JPS61233242A - Motive-power transmitting apparatus for car - Google Patents

Abstract

PURPOSE:To sufficiently support the clutch release load in the state where a flywheel is elastically supported and partially support the flywheel, clutch cover assembly and a clutch disc by a clutch housing. CONSTITUTION:A flywheel 12 is connected to a crankshaft 10 through the elastic torque transmitting mechanisms 50 and 52, and the spherical projection 11a of the flywheel 12 is supported. The minute gap in the degree permitting the close adhesion by the release load of a clutch is formed between the flywheel 12 and the elastic torque transmitting mechanism 50. Further, the inner peripheral part of a clutch cover 22 fixed onto the flywheel 12 is supported onto a fixed cylinder shaft 24 contiguous to a clutch housing. An opened port for projecting the fulcrum rand part 19a of a pressure plate 18 for pressing a clutch disc 16 onto the flywheel 12 is formed onto the clutch cover 22, and a diaphragm spring 20 is installed outside the clutch cover 22.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a power transmission device for an automobile comprising an assembly of a flywheel and a clutch in which the flywheel is supported in a flexible state relative to a crankshaft.

(Prior art and its problems) Conventionally, the crankshaft and flywheel are elastically connected by an elastic plate, and the difference between the frequency of the bending of the crankshaft transmitted to the flywheel and the natural frequency of the flywheel is known. A prior art technique has been developed in which resonance is prevented by generating a difference between the two (Japanese Patent Publication No. 57-58542).

However, in the prior art, the axial load of the flywheel is supported by a pilot bearing or a spherical bearing, so there is a problem in durability due to the pilot bearing or spherical bearing bearing the release load when the clutch is engaged. .

Another problem is that the mass of the elastically supported flywheel and the clutch cover assembly and clutch disk fixed to the flywheel must be entirely borne by an elastic plate with low bending rigidity.

(Object of the Invention) The present invention provides for a flywheel to be elastically supported.
It is an object of the present invention to provide a clutch that can sufficiently support the release load when the clutch is engaged and engaged, and can also support part of the mass of the flywheel, clutch cover assembly, and clutch disc on the clutch housing side.

(Structure of the Invention) (1) Technical Means The present invention provides a flywheel engine that uses an elastic torque transmission mechanism that has small axial bending rigidity and elastically transmits torque from the crankshaft to the rear end of the crankshaft of the engine. The flywheel is provided with a spherical support part that connects the wheel to the crankshaft and supports the inner circumferential part of the flywheel so that it can slide freely in the axial direction and freely swing. A small gap is provided between the clutch cover fixed to the flywheel and the fulcrum land part of the pressure plate that presses the clutch disc against the flywheel outward. In addition to providing an opening for protruding, a support portion is provided to support the inner peripheral portion of the clutch cover on a fixed cylindrical shaft that is continuous with the clutch housing.
The power transmission device for an automobile is characterized in that a diaphragm spring is provided outside the clutch cover.

(2) Operation A small gap provided between the elastic torque transmission mechanism and the flywheel blocks vibrations from the crankshaft, and when the clutch is engaged, the elastic body is deformed by the clutch release load to eliminate the small gap. The flywheel is moved to support the release load at the rear end of the crankshaft.

In addition, the flywheel, the clutch cover assembly, and a part of the clutch disc Ftffi are supported by the fixed cylindrical shaft of the housing at the supporting portion of the clutch cover.

Furthermore, the 7 fulcrum land part of the pressure plate,
The spring force of the diaphragm spring, which protrudes from the flywheel opening and is installed outside the clutch cover, is transmitted to the pressure plate.

(Example) In FIG. 1 showing a clutch to which the present invention is applied, 10
is a crankshaft, and a flywheel 12 is elastically connected to the rear end of the crankshaft 10 by a spherical protrusion 11a, which will be described in detail later. A first flexible plate 50 and a second flexible plate 52 (elastic torque transmission mechanism) are interposed between the front surface of the flywheel 12, that is, the surface facing the engine body, and the crankshaft 10.

Both flexible plates 50 and 52 are members that absorb only bending vibrations from the crankshaft 10.

A clutch disc 16 is located on the rear side of the flywheel 12.
The clutch disc 16 is slidably spline-fitted to the input shaft 15a of the rear-stage transmission. Further, the front end of the input shaft 15a is pivotally supported at the center of the rear end of the crankshaft 10 by a bearing 15b.

A pressure plate 18 is provided to press the facing 17a of the clutch disc 16 toward the flywheel 12.
is pressed by a diaphragm spring 20. The diaphragm spring 20 is disposed outside the clutch cover 22, and is connected to the wire ring 21a1 stud bin 2.
1b, and is supported by a clutch cover 22, which covers the facing 17a1, pressure plate 18, etc., and is fixed to the rear surface of the flywheel 12.

A release bearing 26 is fitted between the inner peripheral part of the diaphragm spring 20 and the fixed cylinder shaft 24 so as to be slidable in the direction of the ° axis, and the release force from the clutch pedal is transmitted to the diaphragm spring 20 by the release bearing 26. It is structured to do this. The fixed cylinder shaft 24 is fixed to a clutch housing (not shown) of the transmission.

Flywheel 12, both flexible plates 50.5
The detailed structure of No. 2 will be explained. The first flexible plate 50 has a substantially disk shape with a relatively thick wall and high bending rigidity, and a radially inner peripheral portion of the first flexible plate 50 is fixed to the crankshaft 10 with bolts 15c. Second
The flexible plate 52 is thinner than the first flexible plate 50 and has a substantially disk shape with lower bending rigidity, and faces the first flexible plate 50.

The bolts 15c are provided at a plurality of locations in the circumferential direction at equal inner corners, and the bolts 15c are accommodated in the holes 15d of the flywheel 12. First flexible plate 5
A ring gear 15e is fixed to the radially outer circumferential surface of the ring gear 15e.

Further, the outer peripheral portion of the first flexible plate 50 is provided with bolts 5.
4 and is collinear with the second flexible plate 52. The bolt 54 has a large diameter sliding ring portion 5 as shown in FIG.
5b is formed, and the sliding shaft portion 55b is the sliding shaft portion 55.
It fits into the hole 11b of the flywheel 12, which has a larger diameter than the hole 11b, while allowing sliding in the axial direction.

The inner peripheral part of the second flexible plate 52 is provided with bolts 53a.
and is fixed to the flywheel 12.

In addition, the flywheel 12 and the first flexible plate 5
A minute gap C of, for example, about 0.2ttttt is provided between 0 and 0.

Therefore, the torque from the crankshaft 10 is transmitted from the bolt 54 to the flywheel 12 via the first flexible plate 50, and the flywheel 12
A is slidably supported in the axial direction. Further, the crankshaft 10 is able to freely vibrate within a minute gap C while being insulated from the flywheel 12 around the spherical support portion 11a.

The detailed structures of the diaphragm spring 20 and the clutch cover 22 will be explained. First, the 7 fulcrum land portion 19a of the pressure plate 18 in the clutch cover 22
In the position corresponding to An opening 23a is formed that allows the lumen land portion 19a to protrude rearward. opening 23
a exists at several locations on the same circumference over the entire circumference of the clutch cover 22. A substantially cylindrical cylindrical boss portion 23b (supporting portion) that protrudes rearward is formed on the inner peripheral portion of the clutch cover 22, and the cylindrical boss portion 23b and the fixed cylindrical shaft 2
A bearing 23C is interposed between 4 and 4. Note 2
3d is a window hole.

As described above, the diaphragm spring 20 is supported behind the clutch cover 22, and the inner peripheral portion of the diaphragm spring 20 is in contact with the release bearing 26. Furthermore, when the clutch is released as shown by the two-dot chain line in FIG. 1, there is a distance D between the rear end surface of the clutch cover 22 and the diaphragm spring 20, so that they do not interfere with each other when the clutch is released.

Next, the effect will be explained. When the crankshaft 10 rotates, torque is transmitted to the flywheel 12 via the first flexible plate 50. The bending vibration of the crankshaft 10 is the second
It is absorbed by the flexible plate 52 and the crankshaft 10
The bending vibrations from the crankshaft 10 are not transmitted to the flywheel 12, and the vibrations of the crankshaft 10 centered on the spherical support portion 11a are insulated by the minute gap 11c.

The first flexible plate 50 is thicker than the second flexible plate 52, and the torque from the crankshaft 10 is transmitted through the first flexible plate 50, which has relatively high rigidity, from the sliding shaft portion 55b of the bolt 54 to the flywheel 1.
2. Further, the bending vibration of the crankshaft 10 is absorbed within the minute gap C by the 27th palm pull plate 52, which has relatively low bending rigidity.

At the time of clutch release in which the clutch disc 16 is disconnected from the pressure plate 18, the flywheel 12 is moved forward by a minute gap C by the pressing force of the release bearing 26, and the flywheel 12 and the flexible plate 14 are brought into close contact.

In this state, the pressing force of the release bearing 26 is received by the crankshaft 10, so no load is applied to the spherical protrusion 11a, resulting in excellent durability and strength.

Part of the mass of the flywheel 12, clutch cover assembly 25, and clutch disc 16 is supported by the fixed cylindrical shaft 24 on the clutch housing side from the cylindrical boss portion 23b via the bearing 23C, and the vibration prevention effect of the flywheel 12 is Improve further.

Also, the diaphragm spring 20 is connected to the clutch cover 22.
Since the clutch cover 22 is disposed outside of the clutch cover 22, the clutch cover 22 is made smaller and lighter. Therefore, the mass of the rotating parts of the clutch is reduced.

Furthermore, the diaphragm spring 20 is connected to the clutch cover 22.
Since it is located outside of the diaphragm spring 2
0 is cooled by relatively low temperature air outside the clutch cover 22, and the diaphragm spring 20 does not overheat.

(Effects of the Invention) As explained above, the automotive power transmission device of the present invention has a small axial bending rigidity at the rear end of the crankshaft of the engine, and has an elastic torque that elastically transmits torque from the crankshaft. The flywheel is connected to the crankshaft via a transmission mechanism, and the flywheel is provided with a spherical support portion that supports the inner circumferential portion of the flywheel so that it can slide freely in the axial direction and freely swing. A small gap is provided between the target torque transmission mechanism and the clutch cover fixed to the flywheel, and a pressure plate 7 is provided to press the clutch disc against the flywheel. In addition to providing an opening that allows the Lucrum land portion to protrude outward,
Since a support portion is provided to support the inner peripheral portion of the clutch cover on a fixed cylindrical shaft continuous to the clutch housing, and a diaphragm spring is provided outside the clutch cover, the following effects are achieved.

The vibration of the crankshaft 10 is caused by the second flexible plate 52
The vibrations from the crankshaft 10 are not transmitted to the flywheel 12, and the vibrations of the crankshaft 10 centered on the spherical support portion 11a can be insulated by the minute gap 11C.

At the time of clutch release, in which the clutch disc 16 is disconnected from the pressure plate 18, the flywheel 12 moves forward by a minute gap C due to the pressing force of the release bearing 26, and the flywheel 12 and the first flexible plate 50 come into close contact, and the release bearing Since the pressing force of 26 is received by the crankshaft 10, the spherical protrusion 1
No load is applied to 1a, resulting in excellent durability and strength.

Part of the mass of the flywheel 12, clutch cover assembly 25, and clutch disc 16 is supported by the fixed cylindrical shaft 24 on the clutch housing side via the cylindrical boss portion 23b and bearing 23c.
The vibration prevention effect of the flywheel 12 can be further improved.

Furthermore, the diaphragm spring 20 is attached to the clutch cover 2.
2, the clutch cover 22 can be made smaller and the weight of the clutch cover 22 can be reduced. This allows the mass of the rotating parts of the clutch to be reduced.

Furthermore, the diaphragm spring 20 is connected to the clutch cover 22.
Since it is located outside of the diaphragm spring 2
0 is cooled by relatively low-temperature air outside the clutch cover 22, which can prevent the diaphragm spring 20 from overheating and maintain the spring characteristics of the diaphragm spring 20 constant over a long period of time.

(Another Embodiment) (1) With reference to FIG. 3, a second embodiment of an elastic torque transmission mechanism that damps only bending vibrations from the crankshaft 10 will be described. The elastic torque transmission mechanism in this case includes a retaining ring 56, a spacer 58, and a first cone spring 6.
0a, a second cone spring 60b, etc., and a small gap C is provided between the retaining ring 56 and the flywheel 12.

The retaining ring 56 is attached to the bolt 59a via the spacer 58.
is fixed to the crank@10, and the flywheel 1
2 is connected to the crankshaft 10 via a spacer 58 in a slidable manner within a minute gap C.

A first cone spring 60a is interposed between the retaining ring 56 and the flywheel 12, and a second cone spring 60a is interposed between the flywheel 12 and the spacer 58.
0b is interposed.

In this second embodiment, torque from the crankshaft 10 is transmitted to the flywheel 12 via the spacer 58. The first cone spring 60a and the second cone spring 60
Since the small gap C is separated by the balance of the spring force of b, vibrations from the crankshaft 10 are absorbed by both springs within the range of the small gap @C.

Further, as shown in FIG. 3a, a wave spring 60C may be interposed between the retaining ring 56 and the flywheel 12.

(2) With reference to FIG. 4, a third embodiment of an elastic torque transmission mechanism that damps only bending vibrations from the crankshaft 10 will be described. The elastic torque transmission mechanism in this case consists of a retaining ring 62, a spacer 58, a rubber ring 64a, a rubber bush 64b, etc., and a small gap C is provided between the retaining ring 62 and the flywheel 12.

An annular rubber ring 64a is interposed between the retaining ring 62 and the flywheel 12, and the flywheel 12
A rubber bush 64b is interposed between the spacer 58 and the spacer 58.

In this third embodiment, torque from the crankshaft 10 is transmitted to the flywheel 12 via the spacer 58. Vibrations from the crankshaft 10 are absorbed within the minute gap C by the elasticity of the rubber ring 64a1 and the rubber bush 64b.

(3) With reference to FIG. 5, a fourth embodiment of the elastic torque transmission mechanism 1 that damps only the bending vibration from the crankshaft 10 will be described. Elastic torque transmission 3 in this case! The mechanism consists of an inner ring 66, an outer ring 68, and a rubber ring 64a, and a small gap C is provided between the inner ring 66 and the flywheel 12.

As shown in Fig. M5a, the inner circumferential ring 66 and the outer circumferential ring 68 engage the chevron-shaped protrusions 67a and 69a with each other to allow the flywheel 12 to slide within a minute gap C, and the crankshaft 10 Torque from is transmitted to the flywheel 12. A rubber ring 64a is interposed between the inner ring 66 and the outer ring 68.

In this fourth embodiment, torque from the crankshaft 10 is transmitted to the flywheel 12 through an inner ring 66 and an outer ring 68. Vibrations of the crankshaft 10 are absorbed within the small gap C by the elastic force of the rubber ring 64a.

(4) With reference to FIG. 6, a fifth embodiment of an elastic torque transmission mechanism that damps both bending vibration and torsional vibration from the crankshaft 10 will be described. The elastic torque transmission mechanism in this case consists of a spacer 58, a rubber bush 70, a holding plate 72, etc., a minute gap C is provided between the crankshaft 10 and the flywheel 12, and a spacer 58 is provided between the crankshaft 10 and the flywheel 12.
Similarly, there is a small gap tIiIC between 8 and the holding plate 72.
are separated.

An annular rubber bush 70 is fixed to the outer peripheral surface of the spacer 58 by baking, and the flywheel 12 is elastically supported by the spacer 58.

As shown in FIG. 6a, an annular holding plate 72 is interposed between the spacer 58 and the flywheel 12, and a bolt 73a for connecting the holding plate 72 to the flywheel 12 is provided between the bolts 59a. ing.

In this fifth embodiment, the torque from the crankshaft 10 is transmitted to the flywheel 12 via the spacer 58 and the rubber bushing 70, and the torsional movement of the crankshaft 10 is absorbed by the elasticity of the rubber bushing 70. Also, crankshaft 1
Bending swing from 0! F7J is a minute gap C between the crankshaft 10 and the flywheel 12 and the flywheel 12
It is absorbed by the elasticity of the rubber bushing 70 in the range of the minute gap IJc between the holding plate 72 and the holding plate 72.

(5) With reference to FIG. 7, a sixth embodiment of an elastic torque transmission mechanism that damps both bending vibration and torsional vibration from the crankshaft 10 will be described. The elastic torque transmission mechanism in this case consists of an inner ring 74, an outer ring 76, a rubber ball 78, etc., and a small gap C is provided between the inner ring 74 and the flywheel 12.

As shown in FIG. 7a, the inner ring 74 and the outer ring 76 are provided with protrusions 75a, 7 at equal intervals in the circumferential direction.
A spherical rubber ball 78 compressed into a block shape is interposed between the protrusion 75a and the protrusion 77a.

In this sixth embodiment, the torque from the crankshaft 10 is transmitted through the rubber balls 78 to the inner ring 74 and the outer ring 76.
The torsional vibration of the crankshaft 10 is absorbed by the elasticity of the rubber ball 78.

In addition, the bending vibration from the crankshaft 10 is transmitted to the inner ring 74.
It is absorbed by the elasticity of the rubber ball 78 in the range of the minute gap C between the flywheel 12 and the flywheel 12.

[Brief explanation of drawings]

Fig. 1 is a vertical cross-sectional view showing a first embodiment of a clutch to which the present invention is applied, Fig. 2 is a partial vertical cross-sectional view showing the detailed structure of the first embodiment, and Fig. 3 is a second embodiment of the present invention. FIG. 3a is a partial vertical cross-sectional view showing a modification of the second embodiment, FIG. 4 is a partial vertical cross-sectional view showing a third embodiment of the present invention, and FIG. 5 is a partial vertical cross-sectional view showing a modification of the second embodiment. FIG. 5a is a vertical cross-sectional partial view showing the fourth embodiment of
The figures are a view taken in the direction of the X arrow in FIG. 5, FIG.
The figure is a partial vertical cross-sectional view showing a sixth embodiment of the present invention, and FIG. 7a is a cross-sectional view taken along the line AA in FIG. 10... Crankshaft, 12... Flywheel, 16... Clutch disc, 18... Pressure plate, 20... Diaphragm spring, 22... Clutch cover, 2
4... Fixed cylindrical shaft, 25... Clutch cover assembly, 23b... Cylindrical boss portion, 23C... Bearing,
C...Minute gap, 50...First frame 4; Shiple plate, 52...Second flexible plate, 54...
・Bolt patent applicant: Daikin Seisakusho Co., Ltd. Figure 4 Figure 5

Claims (1)

[Claims] The flywheel is connected to the rear end of the engine crankshaft via an elastic torque transmission mechanism that has low axial bending rigidity and elastically transmits torque from the crankshaft. The flywheel is provided with a spherical support part that supports the flywheel so as to be slidable and oscillating in the axial direction, and a small part is provided between the flywheel and the elastic torque transmission mechanism to the extent that it comes into close contact with the release load when the clutch is disengaged. A gap is provided, and the clutch cover fixed to the flywheel is provided with an opening through which the fulcrum land portion of the pressure plate that presses the clutch disc against the flywheel projects outward, and the inner circumference of the clutch cover is attached to the clutch housing. A power transmission device for an automobile, characterized in that a support portion is provided to support a continuous fixed cylindrical shaft, and a diaphragm spring is provided outside the clutch cover.