JPH0243931B2 - JIDOSHAYODORYOKUDENTATSUSOCHI - Google Patents

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 have been elastically connected using an elastic plate, and the difference between the frequency of the bending vibration of the crankshaft transmitted to the flywheel and the natural frequency of the flywheel has been known. A prior art technology has been developed in which resonance is prevented by generating (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 disengaged. .

Another problem is that the mass of the elastically supported flywheel, the clutch cover assembly and the 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 sufficient support for the release load when the clutch is engaged and engaged while the flywheel is elastically supported, and also reduces a portion of the mass of the flywheel, clutch cover assembly, and clutch disk. The object is to provide a clutch that can be supported on the clutch housing side.

(Structure of the Invention) (1) Technical Means The present invention provides a flywheel system that uses an elastic torque transmission mechanism that has low bending rigidity in the axial direction 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 peripheral part of the flywheel so as to be slidable in the axial direction and swingable, and the flywheel and the elastic torque transmission mechanism are connected to each other. A small gap is created in between to allow close contact due to the release load when the clutch is engaged, and the fulcrum land portion of the pressure plate that presses the clutch disk against the flywheel is removed from the clutch cover fixed to the flywheel. An automobile characterized in that the clutch cover is provided with an opening that protrudes in the opposite direction, a support portion that supports the inner circumferential portion of the clutch cover on a fixed cylindrical shaft that is continuous with the clutch housing, and a diaphragm spring provided on the outside of the clutch cover. It is a power transmission device for use.

(2) Effect: The 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, part of the mass of the flywheel, clutch cover assembly, and clutch disk is supported by the fixed cylindrical shaft of the housing at the support portion of the clutch cover.

Further, the fulcrum land portion of the pressure plate is made to protrude outside from the opening of the flywheel, and the spring force of the diaphragm spring provided 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. ing. 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 of these flexible plates 50, 52
is a member that absorbs only the bending vibration from the crankshaft 10.

A clutch disk 16 is provided on the rear side of the flywheel 12.
6 is slidably spline-fitted to the input shaft 15a of the rear-stage transmission. In addition, the input shaft 15a
The front end of the crankshaft 10 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 disk 16 toward the flywheel 12, and the pressure plate 18 is pressed by a diaphragm spring 20. The diaphragm spring 20 is arranged outside the clutch cover 22,
It is supported by a clutch cover 22 via a wire ring 21a and a stud pin 21b, and the clutch cover 22 covers the facing 17a, 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 axial direction, and the release force from the clutch pedal is transmitted to the diaphragm spring 20 by the release bearing 26. It's structured. The fixed barrel shaft 24 is fixed to a clutch housing (not shown) of the transmission.

The detailed structure of the flywheel 12 and both flexible plates 50 and 52 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. The second 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 positions in the circumferential direction at equal intervals, and the bolts 15c are accommodated in the holes 15d of the flywheel 12. A ring gear 15e is fixed to the outer peripheral surface of the first flexible plate 50 in the radial direction.

Further, the outer peripheral portion of the first flexible plate 50 is fastened together with the second flexible plate 52 with bolts 54. As shown in FIG. 2, the bolt 54 is formed with a large diameter sliding shaft portion 55b, and the sliding shaft portion 55b is axially inserted into the hole 11b of the flywheel 12, which has a larger diameter than the sliding shaft portion 55b. They are fitted with sliding allowed.

The inner peripheral portion of the second flexible plate 52 is fixed to the flywheel 12 with bolts 53a. Further, a small gap c of, for example, about 0.2 mm is provided between the flywheel 12 and the first flexible plate 50.

Therefore, the torque from the crankshaft 10 is the first
It is transmitted from the bolt 54 to the flywheel 12 via the flexible plate 50, and the flywheel 12 is supported slidably in the axial direction by the spherical support portion 11a. In addition, the crankshaft 10 has a small gap c
It is possible to freely vibrate in a state insulated from the flywheel 12 around the spherical support part 11a within a range of .

The detailed structure of the diaphragm spring 20 and clutch cover 22 will be explained. First, an opening 23a is formed in the clutch cover 22 at a position corresponding to the fulcrum land 19a of the pressure plate 18 so that the fulcrum land 19a projects rearward. The openings 23a are present at several locations on the same circumference over the entire circumference of the clutch cover 22. A substantially cylindrical boss portion 23b that protrudes rearward is provided on the inner peripheral portion of the clutch cover 22.
(support part) is formed, and the cylindrical boss part 23b
A bearing 23c is interposed between the fixed cylinder shaft 24 and the fixed cylinder shaft 24. Note that 23d 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 indicated by the two-dot chain line in FIG.
There is a distance D between them, so that they do not interfere with each other during release.

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 caused by the second flexible plate 52.
The bending vibration from the crankshaft 10 is not transmitted to the flywheel 12 and is absorbed by the spherical support portion 11a.
The vibration of the crankshaft 10 centered on the minute gap c
is insulated.

The first flexible plate 50 is thicker than the second flexible plate 52 and the crankshaft 10 is thicker than the second flexible plate 52.
The torque is applied to the sliding shaft portion 5 of the bolt 54 through the first flexible plate 50, which has relatively high rigidity.
5b to the flywheel 12. Further, the bending vibration of the crankshaft 10 is absorbed within the minute gap c by the second flexible 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 1 is moved by the pressing force of the release bearing 26.
2 moves forward by a minute gap c, and the flywheel 12 and flexible plate 14 come into close contact.
In this state, the pressing force of the release bearing 26 is received by the crankshaft 10, so the spherical protrusion 1
No load is applied to 1a, and it has excellent durability and strength.

A portion of the mass of the flywheel 12, clutch cover assembly 25, and clutch disk 16 is transferred from the cylindrical boss portion 23b to the bearing 2.
3c to the fixed cylinder shaft 2 on the clutch housing side.
4, the vibration prevention effect of the flywheel 12 is further improved.

Further, since the diaphragm spring 20 is disposed outside the clutch cover 22, the clutch cover 22 is made smaller and lighter. The mass of the rotating parts of the clutch is therefore reduced.

Furthermore, since the diaphragm spring 20 is located outside the clutch cover 22, the diaphragm spring 20 is cooled by the relatively cool 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 an elastic torque transmission system that has low bending rigidity in the axial direction and elastically transmits torque from the crankshaft to the rear end of the crankshaft of the engine. The flywheel is connected to the crankshaft via a mechanism, and the flywheel is provided with a spherical support portion that supports the inner peripheral portion of the flywheel so that it can slide freely in the axial direction and freely swing. A fulcrum land portion of the pressure plate that presses the clutch disk against the flywheel is provided with a small gap between the torque transmission mechanism and the clutch cover fixed to the flywheel, so that the clutch release load causes close contact. In addition to providing an opening for projecting the clutch cover outward, a supporting portion for supporting the inner peripheral portion of the clutch cover on a fixed cylindrical shaft continuous to the clutch housing was provided, and a diaphragm spring was provided outside the clutch cover. be effective.

The vibrations of the crankshaft 10 are absorbed by the second flexible plate 52, the vibrations from the crankshaft 10 are not transmitted to the flywheel 12, and the spherical support part 1
Vibrations of the crankshaft 10 centered at 1a can be insulated by the minute gap c.

At the time of clutch release, in which the clutch disc 16 is disconnected from the pressure plate 18, the flywheel 1 is moved by the pressing force of the release bearing 26.
2 moves forward by a small gap c, the flywheel 12 and the first flexible plate 50 come into close contact, and the pressing force of the release bearing 26 is received by the crankshaft 10, so no load is applied to the spherical protrusion 11a, improving durability. Excellent strength.

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

Further, since the diaphragm spring 20 is disposed outside the clutch cover 22, the clutch cover 22 can be made smaller and the weight of the clutch cover 22 can be reduced. Therefore, the mass of the rotating parts of the clutch can be reduced.

Furthermore, since the diaphragm spring 20 is disposed outside the clutch cover 22, the diaphragm spring 20 is cooled by the relatively low temperature air outside the clutch cover 22, which prevents the diaphragm spring 20 from overheating. 20 spring characteristics can be maintained 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. In this case, the elastic torque transmission mechanism includes a retaining ring 56, a spacer 5
8, consisting of a first cone spring 60a, a second cone spring 60b, etc., and a retaining ring 56
A small gap c is provided between the flywheel 12 and the flywheel 12.

The retaining ring 56 is fixed to the crankshaft 10 with a bolt 59a via a spacer 58, and the flywheel 12 is connected to the crankshaft 10 via the 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 60b is interposed between the flywheel 12 and the spacer 58.

In this second embodiment, torque from the crankshaft 10 is transmitted to the flywheel 12 via the spacer 58. First cone spring 60a
Since the balance between the spring forces of the second cone spring 60b and the first cone spring 60b separates the second cone spring 60b from the small gap c, vibrations from the crankshaft 10 are absorbed by both springs within the small gap c.

Also shown in FIG. 3a is a retaining ring 56.
A wave spring 60c may be interposed between the flywheel 12 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. In this case, the elastic torque transmission mechanism includes the retaining ring 62 and the spacer 5.
8. Consists of a rubber ring 64a, a rubber bush 64b, etc., and includes a retaining ring 62 and a flywheel 1.
2 is separated by a minute gap c.

An annular rubber ring 64a is interposed between the retaining ring 62 and the flywheel 12.
A rubber bush 64b is interposed between the flywheel 12 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 by the elasticity of the rubber ring 64a and rubber bush 64b within the minute gap c.

(3) With reference to FIG. 5, a fourth embodiment of an elastic torque transmission mechanism that damps only bending vibrations from the crankshaft 10 will be described. In this case, the elastic torque transmission mechanism includes an inner ring 66 and an outer ring 6.
8. Consisting of a rubber ring 64a, the inner ring 6
6 and the flywheel 12 are separated by a minute gap c.

The inner circumferential ring 66 and the outer circumferential ring 68 have a chevron-shaped protrusion 67a and a chevron-shaped protrusion 69, as shown in FIG. 5a.
a are engaged with each other and the flywheel 12 is allowed to slide within a small gap c, and the torque from the crankshaft 10 is applied to the flywheel 1.
2. Inner ring 6
6 and the outer ring 68 is a rubber ring 64a.
is interposed.

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. The vibration of the crankshaft 10 is caused by the rubber ring 6 within the minute gap c.
It is absorbed by the elastic force of 4a.

(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 is the spacer 5
8, a rubber bush 70, a holding plate 72, etc., and a crankshaft 10 and a flywheel 12.
A small gap c is separated between the spacers 5 and 5.
Similarly, a small gap c is provided between the holding plate 8 and the holding plate 72.

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. Spacer 58 and flywheel 12
An annular holding plate 72 is interposed between them as shown in FIG. 6a, and a bolt 73a for connecting the holding plate 72 to the flywheel 12 is provided between the bolts 59a.

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 vibration of the crankshaft 10 is absorbed by the elasticity of the rubber bushing 70. Further, the bending vibration from the crankshaft 10 is caused by the minute gap c between the crankshaft 10 and the flywheel 12 and the flywheel 1.
It is absorbed by the elasticity of the rubber bushing 70 within the minute gap c between the rubber bushing 2 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. In this case, the elastic torque transmission mechanism consists of the inner ring 7
4. It consists of 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.

The inner ring 74 and the outer ring 76 have a seventh a
As shown in the figure, protrusions 75a and 77a are formed at equal intervals in the circumferential direction, and a spherical rubber ball 78 compressed into a block shape is interposed between the protrusions 75a and 77a. ing.

In this sixth embodiment, the torque from the crankshaft 10 is transmitted to the inner ring 7 through the rubber balls 78.
4. The torsional vibration of the crankshaft 10 is transmitted from the outer ring 76 to the flywheel 12 and 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 within the minute gap c between the flywheel 12 and the flywheel 12.

[Brief explanation of drawings]

FIG. 1 is a vertical sectional view showing a first embodiment of a clutch to which the present invention is applied, FIG. 2 is a vertical sectional partial view showing a detailed structural example 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 partial vertical cross-sectional view showing the fourth embodiment of the present invention, FIG. 5a is a view taken in the direction of the x arrow in FIG. 5, FIG. FIG. 7 is a vertical cross-sectional partial view showing a sixth embodiment of the present invention, and FIG. 7a is a cross-sectional view taken along line AA in FIG. 10...crankshaft, 12...flywheel, 1
6... Clutch disk, 18... Pressure plate, 20... Diaphragm spring, 22... Clutch cover, 24... Fixed cylinder shaft, 25... Clutch cover assembly, 23b... Cylindrical boss portion, 2
3c... Bearing, c... Minute gap, 50... First flexible plate, 52... Second flexible plate, 54... Bolt.

Claims (1)

[Claims] 1 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, and The flywheel is provided with a spherical support portion that supports the slider in the axial direction and can swing freely, and a spherical support portion 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 small gap is provided in the clutch cover fixed to the flywheel, and an opening is provided in which the fulcrum land portion of the pressure plate that presses the clutch disk against the flywheel projects outward, and the inner periphery of the clutch cover is What is claimed is: 1. A power transmission device for an automobile, characterized in that a support portion is provided for supporting the clutch cover on a fixed cylindrical shaft continuous with the clutch housing, and a diaphragm spring is provided outside the clutch cover.