JP3075153B2 - Power transmission mechanism of internal combustion engine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission mechanism for an internal combustion engine, and more particularly, to a power transmission for transmitting a rotational driving force on an output shaft of an internal combustion engine to an input shaft side of a transmission via a motor generator. It concerns the mechanism.

[0002]

2. Description of the Related Art Conventionally, as this kind of technique, for example, there is a technique described in Japanese Patent Application Laid-Open No. 64-77752. The publication describes an engine having a start-up charging device having both functions of a starter motor (electric motor) and an alternator (generator) used for starting the engine.

[0003] As shown in FIG. 9, this start-up charging device includes a flywheel 9 attached to a crankshaft 91 of an engine.
2, a rotating field pole 93 provided on the wheel 92,
A field coil 94 and a stator coil 95 are provided on the inner and outer peripheries of the flywheel 92, respectively.

[0004] The flywheel 92 constitutes a rotor (rotor) of the starting and charging device, and has a crankshaft 9.
One end face is fixed by a plurality of bolts 96,
And can rotate together. In addition, flywheel 9
A plurality of the rotating field poles 93 are formed at regular intervals in the circumferential direction on the outer peripheral portion of the motor 2.

The field coil 94 is attached to an aluminum plate 97 provided on an end face of the engine, and is closely opposed to a flywheel 92. Further, the stator coil 95 is a ring-shaped frame 100 sandwiched between an engine body 98 and a clutch housing 99.
It is stuck to. The core 95a of the stator coil 95 is closely opposed to the outer peripheral surface of the rotating field pole 93, and a minute gap is formed between the core 95a and the same surface.

In the engine with the starting and charging device configured as described above, the flywheel is controlled by applying an electromagnetic force to the rotating field poles 93 by controlling the energization of the field coil 94 and the stator coil 95 to form a rotating magnetic field. 92
Can be rotated. Then, the crankshaft 91 is rotated by the rotational force of the flywheel 92, and the engine can be started. On the other hand, during operation of the engine, only the field coil 94 is energized to generate an induced electromotive force in the stator coil 95, and the battery can be charged by the generated electromotive force.

[0007]

In the above prior art, it is preferable that the gap formed between the rotating field pole 93 and the stator coil 95 be as small as possible. That is, by reducing the gap between the rotating field pole 93 and the stator coil 95, the magnetic resistance can be reduced and the passage of magnetic flux between them can be facilitated. In this way, by passing more magnetic flux between the rotating field pole 93 and the stator coil 95, it is possible to obtain a sufficient rotating torque at the time of starting the engine and to perform more efficient charging. Becomes

However, in the above prior art, since the flywheel 92 having the rotating field poles 93 is attached to the crankshaft 91 of the engine, the air gap fluctuates due to the vibration generated on the crankshaft 91 during operation of the engine. There was a possibility that it would be. Therefore, by setting the gap large, the rotating field pole 93 and the stator coil 9
Therefore, it is necessary to consider design considerations, such as preventing contact with the device 5.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problem, and has a power transmission mechanism for transmitting a rotational driving force on an output shaft of an internal combustion engine to an input shaft of a transmission via a motor generator. It is an object of the present invention to improve the performance of the motor generator by suppressing fluctuation of a gap formed between a stator and a rotor of the motor generator.

[0010]

In order to achieve the above object, the present invention is directed to a rotor which is integrally rotatably connected to an output shaft of an internal combustion engine, and an outer peripheral portion of the rotor. And transmitting the rotational driving force output from the output shaft to the input shaft of the transmission via a motor generator having a stator disposed with a gap through which magnetic flux can pass. In the power transmission mechanism for an internal combustion engine, the stator is fixed to a fixing member provided on the main body of the transmission, while a bearing portion is provided between the rotor and a supporting member provided on the main body of the transmission. The gist is that the rotor is rotatably supported by the bearing portion and the movement of the rotor in the radial direction of the output shaft is restricted.

The invention according to claim 1 having the above-described structure has the following operations. That is, according to the first aspect of the present invention, since both the stator and the rotor of the motor generator are fixed or supported by the main body of the transmission, the fluctuation of the gap formed therebetween is suppressed. You.

More specifically, the stator is fixed to the main body of the transmission, while the rotor is supported by the main body of the transmission via a bearing, and the rotor moves in the radial direction of the output shaft. Is regulated. Therefore, even when vibration occurs on the output shaft of the internal combustion engine during operation, the vibration does not change the gap between the stator and the rotor, and the size of the gap is substantially constant. Will be maintained.

Further, the transmission-side main body on which the stator and the rotor are fixed or supported is less affected by vibrations generated during operation of the internal combustion engine than the main body of the internal combustion engine. The fluctuation is further suppressed.

According to a second aspect of the present invention, in the power transmission mechanism for an internal combustion engine according to the first aspect, the support member extends in the axial direction of the output shaft and is disposed inside the rotor. The gist is that the bearing portion is arranged between an outer peripheral wall surface and an inner peripheral wall surface of the rotor.

According to the second aspect of the present invention having the above structure, in addition to the operation of the first aspect, the outer peripheral wall surface of the support member disposed inside the rotor and the inner peripheral wall surface of the rotor are not required. Since the bearing portion is disposed between the bearing portions, the movement of the rotor in the radial direction of the output shaft is more reliably restricted by the bearing portion.

According to a third aspect of the present invention, in the power transmission mechanism for an internal combustion engine according to the first or second aspect, the output shaft and the input shaft are connected to each other through a fluctuation absorbing means for absorbing the fluctuation of the rotational driving force. The gist is that they are drivingly connected.

According to the third aspect of the present invention having the above-described structure, in addition to the operation of the first or second aspect, the rotational driving force of the output shaft of the internal combustion engine is input to the transmission via the fluctuation absorbing means. Transmitted to the shaft. Although the rotational driving force on the output shaft of the internal combustion engine fluctuates according to the operating state of the internal combustion engine, the fluctuation of the rotational driving force is absorbed by the fluctuation absorbing means. Generation of various vibrations due to the fluctuation is suppressed. Therefore, the stator and the rotor fixed or supported on the main body of the transmission are prevented from vibrating due to the fluctuation of the rotational driving force.

According to a fourth aspect of the present invention, in the power transmission mechanism for an internal combustion engine according to the third aspect, at least a part of the fluctuation absorbing means is provided on an inner peripheral side of the stator, and The gist is that the stator is disposed on the inner side from both end faces of the stator in the axial direction.

According to a fourth aspect of the present invention having the above configuration, in addition to the function of the third aspect of the invention, at least a part of the fluctuation absorbing means is on the inner peripheral side of the stator, and Since the stator is disposed on the inner side from both end faces of the stator in the axial direction of the output shaft, it is possible to suppress an increase in the size of the power transmission mechanism due to the provision of the fluctuation absorbing means.

According to a fifth aspect of the present invention, in the power transmission mechanism for an internal combustion engine according to the third aspect, the fluctuation absorbing means is provided so as to face a base end of the output shaft and a tip end of the input shaft. The gist comprises a pair of rotating members, an elastic member connecting the rotating members, and a viscous fluid sealed between the rotating members.

According to the fifth aspect of the present invention having the above-described structure, in addition to the effect of the third aspect of the present invention, the rotational driving force transmitted from the output shaft of the internal combustion engine to the input shaft side of the transmission varies. When this occurs, the elastic body connecting the two rotating members is elastically deformed and the two rotating members rotate relative to each other, and the viscous fluid sealed between the two rotating members is sheared by the relative rotation. Thus, the elastic body is elastically deformed and the viscous fluid is sheared, whereby the fluctuation of the rotational driving force is effectively absorbed.

[0022]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is embodied as a power transmission mechanism for an engine provided in a vehicle will be described below with reference to FIGS.

FIG. 1 is a sectional view of a power transmission mechanism 11 provided between an engine as an internal combustion engine (located on the left side in the figure) and a transmission as a transmission (located on the right side in the figure). It is. Main power transmission mechanism 11
Has a motor generator 46 having a rotor 49 (rotor) and a stator 50 (stator). Hereinafter, the power transmission mechanism 11 will be described.

As shown in FIG. 1, a crankshaft 12 constituting an output shaft of an engine is rotatably supported by a cylinder block (not shown), and has a base end (right side in the figure) portion. On the side of the cylinder block,
That is, it extends to the transmission side. And
A drive plate 2 is provided on the proximal end surface of the crankshaft 12.
7 is provided so as to be able to rotate integrally with the crankshaft 12.

The input shaft 14 of the transmission
The power transmission mechanism 11 is disposed on the same axis as the crankshaft 12, and has a tip end (left side in the figure) extending from the housing 15 of the transmission to the inside of the power transmission mechanism 11. A drive plate 16 that constitutes a rotating member is provided at the tip of the input shaft 14. The drive plate 16 has a substantially disk shape as a whole, and a boss 16a is formed at the center thereof. As shown in FIG. 1, the boss portion 16a is externally fitted to the distal end portion of the input shaft 14, and is spline-coupled to the coaxial shaft 14, so that the drive plate 16 and the input shaft 14
And can rotate together. The rotational driving force of the engine crankshaft 12 is transmitted from the drive plate 27 to the input shaft 14 of the transmission via the cover, a pair of retainer plates 33 and 34, a coil spring 39, and the drive plate 16, which will be described later. It has become so.

A pump housing 17 as a support member is mounted on the housing 15 of the transmission. A distal end portion of the pump housing 17 is formed in a cylindrical shape having an insertion hole 18 therein as shown in FIG. On the other hand, the proximal end portion of the pump housing 17 is connected to the transmission housing 1 by a plurality of bolts 19.
5 is fixed. A housing hole 20 communicating with the insertion hole 18 and opening toward the housing 15 is formed inside a base end portion of the pump housing 17. When the pump housing 17 is fixed to the transmission housing 15,
A housing space 21 for an oil pump 24 to be described later is formed by a space surrounded by the housing 15 and a wall surface of the housing hole 20.
Are formed. The input shaft 14 of the transmission is inserted through the insertion hole 18 and the housing space 21, and the distal and proximal portions of the coaxial 14 are formed by bearings 22, 23 disposed in the insertion hole 18. Each is rotatably supported.

A drive gear 25 and a driven gear 26 constituting the oil pump 24 are disposed in the housing space 21. The input shaft 14 is inserted into the drive gear 25 and spline-coupled,
The drive gear 25 and the input shaft 14 can rotate integrally. The drive of the input shaft 14 and the rotation of the driven gears 25 and 26 drive the oil pump 24 to supply oil from an oil pan (not shown) to a hydraulic control circuit (not shown) in the transmission. It is supposed to be.

The drive plate 27 has a substantially disk shape, and the center portion thereof is fixed to the base end surface of the crankshaft 12 by a plurality of bolts 31 so that the drive plate 27 can rotate integrally with the crankshaft 12. . Further, a fixing portion 28 which is entirely annular is attached to one side of the outer peripheral side of the drive plate 27 by a bolt 32. The outer peripheral portions of the cover 29 and the connecting member 30 are fixed to the fixing portion 28 by welding. The cover 29 has a substantially disk shape as a whole, and a pair of retainer plates 33 and 34 as a rotating member are attached to one side thereof.

FIG. 3 is an exploded view of the cover 29, the two retainer plates 33 and 34, and the drive plate 16. As shown in the figure, both of the retainer plates 33 and 34 are formed in a dish shape, and through holes 35 and 36 are formed in a central portion thereof. Further, mounting flanges 3 are provided on the outer peripheral portions of both retainer plates 33 and 34.
3a and 34a are formed, and the respective mounting flanges 33a and 34a are fixed to the cover 29 by a plurality of rivets 37 as shown in FIG. Further, the drive plate 16 described above is interposed between the retainer plates 33 and 34.

The drive plate 16 is provided with rectangular spring holders 38 at 90 ° intervals in the circumferential direction.
Inside 8, a coil spring 39 that can expand and contract in the longitudinal direction of the holding portion 38 is provided as an elastic member. The retainer plates 33 and 34 have rectangular holes 43 and 42 at positions corresponding to the spring holding portions 38.
Are formed, respectively. FIG. 4 shows one of the convex portions 41, and FIG. 5 shows a cross section taken along line AA of FIG.

As shown in FIG. 4 and FIG.
0, 41 cover a part of the outer peripheral portion of the coil spring 39, and the spring 39
8 so as not to be detached. Further, both ends of the coil spring 39 are in contact with both side portions 40a, 41a of the convex portions 40, 41, respectively. The rotational driving force of the crankshaft 12 is controlled by the two retainer plates 3.
3, and 34 are transmitted to the drive plate 16 via the coil spring 39.

As described above, the two retainer plates 3
3, 34 and the drive plate 16 are coil springs 39.
, And a slight relative rotation is allowed between the two. That is, FIG.
As shown in FIG. 6A or 6B, when the coil spring 39 is elastically deformed, the two retainer plates 33 and 34 and the drive plate 16 move according to the deformation amounts K ₁ and K ₂ of the coil spring 39. Relative rotation is possible.

As will be described later, the stator 50 including the stator core 58 and the stator coil 59 is formed so as to be entirely annular.
6 and the positions where the spring holding portions 38 and the convex portions 40 and 41 are formed,
As shown in FIG. 2, it is on the inner peripheral side of the stator coil 59. Then, the spring holding portion 38 and the convex portion 4
A part of the coil spring 39 disposed in the insides 0 and 41 is disposed on the inner side with respect to the distal end face of the stator coil 59.

In this embodiment, the cover 2 described above is used.
9. Both retainer plates 33 and 34, drive plate 1
6, a coil spring 39, etc., constitute a damper 45 as fluctuation absorbing means.
The fluctuation of the rotational driving force in the above is absorbed by the damper 45.

Next, the motor generator 46 provided in the power transmission mechanism 11 in the present embodiment will be described. The motor generator 46 has both a function as a motor and a function as a generator. Hereinafter, the configuration will be described in detail.

The motor generator 46 is connected to the connecting member 30, and rotates integrally with the crankshaft 12.
9 (rotor) and a stator 50 (stator) disposed so as to cover the outer peripheral portion of the rotor 49.

The connecting member 30 of the drive plate 27 has a deep dish shape as a whole, and a mounting hole 47 is formed in a central portion thereof. A substantially cylindrical rotor support portion 48 is inserted into the mounting hole 47, and a locking portion 48 a formed at an end of the support portion 48 is welded to a side portion of the connecting member 30.

The rotor 49 includes a rotor core 51 formed in an annular shape and a rotor coil 5 wound around the core 51.
And 2. The rotor core 51 is for guiding magnetic flux to the rotor coil 52, and is formed of a material having a high magnetic permeability (for example, a silicon steel plate). The rotor 49 is rotatable integrally with the drive plate 27 when the rotor core 51 is shrink-fitted and fixed at the outer peripheral portion of the rotor support portion 48.
Further, inside the rotor support portion 48, a portion on the distal end side of the pump housing 17 is disposed so as to extend. Then, a cylindrical pipe member 53 is press-fitted and externally fitted to the extended portion. The pipe member 53 is formed of an iron material whose wear resistance has been improved by heat treatment. Two roller bearings 54 and 55 constituting a bearing are arranged between the outer peripheral portion of the pipe member 53 and the inner peripheral portion of the rotor support portion 48.

As shown in FIG. 7, each of the roller bearings 54, 55 has an annular bearing case 54a, 55.
a, and a plurality of rectangular holes 54b, 55b
Are formed at predetermined intervals in the circumferential direction. And
Rollers 54c and 55c are rotatably arranged in the rectangular holes 54b and 55b.

As shown in FIG. 8, the rotor support 48
A portion of the inner peripheral wall of the bearing case 54a is formed with an enlarged diameter.
An annular member 56 disposed between the two cases 54a and 55a is fitted therein. The two bearing cases 54a, 55a and the annular member 56 are connected to the snap ring 5 attached to the inner peripheral portion of the rotor support 48.
7 restricts the movement of the support portion 48 in the longitudinal direction.

As described above, when the roller bearings 54 and 55 are attached to the rotor support portion 48, the outer peripheral portions of the rollers 54c and 55c provided on the roller bearings 54 and 55 become the outer peripheral portions of the pipe material 53. Abutted on the part.
As a result, the rotor 49 is rotatably supported by the roller housings 54 and 55 with respect to the pump housing 17.

On the other hand, the stator 50 includes a stator core 58 formed in an annular shape, and a stator coil 59 wound around the core 58. Stator core 5
Numeral 8 is made of a material having high magnetic permeability similarly to the rotor core 51. The stator coil 59 is connected to a capacitor (not shown) via an inverter (not shown), and is also connected to a battery (not shown).

The outer peripheral portion of the stator core 58 is shrink-fitted and fixed to a stator support 60 as a fixing member. Further, a motor housing 61 also serving as a fixing member is fixed to the stator support portion 60 in a state where it is positioned by a knock pin (not shown). The motor housing 61 is fixed to the transmission housing 15 by a plurality of bolts 62 while being positioned by knock pins (not shown). Therefore, the stator 50 includes the stator support 60 and the motor housing 61.
To the housing 15 of the transmission.

As described above, when the stator 50 is fixed to the housing 15 of the transmission, an annular gap G is formed between the inner peripheral wall surface of the stator core 58 and the outer peripheral wall surface of the rotor core 51. The magnetic flux generated in the rotor core 51 and the stator core 58 via G can pass through.

In the present embodiment, in addition to the above configuration, an annular space formed between the outer peripheral wall surface of the input shaft 14 and the inner peripheral wall surface of the insertion hole 18 serves as the oil supply passage 63.
The oil supply passage 63 is connected to a discharge port 68 of the oil pump 24 by an oil passage through a hydraulic control circuit (not shown). Lubricating oil as a viscous fluid in the oil pump 24 is supplied through the oil supply passage 63 to the oil supply passage 63. Rotor support 48, connecting member 3
The internal space 64 of the damper 45 (hereinafter, simply referred to as an internal space 64) surrounded by the fixing member 28, the fixing portion 28, and the cover 29.

The roller bearings 54, 55
An annular space formed between the inner peripheral wall surface of the annular member 56 and the outer peripheral wall surface of the pipe member 53 is an oil discharge passage 65. The base end side of the oil discharge path 65 is
It is closed by an oil seal 66 arranged between the pump housing 17 and the pump housing 17. Further, an oil passage 67 is formed inside the pump housing 17 for communicating a base end portion of the oil discharge passage 65 with an oil pan (not shown) of the transmission. When the lubricating oil supplied to the internal space 64 becomes excessive, the lubricating oil is discharged to the oil pan side via the oil discharge passage 65 and the oil passage 67. At this time, the lubricating oil is discharged to the oil pan side after passing between the rollers 54c and 55c of the roller bearings 54 and 55 disposed in the oil discharge path 65.

Next, the operation of the power transmission mechanism 11 according to the present embodiment configured as described above will be described.
First, when starting operation of the engine, the stator coil 5
9 is energized, and the coil 59 has a rotor coil 52
A rotating magnetic field having a phase advanced with respect to the rotation is generated.
Then, a rotational force is applied to the rotor core 51 by the rotating magnetic field, and the engine is started by rotating the drive plate 27 and the crankshaft 12 connected to the rotor 49 via the connecting member 30 and the like by the rotational force. Can be. The rotational force generated in the rotor 49 is used not only at the time of starting the engine, but also as an auxiliary power when the engine is operated at a high output.

Next, when the engine is started, the rotational driving force of the crankshaft 12 is changed to the drive plate 27,
The power is transmitted to the input shaft 14 of the transmission via the cover 29, the retainer plates 33 and 34, the coil spring 39, and the drive plate 16. At this time, the energization of the stator coil 59 is controlled, and the coil 59 generates a rotating magnetic field having a phase delayed with respect to the rotation of the rotor coil 52 and generates an induced electromotive force accompanying the rotation of the rotor 49. Then, the induced electromotive force charges a capacitor (neither is shown) via an inverter. When the stator coil 59 is energized in this way and the rotor 49 is rotated in a state where an induced electromotive force is generated in the coil 59, the rotation of the input shaft 1
4 consumes more rotational energy, and can assist in braking the vehicle.

As described above, according to the power transmission mechanism 11 of the present embodiment, the motor generator 46 provided in the mechanism 11 functions as a motor and a generator, so that the engine can be started and a high output can be obtained. And vehicle braking assistance.

In this embodiment, the rotor support 48 to which the rotor core 51 is fixed is attached to the rotor support 4.
Since the rotor 49 is rotatably supported by roller bearings 54 and 55 disposed between the pump housing 17 and the pump housing 17, movement of the rotor 49 in the radial direction of the crankshaft 12 is restricted. Further, since both the rotor 49 and the stator 50 of the motor generator 46 are fixed or supported on the transmission side,
Nos. 9 and 50 are hardly affected by vibration generated during operation of the engine.

Further, although the rotational driving force of the crankshaft 12 constantly fluctuates, in the present embodiment, the fluctuation of the rotational driving force is absorbed by the damper 45 and is suppressed from being transmitted to the transmission. ing. That is,
The fluctuation of the rotational driving force is absorbed by the elastic deformation of the coil spring 39 of the damper 45 and the shearing of the lubricating oil in the internal space 64 of the damper 45 between the retainer plates 33 and 34 and the driving plate 16. ,
Attenuated. Therefore, the vibration caused by the fluctuation of the rotational driving force is suppressed from being generated on the transmission side.

While the configuration and operation of the present embodiment have been described above, the present embodiment has the following effects (a) to (d). (A) Since the rotor core 51 is rotatably supported by the roller bearings 54 and 55 with respect to the pump housing 17, the movement of the rotor 49 in the radial direction of the crankshaft 12 is reliably restricted. The gap G formed between them can be prevented from changing. Therefore, the gap G can be set smaller than designed, and the magnetic flux density in the gap G can be increased. As a result, the motor generator 46 of the power transmission mechanism 11 can generate a larger rotational force and generate a larger induced electromotive force to perform efficient charging.

(B) In the present embodiment, the motor generator 46
Both the rotor 49 and the stator 50 are fixed or supported on the transmission side. During the operation of the engine, the transmission side has less vibration due to the operation than the engine side. Therefore, the rotor 49 and the stator 50 have less vibration, and the fluctuation of the air gap G can be further suppressed.

(C) The crankshaft 12 and the input shaft 14
Are connected via the damper 45, so that the fluctuation of the rotational driving force in the crankshaft 12 is absorbed and attenuated by the damper 45. Therefore, in the transmission, it is possible to suppress the occurrence of vibration due to the fluctuation of the rotational driving force, and it is possible to suppress the vibration in the rotor 49 and the stator 50. Further, since the damper 45 provided in the power transmission mechanism 11 is a so-called wet damper in which lubricating oil is sealed in the internal space 64, the fluctuation of the rotational driving force can be more effectively absorbed and attenuated. .

(D) In the damper 45 of the present embodiment, a part of the coil spring 39 constituting the damper 45 is located on the inner peripheral side of the stator 50 and on the inner side of the stator 50 from the end face on the tip side. It was arranged to be located. Accordingly, it is possible to suppress an increase in the size of the power transmission mechanism 11 due to the provision of the damper 45, particularly, an increase in the size of the crankshaft 12 in the axial direction.

It should be noted that the present embodiment can be implemented by changing the configuration as described below. (1) In the above embodiment, the roller bearings 54, 55 are provided between the rotor support 48 and the pump housing 17, and the rotor 49
Although the movement in the radial direction of the crankshaft 12 is restricted in this case, this configuration is changed as follows. That is,
The distal end portion of the pump housing 17 is formed in a conical shape, and the outer peripheral wall surface is formed into a tapered surface.
Is formed in a tapered surface parallel to the tapered surface. A roller bearing is arranged between the two tapered surfaces, and the rotor support 48 is rotatably supported by the pump housing 17. Even with the configuration described above, the movement of the rotor 49 in the radial direction of the crankshaft 12 can be restricted, and the fluctuation of the gap G between the rotor 49 and the stator 50 can be suppressed.

(2) In the above embodiment, the damper 45
Although the coil spring 39 is used as the elastic member, the same function and effect can be obtained even if the elastic member is constituted by, for example, a plate spring, rubber, or the like. Further, the number of coil springs 39 provided on the damper 45 is also 4
Without being limited to this, the number may be appropriately increased or decreased according to the magnitude of the elastic coefficient of the spring 39.

In the description of this specification, "fixing member"
The “support member” may be provided separately from the main body of the transmission, or may be provided integrally with the transmission. Also, the shape of the “fixing member” can be any shape as long as the stator of the motor generator can be substantially fixed, and the “supporting member” can be provided with a bearing between the rotor of the motor generator. Is fine.

[0059]

As described above, according to the first aspect of the present invention, it is possible to suppress the fluctuation of the gap formed between the stator and the rotor. Therefore, the air gap can be set smaller, and the torque of the motor generator of the power transmission mechanism can be increased and the power generation function can be improved.

In particular, according to the second aspect of the present invention, in addition to the above effects, the movement of the rotor in the radial direction of the output shaft is more reliably restricted, and the fluctuation of the air gap can be further suppressed.

According to the third and fifth aspects of the present invention, in addition to the effects of the first and second aspects of the present invention, it is possible to suppress the vibration of the stator and the rotor caused by the fluctuation of the rotational driving force. It is possible to further suppress the fluctuation of the gap formed between them. In particular, according to the fifth aspect of the invention, the fluctuation of the rotational driving force can be effectively absorbed by the elastic deformation of the elastic member and the shear deformation of the viscous fluid.

According to the fourth aspect of the present invention, in addition to the effect of the third aspect of the present invention, it is possible to suppress an increase in the size of the power transmission mechanism due to the provision of the fluctuation absorbing means in the power transmission mechanism. .

[Brief description of the drawings]

FIG. 1 is a sectional view of a power transmission mechanism according to an embodiment.

FIG. 2 is an enlarged sectional view of a main part of the power transmission mechanism according to the embodiment.

FIG. 3 is an exemplary exploded perspective view showing a cover, a retainer plate, and a drive plate according to the embodiment;

FIG. 4 is an enlarged view of a main part of a damper according to one embodiment.

FIG. 5 is a sectional view taken along line AA of FIG. 4;

FIGS. 6A and 6B show A of FIG. 4 in the case where the retainer plate and the drive plate are relatively rotated.
-A sectional drawing.

FIG. 7 is a perspective view showing a roller bearing according to one embodiment.

FIG. 8 is an enlarged sectional view showing a state in which a roller bearing is mounted on a rotor support in one embodiment.

FIG. 9 is a cross-sectional view showing a start-up charging device according to the related art.

[Explanation of symbols]

11: power transmission mechanism, 12: crankshaft (output shaft), 1
4 input shaft, 15 housing (transmission), 16 drive plate (rotating member), 17 pump housing (supporting member), 33, 34 retainer plate (rotating member), 39 coil spring (elastic member), 45: damper (fluctuation absorbing means), 46: motor generator, 49: rotor, 50: stator, 54, 55: roller bearing (bearing part), G: air gap.

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F02N 11/04

Claims (5)

(57) [Claims] 1. A stator arranged so as to have a gap through which a magnetic flux can pass between a rotor integrally rotatably connected to an output shaft of an internal combustion engine and an outer peripheral portion of the rotor. A power transmission mechanism for an internal combustion engine that transmits a rotational driving force output from the output shaft to an input shaft of a transmission via a motor generator having: a stator provided on a main body of the transmission. A bearing is disposed between the rotor and a support member provided on the main body of the transmission, while the rotor is rotatably supported by the bearing and the output shaft is fixed. A power transmission mechanism for an internal combustion engine, wherein a movement of a rotor in a radial direction of the engine is restricted. 2. The support member extends in the axial direction of the output shaft and is disposed inside the rotor, and the bearing is disposed between an outer peripheral wall surface of the member and an inner peripheral wall surface of the rotor. The power transmission mechanism for an internal combustion engine according to claim 1, wherein: 3. The power for an internal combustion engine according to claim 1, wherein the output shaft and the input shaft are drivingly connected to each other through a fluctuation absorbing unit that absorbs the fluctuation of the rotational driving force. Transmission mechanism. 4. A method according to claim 1, wherein at least a part of said fluctuation absorbing means is
4. The power transmission mechanism for an internal combustion engine according to claim 3, wherein the power transmission mechanism is disposed on an inner peripheral side of the stator and on an inner side than both end faces of the stator in an axial direction of the output shaft. 5. The fluctuation absorbing unit includes: a pair of rotating members provided so as to face each other on a base end side of the output shaft and a distal end side of the input shaft; an elastic member connecting the two rotating members; 4. A power transmission mechanism for an internal combustion engine according to claim 3, comprising a viscous fluid sealed between the two rotating members.