JP2001187535A - Driving device for hybrid vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve such problems caused by indirect support of an input shaft through a rotor shaft that support accuracy of a counter drive gear interfitted with the input shaft is poor, and that a gear noise is generated, and that assembleability and assembling accuracy are insufficient, and that an oil passage structure is complicated. SOLUTION: The drive gear 21 is directly supported by two angular contact bearings 53 mounted on a case support wall 40a. The rotor shaft 15 is supported through bearings 42, 43 respectively on a center support 48 and a rear cover 41 mounted integrally on the case support wall 40a. An oil pump and a valve body are mounted on the case support wall 40a, and the oil passage is formed on the support wall and the center support.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a parallel-type hybrid vehicle drive device using both an engine and an electric motor as drive sources, and more particularly to an input shaft and a generator (first electric motor) arranged coaxially. (A rotating means), a (shaft) drive gear, and a planetary gear.

[0002]

2. Description of the Related Art Hitherto, a hybrid vehicle drive device disclosed in Japanese Patent Application Laid-Open No. 8-317600 has been proposed. The hybrid vehicle drive device distributes and transmits the rotation of the engine output shaft to the generator and the drive axle via a planetary gear, and rotates and charges the generator by the rotation of the engine, while the engine rotation alone or electrically. The vehicle is driven and driven by the motor, or is driven by the electric motor alone.

As shown in FIG. 9, the hybrid vehicle drive device includes an input shaft 13 connected to an engine output shaft 2a via a damper, etc.
The rotation from the rotor shaft 15, the planetary gear 6, and the planetary gear of the generator 3 (which functions as a generator during normal running, but also functions as a starter and a drive motor during normal running) is transmitted to the counter shaft 11. A traveling rotary shaft 16 having a counter drive gear 21 is disposed, and these members are housed in an integrated case including a front housing 39, a transmission case 40, and a rear cover 41.

The support structure for the first shaft A is shown in FIGS.
The rotor shaft 15 has a front portion supported by a support shaft wall 40 a formed in the case 40 via a radial ball bearing 42, and a rear portion formed on the rear cover 41 by a radial ball bearing 43. Is supported through. The input shaft 13 has a front portion supported by a housing 39 via a radial ball bearing 45, and a rear portion formed by a needle bearing 46 at a hollow hub portion 15 a formed at the tip of the rotor shaft 15.
Is supported through. Further, the traveling rotary shaft 16 on which the counter drive gear 21 is formed is supported by the input shaft 13 via a needle bearing 47. In addition,
The planetary gear 6 has a sun gear S spline-connected to the rotor shaft 15, a carrier CR integrally connected to the input shaft 13, and a ring gear R integrally connected to the traveling rotary shaft 16.

[0005]

In the above-described support structure for the first shaft A, the front portion of the input shaft 13 is directly supported by the housing 39 via the bearing 45, but the rear portion of the input shaft 13 is supported by the housing 39. , Bearing 46, rotor shaft hub 15
a and is supported by the bearing 42 of the case support wall 40a via a. For this reason, even if the axial direction can be shortened, the support accuracy of the input shaft 13 is reduced, and the counter drive gear 21 of the traveling rotary shaft 16 that is indirectly supported on the input shaft has the support accuracy of the input shaft. As a result, the supporting accuracy is not sufficient in the thrust direction and the radial direction caused by the helical gear, and the meshing accuracy with the driven gear 22 is affected, thereby causing gear noise.

Further, since the front portion of the rotor shaft 15 is supported by the case supporting wall 40a, the brake 4 that operates when stopping the generator 3 needs to be disposed on the rear cover 41 together with the hydraulic actuator, and the resolver is required. Together with the rear end arrangement of 20, the assembling is troublesome and causes the assembling accuracy to decrease. In particular, the rear cover 4
The work of assembling the rotor shaft 1 with the rotor shaft 15 is troublesome, and the assemblability is reduced.

Further, the arrangement of the rear cover of the brake 4 and its hydraulic actuator lengthens the formation of the oil passage from the oil pump, and the tube passage routed to the outside of the integrated case and the oil passage formed on the mating surface of the rear cover 41 and the case 40. It is also a cause of losing reliability, such as oil leaks easily occurring.

Further, the rotor shaft 15 of the generator 3
Since the input shaft 13 is supported by the hub portion 15a, it is necessary to attach the rotor 17 to the rotor shaft by spline engagement. Therefore, the rotation change detected by the resolver 20 attached to the rotor shaft 15 is detected by the spline. As a result, it is difficult to perform the detection with high accuracy.

Accordingly, the present invention provides a drive device for a hybrid vehicle which solves the above-mentioned problem by directly supporting a drive gear on a case support wall and attaching a center support for supporting a rotor shaft to the case support wall. The purpose is to do so.

[0010]

The present invention according to claim 1 (for example, see FIGS. 3 to 5) includes an engine output shaft (2).
a) an input shaft (13), a rotor shaft (15) of the first electric rotating means (3), and a traveling drive shaft (331, 3).
3r), a drive gear (21), a first rotating element (CR) connected to the input shaft (13), a second rotating element (S) connected to the rotor shaft (15), and the drive. Third rotating element (R) connected to gear (21)
And a planetary gear (6) having

The input shaft (13) and the rotor shaft (1)
5) The drive gear (21) and the planetary gear (6) are coaxially arranged, and the transmission case (40), the housing (39) for closing one side of the case, and the other end of the case are connected. Closed cover (41)
A first and second support wall (40a) in a hybrid vehicle drive device housed in a case body made of
(48), and one of these support walls (40
a) is formed in the transmission case (40), and the other (48) is fixed to the transmission case, and at least two shafts such as angular contact bearings mounted on the first support wall (40a). The drive gear (21) is directly supported by bearings (53, 53) for regulating the movement in the direction and the radial direction, and the bearing (57) (45) is provided on the inner peripheral side of the drive gear and the housing (39), respectively. The input shaft (13) is supported by the second support wall (48) and the cover (4).
1) The hybrid vehicle drive device, wherein the rotor shaft (15) is supported by bearings (42) and (43), respectively.

The present invention according to claim 2 (see, for example, FIGS. 2 to 6) provides the other of the first and second support walls (4
8) is fixed to the one support wall (40a), and the oil pump (83) and the valve body (86) are mounted on the first support wall (40a) below (89) below the case body (39, 40). ), And the oil from the valve body is supplied to the first support wall (40a) and the second support wall (4).
8) or each oil passage (9) formed on the mating surface (m) thereof.
2. The hybrid vehicle drive device according to claim 1, wherein the first electric rotating means (3) and the bearings are supplied as lubrication / cooling oil to the respective portions requiring lubrication via the first and second electric rotating means (0 a, 90 c, 90 e). It is in.

According to a third aspect of the present invention (see, for example, FIGS. 2 to 6), the other of the first and second support walls (4
8) is fixed to the one support wall (40a), and the brake device for holding the rotor (17) of the first electric rotating means (3) in a stopped state on the second support wall (48). (4) is disposed, and a hydraulic actuator (69) of the brake device is provided with a cylinder (70) formed on the second support wall (48) and a piston (70) which is fitted to the cylinder in an oil-tight manner. 72), and the case body (39, 4).
0) below the first support wall (40).
a) Oil pump (83) and valve body (86)
And the oil from the valve body is supplied to the brake device via oil passages (90a, 90b) formed in the first support wall (40a) and the second support wall (48). The drive device for a hybrid vehicle according to claim 1 or 2, wherein the hydraulic actuator (69) is supplied as hydraulic oil to the hydraulic actuator (69).

According to a fourth aspect of the present invention (see FIGS. 5, 7, and 8), the rotor (17) of the first electric rotating means (3) is provided on the second support wall (48). Brake device (4) for stopping rotation of the rotor, detection means (100) for detecting a rotational displacement of the rotor, and a direction opposite to the engine rotation direction of a first rotary element (CR) connected to the input shaft (13). At least one one-way clutch (101) for preventing rotation of the first electric rotating means (3) is arranged so as to axially overlap with the stator (19) of the first electric rotating means (3). The hybrid vehicle drive device according to any one of the above.

According to a fifth aspect of the present invention (see FIG. 7, for example), a brake for stopping rotation of the rotor (17) of the first electric rotating means (3) is provided on the second support wall (48). A device (4), a detecting means (100) for detecting a rotational displacement of the rotor, and a one-way for preventing rotation of a first rotary element (CR) connected to the input shaft (13) in a direction opposite to an engine rotation direction. Any 2 of clutch (101)
4. The device according to claim 1, wherein a plurality of pieces [for example, the detecting means (100), the one-way clutch (101)] are arranged so as to overlap with the stator (19) of the first electric rotating means (3) in the axial direction. 3. The drive device for a hybrid vehicle according to any one of 3.

According to a sixth aspect of the present invention (see, for example, FIGS. 4 and 5), the stator (19) of the first electric rotating means (3) is fixed to the transmission case (40). And a rotor hub (61) having its rotor (17) integrally and inseparably fixed to the rotor shaft (15).
The hybrid vehicle drive device according to claim 4 or 5, wherein the rotational displacement of the rotor shaft (15) is detected by the detection means (20, 100).

The present invention according to claim 7 (for example, see FIG. 1) further comprises a second electric rotating means (5), and the output shaft (5a) of the second electric rotating means is connected to the drive gear (5). 21. The hybrid vehicle drive device according to claim 1, wherein the drive device is interlocked with the traveling drive shaft together with the traveling drive shaft.

According to the present invention, the first support wall is a case support wall (40a) formed in the transmission case (40), and the second support wall is the case support wall. 8. The drive for a hybrid vehicle according to claim 1, wherein the center support is fixed to a wall.

[Operation] Based on the above configuration, the rotation of the engine output shaft (2a) is transmitted to the first rotating element (for example, the carrier CR) of the planetary gear (6) via the input shaft (13). The planetary gears distribute the power to the second rotating element (for example, the sun gear S) and the third rotating element (for example, the ring gear R), and transmit the power to the rotor shaft (15) of the first electric rotating means (3) to generate power. Together with the (counter) drive gear (21), the traveling drive shaft (331,
33r).

At this time, for example, at least two drive gears (21) mounted on the first support wall (40a) are mounted on the first support wall (40a).
Angular Contact Bearings (53) (53)
Thereby, it is supported with high accuracy in the thrust direction and the radial direction. Further, the rotor shaft (15) of the first electric rotating means (3) has its both ends higher due to bearings (42) and (43) mounted on the second support wall (48) and the cover (41), respectively. Supported with precision.

When the first electric rotating means (3) is output as a driving motor, the rotation of the rotor shaft (15) is transmitted to the second rotating element (S) of the planetary gear (6), and Since the rotation of the first rotating element (CR) of the planetary gear in the direction opposite to the engine rotation direction is prevented by the one-way clutch (101), the third rotating element (CR) is set with the first rotating element as a reaction force element. R)
And transmitted to the traveling drive shafts (331, 33r) via the drive gear (21) and the like.

Note that the reference numerals in parentheses are for the purpose of comparison with the drawings, but are for the purpose of facilitating easy and easy understanding, and have no influence on the configuration of the present invention. It does not give.

[0023]

According to the first aspect of the present invention, since the drive gear is directly supported by at least two angular contact bearings mounted on the first support wall, the drive gear is provided in the radial direction and the thrust direction. On the other hand, it is supported with high accuracy, and the occurrence of gear noise can be reduced.

In the first electric rotating means, the rotor shaft is supported at both ends thereof with high precision by bearings mounted on the second support wall and the cover, respectively. The efficiency of the first electric rotating means can be improved by accurately holding the first electric rotating means in the minute gap.

Further, since the drive gear, the input shaft and the like are supported by the first support wall and the housing, and the rotor shaft is supported by the second support wall and the cover attached to the case support shaft, assembly is easy. And the assembling accuracy can be improved.

According to the second aspect of the present invention, the oil pump and the valve body are disposed on the first support wall so that the oil from the bubble body is directly transmitted to the first support wall and the second pump.
The lubricating oil is supplied to each required lubricating point via the oil passage formed on the supporting wall or the mating surface of the supporting wall, so that the oil passage structure is simplified and shortened, the cost is reduced, and the oil passage is formed exclusively in the case body. As a result, reliability against oil leakage and the like can be improved.

According to the third aspect of the present invention, the brake device is disposed on the second support wall, and the oil is supplied from the oil pump and the valve body disposed on the first support wall to the first support wall. It can be supplied directly to the hydraulic actuator of the brake device via the oil passage formed in the wall and the second support wall, and the hydraulic piping is routed outside the case body or formed on the mating surface of the transmission case and the cover. No need,
The hydraulic circuit is completed in the case, improving reliability against oil leaks and the like. Further, there is no need to form a hydraulic actuator and an oil path on the (rear) cover, simplifying the structure of the cover and reducing costs It is possible to reduce the size of the cover and improve the assemblability of the cover.

According to the fourth aspect of the present invention, the brake device utilizes the second support wall in the dead space on the first shaft which overlaps the stator of the first electric rotating means in the axial direction. Since at least one of the one-way clutch and the rotor rotational displacement detecting means is provided, the axial size of the hybrid vehicle drive device can be reduced.

According to the fifth aspect of the present invention, any one of the brake device, the one-way clutch and the detecting means is provided in the dead space by using both surfaces of the second support wall.
Since the individual components are arranged, it is possible to further shorten the axial direction of the drive device for a hybrid vehicle.

In particular, if the rotor rotational displacement detecting means is arranged on the center support, it is sufficient to reduce the wiring to the electronic control unit and to wire the inside of the case body, and the reliability of control of the first electric rotating means is improved. Can be improved.

According to the present invention, the rotor hub is integrally fixed to the rotor shaft by welding or the like, so that the conventional spline play between the rotor hub and the rotor shaft is eliminated, and the rotational displacement of the rotor shaft is reduced. , The rotational displacement of the rotor can be detected with high accuracy, and the control accuracy of the first electric rotating means can be improved.

According to the seventh aspect of the present invention, the torque of the engine and / or the first electric rotating means is assisted by the second electric rotating means, or the vehicle is controlled by the second electric rotating means alone. Can be driven.

According to the eighth aspect of the present invention, the drive gear and the input shaft are supported on the case supporting wall to improve the support accuracy, and the rotor shaft is supported on the center support to improve the assembling property. be able to.

[0034]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a hybrid vehicle driving apparatus to which the present invention is applied.
FIG. 1 is a schematic view of a drive device for a hybrid vehicle, and FIG.
Is a side sectional view thereof, and FIG. 3 is a front sectional view thereof.

The hybrid vehicle drive device 1 includes an internal combustion engine 2, a generator 3 constituting a first electric rotating means, a brake device 4, an electric motor 5 constituting a second electric rotating means, a planetary gear 6, a hydraulic pressure generating device. And an internal combustion engine 2
The generator 3, the brake device 4, the motor 5,
A planetary gear 6, a hydraulic pressure generator 7, and a differential device 9 are housed therein. Then, the second shaft composed of the first shaft A and the counter shaft 11 aligned with the engine output shaft 2a.
A shaft B, a third shaft C composed of a motor output shaft 5a, a fourth shaft D composed of a driving axle extending to the left and right of the differential device 9, and a fifth shaft E composed of a driving shaft 85 which is a driving member of the oil pump are shown in FIG. Are arranged as shown in FIG. That is, the first axis A, the third axis C, and the fourth axis D are arranged so as to surround the second axis B composed of the counter axis, and the first axis A, the third axis C, and the fourth axis D are located below the first axis A and beside the fourth axis D. The fifth axis E is disposed at the center.

As shown in FIG. 3, on the first shaft A, an input shaft 13, a generator 3, a brake device 4, and a planetary gear 6, which are connected to an engine output shaft 2a via a flywheel 14 and a damper 12, are provided. The planetary gear 6 is provided with a sun gear (second rotating element).
S is connected to a transmission shaft (rotor shaft) 15 to the generator 3, and a carrier (first rotating element) CR supporting the pinion P is connected to the input shaft 13 and its ring gear (third rotating element). R connects the input shaft 13 to a traveling rotary shaft 16 formed of a sleeve to be fitted. The generator 3 has a rotor 17 fixed to the transmission shaft 15 and a stator 19 fixed to the case 40. Any type of generator such as an excitation type generator can be applied. A magnet generator using a permanent magnet (eg, a brushless DC motor / generator) is desirable. A trans-type resolver (rotational displacement sensor) is provided on a portion of the transmission shaft 15 protruding from the rear case 41.
20 is provided, which can accurately detect the rotational displacement of the rotor and perform fine control of the rotational speed.

A counter drive gear (for engine output) 21 is connected to the traveling rotary shaft 16 by spline engagement, and a large gear 2 is mounted on the counter shaft 11.
2 and a small gear 23 are integrally fixed, and the counter drive gear 21 is a large (counter driven) gear 22.
Is engaged. On the other hand, the electric motor 5 is connected to the output shaft 5.
a and a stator 26 fixed to the case 40, and any type of DC motor, induction AC motor, etc. can be applied. Are preferred. A transformer-type resolver (rotational displacement sensor) 27 is disposed on a portion of the output shaft 5a protruding from the case 40 on the side opposite to the motor 5, and accurately detects the position of the rotor 25 to output the motor output. Can be controlled. A counter drive gear (for motor output) 29 is integrally fixed to the output shaft 5a of the motor, and the gear 29 also meshes with the large (counter driven) gear 22 of the counter shaft.

The differential device 9 has an input gear 31 fixed to a differential case 30, and the gear 31 meshes with the small gear 23 of the counter shaft.
Further, a center gear 32 supported by the differential case meshes with left and right side gears (travel driving shafts) 331 and 33r, and distributes and transmits the input torque from the input gear 31 to the left and right side gears and interlocks with the left and right front wheels. Drive the left-right drive axle.

The support structure for the first shaft A will be described with reference to FIGS. The transmission case 40 has a case support wall 40a constituting a first support wall at an intermediate portion thereof, and a housing 39 is integrally fixed to a front (engine) side thereof, and a rear (rear) side thereof. , A rear cover 41 is integrally fixed thereto to form an integral case. A center support 48 constituting a second support wall is integrally fixed to the support wall 40a of the case 40 by a bolt so as to surround the first shaft A, specifically, to surround the planetary gear 6. Have been.

As shown in detail in FIG. 4, a narrow gear 50 is coupled to the input shaft 13 so as to rotate integrally therewith, and a boss portion thereof is supported by a housing 39 via a radial ball bearing 45. The front end of the input shaft 13 is directly supported by the housing 39 by the integral gear boss. One end of the traveling rotary shaft 16 is connected to the ring gear R, and a similar narrow gear 52 is coupled to the other end of the traveling rotary shaft 16 so as to rotate integrally therewith. The boss portion 21a of the counter drive gear 21 is fitted integrally with the counter drive gear 21 by spline engagement.

The outer peripheral surface of the gear boss portion 21 is supported by the support wall 40a of the case via two angular contact ball bearings 53, 53 joined to each other at the back surface. The ball bearings 53,5
The gear 3 is pinched by a nut 55 between the gear 21 and the tooth side surface, and the gear 52 is locked at the tip of the running rotary shaft 16 by a snap ring 56 so that the running rotary shaft 16
The case 1 and the case 52 are rotatably supported by the case 40. The outer races of the two ball bearings 53, 53 are formed in the case supporting wall 40a at an intermediate portion.
The axial movement is prevented by fitting the snap ring 54 into the. Therefore, the gear 21 has two angular contact ball bearings 53,
53 directly supports the case supporting wall 40a.

The input shaft 13 has one end integrally formed with the carrier CR of the planetary gear 6.
The housing 39 is supported at one end via a needle bearing 57 or a bush and at the other end via the bearing 45.

The input shaft 13 is connected to the torsion damper 12
, The damper is supported by the housing 39 in a misaligned state in which the radial biasing force of the damper does not act evenly. Therefore, input shaft 1
3, the eccentric load is constantly applied from the damper 12, and for example, if the housing 3 is supported via a bush or the like, a problem such as an oil film shortage occurs.
Since the input shaft 13 is supported by the radial ball bearing 45, the trouble caused by the oil film shortage or the like does not occur, and the input shaft 13 is supported with high reliability.

On the other hand, as shown in detail in FIG. 5, the rotor 17 of the generator 3 is supported by a hub 61 having a flange 61a substantially at the center, and the hub flange 61a is attached to a rotor shaft (transmission shaft) 15. It is inseparably fixed by welding. The rotor shaft 15 has a front portion supported by the center support 48 via a radial ball bearing 42 and a rear portion supported by the rear cover 41 via a radial ball bearing 42. Furthermore,
An oil seal 66 is interposed between the rear cover 41 and the rotor shaft 15, and the resolver 20 is disposed. Further, a cover plate 67 is fixed to the rear cover 41 so as to cover the resolver 20. . Therefore, both ends of the rotor shaft 15 are directly supported by the support 48 and the rear cover 41 integrated with the case 40 via the bearings 42 and 43, respectively.

The brake device 4 is disposed between the rotor hub 61 and the center support 48. The brake device 4 has a hydraulic actuator 69 provided on the center support 48. The actuator is provided with a cylinder 70 having an annular groove formed on the side surface of the center support and an oil-tight cylinder by an O-ring. It has a piston 72 fitted in a shape. The center support 48 has an annular protrusion (support member) 48a that protrudes rearward in the axial direction, and has a groove extending in the axial direction at a predetermined interval, for example, 120 degrees. Is formed.

A flange 73 having a predetermined thickness and serving as a reaction force receiving member (backup plate) is fitted on the outer peripheral surface of the annular projecting portion 48a, and the inner peripheral surface of the flange is provided at predetermined intervals. A protruding portion that protrudes in the inner diameter direction is formed, and the protruding portion engages with the incision to stop rotation. A snap ring 74 is fitted and mounted on the center support projection 48a behind the flange 73, and the flange is prevented from being removed from the rear. The surface portion (rear inner diameter corner portion) of the flange where the snap ring abuts is shaved and slightly thinned, and the snap ring 74 is arranged in the shaved recessed portion to increase the axial dimension. Is preventing that.

The inner peripheral surface of the flange 73 is joined to the outer peripheral surface of the annular protruding portion 48a almost in its entirety in a state of being in close contact with the outer peripheral surface thereof. As a whole, the flange 73 is prevented from tilting around the joint surface with the snap ring 74 as a fulcrum.

On the other hand, a corner portion on the outer diameter side of the front surface of the flange 73 is also shaved to form a stepped structure, and a groove (spline) e is formed at a predetermined interval on the inner diameter surface of the concave portion d due to the step. Are formed. A spline is also formed on the inner peripheral surface in front of the rotor hub 61 (on the side facing the flange 73). A brake disk (outer friction plate) 75 is accommodated in the concave portion d on the outer periphery of the flange so as to be rotatably supported with a small gap.
The brake disc is formed of an annular member having a short radial length, frictional material such as paper is stuck on both surfaces thereof, and projections are formed on the outer peripheral surface at predetermined intervals. These projections engage with the splines of the rotor hub 61 to rotate integrally. Further, a brake plate (inner friction plate) 76 is housed and arranged in the concave portion d adjacent to the front side in the axial direction of the brake disk 75 (the hydraulic actuator 69 side). Are formed at predetermined intervals on an inner peripheral surface thereof, and these projections engage with the concave grooves (splines) of the flange 73 to rotate integrally. It is supported to be.

An annular pressing portion 72a projecting rearward (toward the brake plate 76) slightly outside the radial center of the piston 72 is formed.
The tip of the pressing portion faces the annular brake plate 76. On the other hand, a retainer 77 is supported on the outer peripheral surface slightly in front of the cut groove end of the center support projecting portion 48a, and a return spring 79 composed of a large number of coil springs is annularly held by the retainer. Further, the retainer 77 has an inner peripheral portion supported by the outer peripheral surface of the protruding portion 48a, and a spring holding portion directly abutting against the front surface of the flange 73 to prevent the retainer 77 from coming off. A return spring 79 composed of a predetermined number of coil springs is contracted between a predetermined number of concave portions formed on the inner diameter side of the pressing portion 72a of the piston and the retainer 77.

In the brake device 4 described above, the retainer 77 for the return spring 79 is supported by a flange 73 serving as a reaction force receiving member (backup plate) and supported by a dedicated retaining member such as a snap ring. Since it becomes unnecessary and is supported by the flange 73 at the load acting portion of the spring 79, a simple and thin structure is sufficient. Further, since the brake disk 75 and the brake plate 76 are arranged and supported in the concave portion d which is a stepped portion of the outer periphery of the flange 73, no special space is required in the axial direction, and the brake 73 is prevented from coming off. The snap ring 74 is also disposed in the concave portion on the inner diameter side of the rear surface of the flange 73, so that no special space is required in the axial direction, and together, the flange 73 secures a sufficient braking capacity. Along with a sufficient thickness as a reaction force receiving member (backup plate), the axial dimension is reduced. Further, the brake disk 75 and the brake plate 76 are formed of an annular member having a short length in the radial direction, are located opposite to the pressing portion 72a of the piston 72, and have a flange 73 serving as a reaction force receiving member. Almost the entire peripheral surface is in close contact with the projecting portion 48a.
The flange 73 is able to secure a sufficient thickness, so that the flange 73, the brake disc, the plate, etc. do not bend, and the one-side contact of the brake plate is prevented. Prevention can stabilize braking performance.

Next, the hydraulic pressure generator 7 will be described with reference to FIGS. The hydraulic pressure generating device 7 includes an oil pump 83 and a drive transmission system thereof, and the fifth shaft E
It has a drive shaft (including a hollow drive shaft) 85 disposed thereon. The drive shaft is arranged in parallel with a position adjacent to and below the first shaft A. The oil pump 83 is a crescent type gear pump (not limited to this type of pump, but may be another type of rotary pump). Transmission case 40 and housing 3
9 is provided in a valve body 86 housed and arranged below. The integral valve body 86 is directly attached to the center support 48 together with the pump 83 and a driving device thereof to be described later, and a suction pipe 87 is projected from the valve body 86 downward. The strainer portion 87a at the tip is an integral case 3
It is located in an oil sump 89 formed at the lower part of the 9, 40. A large number of heat dissipating fins 88 are formed at the lower portion of the case 40 to cool the oil in the oil sump 89.

The valve body 86 has a primary regulator valve, a secondary regulator valve, a switching valve, and the like in addition to the oil pump 83, and is fixed to the support wall 40a of the case 40. The oil pressure supplied from the valve body 86 is supplied to the cooling wall and the lubricating oil via the support wall 40a of the case, the center support 48, oil holes 90 formed in the mating surface thereof, and oil holes formed in each shaft. And sent to the brake device 4 as hydraulic oil. Specifically, as shown in FIG. 5, the oil is supplied to a hydraulic actuator 69 of the brake device 4 through an oil passage 90a formed in the support wall 40a and an oil passage 90b formed in the center support 48. As shown in FIG. 6, the oil is supplied to the drip oil passage 90d through an oil passage 90c formed on the mating surface m of the support wall 40a with the center support 48, and heat exchange is performed with the cooling water in the drip oil passage 90d. The cooled oil is dropped toward the generator 3, the driving electric motor 5, and the like. As shown in FIG. 3, the oil passage formed on the mating surface m is guided to an oil passage 90f formed on the rotor shaft 15 via an oil passage 90e formed on the center support 48, and the bearing 42 is provided. , 43 and the brake device 4 and the like, and are supplied to the oil passages 90f.
The oil is guided to an oil passage 90 g formed in the input shaft 13, and is supplied to each of the parts requiring lubrication such as the bearings 57, 53, 45, and the planetary gear 6.

The oil pump drive shaft 85 is
As shown in detail in FIG.
The inner end of the cylindrical portion 8 is integrally connected to the inner gear of the oil pump 83, and the distal end portion swells in the radial direction and
5a is formed in the shape of a cup. The cylindrical part 85
First and second one-way clutches 90 and 91 are mounted on both the inner peripheral surface a and the outer peripheral surface b of a, that is, on the peripheral surface a and the outer peripheral surface b of the concave portion in the cylindrical portion. On the inner peripheral surface of the inner peripheral side (first) one-way clutch 90, the first
A short shaft 92a provided at a central portion of one side of the gear 92 is fitted, and a cylindrical hub 93a of a second gear 93 is fitted on the outer peripheral surface of the outer peripheral (second) one-way clutch 91. Have been. The two one-way clutches 90,
91 transmits the faster rotation of the first or second gears 92, 93 to the drive shaft 85 in the predetermined one-way rotation, and makes the slower rotation (including stop and reverse rotation) free rotation. Is set to

The gear 50 of the input shaft 13 always meshes with the first gear 92, and
Gear 52 is always meshed with the second gear 93.
The first gear 92 has a thrust washer 95 provided on the support wall between the first gear 92 and the support wall of the case 40. The first gear 92 has a pump drive shaft 85 and a distal end of a cylindrical hub 93a of the second gear. And a thrust washer 96 provided on the first gear. Similarly, the second gear 93 has the thrust washer 96 interposed between the second gear 93 and the first gear 92, and has a valve body 86.
Thrust washer 9 provided on the body between
7 are supported.

As a result, the inner peripheral (first) one-way clutch 90 and the outer peripheral (second) one-way clutch 91 are of different diameters and are located at positions overlapping each other in the axial direction of the drive shaft 83. By being arranged, the first gear 92, the second gear 92,
The gear 93 is supported adjacently to the drive shaft 83 and is disposed adjacent thereto, and the drive shaft 83 is cantilevered supported by the valve body 86, so that the axial dimension of the hydraulic pressure generating device 7 can be reduced. As a result, the distance between the case 40 and the housing 39 in which the hydraulic pressure generating device is pinched can be shortened.

Therefore, the case supporting wall 40a to which the valve body 87 is fixed is prevented from interfering with the planetary gear 6, and the valve body 87, the oil pump 83 provided in the body, and the drive shaft 85 (the fifth The axis E) is changed to an input shaft 13 composed of a double shaft and a traveling rotary shaft 16.
(The first axis A). As a result, the diameters of the first and second gears 92 and 93 can be reduced, and these gears can store the oil even if a relatively large amount of oil is stored in the oil sump 89, that is, even if the oil level is increased. There is no agitation.

Next, the assembling of the above-described hybrid vehicle drive device 1, particularly, the first shaft A portion thereof will be described. First, the carrier supporting the pinion P is integrally attached to the input shaft 13, the ring gear R is attached to the traveling rotary shaft 16, and the bearing 57 is fitted to the input shaft 13. On the other hand, the outer race of the bearings 53, 53 is mounted on the support wall 40a of the transmission case, and the axial movement is prevented by the snap ring 58. In this state, the input shaft 13 supporting the traveling rotating shaft 16 is inserted into the outer race from the rear side, and the counter drive gear 21 is inserted from the front side while being spline-engaged with the traveling rotating shaft 16, Further, one angular contact ball bearing 5 is provided on the outer periphery of the gear boss portion 21a.
No. 3 ball and inner race, then the other ball and inner race are inserted.
Screw 21b.

Then, by tightening the nut 55, two underground contact bearings 53, 53 are formed.
Are positioned between the nut 55 and the side surface of the gear 21 to axially position and directly support the counter drive gear 21 in a rear assembly with a predetermined preload. Further, the narrow gear 52 is spline-engaged with the front end of the traveling rotary shaft 16 and is prevented from being removed by the snap ring 65,
The traveling rotary shaft 16 is also positioned and supported in the axial direction.

Further, a gear 50 is provided on the front side of the input shaft 13.
Are fitted and engaged, and the bearing 45 is mounted,
In this state, the housing 39 connects the two-way one-way clutches 90 and 91 to the thrust washers 95 and 9.
The bearing 45 is fitted into the support hole while holding the input shaft 13 through the holes 6 and 97 to rotatably support the input shaft 13. A thrust bearing 99 is provided at the rear end of the input shaft 13.
, A sun gear S is arranged.

On the other hand, with the center support 48 detached from the transmission case support wall 40a (or attached), the piston 70 and the return spring 79 are attached to the center support 48.
Is mounted, and in this state, the flange 73 on which the brake disc 75 and the plate 76 are assembled is mounted.
Is attached to the projecting portion 48a of the support and stopped by the snap ring 74, whereby the brake device 4 is assembled. Then, with the center support 48 attached to the case support wall 40a by bolts, the rotor shaft 15 having the rotor 17 is engaged with the brake disc 76 with the hub spline and the spline 15a at the tip thereof with the sun gear S. While assembling to the center support 48. Thereafter, the rear cover 41 is inserted into the rotor shaft 15 to attach the rear cover to the case 40, and the resolver 20 and the cover 67 are further attached to assemble.

Next, the operation of the above-described drive device 1 for a hybrid vehicle will be described. The rotation of the internal combustion engine 2 is transmitted to the carrier CR of the planetary gear 6 via the input shaft 13, the torque is distributed by the planetary gear 6, and transmitted to the generator 3 via the sun gear S and the transmission shaft 15, and the ring gear It is transmitted to the traveling rotary shaft 16 via R. Further, the rotation of the traveling rotation shaft 16 is
The rotation of the electric motor 5 is also transmitted to the counter shaft 11 via the gears 29 and 22, and the rotation of the counter shaft 11 is transmitted to the counter shaft 11 via the gears 21 and 22. It is transmitted to a left-right drive axle via a differential device 9. By appropriately controlling the engine 2, the generator 3, and the motor 5, the drive axle is driven by only the motor output, only the engine output, or the assist of the motor output to the engine output, and the remaining battery power is supplied. The generator 3 is driven by the output of the engine 2 to charge the battery according to the amount and the running load.

For example, in the case of normal running in which the vehicle is driven exclusively by the engine output, such as running at a constant speed, or by assisting the motor output to the engine output, the input shaft 13 and the traveling rotary shaft 16 integral with the engine output shaft 2a. Both rotate in a predetermined direction, but generally, the rotation speed of the traveling rotation shaft linked to the ring gear R is higher than the rotation speed of the input shaft 13 linked to the carrier CR (generally, the ring gear for the carrier CR). The rotation ratio of R is 2), and therefore the second rotation speed through the gear 52 is higher than the rotation speed of the first gear 92 through the gear 50.
Of the gear 93 is high. Thereby, the outer peripheral side (second
), The one-way clutch 91 is locked, and the inner peripheral side (first) one-way clutch 90 is in the free state, and the pump is driven via the second gear 93 and the one-way clutch 91 that are rotating on the high-speed side. The shaft 85 is rotated, and the oil pump 83 is driven at a high speed according to the traveling speed.

Also, the remaining battery charge (SOC) is sufficient,
When all of the engine output is exclusively used as the traveling energy, the switching valve in the valve body 86 is switched, and the line pressure (operating oil pressure) from the primary regulator valve based on the discharge pressure of the oil pump 83 is applied to the support wall 4.
Oil passage 90b formed in the center support 48 integrated with the case, which is directly communicated with the oil passage 90a formed in the case 0a.
, I.e., directly to the cylinder 70 of the hydraulic actuator 69 via a short oil passage formed in the case. Thereby, the piston 72 of the hydraulic actuator 69 extends against the return spring 79,
The pressing portion 72a presses the brake plate 76,
The brake disk 75 is pressed between the brake plate and the flange 73, and the frictional force therebetween increases the torque capacity, thereby reducing the inertia of the rotor 17 and the rotational force from the planetary gear 6 to the rotor shaft 15. On the other hand, a sufficient torque capacity is secured, that is, the brake device 4 is in the operating state in which the brake disk 75, the brake plate 76, and the flange 73 are integrally engaged.

In this state, the rotor hub 61 is integral with the brake disc 76 in the rotational direction, the brake plate 76 and the flange 73 are integral with the center support 48 in the rotational direction.
As a result, the rotor 17 is mechanically stopped.
As a result, the generator 3 is stopped without performing fine control of the generator, and the engine output is used exclusively for running the vehicle, and functions in the same manner as a normal vehicle driven by an internal combustion engine. In this case, as described above,
The oil pump 83 is driven based on the rotation of the traveling rotation drive shaft 16.

Except when the generator 3 is stopped mechanically, the switching valve of the valve body 86 is in the drain state of the line pressure (operating oil pressure), and the oil pressure of the hydraulic actuator 69 is drained, and the piston 72
Is at a position where it is retracted into the cylinder 70 by the return spring 79. In this state, the brake disc 7
5 has no torque capacity between the flange 73 and the brake plate 76, that is, the brake device 4 is released and the rotor 17 is freely rotatable.

Further, in a state where the engine 2 is idling or the generator 3 is exclusively rotated and charged by the engine 2 to stop the vehicle, the traveling rotary shaft 16 linked to the driving axle is stopped. However, the input shaft 13 connected to the engine output shaft 2a rotates at a predetermined rotation. Therefore, the rotation of the input shaft 13 is
The driving force is transmitted to the drive shaft 85 via the second and inner circumferential (first) one-way clutch 90 to drive the oil pump 83.

On the other hand, when the vehicle travels forward in the motor drive mode, the engine 2 is not driven. And the motor 5
The rotation of the output shaft 5a is controlled by the counter shaft 11 as described above.
And transmitted to the traveling rotary shaft 16 via the gears 22 and 21 as rotation in a predetermined direction. Accordingly, the rotation at the traveling speed 16 is transmitted to the pump drive shaft 85 via the gears 52 and 93 and the outer peripheral side (second) one-way clutch 91,
The oil pump 85 is driven by the rotation according to the traveling speed. At this time, the rotation of the traveling rotary shaft 16 also causes the rotor 17 of the generator 3 to rotate freely (the engine output shaft may also rotate freely), and the engine 2 and the generator 3 do not function at all and the hybrid The vehicle functions exclusively as an electric vehicle driven by the electric motor 25.

When the vehicle is stopped in the motor drive mode, the motor output shaft 5a and the drive axle are stopped, so that the gears 29, 22, 21 and 31, 23, 2
The traveling rotary shaft 16 is also stopped via the gears 2 and 21, and the second gear 93 is also stopped via the gear 52.
Also, during reverse running, by rotating the motor 5 in reverse,
The drive wheels travel backward through the gears 29, 21, 23, 31 and the differential device 9, and the reverse rotation is transmitted to the traveling rotary shaft 16 through the gears 22, 21 and further through the gear 52 to the first rotation. Gear 93 is rotated in the reverse direction. The reverse rotation of the gear 93 is not transmitted to the pump drive shaft 8 by free rotation of the outer peripheral side (second) one-way clutch 91.

When the vehicle is in a stopped state or a reverse state in the motor drive mode, the generator (first electric rotating means) 3 functions as an electric motor, and the generator 3
Thus, the transmission shaft 15 is rotated and driven in a predetermined direction. In this state, the engine 2 is in a non-drive state and is in free rotation, and the carrier CR and the input shaft 13 integrated therewith are decelerated and rotated in a predetermined direction based on the stop or reverse rotation of the ring gear R integrated with the traveling rotary shaft 16. I do. The rotation of the input shaft 13 is transmitted to the pump drive shaft 83 via the gears 50 and 92 and the inner peripheral side (first) one-way clutch 90 to drive the oil pump 83. The function of the generator 3 as an electric motor is used as a starter of the engine in addition to the drive of the oil pump.

Then, on the basis of the rotation of the engine output shaft 2a, the traveling rotary shaft 16
The rotation transmitted to the counter drive gear 21 depends on whether the counter drive gear 21 is in a predetermined preload state.
Since it is directly supported by the plurality of angular contact ball bearings 53 with high precision, it is transmitted to the counter driven gear 22 with high rotational precision, and gear noise is reduced.

In the generator 3, the rotor shaft 15 is supported with high accuracy on both ends by a center support 48 and a rear cover 41 via bearings 42 and 43, respectively, and an air gap between the rotor 17 and the stator 19 is provided. Can be held in the minute gap, and high efficiency can be maintained.

Further, the housing 39 may be assembled with the input shaft 13, the traveling rotary shaft 16, the planetary gear 6, and the counter drive gear 21 mounted and supported on the support wall 40a of the mission case 40. The rear cover 41 may be mounted in a state where the rotor shaft 15 is mounted and supported on the center support 48 mounted on the case support wall 40a, and the brake device 4 is easily mounted. The assembling performance of the device 1 is improved, and the assembling accuracy, particularly, the assembling accuracy of the portion 1A is improved.

Further, as described above, the case support wall 40
a, a pump 83 and a valve body 86 are formed directly, and oil from the valve body is supplied to an oil passage 90 formed in the case support wall 40a and the center support 48.
a, 90b are supplied directly to the hydraulic actuator 69 as hydraulic oil, and are formed in the oil passages 90c, 90d, 90e formed in the case support wall 40a, the center support 48 and their mating surface m, and the shaft. Oilway 90
f, 90 g are supplied directly to the required lubrication points as lubrication / cooling oil, shortening the oil path length, and providing an oil path such as a tube on the mating surface between the case and the housing and the rear cover or outside the integrated case. By doing so, it is possible to eliminate external leakage of oil, improve the reliability of the oil passage structure, and reduce costs.

Next, referring to FIG. 7, a partially modified second
An example will be described. In the present embodiment, a resolver which is a rotary displacement sensor of a rotary shaft is of a type different from the above-mentioned transformer type, the arrangement of the brake device is different, and the reaction force support when the generator 3 is newly used as a drive motor. This embodiment differs from the previous embodiment in that a one-way clutch serving as a part is provided.
Since the supporting portion of the traveling rotary shaft 16 and the counter drive gear 21 and the hydraulic pressure generating device 7 are the same as those in the previous embodiment, the same reference numerals are given and the description is omitted.

That is, in the second embodiment, the generator 3
A VR resolver 100 is disposed between the rotor shaft 15 and the rear side of the center support 48, and a one-way clutch 101 is disposed between the front side (inside) of the center support and the carrier CR of the planetary gear 6. Have been. In the above-mentioned VR resolver 100, the above-mentioned transformer type resolver has a coil wound on the rotor (rotor shaft) side, but has no coil wound on the rotor (rotor shaft 15) side. Is fixed integrally with the rotor shaft 15. The resolver 100
The stator 100b is fixed to a flange portion 48b protrudingly formed on the rear side surface of the center support 48 by a bolt 102, is formed in an annular shape, and is wound with a coil.

The VR resolver 100 detects the rotational displacement based on the angular displacement of the gap between the annular stator 100b and the elliptical rotor 100a. And can be integrated into the middle part of the shaft. Therefore, by using the VR resolver 100, the dimension in the axial direction can be reduced, and the assembling property can be improved. Further, the resolver 100 is disposed at an upper portion in a central portion in the integrated case, and
The wire 100c is connected to the inverter 104a of the electric control unit 104 disposed above the case 40 through a notch provided in the connector 8b. Therefore, wiring 1
00c can be arranged in an integrated case, and the wiring structure can be completed inside the case without routing around the case.

On the other hand, the one-way clutch 101 has an inner race 101a fixed by rivets or the like in the center support 48, and an outer race 101b engaged with a ring-shaped member 103 connected to the carrier CR. The carrier CR and thus the rotation of the input shaft 13 in the direction opposite to the engine rotation direction are prevented.

[0078] The brake device _{4 2,} the previous (first
Similarly to the embodiment, the rear cover 41 includes a flange 73, a brake disk 75, a brake plate 76, a piston 72, a return spring 79, and a retainer 77 which is in contact with the flange 73 to prevent the removal.
The pin ton 72 is fitted in an oil-tight manner into an annular cylinder 70 formed as described above to constitute a hydraulic actuator 69. Reference numeral 105 in FIG. 7 denotes a sensor that detects the rotation speed of the ring gear R of the planetary gear 6.

Since the present embodiment is constructed as described above, the generator 3 is used alone as the starter of the engine 2 and the drive motor of the oil pump 83, as well as for driving the vehicle, alone or with the electric motor 5 as described above. Can be used with assistance. That is, when the generator 3 is used as a vehicle drive motor, the engine 2 is stopped and is in a free rotation state, so that the reaction force of the planetary gear 6 is not supported. Therefore, a one-way clutch 101 is provided to support the reaction force, and the torque of the rotor shaft 15 of the generator is controlled by the one-way clutch 101 to prevent the carrier CR from rotating in a predetermined direction. And transmitted to the ring gear R via the pinion P at a reduced speed. Further, the traveling rotary shaft 16, the counter drive gear 21, the driven gear 22,
The power is transmitted to the differential device 9 via the gears 23 and 31.

In this embodiment, as in the previous embodiment,
The counter drive gear 21 is provided by an angular contact ball bearing 53 mounted on the case support wall 40a.
Are directly supported to prevent the generation of gear noise, and the rotor shaft 15 is supported at both ends by the bearing 42 mounted on the center support 48 and the bearing 43 mounted on the rear cover 41, so that the efficiency of the generator 3 can be improved. . Further, assembling of the present driving device becomes easy, and assembling accuracy, particularly, assembling accuracy of the first shaft A can be improved.

The resolver 10 is attached to the center support 48.
Since the zero and one-way clutch 101 is disposed and a thin VR resolver is used as the resolver, the resolver and the one-way clutch are disposed at positions overlapping the stator 19 of the generator 3 in the axial direction. By using the dead space, the axial direction can be shortened.

Next, along with FIG.
An example will be described. The same parts as those in the previous embodiment are denoted by the same reference numerals, and description thereof will be omitted.

[0083] This example to the center support 48 together with the one-way clutch 101 is disposed, the brake device 4 ₃ is disposed in the rear cover 41. The braking device 4 _3, together with the retainer 77 is fit retaining at the snap ring consists of a conventional type where the backup flange 73 'and the brake plate 76 is engaged with the rear cover 41 in parallel.

In this embodiment, the input shaft 13 and the traveling rotary shaft 16
The direction of assembling the counter drive gear 21 is opposite to that of the previous embodiment. That is, the input shaft 13 has a large diameter on the front side, the traveling rotary shaft 16 is fitted to the input shaft from the rear side, and the counter drive gear 21 is fitted to the traveling rotary shaft from the front side, The two angular contact ball bearings 53 are clamped by screwing and tightening a nut 55 to a ring gear connecting portion 16a of the traveling rotating shaft and a thread formed on the front side of the traveling rotating shaft 16. Thus, the counter drive gear 21, the traveling rotary shaft 16 and the input shaft 13 are assembled and supported by the case support wall 40a. Note that the carrier CR is spline-engaged with the input shaft 13 and is mounted between the sun gear S and the ring gear connecting portion 16a.

In this embodiment, as in the previous embodiment, the counter drive gear 21 is directly supported by the angular contact ball bearing 53 mounted on the case support wall 40a, thereby preventing the generation of gear noise. Also, the bearing 4 mounted on the center support 48
The rotor shaft 15 is supported at both ends by the bearing 2 and the bearing 43 attached to the rear cover 41, so that the efficiency of the generator 3 can be improved. Further, assembling of the present driving device becomes easy, and assembling accuracy, particularly, assembling accuracy of the first shaft A can be improved.

Further, a one-way clutch 101 is disposed on the center support 48, and the one-way clutch is located at a position overlapping the stator 19 of the generator 3 in the axial direction. The direction can be shortened.

Although the VR resolver 100 and the one-way clutch 101 are arranged on the center support 48 in the second embodiment (see FIG. 7), the first embodiment (see FIG. 5) is used instead of the VR resolver. The brake device 4 may be arranged as shown in FIG. In short, any two of the resolver, the one-way clutch, and the brake device can be distributed and arranged on both side surfaces of the center support 48. Further, the drive device for a hybrid vehicle is not limited to the type of the above-described embodiment, and can be similarly applied to other types. Further, the counter drive gear 21
Two angular contact bearings 53 for supporting
Is not limited to a ball bearing, but may be a roller bearing. In short, any bearing may be used as long as it can restrict movement in the axial and radial directions. Another radial bearing 42,
43 and 45 are not limited to ball bearings, but may be roller bearings. In the above-described embodiment, the first support wall for supporting the drive gear 21 is provided in the transmission case 4.
0 and the rotor shaft 16
The center support 48 is fixed to the case support wall, and the second support wall is fixed to the case support wall. However, the center support 48 is reversed. It may be.

[Brief description of the drawings]

FIG. 1 is an overall schematic diagram showing a drive device for a hybrid vehicle to which the present invention is applied.

FIG. 2 is a side sectional view thereof.

FIG. 3 is a front sectional view thereof.

FIG. 4 is an enlarged front sectional view showing a front side of a first shaft A;

FIG. 5 is a cross-sectional view showing a generator (first electric rotating means) on the rear side of the first shaft A;

FIG. 6 is a side sectional view showing an oil passage structure.

FIG. 7 is a front sectional view showing a first axis A portion according to a second embodiment.

FIG. 8 is a front sectional view showing a first shaft A portion according to a third embodiment.

FIG. 9 is a front sectional view showing a first shaft portion according to a conventional technique.

FIG. 10 is a view schematically showing a support structure of a first shaft portion according to a conventional technique.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Hybrid vehicle drive device 2 (Internal combustion) engine 2a Engine output shaft 3 First electric rotating means (generator) 4 Brake device 5 Second electric rotating means (electric motor) 6 Planetary gear 7 Hydraulic pressure generating device 9 Differential device 13 Input Shaft 15 Rotor shaft 16 Running rotating shaft 17 Rotor 19 Stator 20 Rotational displacement detection (resolver) 21 (Counter) drive gear 331, 33r Running drive shaft (side gear) 39 Housing 40 Case 40a First support wall (Case support wall) 41 (Rear) cover 42, 43, 45 (Radial ball) bearing 48 Second support wall (center support) 53 Angular contact (ball) bearing 57 (Needle) bearing 69 Hydraulic actuator 70 Cylinder 72 Piston 83 Il pump 86 Valve body 90 ... Oil passage 100 (VR) resolver 101 One-way clutch 104 Electric control unit A First shaft CR First rotating element (carrier) S Second rotating element (sun gear) R Third rotating element (ring gear) ) M mating surface

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Mika Kawaguchi 10th Takane, Fujii-machi, Anjo-shi, Aichi F-term in Aisin AW Co., Ltd. 3D039 AA00 AA11 AA25 AB26 AC06 AC21 AC26 AC65 AC68 AC86 AC87 AD43 3D042 AA00 AA01 AA05 AA06 AA08 AB01 BE01 BE02 EA05 EA09 5H115 PG04 PI22 PU10 PU11 PU24 PU25 PU29 QI07 RB08 TO30 UI32

Claims (8)

[Claims] 1. An input shaft interlocked with an engine output shaft, a rotor shaft of first electric rotating means, a drive gear interlocked with a traveling drive shaft, a first rotary element connected to the input shaft, and the rotor A planetary gear having a second rotating element connected to a shaft and a third rotating element connected to the drive gear, wherein the input shaft, the rotor shaft, the drive gear, and the planetary gear are coaxially arranged. And a hybrid vehicle drive device housed in a case body including a transmission case, a housing closing one side of the case, and a cover closing the other end of the case, wherein the first and second support walls are provided. One of these support walls is formed in the transmission case, and the other is fixed to the transmission case. The drive gear is directly supported by a mounted bearing that regulates axial and radial movement, and the input shaft is supported on an inner peripheral side of the drive gear and the housing via a bearing, respectively. The drive device for a hybrid vehicle, wherein the rotor shaft is supported on the support wall and the cover via respective bearings. 2. The other of the first and second support walls is fixed to the one support wall, and an oil pump and a valve body are arranged on the first support wall below the case body. The oil from the valve body is lubricated to each of the first electric rotating means, the bearings, and the like via the oil passages formed on the first support wall, the second support wall, or their mating surfaces. The drive device for a hybrid vehicle according to claim 1, wherein the drive device is supplied as lubrication / cooling oil to a necessary portion. 3. The other of the first and second support walls is fixed to the one support wall, and the second support wall holds the rotor of the first electric rotating means in a stopped state. A brake device is provided, and a hydraulic actuator of the brake device has a cylinder formed on the second support wall and a piston fitted in an oil-tight manner to the cylinder, and the piston below the case body. An oil pump and a valve body are provided on a first support wall, and the oil from the valve body is supplied to the brake device via respective oil passages formed in the first support wall and the second support wall. The hybrid vehicle drive device according to claim 1, wherein the drive device is supplied as hydraulic oil to the hydraulic actuator. 4. A brake device for stopping rotation of a rotor of the first electric rotating means, a detecting means for detecting a rotational displacement of the rotor, and a first means connected to the input shaft, the second supporting wall being provided on the second supporting wall. At least one one-way clutch that prevents rotation of the rotating element in a direction opposite to the engine rotation direction is arranged so as to axially overlap with a stator of the first electric rotating means. 4. The drive device for a hybrid vehicle according to any one of 3. 5. A brake device for stopping rotation of a rotor of the first electric rotating means, a detecting means for detecting a rotational displacement of the rotor, and a first means connected to the input shaft, the second supporting wall being provided on the second supporting wall. One of the two-way clutches to prevent the rotation of the rotating element in the direction opposite to the engine rotation direction,
The drive device for a hybrid vehicle according to any one of claims 1 to 3, wherein the drive device is arranged so as to overlap the stator of the first electric rotating means in the axial direction. 6. The first electric rotating means has a stator fixed to the transmission case and a rotor mounted on a rotor hub which is integrally fixed to the rotor shaft. The drive device for a hybrid vehicle according to claim 4, wherein the rotational displacement of the hybrid vehicle is detected by the detection unit. 7. The electric vehicle according to claim 7, further comprising a second electric rotating means,
The drive device for a hybrid vehicle according to claim 1, wherein an output shaft of said electric rotating means is interlocked with said traveling drive shaft together with said drive gear. 8. The case according to claim 1, wherein the first support wall is a case support wall formed on the transmission case, and the second support wall is a center support fixed to the case support wall. 8. The drive device for a hybrid vehicle according to any one of claims 7 to 7.