JP2000014081A - Hybrid driving device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the productivity of a hybrid driving device. SOLUTION: A hybrid driving device is provided with a multilayered motor 1 in which an inner rotor 10 and an outer rotor 30 are concentrically arranged and a planetary gear mechanism 3 which distributes the output of an engine to the inner rotor 10, outer rotor 30, and an output gear 35. The driving device is also provided with a thrust receiving section which receives the thrust load acting on the gear element of the planetary gear mechanism 3 and a spline which connects the multilayered motor 1 to the gear element of the mechanism 3 in such a way that no thrust load is inputted to the motor 1 in a gear housing housing the mechanism 3.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hybrid drive system in which outputs of an engine and a motor are transmitted to an output gear via a planetary gear mechanism.

[0002]

2. Description of the Related Art Conventionally, as a hybrid drive device of this type, one disclosed in Japanese Patent Application Laid-Open No. 8-317600 has an output shaft of an engine, an output gear and a planetary gear mechanism on one axis. One motor is arranged respectively, and the second motor is arranged on another axis parallel to this,
The output of the engine is distributed to two motors and an output gear by a planetary gear mechanism.

In this case, the motor, the planetary gear mechanism and the output gear are housed in a common housing, the sun gear of the planetary gear mechanism is connected to the rotor shaft of the motor, and the ring gear of the planetary gear mechanism is connected to the output gear shaft. Are combined.

[0004]

However, in such a conventional hybrid drive device, since the sun gear of the planetary gear mechanism is connected to the rotor shaft of the motor, the planetary gear mechanism and the motor are connected at the time of production. It cannot be subassembled separately. For this reason, the performance of the motor and the like cannot be individually examined during production, and there is a problem that productivity is poor.

Further, since the thrust load acting on the output gear is input to the gear element of the planetary gear mechanism,
There is a problem that the bearing structure provided in the planetary gear mechanism becomes large.

[0006] The present invention has been made in view of the above problems, and has as its object to improve the productivity of a hybrid drive device.

[0007]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the invention according to claim 1 is directed to a motor in which an inner rotor and an outer rotor are arranged concentrically inside a motor housing; A planetary gear mechanism for selectively transmitting the rotation of the rotor and the rotation of the outer rotor to an output gear via a gear element; a gear housing for accommodating the planetary gear mechanism; and a thrust receiving a thrust load acting on the gear element in the gear housing. It is provided with a receiving portion, and coupling means for connecting at least one of the inner rotor and the outer rotor and the gear element of the planetary gear mechanism to each other so that a thrust load is not input.

According to a second aspect of the present invention, an oil passage for guiding oil for lubricating the planetary gear mechanism is formed in the thrust receiving portion.

According to a third aspect of the present invention, there is provided means for connecting an output gear to a gear element of a planetary gear mechanism so that a thrust load is not inputted, and a housing for accommodating a thrust load acting on the output gear in a housing for accommodating the output gear. And a bearing for supporting the bearing.

According to a fourth aspect of the present invention, an output gear is connected to the outer rotor.

According to a fifth aspect of the present invention, the output gear is supported via a pair of rolling bearings, each rolling bearing is arranged so that each rolling element is inclined outward, and oil is supplied to each rolling bearing. A configuration is adopted in which the liquid is introduced from the rotation shaft side.

[0012]

According to the first aspect of the present invention, a thrust receiving portion for supporting a thrust load acting on the gear element of the planetary gear mechanism is formed in the housing, and the motor is mounted on the gear element of the planetary gear mechanism. By connecting via joint means so that is not input,
It is possible to separate the sub-assembly in which the motor is assembled and the sub-assembly in which the planetary gear mechanism is assembled. As a result, it is possible to individually check the performance of the motor and the planetary gear mechanism at the time of production, thereby improving productivity.

Further, since the thrust load from the planetary gear mechanism does not act on the motor, the size of the bearing structure of the motor can be reduced and the durability can be improved.

According to the second aspect of the present invention, since the oil passage is formed in the thrust receiving portion, it is not necessary to arrange the oil passage inside the motor, and the structure of the motor-side sub-assembly can be simplified. .

According to the third aspect of the present invention, the thrust load acting on the output gear is not input to the planetary gear mechanism, and the bearing structure provided in the planetary gear mechanism can be reduced in size and the durability is improved. . Furthermore, the structure in which the planetary gear mechanism and the output gear are independently supported makes it easy to change the design of the planetary gear mechanism and the output gear according to, for example, the vehicle on which the device is mounted.

According to the fourth aspect of the invention, the torque generated in the outer rotor is directly transmitted to the output gear. Since the outer rotor provided outside the stator has a larger radius of rotation than the inner rotor provided inside the stator, a large torque can be applied to the output gear. For example, by operating the outer rotor as a motor when the vehicle starts moving, the starting acceleration can be enhanced.

In the invention described in claim 5, each rolling bearing is arranged so that each rolling element is inclined outward, thereby shortening the axial span of each rolling bearing.
Compactness is measured. The oil is introduced between the rolling bearings from the side of the rotating shaft, whereby the oil receives centrifugal force and is guided to the rolling bearings and the output gear, so that the lubricity thereof can be ensured.

[0018]

BEST MODE FOR CARRYING OUT THE INVENTION

[0019]

Embodiments of the present invention will be described below with reference to the accompanying drawings.

As shown in FIG. 1, the hybrid drive system for a vehicle includes a multi-layer motor 1 having a multi-rotor structure, an engine (not shown), a planetary gear mechanism 3, a reduction gear mechanism 4, a differential gear mechanism 5, and the like. You.

The multi-layer motor 1, an engine provided in the planetary gear mechanism 3 is first on the axis O _1, respectively, the axis O ₁
The reduction gear mechanism 4 is provided on an axis O ₂ parallel to the axis O ₂ , and the differential gear mechanism 5 is provided on an axis O _{3 also} parallel to the axis O ₁ .

The output torque generated by the engine or the multi-layer motor 1 is transmitted through the output gear 35 and the reduction gear mechanism 4 to the final gear 18 after being reversed and reduced in speed. Is transmitted.

Idler shaft 36 of reduction gear mechanism 4
, A primary reduction gear 16 meshing with the output gear 35, a secondary reduction gear 17 meshing with the final gear 18 of the differential gear mechanism 5, and a parking gear 19 fastened when parking.

The multi-layer motor 1 has a three-layer multi-rotor structure in which the inner rotor 10 and the outer rotor 30 are arranged concentrically with predetermined gaps inside and outside the cylindrical stator 20, respectively. The inner rotor 10 includes a cylindrical inner rotor shaft 11 rotatably supported, and a plurality of permanent magnets 37 coupled to the outer periphery of the inner rotor shaft 11, and the outer rotor 30 has a rotatably supported cylindrical shape. , And a plurality of permanent magnets 38 coupled to the inner periphery of the outer rotor drum 13. The stator 20 includes a plurality of core steel plates 21 stacked in the axial direction, and a coil 15 wound on the stacked core steel plates 21. The coil 15 of the stator 20 is shared between the inner rotor 10 and the outer rotor 30, and each coil 15 has an inner rotor 10.
The inner rotor 10 and the outer rotor 30 are operated as a motor or a generator by applying a composite current so that a rotating magnetic field is generated with respect to the outer rotor 30. As a result, the size of the multilayer motor 1 can be reduced, and the loss due to current can be reduced. The basic structure of the multilayer motor 1 has already been proposed by the present applicant as Japanese Patent Application No. 10-77449.

The planetary gear mechanism 3 includes, as three gear elements, a sun gear 31, a plurality of pinions 32 meshing with the sun gear 31, and each pinion 32 is connected to a pinion shaft 3.
9 and a ring gear 33 meshed with each pinion 32.
1 and a carrier 34 and a ring gear 33 have a three-layer multi-axis structure in which they are arranged concentrically.

In the planetary gear mechanism 3, the sun gear 31 is connected to the inner rotor 10, the carrier 34 is connected to the engine crankshaft via the engine output shaft 24 and the flywheel damper 26, and the ring gear 3
3 is connected to the outer rotor 30 and to the output gear 35. The drive plate 49 is fastened to the rear end of the crankshaft via a bolt 29.

The outer rotor 30 is connected to the output gear 35 via the ring gear 33, so that a large torque can be directly applied from the outer rotor 30 to the output gear shaft 40 when the vehicle starts moving. In addition, when the vehicle is decelerated, torque is directly applied from the output gear 35 to the outer rotor 30, so that regenerative power generation is effectively performed.

When the electromagnetic clutch 6 is not engaged, the torque generated by the engine is transmitted from the crankshaft to the carrier 34 via the drive plate 49, the flywheel damper 26 and the engine output shaft 24, and
2 and is distributed to a sun gear 31 and a ring gear 33. At this time, the rotation speed and torque of the output gear 35 are adjusted by operating the inner rotor 10 and the outer rotor 30 as a motor or a generator. The engine is started by rotating the crankshaft by operating the inner rotor 10 as an electric motor.

When the electromagnetic clutch 6 is engaged, the torque generated by the engine is transmitted from the crankshaft to the output gear 35 via the drive plate 49, the drive member 62, the driven member 61, and the clutch output shaft 60. During traveling, the torque generated by the engine is directly transmitted to the output gear 35. These electromagnetic clutches 6,
The drive plate 49, the flywheel damper 26 and the drive plate 49 serve as a flywheel mass.

The hybrid drive unit includes a sub-assembly 7 in which the multilayer motor 1 is housed in a motor housing 41 and is unitized, a planetary gear mechanism 3, a reduction gear mechanism 4, a differential gear mechanism 5, and the like. It is structured to be housed in the housing 57 and separable into the unitized sub-assembly 8.

As shown in FIG. 2, the motor housing 41 of the multi-layer motor 1 has a bottomed cylindrical shape, and the cylindrical stator 20 is substantially provided with a plurality of bolts 43 on a rear wall portion 41a serving as the bottom. It is concentrically concluded. Thus, the stator 20 is cantilevered by the motor housing 41. A disk-shaped separate plate 46 and a stator bracket 44 are interposed between the motor housing rear wall portion 41a and the rear surface of the stator 20, and a disk-shaped front plate 45 joined to the front surface of the stator 20 is provided. Each bolt 4
The reference numeral 3 penetrates the rear wall portion 41 a of the motor housing, the separate plate 46, the stator bracket 44, and the stator 20, and is screwed to the front plate 45 to fasten the stator 20 to the motor housing 41.

The outer rotor shaft portions 30a and 30b provided at both ends of the outer rotor 30 are rotatably supported at both ends via ball bearings 63 and 64 and a ball bearing 65, respectively.

The outer rotor shaft portion 30a located on the side from which the output of the outer rotor 30 is taken out is divided into a cylindrical outer rotor drum 13 to which a permanent magnet 38 is coupled and a thrust support member for the outer rotor drum 13. As a thrust support member of the outer rotor drum 13, an outer drum cover 23 is fastened to the front end of the outer rotor drum 13 via a plurality of bolts 28, and an inner drum cover 27 is welded to the inner peripheral end of the outer drum cover 23. Is fixed. The outer drum cover 23 is positioned with respect to the outer rotor drum 13 via the knock pin 166.

Openings 50w, 23w, 13w, 41w for guiding cooling air into the gear housing 50, the outer drum cover 23, the outer rotor drum 13, and the motor housing 41.
Are respectively formed. The outer drum cover 23 has cooling fins 23a and is formed by press working.
As the outer rotor 30 rotates, air is blown around the stator 20 by the cooling fins 23a to cool the stator 20. The air filters 17 are provided in the openings 41w and 50w.
0,171 is attached. The cooling air is taken into the motor housing 41 through the air filters 170 and 171 to prevent iron powder and the like from entering the motor housing 41 and prevent the iron powder from adhering to the permanent magnets 37 and 38. I have to.

The inner drum cover 27 has a cylindrical shaft portion 27.
a and a scale portion 27b. The inner drum cover 27 is formed by casting or forging. The outer drum cover 23 and the inner drum cover 27 are fixed by beam welding, and thermal deformation of both is suppressed.

The pair of ball bearings 63 and 64 are mounted on the gear housing 50 so as to sandwich the outer rotor shaft 30a.
And the stator 20.

The rear end of the inner race of the deep ball type ball bearing 63 has a cylindrical shaft portion 27a of the outer rotor shaft portion 30a.
, And the front end of the outer race is in contact with the gear housing 50 via the shim 66. The deep ball type ball bearing 64 has a rear end of its inner race in contact with the cylindrical shaft portion 27a of the outer rotor shaft portion 30a, and a front end of its outer race in contact with the front plate 45 of the stator 20. The outer rotor drum 13 is supported by a ball bearing 63 against a thrust load that is to be moved forward (rightward in the figure). The outer rotor drum 13 is supported via a ball bearing 64 against a thrust load to be moved rearward (leftward in the figure).

The outer rotor shaft portion 30b located on the side from which the output of the outer rotor 30 is not taken out is formed integrally with the rear end of the outer rotor drum 13. The ball bearing 65 is interposed between the outer rotor shaft 30b and the motor housing 41. The inner race of the deep ball type ball bearing 65 is connected to the motor housing 41 via a snap ring 67.
And the outer rotor shaft portion 30b is slidably fitted to the outer race. Outer rotor drum 1
3 is each ball bearing 63,
64 and 65 are supported.

The opening diameter of the outer rotor shaft portion 30b is
0, the outer rotor drum 1 with respect to the motor housing 41 when the sub-assembly 7 is assembled.
3 needs to be assembled before the stator 20. For this reason, the outer rotor drum 13 and the outer drum cover 23
Can be separated from each other, and the outer rotor shaft portion 30b
No need to position in the thrust direction. When assembling the sub-assembly 7, the motor housing 41
After the outer rotor shaft portion 30b is fitted to the outer race of the ball bearing 65, the stator 20 is fastened to the motor housing 41 via the bolts 43, and the outer drum is connected to the outer drum. The cover 23 is fastened to the front end of the outer rotor drum 13 via each bolt 28.

The inner rotor shaft portion 10 a located on the side from which the output of the inner rotor 10 is taken out is formed integrally with the inner rotor shaft 11. The deep ball type ball bearing 71 has an inner race fitted to the inner rotor shaft portion 10a and fixed via a snap ring 73, and an outer race fitted to the inside of the cylindrical shaft portion 27a of the outer rotor shaft portion 30a. Then, it is fixed via the snap ring 74.

The inner rotor shaft 10 b located on the side from which the output of the inner rotor 10 is not taken out is formed integrally with the rear end of the inner rotor shaft 11. Radial needle bearing 72
Is interposed between the inner peripheral surface of the rear wall portion 41a of the motor housing and the inner rotor shaft portion 10a. The radial needle bearing 72 includes the stator bracket 44 and the end plate 7.
5 for positioning in the thrust direction.

The deep ball bearings 63, 64, 65, 71 and the radial needle bearing 72 interposed in the sub-assembly 7 have a sealed structure in which grease is sealed.

The inner rotor shaft 11 has a ball bearing 71 and a radial needle bearing 72 for a radial load.
It is supported by sharing. The inner rotor shaft 11 is not supported by the thrust load via the radial needle bearing 72, but is supported by only the ball bearing 71.

The multilayer motor 1 has a structure in which the cooling liquid flows in and out from the rear end of the stator 20, and the cooling liquid flows in the stator 20 in the axial direction and makes a U-turn at the front end of the stator 20.

The water jacket 80 for circulating the coolant through the stator 20 is defined between a bolt hole 81 for passing the bolt 43 of the core steel plate 21 and the outer peripheral surface of the bolt shaft 43a. The bolt 43 has an outer diameter of the shaft portion 43a and the screw portion 4
Since it is formed smaller than the outer diameter of 3b, a sufficient flow passage cross-sectional area of the cooling liquid is secured between the bolt 43 and the bolt hole 81.

FIG. 7 shows the stator 20 along the line EE in FIG.
The core steel plate 21 is divided into 18 pieces in the circumferential direction and is connected to each other via a resin mold 83. Two coils 1 for one core steel plate 21
5, and a total of 36 coils 15 are wound on the entire stator 20. Each core steel plate 21 extends in the radial direction 2
The coil 15 is wound around each core 21a.

The number of the water jackets 80 is 15
Is set to の of the number, ie, 18. Bolt holes 81 that define each water jacket 80 are formed between adjacent core steel plates 21.

FIG. 8 is a front view of the front plate 45 along the line FF in FIG. 2. The front plate 45 is formed with a U-turn flow path 84 that connects two adjacent water jackets 80. One water jacket 8
The coolant that has flowed forward through 0 (rightward in FIG. 2) flows into the adjacent water jacket 80 through the U-turn flow path 84, and flows backward (leftward in FIG. 2) through the water jacket 80. It is flowing. That is, the flow of the coolant flowing forward from the inlet 85 through the water jacket 80 and the flow of the coolant flowing backward through the U-turn flow path 84 are alternately arranged. 8, reference numeral 119 denotes a screw hole into which the screw portion 43a of each bolt 43 is screwed. The space between the bolt 43 and the screw hole 119 is sealed via a liquid gasket.

The flow paths through which the coolant flows into and out of the water jackets 80 include the laminated end plates 75, the rear wall portion 41a of the motor housing, the separate plates 46,
It is provided on the stator bracket 44. These members are sealed with a gasket such as a liquid sheet rubber coating.

The motor housing 41 has a rear wall portion 41a.
A cylindrical portion 41c projecting rearward from the outer periphery of the cylindrical portion 41c.
The inner race of the ball bearing 65 is fitted on the outer peripheral surface of the cylindrical portion 41c, and the end plate 75 is disposed inside the cylindrical portion 41c. The flow path through which the coolant flows into and out of each water jacket 80 is provided in a space inside the cylindrical portion 41c of the motor housing 41.

The end plate 75 is joined to the rear portion of the motor housing rear wall portion 41a and is fastened through a plurality of bolts 76. Each bolt 76 passes through the end plate 75 and the rear wall 42 of the motor housing, and is screwed to the stator bracket 44.

FIG. 3 is a view of the end plate 75 and the like viewed from the direction of arrow A in FIG. 2. The end plate 75 is provided with an inlet 85 and an outlet 86 as coolant passages for allowing coolant to enter and exit the water jackets 80. Is done. The inlet 85 communicates with the discharge side of the pump via a pipe (not shown) connected thereto. The outlet 86 communicates with a pipe (not shown) connected thereto and a suction side of the pump via a radiator (heat exchanger). The inlet 85 and the outlet 86 are arranged between the ball bearings 65.

In order to rotate the inner rotor 10 and the outer rotor 30 synchronously, rotation angle sensors 113 and 114 for detecting the phases of the inner rotor 10 and the outer rotor 30 are provided. A control circuit (not shown) to which signals from the rotation angle sensors 113 and 114 are input generates a PWM signal based on required torque (positive or negative) data for the inner rotor 10 and the outer rotor 30.

The rotation angle sensor 114 is connected to the gear housing 5.
0, and the phase of the outer rotor 30 is detected facing the scale portion 27b of the inner drum cover 27.

In FIG. 3, reference numeral 116 denotes an electric wire for guiding a current to each coil 15.
3 is a unit component 11 integrated via a resin mold
7 is fastened via three bolts 79. A rear end of the rotation part of the rotation angle sensor 113 is coupled to the inner rotor shaft 11 with a spline or a two-sided width to allow the inner rotor shaft 11 to be displaced in the thrust direction.

The unit part 117 includes an inlet 85 and an outlet 8
6 and arranged between the inner rotor 10 and the inner rotor 10 so that the unit component 117 does not project from the rear end of the multilayer motor 1.

FIG. 4 is a sectional view of the rear wall portion 41a of the motor housing taken along the line BB in FIG. 2. Two annular flow paths 87 and 88 are formed concentrically on the rear wall portion 41a of the motor housing. You. The inner annular channel 87 communicates with an inlet 85 of the end plate 75, and the outer annular channel 88 communicates with an outlet 86 of the end plate 75. Each annular channel 87,
Reference numeral 88 denotes a hole 89 through which each bolt 76 is inserted, and each bolt 7
It is formed so as to be curved so as to avoid the hole 90 through which the hole 9 is inserted. In FIG. 4, reference numeral 96 denotes a hole through which the bolt 43 is inserted.

FIG. 5 is a front view of the separate plate 46 along the line CC in FIG. 2, and the separate plate 46 has holes 91, 92 communicating with the annular flow paths 87, 88, respectively.
Are formed nine by one. For convenience, FIG. 5 shows each of the annular passages 87, 88 formed on the motor housing rear wall 41a side.
Is indicated by a two-dot chain line. In FIG. 5, reference numeral 97 denotes a hole through which the bolt 43 is inserted, 98 denotes a hole through which the bolt 76 is inserted, and 99 denotes a hole through which the bolt 79 is inserted.

FIG. 6 shows the stator bracket 4 shown in FIG.
FIG. 4 is a front view of FIG. 4, and nine radial channels 93 and 94 extending radially are formed in the stator bracket 44.
The inner peripheral end of the radial flow path 93 is formed through the hole 91 through the annular flow path 8.
7, the inner peripheral end of the radial flow path 94 communicates with the annular flow path 88 via a hole 92. For convenience, FIG. 6 shows each annular flow path 8 formed on the motor housing rear wall 41a side.
7, 88 is indicated by a two-dot chain line. Each radial channel 93,
Numerals 94 extend radially and each outer peripheral end is
3 is connected to a hole 95 through which the water jacket 80 is inserted, and communicates with each water jacket 80. In FIG. 6, reference numeral 121 denotes a hole through which the bolt 76 is inserted, and reference numeral 122 denotes a hole through which the bolt 79 is inserted.

As shown in FIG. 9, a thrust receiving wall portion 50a for receiving a thrust load acting on the planetary gear mechanism 3 is formed in the gear housing 50. The front end of the inner rotor shaft 11 is connected to the sun gear 31 via a spline 125 as coupling means, and is slidable in the rotational direction and the thrust direction with respect to the engine output shaft 24 via a radial bush bearing 126. Be linked.
Further, the cylindrical shaft portion 27a is connected to the rotating member 129 of the ring gear 33 via a spline 127 as joint means. Thereby, rotation is transmitted between the inner rotor 10 and the sun gear 31 and rotation is transmitted between the outer rotor 30 and the ring gear 33, but no thrust load acts on the inner rotor shaft 11 from the planetary gear mechanism 3.

From the planetary gear mechanism 3 to the inner rotor shaft 11
The sub-assembly 7 and the sub-assembly 8 can be unitized by the structure in which the thrust load does not work. The multilayer motor 1 can operate as a motor or a generator by supporting the inner rotor shaft 11 in the thrust direction even when the sub-assembly 7 is alone.

The rotating member 129 is connected to the outer periphery of the ring gear 33 via a spline 128. Rotating member 1
A thrust needle bearing 130 is interposed between the gear 29 and the thrust receiving wall 50a of the gear housing 50. A thrust needle bearing 131 is interposed between each pinion shaft 39 and a disk-shaped plate 132 connected to the rear end of the carrier 34. Rotating member 1
29 is supported by the thrust needle bearings 130 and 131 with respect to the thrust load. Rotating member 12
A radial bush bearing 134 is interposed between the gear bush 9 and the gear housing 50, and the rotating member 129 is supported by the radial bush bearing 134 against a radial load.

A sleeve 135 is interposed between the inner rotor shaft 11 and the rotating member 129, and a thrust needle bearing 136 is interposed between the sleeve 135 and the sun gear 31. A thrust needle bearing 137 is interposed between the sun gear 31 and the carrier 34.

The carrier 34 is connected to the engine output shaft 24 via a spline 138. Carrier 34
A thrust needle bearing 141 is interposed between the ring member 33 and the rotating member 25 of the ring gear 33.

The output gear 35 is arranged on a concentric circle of the output gear shaft 40, and the output gear 35 and the output gear shaft 40 are integrally formed via a disk-shaped disk portion 48. Output gear shaft 4
The rotation member 25 of the ring gear 33 is connected to the inner periphery of the ring gear 0 via a spline 142 and the clutch output shaft 60 is connected to the inner circumference of the ring gear 33 via a spline 143.

The splines 127 of the cylindrical shaft 27a, the splines 138 of the carrier 34, and the like are formed by broaching.

A sub-housing 147 is fastened to the clutch housing 57 via a plurality of bolts 148. The output gear shaft 40 has a pair of roller bearings (rolling bearings) 1 between the clutch housing 57 and the sub-housing 147.
44, 145 are supported. Roller bearing 1
45 is interposed between the sub-housing 147 and the disk part 48. The roller bearing 145 is interposed between the clutch housing 57 and the disk part 48.

The roller bearing 144 has a front end of the inner race in contact with the clutch housing 57 and a rear end of the outer race in contact with the disk portion 48 of the output gear 35. The output gear 35 is supported by the roller bearing 144 against a thrust load that is to be moved forward (to the right in the drawing).

The roller bearing 145 has a rear end of its inner race in contact with the sub-housing 147 and a front end of its outer race in contact with the disk portion 48 of the output gear 35. The output gear 35 is supported by a roller bearing 145 against a thrust load that is to be moved rearward (leftward in the figure).

The roller bearings 144 and 145 are arranged so that each tapered roller (rolling element) is inclined outward.
The shaft span between the roller bearings 144 and 145 is shortened.

In order to forcibly lubricate the planetary gear mechanism 3 and the roller bearings 144, 145, etc., the thrust receiving wall 50 a of the gear housing 50 has an oil inlet 150 as an oil passage for introducing oil into the gear housing 50. Is formed. Oil discharged from an electric oil pump (not shown) is introduced into an oil inlet 150, and then formed into an annular flow path 151 formed in a radial bush bearing 134 and an annular flow path 1 formed in a sleeve 135.
Oil gallery 15 in the inner rotor shaft 11 through
Flow into 3 Part of the oil that has flowed into the oil gallery 153 is guided to the planetary gear mechanism 3 through the radial bush bearing 126, and the rest is supplied to the engine output shaft 2.
4 through the oil gallery 154, the plurality of through holes 155 formed in the output gear shaft 40, and the plurality of holes 156 formed in the disc portion 48.
5 and the output gear 35. The oil that has lubricated each part in this way is recovered via a return passage (not shown) connected to the gear housing 50. In addition, the through hole 155 also serves as a working window when the bearing is removed.

An oil seal 161 is provided between the gear housing 50 and the rotating member 129, an oil seal 162 is provided between the rotating member 129 and the inner rotor shaft 11, and an oil seal 16 is provided between the clutch housing 57 and the clutch output shaft 60.
3, an oil seal 164 is interposed between the clutch output shaft 60 and the engine output shaft 24, respectively. Each oil seal 161 shaft portion 164 is sealed so that oil guided to the planetary gear mechanism 3 and each roller bearing 144, 145, etc. does not leak to the multilayer motor 1 side or the electromagnetic clutch 6 side.

Next, the operation of the embodiment of the present invention configured as described above will be described.

For example, during normal running of the vehicle, the torque generated by the engine 2 is transmitted from the crankshaft to the carrier 34 via the drive plate 49, the flywheel damper 26 and the engine output shaft 24, and the pinions 32
Through the sun gear 31 and the ring gear 33.
At this time, the rotation speed and torque of the output gear shaft 40 are adjusted by operating the inner rotor 10 and the outer rotor 30 as a motor or a generator.

The outer rotor 30 provided outside the stator 20 is similar to the inner rotor 10 provided inside the stator 20.
Since the radius of rotation is larger than that of, the generated torque can be increased. Outer rotor 30 is ring gear 33
And the output gear shaft 40 is rotated integrally with the output gear shaft 40 through the outer rotor 30 when the vehicle starts moving.
By applying a large torque directly to zero, acceleration at the start can be ensured. Further, when the vehicle is decelerated, torque is directly applied from the output gear shaft 40 to the outer rotor 30, so that regenerative power generation is effectively performed.

When the vehicle is running at high speed, the torque generated by the engine is directly transmitted to the output gear shaft 40 by the engagement of the electromagnetic clutch 6, so that the engine output is divided by the planetary gear mechanism 3 and the inner rotor 10 The engine and the output gear shaft 4 generate electricity and do not drive the outer rotor 30.
By directly connecting 0, the power generation amount of the inner rotor 10 required at the time of high-speed traveling can be small, and the size of the inner rotor 10 can be reduced.

By the way, the inner rotor 10 and the outer rotor 30 of the multilayer motor 1 are arranged concentrically, are coaxial with the sun rotor 31 and the sun gear 31 of the planetary gear mechanism 3.
The structure in which the carrier 34 and the ring gear 33 are also arranged on concentric circles makes it possible to reduce the size of the apparatus. As a result, when mounted on a vehicle, the limitation on the size of the multilayer motor 1 can be reduced, and the structure for taking out the output from the output gear 35 can be simplified.

In the multilayer motor 1, the outer rotor drum 1
3 is each ball bearing 63,
64 and 65 are supported. Ball bearing 6
Since the support span of the outer rotor drum 13 is sufficiently secured, the gap between the outer rotor 30 and the stator 20 can be properly maintained.

The outer rotor 30 is not supported via a ball bearing 65 against a thrust load, but is supported by a pair of ball bearings 63 and 64 provided on the output take-out side. Thus, a snap ring or the like for positioning the ball bearing 65 with respect to the outer rotor shaft portion 30b becomes unnecessary, and the front-rear length of the outer rotor drum 13 can be reduced.

When assembling the sub-assembly 7, the ball bearing 65 is connected to the motor housing 41 via the snap ring 67, and then the outer rotor shaft 30b is fitted to the outer race of the ball bearing 65. Since the outer rotor shaft portion 30b is not required to be positioned in the thrust direction with respect to the ball bearing 65, the outer rotor 30 can be easily assembled to the motor housing 41 and the productivity can be increased.

When assembling the sub-assembly 7,
Since the outer rotor drum 13 is separated from the outer drum cover 23 and the like with respect to the motor housing 41 and is assembled before the stator 20, the outer rotor shaft portion 3 is formed.
The opening diameter of 0b can be formed smaller than the outer diameter of the stator 20. As a result, the diameter of the ball bearing 65 can be reduced, and the maximum rotation speed of the outer rotor 30 can be increased.

The inner rotor 10 is provided with a ball bearing 71 and a radial needle bearing 72 for a radial load.
It is supported by sharing. The inner rotor 10 is not supported by the radial needle bearing 72 with respect to the thrust load, but is supported only by the ball bearing 71. Thus, the inner rotor shaft portion 10b can be supported by the thin radial needle bearing 72.

By reducing the size of the ball bearing 65 and the radial needle bearing 72 provided at the rear portion of the multilayer motor 1 as a structure for supporting only a radial load, a space for providing a support structure for the stator 20 between the two is provided. It is possible to secure a space for the coolant for cooling the cooling water 20 to enter and exit.

The radial needle bearing 72 is positioned in the thrust direction by being sandwiched between the stator bracket 44 and the end plate 75, thereby simplifying the structure.

The rotation angle sensor 114 detects the phase of the outer rotor 30 facing the scale portion 27b of the inner drum cover 27. The rotation angle sensor 11 is formed by integrally forming the scale portion 27b with the inner drum cover 27 supported by the pair of ball bearings 63 and 64.
4, the displacement of the scale portion 27b with respect to 4 is kept small,
The detection accuracy of the rotation angle sensor 114 can be sufficiently ensured.

Then, in the multilayer motor 1, the stator 2
The coolant circulates inside the stator 20 to absorb the heat generated by the zero copper loss and iron loss. However, since the stator 20 is cantilevered and the outer drum cover 23 and the like of the outer rotor 30 rotate facing the front end of the stator 20, it is difficult to connect the coolant passage to the front end of the stator 20. In response to this, the coolant flows in the stator 20 in the axial direction, and U
The cooling liquid is made to enter and exit from the rear end of the stator 20.

The coolant discharged from the pump flows through the inlet 85, the annular passage 87, the hole 91, and the radial passage 93, and is diverted to each water jacket 80. The coolant circulating in each water jacket 80 absorbs heat of the stator 20, flows out through the radial flow path 94, the hole 92, the annular flow path 88, and the outlet 86, and radiates heat to the outside air through the radiator. Sucked in the pump.

By defining the water jacket 80 around each bolt 43 for fastening the stator 20,
The water jackets 80 can be densely arranged in a limited space located inside the coil 15, and the stator 20 can be sufficiently cooled. Further, the size of the stator 20 can be prevented from being increased due to the water jacket 80.

The number of the water jackets 80 is
Of each water jacket 80
By symmetrically arranging the coils 15 as heat sources, cooling of the stator 20 is performed uniformly in the circumferential direction.

While the coolant absorbs the heat of the stator 20 while flowing through the water jacket 80, the coolant gradually rises.
By alternately arranging the flow of the coolant toward the water jacket 80 and the flow of the coolant toward the rear, the stator 20 is cooled uniformly in the circumferential direction.

The ball bearing 65 and the inner rotor shaft 11 are formed by stacking the rear wall portion 41a of the motor housing in which the annular flow paths 87 and 88 are formed and the stator bracket 44 in which the radial flow paths 93 and 94 are formed. It is possible to form a flow path through which the coolant flows into and out of each water jacket 80 in a limited space therebetween. By keeping the flow path of the coolant in a small space in this manner, the diameter of the ball bearing 65 can be reduced, and the maximum rotation speed of the outer rotor 30 can be increased.

Also, the housing portion is a small hole in assembly.
After soldering the terminal board after assembly,
By providing a unit component 117 in which the terminal plate 6 and the rotation angle sensor 113 are integrated via a resin mold,
Electric wire 116 for guiding current to each coil 15 and rotation angle sensor 1
13 can be easily assembled, and the productivity can be increased.

The unit part 117 includes an inlet 85 and an outlet 8
By arranging in the space between the inner rotor 6 and the inner rotor 10, the unit component 117 does not protrude from the rear end of the multilayer motor 1, and the front-rear length of the multilayer motor 1 can be reduced.

The gear housing 50 for accommodating the planetary gear mechanism 3 has a thrust receiving portion 50a for receiving a thrust load acting on the planetary gear mechanism 3, and connects the inner rotor 10 to the sun gear 31 so that the thrust load is not input. 125 and a spline 127 for connecting the outer rotor 30 to the ring gear 33 so that a thrust load is not input, the sub-assembly 7 in which the multilayer motor 1 is assembled and the sub-assembly 8 in which the planetary gear mechanism 3 and the like are assembled. It becomes possible to separate. As a result, at the time of production, the multilayer motor 1 can be operated via the test machine in a state of the sub-assembly 7 alone, and the performance of the multilayer motor 1 can be checked in advance.

Further, since the thrust load does not act on the inner rotor shaft 11 from the planetary gear mechanism 3, the ball bearings 63, 64, 71 for supporting the thrust load in the multilayer motor 1 can be prevented from being enlarged. Durability is improved.

A relatively large thrust load acting on the output gear 35 constituted by a helical gear is supported via a pair of roller bearings 144 and 145. Thus, the thrust load acting on the output gear shaft 40 is not input to the planetary gear mechanism 3 via the spline 142,
Operability of the planetary gear mechanism 3 can be ensured. Further, in the planetary gear mechanism 3, the bearing structure constituted by the thrust needle bearings 130, 131, 136, 137, 141 is prevented from being enlarged, and the durability is improved. Further, the planetary gear mechanism 3 and the output gear shaft 40
Are independently supported, the design of the planetary gear mechanism 3 and the output gear 35 can be easily changed according to the vehicle to be mounted.

Each of the roller bearings 144 and 145 is disposed such that each tapered roller is inclined outward, thereby shortening the axial span between the roller bearings 144 and 145.
Accordingly, in a limited space between the multilayer motor 1 and the engine, the planetary gear mechanism 3, the output gear 35, and the electromagnetic clutch 6 can be arranged in parallel.

The oil introduced into the oil inlet 150 is
An annular channel 151 formed in the radial bush bearing 134 and an annular channel 152 formed in the sleeve 135
And flows into the oil gallery 153 in the inner rotor shaft 11. A part of the oil that has flowed into the oil gallery 153 is guided to the planetary gear mechanism 3 through the radial bush bearing 126, and the remaining oil is provided in the oil gallery 154 in the engine output shaft 24 and a plurality of through holes formed in the output gear shaft 40. 155 and the roller gears 144 and 145 and the output gear 35 through a plurality of holes 156 formed in the disk portion 48. Each roller bearing 144
The oil is guided to the 145 and the output gear 35 by receiving the centrifugal force, and the lubricity thereof can be secured.

The oil introduced into the oil inlet 150 formed in the thrust receiving portion 50a is supplied to the planetary gear mechanism 3
The oil inlet 1
The entire oil passage constituted by 50 and the like can be accommodated in the sub-assembly 8, and it is not necessary to provide the oil inlet 150 and the like in the sub-assembly 7, and the structure can be simplified.

As another embodiment, the multilayer motor 1 may have a structure in which the stator 20 is provided with dedicated coils for the inner rotor 10 and the outer rotor 30, respectively. However, in that case, the size of the mechanism increases, and the loss due to current increases.

Further, the multi-layer motor 1 may be an induction motor having coils on the inner rotor 10 and the outer rotor 30.

Further, in the above-described embodiment, the outer rotor 30 and the inner rotor 10 are configured to rotate separately.
The configuration is not limited to this, and the outer rotor 30 and the inner rotor 10 may be configured to rotate integrally.

In the above embodiment, the outer rotor 3
Although the output of the inner rotor shaft 10 is extracted from the front end side of the output of the inner rotor shaft 11, the output of the inner rotor shaft 11 may be extracted from the rear end side.

Further, a dry single-plate clutch, a wet multi-plate clutch or the like may be provided instead of the electromagnetic clutch 6.

The outer drum cover 23 and the inner drum cover 27 may be connected to each other via rivets.

Further, in the rear wall portion 41a of the motor housing, each annular flow path is formed facing the end plate 75, and a hole is formed for communicating each annular flow path with each radial flow path 93 of the stator bracket 44. May be. In this case, the separate plate 46 can be eliminated.

The radial bush bearing 126
A needle bearing may be provided instead. In this case, the amount of oil guided to the planetary gear mechanism 3 can be increased.

The present invention can be applied not only to the multilayer motor 1 constituting the hydride drive device combined with the engine as in the above embodiment, but also to a multilayer motor used in another device.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of a hybrid drive device according to an embodiment of the present invention.

FIG. 2 is a sectional view of a motor and the like.

FIG. 3 is a front view similarly viewed from the direction of arrow A in FIG. 2;

FIG. 4 is a sectional view taken along the line BB of FIG. 2;

5 is a front view of the separate plate along the line CC in FIG. 2;

FIG. 6 is a front view of the stator bracket taken along the line DD in FIG. 2;

FIG. 7 is a sectional view taken along the line EE in FIG. 2;

FIG. 8 is a front view of the front plate along the line FF of FIG. 2;

FIG. 9 is a sectional view of a planetary gear mechanism and the like.

[Explanation of symbols]

 Reference Signs List 1 multilayer motor 3 planetary gear mechanism 4 reduction gear mechanism 5 differential gear mechanism 6 electromagnetic clutch 7 sub-assembly 8 sub-assembly 10 inner rotor 10a inner rotor shaft 10b inner rotor shaft 11 inner rotor shaft 13 outer rotor drum 15 coil 20 stator 21 Core steel plate 23 Outer drum cover 24 Engine output shaft 27 Inner drum cover 27a Cylindrical shaft portion 27b Scale portion 30 Outer rotor 30a Outer rotor shaft portion 30b Inner rotor shaft portion 31 Sun gear 32 Pinion 33 Ring gear 34 Carrier 35 Output gear 40 Output gear shaft 41 Motor Housing 41a Rear Wall of Motor Housing 43 Bolt 44 Stator Bracket 45 Front Plate 46 Separate Plate 50 Gear Housing 50a Thrust G receiving portion 60 Clutch output shaft 57 Clutch housing 80 Water jacket 81 Bolt hole 63 Ball bearing 64 Ball bearing 65 Ball bearing 71 Ball bearing 72 Radial needle bearing 75 End plate 84 U-turn flow path 85 Coolant inlet 86 Coolant outlet 87 Inlet Side annular channel 88 Outlet-side annular channel 93 Inlet-side radial channel 94 Outlet-side radial channel 113 Rotation angle sensor 114 Rotation angle sensor 116 Electric wire 117 Unit part 126 Radial bush bearing 129 Rotary member 134 Radial bush bearing 144 Roller bearing 145 Roller bearing 150 Oil inlet 153 Oil gallery 154 Oil gallery

──────────────────────────────────────────────────の Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) H02K 7/08 H02K 16/02 7/116 B60K 9/00 Z // H02K 16/02 F term (reference) 3J027 FA17 FA36 FA37 FB02 FB40 GB06 GC13 GC22 GD03 GD04 GD07 GE25 GE27 GE29 5H111 AA00 BB02 CC13 DD01 DD08 5H607 AA11 BB01 BB09 BB14 CC01 CC03 CC05 DD02 DD05 DD07 DD19 EE33 FF22 FF24

Claims (5)

[Claims] 1. A motor in which an inner rotor and an outer rotor are concentrically arranged inside a motor housing, and an engine gear, a rotation of the inner rotor and a rotation of the outer rotor are selected as output gears via gear elements. A planetary gear mechanism that transmits the planetary gear mechanism, a gear housing that houses the planetary gear mechanism, a thrust receiving portion that receives a thrust load acting on the gear element in the gear housing, and at least one of the inner rotor and the outer rotor. Coupling means for connecting the gear elements of the planetary gear mechanism to each other so that a thrust load is not input. 2. The hybrid drive device according to claim 1, wherein an oil passage for guiding oil for lubricating the planetary gear mechanism is formed in the thrust receiving portion. 3. A means for connecting the output gear to a gear element of the planetary gear mechanism so that a thrust load is not input, and supporting the thrust load acting on the output gear with respect to a housing accommodating the output gear. The hybrid drive device according to claim 1, further comprising: a bearing. 4. The hybrid drive device according to claim 1, wherein said output gear is connected to said outer rotor. 5. The output gear is supported via a pair of rolling bearings, each of the rolling bearings is arranged such that each rolling element is inclined outward, and a rotary shaft is provided between each rolling bearing. The hybrid drive device according to claim 1, wherein the hybrid drive device is configured to be introduced from a side.