JP2000002267A - Clutch cover assembly - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make hard generation of problem in a wedge member in an energizing mechanism of friction follower of a clutch cover assembly. SOLUTION: This assembly has a friction follower and moves a first support plate and a fulcrum ring in the axial direction only by a friction amount by rotating a second support plate 32 provided at a pusher plate when wear generates in a wear facing. As a result, the fulcrum ring being the fulcrum of a pushing member does not change in its axial position. A reverse rotation restraining mechanism 101 allows the second support plate 32 to move in the rotational direction R2 to the pressure plate and restrict the movement to the side of rotational direction R1. The mechanism 101 is comprised of a plurality of teeth 102 formed at the support plate 32 and a claw 103 fixed to the pusher plate so as to be swingable.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch cover assembly, and more particularly to a clutch cover assembly having a wear following mechanism for maintaining a pressing load in an initial state regardless of wear of a friction member.

[0002]

2. Description of the Related Art A clutch cover assembly of a clutch device is mounted on a flywheel of an engine, and a friction facing of a clutch disc assembly is pressed against the flywheel by using a spring force of a diaphragm spring.
The engine's driving force is transmitted to the transmission.
In such a clutch device, when the amount of wear of the friction facing becomes equal to or more than a certain value, the friction facing wears out and becomes unusable, or the posture of the diaphragm spring of the clutch cover changes and the pressing load changes. Therefore, it is necessary to replace the clutch disk assembly. There has been a demand for extending the replacement time, that is, extending the life of the clutch.

In order to extend the life of the clutch,
In a clutch disk assembly, it is important to increase the effective thickness of the friction facing. Therefore, a method of fixing the friction facing to the cushioning plate without using rivets or the like is used. In the clutch cover assembly, it is necessary to return the attitude of the diaphragm spring to the initial state when the friction facing is worn. For this purpose, the wear amount of the friction facing is detected, and a member (a fulcrum ring on the pressure plate side or a support mechanism on the clutch cover side) that supports the diaphragm spring is moved according to the wear amount. This allows the friction facing of the clutch disk assembly to be used to the maximum.

In the clutch cover assembly disclosed in JP-A-6-42553, the wear following mechanism mainly includes a fulcrum ring disposed between the clutch cover and the diaphragm spring, and a direction in which the fulcrum ring is separated from the pressure plate. And a regulating mechanism to prevent the Fulcrum ring from coming off the pressure plate and to allow the Fulcrum ring to move from the pressure plate in the axial direction by the amount of wear if friction facing wear occurs. have.

[0005] The biasing mechanism is arranged between the transmission side surface of the pressure plate and the fulcrum ring. The urging mechanism has a wedge mechanism including a plurality of first inclined surfaces provided on the fulcrum ring side and a member disposed on the pressure plate side and having a plurality of second inclined surfaces that abut on the first inclined surface. ing. The wedge member having the second inclined surface is mounted movably in the circumferential direction with respect to the pressure plate. The biasing member circumferentially biases the wedge member having the second inclined surface against the first inclined surface, thereby biasing the fulcrum ring in an axial direction, that is, in a direction away from the pressure plate. .

When the release operation is performed after the friction facing of the clutch disk assembly has been worn, the fulcrum ring is separated from the pressure plate by the biasing member. Since the movement of the fulcrum ring in the axial direction is restricted by the regulating mechanism, only the wear amount of the friction facing moves. Thereby, the posture of the pressing member is kept constant.

[0007]

If, for example, intense vibration occurs during the engagement of the clutch, a phenomenon called under-adjustment may occur. What is under adjustment?
When the clutch is engaged, that is, when a force acts in the axial direction from the pressing member to the fulcrum ring, and as a result, a force acts in the axial direction from the first inclined surface to the second inclined surface of the wedge mechanism, This is a phenomenon in which the force acting on the formed wedge member in the circumferential direction increases, and the wedge member slides in the original direction. There, the position of the fulcrum ring no longer corresponds to the amount of wear.

In order to prevent under-adjustment,
It is conceivable to reduce the inclination angles of the first and second inclined surfaces. In this case, since the circumferential component of the axial force acting on the wedge member is reduced, the wedge member is unlikely to slide in the original direction. However, when the inclination angle is reduced, an overadjustment in which the wedge member moves in the circumferential direction more than necessary and pushes up the fulcrum ring more than the wear amount is likely to occur. Therefore, it is not preferable to prevent the under adjustment by changing the inclination angle.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a biasing mechanism for a wear following mechanism of a clutch cover assembly, which makes it difficult for the wedge member to be under-justified.

[0010]

According to a first aspect of the present invention, there is provided a clutch cover assembly for urging friction facing of a clutch disk assembly to a flywheel side to connect a clutch. And a fulcrum ring, a pressing member, a biasing mechanism, a regulating mechanism, and a reverse rotation suppressing mechanism. The clutch cover is fixed to the flywheel and has a facing portion facing the friction facing. The pressure plate is disposed between the friction facing and the opposing portion in close proximity to the friction facing, and has a first side on the friction facing side and a second side on the opposing portion side. The fulcrum ring is disposed on the second side of the pressure plate. The pressing member is supported by the clutch cover, and applies a pressing force to the fulcrum ring toward the pressure plate. The biasing mechanism has a first inclined surface, a wedge member, and a biasing mechanism. The plurality of first inclined surfaces are provided on a surface of the fulcrum ring facing the pressure plate. The first inclined surface may be formed integrally with the fulcrum ring, or may be formed on a member separate from the fulcrum ring. The wedge member is the second of the pressure plate
A plurality of second inclined surfaces are rotatably disposed on the side surface and abut on the plurality of first inclined surfaces. The urging member urges the wedge member in the first rotation direction to urge the second inclined surface toward the first inclined surface, thereby moving the fulcrum ring in the axial direction. The regulating mechanism prohibits the fulcrum ring from moving in the axial direction when there is no wear on the friction facing, and detects the amount of wear when the friction facing wears out,
This is a mechanism for allowing the fulcrum ring to move in the axial direction according to the amount of wear. The reverse rotation suppressing mechanism allows the wedge member to move in the first rotation direction with respect to the pressure plate, and restricts the movement of the wedge member in the second rotation direction opposite to the first rotation direction.

In the clutch cover assembly according to the first aspect, when the pressing member presses the fulcrum ring,
The pressure plate is pushed to the friction facing side via the fulcrum ring. As a result, the friction facing of the clutch disc assembly is sandwiched between the flywheel and the pressure plate. Thus, the clutch is connected. Next, when the pressing force from the pressing member is released, the pressing force against the friction facing from the pressure plate is released. As a result, the friction facing separates from the flywheel and the pressure plate. In this way, the clutch connection is released.

If the friction facing wears when the clutch is engaged, the restricting mechanism allows the fulcrum ring to move in the axial direction away from the pressure plate in accordance with the amount of wear. Therefore, the wedge member moves in the first rotation direction with respect to the pressure plate in the urging mechanism. At this time, when the second inclined surface presses the first inclined surface, the fulcrum ring is moved in the axial direction, and is separated from the pressure plate by the amount of wear. As a result,
The pressing member is returned to the initial position, and the load applied to the pressure plate is maintained at the initial pressing load.

In this clutch cover assembly, the movement of the wedge member in the second rotation direction with respect to the pressure plate is suppressed by the reverse rotation suppressing mechanism. Therefore, under-adjustment, which is a phenomenon in which the height of the fulcrum ring is reduced in the axial direction, is less likely to occur. In the clutch cover assembly according to the second aspect, in the first aspect, the reverse rotation suppressing mechanism includes a plurality of teeth and a swingable claw for meshing with the plurality of teeth.

According to a third aspect of the present invention, in the clutch cover assembly according to the second aspect, the plurality of teeth are provided on the wedge member. The pawl is swingably fixed to the pressure plate. In the clutch cover assembly according to the fourth aspect, in the third aspect, when the centrifugal force acts, the pawl is urged against the plurality of teeth.

In the clutch cover assembly according to the fourth aspect, the pawl is biased by the plurality of teeth during the rotation of the flywheel, so that the special member for biasing the pawl to the plurality of teeth is provided. Becomes unnecessary. In the clutch cover assembly according to the fifth aspect, in the fourth aspect, the pawl includes one end where a claw portion that engages with the plurality of teeth is formed, the other end where the center of gravity is located, and
A swinging portion between one end and the other end, the swinging portion being swingably fixed to the pressure plate.

In the clutch cover assembly according to the fifth aspect, when a centrifugal force acts on the pawl, the other end on which the center of gravity is located moves radially outward, and the one end on which the pawl portion is formed moves radially inward. Move and engage multiple teeth. In the clutch cover assembly according to the sixth aspect, in any one of the first to fifth aspects, the plurality of teeth are provided on a tooth member fixed to the wedge member.

In the clutch cover assembly according to the sixth aspect, since the plurality of teeth are provided on the tooth member separate from the wedge member, processing and processing are facilitated. In the clutch cover assembly according to the seventh aspect, in the sixth aspect, the tooth member includes a fixing portion fixed to the wedge member, and a tooth portion extending in a circumferential direction from the fixing portion and having a plurality of teeth formed thereon. Have.

[0018] In the clutch cover assembly according to the eighth aspect, in the seventh aspect, the wedge member includes a plurality of arc-shaped members, and the fixing portion fixes the plurality of arc-shaped members arranged in the circumferential direction to each other. In the clutch cover assembly according to the eighth aspect, since the fixing portions of the tooth members fix the arc-shaped members arranged in the circumferential direction to each other, it is not necessary to provide another fixing member.

In the clutch cover assembly according to the ninth aspect, the clutch is connected by urging the friction facing of the clutch disk assembly to the flywheel side, and the clutch cover, the annular pressure plate, the fulcrum ring and A pressing member, an urging mechanism, a regulating mechanism, and a reverse rotation suppressing mechanism are provided. The clutch cover is fixed to the flywheel and has a facing portion facing the friction facing. The annular pressure plate is disposed between the friction facing and the opposing portion in close proximity to the friction facing, and has a first side facing the friction facing and a second side facing the opposing portion. The fulcrum ring is disposed on the second side of the pressure plate. The pressing member is supported by the clutch cover, and applies a pressing force to the fulcrum ring toward the pressure plate. The biasing mechanism has a plurality of first inclined surfaces, a wedge member, and a biasing member. The plurality of first inclined surfaces are provided on a surface of the fulcrum ring on the pressure plate side. The annular wedge member is rotatably disposed on the second side surface of the pressure plate, and has a plurality of second inclined surfaces that contact the plurality of first inclined surfaces. The urging member urges the second inclined surface to the first inclined surface by urging the wedge member in the first rotation direction. As a result, an attempt is made to move the fulcrum ring in the axial direction. The regulating mechanism forbids the Fulcrum ring from moving in the axial direction when there is no wear on the friction facing, and detects the amount of wear when the friction facing wears out, and prevents the Fulcrum ring from moving in the axial direction according to the wear amount. A mechanism to forgive. The reverse rotation suppression mechanism is a mechanism that allows the wedge member to move in the first rotation direction with respect to the pressure plate, and restricts the movement in the second rotation direction opposite to the first rotation direction. The reverse rotation suppressing mechanism has a plurality of teeth formed in the wedge member in the circumferential direction, and a plurality of teeth which are swingably fixed to the pressure plate corresponding to the plurality of teeth and are urged to the plurality of teeth. Consists of nails.

In the clutch cover assembly according to the ninth aspect, the wedge member is restricted from moving in the second rotation direction by the reverse rotation suppressing mechanism including a plurality of teeth and a plurality of claws. Under adjustment, which is a phenomenon that the height of the fulcrum ring decreases in the axial direction, is less likely to occur. In the clutch cover assembly according to a tenth aspect, in the ninth aspect, the plurality of claws include a first claw and a second claw. The second claw is located between the teeth of the corresponding group of teeth while the first claw is engaged with the teeth of the corresponding group of teeth.

[0021] In the clutch cover assembly according to the tenth aspect, the first pawl is engaged with the teeth of the corresponding teeth, and the second pawl is engaged.
The claws are located between the teeth of the corresponding group of teeth. When the second pawl is engaged with the teeth of the corresponding tooth group, the first pawl is located between the teeth of the corresponding tooth group. As a result, for example, when the wedge member attempts to move in the second rotation direction due to vibration, the distance until the teeth come into contact with the claws is reduced. Specifically, one of the claws is engaged with the corresponding teeth of the group of teeth in a pitch unit that is half the circumferential interval between the claws. This means that the fluctuation of the amount of play of the pedal caused by the under-adjustment is smaller than before.

In the clutch cover assembly according to the eleventh aspect, in the ninth aspect, the plurality of claws include a pair of first claws radially opposed to each other and a second claw radially opposed to each other. Have. The pair of second claws are located between the teeth of the corresponding group of teeth while the pair of first claws are engaged with the teeth of the corresponding group of teeth. Here, when the wedge member attempts to move in the second rotation direction, the rotation of the wedge member is stopped by making sure that the pair of claws engage the teeth. Here, a pair of claws makes underadjustment less likely to occur.

According to a twelfth aspect of the present invention, in the clutch cover assembly according to the tenth or eleventh aspect, a circumferential angle between the teeth of the tooth group is 1 ° or less. In the clutch cover assembly according to the twelfth aspect, the circumferential angle between the teeth of the tooth group is 1 ° or less, and the maximum circumferential angle until the teeth of the wedge member abut on the pawl during under adjustment. Is 0.
It is as small as 5 ° or less.

[0024]

1 to 3 show a basic structure of a clutch cover assembly 1 to which an embodiment of the present invention can be applied. The clutch cover assembly 1 is used for a vehicle, particularly a large vehicle such as a truck. The clutch cover assembly 1 includes:
This is a device for transmitting or interrupting the torque transmitted from the flywheel 2 of the engine to the clutch disk assembly 3, and is attached to the flywheel 2. In addition,
In this clutch device, two clutch disk assemblies 3 are provided, and an intermediate plate 5 is arranged between the clutch disks 4 of both clutch disk assemblies 3. The present invention can be applied to a single-plate clutch device provided with only one clutch disk assembly. Each clutch disc assembly 3 mainly includes a clutch disc 4 and a hub 7 connected to the clutch disc 4 via a coil spring. The clutch disk 4 is composed of a plurality of friction plates 8 fixed on both surfaces of an outer peripheral portion of a disk-shaped plate 9. Each friction plate 8 has a rivet 1
2, a core plate 10 fixed to the disk-shaped plate 9 and a friction facing 11 fixed to the core plate 10. In this embodiment, the friction facing 11 is made of a sintered ceramic metal material.

The R1 direction in FIG. 1 is the direction of rotation of the clutch device, and the opposite R2 direction is the direction of rotation of the second support plate 32 during wear adjustment. An engine (not shown) is arranged on the left side in FIGS. 2 and 3,
A transmission (not shown) is arranged on the right side. The clutch cover assembly 1 mainly includes a clutch cover 21, a pressure plate 22, a fulcrum ring 23, a biasing mechanism 24, a regulating mechanism 25, a clutch pressing mechanism 27, a drive mechanism 26, and a release device 28. It is composed of

The clutch cover 21 is a dish-shaped member attached to the flywheel 2. Clutch cover 2
1 has an outer peripheral covering portion 21a that covers the outer peripheral side of the clutch disk assembly 3, and a disk-shaped portion 21b that faces the transmission side of the clutch disk assembly 3.
Further, as shown in FIG. 4, an annular opposing portion 21c which is axially opposing the clutch disc 4 is formed on the outer peripheral portion of the disc-shaped portion 21b. This opposing portion 21
Four first axial holes 21d are formed in c (that is, the outer peripheral portion of the disc-shaped portion 21b) at equal intervals in the circumferential direction. A recess 21e having a larger diameter than the first axial hole 21d is formed on the transmission side of the first axial hole 21d.

The fulcrum ring 23 is arranged on the second side surface 22 b of the pressure plate 22. The fulcrum ring 23 is a member for receiving a load from the lever member 46 and moving to the flywheel 2 together with the pressure plate 22. The fulcrum ring 23 includes an annular portion 23a and three projecting portions 23b extending radially outward from the annular portion 23a. Annular part 2
3a is arranged to face the groove 22c of the pressure plate 22 at a predetermined interval in the axial direction. Further, the protruding portion 23 b is
Is in contact with the second side surface 22b. As is clear from FIG. 1, the protrusion 23b extends a predetermined angle in the circumferential direction,
A second axial hole 23c is formed on the R2 direction side,
A third axial hole 23d is formed on the R1 direction side.
The second axial hole 23c and the third axial hole 23d correspond to the screw hole 22e and the engaging recess 22d of the pressure plate 22, respectively. The second axial hole 23c is the first axial hole 23c.
It corresponds to the axial hole 21d and has a smaller diameter than the first axial hole 21d.

The fulcrum ring 23 and the pressure plate 22 rotate integrally with the clutch cover 21, that is, the flywheel 2 by the drive mechanism 26. The drive mechanisms 26 are provided at four locations along the circumferential direction,
Each is composed of a strap plate 42, a bolt 43, and a block 44. The strap plate 42 is a member for connecting the fulcrum ring 23 to the clutch cover 21 so as to be non-rotatable and movable in the axial direction. Each strap plate 42 is a plate-like elastic member that extends in a circumferential direction (generally a tangential direction) in which three plate members are stacked. The R1 direction end of the strap plate 42 is fixed to the clutch cover 21. Strap plate 4
2 is fixed to the fulcrum ring 23 by bolts 43. The tip of the bolt 43 passes through the third axial hole 23 d of the fulcrum ring 23 and is screwed into the block 44. R2 of strap plate 42
The directional end is sandwiched between the protrusion 23 b and the head of the bolt 43. The block 44 is inserted into the engagement recess 22 d of the pressure plate 22. The block 44 is movable toward the transmission from the state shown in FIG. 3 with respect to the engagement recess 22d. By this block 44, the fulcrum ring 23 and the pressure plate 20 are connected so that they cannot rotate relative to each other and can relatively move in the axial direction.

As shown in FIG. 6, most of the urging mechanism 24 is disposed in an annular space between the groove 22c of the pressure plate 22 and the annular portion 23a of the fulcrum ring 23. The annular space includes an annular portion (annular portion 23a) protruding radially inward from the transmission side of the outer peripheral wall 23f of the fulcrum ring 23 and an annular portion protruding radially inward from the engine side of the outer peripheral wall 22f of the pressure plate 22. Is formed between. As a result, the outer peripheral side of the annular space is closed by the outer peripheral wall 22f of the pressure plate 22 and the outer peripheral wall 23f of the fulcrum ring 23, and both sides in the axial direction are
2 and an annular portion 23 a of the fulcrum ring 23. However, the inner peripheral side of the annular space is open, and the annular space communicates with the outside.

The urging mechanism 24 includes a fulcrum ring 23
This is a mechanism for applying an urging force in a direction away from the pressure plate 22 (transmission side). The urging mechanism 24 mainly includes the first support plate 31
And a second support plate 32 and a plurality of return springs 33. The first and second support plates 31, 32 are annular sheet metal members. These support plates 31 and 32 are formed by press working. Each of the first and second support plates 31 and 32 has a plurality of arc-shaped members arranged in the circumferential direction to form an annular shape. As shown in detail in FIG.
Between the annular portion 23a of the pressure plate 22 and the annular groove 22c in the inner peripheral portion of the pressure plate 22. The plurality of arc-shaped members constituting the first support plate 31 are arranged on the fulcrum ring 23 side and are in contact with the annular portion 23a. The arc-shaped member constituting the first support plate 31 includes:
It is fixed to the fulcrum ring 23 by rivets (not shown). The second support plate 32 is arranged on the pressure plate 22 side and is in contact with the groove 22c (in this embodiment, the friction plate 67). The arc-shaped member that forms the second support plate 32 includes the first support plate 3
1 are arranged corresponding to the arc-shaped members. Second
The radial width of the support plate 32 coincides with the radial width of the groove 22c, so that the second support plate 3
2 is movable only in the circumferential direction with respect to the groove 22c. The first and second inclined surfaces 31a, 32a extending a predetermined distance in the circumferential direction are formed on the main body of the arc-shaped member constituting the first and second support plates 31, 32, respectively. The first and second inclined surfaces 31a, 32a are formed at the radially intermediate portions of the main bodies of the support plates 31, 32, respectively.

The first inclined surface 3 of the first support plate 31
1a is higher at the end in the R2 direction (projecting toward the engine side) and lower at the end in the R1 direction. The inclination angles of the first and second inclined surfaces 31a, 32a (the inclined surfaces 31a, 3a)
The angle between 2a and groove 22c) is preferably in the range of 10 to 15 °, and more preferably in the range of 12 to 14 °. In an initial state in which the friction facing 11 is not worn, the first inclined surfaces 31a and the second inclined surfaces 32a are entirely in contact with each other. Here, the first inclined surface 31a and the second inclined surface 32a constitute a wedge mechanism. Since the arc members forming the first and second support plates 31 and 32 have the same shape, the support plates 31 and 32 can be formed only by manufacturing one type of arc member.

In this embodiment, the first and second support plates 31 and 32 are formed with a plurality of first and second inclined surfaces 31a and 32a, respectively, over the entire circumference. As a result, a larger number of wedge structures are formed than in the related art. The first and second support plates 31, 32 have outer peripheral cylindrical portions 31b, 32b bent in the axial direction.
Are formed on the outer peripheral side. The outer cylindrical portion 31b of the first support plate 31 is
Is in contact with the outer peripheral wall 23f. The outer peripheral cylindrical portion 32 b of the second support plate 32 is in contact with the outer peripheral wall 22 f of the pressure plate 22.

First and second support plates 31, 32
Each of the arc-shaped members is formed with a spring engaging portion 31d, 32d protruding inward in the radial direction on an inner peripheral portion. The spring engagement portions 31d and 32d protrude from the annular space and extend further inward in the radial direction. Spring engaging part 3
1d is provided on the R2 side of the arc-shaped member constituting the first support plate 31. The spring engaging portion 32d is provided on the R1 side of the arc-shaped member constituting the second support plate 32. Rivets 61 are attached to the spring engaging portions 31d and 32d.
Has been fixed. The rivet 61 has a cylindrical main body 6.
2, a portion 63 extending from the main body 62 into the spring engaging portions 31d, 32d, a first head 64 formed on the opposite side of the spring engaging portions 31d, 32d from the portion 63, and a portion 63 opposite to the main body 62. And a second head 65 formed on the side. The spring engaging portions 31d and 32d are rivets 61
Between the main body 62 and the first head 64. The main body 62 has a cylindrical shape whose center line extends in parallel with the axis OO of the clutch cover assembly 1, and has an outer peripheral surface.

The return spring 33 is a tension coil spring, and urges the arc member forming the first support plate 31 and the corresponding arc member forming the second support plate 32 in the circumferential direction. The first support plate 31 and the fulcrum ring 2 are urged toward each other by the first inclined surface 31a and the second inclined surface 32a.
3 is a member for urging the pressure plate 3 in a direction away from the pressure plate 22 in the axial direction.

At both ends of the return spring 33 are formed end portions 66 which are wound around the main body 62 of the rivet 61 in the rotational direction. The radius of the end 66 is the main body 6 of the rivet 61.
It is almost equal to the radius of 2. As shown in FIG. 8, the end 66 is wound around the transmission 62 with respect to the main body 62 of the rivet 61 at the spring engagement portion 31 d of the first support plate 31 (FIG. 6). The spring engaging portion 32d is wound around the main body 62 of the rivet 61 on the engine side. End 6
6 is in the axial direction with respect to the main body 62, that is, the spring engagement portion 31
d and 32d and the second head 65 can be moved or deformed.

As shown in FIG. 7, the return spring 33 is disposed on the inner peripheral side of the first and second support plates 31, 32, that is, further on the inner peripheral side of the pressure plate 22 and the fulcrum ring 23. The return spring 33 is a spring engaging portion 31 of the corresponding arc-shaped member.
d, 32d, the first support plate 31 is urged toward the R1 side with respect to the second support plate 32, and the second support plate 32 is urged toward the R2 side with respect to the first support plate 31. are doing. As a result, when the fulcrum ring 23 and the first support plate 31 are movable in the axial direction, the second support plate 32 is moved to the pressure plate 22 and the first support plate 3.
The second inclined surface 32a moves toward the engine side of the first inclined surface 31a with respect to the first inclined surface 31a, and pushes up the first support plate 31 in a direction away from the pressure plate 22.

The urging mechanism 24 includes the pressure plate 2
2 and the annular space is formed on the inner peripheral side at the same time, so that the urging mechanism 24 can be easily operated. For example, attachment and detachment of the return spring 33 are easy. Further, since the spring engaging portions 31d and 32d for locking the return spring 33 are formed integrally with the first and second support plates 31 and 32, the entire structure is simple.

The return spring 33 is arranged in a space further inside the annular space formed by the pressure plate 22 and the fulcrum ring 23 (that is, the return spring 33 is placed in the pressure plate 22).
And not between the fulcrum ring 23)
As a result, the following four advantages are obtained. (1) The length of the return spring 33 can be increased, and the design becomes easier. (2) The exchange of the return spring 33 becomes easy. (3) Since there is no need to provide a spring between the pressure plate 22 and the fulcrum ring 23, the structure of that part is simplified. If the spring is arranged between the two members, a structure for locking both ends of the spring must be arranged in the annular space, which complicates the structure. (4) The first and second inclined surfaces 31a, 32a can be provided over the entire circumference of the first and second support plates 31, 32, respectively, and the first and second inclined surfaces 31a, 32 can be provided.
The number of a increases. As a result, the first and second inclined surfaces 31
a, 32a can reduce the surface pressure of the contact surface in the wedge mechanism, and therefore the first and second inclined surfaces 31a, 32a.
Wear and breakage can be suppressed.

First and second support plates 31, 32
As shown in FIG. 7, each of the stays 68 is formed integrally with the main body of the arc-shaped member and protrudes inward in the radial direction. The stay 68 is a member for suppressing the outward bending of the return spring 33 in the radial direction. The stay 68 formed on the arc-shaped member constituting the first support plate 31 is provided on the R1 side of the spring engagement portion 31d, and the stay 68 formed on the arc-shaped member constituting the second support plate 32 is provided with a spring engaging member. It is provided on the R2 side of the joint 32d and on the R1 side of a stay 68 formed on the first support plate 31. As a result, for each return spring 33, the second support plate 32
And a stay 68 of the first support plate 31 is arranged on the R2 side.

Each stay 68 is made of sheet metal integrally extending from the inner peripheral edge of the main body of the first and second support plates 31 and 32, and has a contact portion 69 extending in the axial direction inside in the radial direction. The inner surface in the radial direction of the contact portion 69 is smoothly curved so as to protrude inward in the radial direction.
The contact portion 69 of the first support plate 31 extends toward the engine, and the contact portion 69 of the second support plate 32 extends toward the transmission. In this way, each contact portion 69 has an axial position corresponding to the return spring 33, and is arranged on the outer peripheral side of the return spring 33. A small gap is secured between the contact portion 69 and the return spring 33 in the radial direction. Also,
The two stays 68 corresponding to the respective return springs are arranged so as to be able to abut each other in the circumferential direction. As will be described later, when the wear amount of the friction facing 11 increases and reaches a predetermined value, the stays 68 come into contact with each other in the circumferential direction. It has become.

A friction plate 67 is disposed between the groove 22c and the second support plate 32. The friction plate 67 is an annular friction lining, and has a higher friction coefficient than the pressure plate 22 and the second support plate 32. The friction plate 67 preferably has excellent heat resistance and wear resistance. An example of the friction plate 67 is a brand name NAH44 (Nippon Valqua). The friction plate 67 is provided with the groove 22 c of the pressure plate 22 or the second support plate 32.
May be fixed to one of them. Further, the friction plate 67 may be constituted by a plurality of divided arc-shaped plates. Instead of the friction plate 67, both or one of the engine side surface of the second support plate 32 and the groove 22c of the pressure plate 22 may be coated with a friction material for increasing the friction coefficient as compared with the related art.

With the friction plate 67 or the friction material described above, under-adjustment hardly occurs even under severe vibration conditions. Under-adjust means that, when the clutch is engaged, the force acting in the axial direction from the first support plate 31 to the second support plate 32 by vibration increases, that is, the circumferential component of the force increases. This is a phenomenon in which the second support plate 32 slides in the R1 direction (the direction opposite to the direction in which it slides during wear compensation). In this case, the axial height of the first support plate 31, that is, the fulcrum ring 23 is reduced, and the axial position of the fulcrum ring 23 does not correspond to the amount of wear. As another method for preventing the above-described under-adjustment, it is conceivable to reduce the inclination angles of the first and second inclined surfaces 31a and 32a. In that case, the first inclined surface 3
The circumferential component of the force acting in the axial direction from 1a to the second inclined surface 32a can be reduced. However, if the angle is made extremely small, there are the following two problems, so that practical use is difficult. First, when the clutch is released, the second support plate 32 rotates more than necessary in the R2 direction with respect to the pressure plate 22, and a phenomenon (overadjustment) occurs in which the fulcrum ring 23 moves in the axial direction more than the wear amount. easy. Second, the rotation angle of the second support plate 32 increases for the same amount of wear. In this case, the reduction in the tensile load of the return spring 33 becomes extremely unfavorable, and it is difficult to design the return spring 33 to prevent it.

That is, in the present application, under-adjustment is suppressed without extremely reducing the inclination angles of the inclined surfaces 31a and 32a. The regulating mechanism 25 includes the friction facing 1
When the friction facing 11 wears out, when the friction facing 11 wears out, the wear amount of the friction facing ring 11 is detected, and when the friction facing 11 wears out, the fulcrum ring 23 is allowed to move in the axial direction. It is a mechanism for.
The regulating mechanism 25 is provided with the screw holes 2 of the pressure plate 22.
Corresponding to 2 e and the second axial hole 23 c of the fulcrum ring 23, four holes are provided at equal intervals in the circumferential direction. The members constituting the regulating mechanism 25 are:
It is a bolt 38 and a bush 39.

As shown in detail in FIG.
A main body 38a and a screw portion 3 formed at the tip of the main body 38a
8b and a head 38c. Screw part 38
b is screwed into the screw hole 22e of the pressure plate 22. Thus, the bolt 38 is fixed integrally with the pressure plate 22. Body 38 of bolt 38
a penetrates through the second axial hole 23c of the fulcrum ring 23 and the first axial hole 21d of the clutch cover 21. The main body 38a has a gap between the first axial hole 21d and the second axial hole 23c in the radial direction. Head 3
8c is arranged at a distance from the opposing portion 21c of the clutch cover 21 to the transmission side. In addition,
The member fixed to the pressure plate 22 is not limited to a bolt, but may be another rod-shaped member such as a pin.

As shown in FIG. 5, the bush 39 is a cylindrical member, and is capable of expanding and contracting, that is, elastically deforming in the radial direction. The bush 39 includes a cylindrical portion 39a and a disk-shaped flange 39b extending from one end of the cylindrical portion 39a to the outer peripheral side. A slit 39c extending in the axial direction is formed in the cylindrical portion 39a and the flange 39b. As shown in FIG. 4, the bush 39 is provided in the first axial hole 21 d of the facing portion 21 c of the clutch cover 21 and the bolt 38
Is disposed on the outer periphery of the main body 38a. The bush 39 is tightly fitted to the main body 38a. Also, the cylindrical portion 39a
Is in contact with the engine-side surface of the projection 23b of the fulcrum ring 23. A gap is provided between the outer peripheral surface of the cylindrical portion 39a and the first axial hole 21d of the clutch cover 21. The flange 39b is connected to the facing portion 21c.
Is arranged in contact with the bottom surface of the concave portion 21e. Axial gap A between flange 39b and head 38c of bolt 38
Is substantially equal to or larger than the wear allowance of the friction facing 11. Since the bush 39 is an elastic cylindrical body having a slit, it is easily bent and deformed, and stabilizes sliding resistance generated between the bush 39 and the bolt 38.

The clutch pressing mechanism 27 is a mechanism for pressing the pressure plate 22 toward the flywheel 2 via the fulcrum ring 23. The clutch pressing mechanism 27 includes a lever member 46, a retainer 47, a plate 48, a contact plate 49, and a snap ring 50.
, A diaphragm spring 51, a pin 52, and a split pin 53.

The retainer 47 is an annular member disposed on the outer periphery of an input shaft (not shown) of the transmission. The retainer 47 is engaged with a release device 28 described later. The retainer 47 includes a cylindrical main body 47a,
And a flange 47b extending outward from the transmission side end. The retainer 47 is
The clutch cover 21 is engaged with a pin 52 fixed to the inner peripheral portion of the disc-shaped portion 21b so as to be relatively non-rotatable and movable in the axial direction.

The diaphragm spring 51 is a substantially disk-shaped spring member. The diaphragm spring 51
An annular portion 51a is provided on the outer peripheral side, and a number of lever portions 51b extend from the annular portion 51a to the inner peripheral side. In other words,
A large diameter center hole is formed in the diaphragm spring 51 and a plurality of slits 51 extending radially from the inner peripheral edge thereof.
c is a disk shape formed. An oval hole 51d having a larger circumferential width than the slit 51c is formed at a radially outer end of the slit 51c, that is, at a root portion of the lever portion 51b. The diaphragm spring 51 has an outer peripheral portion supported by the clutch cover 21 and an inner peripheral portion having a retainer 47.
It is supported by. The diaphragm spring 51 is compressed in the axial direction, and the clutch cover 21 and the retainer 4
7 gives repulsion. As a result, the retainer 47 is urged toward the engine. The split pin 53 fixed to the retainer 47 is inserted between the lever portions 51b of the diaphragm spring 51 at a plurality of positions in the circumferential direction. As a result, the diaphragm spring 51 rotates together with the retainer 47.

The lever member 46 is a pressing member for increasing the pressing force of the diaphragm spring 51 according to the lever ratio and transmitting it to the fulcrum ring 23. The lever members 46 are radially arranged at equal intervals in the circumferential direction. Each lever member 46 is formed by, for example, bending a strip-shaped plate member. The radially outer portion of the lever member 46 is bent so as to protrude toward the transmission. A hole 46b extending in the circumferential direction is formed in that portion. An engagement protrusion 21f extending from the inside of the clutch cover 21 is engaged in the hole 46b. This engagement causes the lever member 46 to move the clutch cover 2
1 and rotate together. Both sides in the circumferential direction of the hole 46b are fulcrums 46a that swingably contact the clutch cover 21. Further, the lever member 46 is provided with an action point 46c that projects toward the engine at a portion closer to the outside in the radial direction and contacts the annular portion 23a of the fulcrum ring 23. A force point 46d protruding toward the transmission is formed on a radially inner portion of the lever member 46. The force point 46d is located on the transmission side of the flange 47b of the retainer 47. The cone spring 60 and the plate 48 are arranged between the flange 47b and the force point 46d of the lever member 46. The cone spring 60 is compressed and flat between the flange 47b and the force point 46d in the clutch connected state shown in FIGS. A force point 46d of the lever member 46 abuts on the engine side of the disk-shaped plate 48. The contact plate 49 is fixed by a snap ring 50 to the transmission side on the outer peripheral side of the main body 47a of the retainer 47. The outer peripheral portion of the contact plate 49 is a bent portion protruding toward the transmission. In the clutch connected state shown in the figure, a predetermined gap is secured between the bent portion and the lever member 46 in the axial direction.

The release device 28 includes the clutch pressing mechanism 2
This is a device for releasing the clutch by releasing the pressing force of the pressure plate 22 on the pressure plate 22. The release device 28 includes a release bearing 54 and a quill 55.
, A cylindrical member 56, a support ring 57, a snap ring 58, and a coil spring 59. The release bearing 54 includes an inner race, an outer race, and a plurality of rolling elements disposed between the two races. Quill 55 is release bearing 5
4 and is fixed to the outer race so that it cannot rotate relative to the outer race. The cylindrical member 56 is fixed to the inner race, and the tip is disposed on the inner peripheral side of the retainer 47. The support ring 57 is fixed to the cylindrical member 56 by a snap ring 58 fixed to the outer periphery of the distal end of the cylindrical member 56. The support ring 57 is in contact with a surface on the engine side of an inner peripheral portion of the retainer 47. The contact surface between the support ring 57 and the retainer 47 has a spherical shape, and can absorb misalignment. The coil spring 59
It is arranged on the outer periphery of the cylindrical member 56. The coil spring 59 is arranged to be compressed between the inner race and the retainer 47. Operation [Clutch Connection] In the clutch connection state shown in FIGS. 2 to 4, the diaphragm spring 51 urges the retainer 47 toward the engine, and the retainer 47 further moves the lever member 46.
Urges the fulcrum ring 23 toward the engine. Thereby, the pressure plate 22 sandwiches the clutch disk 4 and the intermediate plate 5 of the clutch disk assembly 3 between the pressure plate 22 and the flywheel 2. Thus, the clutch is connected.

The power point 46d of the lever member 46 and the fulcrum 46a
Is E, and the distance between the action point 46c and the fulcrum 46a is F, the lever ratio of the lever member 46 is E / F. That is, the pressing force of the diaphragm spring 51 becomes E / F times and acts on the fulcrum ring 23.
Therefore, the pressing force of the diaphragm spring 51 can be set small.

The cone spring 60 functions as a cushioning plate when shifting to the clutch engaged state. [Clutch Release] At the time of clutch release, the quill 55 is moved to the transmission side, and the release bearing 54, the cylindrical member 56, and the retainer 47 are moved to the transmission side. When the bent portion of the contact plate 49 contacts the lever member 46, the lever member 46 is thereafter moved to the transmission. At this time, since the distance from the contact portion of the lever member 46 with the contact plate 49 to the action point 46c is shorter than the distance from the force point 46d to the action point 46c, the action point 46
c moves away from the fulcrum ring 23 quickly. That is, the disengagement performance of the clutch is improved.

Since the pressing force of the diaphragm spring 51 is set small, the load applied to the retainer 47 by the diaphragm spring 51 during the release operation is small. That is, the release load is small. Further, since the cone spring 60 applies a load to the retainer 47 in the moving direction (transmission side) of the retainer 47, the release load is further reduced. As a result, the pedal effort of the clutch pedal is significantly reduced. When the action point 46c of the lever member 46 moves away from the fulcrum ring 23, the fulcrum ring 23 moves to the transmission side by the urging force from the strap plate 42. At this time, the fulcrum ring 23 and the pressure plate 22 move integrally in the axial direction. This is because the sliding resistance (maximum static friction) generated between the bolt 38 and the bush 39 is reduced by the strap plate 4.
This is because the force is set to be larger than the sum of the urging force from the urging mechanism 2 and the urging force from the urging mechanism 24, and no slip occurs between the bolt 38 and the bush 39. That is, the fulcrum ring 23 moves the pressure plate 22 in the axial direction via the regulating mechanism 25. As a result, the pressing force of the clutch disk assembly 3 against the clutch disk 4 from the pressure plate 22 is released.

It is preferable that the sliding resistance (maximum static friction) generated between the bolt 38 and the bush 39 is sufficiently larger than the sum of the urging force from the strap plate 42 and the urging force from the urging mechanism 24. It is preferably at least two times. With such a setting, when vibration is transmitted from the flywheel 2 to the pressure plate 22, no slip occurs between the bolt 38 and the bush 39, and the strap plate 42 bends instead. That is, the tracking of the wear amount is accurately maintained. [Wear occurrence] When the friction facing 11 is worn when the clutch is engaged, the pressure plate 22 and the fulcrum ring 23 move toward the friction facing 11 by the wear amount. At this time, the bolt 38 of the regulating mechanism 25 moves to the engine side together with the pressure plate 22. However, the bush 39 cannot move because the flange 39b is in contact with the facing portion 21c. Therefore, bolt 3
8 moves relative to the bush 39 in the axial direction. As a result, as shown in FIG. 10, a gap B equal to the wear amount of the friction facing 11 is formed between the protrusion 23b of the fulcrum ring 23 and the tip of the cylindrical portion 39a of the bush 39. Flange 39b of bush 39 and bolt 38
The gap in the axial direction between the head 38c and the head 38c becomes shorter by the amount of wear, and becomes A '(AB).

Next, when the clutch release operation is performed, the fulcrum ring 23 moves toward the transmission by the urging force from the urging mechanism 24 until it comes into contact with the bush 39. When the protrusion 23b abuts on the cylindrical portion 39a of the bush 39, the fulcrum ring 23 does not move further away from the pressure plate 22. This is because the bolt 38 and the bush 3
9 is set to be larger than the sum of the urging force from the strap plate 42 and the urging force from the urging mechanism 24. As a result, overadjustment of the wear amount is unlikely to occur. The term “over-adjust” means that the fulcrum ring 23 moves in the axial direction with respect to the pressure plate 22 more than the amount of wear.

As a result of the above operation, as shown in FIG.
A gap C between the second side surface 22b of the pressure plate 22 and the fulcrum ring 23, which is equal to the wear amount B described above.
Is formed. When the clutch connection operation is performed from this state, the state shifts to the state in FIG. 12 and FIG. 2, a gap C is formed between the pressure plate 22 and the fulcrum ring 23, and an initial gap A is formed between the flange 39 b of the bush 39 and the head 38 c of the bolt 38. A gap A ′ that is shorter by the amount (B) of the previous wear amount is formed. [Effect] In the structure of the regulating mechanism 25, since the bolt 38 and the bush 39 for detecting the amount of wear are provided on the second side surface 22b side of the pressure plate 22, the friction member for regulating the movement of the fulcrum ring 23 is provided. The joint portion is less likely to be affected by heat generated on the friction surface 22a side of the pressure plate 22. As a result, the magnitude of the sliding resistance generated between the bolt 38 and the bush 39 is stabilized for a long time.

Further, since the bolt 38 and the bush 39 are members independent of the pressure plate 22 and the clutch cover 21, it is easy to set the sliding resistance of the frictional engagement portion. The restricting mechanism 25 is completed by winding a bush 39 around a bolt 38 before attaching to the clutch cover assembly 1. That is, the setting of the sliding resistance of the friction engagement portion can be performed outside the clutch cover assembly 1. In addition, since the friction engagement portion is not provided on the pressure plate or the flywheel, the setting of the sliding resistance at the friction engagement portion is further facilitated. In the conventional example in which the friction engagement portion is provided on the pressure plate or the clutch cover, it is necessary to adjust the load in the holes formed in those members, and it is difficult to set the load.

The regulating mechanism 25 can be easily attached to and detached from the clutch cover assembly 1. Each of the regulating mechanisms 25 is attached to the clutch cover 21 from the transmission side with the screw hole 22e of the pressure plate 22, the second axial hole 23c of the fulcrum ring 23, and the first axial hole 21d of the clutch cover 21 aligned. It can be removed.

Further, as the wear is generated in the friction facing 11 and the wear adjusting operation is performed, the clearance A between the head 38c of the bolt 38 and the flange 39b of the bush 39 is increased.
Is getting shorter. Since the gap A can be observed from the outside of the clutch cover assembly 1, the operator can easily determine the replacement time of the clutch cover assembly 1. Since the fulcrum ring 23 is not rotatably connected to the clutch cover by the strap plate 42 instead of the pressure plate, even if the friction facing 11 is worn, the posture of the strap plate 42 is kept constant without change. This is because the fulcrum ring 23 is attached to the flywheel 2 and the clutch cover 2 by the wear following mechanism.
This is because the position in the axial direction with respect to 1 does not change. When the strap plate is fixed to the pressure plate, the posture of the strap plate changes with the movement of the pressure plate due to friction facing wear. In that case, the urging force from the strap plate changes. [Biasing Mechanism] The operation of the biasing mechanism 24 will be described. When the friction facing 11 becomes worn and the fulcrum ring 23 becomes movable toward the transmission, the second
The support plate 32 rotates to the R2 side with respect to the first support plate 31. As a result, the states shown in FIGS. 7 and 8 shift to the states shown in FIGS. 9 and 10, respectively. That is, when the second support plate 32 urged by the return spring 33 rotates, the second inclined surface 32a pushes up the first inclined surface 31a of the first support plate 31. As a result, the fulcrum ring 23 moves away from the pressure plate 2 in the axial direction until it contacts the bush 39 of the regulating mechanism 25.

Assuming that the initial axial height of the first support plate 31 and the second support plate 32 is T1, the axial height after operation is T2 which is increased from T1 by the wear amount C. At this time, as shown in FIG. 9, when the spring engaging portions 31d and 32d corresponding to the respective return springs 33 approach in the circumferential direction, the return springs 33 move radially outward, and The contact portion 68 may contact the contact portion 69. At this time, as shown in FIG. 10, since the first support plate and the second support plate 32 are separated in the axial direction, the positions of the rivets 61 at both ends 66 of the return spring 33 are also shifted in the axial direction. In this state, both ends 66 of the return spring 33 are freely moved or deformed in the axial direction in the main body 62 of the rivet 61, and stress is hardly generated at both ends 66.

The stay 68 limits the amount of flexure when the return spring 33 flexes radially outward due to centrifugal force in either the initial stage or when wear occurs. Since the stay 68 suppresses the return spring 33 from being bent by the centrifugal force, the return spring 33 is less likely to be damaged. In particular, wear and breakage at contact portions at both ends 66 of the return spring 33 are less likely to occur.

When the wear of the friction facing 11 progresses, the stays 68 corresponding to one return spring 33 approach each other in the circumferential direction and come into contact with each other. Due to this contact, the first support plate 31 and the second support plate 32 are not further rotated relative to each other. That is, the fulcrum ring 23 does not move further in the axial direction. In this manner, the stay 68 functions as a rotation stopping mechanism, and when the wear of the friction facing 11 reaches a predetermined value, the urging of the urging mechanism 24 automatically stops.

Further, in this embodiment, since both ends 66 of the return spring 33 are engaged with the outer peripheral surfaces of the rivets 61 provided on the first and second support plates 31, 32, the contact area increases. Due to the lower surface pressure, wear and breakage are less likely to occur. Therefore, the return spring 33 and the mating member (rivet) are less likely to be worn or damaged.

In the structure of the present embodiment in which the return spring 33 is disposed further inside the annular space, the return spring 33 is bent outward in the radial direction to allow the return spring 33 and the end to be locked. Sliding easily. For this reason, there is a possibility that the sliding portion is worn or damaged. Therefore, in the present invention, the stay 68 suppresses the deflection of the return spring 33 and the rivet 61 is used.
By reducing the surface pressure of the sliding portion, wear and breakage of the sliding portion are less likely to occur. Next, the structure of the reverse rotation suppressing mechanism 101 according to the present invention will be described in detail with reference to FIGS. This reverse rotation suppressing mechanism 101 is used for the clutch cover assembly as the basic structure described above. Therefore, the description of the other parts of the basic structure other than the reverse rotation suppressing mechanism 101 is omitted.

The reverse rotation suppressing mechanism 101 is a mechanism for preventing the second support plate 32 from rotating in the rotation direction R1 (second rotation direction) or reducing the amount of rotation as much as possible. This reverse rotation suppressing mechanism 101 prevents or minimizes the underadjustment in which the axial height of the fulcrum ring 23 decreases. Reverse rotation suppression mechanism 101
Is composed of a plurality of teeth 102 and swingable claws 104 meshing with the teeth 102. The plurality of teeth 102 are provided on the second support plate 32 (wedge member), and
3 is swingably fixed to the pressure plate 22. The engagement of the teeth 102 with the claws 103 makes it difficult for the second support plate 32 to rotate in the rotation direction R1.

The reverse rotation suppressing mechanism 101 will be described more specifically. The claws 104 are provided at, for example, four locations at equal intervals in the circumferential direction. The claw 103 is arranged on the outer peripheral side of the second support plate 32 in each space formed by the recess 109 formed in the pressure plate 22 and the recess 110 formed in the fulcrum ring 23. The claw 103 contacts the pressure plate 22 side and is fixed to the pressure plate 22 by a bolt 105. Specifically, the body of the bolt 105 is inserted into a hole formed in the claw 103. This allows
The claw 103 is rotatable around the axial center line of the bolt 105. The claw 103 is turned from the vicinity of the bolt 105 to the R
An engagement portion 106 extending to the second side, and
And the other end 107 extending to one side. Engaging portion 106
A plurality of engaging claws 108 are formed on the inside in the radial direction. The center of gravity of the claw 103 is located on the other end 107 side. As a result, when a centrifugal force acts on the pawl 103 with the rotation of the clutch cover assembly, the other end 107 moves outward in the radial direction, and the engaging portion 106 moves inward in the radial direction.

The plurality of teeth 102 are formed on the outer peripheral surface of the outer cylindrical portion 32b of the second support plate 32. Note that, in this embodiment, the plurality of teeth 102 are formed only at portions corresponding to the claws 103. The engaging claw portion 108 of the claw 103 is engaged with the R2 side portion of each of the plurality of teeth 102. As shown in detail in FIG. 19, the plurality of teeth 102
Side surface 102a has a low angle, and the R2 side surface 10a
2b is at a high angle. The surface 108a on the R1 side of the engaging claw 108 of the engaging portion 106 has a low angle, and the surface 108b on the R2 side has a high angle. As a result, in the meshing state shown in FIG. 17, the angle θ1 between the straight line connecting the center and the bottom of each tooth 102 to the surfaces 102a and 108a is larger than the angle θ2 from the straight line to the surfaces 102b and 108b. With the above structure,
When the second support plate 32 attempts to move in the rotation direction R1 side, the radially outer component of the force acting on the engagement claw 108 from each tooth 102 becomes smaller when the second support plate 32 attempts to move in the rotation direction R1. The force acting on the engagement claw portion 108 from the outside is smaller than the radially outer component of the force. As a result, when the engagement state shown in FIG. 9 is reached, the second support plate 32 engages with the claw 103, so that the second support plate 32 cannot rotate relative to the pressure plate 22 in the R1 direction. When the second support plate 32 attempts to move to the R2 side, the engagement claw 10
The radially outward component of the force acting on 8 is relatively large. The plurality of teeth 102 can rotate with respect to the pressure plate 22 while moving the engagement portion 106 side of the claw 103 radially outward.

Next, the relationship between the plurality of claws 103 and the teeth 102 will be described with reference to FIG. FIG. 18 is a schematic diagram for explaining the relationship between the two, and the actual shape, size, angle, and the like are emphasized, and are different from the actual ones. The plurality of teeth 102 are provided at four locations in the circumferential direction corresponding to the claws 103. That is, a tooth group consisting of a plurality of teeth is formed at four locations in the circumferential direction.
The teeth 102 may be formed over the entire circumference of the second support plate 32 by forming the teeth between the respective tooth groups. The circumferential pitch angle θ3 of each tooth 102 is the same and the phases match. θ3 is, for example, 1 ° or less.

The four claws 103 are arranged corresponding to each tooth group, and are arranged at intervals of about 90 ° in the circumferential direction. Also,
The two claws 103 diametrically opposed to each other are a first group 121 and a second group 12 each comprising a pair of claws 103.
2. The claws 103 of the first group 121 face each other in the radial direction, and each of the engaging claws 108
2 and is completely engaged. This prevents the second support plate 32 from rotating toward the R1 side. The pair of claws 103 forming the second group 122 are arranged to face each other in the radial direction. However, the second group 122 is the first group 1
21 is arranged at a position slightly shifted from the intermediate position in the circumferential direction. Specifically, the nail 1 of the second group 122
Numeral 03 is shifted from the line perpendicular to the line connecting the centers of the first group 121 to the R2 side. This shifted angle θ4
Is 0.5 ° in this embodiment, which is half of θ3. As a result, the nails 10 of the second group 122 on the R1 side as viewed from the nails 103 of the first group 121.
3 is θ6 (eg, 89.5 °), and the circumferential angle between the second group 122 on the R2 side and the claw 103 is θ5 (eg, 90.5 °). . With such an arrangement, the engaging claw 108 of the claw 103 of the second group 122 abuts on the intermediate position of the tooth 102 instead of the bottom of the tooth 102.

To summarize the structure described above, when the claws 103 of the first group 121 are engaged with the teeth 102, the engaging claws 108 of the second group 122 are not engaged with the teeth 102. . More precisely, the engagement claw 108
Is located in the middle of the engagement position with the teeth 102.
Unlike FIG. 18, the claws 103 of the second group 122 have teeth 1
02 is engaged with the claws 10 of the first group 121.
3 is located in the disengaged position of the tooth 102. In the state where the actual wear following operation is performed, the first group 1
There may be a state where neither the 21 nor the second group 122 is engaged with the tooth 102.

The above-described structure may be composed of, for example, only two claws. In this case, one of the claws is engaged with the tooth and the other is not engaged with the tooth. Further, by using three types of claws, it is possible to always maintain a state in which the other two claws are not engaged when one claw is engaged. In this case, the pitch circumferential angle of the claw can be divided into three equal parts.

In the structure shown in FIG. 18, the actual maximum movement angle is further reduced while maintaining the pitch circumferential angle of the teeth 102 at 1 ° or less. The circumferential angular pitch of the teeth 102, 118 is limited to 1 ° or slightly less than 1 ° due to processing problems. Conventionally, a tooth having a pitch much less than 1 ° (for example, 0.5 °) is used. It is difficult to form.

The operation of the urging mechanism 24 will be described. Wear occurs in the friction facings and the Fulcrum ring 23
Becomes movable toward the transmission, the second support plate 32 rotates toward the R2 with respect to the first support plate 31. At this time, the second support plate 3
The tooth 102 formed in 2 rotates while pushing the engaging claw 108 of the claw 103 outward in the radial direction. At this time, the resistance acting on the second support plate 32 from the claw 103 is small.

Next, the underadjustment phenomenon during the engagement of the clutch and the prevention of the underadjustment by the reverse rotation suppressing mechanism 101 will be described. Under-adjust means that, when the clutch is engaged, the first support plate 31
As a result, the force acting on the second support plate 32 in the axial direction increases, that is, the circumferential component of the force increases, so that the second support plate 32 moves in the R1 direction (the direction opposite to the direction in which it slides during wear compensation). ) Is a phenomenon that slips. At that time, the height of the first support plate 31 and the fulcrum ring 23 in the axial direction becomes low, and the axial position of the fulcrum ring 23 does not correspond to the wear amount. In order to prevent, suppress or minimize such under-adjustment, a reverse rotation suppression mechanism 101 is provided. As shown in FIG. 18, for example, in a state where the claws 103 of the first group 121 are completely engaged with the teeth 102 of the second support plate 32 or in a state where the claws 103 of the second group 122 are completely engaged with the teeth 102, The second support plate 32 is locked by the claw 103, and therefore cannot be moved in the rotation direction R1 side. As another case, when the engaging claw portion 108 of any of the claws 103 is not completely engaged with the teeth 102, the second support plate 32
Moves in the rotation direction R1 until the teeth 102 are completely engaged with the engagement claws 108 of any of the claws 103. At this time, the maximum angle at which the second support plate 32 can rotate in the R1 direction is θ4 which is one half of the pitch angle θ3 of the teeth 102. This θ4 is about 0.5 ° in this embodiment.

In other words, the reverse rotation inhibiting mechanism 101
In, the maximum rotation angle of the under adjustment is θ4
It is set to be as follows. As a result, the increase in the amount of play of the pedal when the under adjustment occurs is very small. In this embodiment, different from the above-described embodiment, the second support plates 32 are each composed of a plurality of arc-shaped members, and each is fixed to each other by the fixing member 112 to form one annular member. Fixing member 11
Reference numeral 2 denotes a plate member, which fixes both ends of adjacent arc-shaped members to each other by welding. Since the second support plate 32 is an integral member in the circumferential direction in this manner, the amount of movement of each inclined surface 32a in the circumferential direction becomes constant, whereby the first support plate 31 and the fulcrum ring 23
Is constant in the circumferential direction. Furthermore, since the second support plate 32 is an annular member, it is not necessary to provide one end of the return spring to each of the arc-shaped members, so that the number of return springs can be reduced. For example, the return spring has the number 2
Can be reduced to books. Structure of Reverse Rotation Suppressing Mechanism According to the Present Invention (Second Embodiment) The structure and operation of a reverse rotation suppressing mechanism according to a second embodiment of the present invention will be described with reference to FIGS. Since the reverse rotation suppressing mechanism is applicable to the above-described basic structure of the clutch cover assembly similarly to the first embodiment, only the basic structure and parts different from the first embodiment will be described in detail. .

The tooth member 115 mainly includes a fixing portion 116 and a tooth portion 117 extending from the fixing portion 116. The fixing part 116 fixes a plurality of arc-shaped members constituting the second support plate 32 to each other. In particular,
The fixing portion 116 fixes the circumferential ends of the arc-shaped member constituting the second support plate 32 to each other by welding. From the outside in the radial direction of the fixing portion 116, the teeth 117 extend in an arc shape on both sides in the circumferential direction. The teeth 117 are arranged on the outer peripheral side of the outer cylindrical portion 32b of each arc-shaped member. Further, the radially inner surface of the tooth portion 117 is in contact with the radially outer surface of the cylindrical portion 32b. Teeth 118 are formed radially outside the tooth portions 117. Teeth 118 are nails 103
Are engaged with the engaging claw portions 108 of FIG. In the initial state, the engaging claw 108 is in contact with the tooth 118 at the most R1 side.

The claw 103 has an engaging portion 106, the other end 107 and an engaging claw portion 108, similarly to the above embodiment, and is swingably fixed to the pressure plate 22 by bolts 105. . The engaging claw 108 has a single shape. The effect of preventing, suppressing or minimizing the underadjustment of the second support plate 32 in the reverse rotation suppressing mechanism 101 is the same as that in the above embodiment.

In particular, in this embodiment, since the tooth portion 117 having the teeth 118 is a member separate from the member constituting the second support plate 32, the following two advantages are obtained. First, it is easier to form the teeth 118 on the teeth 117. That is, the tooth member 115 is a flat member and does not need to be subjected to a complicated press work unlike the second support plate 32. Second, the teeth 118 of the tooth member 115
Or a harder material than the second support plate 32 can be used for the tooth member 115. Thus, wear and breakage of the teeth 118 are less likely to occur.

Further, the tooth member 115 is
1 and the arc-shaped members of the second support plate 32 are fixed to each other, so that the total number of components does not become too large. As shown in FIG.
The engaging claw 108 of the claw 103 may be urged against the teeth 102 by using 27. The spring 127 is a torsion coil spring. The spring 127 is wound around the bolt 105 and urges the other end 107 of the claw 103 radially outward.
Therefore, the engaging claw portion 108 of the claw 103 rotates inward in the radial direction and is urged by the teeth 102.

The reverse rotation suppressing mechanism according to the present invention can be applied to a structure other than the clutch cover assembly as the basic structure described first. For example, the clutch pressing mechanism may have a structure including only a diaphragm spring without a lever member or the like. In the urging mechanism, the first inclined surface may be formed directly on the fulcrum ring.

[0081]

In the clutch cover assembly according to the present invention, the movement of the wedge member in the second rotation direction with respect to the pressure plate is suppressed by the reverse rotation suppressing mechanism. Therefore, under-adjustment, which is a phenomenon that the height of the fulcrum ring in the axial direction is reduced, is less likely to occur.

[Brief description of the drawings]

FIG. 1 is a plan view of a clutch cover assembly as a basic structure to which an embodiment of the present invention can be applied.

FIG. 2 is a schematic longitudinal sectional view of a clutch device.

FIG. 3 is a schematic longitudinal sectional view of a clutch device.

FIG. 4 is a partially enlarged view of FIG. 2;

FIG. 5 is a perspective view of a bush of the regulating mechanism.

FIG. 6 is a partially enlarged view of FIG. 1, and is a cross-sectional view of an urging mechanism.

FIG. 7 is a plan view of an urging mechanism.

FIG. 8 is a front view of an urging mechanism.

FIG. 9 is a partial plan view of an urging mechanism.

FIG. 10 is a side view of the urging mechanism.

FIG. 11 is a schematic longitudinal sectional view showing an operation state of the clutch device.

FIG. 12 is a schematic longitudinal sectional view showing an operation state of the clutch device.

FIG. 13 is a schematic longitudinal sectional view showing an operation state of the clutch device.

FIG. 14 is a partial plan view showing a pressure plate, a second support plate, and a reverse rotation suppressing mechanism according to the present invention.

FIG. 15 is a schematic longitudinal sectional view for explaining an urging mechanism and a reverse rotation suppressing mechanism.

FIG. 16 is a partially enlarged view of FIG. 14;

FIG. 17 is a partially enlarged view of FIG. 16;

FIG. 18 is a schematic diagram for explaining a positional relationship between a plurality of claws and teeth.

FIG. 19 is a diagram corresponding to FIG. 14 in the second embodiment.

FIG. 20 is a diagram corresponding to FIG. 15 in the second embodiment.

FIG. 21 is a diagram corresponding to FIG. 16 in the second embodiment.

FIG. 22 is a partial plan view of a reverse rotation suppressing mechanism in a modified example.

[Explanation of symbols]

 22 Pressure plate 23 Fulcrum ring 32 Second support plate 33 Return spring 101 Reverse rotation suppression mechanism 102 Teeth 103 Claw 105 Bolt 107 Other end 106 Engagement part 108 Engagement claw

Claims (12)

[Claims] 1. A clutch cover assembly for urging a friction facing of a clutch disc assembly to a flywheel side to connect a clutch, comprising a facing portion fixed to the flywheel and facing the friction facing. A clutch cover, an annular pressure plate disposed between the friction facing and the facing portion in close proximity to the friction facing, and having a first side surface on the friction facing side and a second side surface on the facing portion side; A fulcrum ring disposed on the second side surface of the pressure plate; a pressing member supported by the clutch cover to apply a pressing force to the fulcrum ring toward the pressure plate; and the pressure plate of the fulcrum ring Multiple first A wedge member having an inclined surface, a plurality of second inclined surfaces rotatably disposed on the second side surface of the pressure plate and abutting on the plurality of first inclined surfaces, and attaching the wedge member in a first rotation direction. An urging mechanism having an urging member that urges the second inclined surface toward the first inclined surface by urging to move the fulcrum ring in the axial direction; and that the friction facing has no wear. When the fulcrum ring is prohibited from moving in the axial direction, when the friction facing wears, a wear amount is detected, and a regulating mechanism for allowing the fulcrum ring to move in the axial direction according to the wear amount is provided. Permitting the wedge member to move in the first rotation direction with respect to the pressure plate, and restricting movement in the second rotation direction opposite to the first rotation direction. Clutch cover assembly comprising a reverse suppression mechanism, the that. 2. The clutch cover assembly according to claim 1, wherein said reverse rotation suppressing mechanism includes a plurality of teeth and a swingable claw for meshing with said plurality of teeth. 3. The clutch cover assembly according to claim 2, wherein said plurality of teeth are provided on said wedge member, and said pawl is swingably fixed to said pressure plate. 4. The clutch cover assembly according to claim 3, wherein said pawl is urged against said plurality of teeth when a centrifugal force acts. 5. The pawl is provided between a claw and the center of gravity at one end where a claw portion engaging with the plurality of teeth is formed, another end at which a center of gravity is located, and swings on the pressure plate. The clutch cover assembly according to claim 4, further comprising: a swinging portion movably fixed. 6. The clutch cover assembly according to claim 1, wherein said plurality of teeth are provided on a tooth member fixed to said wedge member. 7. The toothed member according to claim 6, wherein the tooth member has a fixed portion fixed to the wedge member, and a tooth portion extending in a circumferential direction from the fixed portion and having the plurality of teeth formed thereon. Clutch cover assembly. 8. The clutch cover assembly according to claim 7, wherein said wedge member comprises a plurality of arc-shaped members, and said fixing portion fixes said arc-shaped members arranged in a circumferential direction to each other. 9. A clutch cover assembly for urging a friction facing of a clutch disc assembly to a flywheel side to connect a clutch, the clutch cover assembly having an opposing portion fixed to the flywheel and facing the friction facing. A clutch cover, an annular pressure plate disposed between the friction facing and the facing portion and adjacent to the friction facing, and having a first side surface on the friction facing side and a second side surface on the facing portion side. A fulcrum ring disposed on the second side surface of the pressure plate; a pressing member supported by the clutch cover to apply a pressing force to the fulcrum ring toward the pressure plate; and the pressure plate of the fulcrum ring Multiple first An annular wedge member having an inclined surface, a plurality of second inclined surfaces rotatably disposed on the second side surface of the pressure plate and abutting on the plurality of first inclined surfaces, and a wedge member in a first rotational direction; A biasing member having a biasing member for biasing the second inclined surface toward the first inclined surface to move the fulcrum ring in the axial direction; When the friction facing is worn, when the friction facing is worn, the amount of wear is detected, and a regulation is made to allow the falk lamb ring to move in the axial direction according to the worn amount. A mechanism for allowing the wedge member to move in the first rotational direction with respect to the pressure plate and moving in a second rotational direction opposite to the first rotational direction. A limiting mechanism, comprising a plurality of teeth groups formed in the wedge member in a circumferential direction, and a plurality of claws biased by the plurality of teeth groups, and a reverse rotation suppressing mechanism, Clutch cover assembly. 10. The plurality of claws include a first claw and a second claw, wherein the first claw is engaged with a corresponding tooth of the tooth group.
The second pawl is located between the teeth of the corresponding group of teeth;
The clutch cover assembly according to claim 9. 11. The plurality of claws have a pair of first claws radially opposed to each other and a second claw radially opposed to each other, and the pair of first claws correspond to each other. The clutch cover assembly according to claim 9, wherein the pair of second pawls are located between the corresponding teeth of the teeth when engaged with the teeth of the teeth. 12. The clutch cover assembly according to claim 10, wherein a circumferential angle between the teeth of the group of teeth is 1 degree or less.