member <NUM> furthermost on the axial-direction first side L1.

The contact member <NUM> for the present embodiment is supported by the cylindrical portion <NUM> from the radially outer side R2. The contact member <NUM> in the illustrated example includes at an outer circumferential portion thereof a plurality of splines extending in the axial direction L and separated from one another in the circumferential direction C. These splines are engaged with the splines at the inner circumferential portion of the cylindrical portion <NUM>, so that the contact member <NUM> is restricted in its rotation relative to the cylindrical portion <NUM> and supported by the cylindrical portion <NUM> from the radially outer side R2 in such a manner as to be slidable in the axial direction L. Further, the illustrated example includes a ring-shaped fixing member <NUM> that is in contact with the contact member <NUM> from the axial-direction first side L1 and that is fixed to the inner circumferential portion of the cylindrical portion <NUM>. The fixing member <NUM> thus restricts movement of the contact member <NUM> toward the axial-direction first side L1. The fixing member <NUM> for the present embodiment is a snap ring.

The second piston <NUM> for the present embodiment is configured to press the second friction members <NUM> in the axial direction L with a pressure corresponding to the pressure of oil supplied into the second operating oil chamber <NUM>. The second piston <NUM> for the present embodiment is on the axial-direction second side L2 of the second friction members <NUM>. The second piston <NUM>, in other words, does not coincide with the second friction members <NUM> as viewed in the radial direction R. The second piston <NUM> includes a second slide section <NUM> and a second press section <NUM>.

The second slide section <NUM> is slidable in the axial direction L inside a second cylinder C2. The second cylinder C2 extends in the axial direction L. The second cylinder C2 for the present embodiment is made up of a cylinder forming portion <NUM> of the flange portion <NUM>. The present embodiment is, in other words, arranged such that the flange portion <NUM> includes a portion that is also a portion of the second clutch device CL2.

The cylinder forming portion <NUM> protrudes toward the axial-direction second side L2 in such a manner as to form a second cylinder C2 in which the second piston <NUM> is slidable. The cylinder forming portion <NUM> for the present embodiment includes an inner cylindrical portion <NUM>, an outer cylindrical portion <NUM>, and a radial coupling portion <NUM>.

The inner cylindrical portion <NUM> extends in the axial direction L. The inner cylindrical portion <NUM> has an outer circumferential surface having a portion that serves as a slide surface for that end portion of the second slide section <NUM> which is on the radially inner side R1 to slide on. The inner cylindrical portion <NUM> for the present embodiment covers the cylindrical protrusion <NUM> of the case <NUM> from the radially outer side R2.

The outer cylindrical portion <NUM> extends in the axial direction L, and is on the radially outer side R2 of the inner cylindrical portion <NUM>. The outer cylindrical portion <NUM> has an inner circumferential surface having a portion that serves as a slide surface for that end portion of the second slide section <NUM> which is on the radially outer side R2 to slide on.

The radial coupling portion <NUM> extends in the radial direction R in such a manner as to couple the inner cylindrical portion <NUM> to the outer cylindrical portion <NUM>. The radial coupling portion <NUM> for the present embodiment is a ring-shaped plate extending in the radial direction R and the circumferential direction C. The radial coupling portion <NUM> for the present embodiment includes on the radially inner side R1 an end portion coupled to that end portion of the inner cylindrical portion <NUM> which is on the axial-direction second side L2, and also includes on the radially outer side R2 an end portion coupled to that end portion of the outer cylindrical portion <NUM> which is on the axial-direction second side L2. The flange portion <NUM> includes on the radially outer side R2 of the cylinder forming portion <NUM> a ring-shaped plate extending in the radial direction R and the circumferential direction C and coupled to that end portion of the outer cylindrical portion <NUM> which is on the axial-direction first side L1. The flange portion <NUM> in the illustrated example is a single member made up integrally of the inner cylindrical portion <NUM>, the outer cylindrical portion <NUM>, and the radial coupling portion <NUM>.

The second press section <NUM> extends from the second slide section <NUM> toward the radially outer side R2. The second press section <NUM> for the present embodiment is on that side of the second friction members <NUM> in the axial direction L which is opposite to the contact member <NUM> (for the present embodiment, on the axial-direction second side L2).

The second piston <NUM> is supported by the rotor support <NUM> in such a manner as to rotate integrally with the rotor support <NUM>. The present embodiment is arranged such that the flange portion <NUM> of the rotor support <NUM> restricts rotation of the second piston <NUM> relative to the flange portion <NUM> so that the flange portion <NUM> is rotatable integrally with the second piston <NUM>.

The second piston <NUM> for the present embodiment is urged by second urging members 52a, which are attached to an attachment member <NUM>, toward the axial-direction second side L2. The second urging members 52a are between the second slide section <NUM> and the attachment member <NUM> in the axial direction L. The second urging members 52a for the present embodiment are separated from one another in the circumferential direction C. The second urging members 52a may be, for example, a return spring. With the above arrangement, when the second operating oil chamber <NUM> has received oil with a predetermined pressure from a hydraulic pressure control device (not illustrated in the drawings), the second piston <NUM> responds to the pressure to slide toward the axial-direction first side L1 against the urging force of the second urging members 52a and press the second friction members <NUM> toward the axial-direction first side L1.

The attachment member <NUM> is on the radially outer side R2 of the inner cylindrical portion <NUM> of the cylinder forming portion <NUM>. The attachment member <NUM> for the present embodiment is in contact with the outer circumferential surface of the inner cylindrical portion <NUM>. The attachment member <NUM> for the present embodiment is on the axial-direction first side L1 of the second slide section <NUM> of the second piston <NUM>, and is adjacent to the second slide section <NUM>.

The second operating oil chamber <NUM> is adjacent to the second piston <NUM> in the axial direction L. The second operating oil chamber <NUM> for the present embodiment is between the second piston <NUM> and the cylinder forming portion <NUM>. Specifically, the second operating oil chamber <NUM> is between the second slide section <NUM> of the second piston <NUM> and the radial coupling portion <NUM> of the cylinder forming portion <NUM> in the axial direction L.

The second operating oil chamber <NUM> for the present embodiment coincides with the second friction members <NUM> as viewed in the axial direction L. The second operating oil chamber <NUM> for the present embodiment does not coincide with the second friction members <NUM> as viewed in the radial direction R.

The present embodiment includes a second cancel oil chamber <NUM> on that side of the second piston <NUM> in the axial direction L which is opposite to the second operating oil chamber <NUM> (for the present embodiment, on the axial-direction first side L1). The second cancel oil chamber <NUM> is a space for creating a hydraulic pressure for counteracting a centrifugal hydraulic pressure created in the second operating oil chamber <NUM>. The second cancel oil chamber <NUM> for the present embodiment is between the second slide section <NUM> and the attachment member <NUM> in the axial direction L.

As illustrated in <FIG>, the vehicle drive transmission device <NUM> for the present embodiment includes a first bearing B1 and a second bearing B2 both supporting the rotor support <NUM> in such a manner that the rotor support <NUM> is rotatable as well as a third bearing B3 supporting the input member I in such a manner that the input member I is rotatable. The first bearing B1, second bearing B2, and third bearing B3 for the present embodiment are each a ball bearing.

The first bearing B1 supports the cylindrical portion <NUM> of the rotor support <NUM> in such a manner that the cylindrical portion <NUM> is rotatable. The first bearing B1 for the present embodiment is on the radially outer side R2 of the first cylindrical support section <NUM> of the first inner support <NUM>. The first bearing B1 for the present embodiment is on the axial-direction first side L1 of the rotor Ro. The first bearing B1 for the present embodiment is on the outer circumferential surface of the cylindrical portion <NUM>. Specifically, the first bearing B1 is attached to the cylindrical portion <NUM> in such a manner as to have an inner circumferential surface in contact with the outer circumferential surface of a bearing support section <NUM> of the cylindrical portion <NUM>, which protrudes on the axial-direction first side L1 of the rotor Ro. The first bearing B1 for the present embodiment is supported by a bearing support section 11a (see <FIG>) of the first side wall <NUM> of the case <NUM>. The bearing support section 11a protrudes toward the axial-direction second side L2, and supports the first bearing B1 from the radially outer side R2. The first bearing B1, as described above, supports the cylindrical portion <NUM> in such a manner that the cylindrical portion <NUM> is rotatable relative to the first side wall <NUM>.

The first bearing B1 for the present embodiment coincides with the first piston <NUM> as viewed in the radial direction R. Specifically, the first bearing B1 coincides with the first press section <NUM> of the first piston <NUM> as viewed in the radial direction. The first bearing B1 for the present embodiment does not coincide with the rotor Ro as viewed in the axial direction L. The first bearing B1 for the present embodiment coincides with a coil end portion Ce of the stator St as viewed in the radial direction R (see <FIG>).

The cylindrical portion <NUM> for the present embodiment includes a projection 21a protruding from the outer circumferential surface of the cylindrical portion <NUM> toward the radially outer side R2 and present on the axial-direction first side L1 of the rotor Ro. The projection 21a extends continuously over the entire area in the circumferential direction C. The projection 21a is sandwiched between the rotor Ro and the first bearing B1 in the axial direction L. Specifically, the rotor Ro is in contact with the projection 21a from the axial-direction second side L2, whereas the first bearing B1 is in contact with the projection 21a from the axial-direction first side L1.

The second bearing B2 supports the flange portion <NUM> of the rotor support <NUM> in such a manner that the flange portion <NUM> is rotatable. The second bearing B2 for the present embodiment coincides with the second piston <NUM> as viewed in the radial direction R. The second bearing B2 for the present embodiment is on the radially inner side R1 of the cylinder forming portion <NUM> of the flange portion <NUM>, and coincides with the cylinder forming portion <NUM> as viewed in the radial direction R. The second bearing B2 supports the rotor support <NUM> from the radially inner side R1. The second bearing B2 in the illustrated example is between the inner cylindrical portion <NUM> of the rotor support <NUM> and the cylindrical protrusion <NUM> of the case <NUM>.

The third bearing B3 for the present embodiment is on the radially inner side R1 of at least a portion of the first piston <NUM>, and coincides with the first piston <NUM> as viewed in the radial direction R. The third bearing B3 for the present embodiment is on the radially inner side R1 of the first press section <NUM> of the first piston <NUM>. The third bearing B3 coincides with the first press section <NUM> as viewed in the radial direction. The third bearing B3 for the present embodiment is on the axial-direction first side L1 of the oil chamber forming member <NUM>. The third bearing B3 is on the radially inner side R1 of a portion of the oil chamber forming member <NUM>.

The third bearing B3 for the present embodiment is on the outer circumferential surface of the cylindrical input section Ia of the input member I. Specifically, the third bearing B3 is attached to the cylindrical input section Ia in such a manner as to have an inner circumferential surface in contact with the outer circumferential surface of the cylindrical input section Ia. The third bearing B3 is supported by the first side wall <NUM> of the case <NUM> from the radially outer side R2. The third bearing B3, as described above, supports the input member I in such a manner that the input member I is rotatable relative to the first side wall <NUM>.

The third bearing B3 for the present embodiment includes an inner race in contact with a step portion on the outer circumferential surface of the cylindrical input section Ia from the axial-direction first side L1, and also includes an outer race in contact with the first side wall <NUM> from the axial-direction second side L2. The third bearing B3 is thus restricted in its movement in the axial direction L by the cylindrical input section Ia and the first side wall <NUM>. This allows the third bearing B3 to support a thrust load on the input member I which the third bearing B3 supports.

The description below deals with the protrusions <NUM> of the intermediate member <NUM> and the insertion holes <NUM> in the first piston <NUM> in detail.

As illustrated in <FIG>, the protrusions <NUM> for the present embodiment are each in the shape of a plate extending in the axial direction L and the circumferential direction C. The protrusions <NUM> share an equal dimension in the radial direction R (thickness) over the entire area in the axial direction L and the circumferential direction C. The insertion holes <NUM> are shaped to match the outer shape of the respective protrusions <NUM>. The insertion holes <NUM> for the present embodiment, similarly to the protrusions <NUM>, share an equal dimension in the radial direction R over the entire area in the axial direction L and the circumferential direction C.

The protrusions <NUM> for the present embodiment are separated from one another in the circumferential direction C. The illustrated example includes eight protrusions <NUM> disposed at regular intervals in the circumferential direction C. The insertion holes <NUM> for the present embodiment are separated from one another in the circumferential direction C. The insertion holes <NUM> are present in a number equal to the number of the protrusions <NUM>. The illustrated example includes eight insertion holes <NUM> disposed at regular intervals in the circumferential direction C.

As illustrated in <FIG>, inserting the protrusions <NUM> into the respective insertion holes <NUM> results in the first piston <NUM> being restricted in its rotation relative to the intermediate member <NUM>. Specifically, with the protrusions <NUM> in the respective insertion holes <NUM>, trying to rotate the first piston <NUM> in the circumferential direction relative to the intermediate member <NUM> causes each protrusion <NUM> to come into contact in the circumferential direction C with an inner side face of the connection section <NUM> that faces the corresponding insertion hole <NUM>. For instance, trying to rotate the first piston <NUM> toward a first side in the circumferential direction C relative to the intermediate member <NUM> causes that face of each protrusion <NUM> which faces the side opposite to the first side in the circumferential direction (that is, a second side in the circumferential direction) to come into contact with that face of the corresponding insertion hole <NUM> which faces the first side in the circumferential direction. Trying to rotate the first piston <NUM> toward the second side in the circumferential direction relative to the intermediate member <NUM> causes that face of each protrusion <NUM> which faces the first side in the circumferential direction to come into contact with that face of the corresponding insertion hole <NUM> which faces the second side in the circumferential direction. The first piston <NUM> is, as described above, restricted in its rotation relative to the intermediate member <NUM>. The insertion holes <NUM> for the present embodiment each have a dimension in the circumferential direction C that is larger than the dimension of each protrusion <NUM> in the circumferential direction C by an amount not smaller than tolerances on (i) the respective dimensions of the protrusions <NUM> and the insertion holes <NUM> in the circumferential direction C and (ii) the intervals at which the protrusions <NUM> and the insertion holes <NUM> are disposed.

As illustrated in <FIG>, when the first piston <NUM> is assembled to the intermediate member <NUM> from the axial-direction first side L1, the position of the first piston <NUM> in the circumferential direction C relative to the intermediate member <NUM>, that is, its rotation phase, is adjusted such that all the protrusions <NUM> coincide with the respective insertion holes <NUM> as viewed from the axial-direction first side L1. Moving the first piston <NUM> in the above state toward the intermediate member <NUM>, that is, toward the axial-direction second side L2, causes the protrusions <NUM> to enter the respective insertion holes <NUM>. Then, moving the first piston <NUM> further toward the intermediate member <NUM> such that the protrusions <NUM> are inserted into the respective insertion holes <NUM> allows the first piston <NUM> to be assembled to the intermediate member <NUM>. The assembly of the first piston <NUM> is facilitated as described above through simple adjustment of the position of the first piston <NUM> relative to the intermediate member <NUM> so that all the protrusions <NUM> coincide with the respective insertion holes <NUM> as viewed from the axial-direction first side L1.

The present embodiment, as described above, includes a first seal member S1 in a gap between that end portion of the first slide section <NUM> which is on the radially inner side R1 and the cylindrical input section Ia, and also includes a second seal member S2 in a gap between that end portion of the first slide section <NUM> which is on the radially outer side R2 and the coupling portion <NUM>. Facilitating the assembly of the first piston <NUM> for the above configuration reduces unnecessary movements and rotations of the first piston <NUM> relative to the intermediate member <NUM> during the assembly. This in turn reduces the risk of the first seal member S1 and the second seal member S2 being damaged by, for example, friction during assembly. It is preferable to design the respective positions of the insertion holes <NUM> in the axial direction L and the respective positions and dimensions of the protrusions <NUM> in the axial direction L such that the first seal member S1 comes into contact with that end portion of the first slide section <NUM> which is on the radially inner side R1, whereas the second seal member S2 comes into contact with the inner circumferential portion of the coupling portion <NUM>, immediately before the protrusions <NUM> start to enter the respective insertion holes <NUM> for insertion or as soon as the protrusions <NUM> start to enter the respective insertion holes <NUM> for insertion.

The description below outlines the vehicle drive transmission device (<NUM>) and vehicle drive device (<NUM>) described above.

A vehicle drive transmission device (<NUM>) includes:.

The above vehicle drive transmission device is configured such that the intermediate member (<NUM>) includes a body (<NUM>) and a protrusion (<NUM>) protruding toward the first side (L1) of the body (<NUM>) in the axial direction and that the press member (<NUM>) has an insertion hole (<NUM>) extending through the press member (<NUM>) in the axial direction (L) and configured to receive the protrusion (<NUM>). With the protrusion (<NUM>) in the insertion hole (<NUM>), the press member (<NUM>) is restricted in its rotation relative to the second support (<NUM>). The use of the protrusion (<NUM>) and the insertion hole (<NUM>) appropriately restricts rotation of the press member (<NUM>) and the second support (<NUM>) relative to each other. Further, when the press member (<NUM>) is assembled to the intermediate member (<NUM>) from the first side (L1) in the axial direction, the assembler is able to see, from the first side (L1) in the axial direction through the insertion hole (<NUM>) in the press member (<NUM>), the protrusion (<NUM>) to be inserted into the insertion hole (<NUM>). The above configuration thereby allows the assembler to easily adjust the rotation phase of the press member (<NUM>) and insert the protrusion (<NUM>) into the insertion hole (<NUM>), facilitating the assembly of the press member (<NUM>).

The vehicle drive transmission device (<NUM>) may preferably further include: a cancel oil chamber (<NUM>) and a lubricating oil path (<NUM>) between the press member (<NUM>) and the second support (<NUM>) in the axial direction (L), the cancel oil chamber (<NUM>) being configured to create a hydraulic pressure for counteracting a centrifugal hydraulic pressure created in an operating oil chamber (<NUM>) configured to receive oil for operating the press member (<NUM>), the lubricating oil path (<NUM>) being configured to supply oil to an inner circumferential portion of the second support (<NUM>) from the inner side (R1) in the radial direction (R), wherein
the body (<NUM>) separates the cancel oil chamber (<NUM>) and the lubricating oil path (<NUM>) from each other.

With the above configuration, the body (<NUM>) of the intermediate member (<NUM>) separates the cancel oil chamber (<NUM>) and the lubricating oil path (<NUM>) from each other. This allows the vehicle drive transmission device (<NUM>) to be downsized easily as compared to a configuration including an additional member for separating the cancel oil chamber (<NUM>) and the lubricating oil path (<NUM>) from each other.

The above vehicle drive transmission device is configured such that the second support (<NUM>) includes a cylindrical support section (<NUM>) and a protrusion (<NUM>) protruding from the cylindrical support section (<NUM>) toward the first side (L1) in the axial direction and that the press member (<NUM>) has an insertion hole (<NUM>) extending through the press member (<NUM>) in the axial direction (L) and configured to receive the protrusion (<NUM>). With the protrusion (<NUM>) in the insertion hole (<NUM>), the press member (<NUM>) is restricted in its rotation relative to the second support (<NUM>). The use of the protrusion (<NUM>) and the insertion hole (<NUM>) appropriately prevents rotation of the press member (<NUM>) and the second support (<NUM>) relative to each other. Further, when the press member (<NUM>) is assembled to the second support (<NUM>) from the first side (L1) in the axial direction, the assembler is able to see, from the first side (L1) in the axial direction through the insertion hole (<NUM>) in the press member (<NUM>), the protrusion (<NUM>) to be inserted into the insertion hole (<NUM>). The above configuration thereby allows the assembler to easily adjust the rotation phase of the press member (<NUM>) and insert the protrusion (<NUM>) into the insertion hole (<NUM>), facilitating the assembly of the press member (<NUM>).

The vehicle drive transmission device (<NUM>) may preferably be further arranged such that the press member (<NUM>) is slidable in the axial direction (L) on the second support (<NUM>) or a slide reference member (T) configured to rotate integrally with the second support (<NUM>), and
the press member (<NUM>) is slidable on the slide reference member (T) at a portion with a gap filled with a seal member (S1, S2).

Facilitating the assembly of the press member (<NUM>) to the intermediate member (<NUM>) or the second support (<NUM>) reduces unnecessary movements and rotations of the press member (<NUM>) relative to the slide reference member (T) during the assembly, and thereby reduces the risk of the seal member (S <NUM>, S2) being damaged by, for example, friction during the assembly.

A vehicle drive device (<NUM>) includes:.

Suppose a friction clutch device that is positioned on the inner side (R1) of a cylindrical portion (<NUM>) of a rotor support (<NUM>) in the radial direction (R) and on the first side (L1) of a flange portion (<NUM>) in the axial direction as with the above configuration. In such a case, an assembler would normally assemble a press member (<NUM>) to, for example, a second support (<NUM>) on the inner side (R1) of the cylindrical portion (<NUM>) in the radial direction (R). The assembler would then be unable to easily see the components during the assembly. The above configuration, in contrast, ensures that the assembler is able to easily see the components during the assembly as described above, facilitating the assembly of the press member (<NUM>) in the above case as well.

Claim 1:
A vehicle drive transmission device (<NUM>), comprising:
a first friction plate (<NUM>) and a second friction plate (<NUM>) arranged in an axial direction (L);
a friction clutch device (CL1) including a press member (<NUM>) configured to press the first friction plate (<NUM>) and the second friction plate (<NUM>) in the axial direction (L);
a first support (<NUM>) supporting the first friction plate (<NUM>) from an outer side (R2) in a radial direction (R);
a second support (<NUM>) supporting the second friction plate (<NUM>) from an inner side (R1) in the radial direction (R); and being characterised in that it further comprises
an intermediate member (<NUM>) coupled to the second support (<NUM>) in such a manner as to rotate integrally with the second support (<NUM>), wherein
the first support (<NUM>) is open toward a first side (L1) in the axial direction (L),
the press member (<NUM>) is at such a position as to press the first friction plate (<NUM>) and the second friction plate (<NUM>) from the first side (L1) in the axial direction (L),
the intermediate member (<NUM>) includes:
a body (<NUM>) between the press member (<NUM>) and the second support (<NUM>) in the axial direction (L); and
a protrusion (<NUM>) protruding toward the first side (L1) of the body (<NUM>) in the axial direction (L); and
the press member (<NUM>) has an insertion hole (<NUM>) extending through the press member (<NUM>) in the axial direction (L) and configured to receive the protrusion (<NUM>).