Patent Description:
Conventionally, as a hybrid drive device of this type, a hybrid drive device including a case for housing a rotary electric machine and a clutch, and a rotor support member that supports a rotor and that is rotatably supported by the case is known (for example, see <CIT>). The case of this hybrid drive device includes a support wall portion extending in a radial direction on the engine side, and an annular boss portion that protrudes in an axial direction toward the transmission is formed in an inner peripheral portion of the support wall portion. An annular plate-shaped member is fixed to the rotor support member so as to face the support wall portion, and a tubular portion protruding in the axial direction toward the engine is formed on an inner periphery of the plate-shaped member. Further, a ball bearing is disposed between an inner peripheral surface of the boss portion of the support wall portion and an outer peripheral surface of the tubular portion of the plate-shaped member. As a result, the rotor support member, that is, the rotor of the rotary electric machine is rotatably supported and supported in the radial direction by the case via the ball bearing. Further, a radial bearing is disposed between an inner peripheral surface of the tubular portion of the plate-shaped member and an outer peripheral surface of an input member driven by the engine. As a result, the input member is rotatably supported and supported in the radial direction by the case via the ball bearing, the tubular portion of the plate-shaped member, and the radial bearing.

<CIT> and <CIT> disclose further hybrid drive devices.

In the conventional hybrid drive device described above, a deflection with respect to the axis of a crankshaft is generated in accordance with a rotation of the engine and transmitted to the input member described above. Thus, the input member also deflects with respect to the axis, and the deflection of the input member is transmitted to the ball bearing via the radial bearing and the tubular portion of the plate-shaped member. Further, in the hybrid drive device described above, one of an inner race and an outer race of the ball bearing is press-fitted into the support wall portion of the case or the tubular portion of the plate-shaped member, and the other is press-fitted into the tubular portion of the plate-shaped member or the support wall portion of the case. Thus, in the hybrid drive device described above, wear may occur at a fitting portion of the ball bearing and the plate-shaped member or the case due to the deflection of the input member, and the rotor support member may not be appropriately supported by the case. Further, since the deflection of the input member is transmitted to the ball bearing, the increase in the load may lead to an increase in the size of the ball bearing.

Therefore, it is a main object of the present disclosure to appropriately support the rotor of the rotary electric machine of the hybrid drive device and to reduce the size of the bearing for supporting the rotor in the radial direction.

A hybrid drive device of the present disclosure includes a rotary electric machine having a stator and a rotor, a transmission coupled to the rotary electric machine, a clutch that couples an engine and the rotary electric machine and that releases connection of the two, and a case for housing the rotary electric machine and the clutch, and the hybrid drive device includes: a first transmitting shaft coupled to an output shaft of the engine; a second transmitting shaft that transmits power from the rotor of the rotary electric machine to the transmission; and a rotor support member that supports the rotor of the rotary electric machine, in which the case includes an end wall portion that is extended so as to face the rotary electric machine and the clutch on the engine side, the rotor support member includes an annular member that is disposed so as to face the end wall portion of the case, the end wall portion includes a first tubular portion that protrudes in an axial direction from an inner periphery toward the transmission, and a second tubular portion that protrudes in the axial direction toward the transmission so as to surround the first tubular portion, the annular member includes a tubular portion that protrudes in the axial direction from an inner periphery toward the engine, an inner side radial bearing is disposed between the first transmitting shaft and an inner peripheral surface of the first tubular portion of the end wall portion, a clearance is formed between an outer peripheral surface of the first tubular portion of the end wall portion and an inner peripheral surface of the tubular portion of the annular member, and an outer side radial bearing is disposed between an outer peripheral surface of the tubular portion of the annular member and an inner peripheral surface of the second tubular portion of the end wall portion.

In the hybrid drive device of the present disclosure, the case includes the end wall portion that is extended so as to face the rotary electric machine and the clutch on the engine side, the rotor support member includes the annular member that faces the end wall portion of the case. The end wall portion of the case includes the first tubular portion that protrudes in the axial direction from the inner periphery toward the transmission, and the second tubular portion that protrudes in the axial direction toward the transmission so as to surround the first tubular portion, and the annular member described above includes the tubular portion that protrudes in the axial direction from the inner periphery toward the engine. The inner side radial bearing that supports the first transmitting shaft in the radial direction is disposed between the first transmitting shaft that is coupled to the output shaft of the engine and the inner peripheral surface of the first tubular portion of the end wall portion, the clearance is formed between the outer peripheral surface of the first tubular portion and the inner peripheral surface of the tubular portion of the annular member. The outer side radial bearing for supporting the rotor support member in the radial direction is disposed between the outer peripheral surface of the tubular portion of the annular member and the inner peripheral surface of the second tubular portion of the end wall portion. Thus, even if deflection of the first transmitting shaft with respect to the shaft center occurs in accordance with the rotation of the engine, since the clearance is formed between the outer peripheral surface of the first tubular portion and the inner peripheral surface of the tubular portion of the annular member, the deflection of the first transmitting shaft does not affect the tubular portion of the annular member. Thus, in the hybrid drive device of the present disclosure, the rotor support member can be properly supported by the case via the outer side radial bearing. Further, since the first transmitting shaft is supported in the radial direction by the end wall portion of the case via the inner side radial bearing, a torque fluctuation (vibration) of the engine transmitted to the first transmitting shaft is no longer directly transmitted to the outer side radial bearing. As a result, in the hybrid drive device of the present disclosure, the load acting on the outer side radial bearing for supporting the rotor support member, that is, the rotor of the rotary electric machine in the radial direction can be decreased, the durability thereof can be further improved, and the outer side radial bearing can be decreased in size (the cost can be decreased).

Next, embodiments for carrying out the invention of the present disclosure will be described with reference to the drawings.

<FIG> is a schematic configuration diagram showing a hybrid drive device <NUM> of the present disclosure. <FIG> and <FIG> are enlarged views showing the hybrid drive device <NUM>. The hybrid drive device <NUM> is mounted on a vehicle <NUM> and generates a driving force for traveling, and as shown in <FIG>, includes an engine <NUM>, a motor generator (rotary electric machine) MG, a first transmitting shaft <NUM> coupled to the engine <NUM>, a second transmitting shaft <NUM> to which power is transmitted from the motor generator MG, a clutch K0 that couples the first and second transmitting shafts <NUM>, <NUM> and that releases the connection of the two, and a power transmitting device <NUM>. The hybrid drive device <NUM> may be mounted on a rear-wheel drive vehicle as illustrated, may be mounted on a front-wheel drive vehicle, or may be mounted on a four-wheel drive vehicle including a transfer coupled to the power transmitting device <NUM>.

The engine <NUM> is an internal combustion engine that converts a reciprocating motion of a piston (not shown) in accordance with the combustion of a mixture of hydrocarbon fuel such as gasoline or light oil and air into a rotational motion of a crankshaft (output shaft) <NUM>. The crankshaft <NUM> of the engine <NUM> is coupled to the first transmitting shaft <NUM> via an annular coupling member <NUM> and a damper mechanism <NUM>. For example, the damper mechanism <NUM> includes an input element coupled to the crankshaft <NUM> via the coupling member <NUM>, an output element coupled to the first transmitting shaft <NUM>, and a plurality of coil springs (elastic bodies) that transmits a torque between the input element and the output element and that dampens a torsional vibration.

The motor generator MG is a synchronous generator motor (three-phase alternating current motor), and transmits and receives electric power to and from a power storage device (battery, not shown) via an inverter that is not shown. The motor generator MG operates as an electric motor that is driven by electric power from the power storage device to generate a drive torque, and outputs a regenerative braking torque when the vehicle <NUM> is braked. The motor generator MG also operates as a generator that generates electric power by using at least a part of the power from the engine <NUM> that is operated under load.

As shown in <FIG>, the motor generator MG includes a stator <NUM> and a rotor <NUM> housed in a motor case <NUM>. The motor case <NUM> includes a housing <NUM> having one end open and a cover <NUM> fixed to the housing <NUM> so as to cover the one end. The housing <NUM> of the motor case <NUM> is a generally bottomed tubular body in which one end in the axial direction, that is, an end portion on the engine <NUM> side is opened, and the other end in the axial direction, that is, an end portion on the power transmitting device <NUM> side is closed. In the present embodiment, the housing <NUM> is formed by casting an aluminum alloy, and includes a tubular outer shell portion <NUM> and an end wall (wall portion) <NUM> that closes the other end of the outer shell portion <NUM>.

As shown in <FIG>, a front side flange portion 81f having a plurality of bolt holes is formed on one end (front end) of the outer shell portion <NUM> of the housing <NUM>, that is, on an outer periphery on an open end side. The front side flange portion 81f is fastened (fixed) to an engine block of the engine <NUM> via a plurality of bolts that is not shown and that is each inserted into a corresponding bolt hole. Further, the other end portion of the outer shell portion <NUM> protrudes from the end wall <NUM> toward the opposite side from the front side flange portion 81f, and a rear side flange portion 81r having a plurality of bolt holes is formed on an outer periphery of the other end (rear end) of the outer shell portion <NUM>. The rear side flange portion 81r is fastened (fixed) to an end portion (front end) of a transmission case <NUM> (see <FIG>) of the power transmitting device <NUM> via a plurality of bolts that is not shown and that is each inserted into the corresponding bolt hole.

Further, a tubular shaft support portion <NUM> having a through hole is provided in a center portion of the end wall <NUM> of the housing <NUM>, and the second transmitting shaft <NUM> protrudes from the through hole of the tubular support portion <NUM> toward the power transmitting device <NUM> side. The shaft support portion <NUM> may be formed integrally with the end wall <NUM>, or the shaft support portion <NUM> separate from the housing <NUM> may be fixed to the end wall <NUM>. A flange portion 142f (see <FIG>) is formed on an end portion of the second transmitting shaft <NUM> protruding from the end wall <NUM>, and an inner peripheral portion of a flex plate <NUM> is fastened (fixed) to the flange portion 142f via a plurality of bolts not shown. Further, a seal member <NUM> is disposed in a clearance between the second transmitting shaft <NUM> and the shaft support portion <NUM>.

The cover <NUM> of the motor case <NUM> is a disk-shaped member formed by casting an aluminum alloy. As shown in <FIG>, the cover <NUM> includes a flange portion 88f having a plurality of bolt holes arranged at intervals along the outer periphery, a through hole through which the first transmitting shaft <NUM> is inserted, and a plurality of boss portions 88b each having a screw hole and that is formed at intervals in the circumferential direction. A seal member <NUM> is disposed in a clearance between the cover <NUM> and the first transmitting shaft <NUM> inserted through the through hole of the cover <NUM>.

As shown in <FIG>, the stator <NUM> includes an annular stator core <NUM> and a stator coil <NUM> wound around the stator core <NUM>. The stator core <NUM> is integrally formed by stacking a plurality of electromagnetic steel plates formed in an annular shape by press working and coupling the plurality of electromagnetic steel plates in a stacking direction, for example. A plurality of bolt holes extending in the axial direction is formed in the stator core <NUM>, and a bolt <NUM> is inserted into each bolt hole. Each bolt <NUM> is screwed into the screw hole of the corresponding boss portion 88b of the cover <NUM> and thus, the stator <NUM> is fixed to the cover <NUM>.

The cover <NUM> to which the stator <NUM> is fixed is fixed to the housing <NUM> via a plurality of bolts <NUM> so that the stator <NUM> is surrounded by the outer shell portion <NUM> and a coil end 22b faces the end wall <NUM>. As a result, the stator <NUM> is non-rotatably fixed to the motor case <NUM>, and the cover <NUM> forms an end wall portion of the motor case <NUM> extending in the radial direction so as to face the motor generator MG and the clutch K0 on the engine <NUM> side. Further, in the present embodiment, as shown in <FIG>, the cover <NUM> is fixed to the housing <NUM> so as to be close to the front side flange portion 81f, that is, a fastening portion (fixing portion) between the housing <NUM> and the engine block. This makes it possible to fix the cover <NUM> and the stator <NUM> to the engine block and the housing <NUM> more firmly.

The stator coil <NUM> includes three coils of a U phase, a V phase and a W phase, and includes a coil end 22a protruding from an end surface on the damper mechanism <NUM> side (left side in <FIG>) in the axial direction of the stator core <NUM>, and a coil end 22b protruding from an end surface on the power transmitting device <NUM> side (right side in <FIG>). One end portion of the U phase, V phase, and W phase coils protrudes in the axial direction from the coil end 22b and is used as a terminal 22c of each phase. The terminal 22c of each phase is electrically coupled to an inverter (not shown) via a bus bar (not shown) of the V phase, the U phase, or the W phase corresponding to each terminal 22c.

As shown in <FIG>, the rotor <NUM> includes a rotor core <NUM>, end plates <NUM>, <NUM> disposed on both sides of the rotor core <NUM> in the axial direction, and a rotor support member <NUM> for holding the rotor core <NUM> and the like. The rotor core <NUM> is formed by stacking a plurality of electromagnetic steel plates formed in an annular shape by press working, for example. Further, a plurality of through holes (not shown) each extending in the axial direction at intervals in the circumferential direction is formed in the rotor core <NUM>, and a permanent magnet is embedded in each through hole.

The rotor support member <NUM> includes an annular outer side half portion <NUM>, an annular inner side half portion <NUM> fixed to the outer side half portion <NUM>, and an annular plate member (annular member) <NUM>. Both the outer side half portion <NUM> and the inner side half portion <NUM> are formed by machining a forged body made of a steel material (made of an iron alloy), for example. The plate member <NUM> is also made of steel material. As shown in <FIG>, the outer side half portion <NUM> includes a cylindrical outer tubular portion (tubular support portion) <NUM> in which the rotor core <NUM> is fixed to an outer peripheral portion, an annular flange portion <NUM> extended radially outward from one end (left end in <FIG>) of the outer tubular portion <NUM> in the axial direction, and an annular radial protruding portion <NUM> protruding radially inward along the entire circumference from the other end side (right end in <FIG>) of the center portion of the outer tubular portion <NUM> in the axial direction. The rotor core <NUM> is fixed to the outer tubular portion <NUM> of the rotor support member <NUM> by shrink fitting processing in a state in which the end plates <NUM>, <NUM> are disposed on both sides in the axial direction. Further, the end plate <NUM> positioned on the opposite side of the flange portion <NUM> is fixed to the outer tubular portion <NUM> by swaging or the like. However, the rotor core <NUM> may be fixed to the outer tubular portion <NUM> by press fitting.

The inner side half portion <NUM> includes: an annular wall portion <NUM> extended in the radial direction; an inner tubular portion <NUM> that has a tubular shape and that is extended from an inner peripheral portion of the annular wall portion <NUM> to one side (left side in <FIG>) in the axial direction; a cylindrical supported portion <NUM> extended from the annular wall portion <NUM> to the other side (right side in <FIG>), on an outer radial side of the inner tubular portion <NUM>; and a short tubular piston support portion <NUM> extended from the annular wall portion <NUM> to one side in the axial direction, on an outer radial side of the supported portion <NUM>. In the present embodiment, on a surface on the opposite side of the annular wall portion <NUM> from the piston support portion <NUM>, at least one recess portion 46a recessed to the piston support portion <NUM> side (one side) is formed so as to at least partially overlap with the piston support portion <NUM> when viewed in the axial direction of the rotor <NUM>. The recess portion 46a is formed in the annular wall portion <NUM> in order to correct the imbalance of the entire rotor <NUM> after the rotor core <NUM> and the end plates <NUM>, <NUM> are fixed to the rotor support member <NUM>.

As shown in <FIG>, an outer periphery of the annular wall portion <NUM> is fixed to an inner periphery of the radial protruding portion <NUM> of the outer side half portion <NUM> by welding. Further, an outer peripheral portion of the plate member <NUM> is fastened to the flange portion <NUM> of the rotor support member <NUM> (outer side half portion <NUM>) by a plurality of bolts 43b so as to face the annular wall portion <NUM> at a distance in the axial direction. In the present embodiment, the plate member <NUM> is fixed to the flange portion <NUM> in a state in which a surface of the outer peripheral portion is in contact with an end surface (left side end surface in <FIG>) on the opposite side of the flange portion <NUM> from the rotor <NUM> side. Further, an axial protruding portion 43p that has a short cylindrical (annular) shape is formed in the flange portion <NUM> so as to protrude in the axial direction from an outer peripheral portion of the end surface, with which the plate member <NUM> is in contact, to the opposite side (engine <NUM> side) from the rotor core <NUM> side. As a result, the outer peripheral surface of the plate member <NUM> is supported in the radial direction by the axial protruding portion 43p of the flange portion <NUM>. A plurality of the axial protruding portions 43p may be formed on the outer peripheral portion of the end surface of the flange portion <NUM> at intervals in the circumferential direction.

Further, an outer peripheral surface of the supported portion <NUM> of the rotor support member <NUM> (inner side half portion <NUM>) is supported in the radial direction and is supported so as to be rotatable by the motor case <NUM> via a radial bearing Brr (ball bearing in the present embodiment) held by the end wall <NUM> of the housing <NUM>. The movement of the rotor support member <NUM> toward a speed change mechanism <NUM> side is restricted by the housing <NUM>, that is, the case <NUM> via the radial bearing Brr. In contrast, the inner peripheral portion of the plate member <NUM> is supported in the radial direction and is supported so as to be rotatable by the cover <NUM> of the motor case <NUM> via a radial bearing Brf (an outer side radial bearing, in the present embodiment, a ball bearing). As a result, the rotor <NUM> is supported in the radial direction by the motor case <NUM> via the radial bearing Brf. Further, the inner tubular portion <NUM> of the rotor support member <NUM> includes a spline formed on an inner peripheral surface of a tip end portion (an end portion on the engine <NUM> side), and is always coupled (fixed) to the second transmitting shaft <NUM> via the spline.

The clutch K0 couples the first transmitting shaft <NUM>, that is, the crankshaft <NUM> of the engine <NUM>, and the second transmitting shaft <NUM>, that is, the rotor <NUM> of the motor generator MG, and releases the connection of the two. In the present embodiment, the clutch K0 is a multi-plate friction type hydraulic clutch that uses the rotor support member <NUM> of the rotor <NUM> that is always coupled to the second transmitting shaft <NUM> as a clutch drum, and is disposed in the motor case <NUM>, that is, on the inner radial side of the rotor <NUM>. As shown in <FIG>, in addition to the rotor support member <NUM> serving as a clutch drum, the clutch K0 includes a clutch hub <NUM> that is disposed between the annular wall portion <NUM> of the rotor support member <NUM> and the plate member <NUM> in the axial direction and that is always coupled (fixed) to the first transmitting shaft <NUM>, a plurality of friction plates (second friction engagement plates) <NUM>, a plurality of separator plates (first friction engagement plates) <NUM> and backing plates <NUM> that are alternately arranged with the friction plates <NUM>, a snap ring <NUM>, a piston <NUM>, a plurality of return springs SP, and a cancel plate (cancel oil chamber defining member) <NUM>.

As shown in <FIG>, the clutch hub <NUM> includes a tubular portion 61a and an annular wall portion 61b extended radially inward from one end of the tubular portion 61a. Splines <NUM> are formed on an outer peripheral surface of the tubular portion 61a, and an inner periphery of the annular wall portion 61b is fixed to the first transmitting shaft <NUM>. Further, splines <NUM> are formed on the inner peripheral surface of the outer tubular portion <NUM> of the rotor support member <NUM> serving as the clutch drum so as to be positioned closer to the flange portion <NUM> side than the radial protruding portion <NUM>.

The friction plate <NUM> is an annular member to which a friction material is attached to both surfaces, and an outer peripheral portion of each friction plate <NUM> is fitted to the splines <NUM> (inner peripheral portion) of the outer tubular portion <NUM>. Further, the backing plate <NUM> is fitted to the splines <NUM> of the outer tubular portion <NUM> so as to be able to come into contact with the friction plate <NUM> farthest from the piston <NUM> among the plurality of friction plates <NUM>. The separator plate <NUM> is an annular member in which both surfaces are formed to be smooth, and an inner peripheral portion of each separator plate <NUM> is fitted to the splines <NUM> (outer peripheral portion) formed in the tubular portion 61a of the clutch hub <NUM>.

Further, an annular recess portion 42a that is recessed radially outward is formed in the splines <NUM> of the outer tubular portion <NUM>. The snap ring <NUM> is attached (fitted) to the annular recess portion 42a, and the movement of the backing plate <NUM>, etc. in the axial direction (the movement in a direction away from the piston <NUM>) is restricted by the snap ring <NUM>. In the present embodiment, when viewed in the radial direction of the rotor <NUM>, the annular recess portion 42a is formed in the splines <NUM> so as to overlap in the axial direction with a part of the flange portion <NUM> (including the annular plate disposed between the flange portion <NUM> and the end plate <NUM>), more specifically, an end surface (an end surface in contact with the end plate <NUM>) on the rotor <NUM> side of the flange portion <NUM>.

That is, in the present embodiment, the flange portion <NUM> is extended radially outward from one end in the axial direction of the outer tubular portion <NUM> of the rotor support member <NUM>, and the radial protruding portion <NUM> and the annular wall portion <NUM> are extended radially inward from the other end side of the center portion in the axial direction of the outer tubular portion <NUM>. In such a configuration, when the rotor core <NUM> is fixed to the outer tubular portion <NUM> by shrink fitting processing or press fitting, according to the experiments and analysis by the present inventors, it was found that a relatively large stress acts on the outer tubular portion <NUM> from the rotor core <NUM> between the flange portion <NUM> and the radial protruding portion <NUM> in the axial direction. Thus, when the annular recess portion 42a is formed between the flange portion <NUM> of the outer tubular portion <NUM> and the radial protruding portion <NUM> in the axial direction, the stress from the rotor core <NUM> is concentrated in the annular recess portion 42a and there is a possibility that the durability of the outer tubular portion <NUM> as well as the rotor support member <NUM> as a whole is decreased. Based on this, in the present embodiment, the annular recess portion 42a is formed in the outer tubular portion <NUM> so as to overlap with a part of the flange portion <NUM> (the end surface on the rotor <NUM> side) in the axial direction when viewed in the radial direction of the rotor <NUM>. As a result, it is possible to suppress the stress acting on the outer tubular portion <NUM> from the rotor core <NUM> from being concentrated in the annular recess portion 42a, and satisfactorily ensure the durability of the rotor support member <NUM>.

Then, in the hybrid drive device <NUM>, since the plate member <NUM> is coupled to the flange portion <NUM> in a state in which the plate member <NUM> is in contact with the end surface on the opposite side of the flange portion <NUM> from the rotor <NUM> side, the annular recess portion 42a can be formed in the outer tubular portion <NUM> so as to overlap with at least a part of the flange portion <NUM>. In addition, when the plate member <NUM> is fastened to the flange portion <NUM> by the bolt 43b, since a thickness (axial length) of the flange portion <NUM> is ensured to some extent, it is possible to further improve the durability of the rotor support member <NUM> by making the end surface on the radial protruding portion <NUM> side of the annular recess portion 42a substantially flush with the end surface on the rotor <NUM> side of the flange portion <NUM>, when viewed in the radial direction of the rotor <NUM>.

The piston <NUM> includes an annular pressure receiving portion 67a, a tubular supported portion 67b extended from an outer periphery of the pressure receiving portion 67a to the clutch hub <NUM> side in the axial direction, and a pressing portion 67c formed radially outward of the supported portion 67b, and the piston <NUM> is disposed between the annular wall portion <NUM> of the rotor support member <NUM> and the plate member <NUM> in the axial direction. An inner peripheral surface of the pressure receiving portion 67a of the piston <NUM> is supported so as to be movable in the axial direction by an outer peripheral surface of the inner tubular portion <NUM> of the rotor support member <NUM> serving as a clutch drum via the seal member. Further, the outer peripheral surface of the pressure receiving portion 67a is movably supported in the axial direction by the inner peripheral surface of the piston support portion <NUM> of the rotor support member <NUM> via a seal member, and an engagement oil chamber 69a of the clutch K0 is defined between the annular wall portion <NUM> of the rotor support member <NUM> and the pressure receiving portion 67a of the piston <NUM>. Further, a plurality of recess portions (grooves) loosely fitted in the splines <NUM> of the outer tubular portion <NUM> of the rotor support member <NUM> is formed in the outer peripheral portion of the pressing portion 67c at intervals in the circumferential direction. Thus, the piston <NUM> can be stopped from rotating with respect to the outer tubular portion <NUM>, and the piston <NUM> and the outer tubular portion <NUM> can be rotated integrally.

The cancel plate <NUM> is an annular member disposed on an opposite side of the piston <NUM> from the annular wall portion <NUM> of the rotor support member <NUM>. An inner peripheral portion of the cancel plate <NUM> is fixed to the inner tubular portion <NUM> of the rotor support member <NUM> by using a snap ring. Further, an outer peripheral surface of the cancel plate <NUM> movably supports an inner peripheral surface of the supported portion 67b of the piston <NUM> via a seal member, in the axial direction. As a result, a centrifugal hydraulic pressure cancel chamber 69b for canceling a centrifugal hydraulic pressure generated in the engagement oil chamber 69a is defined between the pressure receiving portion 67a of the piston <NUM> and the cancel plate <NUM>. Further, the plurality of return springs (coil springs) SP is disposed at intervals in the circumferential direction between the pressure receiving portion 67a of the piston <NUM> and the cancel plate <NUM> in the axial direction. Each return spring SP urges the piston <NUM> to a side away from the friction plate <NUM> and the separator plate <NUM>.

The power transmitting device <NUM> includes units such as a torque converter (fluid transmission device) <NUM> having a torque amplification function, a lockup clutch CL, the speed change mechanism (automatic transmission) <NUM>, a mechanical oil pump <NUM>, and a hydraulic control device <NUM> that adjust working oil pressure, the transmission case <NUM> that houses the speed change mechanism <NUM>, etc. The torque converter <NUM> includes a front cover serving as an input member that is always coupled to the second transmitting shaft <NUM> via the flex plate <NUM> (see <FIG> and <FIG>), a pump impeller fixed to the front cover, and a turbine runner coupled to an input shaft 17i of the speed change mechanism <NUM>, and a stator that rectifies the flow of the working oil from the turbine runner to the pump impeller so as to amplify the torque. However, the power transmitting device <NUM> may include a fluid coupling that has no stator, instead of the torque converter <NUM>. The lockup clutch CL couples the front cover and the input shaft 17i of the speed change mechanism <NUM> and releases the connection of the two.

The speed change mechanism <NUM> is, for example, a <NUM>-speed to <NUM>-speed type multi-speed transmission including an output shaft 17o, a plurality of planetary gears, a plurality of clutches and a plurality of brakes (engagement elements for shifting), in addition to the input shaft 17i. The speed change mechanism <NUM> shifts a power transmitted from at least one of the engine <NUM> and the motor generator MG to the input shaft 17i via the second transmitting shaft <NUM> and either one of the torque converter <NUM> and the lockup clutch CL, in a plurality of stages, to output from the output shaft 17o to left and right drive wheels DW via a differential gear DF. However, the speed change mechanism <NUM> may be a dual clutch transmission or a mechanical continuously variable transmission. The torque converter <NUM> and the lockup clutch CL may be omitted from the power transmitting device <NUM>. In this case, the speed change mechanism <NUM> may be coupled to the motor generator MG (the rotor support member <NUM> or the second transmitting shaft <NUM>) via a clutch different from the clutch K0.

The oil pump <NUM> is a gear pump or a vane pump coupled to the pump impeller of the torque converter <NUM> via a winding transmitting mechanism, and is disposed on a shaft different from the input shaft 17i of the speed change mechanism <NUM>. The oil pump <NUM> is driven by the power from the second transmitting shaft <NUM> via the winding transmitting mechanism, and sucks the working oil (ATF) stored in a working oil storage portion (not shown) to pressure-feed to the hydraulic control device <NUM>. The hydraulic control device <NUM> includes a valve body in which a plurality of oil passages is formed, a plurality of regulator valves, a plurality of linear solenoid valves, and the like. The hydraulic control device <NUM> adjusts the hydraulic pressure (working oil) from the oil pump <NUM> and supplies the hydraulic pressure to the torque converter <NUM>, the lockup clutch CL, the clutches and the brakes of the speed change mechanism <NUM>. The transmission case <NUM> is a cast product made of an aluminum alloy.

In addition, the hybrid drive device <NUM> includes a second hydraulic control device <NUM> that supplies hydraulic pressure to the clutch K0. The hydraulic control device <NUM> is attached to a lower portion of the motor case <NUM> and adjusts the hydraulic pressure from the oil pump <NUM> to supply the hydraulic pressure to the engagement oil chamber 69a of the clutch K0 and the like. When the hydraulic pressure of the hydraulic control device <NUM> is supplied to the engagement oil chamber 69a via a radial oil passage <NUM> formed in the housing <NUM> (shaft support portion <NUM>) of the motor case <NUM>, an axial oil passage L1 and a radial oil passage L3 formed in the second transmitting shaft <NUM>, and an oil hole 47a formed in the inner tubular portion <NUM> of the rotor support member <NUM>, the piston <NUM> moves toward the cancel plate <NUM> by the action of an engagement hydraulic pressure. As a result, the separator plate <NUM> and the friction plate <NUM> are pressed by the pressing portion 67c and are frictionally engaged, and the clutch K0 is engaged. Further, the working oil drained from the hydraulic control device <NUM> is supplied to the centrifugal hydraulic pressure cancel chamber 69b of the clutch K0 via a radial oil passage <NUM> formed in the end wall <NUM> (shaft support portion <NUM>), the axial oil passage L2 and a radial oil passage L4 formed in the second transmitting shaft <NUM>, and the oil hole 47a formed in the inner tubular portion <NUM> of the rotor support member <NUM> so as to be side by side with an oil hole 47b in the axial direction. The hydraulic control device <NUM> may be omitted from the hybrid drive device <NUM>, and in this case, the clutch K0 may be supplied with the hydraulic pressure from the hydraulic control device <NUM> of the power transmitting device <NUM>. Further, the centrifugal hydraulic pressure cancel chamber 69b may be omitted from the clutch K0.

Subsequently, with reference to <FIG>, support structures of the first and second transmitting shafts <NUM>, <NUM> and the rotor support member <NUM> in the hybrid drive device <NUM>, etc. will be described in detail.

As shown in <FIG>, the first transmitting shaft <NUM> includes a first end portion 141a on the engine <NUM> side (left side in <FIG>), a second end portion 141b on the speed change mechanism <NUM> side (right side in <FIG>), and a disc-shaped expanded radius portion 141e formed between the first and second end portions 141a, 141b in the axial direction. The first end portion 141a has an outer peripheral surface having columnar surface shape, and the second end portion 141b is formed in a cylindrical shape (tubular shape) having a radius smaller than that of the first end portion 141a, as illustrated. The expanded radius portion 141e of the first transmitting shaft <NUM> is formed to have a larger radius than that of the first and second end portions 141a, 141b, and is adjacent to the second end portion 141b on the engine <NUM> side. That is, the second end portion 141b protrudes from an end surface of the expanded radius portion 141e on the speed change mechanism <NUM> side to the opposite side of the first end portion 141a.

Further, an annular flange portion 141f is extended from the expanded radius portion 141e of the first transmitting shaft <NUM>. The flange portion 141f is extended radially outward and toward the speed change mechanism <NUM> side, from the outer peripheral portion of the expanded radius portion 141e so as to surround a part (about half of the expanded radius portion 141e side) of the second end portion 141b on the speed change mechanism <NUM> side of the plate member <NUM> of the rotor support member <NUM>. In the present embodiment, an inner peripheral portion of a surface of the flange portion 141f on the speed change mechanism <NUM> side is formed in a conical surface shape so that a radius decreases from the speed change mechanism <NUM> side toward the engine <NUM> side. The inner periphery of the annular wall portion 61b of the clutch hub <NUM> is fixed to an outer peripheral portion of the flange portion 141f by welding. Further, a thrust bearing (outer side thrust bearing) Btm that supports the first transmitting shaft <NUM> in the axial direction is disposed between the flange portion 141f and the inner peripheral portion of the plate member <NUM> facing the flange portion 141f.

An end portion 142a of the second transmitting shaft <NUM> on the engine <NUM> side is formed in a cylindrical shape (tubular shape) having an outer radius smaller than an outer radius of the expanded radius portion 141e of the first transmitting shaft <NUM> and an inner radius larger than an outer radius of the second end portion 141b of the first transmitting shaft <NUM>. An internal space of the end portion 142a communicates with an axial oil passage L2 of the second transmitting shaft <NUM>. Further, splines into which the splines of the inner tubular portion <NUM> of the rotor support member <NUM> are fitted are formed on an outer peripheral surface of the end portion 142a.

The first end portion 141a of the first transmitting shaft <NUM> is supported in the radial direction by the crankshaft <NUM> of the engine <NUM> via the coupling member <NUM> that couples the crankshaft <NUM> and the damper mechanism <NUM>, and a radial bearing Br0 (a fourth radial bearing, a ball bearing in the present embodiment). Further, the expanded radius portion 141e of the first transmitting shaft <NUM> is supported in the radial direction, between the first and second end portions 141a, 141b in the axial direction, by the cover <NUM> that is an end wall portion of the motor case <NUM> on the engine <NUM> side via a radial bearing Br1 (a first radial bearing or an inner side radial bearing). As shown in <FIG>, the cover <NUM> includes a cylindrical first tubular portion <NUM> that protrudes from an inner periphery thereof toward the speed change mechanism <NUM> side so as to define a through hole through which the first transmitting shaft <NUM> is inserted. The radial bearing Br1 is disposed between an inner peripheral surface of the first tubular portion <NUM> and an outer peripheral surface of the expanded radius portion 141e of the first transmitting shaft <NUM> so as to be positioned on the speed change mechanism <NUM> side (right side in the figure) than the seal member <NUM> described above. In the present embodiment, the radial bearing Br1 is a cylindrical roller bearing including a cup that is press-fitted into the first tubular portion <NUM> of the cover <NUM>.

The second end portion 141b of the first transmitting shaft <NUM> is inserted into the end portion 142a that is formed in a tubular shape and that is on the engine <NUM> side of the second transmitting shaft <NUM>, and a radial bearing Br2 (a second radial bearing or an intermediate radial bearing) that supports the second transmitting shaft <NUM> in the radial direction is disposed between the outer peripheral surface of the second end portion 141b of the first transmitting shaft <NUM> and the inner peripheral surface of the end portion 142a of the second transmitting shaft <NUM> (therebetween in the radial direction). In the present embodiment, the radial bearing Br2 is a cylindrical roller bearing including a cup that is press-fitted into the end portion 142a of the second transmitting shaft <NUM>. As can be seen from <FIG>, when viewed in the radial direction, the radial bearing Br2 overlaps at least partially with the clutch hub <NUM> fixed to the outer peripheral portion of the flange portion 141f of the first transmitting shaft <NUM>, in the axial direction.

Further, between the end surface on the engine <NUM> side of the second transmitting shaft <NUM>, that is, an end surface of the end portion 142a and the end surface on the speed change mechanism <NUM> side of the expanded radius portion 141e in the axial direction, a thrust bearing (inner side thrust bearing) Bt1 that supports the first and second transmitting shafts <NUM>, <NUM> in the axial direction is disposed. In the present embodiment, a thrust bearing that includes a single cage is adopted as the thrust bearing Bt1 in order to ensure oil permeability. As illustrated, a clearance is formed between an inner peripheral portion of the flange portion 141f of the first transmitting shaft <NUM> and the end portion 142a of the second transmitting shaft <NUM>.

Further, as shown in <FIG>, an internal space communicating with the axial oil passage L2 is defined between the end surface of the second end portion 141b of the first transmitting shaft <NUM> and an inner end surface in which the axial oil passage L2 in the end portion 142a of the second transmitting shaft <NUM> opens. Further, the first transmitting shaft <NUM> includes a plurality of inner side oil holes (first oil holes) hi formed in the second end portion 141b at intervals in the circumferential direction, and a plurality of outer side oil holes (second oil holes) ho each formed at intervals in the circumferential direction so as to pass through a vicinity of a base end portion of the flange portion 141f of the first transmitting shaft <NUM>.

The plurality of inner side oil holes hi is each opened on an inner peripheral surface of the second end portion 141b, is opened between the radial bearing Br2 and the thrust bearing Bt1 on the outer peripheral surface of the second end portion 141b and the thrust bearing Bt1 in the axial direction, and forms an oil passage with an internal space that is opened at the end surface of the second end portion 141b. In the present embodiment, each inner side oil hole hi is formed obliquely so as to approach the engine <NUM> from the outer peripheral surface toward the inner peripheral surface of the second end portion 141b of the first transmitting shaft <NUM>. This makes it possible to form the plurality of inner side oil holes hi each passing through the second end portion 141b without causing a drill bit to interfere with the flange portion 141f that surrounds a part of the second end portion 141b. A plurality of outer side oil holes o is formed so as to at least partially overlap with the radial bearing Br1 and the thrust bearing Bt1 in the axial direction when viewed in the radial direction, and is extended in the radial direction.

Then, the second transmitting shaft <NUM> is supported in the radial direction by the shaft support portion <NUM> that is provided in the housing <NUM> (end wall <NUM>) of the motor case <NUM> on the speed change mechanism <NUM> side of the end portion 142a via a radial bearing (third radial bearing) Br3. In the present embodiment, the radial bearing Br3 is a cylindrical roller bearing including a cup that is press-fitted in the shaft support portion <NUM> of the housing <NUM>. Further, a thrust bearing Bt2 that supports the second transmitting shaft <NUM> in the axial direction is disposed between the flange portion 142f of the second transmitting shaft <NUM> and the end wall <NUM> of the housing <NUM> in the axial direction. In the present embodiment, the thrust bearing Bt2 includes two cages.

The shaft support portion <NUM> of the housing <NUM> is formed in the end wall <NUM> so as to have an axial length of approximately half an axial length of a part (cylindrical part) of the second transmitting shaft <NUM> excluding the flange portion 142f. Further, the inner tubular portion <NUM> of the rotor support member <NUM> is fitted to the second transmitting shaft <NUM> so as to be positioned closer to the engine <NUM> than the shaft support portion <NUM>. Further, splines on the inner peripheral surface of the inner tubular portion <NUM> are fitted to splines formed on the outer peripheral surface of the end portion 142a of the second transmitting shaft <NUM>, and a snap ring that restricts the axial movement of the inner tubular portion <NUM>, that is, the rotor support member <NUM> is attached to the end portion 142a. As a result, the rotor support member <NUM>, that is, the rotor <NUM> of the motor generator MG is always coupled to the second transmitting shaft <NUM>, and a fixing portion (spline fitting portion) f (see dotted line in <FIG>) of the inner tubular portion <NUM>, that is, the rotor support member <NUM> and the second transmitting shaft <NUM> is at least partially overlapped with the radial bearing Br2 in the axial direction when seen in the radial direction.

Further, as shown in <FIG>, the cover <NUM> of the motor case <NUM> includes a cylindrical second tubular portion <NUM> protruding in the axial direction toward the speed change mechanism <NUM> so as to surround the first tubular portion <NUM>. The second tubular portion <NUM> has an inner radius larger than an outer radius of the first tubular portion <NUM>. Further, the plate member <NUM> of the rotor support member <NUM> includes a cylindrical tubular portion <NUM> that protrudes in the axial direction from the inner periphery thereof toward the engine <NUM>. The tubular portion <NUM> of the plate member <NUM> has an inner radius larger than the outer radius of the first tubular portion <NUM> of the cover <NUM> and has an outer radius smaller than an inner radius of the second tubular portion <NUM>.

An outer race of the radial bearing Brf (ball bearing) is press-fitted into the second tubular portion <NUM> so as not to come into contact with a surface (inner side surface) of the cover <NUM> on the speed change mechanism <NUM> side, and the tubular portion <NUM> of the plate member <NUM> is fitted in an inner race of the radial bearing Brf. As a result, the radial bearing Brf is disposed between an outer peripheral surface of the tubular portion <NUM> of the plate member <NUM> and an inner peripheral surface of the second tubular portion <NUM> of the cover <NUM>, and the plate member <NUM> is supported by the cover <NUM> via the radial bearing Brf so as to be rotatable and is also supported in the radial direction. Further, since the outer race of the radial bearing Brf is press-fitted into the second tubular portion <NUM> and the tubular portion <NUM> is fitted into the inner race of the radial bearing Brf, the movement of the plate member <NUM>, that is, the rotor support member <NUM> to the engine <NUM> side is restricted by the cover <NUM>, that is, the case <NUM> via the radial bearing Brf.

As described above, the inner radius of the tubular portion <NUM> of the plate member <NUM> is larger than the outer radius of the first tubular portion <NUM> of the cover <NUM>. Thus, as illustrated, an annular clearance a is formed between the outer peripheral surface of the first tubular portion <NUM> and the inner peripheral surface of the tubular portion <NUM> of the plate member <NUM>. Further, as shown in <FIG> and <FIG>, a plurality of (for example, three in the present embodiment) oil holes h1 is formed in the first tubular portion <NUM> of the cover <NUM> at intervals in the circumferential direction. Each oil hole h1 is opened on the outer peripheral surface of the first tubular portion <NUM> and is opened on the inner peripheral surface of the first tubular portion <NUM> between the radial bearing Br1 and the seal member <NUM> in the axial direction. That is, each oil hole h1 communicates with a space in the axial direction between the clearance a, the radial bearing Br1, and the seal member <NUM>.

Further, an end surface of the first tubular portion <NUM> of the cover <NUM> faces the flange portion 141f of the first transmitting shaft <NUM> at a distance, and an annular clearance b that communicates with the clearance a is formed between the end surface of the first tubular portion <NUM> and the flange portion 141f, as shown in <FIG>. The above clearance b also communicates with an inner peripheral portion of the space in which the thrust bearing Btm is disposed. In contrast, the end surface of the second tubular portion <NUM> of the cover <NUM> faces the plate member <NUM> at a distance, and an annular clearance c is formed between the end surface of the second tubular portion <NUM> (and the end surfaces of the inner race and outer race of the radial bearing Brf) and the plate member <NUM>.

Further, the second tubular portion <NUM> includes a plurality of (for example, two in the present embodiment) oil grooves g and a plurality of (for example, two in the present embodiment) oil holes h2. The plurality of oil grooves g is spaced at intervals in the circumferential direction on the inner peripheral surface of the second tubular portion <NUM> so that at least one oil groove g is positioned on an upper side in the motor case <NUM> and at least one oil groove g is positioned on a lower side in the motor case <NUM>, and each communicates with the clearance c and a space defined between an inner side surface of the cover <NUM> and the radial bearing Brf. As shown in <FIG> and <FIG>, the plurality of oil holes h2 is formed so that at least one oil hole h2 is positioned on the upper side in the motor case <NUM> and at least one oil hole h2 is positioned on the lower side in the motor case <NUM>, and each opens at the outer peripheral surface of the second tubular portion <NUM> and opens at a bottom surface (inner peripheral surface) of the corresponding oil groove g.

Further, as shown in <FIG> and <FIG>, the cover <NUM> includes a pair of oil collecting guides (protruding portions) <NUM> protruding from the inner side surface so as to be included in an upper side half region in the motor case <NUM>. The pair of oil collecting guides <NUM> is formed on the inner side surface of the cover <NUM> so that the oil collecting guides <NUM> are separated from each other (are opened to the left and right) from the vicinity of an uppermost portion of the second tubular portion <NUM> in the motor case <NUM> toward an outer radial side. Further, as shown in <FIG>, the base end portion of each oil collecting guide <NUM> protrudes to the vicinity of the end surface of the second tubular portion <NUM>. Further, in the present embodiment, one oil hole h2 is disposed between the base end portions of the pair of oil collecting guides <NUM>.

In the hybrid drive device <NUM> configured as described above, the first transmitting shaft <NUM> coupled to the crankshaft <NUM> of the engine <NUM> is supported in the radial direction by the cover <NUM> of the motor case <NUM> via the radial bearing (first radial bearing) Br1, between the first end portion 141a on the engine <NUM> side and the second end portion 141b on the speed change mechanism <NUM> side in the axial direction. The second end portion 141b of the first transmitting shaft <NUM> is inserted into the end portion 142a that is formed in a tubular shape and that is on the engine <NUM> side of the second transmitting shaft <NUM>, and a radial bearing (a second radial bearing) Br2 that supports the second transmitting shaft <NUM> in the radial direction is disposed between the outer peripheral surface of the second end portion 141b of the first transmitting shaft <NUM> and the inner peripheral surface of the end portion 142a of the second transmitting shaft <NUM>. Further, the second transmitting shaft <NUM> is supported in the radial direction by the shaft support portion <NUM> that is provided in the housing <NUM> of the motor case <NUM> on the speed change mechanism <NUM> side of the end portion 142a via a radial bearing (third radial bearing) Br3.

That is, the second transmitting shaft <NUM> is supported in the radial direction by the motor case <NUM> (cover <NUM>) via the radial bearing Br2, the first transmitting shaft <NUM>, and the radial bearing Br1 on the engine <NUM> side, and is supported in the radial direction by the shaft support portion <NUM> of the motor case <NUM> (housing <NUM>) via the radial bearing Br3 on the speed change mechanism <NUM> side. As a result, it is possible to satisfactorily suppress the shaft runout of the second transmitting shaft <NUM> that transmits power from the rotor <NUM> of the motor generator MG to the speed change mechanism <NUM>. Further, in the hybrid drive device <NUM>, since it is not necessary to extend the shaft support portion <NUM> of the motor case <NUM> to the engine <NUM> side so as to support the radial bearing Br2, the shaft support portion <NUM> can be shortened, and another member, that is, the rotor support member <NUM> (inner tubular portion <NUM>) can be disposed in the surplus space made as a result of the shaft support portion <NUM> being shortened. As a result, it is possible to shorten the axial length of the hybrid drive device <NUM> while suppressing a shaft runout of the second transmitting shaft <NUM>.

Further, in the hybrid drive device <NUM>, the inner tubular portion <NUM> of the rotor support member <NUM> is fitted to the second transmitting shaft <NUM> on the engine <NUM> side of the shaft support portion <NUM> of the motor case <NUM>, and the fixing portion f of the inner tubular portion <NUM> (rotor support member <NUM>) and the second transmitting shaft <NUM> is at least partially overlapped in the axial direction with the radial bearing Br2 when seen in the radial direction. As a result, the axial length of the hybrid drive device <NUM> can be further shortened by effectively utilizing the surplus space made by shortening the shaft support portion <NUM> of the motor case <NUM>.

Further, the first end portion 141a of the first transmitting shaft <NUM> is supported in the radial direction by the coupling member <NUM> that couples the crankshaft <NUM> of the engine <NUM> and the damper mechanism <NUM> via the radial bearing (fourth radial bearing) Br0. The first transmitting shaft <NUM> includes the expanded radius portion 141e having a radius larger than that of the second end portion 141b adjacent to the second end portion 141b on the engine <NUM> side, and the expanded radius portion 141e is supported in the radial direction by the cover <NUM> of the motor case <NUM> via the radial bearing Br1. This makes it possible to support both the first and second transmitting shafts <NUM>, <NUM> so that a shaft runout does not occur for the two.

Further, in the hybrid drive device <NUM>, the annular flange portion 141f is extended radially outward from the expanded radius portion 141e of the first transmitting shaft <NUM> so as to surround at least a part of the second end portion 141b on the speed change mechanism <NUM> side. The clutch hub <NUM> of the clutch K0 is fixed to the outer peripheral portion of the flange portion 141f so as to at least partially overlap with the radial bearing Br2 in the axial direction when viewed in the radial direction. As a result, it is possible to connect the first transmitting shaft <NUM> and the clutch hub <NUM> of the clutch K0 while shortening the axial length of the hybrid drive device <NUM>.

Further, the motor case <NUM> of the hybrid drive device <NUM> includes the cover <NUM> serving as the end wall portion extending so as to face the motor generator MG and the clutch K0 on the engine <NUM> side, and the rotor support member <NUM> includes the plate member (annular member) <NUM> that faces the cover <NUM>. The cover <NUM> includes the first tubular portion <NUM> that protrudes in the axial direction from the inner periphery toward the speed change mechanism <NUM>, and the second tubular portion <NUM> that protrudes in the axial direction toward the speed change mechanism <NUM> so as to surround the first tubular portion <NUM>, and the plate member <NUM> of the rotor support member <NUM> includes the tubular portion <NUM> that protrudes in the axial direction from the inner periphery toward the engine <NUM>. Further, the radial bearing (inner side radial bearing) Br1 for supporting the first transmitting shaft <NUM> in the radial direction is disposed between the first transmitting shaft <NUM> (expanded radius portion 141e) coupled to the crankshaft <NUM> of the engine <NUM> and the inner peripheral surface of the first tubular portion <NUM> of the cover <NUM>, and the clearance a is formed between the outer peripheral surface of the first tubular portion <NUM> and the inner peripheral surface of the tubular portion <NUM> of the plate member <NUM>. Moreover, the radial bearing (outer side radial bearing) Brf for supporting the rotor support member <NUM> in the radial direction is disposed between the outer peripheral surface of the tubular portion <NUM> of the plate member <NUM> and the inner peripheral surface of the second tubular portion <NUM> of the cover <NUM>.

As a result, even if the cup of the radial bearing Br1 is press-fitted into the first tubular portion <NUM> of the cover <NUM> of the motor case <NUM> and the first tubular portion <NUM> is deformed, since the clearance a is formed between the outer peripheral surface of the first tubular portion <NUM> and the inner peripheral surface of the plate member <NUM> of the tubular portion <NUM>, the deformation of the first tubular portion <NUM> does not affect the tubular portion <NUM> of the plate member <NUM>. Even if deflection of the first transmitting shaft <NUM> with respect to the shaft center occurs in accordance with the rotation of the engine <NUM>, since the clearance a is formed between the outer peripheral surface of the first tubular portion <NUM> and the inner peripheral surface of the tubular portion <NUM> of the plate member <NUM>, the deflection of the first transmitting shaft <NUM> does not affect the tubular portion <NUM> of the plate member <NUM>. Thus, in the hybrid drive device <NUM>, the rotor support member <NUM> can be appropriately supported by the cover <NUM>, that is, the case <NUM> via the radial bearing Brf, and the fluctuation of the clearance between the stator <NUM> and the rotor <NUM> can be satisfactorily suppressed.

Further, since the expanded radius portion 141e of the first transmitting shaft <NUM> is supported in the radial direction by the cover <NUM> of the motor case <NUM> via the radial bearing Br1, a torque fluctuation vibration (vibration) of the engine <NUM> transmitted to the first transmitting shaft <NUM> is no longer directly transmitted to the outer side radial bearing Brf. As a result, in the hybrid drive device <NUM>, the load acting on the radial bearing Brf for supporting the rotor support member <NUM>, that is, the rotor <NUM> of the motor generator MG so as to be rotatable and for also supporting the rotor support member <NUM> in the radial direction can be decreased, the durability thereof can be further improved, and the radial bearing Brf can be decreased in size (the cost can be decreased).

Further, the thrust bearing (inner side thrust bearing) Bt1 is disposed between the end surface on the speed change mechanism <NUM> side of the expanded radius portion 141e of the first transmitting shaft <NUM> and the end surface on the engine <NUM> side of the second transmitting shaft <NUM>. Moreover, the flange portion 141f extended from the expanded radius portion 141e of the first transmitting shaft <NUM> faces the end surface of the first tubular portion <NUM> of the cover <NUM> and the plate member <NUM> on the speed change mechanism <NUM> side, and the thrust bearing (outer side thrust bearing) Btm is disposed between the flange portion 141f and the inner peripheral portion (a back surface of the tubular portion <NUM>) of the plate member <NUM>. Further, the first transmitting shaft <NUM> includes the plurality of inner side oil holes (first oil holes) hi each opened on the outer peripheral surface of the second end portion 141b between the radial bearing Br2 and the thrust bearing Bt1 in the axial direction and on the inner peripheral surface of the second end portion 141b.

Further, the first transmitting shaft <NUM> includes the plurality of outer side oil holes ho that at least partially overlaps with the radial bearing Br1 and the thrust bearing Bt1 in the axial direction when viewed in the radial direction. The cover <NUM> includes the plurality of oil holes h1 each opened on the outer peripheral surface of the first tubular portion <NUM> and opened on the inner peripheral surface of the first tubular portion <NUM> between the radial bearing Br1 and the seal member <NUM> in the axial direction. Further, the annular clearance b communicating with the clearance a is formed between the end surface of the first tubular portion <NUM> and the flange portion 141f, and the annular clearance c is formed between the end surface of the second tubular portion <NUM> and the plate member <NUM>. In addition, the second tubular portion <NUM> includes the plurality of oil grooves g and the plurality of oil holes (second oil holes) h2 as described above.

As a result, the working oil serving as a lubricating cooling medium supplied from the axial oil passage L2 of the second transmitting shaft <NUM> into the second end portion 141b of the first transmitting shaft <NUM> can be supplied from the plurality of inner side oil holes hi to the radial bearing (intermediate radial bearing) Br2 and the thrust bearing Bt1, and can be supplied to the clutch K0 (the friction plate <NUM>, the separator plate <NUM>, etc.) on the outer radial side via the thrust bearing Bt1. Further, the working oil serving as the lubricating cooling medium supplied to the clutch K0 side can be supplied to the rotor core <NUM> and the coil ends 22a, 22b of the stator <NUM> via a plurality of oil holes 42o formed in the outer tubular portion <NUM> of the rotor support member <NUM>, a plurality of oil grooves <NUM> formed in the rotor core <NUM>, and the like.

Further, a part of the oil scattered from the inner side oil hole hi toward the rotor <NUM> side of the motor generator MG, that is, the coil end 22a side of the stator <NUM>, travels along the inner side surface of the cover <NUM> and flows into the clearance c and the oil holes h2 of the second tubular portion <NUM>. Thus, in the hybrid drive device <NUM>, a part of the working oil that has flowed out from the inner side oil holes hi to the rotor <NUM> side can be supplied to the radial bearing Brf. As a result, the radial bearing Br2, the thrust bearing Bt1, and the radial bearing Brf can be sufficiently lubricated and cooled, and the durability of each bearing can be satisfactorily ensured. In addition, on the inner side surface of the cover <NUM>, the pair of oil collecting guides <NUM> is formed so as to collect the oil scattered from above and guide the oil to the clearance c between the end surface of the second tubular portion <NUM> and the plate member <NUM> and to the oil holes h2 of the second tubular portion <NUM>. Thus, the amount of oil that is scattered from the inner side oil holes hi of the first transmitting shaft <NUM> to the rotor <NUM> side and that flows into the clearance c between the end surface of the second tubular portion <NUM> and the plate member <NUM> can be increased, and a sufficient amount of oil can be supplied to the radial bearing Brf. However, the oil holes h2 may be omitted from the second tubular portion <NUM>.

Moreover, in the hybrid drive device <NUM>, the working oil that has passed through the thrust bearing Bt1 can supplied from the plurality of outer side oil holes ho of the first transmitting shaft <NUM> to the radial bearing Br1, and a part of the oil that has flowed into the outer side oil holes ho can be supplied to the thrust bearing Btm via the clearance b between the end surface of the first tubular portion <NUM> and the flange portion 141f of the first transmitting shaft <NUM>. A part of the oil that has flowed into the outer oil holes ho is also supplied to the radial bearing Brf via the clearance a between the outer peripheral surface of the first tubular portion <NUM> and the inner peripheral surface of the tubular portion <NUM> of the plate member <NUM>. Further, the working oil moves from the upper side to the lower side via the oil holes h1 of the first tubular portion <NUM> (cover <NUM>). As a result, the radial bearings Br1, Brf and the thrust bearing Btm can be sufficiently lubricated and cooled, and the durability of each bearing can be satisfactorily ensured.

Further, in the hybrid drive device <NUM>, the plurality of inner side oil holes hi of the first transmitting shaft <NUM> is formed obliquely so as to approach the engine <NUM> from the outer peripheral surface toward the inner peripheral surface of the second end portion 141b. As a result, the flange portion 141f of the first transmitting shaft <NUM> can be formed so as to surround a part of the second end portion 141b in order to shorten the axial length of the hybrid drive device <NUM>, the first transmitting shaft <NUM> and the clutch hub <NUM> of the clutch K0 can be connected, and the inner side and the outer side of the second end portion 141b can be communicated via the plurality of inner side oil holes hi.

Further, in the hybrid drive device <NUM>, the rotor support member <NUM> incudes the annular wall portion <NUM> that is supported in the radial direction by the motor case <NUM> (housing <NUM>) via the radial bearing Brr, and the plate member <NUM> that is supported in the radial direction by the motor case <NUM> (cover <NUM>) via the radial bearing Brr. Further, the plate member <NUM> is coupled to the annular flange portion <NUM> extended radially outward from one end of the outer tubular portion <NUM> of the rotor support member <NUM> in the axial direction so that the plate member <NUM> rotates integrally with the rotor <NUM>, and the plate member <NUM> faces the annular wall portion <NUM> at a distance in the axial direction. Further, the plate member <NUM> is coupled to the flange portion <NUM> in a state of being in contact with the end surface on the opposite side of the flange portion <NUM> from the rotor core <NUM> side, and the flange portion <NUM> includes the axial protruding portion 43p that protrudes in the axial direction from the outer peripheral portion of the end surface in which the plate member <NUM> is in contact with to the opposite side of the rotor core <NUM> side and that supports the outer peripheral surface of the plate member <NUM> in the radial direction.

As a result, the plate member <NUM> is accurately aligned with the shaft center of the engine <NUM> and the speed change mechanism <NUM> by the axial protruding portion 43p of the flange portion <NUM> and thus, the rotor <NUM> of the motor generator MG can be accurately aligned with the axial center of the engine <NUM>, and the like. Further, by bringing the plate member <NUM> into contact with the end surface on the opposite side of the flange portion <NUM> from the rotor side, the distance in the axial direction between the plate member <NUM> and the annular wall portion <NUM>, that is, a disposition space of the clutch K0 can be sufficiently ensured, and the friction plates <NUM> and the separator plates <NUM> of the number in accordance with a torque capacity required for the clutch K0 can be disposed. As a result, in the hybrid drive device <NUM>, it is possible to sufficiently ensure the torque capacity of the clutch K0 while accurately aligning the rotor <NUM> of the motor generator MG with respect to the shaft centers of the engine <NUM> and the speed change mechanism <NUM>.

Further, the clutch K0 includes the piston <NUM> that is disposed between the annular wall portion <NUM> (and the radial protruding portion <NUM>) and the plate member <NUM> in the axial direction, and the engagement oil chamber 69a of the clutch K0 is defined by the piston <NUM> and the annular wall portion <NUM> of the rotor support member <NUM>. As a result, since a torque transmitting function and a pressure receiving function when engaging the clutch K0 are gathered on the outer tubular portion <NUM> and the annular wall portion <NUM> sides, the rigidity required for the plate member <NUM> can be reduced so as to reduce the cost. Further, the plate member <NUM> of the rotor support member <NUM> does not transmit torque when the clutch K0 is engaged. Thus, the plate member <NUM> does not need to be coupled to the flange portion <NUM> via splines, etc., and may be coupled to the flange portion <NUM> by a relatively small number of bolts 43b so that the plate member <NUM> rotates integrally with the rotor <NUM>.

As described above, a hybrid drive device of the present disclosure includes a rotary electric machine (MG) having a stator (<NUM>) and a rotor (<NUM>), a transmission (<NUM>) coupled to the rotary electric machine (MG), a clutch (K0) that couples an engine (<NUM>) and the rotary electric machine (MG) and that releases a connection of the two, and a case (<NUM>) for housing the rotary electric machine (MG) and the clutch (K0), the hybrid drive device (<NUM>) including: a first transmitting shaft (<NUM>) coupled to an output shaft (<NUM>) of the engine (<NUM>); a second transmitting shaft (<NUM>) that transmits power from the rotor (<NUM>) of the rotary electric machine (MG) to the transmission (<NUM>); and rotor support member (<NUM>) that supports the rotor (<NUM>) of the rotary electric machine (MG) and that is fixed to the second transmitting shaft (<NUM>), in which the clutch (K0) includes a clutch hub (<NUM>) fixed to the first transmitting shaft (<NUM>) and uses the rotor support member (<NUM>) as a clutch drum, and the case (<NUM>) includes an end wall portion (<NUM>) that is extended so as to face the rotary electric machine (MG) and the clutch (K0) on the engine (<NUM>) side, the rotor support member (<NUM>) includes an annular member (<NUM>) that is disposed so as to face the end wall portion (<NUM>) of the case (<NUM>), the end wall portion (<NUM>) includes a first tubular portion (<NUM>) that protrudes in the axial direction from an inner periphery toward the transmission (<NUM>), and a second tubular portion (<NUM>) that protrudes in the axial direction toward the transmission (<NUM>) so as to surround the first tubular portion (<NUM>), the annular member (<NUM>) includes a tubular portion (<NUM>) that protrudes in the axial direction from an inner periphery toward the engine (<NUM>), an inner side radial bearing (Br1) is disposed between the first transmitting shaft (<NUM>) and an inner peripheral surface of the first tubular portion (<NUM>) of the end wall portion (<NUM>), a clearance (a) is formed between an outer peripheral surface of the first tubular portion (<NUM>) of the end wall portion (<NUM>) and an inner peripheral surface of the tubular portion (<NUM>) of the annular member (<NUM>), and an outer side radial bearing (Brf) is disposed between an outer peripheral surface of the tubular portion (<NUM>) of the annular member (<NUM>) and an inner peripheral surface of the second tubular portion (<NUM>) of the end wall portion (<NUM>).

Further, the first transmitting shaft (<NUM>) may be supported by the output shaft (<NUM>) via a bearing (Br0) on the engine (<NUM>) side.

Further, the inner side radial bearing (Br1) may be a roller bearing, the outer side radial bearing (Brf) may be a ball bearing, the rotor support member (<NUM>) may be supported in a radial direction by the case (<NUM>, <NUM>) via another ball bearing (Brr) on the transmission (<NUM>) side, the movement of the rotor support member (<NUM>) to the engine (<NUM>) side may be restricted by the case (<NUM>, <NUM>) via the outer side radial bearing (Brf), and the movement of the rotor support member (<NUM>) to the transmission (<NUM>) side may be restricted by the case (<NUM>, <NUM>) via the other ball bearing (Brr).

Further, the rotor support member (<NUM>, <NUM>) may be always connected to the second transmitting shaft via a spline (f), the second transmitting shaft (<NUM>) may be supported in the radial direction by a shaft support portion (<NUM>) provided in the case (<NUM>, <NUM>) on the transmission (<NUM>) side via a radial bearing (Br3), one of the first transmitting shaft (<NUM>) and the second transmitting shaft (<NUM>) may be inserted inside the other one formed in a tubular shape, and an intermediate radial bearing (Br2) may be disposed between the first transmitting shaft (<NUM>) and the second transmitting shaft (<NUM>) in the radial direction.

Moreover, the clutch (K0) may include a clutch hub (<NUM>) fixed to the first transmitting shaft (<NUM>) and may use the rotor support member (<NUM>) as a clutch drum, and the clutch hub (<NUM>) may be disposed between an annular wall portion (<NUM>) of the rotor support member (<NUM>) facing the annular member (<NUM>) and the annular member (<NUM>) in the axial direction.

The first transmitting shaft (<NUM>) may include a first end portion (141a) on the engine side, a second end portion (141b) that is on the transmission (<NUM>) side and that is formed in a tubular shape, and an expanded radius portion (141e) that is adjacent to the second end portion (141b) on the engine (<NUM>) side and that has a larger radius than a radius of the second end portion (141b), a flange portion (141f) that has an annular shape may be extended radially outward from the expanded radius portion (141e) of the first transmitting shaft (<NUM>) so as to face an end surface of the first tubular portion (<NUM>) of the end wall portion (<NUM>) and the annular member (<NUM>) on the transmission (<NUM>) side, the clutch hub (<NUM>) may be fixed to an outer peripheral portion of the flange portion (141f), the second end portion (141b) of the first transmitting shaft (<NUM>) may be inserted into an end portion (142a) that is formed in a tubular shape and that is on the engine (<NUM>) side of the second transmitting shaft (<NUM>), the intermediate radial bearing (Br2) that supports the second transmitting shaft (<NUM>) in the radial direction may be disposed between an outer peripheral surface of the second end portion (141b) of the first transmitting shaft (<NUM>) and an inner peripheral surface of the end portion (142a) of the second transmitting shaft (<NUM>), and an inner side thrust bearing (Bt1) may be disposed between an end surface on the transmission (<NUM>) side of the expanded radius portion (141e) of the first transmitting shaft (<NUM>) and an end surface on the engine (<NUM>) side of the second transmitting shaft (<NUM>), and an outer side thrust bearing (Btm) may be disposed between the flange portion (141f) of the first transmitting shaft (<NUM>) and an inner peripheral portion of the annular member (<NUM>).

Further, the first transmitting shaft (<NUM>) may include an oil passage (hi) that opens on an end surface of the second end portion (141b) and that opens between the intermediate radial bearing (Br2) and the inner side thrust bearing (Bt1) in the axial direction. As a result, the oil serving as the lubricating cooling medium supplied in the second end portion of the first transmitting shaft can be supplied to the intermediate radial bearing and the inner side thrust bearing, and can be supplied to the clutch or the rotor and the stator of the rotary electric machine via the inner side thrust bearing. Further, the oil scattered on the rotor side of the rotary electric machine can be supplied to the outer side radial bearing. As a result, the intermediate radial bearing, the inner side thrust bearing, and the outer side radial bearing can be sufficiently lubricated and cooled, and the durability of each bearing can be satisfactorily ensured.

A seal member (<NUM>) may be disposed between an outer peripheral surface of the first transmitting shaft (<NUM>) and the inner peripheral surface of the first tubular portion (<NUM>) of the end wall portion (<NUM>) and also on the engine (<NUM>) side of the inner side radial bearing (Br1), the first transmitting shaft (<NUM>) may include a plurality of second oil holes (ho) that at least partially overlap with the inner side radial bearing (Br1) and the inner side thrust bearing (Bt1) in the axial direction when viewed in the radial direction, the end wall portion (<NUM>) may include a plurality of oil holes (h1) each opened on the outer peripheral surface of the first tubular portion (<NUM>) and opened on the inner peripheral surface of the first tubular portion (<NUM>) between the inner side radial bearing (Br1) and the seal member (<NUM>) in the axial direction, and clearance (b, c) may be formed between the end surface of the first tubular portion (<NUM>) of the end wall portion (<NUM>) and the flange portion (141f) of the first transmitting shaft (<NUM>), and between an end surface of the second tubular portion (<NUM>) of the end wall portion (<NUM>) and the annular member (<NUM>).

As a result, the oil that has passed through the inner side thrust bearing can be supplied to the inner side radial bearing from the second oil holes of the first transmitting shaft. Further, a part of the oil that has flowed into the second oil holes can be supplied to the outer side thrust bearing via the clearance between the end surface of the first tubular portion and the flange portion of the first transmitting shaft. Moreover, a part of the oil that has flowed into the second oil holes can be supplied to the outer side radial bearing via the clearance between the outer peripheral surface of the first tubular portion and the inner peripheral surface of the tubular portion of the annular member. Further, the oil can flow from the upper side to the lower side via the oil holes in the end wall portion. As a result, the inner side radial bearing, the outer side thrust bearing, and the outer side radial bearing can be sufficiently lubricated and cooled, and the durability of each bearing can be satisfactorily ensured.

Further, the end wall portion (<NUM>) of the case (<NUM>) may include a pair of oil collecting guides (<NUM>) that protrudes from a surface on the transmission (<NUM>) side so as to collect oil scattered from above and guide the oil to the clearance (c) between the end surface of the second tubular portion (<NUM>) and the annular member (<NUM>). Thus, the amount of oil that is scattered from first oil holes of the first transmitting shaft to the rotor side of the rotary electric machine and that flows into the clearance between the end surface of the second tubular portion and the annular member can be increased, and a sufficient amount of the oil can be supplied to the outer side radial bearing.

The flange portion (141f) of the first transmitting shaft (<NUM>) may be formed so as to surround at least a part of the second end portion (141b) on the transmission (<NUM>) side of the annular member (<NUM>), and the plurality of first oil holes (hi) may be formed obliquely so as to approach the engine (<NUM>) from the outer peripheral surface toward an inner peripheral surface of the second end portion (141b) of the first transmitting shaft (<NUM>). As a result, the first transmitting shaft and the clutch hub of the clutch can be connected, and the inner side and the outer side of the second end portion of the first transmitting shaft can be communicated via the plurality of first oil holes, while the axial length of the hybrid drive device is shortened.

The case (<NUM>) may include a housing (<NUM>) in which one end in the axial direction is open and the other end in the axial direction is closed, and a cover (<NUM>) that is fixed to the housing (<NUM>) so as to cover the one end and that forms the end wall portion.

Further, it is understood that the invention of the present disclosure is not limited to the embodiments described above, and various modifications can be made within the scope of the claims. Furthermore, the embodiment described above is merely one specific form of the invention described in the SUMMARY OF THE INVENTION, and does not limit the elements of the invention described in the SUMMARY OF THE INVENTION.

Claim 1:
A hybrid drive device including a rotary electric machine (MG) having a stator (<NUM>) and a rotor (<NUM>), a transmission (<NUM>) coupled to the rotary electric machine (MG), a clutch (K0) that couples an engine (<NUM>) and the rotary electric machine (MG) and that releases a connection of the two, and a case (<NUM>) for housing the rotary electric machine (MG) and the clutch (K0), the hybrid drive device (<NUM>) comprising:
a first transmitting shaft (<NUM>) coupled to an output shaft (<NUM>) of the engine (MG); and
a second transmitting shaft (<NUM>) that transmits power from the rotor (<NUM>) of the rotary electric machine (MG) to the transmission (<NUM>); and
a rotor support member (<NUM>) that supports the rotor (<NUM>) of the rotary electric machine +(MG), wherein
the case (<NUM>) includes an end wall portion (<NUM>) that is extended so as to face the rotary electric machine (MG) and the clutch (K0) on the engine (<NUM>) side,
the rotor support member (<NUM>) includes an annular member (<NUM>) that is disposed so as to face the end wall portion (<NUM>) of the case (<NUM>),
the end wall portion (<NUM>) includes a first tubular portion (<NUM>) that protrudes in an axial direction from an inner periphery toward the transmission (<NUM>), and a second tubular portion (<NUM>) that protrudes in the axial direction toward the transmission (<NUM>) so as to surround the first tubular portion (<NUM>),
the annular member (<NUM>) includes a tubular portion (<NUM>) that protrudes in the axial direction from an inner periphery toward the engine (<NUM>),
an inner side radial bearing (Br1) is disposed between the first transmitting shaft (<NUM>) and an inner peripheral surface of the first tubular portion (<NUM>) of the end wall portion (<NUM>),
a clearance (a) is formed between an outer peripheral surface of the first tubular portion (<NUM>) of the end wall portion (<NUM>) and an inner peripheral surface of the tubular portion (<NUM>) of the annular member (<NUM>), and
an outer side radial bearing (Brf) is disposed between an outer peripheral surface of the tubular portion (<NUM>) of the annular member (<NUM>) and an inner peripheral surface of the second tubular portion (<NUM>) of the end wall portion (<NUM>).