JP2001304289A - Clutch cover assembly - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the number of parts on an abrasion compensating mechanism to compensate abrasion of a friction member by moving a support member on the side of a clutch cover. SOLUTION: The abrasion compensating mechanism 18 of a clutch cover assembly 5 is provided on the clutch cover 15 and supports a lever member 45. The abrasion compensating mechanism 18 is a mechanism to move a supporting position of the lever member 45 to the side of a friction facing 4a when the friction facing 4a is abrased. The abrasion compensating mechanism 18 has a first inclined part 58 extending in the rotating direction which is integrally formed on a surface on the side of the friction facing 4a of the clutch cover 15, an adjust ring 59 having a second inclined part to complementarily make contact with the first inclined part 58 and arranged free to move and rotate in the axial direction against the clutch cover 15 and an adjust spring 61 to energize the adjust ring 59 in the rotating direction against the clutch cover 15 so that the adjust ring 59 is separated in the axial direction from the clutch cover 15.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention provides a clutch cover assembly, particularly a wear compensating mechanism which can move a fulcrum of a pressing member toward a friction member in accordance with an amount of wear when the friction member is worn. A clutch 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, it is necessary to return the posture of a spring such as a diaphragm spring to an initial state when the friction member is worn. 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 for moving 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 has been 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]

In the wear compensation mechanism of the conventional clutch cover assembly, the use of two ring members increases the number of parts and complicates the structure. An object of the present invention is to reduce the number of parts in a wear compensation mechanism that compensates for wear of a friction member by moving a support member on the clutch cover side.

[0007]

According to a first aspect of the present invention, there is provided a clutch cover assembly mounted on a flywheel for connecting and disconnecting a friction member to and from the flywheel. It has 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 friction member side to the pressure plate. The wear compensation mechanism is provided on the clutch cover and supports the pressing member. The wear compensation mechanism is a mechanism for moving the support position of the pressing member toward the friction member when the friction member wears. The wear compensation mechanism has a first inclined surface integrally formed on the friction member side surface of the clutch cover and extending in the rotational direction, and a second inclined surface complementary to the first inclined surface. A first ring member disposed so as to be axially movable and rotatable with respect to the clutch cover;
An elastic member for urging the ring member in the rotational direction with respect to the clutch cover.

In this clutch cover assembly, when the friction member wears, the wear compensation mechanism moves the support position of the pressing member toward the friction member. At this time, the wear compensation operation
This is performed by moving the first ring member in the axial direction while rotating with respect to the clutch cover. In this clutch cover assembly, one of the inclined surfaces of the wedge mechanism is formed integrally with the clutch cover, so that the total number of parts is reduced.

[0009] In the clutch cover assembly according to the second aspect, in the first aspect, the wear compensation mechanism further includes a second ring member. The second ring member is arranged in contact with the friction member side of the first ring member, and is engaged with the clutch cover so as to be relatively non-rotatable and movable in the axial direction. The second ring member has a support for supporting the pressing member.

In this clutch cover assembly, when the first ring member moves in the axial direction while rotating with respect to the clutch cover in the wear compensation operation, the second ring member does not rotate with respect to the clutch cover but moves in the axial direction. Move. As described above, since the second ring member does not rotate with respect to the clutch cover, the support portion supporting the pressing member does not move in the rotation direction.

According to a third aspect of the present invention, in the clutch cover assembly according to the second aspect, the elastic member functions between the first ring member and the second ring member. In this clutch cover assembly, since the first ring member and the second ring member do not move relative to each other in the axial direction, the posture of the elastic member functioning therebetween is stable. In the clutch cover assembly according to a fourth aspect, in the third aspect, the elastic member is disposed in a space formed between the first ring member and the second ring member.

In this clutch cover assembly, space is saved by disposing the elastic member between the first ring member and the second ring member.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Structure FIGS. 1 and 2 show a basic structure of a clutch device 1 to which an embodiment of the present invention can be applied. 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. The O shown in FIG.
-O is the rotation axis of the clutch device 1, and the lower side in FIG. 1 is the first axial direction (engine side), and the upper side in FIG. 1 is the second axial direction side (transmission side). 4 and 6
Is the rotation direction of the clutch device 1, and the arrow R2 direction is the opposite direction. The position and posture of each member in FIG. 1 are in a state in which the clutch device 1 is connected at a stage where the clutch disk assembly 4 is not worn, and the position and posture of each member in FIG. The state where the clutch device 1 is connected at the stage when the wear of No. 4 has progressed. Further, since the transmission in which the clutch device 1 is provided does not have a synchronization mechanism, the clutch brake 7
(Described later) are 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, on the inner peripheral side of the cylindrical portion 23 of the clutch cover 15, that is, on the first axial direction side of the annular portion 26, a biasing mechanism 55 of the wear compensating mechanism 18 described later is accommodated. Is formed. Annular part 2
An annular protrusion 30 is formed at an inner peripheral end of the second protrusion 6 in the first axial direction. An annular groove 32 is formed between the cylindrical portion 23 and the annular protrusion 30.

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 toward the second axial direction from other portions.

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 a 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 60. 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 pressure plate 16 and a clutch cover 15, particularly,
9 and is disposed axially. A second axial side surface of the outer peripheral portion of the lever member 45 is a fulcrum ring 6 described later.
0 supported. 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 arranged on the second axial direction side of the lever member 45 and is spaced apart in the axial direction.
The second axial side surface of the outer peripheral portion of the diaphragm spring 44 is supported by the annular projecting portion 30 in the clutch cover 15, particularly in the housing portion 29. Diaphragm spring 44
Has an inner peripheral end 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 at which a force from the retainer 46 to the first axial direction acts, an action point 51 at which a force can be applied to the pressure plate 16, and a fulcrum 52 supported at the clutch cover 15 side. have. Each point 50,
Actually, 51 and 52 are linear portions formed in an arc shape or an annular shape around the central axis O. The point of action 51 is the lever member 45
Is a portion protruding in the first axial direction, and is in contact with the support portion 39 of the pressure plate 16. Fulcrum 5
Reference numeral 2 denotes a portion of the lever member 45 protruding in the second axial direction, which is in contact with the annular support portion 40 formed on the first axial side surface of the fulcrum ring 60. In addition,
At the fulcrum 52, a plurality of holes 52a are formed in the circumferential direction, and the projections 40a extending from the support portion 40 of the fulcrum ring 60 are inserted into the holes 52a. As a result, the lever member 45 rotates integrally with the clutch cover 15. Let L be the radial distance from the power point 50 to the fulcrum 52.
1, the radial distance from the force point 50 to the action point 51 is L2, and the radial distance from the action point 51 to the fulcrum 52 is L3. Thereby, the diaphragm spring 4
4 to the lever member 45 is L2 / L.
The power is multiplied by three and transmitted to the pressure plate 16.

Next, the wear compensation mechanism 18 will be described. The wear compensating mechanism 18 shown in detail in FIG. 3 restores the axial height of the tip of the lever member 45, that is, the force point 50, which is the inner peripheral end, to the initial position after the friction facing 4a of the clutch disk assembly 4 is worn. The purpose is to keep the clutch brake gap constant by keeping the release bearing 84 at a constant axial position. Therefore, when the friction facing 4a of the clutch disk assembly 4 is worn out, the wear compensating mechanism 18 moves the clutch cover side fulcrum 52 of the lever member 45 at the next clutch release according to the wear.
It is designed to be moved to the a side.

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 later-described fulcrum ring 60 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 allows the pressure plate 16 to move in the second axial direction side in the next release according to the wear amount, thereby providing an urging mechanism. 55 is a mechanism for enabling the fulcrum ring 60 to move in the axial direction.

The urging mechanism 55 is disposed in the housing 29 of the clutch cover 15. The urging mechanism 55 mainly includes a plurality of first inclined portions 58 formed on the clutch cover 15.
, Adjust ring 59 and fulcrum ring 60
And an adjustment spring 61.
The adjust ring 59 (first ring) is disposed on the first axial direction side of the clutch cover 15, and
0 (second ring) is arranged on the first axial direction side of the adjust ring 59. Each member is in contact with each other in the axial direction. The bottom surface of the groove 32 of the clutch cover 15 (the first axial side surface of the annular portion 26), both axial side surfaces of the adjust ring 59, and the second axial side surface of the fulcrum ring 60 are aligned with the rotation axis O of the clutch device 1. The plane is perpendicular to -O.

The plurality of first inclined portions 58 are formed integrally with the clutch cover 15 in the grooves 32,
At a radially intermediate portion of the groove 32, the groove 32 extends with a predetermined length in the circumferential direction. As shown in FIG. 4, each of the first inclined portions 58 is inclined such that the height in the axial direction increases from the rotation direction R2 toward the rotation direction R1. In this manner, each of the first inclined portions 58 has the inclined surface 5 facing the first axial direction side.
8a. In this structure, since one of the inclined surfaces forming the wedge mechanism is formed integrally with the clutch cover 15, the number of components constituting the urging mechanism 55 is reduced.

The adjust ring 59 is arranged in contact with the bottom surface of the groove 32. The adjust ring 59 has an outer peripheral surface supported by the inner peripheral surface of the tubular portion 23, and an inner peripheral surface supported by the outer peripheral surface of the annular projection 30. Adjustable 5
9, a plurality of second inclined portions 63 are formed on the second axial side surface so as to correspond to the first inclined portions 58. Specifically, a concave portion 57 is formed at a portion corresponding to the first inclined portion 58 on the second axial side surface of the adjust ring 59, and the bottom surface of the concave portion 57 is a second inclined portion 63. . The first inclined portion 58 is inserted into the concave portion 57, and the inclined surface 58a is
It is in contact with the inclined surface 63a of the inclined portion 63. That is, the first inclined portion 58 of the clutch cover 15 and the second inclined portion 63 of the adjust ring 59 form a wedge mechanism.

The outer teeth 65 are formed on the outer peripheral surface of the adjust ring 59. The outer peripheral teeth 65 are arranged in the rotation direction, and each of them extends in the axial direction. A plurality of grooves 66 extending long in the rotation direction are formed on the first axial side surface of the adjust ring 59. The adjusting spring 61 is accommodated in the groove 66. A spring engaging portion 66a is provided at an end of the groove 66 on the rotation direction R2 side.

The fulcrum rings 60 are arranged on the adjuster ring 59 on the first axial side so as to abut against each other. The adjust ring 59 and the fulcrum ring 60 are relatively rotatable. Fulcrum Ring 60
The outer peripheral surface 68 is formed with outer peripheral teeth 68. Outer teeth 6
Numerals 8 are arranged in the rotation direction, and each of them extends in the axial direction. The outer peripheral teeth 68 are provided on the cylindrical portion 23 of the clutch cover 15.
Are engaged with a plurality of inner peripheral teeth 23a formed on the inner peripheral surface so as to be relatively non-rotatable and axially movable.

On the second axial side surface of the fulcrum ring 60, a spring engaging portion 69 extending into the groove 66 of the adjust ring 59 is formed. The spring engagement portion 69 is located at the end in the rotation direction R1 in the groove 66. The adjusting spring 61 extends in the rotation direction in the groove 66 and rotates in the rotation direction R.
The two-side end is locked by the spring engaging portion 66a of the adjust ring 59, and the end in the rotation direction R1 is locked by the engaging portion 69 of the fulcrum ring 60. Adjust spring 6
Reference numeral 1 denotes a tension coil spring which rotates the adjust ring 59 with respect to the fulcrum ring 60 in the rotation direction R.
It is biased to one side. Due to the axial component of the force acting on the second inclined portion 63 of the adjusting ring 59 from the first inclined portion 58 of the adjusting ring 59 by being biased by the adjusting spring 61, the adjusting ring 59 is always moved in the first axial direction. Being energized. Thus, the adjusting spring 61 functions between the adjusting ring 59 and the fulcrum ring 60. Since the adjusting ring 59 and the fulcrum ring 60 do not move relative to each other in the axial direction, the adjusting spring 61 functioning between them has a stable posture. In other words, the adjusting spring 61 is less likely to cause problems such as deformation and breakage due to inclination even when the wear compensation operation proceeds. The adjusting spring 61 is disposed between the two members, and is not disposed between the adjusting ring 59 and the clutch cover 15. Therefore, the number and area of the first and second inclined portions 58 and 63 can be increased, and the space can be further reduced. The adjusting spring may be a compression spring.

The wear amount detecting mechanism 56 is a mechanism for permitting the movement of the pressure plate 16 in the second axial direction in accordance with the amount of wear when the clutch disk assembly 4 is worn out during the subsequent release. . In this embodiment, the wear amount detecting mechanism 56 includes, for example, two sets of mechanisms provided at positions facing each other in the radial direction. Each set includes a roll pin 73, a nut 74, and a bolt 75. The roll pin 73 is inserted into an axial hole 24 a formed in the flat portion 24 of the clutch cover 15. Roll pin 7
Reference numeral 3 denotes a spring member having a slit formed in the axial direction, which elastically abuts against the wall surface of the axial hole 24a. Thus, the roll pin 73 is frictionally engaged so as not to move in the axial direction until a predetermined amount of force acts on the clutch cover 15. 3, a predetermined axial gap is formed between the first axial end face of the roll pin 73 and the second axial face 38 of the pressure plate 16. In FIG. This axial gap is the amount by which the pressure plate 16 can move toward the second axial direction when the clutch is released (the cutoff 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.
, It is possible to approach in the axial direction, but it is impossible to move away from it. As a result, when the pressure plate 16 moves from the state shown in FIG. 3 to the second axial direction side, a resistance force acts from the bolt 75, but when the pressure plate 16 moves to the first axial direction side, the pressure plate 16 abuts against the roll pin 73. 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. 5 and 6 is a mechanism for stopping 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. The 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 member 92, and a torsion spring 93. The bolt 91 is screwed into the flat portion 25 from the second axial direction side. However, the head 91 of the bolt 91
a is disposed axially away from the second axial side surface of the flat portion 25. As is apparent from FIG. 6, the lock member 92 is a substantially rectangular plate in plan view. The lock member 92 is rotatable around its center by a bolt 91. The hole through which the body 91b of the bolt 91 penetrates in the lock member 92 is shifted toward the rotation direction R2. That is, the portion of the lock member 92 on the rotation direction R1 side with respect to the bolt 91 is longer than the portion on the rotation direction R2 side. The torsion spring 93 is a member that applies a force to rotate the lock member 92 counterclockwise in FIG. 6 with respect to the center of the bolt. The coil portion 93a of the torsion spring 93 is formed around the body 91b of the bolt 91 by the locking member 92 and the flat portion 2.
5 is arranged. Also, the coil part 93a
It also acts as a compression spring, and urges the lock member 92 against the head 91a of the bolt 91. The first arm 93b of the torsion spring 93 is inserted into a hole formed in the clutch cover 15. The second arm 93c of the torsion spring 93 is connected to the rotation direction R of the lock member 92.
It is in contact with the clockwise side surface in the rotation direction of one side portion. In this manner, when the torsion spring 93 is stationary, the torsion spring 93 is locked.
2 is rotated around the center of the bolt and moved to the position indicated by the two-dot chain line in FIG.

An engaging portion 95 that can engage with the outer teeth 65 of the adjust ring 59 is formed radially inward of the end of the lock member 92 in the rotation direction R2. At the position indicated by the two-dot line, the engaging portion 95 is located radially outward from the outer peripheral teeth 65. However, when the rotation speed increases and the centrifugal force increases, the rotation direction R1 side portion of the lock member 92 moves outward in the radial direction, and as a result, the lock member 92 overcomes the urging force of the torsion spring 93 and rotates around the bolt center. Rotate clockwise. As a result, the engaging portion 95 moves radially inward and engages with the outer peripheral teeth 65. As a result, the rotation of the adjust ring 59 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 turning point range such as 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 rotational speed, the wear compensation is not performed, and thus the adjust ring 59 is unnecessarily increased due to vibration or shock during the clutch release operation in the high rotational speed region.
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 60 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 defined, but the radial outer end is between the pressure plate 16 and the fulcrum ring 60. 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
9 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 59 is rotated in the rotational direction R1 with respect to the clutch cover 15 and the fulcrum ring 60 by the biasing force of the adjust spring 61. The adjust ring 59 moves toward the first axial direction due to the axial component of the force acting on the inclined surface 63a of the second inclined portion 63 from the inclined surface 58a of the first inclined portion 58. As a result, the adjust ring 59 pushes the fulcrum ring 60 toward the first axial direction. Fulcrum Ring 60
Keeps moving 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 60.

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. [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 comprises only a spring such as a diaphragm spring, a clutch device in which the pressing member comprises 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.

[0052]

In the clutch cover assembly according to the present invention, the number of parts is reduced because one of the inclined surfaces forming the wedge mechanism is formed integrally with the clutch cover.

[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 an embodiment of the present invention.

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

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

FIG. 4 is a schematic diagram for explaining the structure of a wedge mechanism including two types of inclined surfaces in the wear compensation mechanism.

FIG. 5 is a schematic longitudinal sectional view for explaining a lock mechanism.

FIG. 6 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 59 Adjust ring 60 Fulcrum ring 61 Adjust spring

Claims (4)

[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, which is arranged integrally with the clutch cover but is movable in the axial direction, a pressing member for applying a pressing force to the friction member side to the pressure plate, and the pressing provided on the clutch cover. And a wear compensation mechanism for moving a support position of the pressing member to the friction member side when the friction member wears, wherein the wear compensation mechanism is provided on the friction member side of the clutch cover. A first inclined surface integrally formed on the surface and extending in the rotational direction, and abutting complementarily on the first inclined surface; A first ring member having two inclined surfaces and axially movable and rotatable with respect to the clutch cover, and the first ring member so that the first ring member is axially separated from the clutch cover. An elastic member for urging the clutch cover in a rotational direction with respect to the clutch cover. 2. The wear compensation mechanism further includes a second ring member, wherein the second ring member is disposed in contact with the friction member side of the first ring member, and rotates relative to the clutch cover. 2. The clutch cover assembly according to claim 1, further comprising a support portion that is immovably and axially movably engaged and supports the pressing member. 3. 3. The clutch cover assembly according to claim 2, wherein said elastic member functions between said first ring member and said second ring member. 4. The clutch cover assembly according to claim 3, wherein said elastic member is disposed in a space formed between said first ring member and said second ring member.