JPH08114239A - Clutch disk assembly - Google Patents

Abstract

PURPOSE: To prevent respective members form break-down by making a clutch disk assembly difficult to produce an axial clearance between a cushioning plate and disk-like plate. CONSTITUTION: A clutch disk assembly is provide with a cushioning plate, friction facing, clutch plate 3, stop pin 10, cone spring 12 and hub. The cushioning plate has a cushioning part and a flat fixed part 7c formed on the inner peripheral side of the cushioning part. The clutch plate 3 is disposed on the side of the flat fixed part 7c and the stop pin 10 fixes clutch plate 3 and flat fixed part 7c. The cone spring 12 sets the flat fixed part 7c in pressure contact with the clutch plate 3 near the stop pin 10.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch disc assembly used in automobiles and the like.

[0002]

BACKGROUND OF THE INVENTION A clutch disc assembly is generally located between the flywheel on the engine side and an input shaft extending from the transmission. The clutch disc assembly includes a spline hub connected to the input shaft of the transmission, a disc plate that engages with the spline hub, and a coil spring that elastically connects the disc plate and the spline hub in the circumferential direction. And a clutch connecting portion fixed to the outer periphery of the plate. The clutch connecting portion is mainly composed of a plurality of cushioning plates and an annular friction facing fixed to both side surfaces of the cushioning plates. The cushioning plate has an inner peripheral portion fixed to the outer periphery of the disc-shaped plate by rivets. When the clutch connecting portion is pressed against the side surface of the flywheel, torque is input to the clutch disc assembly.

[0003]

In the above conventional structure,
The cushioning plate is fixed to the disc-shaped plate by rivets, and both plates are pressed against each other in the axial direction by rivet caulking. Therefore, torque is transmitted not only through the rivets but also between the contact surfaces of both plates. However, when the clutch disc assembly is repeatedly operated, a gap may occur between the cushioning plate and the disc-shaped plate in the axial direction. When both plates rattle in the axial direction, torque transmission between the plates is performed only by the body of the rivet, and the portion around the rivet of the cushioning plate is damaged.

An object of the present invention is to prevent the axial gap between the cushioning plate and the disk-shaped plate from occurring, thereby making it difficult to damage each member.

[0005]

A clutch disc assembly according to the present invention comprises a cushioning plate, a friction facing, a disc-shaped plate, a pin, a pressure contact member and a hub. The cushioning plate has a cushioning portion and a flat portion formed on the inner peripheral side of the cushioning portion. The friction facings are fixed on both sides of the cushioning portion. The disk-shaped plate is arranged laterally of the flat portion of the cushioning plate. The pins are
Fix the plate and flat part. The pressing member presses the cushioning plate and the plate in the vicinity of the pin. The hub engages the discoid plate.

The pressure contact member is preferably a cone spring through which the pin penetrates. The cone spring is arranged beside the plate and the flat portion, and the pin is in contact with the body, which penetrates the plate, the flat portion, and the cone spring, the head arranged outside the penetrated member, and the cone spring. It is preferable to have a seat portion which contacts. The cone spring is compressed between the flat portion and the seat portion and preferably has a larger area than the seat portion.

[0007]

In the clutch disc assembly according to the present invention, when torque is input to the friction facing, the torque is transmitted to the disc plate and further output to the hub. The press contact member presses the flat portion and the plate into contact with each other near the pin. Therefore, the inter-plate frictional force is maintained between the flat portion, the disc-shaped plate, and the pin. As a result, the flat portion of the cushioning plate is less likely to be damaged.

When the pressing member is a cone spring, a large pressing force can be obtained in a small area. When each member is sandwiched between the head portion and the seat portion of the pin, the flat portion and the disk-shaped plate are pressed against each other by the cone spring. When the area of the cone spring is larger than the area of the seat portion, rattling between the members is less likely to occur.

[0009]

1 shows a clutch disc assembly 1 as an embodiment of the present invention. The clutch disc assembly 1 is for transmitting torque from a flywheel (not shown) on the engine side (left side in FIG. 1) to a transmission input shaft (not shown) extending from the transmission side (right side in FIG. 1). It is a device. In FIG. 1, O-O is a rotation axis of the clutch disc assembly 1.

The clutch disc assembly 1 is mainly composed of
It is composed of a clutch connecting portion 2, a clutch plate 3, a retaining plate 4, a plurality of coil springs 5 and a spline hub 6. The clutch connecting portion 2 is mainly composed of an integrated cushioning plate 7 and two friction facings 8. As is apparent from FIG. 3, the cushioning plate 7 includes the annular connecting portion 7
a, a plurality of cushioning parts 7b formed on the outer peripheral side of the annular connecting part 7a, and four flat fixing parts 7c formed on the inner peripheral side of the annular connecting part 7a at equal intervals in the circumferential direction. ing. A step is formed in the cushioning portion 7b, and friction facings 8 are fixed on both surfaces thereof. A hole is formed in the flat fixing portion 7c, and the flat fixing portion 7c is fixed to the clutch plate 3 and the retaining plate 4 by the hole (described later).

The clutch plate 3 and the retaining plate 4 are substantially disk-shaped plate members and are arranged with a predetermined gap therebetween in the axial direction. The clutch plate 3 and the retaining plate 4 are fixed to each other by stop pins 10 provided at four locations on the outer circumference. As is apparent from FIG. 2, the stop pin 10 has a first body portion 10a that penetrates the retaining plate 4 and a second body portion 12b that penetrates the clutch plate 3 and has a smaller diameter than the first body portion 10a. are doing. The first head portion 10c is in contact with the outer side surface of the retaining plate 4, and the second head portion 10 is in contact with the outer side surface of the clutch plate 3.
d is in contact. The end surface of the first body portion 10a is the seat surface 10
e. Between the seat surface 10e and the clutch plate 2, the flat fixing portion 7c of the cushioning plate 7 and the cone spring 12 are arranged from the clutch plate 3 side. The cone spring 12 has a flat fixing portion 7
It is compressed between c and the seat surface 10e, so that the outer peripheral portion of the clutch plate 3 and the flat fixing portion 7c are pressed against each other in the axial direction. The cone spring 12
Has an outer diameter larger than the diameter of the seat surface 10e of the stop pin 10.

The clutch plate 3 and the retaining plate 4 are formed with a plurality of supporting portions 3a and 4a, respectively. The support portions 3a and 4a are cut-and-raised portions that are cut and raised in the axial direction, and accommodate and support the coil spring 5. The spline hub 6 is arranged inside the clutch plate 3 and the retaining plate 4. The spline hub 6 is mainly composed of a boss 15 formed at the center and a flange 16 integrally extending from the boss 15 in the outer peripheral direction. A spline hole 15a that engages with an input shaft (not shown) of the transmission is formed at the center of the boss 15. A window hole 16a is formed in the flange 16 at a position corresponding to the support portions 3a and 4a of the plates 3 and 4. The coil spring 5 is arranged in the window hole 16a. The torque from the plates 3 and 4 is transmitted to the flange 16 via the coil spring 5. Further, a notch 16b, through which the first body portion 10a of the stop pin 10 is inserted, is formed on the outer peripheral edge of the flange 16. The notch 16b is formed to be long in the circumferential direction, and the plates 3 and 4 and the spline hub 6 are relatively rotatable within a range in which the circumferential end portion abuts the stop pin 10.

A frictional resistance generating mechanism 18 composed of a plurality of plate members is arranged between the inner peripheral portions of the plates 3 and 4 and the inner peripheral portion of the flange 16. The frictional resistance generating mechanism 18 is a mechanism for generating a predetermined frictional resistance between the plates 3 and 4 and the spline hub 6 when they rotate relative to each other. When the pressure plate (not shown) presses the clutch connecting portion 2 against the flywheel (not shown), the friction facing 8 comes into contact with the flywheel (not shown). Then, the cushioning portion 7b of the cushioning plate 7 is elastically deformed between the two friction facings 8 to absorb the shock when the clutch is engaged.

When the friction facing 8 is pressed against the flywheel, torque is input to the clutch connecting portion 2 and further transmitted to the clutch plate 3 and the retaining plate 4. The torque is further transmitted to the flange 16 via the coil spring 5 and output from the boss 15 to the input shaft of the transmission (not shown). When the torque transmission as described above is repeatedly performed, a gap is generated between the clutch plate 3, the flat fixing portion 7c and the stop pin 10 in the portion where the clutch coupling portion 2 and the clutch plate 3 are coupled. There is. Even in that case, due to the elastic force of the compressed cone spring 12, the outer peripheral portion of the clutch plate 3 and the flat fixing portion 7c are
A gap in the axial direction is less likely to occur between the stop pin 10 and the stop pin 10. Since the clutch plate 3 and the flat fixing portion 7c are in pressure contact with each other as described above, the torque is transmitted also by the friction force between the plates. Therefore, the flat fixing portion 7c
However, unlike the conventional case, torque transmission is not performed only by rivets, and the flat fixing portion 7c is less likely to be damaged.

The outer diameter of the cone spring 12 is larger than the seat surface 10e of the stop pin 10. for that reason,
The clutch plate 3 and the flat fixing portion 7c have a large area for receiving the pressure contact force of the cone spring 12. Therefore, rattling is less likely to occur between both members. Since the cone spring is used as the pressing member, a large pressing force can be obtained with a small occupied area.

In this embodiment, the clutch plate 3 and the cushioning plate 7 are also connected by the stop pin 10 for restricting the relative rotation between the plates 3 and 4 and the spline hub 6. Therefore, the member for connecting is omitted. Also, in this example,
The cushioning plate 7 is formed of an integral member. Therefore, the fixed portion with the clutch plate 3 is small. As a result, the structure is simplified and the number of parts is reduced.

[0017]

In the clutch disc assembly according to the present invention, the press contact member presses the flat portion and the plate in the vicinity of the pin. Therefore, the inter-plate frictional force is maintained between the flat portion, the disc-shaped plate, and the pin. As a result, the flat portion of the cushioning plate is less likely to be damaged.

When the pressing member is a cone spring, a large pressing force can be obtained in a small area. When each member is sandwiched between the head portion and the seat portion of the pin, the flat portion and the disk-shaped plate are pressed against each other by the cone spring. When the area of the cone spring is larger than the area of the seat portion, rattling between the members is less likely to occur.

[Brief description of drawings]

FIG. 1 is a schematic vertical sectional view of a clutch disc assembly as an embodiment of the present invention.

FIG. 2 is a partially enlarged view of FIG.

FIG. 3 is a plan view of a cushioning plate.

[Explanation of symbols]

 1 Clutch Disc Assembly 2 Clutch Connection Part 3 Clutch Plate 6 Spline Hub 7 Cushioning Plate 7b Cushioning Part 7c Flat Fixing Part 8 Friction Facing 10 Stop Pin 10e Seating Surface 12 Cone Spring

Claims (4)

[Claims] 1. A cushioning plate having a cushioning portion and a flat portion formed on an inner peripheral side of the cushioning portion, friction facings fixed to both surfaces of the cushioning portion, and a friction facing disposed on a side of the flat portion. Disc-shaped plate, a pin that fixes the disc-shaped plate and the flat portion, a pressure contact member that press-contacts the cushioning plate and the disc-shaped plate with each other in the vicinity of the pin, and the disc-shaped plate. A clutch disc assembly having a mating hub. 2. The clutch disc assembly according to claim 1, wherein the pressure contact member is a cone spring through which the pin penetrates. 3. The cone spring is arranged laterally of the disc plate and the flat portion, and the pin includes a body portion penetrating the disc plate, the flat portion, and the cone spring. The clutch disc assembly according to claim 2, further comprising a head portion disposed outside the penetrated member and a seat portion that abuts on the cone spring. 4. The clutch disc assembly according to claim 3, wherein the cone spring is compressed between the flat portion and the seat portion and has a larger area than the seat portion.