JP2001304290A - Clutch cover assembly - Google Patents

Abstract

PROBLEM TO BE SOLVED: To facilitate processing of each of members on an abrasion compensating mechanism. SOLUTION: A clutch cover 15 is devised to integrally rotate with a flywheel 2. A pressure plate 16 is arranged in the vicinity of a friction facing 4a, integrally rotates with the clutch cover 15 and free to move in the axial direction. A lever member 45 is a member to give pressurizing force to the side of the friction facing 4a to the pressure plate 16. The abrasion compensating mechanism 18 has a support part to support the lever member 45 and it is a mechanism to move the support part to the abrasion compensating side in accordance with abrased quantity at the time when abrasion is caused on the friction facing 4a. The abrasion compensating mechanism 18 has an adjust ring 58 free to move the support part to the abrasion compensating side by being screwed and engaged with the clutch cover 15 and an energizing part 60 to energize it in the rotating direction.

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 provided with a wear compensation mechanism capable of adjusting the position of a fulcrum of a pressing member in accordance with the amount of wear when the friction member is worn. The present invention relates to a cover assembly.

[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 member of a clutch disc assembly is pressed against the flywheel by using a spring force of a diaphragm spring or the like.
The engine's driving force is transmitted to the transmission.
In such a clutch device, when the amount of wear of the friction member exceeds a certain level, the friction member becomes unusable or the pressure load changes due to a change in the posture of the diaphragm spring of the clutch cover assembly. Failure occurs. Therefore, when the amount of wear becomes constant, 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 member. Therefore, a method of fixing the friction member to the cushioning plate without using a rivet or the like is known. In the clutch cover assembly, when the friction member is worn, it is necessary to return the posture of a spring such as a diaphragm spring to an initial state. For this purpose, the amount of wear of the friction member is detected, and a fulcrum of a spring such as a diaphragm spring (the fulcrum ring on the pressure plate side,
Alternatively, a wear compensation mechanism for moving the clutch cover side support mechanism) is used. Accordingly, the posture of the diaphragm spring or the like can be kept constant regardless of the wear of the friction member, and the friction member of the clutch disk assembly can be used to the maximum.

In a clutch cover assembly disclosed in Japanese Patent Application Laid-Open No. 8-170652, a pressing mechanism for applying a pressing force to a pressure plate includes a spring and a lever member. The wear compensation mechanism is a mechanism for moving the support mechanism on the clutch cover side to the friction member according to the amount of wear. The wear compensation mechanism mainly includes a support member for supporting a fulcrum of the lever member on the clutch cover side, an urging mechanism for urging the support member toward the friction member, and detecting and measuring the amount of wear of the friction member. A mechanism that allows the pressure plate to move toward the clutch cover in accordance with the amount of wear. The urging mechanism includes two ring members having a wedge mechanism composed of a plurality of inclined surfaces that abut against each other complementarily, and the other ring member and the supporting member by urging the ring member on the clutch cover side in the rotational direction. And a spring that attempts to move the spring toward the friction member.
Further, the wear detecting mechanism includes a cylindrical member frictionally locked so as to be axially movable in a hole of the clutch cover, and a bolt extending from the pressure plate and having a head abutting on the opposite side of the cylindrical member to the friction member. It is configured. An axial gap corresponding to an allowance of the pressure plate is secured between the pressure plate and the cylindrical member in the axial direction. The pressure plate is constantly urged to the opposite side of the friction member by a plurality of strap plates. This allows
In the clutch release state in which the urging force from the spring is released, the pressure plate moves in a direction away from the friction member and continues to move until it comes into contact with the cylindrical member.

When the friction member wears, the pressure plate moves to the flywheel side, and moves the bush relative to the clutch cover by the amount of wear. As a result,
The axial gap between the pressure plate and the cylindrical member is the same as before the friction member was worn. Thereafter, when the clutch release operation is performed, the movement of the pressure plate in the axial direction is stopped by the tubular member, but the stop position is located on the friction member side by the amount of wear as compared with the clutch release before wear. Therefore, the radially outer portion of the lever member can swing in the axial direction. As a result, the biasing mechanism can move the support member in the axial direction until the radially outer portion of the lever member is immovably supported between the support member and the pressure plate.

[0006]

The wear compensating mechanism in the conventional clutch cover assembly requires the accuracy of each member, but it is difficult to machine the slope of the wedge mechanism. Therefore, there was a problem that the cost was increased. An object of the present invention is to facilitate processing of each member in a wear compensation mechanism.

[0007]

SUMMARY OF THE INVENTION A clutch cover assembly according to claim 1 is a device mounted on a flywheel for connecting and disconnecting a friction member to and from a flywheel. The clutch cover assembly includes a clutch cover, a pressure plate, a pressing member, and a wear compensation mechanism. The clutch cover rotates integrally with the flywheel. The pressure plate is arranged close to the friction member, rotates integrally with the clutch cover, but is movable in the axial direction. The pressing member is a member for applying a pressing force to the pressure plate toward the friction member. The wear compensation mechanism is a mechanism that has a support portion that supports the pressing member, and that moves the support portion to the wear compensation side according to the amount of wear when the friction member wears. The wear compensation mechanism has a screw member capable of moving the support position to the wear compensation side by screwing with the clutch cover, and an urging portion for urging the screw member in the rotational direction.

In this clutch cover assembly, at the time of wear compensation, the screw member is axially moved by being rotated by the urging portion. Since the formation of the screw is easier than the conventional formation of a slope or the like, the processing is facilitated while maintaining the accuracy. In the clutch cover assembly according to claim 2,
In claim 1, the biasing portion includes a gear member having a gear engaged with the screw member, and an elastic member for biasing the gear member in the rotation direction.

According to a third aspect of the present invention, in the clutch cover assembly according to the second aspect, the gear member has a first member urged by an elastic member and a gear engaged with the first member such that the first member cannot rotate relative to the first member. A second member. In the clutch cover assembly according to the fourth aspect, in the third aspect, the first member can return to the initial rotation position side with respect to the second member. Therefore, the gear member can apply a biasing force to the screw member for a long period of time.

In the clutch cover assembly according to the fifth aspect, in the fourth aspect, the first member can return to the initial rotation position side by centrifugal force when the rotation speed exceeds a predetermined number of rotations.
Thus, the first member automatically returns to the initial rotation position side.
In the clutch cover assembly according to claim 6, claims 3 to
In any one of 5, the elastic member urges the first member in the rotational direction and urges the first member and the second member in the axial direction. Thereby, the engagement between the first member and the second member is ensured.

According to a seventh aspect of the present invention, in the clutch cover assembly according to any one of the third to sixth aspects, the urging portion includes the first urging portion.
There is further provided a support member that penetrates the member and the second member in the axial direction and supports the two members so as to be relatively rotatable and movable in the axial direction within a limited range in the axial direction.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment Structure FIGS. 1 and 2 show a basic structure of a clutch device 1 in which a first embodiment of the present invention can be adopted. This clutch device 1 is employed in a vehicle, particularly a large vehicle such as a truck. The clutch device 1 is a device for transmitting torque from the flywheel 2 of the engine to the input shaft 3 of the transmission, and interrupting the transmission of torque as necessary. The clutch device 1 mainly includes a clutch disk assembly 4, a clutch cover assembly 5, and a release device 6. Note that OO shown in FIG. 1 is the rotation axis of the clutch device 1, the lower side of FIG. 1 is the first axial direction side (engine side), and the upper side of FIG.
Axial side (transmission side). An arrow R1 direction shown in FIGS. 6 and 11 is the rotation direction of the clutch device 1, and an arrow R2 direction is the opposite direction. FIG.
The positions and postures of the members in FIG. 2 indicate the state in which the clutch device 1 is connected at a stage where the clutch disk assembly 4 is not worn, and the positions and postures of the members in FIG. At the advanced stage, the clutch device 1 is in a connected state. Further, since the transmission provided with the clutch device 1 is of a type having no synchronizing mechanism, a clutch brake 7 described later is provided.

The flywheel 2 is a circular slope member attached to an end of a crankshaft (not shown) of the engine. An annular and flat friction surface 11 is formed on the outer peripheral portion of the flywheel 2 in the second axial direction. The clutch disk assembly 4 is disposed close to the flywheel 2 on the second axial side. The clutch disk assembly 4
This is a device for transmitting torque on the engine side to the transmission input shaft 3 by being connected to the flywheel 2. Here, two devices are used as the clutch disk assembly 4, each of which has a friction facing 4 a (friction member) provided on the outer peripheral portion, a hub 4 b connected to the transmission input shaft 3, and a rotational direction. And a damper mechanism 4c which is elastically connected to the second member. The friction facing 4a of one clutch disk assembly 4 is disposed close to the friction surface 11 of the flywheel 2. The friction facing 4a of the other clutch disc assembly 4 is disposed at a position separated from the friction surface 11 of the flywheel 2 in the second axial direction. An intermediate plate 13 is arranged between the friction facings 4a in the axial direction. The intermediate plate 13 is a member that rotates integrally with a clutch cover 15 described later and is movable in the axial direction.

The clutch cover assembly 5 is a device for transmitting or interrupting the torque of the flywheel 2 to the clutch disk assembly 4, and is attached to the flywheel 2. As shown in FIG. 3, the clutch cover assembly 5 mainly includes a clutch cover 15, a pressure plate 16, a pressing mechanism 17, and a wear compensation mechanism 18.

The clutch cover 15 is an annular member fixed to the flywheel 2. Specifically, the outer peripheral portion of the clutch cover 15 is fixed to the flywheel 2 by bolts. The clutch cover 15 covers the outer peripheral side of the clutch disk assembly 4 and is located on the second axial direction side of the clutch disk assembly 4. Thus, the clutch cover 15 is connected to the friction surface 1 of the flywheel 2.
1 in the axial direction.

The clutch cover 15 is roughly divided into an outer peripheral cover portion 21, a disk-shaped portion 22, and a cylindrical portion 23 formed between the two. The outer peripheral covering portion 21 has a substantially cylindrical shape that covers the outer peripheral side of the pressure plate 16, and the outer peripheral end thereof is fixed to the flywheel 2 by bolts (not shown). A plurality of portions of the outer peripheral covering portion 21 are cut out so as to open the outer peripheral side. Also,
A plurality of flat portions 24 and 25 are formed on the outer peripheral side of the cylindrical portion 23 in the outer peripheral covering portion 21. Flat part 24, 2
5 is continuous with the first axial direction end of the cylindrical portion 23, and the second axial surface 38 of the inner peripheral portion of the pressure plate 16.
And are spaced apart in the axial direction. Disc-shaped part 22
Is a portion extending from the second axial end of the outer peripheral covering portion 21 to the inner peripheral side, and the inner peripheral edge thereof is close to the periphery of the input shaft 3. A plurality of holes 27 are formed in a circumferential direction at a radially intermediate portion of the disc-shaped portion 22, and an annular portion is formed at an outer peripheral portion of the disc-shaped portion 22, i. Portion 26 is secured. A rod-shaped member 28 is fixed near the inner peripheral edge of the disc-shaped portion 22. The rod-shaped member 28 extends from the inner peripheral end of the clutch cover 15 toward the first axial direction.

As shown in FIG. 3, a tubular portion 29 extending toward the engine in the axial direction is formed at the inner peripheral end of the annular portion 26 of the clutch cover 15. A screw 29a described later is formed on the outer peripheral surface of the cylindrical portion 29. Further, an annular support portion 30 is formed at an inner peripheral end of the annular portion 26. Although the tubular portion 29 is formed integrally with the clutch cover 15, they may be fixed to each other separately.

The pressure plate 16 is an annular member disposed on the inner peripheral side of the clutch cover 15 and between the friction facing 4a of the clutch disk assembly 4 on the second axial direction side and the clutch cover 15 in the axial direction. . The surface on the first axial direction side of the pressure plate 16 is an annular and flat pressing surface 37. On the second axial direction side of the pressure plate 16, a second axial surface 38 facing the clutch cover 15 is formed. Further, an annular support portion 39 is formed on the inner peripheral side of the second axial surface 38. The support portion 39 protrudes from the outer peripheral portion toward the second axial direction.

The pressure plate 16 is connected to the clutch cover 15 by a strap plate 41 shown in FIG. Specifically, a plurality of strap plates 41 are provided at equal intervals in the circumferential direction, the R2 side end of each strap plate 41 is fixed to the outer peripheral portion of the pressure plate 16 by a bolt 42, and the R1 side end is a bolt (not shown). To the clutch cover 15. With this connection, the pressure plate 16 rotates together with the clutch cover 15 toward the R1 side. Also, in the clutch connected state, the strap plate 41
Are bent in the axial direction, and the strap plate 41 applies an urging force to the pressure plate 16 in the second axial direction. The head of the bolt 42 is arranged corresponding to the above-mentioned notch of the clutch cover 15.

The pressing mechanism 17 includes the pressure plate 1
This is a mechanism for applying a pressing force to the clutch 6 for clutch connection, and includes a diaphragm spring 44 and a lever member 45 retainer 46. The retainer 46 is an annular member, and is disposed close to the input shaft 3. The retainer 46 has an annular groove 46a formed on the outer peripheral surface and an inner peripheral side flange 46 formed on the inner peripheral surface.
b.

The lever member 45 is composed of a plurality of plate members radially arranged in the circumferential direction, and is disposed around the first axial side portion of the retainer 46. Each lever member 45
Has a radially inner end engaged with the retainer 46 and a radially outer end engaged with the pressure plate 16 and the fulcrum ring 59. Note that the lever member may be composed of one annular plate. Lever member 4
The radially inner end of 5 is inserted into the groove 46a of the retainer 46. The first radial inner end of the lever member 45
The axial side has a convex surface curved in the radial direction, and swingably contacts the first axial side surface of the groove 46a. The lever member 45 has a radially outer portion disposed axially between the pressure plate 16 and the clutch cover 15. The second axial side surface of the outer peripheral portion of the lever member 45 is supported by a fulcrum ring 59 described later. Further, in the lever member 45, the first axial side surface of a portion on the inner peripheral side of the above-described support portion is supported by the support portion 39 of the pressure plate 16.

The diaphragm spring 44 is disposed on the second axial direction side of the lever member 45 and is spaced apart in the axial direction.
A second axial side surface of the outer peripheral portion of the diaphragm spring 44 is supported by the clutch cover 15, particularly the annular support portion 30. The inner peripheral end of the diaphragm spring 44 is in contact with the second axial surface of the retainer 46. In this state, the diaphragm spring 44 urges the inner peripheral end of the lever member 45 through the retainer 46 toward the first axial direction.

The inner peripheral end of the diaphragm spring 44 is engaged with the rod-shaped member 28 and is prevented from rotating. A hole into which the bar-shaped member 28 is inserted is formed in the retainer 46, and the retainer 46 is guided by the bar-shaped member 28 and moves in the axial direction. Lever member 45
Are, from the inner peripheral side, a force point 50 where a force is applied from the retainer 46 to the first axial direction side, an action point 51 where a force can be applied to the pressure plate 16, and a fulcrum 52 supported on the clutch cover 15 side. And the like or each supported portion. Each point 50, 51, 52 is actually a linear portion formed in an arc or ring around the central axis O. The action point 51 is a portion of the lever member 45 that protrudes toward the first axial direction, and the support portion 39 of the pressure plate 16
Is in contact with The fulcrum 52 is a portion of the lever member 45 that protrudes toward the second axial direction, and is an annular support portion 40 formed on a side surface of the fulcrum ring 59 in the first axial direction.
Is in contact with A plurality of holes 52a are formed in the circumferential direction at the fulcrum 52, and projections 40 extending from the support portion 40 of the fulcrum ring 59 are formed in the holes 52a.
a is inserted. As a result, the lever member 45 rotates integrally with the clutch cover 15. Support point 52 from power point 50
L1 is the radial distance from the point of force 50 to the point of action 5
The radial distance from L1 to L1 is L2, and the radial distance from the point of application 51 to the fulcrum 52 is L3. As a result, the pressing load transmitted from the diaphragm spring 44 to the lever member 45 is transmitted to the pressure plate 16 after being multiplied by L2 / L3.

Next, the wear compensation mechanism 18 will be described. The wear compensating mechanism 18 shown in detail in FIGS. 3 and 4 adjusts the initial height in the axial direction of the force point 50, which is the tip of the lever member 45, that is, the inner peripheral end, after the friction facing 4a of the clutch disk assembly 4 is worn. The purpose is to return to the position, that is, to keep the axial position of the release bearing 84 constant, thereby making the clutch brake gap constant. Therefore, the wear compensation mechanism 18
Is a friction facing 4a of the clutch disk assembly 4.
When the wear occurs, the fulcrum 52 of the lever member 45 on the clutch cover side is moved toward the friction facing 4a in accordance with the wear at the time of the next clutch release.

The wear compensating mechanism 18 mainly includes an urging mechanism 55 and a wear amount detecting mechanism 56. The urging mechanism 55 is a mechanism for urging a below-described fulcrum ring 59 toward the first axial direction, that is, toward the clutch disk assembly 4 with a constant force. When the friction facing 4a of the clutch disk assembly 4 wears, the wear amount detection mechanism 56 limits the movement of the pressure plate 16 in the second axial direction side at the next release according to the wear amount, and thus the urging mechanism 55 is a mechanism for enabling the fulcrum ring 59 to move in the axial direction.

As shown in FIG. 3, the urging mechanism 55 mainly includes an adjust ring 58 and a fulcrum ring 59.
And an urging portion 60. The adjust ring 58 is disposed on the clutch cover 15, particularly on the first axial direction side of the annular portion 26, and is located on the inner peripheral side of the tubular portion 29. On the inner peripheral surface of the adjust ring 58, a screw 58a to be screwed with the screw 29a of the tubular portion 29 is formed. Due to the threaded portion, the adjust ring 58 moves in the first axial direction when rotated in the clutch rotation direction R1, and moves in the second axial direction when rotated in the clutch rotation direction R2. It has become. An outer peripheral gear 58b is formed on the outer peripheral surface of the adjust ring 58. The outer peripheral gears 58b are arranged in the rotation direction, and each of them extends long in the axial direction.

The fulcrum ring 59 is disposed in contact with the adjust ring 58 in the first axial direction. The adjust ring 58 and the fulcrum ring 59 are relatively rotatable. A projection or groove (not shown) is formed on the outer peripheral surface of the fulcrum ring 59 and engages with the groove or projection formed on the inner peripheral surface of the clutch cover 15 so as to be relatively non-rotatable and movable in the axial direction. Further, the fulcrum ring 59 covers the cylindrical portion 5 covering the outer peripheral side of the cylindrical portion 29.
9a.

Next, the urging portion 60 will be described with reference to FIGS. 3, 6, and 7. FIG. The urging unit 60 applies a urging force in the rotational direction R1 side of the adjust ring 58,
This is a mechanism for urging the adjuster ring 58 from the clutch cover 15 in the first axial direction. Urging part 60
Consists mainly of bolts 61 (support members), torsion coil springs 62 (elastic members), swing plates 63 (first members), and gear members 64 (second members). The urging portion 60 is provided on the flat portion 24 of the clutch cover 15. The urging portion 60 may be single or plural, but the clutch cover 15 has a hole communicating with the radial direction at the portion where the urging portion 60 is provided.

The bolt 61 is screwed into the flat portion 24 of the clutch cover 15 from the second axial direction side, and has a screw portion 61a, a body portion 61b, and a head portion 61c. The trunk 61b extends from the clutch cover 15 in the second axial direction,
The head 61c is located at a position axially away from the second axial side surface of the flat portion 24. The swing plate 63 is a substantially rectangular plate member, and has a body 6 of a bolt 61 at one end.
The hole 63a through which 1b penetrates is formed. This allows the swing plate 63 to rotate and move axially with respect to the bolt 61. The swing plate 63 rotates around a center line C1 of the bolt 61 (the center line C1 is parallel to the rotation axis OO of the clutch device 1), and rotates clockwise in FIG. The bolt rotation direction is R3, and the counterclockwise direction is bolt rotation direction R4. Further, the end of the swing plate 63 on the side of the hole 63a is defined as a base end 63c, and the opposite side is defined as a tip 63d.
And The length from the hole 63a to the edge of the proximal end 63c is shorter than the length from the hole 63a to the edge of the distal end 63d. As is clear from FIG. 6, the proximal end 63c of the swing plate 63
Is located on the rotation direction R1 side of the bolt 61, and the tip 63d is located on the rotation direction R2 side of the bolt 61. Further, ratchet teeth 63b are formed on the second axial side surface (around the hole 63a) near the base end 63c of the swing plate 63. As shown in FIG. 8, each tooth of the ratchet teeth 63b has an inclined surface that becomes higher in the axial direction as it goes to the rotation direction R3 side, and further has a contact surface that extends straight in the axial direction at the end on the R3 side. ing. The gear member 64 is formed with a hole 64a through which the body 61b of the bolt 61 passes,
It is an annular member. Thus, the gear member 64 is rotatable around the center C1 of the bolt 61 and is movable in the axial direction. However, the gear member 64 is supported on the first axial direction side by a ring 65 fixed to the body 61b, and on the second axial direction side by the head 61c. Therefore, the gear member 64 does not fall off the bolt 61 and can move in the axial direction within a small range. A second hole 64b having a larger diameter than the second axial side surface of the gear member 64 around the hole 64a is formed.
The head 61c of the bolt 61 is in contact with the bottom surface of the second hole 64b. Further, a plurality of rotation grooves 64c extending in the radial direction are formed on the second axial side surface (around the second hole 64b) of the gear member 64.

An outer peripheral gear 64d is provided on the outer peripheral surface of the gear member 64.
Are formed. The outer peripheral gear 64d meshes with a part of the outer peripheral gear 58b of the adjust ring 58. Further, a ratchet tooth 64 is provided on the first axial direction side of the gear member 64.
e is formed. The ratchet teeth 64e complementarily mesh with the ratchet teeth 63b. That is,
As shown in FIG. 8, each tooth of the ratchet teeth 64e has an inclined surface that becomes higher in the axial direction as it goes to the rotation direction R4 side, and further has a contact surface that extends straight in the axial direction at the R4 side end. ing.

The torsion coil spring 62 has a function of urging the swing plate 63 in the rotation direction R3 around the bolt,
The swing plate 63 has a function of urging the swing plate 63 toward the second axial direction to maintain the meshing state of the ratchet teeth 63b and 64e. The torsion coil spring 62 has a coil portion 62.
a, a first arm 62b, and a second arm 62c. The coil portion 62a is disposed around the body 61b between the clutch cover 15 and the swing plate 63. The coil portion 62a is compressed in the axial direction, and constantly biases the swing plate 63 toward the second axial direction.
Note that the coil portion 62a can be further compressed. In this case, as shown in FIG.
b and 64e can be relatively rotated completely apart from each other in the axial direction. The tip of the first arm portion 62b is inserted into a hole formed in the clutch cover 15. The tip of the second arm portion 62c has a rotation direction R of the swing plate 63.
4 and urges the swing plate 63 toward the rotation direction R3.

As described above, the bolt 61 functions as a support member that supports the swing plate 63 and the gear member 64 so as to be relatively rotatable and movable in the axial direction within a limited range in the axial direction. With the above structure, as shown in FIG. 6, the swing plate 63 has a first posture (initial posture) on the rotation direction R4 side drawn with a solid line and a second posture (the initial posture) on the rotation direction R3 side drawn with a two-dot chain line. (The final posture). As shown in FIG. 8, the ratchet teeth 63b urge the ratchet teeth 64e in the rotation direction R3.
When the swing plate 63 rotates in the rotation direction R3 and rotates the gear member 64, that is, when the wear compensation operation proceeds, the swing plate 63 moves from the first posture to the rotation direction R.
It turns to the third side, and the tip 63d moves inward in the radial direction. However, when the rotation speed of the engine increases, the swing plate 63 rotates in the rotation direction R4 due to centrifugal force, and the tip 63d moves radially outward. At the time of this return operation, the ratchet tooth 63b is moved from the state shown in FIG. 8 to the first position by the inclined surface of the ratchet tooth 64e as shown in FIG.
While being pushed down in the axial direction, it rotates in the rotation direction R4.

As described above, in the biasing portion 60 which is a winding mechanism utilizing centrifugal force and ratchet, the force acting on the adjust ring 58 from the gear member 64 is substantially constant regardless of the wear of the friction facing 4a. is there. The wear amount detection mechanism 56 is a mechanism for restricting the movement of the pressure plate 16 in the second axial direction during the subsequent release when the wear occurs in the clutch disk assembly 4 according to the wear amount. In this embodiment, as shown in FIG. 4, the wear amount detecting mechanism 56 is composed of, for example, two sets of mechanisms provided at positions facing each other in the radial direction, and each set includes a roll pin 73, a nut 74, and a bolt 75. Have been. The roll pin 73 is connected to the flat portion 2 of the clutch cover 15.
4 is inserted into an axial hole 24a formed in the hole 4a. The roll pin 73 is a spring member having a slit formed in the axial direction, and is elastically in contact with the wall surface of the axial hole 24a. Thus, the roll pin 73 is attached to the clutch cover 15.
Are frictionally engaged so that they do not move in the axial direction until a predetermined amount of force acts on them. In FIG. 4 in a clutch connected state, a predetermined axial gap is formed between the first axial side end surface of the roll pin 73 and the second axial surface 38 of the pressure plate 16. This axial gap is such that the pressure plate 16
It is the amount that can be moved in the axial direction (the allowance of the pressure plate). In addition, when the pressure plate 16 moves by the margin in the second axial direction and abuts on the roll pin 73 to forcibly restrict the movement, the state is the maximum release state (described later).

The nut 74 is inserted into the roll pin 73. The nut 74 has a screw hole 74a formed on the first axial direction side, and has a flange 74b abutting on the second axial side surface of the roll pin 73 on the second axial direction side. The first axial side end of the nut 74 is located closer to the second axial direction than the first axial side end of the roll pin 73. In this embodiment, the nut 74 is press-fitted into the roll pin 73, and the nut 74 does not move in a direction in which the nut 74 is separated in the axial direction. The method of fixing the nut 74 and the roll pin 73 is not limited to press-fitting.

The screw portion 77 of the bolt 75 is screwed into a screw hole 74 a of a nut 74. The head 78 of the bolt 75
It is arranged in an axial hole 79 of the pressure plate 16. The axial hole 79 is located in the pressure plate 16 at a position corresponding to the axial hole 24 a of the clutch cover 15. The axial hole 79 is provided in the first
It comprises a hole 80 and a second hole 81 connected to the first hole 80 and opened on the side surface in the second axial direction. The second hole 81 is the first
It is concentric with the hole 80 but has a small diameter. The head 78 of the bolt 75 is in contact with the bottom of the first hole 80.

With the above configuration, the bolt 75, the nut 74, and the roll pin 73 are one member that moves integrally in the axial direction, and the pressure plate 16 is moved from the state shown in FIG.
, It is possible to approach in the axial direction, but it is impossible to move away from it. Thus, the pressure plate 16 receives a resistance from the bolt 75 when moving in the second axial direction from the state shown in FIG. 4, but abuts against the roll pin 73 when moving in the first axial direction. You can move freely until you touch. A bolt 83 for preventing the bolt 75 from dropping is screwed to the pressing surface 37 side of the second hole 81.

The release device 6 shown in FIG. 1 is a device for releasing the connection of the clutch device 1 by pulling out the distal end of the lever member 45 in the second axial direction, and mainly comprises a sleeve 82 and a release bearing 84. It is composed of
The sleeve 82 is a cylindrical member arranged on the outer periphery of the transmission input shaft 3. First of sleeve 82
The outer peripheral flange 82a formed at the axial end contacts the inner peripheral surface of the inner peripheral flange 46b of the retainer 46 from the first axial direction side.

The release bearing 84 includes a sleeve 82
Are arranged around the second axial side end of the second member. The inner race 84 a of the release bearing 84 is fixed to the sleeve 82. An outer peripheral wall 85 is fixed to the outer periphery of the outer race 84b of the release bearing 84. Engaging portions 86 are provided on the outer peripheral wall 85 at, for example, two locations facing each other in the radial direction. The release fork 87 is swingably supported by support means (not shown) attached to a clutch housing (not shown), and is connected to a clutch operating mechanism (not shown). The tip of the release fork 87 is the first of the engagement portions 86 of the outer peripheral wall 85.
They are arranged with a predetermined gap in the axial direction.

A coil spring 88 is disposed between the inner race 84a of the release bearing 84 and the inner periphery of the retainer 46 in the axial direction. The coil spring 88 urges the retainer 46 against the sleeve 82. As a result, the retainer 46 is pressed against the sleeve 82 in the first axial direction, so that the inner peripheral flange 46b and the outer peripheral flange 82a are not separated from each other in the axial direction. As a result, the sleeve 82 and the inner race 84a rotate integrally with the clutch cover 15.

Further, a clutch brake 7 is provided on a wall surface of a transmission housing (not shown). A predetermined axial clearance (clutch brake gap) between the clutch brake 7 and the release bearing 84
Is secured. The clutch brake 7 is a mechanism for smoothly shifting the transmission.
More specifically, the clutch brake 7 is interposed between the release device 6 and the wall surface of the transmission housing in a state where the release device 6 is moved to the second axial direction side, and thereby rotates the transmission input shaft 3. Has a function to stop. The clutch brake gap is a value obtained by multiplying the margin of the pressure plate 16 by the lever ratio of the lever member 45. A state in which the release bearing 84 contacts the clutch brake 7 is referred to as a maximum release state.

The lock mechanism 90 shown in FIGS. 10 and 11
Is a mechanism for locking the operation of the wear compensating mechanism 18, that is, the urging mechanism 55 at a predetermined rotational speed (for example, the idling rotational speed of the engine) or more. Lock mechanism 90
Is provided on the flat portion 25 of the clutch cover 15.
At a position corresponding to the flat portion 25, a cutout portion 23b penetrating through the cylindrical portion 23 in the radial direction is formed.
The lock mechanism 90 includes a bolt 91, a lock plate 92, and a torsion coil spring 93. Bolt 91 is flat part 2
5 is screwed from the second axial direction side,
a, a trunk 91b and a head 91c. Torso 91
b extends in the second axial direction from the clutch cover 15 and
1a is located at a position axially away from the second axial side surface of the flat portion 25. The lock plate 92 is a substantially rectangular plate member, and has a hole 92a formed at one end thereof, through which the body 91b of the bolt 91 passes. This allows the lock plate 92 to rotate and move axially with respect to the bolt 91. Note that the lock plate 92 rotates around a center line C2 of the bolt 91 (the center line C2 is parallel to the rotation axis OO of the clutch device 1), and moves in a clockwise direction in FIG. The bolt rotation direction is R6, and the counterclockwise direction is bolt rotation direction R5. Further, the end on the hole 92a side of the lock plate 92 is defined as a base end 92b, and the opposite end is defined as a distal end 92c. FIG.
As can be seen from FIG.
b is located on the rotation direction R2 side of the bolt 91 and has a tip 92c.
Are located on the rotation direction R1 side of the bolt 91. The torsion coil spring 93 connects the lock plate 92 with the bolt center C2.
Is a member that applies a force to rotate in the direction of rotation R5. The torsion coil spring 93 has a coil portion 93a.
And a first arm 93b and a second arm 93c. The coil portion 93 a of the torsion coil spring 93 is disposed between the lock plate 92 and the flat portion 25 around the body 91 b of the bolt 91. Also, the coil portion 93a
Are axially compressed and urge the lock plate 92 against the head 91c of the bolt 91. The tip of the first arm 93 b is inserted into a hole formed in the clutch cover 15. The tip of the second arm portion 93c is in contact with the rotation direction R6 side surface of the tip 92c of the lock plate 92, and urges the lock plate 92 toward the rotation direction R5.

An engaging portion 95 is formed radially inward of the base end 92b of the lock plate 92 so as to be able to engage with the outer peripheral gear 58b of the adjust ring 58. At the position indicated by the two-dot line, the engaging portion 95 is located radially outward from the outer peripheral gear 58b. With the above structure, FIG.
As shown in FIG. 7, the lock plate 92 can swing between a first posture on the rotation direction R5 side drawn by a two-dot chain line and a second posture on the rotation direction R6 side drawn by a two-dot chain line. I have.
When the torsion coil spring 93 is stationary, the lock plate 92
Is rotated in the rotation direction R5 around the center of the bolt and moved to the position indicated by the two-dot chain line in FIG. In this state, the engaging portion 95 is connected to the outer peripheral gear 5 of the adjust ring 58.
8c radially outward. However, when the rotation speed increases and the centrifugal force increases, the lock plate 92 overcomes the biasing force of the torsion coil spring 93 and the bolt center C
2 turns to the rotation direction R6 side, and lock plate 92
Is moved radially outward. As a result, the engaging portion 95 moves radially inward and engages with the outer peripheral gear 58b. As a result, the rotation of the adjust ring 58 and the accompanying axial movement become impossible.

As described above, the wear compensation operation to be described later is performed only by the clutch release operation in the low rotation speed region when the engine is stopped or during idling. That is, for example, even if the clutch release operation is performed at or above the idling rotation speed, the wear compensation is not performed.
It is difficult for over-adjustment, which causes rotation, to occur.

Operation In the clutch connected state shown in FIG. 1, the lever member 45 applies a pressing force to the pressure plate 16.
At this time, the strap plate 41 applies an urging force in a direction to separate the pressure plate 16 from the clutch disk assembly 4. That is, the force obtained by subtracting the urging force from the pressing force acts on the clutch disk assembly 4 from the pressure plate 16. In this state, the fulcrum ring 59 and the roll pin 73 do not move in the axial direction.

Next, a description will be given of a wear compensation operation in the clutch cover assembly 5 when the clutch disk assembly 4 is worn. When the friction facing 4a of the clutch disk assembly 4 wears from the state of FIG. 1, the pressure plate 16 moves to the friction surface 11 side accordingly. At this time, the pressure plate 16 acts on the bolt 75 to move the nut 74 and the roll pin 73 toward the flywheel 2 with respect to the clutch cover 15 by the amount of wear. That is, the pressure plate 1
The force acting on the flywheel side with respect to 6 is set to be greater than the static friction force acting on the roll pin 73 from the clutch cover 15.

Next, a clutch release operation is performed. When the operator steps on the clutch pedal, the release fork 87 moves the release device 6 to the second position via the clutch operation mechanism.
Move in the axial direction. Specifically, the tip of the release fork 87 contacts the engaging portion 86 provided on the outer peripheral wall 85, and moves the entire release device 6 in the second axial direction. At this time, the inner peripheral ends of the diaphragm spring 44 and the lever member 45 are moved toward the second axial direction via the retainer 46. As a result, the pressing force acting on the pressure plate 16 from the lever member 45 is released, and the pressure plate 16 is moved in the second axial direction by the urging force from the strap plate 41.

The pressure plate 16 is a roll pin 7
No. 3 stops in contact with the first axial end face. At this time, the axial position of the pressure plate 16 is located on the first axial direction side by the amount of wear with respect to the release position before wear occurs. For this reason, when the release device 6 reaches the maximum release state, the radial inner end of the lever member 45 has an axial position, but the radial outer end is between the pressure plate 16 and the fulcrum ring 59. It becomes swingable in the axial direction.

In this state, when the rotation speed is high and the lock mechanism 90 is in the locked state, the adjusting ring 5
8 cannot rotate and move in the axial direction, so that the wear compensation operation is not performed. On the other hand, when the rotation speed is high and the lock mechanism 90 is in the unlocked state, the following wear compensation operation is performed. The adjust ring 58 is rotated in the rotation direction R1 by the action of the urging portion 60. At this time, the adjusting ring 58 moves in the first axial direction due to the engagement between the screw 58a and the screw 29a, and pushes the fulcrum ring 59 in the first axial direction. Fulcrum Ring 5
9 continues to move in the axial direction until the point of action 51 of the lever member 45 is supported by the pressure plate 16 and the fulcrum 52 is supported by the fulcrum ring 59.

As described above, by the wear compensation operation, the axial position of the fulcrum 52 of the lever member 45 is moved toward the first axial direction in accordance with the wear amount of the friction facing 4a.
As a result, the fulcrum 52 and the action point 51 of the lever member 45 move in the first axial direction in accordance with the amount of wear, so that the attitude of the lever member 45 changes but the axial position of the force point 50 changes. Not done, diaphragm spring 4
4 does not change, and the axial positions of the retainer 46, the sleeve 82, and the release bearing 84 do not change. That is, the axial gap and the clutch brake gap between the tip of the release fork 87 and the engaging portion 86 of the release device 6 have not changed.

When the wear compensation operation described above is performed, the swing plate 63 changes its posture from the first posture indicated by the solid line to the second posture. However, when the rotation speed of the engine increases, the swing plate 63 returns to the first posture side indicated by the solid line due to the centrifugal force. Since the swing plate 63 automatically returns to the initial rotation position side in this manner, the urging portion 60 can apply an urging force to the adjust ring 58 for a long period of time.

When the friction facing 4a wears out and is replaced, it is necessary to perform a resetting operation to return the adjuster ring 58 to the initial position in the axial direction. At that time, as shown in FIG.
Is pressed down to release the engagement between the ratchet teeth 63b and 64e, and the gear member 64 is rotated around the bolt in the rotation direction R4. As a result, the adjust ring 58 rotates in the rotation direction R2. At this time, the adjusting ring 58 is brought into the second position by the engagement between the screw 58a and the screw 29a.
Moves in the axial direction and returns to the initial position.

In this embodiment, at the time of wear compensation, the adjust ring 58 is axially moved by the screw structure by being rotated by the urging portion 60. Since the formation of the screw is easier than the conventional formation of a slope or the like, the processing is facilitated while maintaining the accuracy. In the present embodiment, the urging portion 60 and the lock mechanism 90 are engaged with the outer peripheral gear 58b of the adjust ring 58, so that the adjust ring 58 is rotated and prohibited from rotating. By having such a common portion, the total number of parts is reduced, and the structure is further simplified.

The number of parts can be reduced by integrally forming the urging portion and the lock mechanism. For example, by omitting the lock mechanism 90 and providing the urging portion 60 with an engaging portion similar to the engaging portion 95 of the lock mechanism 90 on the base end 63c side of the swing plate 63, the swing plate 63 is configured as shown in FIG. When it is at the solid line position, its engaging portion is
b, the rotation of the adjust ring 58 can be stopped. In summary, in the urging portion 60, the gear member 64 always applies a urging force to the adjust ring 58. At the initial position of the solid line of the swing plate 63, the engaging portion is the outer peripheral gear 5 of the adjust ring 58.
8b, the swing plate 63 is rotated in the rotation direction R3 by the torsion coil spring 62,
The engaging portion is separated from the outer peripheral gear 58b. Therefore, the gear member 64 drives the adjust ring 58 in the rotation direction R1. Subsequently, when the rotation speed of the engine becomes higher than a certain value, the swing plate 63 rotates in the rotation direction R4, and returns to the initial position indicated by the solid line. Therefore, the engaging portion engages with the outer peripheral gear 58b. Even in this state, even if the wear compensating operation can be performed, the adjusting ring 58 cannot be rotated by being locked by the swing plate 63. Second Embodiment A clutch device according to a second embodiment shown in FIGS. 12 to 16 has the same basic structure as the clutch device according to the first embodiment. Therefore, only different points will be described here.

A major difference from the above embodiment is that in this embodiment, the wear compensating mechanism 118 is
Fulcrum on the pressure plate 116 side (action point 51)
To adjust the axial position of the motor. Therefore, the urging mechanism 155 is provided not on the clutch cover 115 but on the pressure plate 116. Further, a lock mechanism 190 is also provided on the pressure plate 116.

The urging mechanism 155 is a mechanism for urging a fulcrum ring 158, which will be described later, toward the second axial direction, that is, the transmission side with a constant force. As shown in FIG. 13, the urging mechanism 55 mainly includes the fulcrum ring 1.
58 and an urging portion 160. The second axial side surface of the pressure plate 116 is the outer peripheral side surface 11.
6b and an inner peripheral side surface 116c. Outer side surface 11
Although 6b is close to the clutch cover 115, the inner peripheral side surface 116c is lower than the outer peripheral side surface 116b, and a predetermined gap is secured in the axial direction with the annular portion 126 of the clutch cover 115. A screw 116 d is formed on the inner peripheral surface of the pressure plate 116.

The fulcrum ring 158 is disposed near the inner peripheral portion of the pressure plate 116 in the second axial direction. The screw 11 of the pressure plate 116 is provided on the outer peripheral surface of the fulcrum ring 158 on the first axial side.
A screw 158a screwed to 6d is formed. Due to the threaded portion, the fulcrum ring 158 moves to the second axial direction, that is, the transmission side when rotated in the rotation direction R1 with respect to the pressure plate 116, and moves to the first direction when rotated in the rotation direction R2. It moves to the axial side, that is, the engine side.

The second outer peripheral surface of the fulcrum ring 158
An outer peripheral gear 158b is formed on the axial side portion. Each tooth of the outer peripheral gear 158b is arranged in the circumferential direction and extends in the axial direction. The fulcrum ring 158 has a support portion 158c for supporting the action point 51 of the lever member 45 on the second axial direction side. With this structure, when a load acts on the fulcrum ring 158 from the lever member 45, the load is transmitted to the pressure plate 116 via the threaded portion.

Next, the urging portion 160 will be described. The urging portion 160 rotates the fulcrum ring 158 in the rotation direction R1.
By applying a biasing force to the side, the pressure plate 1
This is a mechanism for urging the fulcrum ring 158 from the side 16 in the second axial direction. The urging portion 160 mainly includes a bolt 161 (support member) and the torsion coil spring 1.
62 (elastic member), a swing plate 163 (first member), and a gear member 164 (second member). The urging portion 160 is provided on the inner peripheral side surface 11 of the pressure plate 116.
6c.

The structure of the urging portion 160 is the same as that of the above embodiment. Therefore, the description is omitted here. FIG.
The lock mechanism 190 shown in FIG. 6 has a wear compensation mechanism 11 at a predetermined rotation speed (for example, the idling rotation speed of the engine) or more.
8, ie, a mechanism for stopping the operation of the urging mechanism 155. The lock mechanism 190 is a pressure plate 1
16 are provided on the inner peripheral side surface 116c. The structure of the lock mechanism 190 is the same as that of the above embodiment. Therefore, the description is omitted here.

Next, a description will be given of a wear compensation operation in the clutch cover assembly 5 when the clutch disk assembly 4 is worn. When the friction facing 4a of the clutch disk assembly 4 wears from the state of FIG. 12, the pressure plate 116 moves to the friction surface 11 side accordingly. At this time, the pressure plate 116
By acting on the bolt 75, the nut 74 and the roll pin 73 are attached to the flywheel 2 against the clutch cover 115.
To the side by the amount of wear. That is, the force acting on the flywheel side with respect to the pressure plate 116 is set to be larger than the static friction force acting on the roll pin 73 from the clutch cover 115.

Next, a clutch release operation is performed. When the operator steps on the clutch pedal, the release fork 87 moves the release device 6 to the second position via the clutch operation mechanism.
Move in the axial direction. Specifically, the tip of the release fork 87 contacts the engaging portion 86 provided on the outer peripheral wall 85, and moves the entire release device 6 in the second axial direction. At this time, the inner peripheral ends of the diaphragm spring 44 and the lever member 45 are moved toward the second axial direction via the retainer 46. As a result, the pressing force acting on the pressure plate 116 from the lever member 45 is released, and the pressure plate 116 is moved in the second axial direction by the urging force from the strap plate 41.

The pressure plate 116 comes into contact with the first axial end surface of the roll pin 73 and stops moving. At this time, the axial position of the pressure plate 116 is located on the first axial direction side by the amount of wear with respect to the release position before wear occurs. For this reason, when the release device 6 reaches the maximum release state, the radial inner end of the lever member 45 has an axial position defined, but the radial outer end is between the pressure plate 116 and the fulcrum ring 59. It becomes swingable in the axial direction.

In this state, when the rotation speed is high and the lock mechanism 190 is in the locked state, the fulcrum ring 158 cannot rotate and move in the axial direction, so that the wear compensation operation is not performed. On the other hand, when the rotation speed is high and the lock mechanism 190 is in the unlocked state, the following wear compensation operation is performed. The fulcrum ring 158 is rotated in the rotation direction R1 by the action of the urging portion 160. At this time, the fulcrum ring 158 moves in the second axial direction due to the screw engagement between the screw 158a and the screw 116d. The fulcrum ring 158 is connected to the lever member 45.
The axial movement continues until the point of action 51 is supported by the fulcrum ring 158 and the fulcrum 52 is supported by the clutch cover 115.

As described above, by the wear compensation operation, the fulcrum ring 158 is moved from the pressure plate 116 toward the second axial direction in accordance with the amount of wear. Therefore, the axial position of the action point 51 of the lever member 45 has returned to the initial position before wear. Therefore, the position / posture of the lever member 45 hardly changes. As a result, the attitude of the diaphragm spring 44 does not change, and the retainer 46, the sleeve 82, and the release bearing 8
The axial position of No. 4 has not changed. That is, the axial gap and the clutch brake gap between the tip of the release fork 87 and the engaging portion 86 of the release device 6 have not changed.

In the present embodiment, the change in the posture of the lever member 45 is smaller than in the first embodiment. In the present embodiment, there is no need to provide a special structure for accommodating the urging mechanism 155 of the wear compensation mechanism 118 on the clutch cover 115 side, so that the structure is simplified and the manufacturing cost is reduced. Further, in the present embodiment, machining of the clutch cover 115 is facilitated. [Modification] The present invention is not limited to the clutch device according to the present embodiment.

The present invention relates to a clutch device in which the clutch disk assembly is a single clutch device, a clutch device in which the pressing member includes only a spring such as a diaphragm spring, a clutch device in which the pressing member includes a lever member and another spring, and a flywheel in which the pressing member is a flywheel. It can also be applied to a clutch device or the like that performs clutch release by pushing to the side. Further, the presence or absence of the clutch brake is not limited.

Further, the configuration of the wear amount detecting mechanism is not limited to the above embodiment. For example, the friction engagement member may be engaged with a pressure plate.

[0068]

In the clutch cover assembly according to the present invention, the screw member is moved in the axial direction by being rotated by the urging portion during wear compensation. Since the formation of the screw is easier than the conventional formation of a slope or the like, the processing is facilitated while maintaining the accuracy.

[Brief description of the drawings]

FIG. 1 is a schematic longitudinal sectional view showing a clutch connection state before wear compensation of a clutch device employing a clutch cover assembly as a first embodiment of the present invention.

FIG. 2 is a schematic longitudinal sectional view showing a clutch connection state after wear compensation of the clutch device employing the clutch cover assembly as the first embodiment of the present invention.

FIG. 3 is a partially enlarged view of FIG. 1 and is a schematic partial longitudinal sectional view showing an urging mechanism of a wear compensation mechanism of a clutch cover assembly.

FIG. 4 is a schematic partial longitudinal sectional view showing a wear amount detection mechanism of a wear compensation mechanism.

FIG. 5 is a schematic partial longitudinal sectional view for explaining a relationship between a strap plate and a pressure plate.

FIG. 6 is a partial plan view for explaining an urging portion of the wear adjusting mechanism.

FIG. 7 is a partial cross-sectional view for explaining a resetting operation of the urging unit.

FIG. 8 is a partial side view showing a meshing state of the ratchet.

FIG. 9 is a partial side view showing a ratchet returning operation.

FIG. 10 is a schematic longitudinal sectional view for explaining a lock mechanism.

FIG. 11 is a plan view of a lock mechanism.

FIG. 12 is a schematic longitudinal sectional view showing a clutch connection state before wear compensation of a clutch device employing a clutch cover assembly as a second embodiment of the present invention.

FIG. 13 is a schematic longitudinal sectional view showing a clutch connection state after wear compensation of a clutch device employing a clutch cover assembly as a second embodiment of the present invention.

14 is a partially enlarged view of FIG. 12, and is a schematic partial longitudinal sectional view showing an urging mechanism of a wear compensation mechanism of the clutch cover assembly.

FIG. 15 is a plan view of an urging portion of the wear compensation mechanism.

FIG. 16 is a plan view of a lock mechanism.

[Brief description of reference numerals]

 DESCRIPTION OF SYMBOLS 1 Clutch device 2 Flywheel 4 Clutch disk assembly 5 Clutch cover assembly 6 Release device 15 Clutch cover 16 Pressure plate 17 Pressing mechanism 18 Wear compensation mechanism 55 Biasing mechanism 56 Wear detection mechanism 58 Adjust ring 59 Fulcrum ring 60 Biasing Department

Claims (7)

[Claims] 1. A clutch cover assembly mounted on a flywheel for connecting and disconnecting a friction member to and from the flywheel, comprising: a clutch cover that rotates integrally with the flywheel; A pressure plate that is arranged in such a manner as to rotate integrally with the clutch cover but is movable in the axial direction; a pressing member that applies a pressing force to the friction member side to the pressure plate; and a support portion that supports the pressing member. A wear compensating mechanism for moving the support portion to a wear compensating side in accordance with an amount of wear when the friction member is worn, wherein the wear compensating mechanism is engaged with the clutch cover by screw engagement. A screw member capable of moving the support position in the axial direction toward the wear compensation side, and an urging portion for urging the screw member in a rotational direction. To, the clutch cover assembly. 2. The clutch cover according to claim 1, wherein said urging portion has a gear member having a gear engaged with said screw member, and an elastic member for urging said gear member in a rotational direction thereof. Assembly. 3. The gear member according to claim 2, wherein the gear member includes a first member biased by the elastic member, and a second member having the gear engaged with the first member so as to be relatively non-rotatable. A clutch cover assembly as described. 4. The clutch cover assembly according to claim 3, wherein said first member can return to an initial rotation position side with respect to said second member. 5. The clutch cover assembly according to claim 4, wherein said first member can return to said initial rotation position side by centrifugal force when exceeding a predetermined number of rotations. 6. The elastic member according to claim 3, wherein the elastic member urges the first member in a rotational direction and urges the first member and the second member to each other in an axial direction. 4. The clutch cover assembly according to claim 1. 7. The urging portion penetrates the first member and the second member in the axial direction so as to be rotatable relative to each other and movable within a limited range in the axial direction. The clutch cover assembly according to any one of claims 3 to 6, further comprising a support member for supporting the clutch cover.