JP3389457B2 - Clutch cover assembly - Google Patents

Description

Detailed Description of the Invention

[0001]

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

[0002]

2. Description of the Related Art A clutch cover assembly of a clutch device is mounted on a flywheel of an engine, and the frictional facing of a clutch disc assembly is pressed against the flywheel by utilizing the spring force of a diaphragm spring.
The driving force of the engine is transmitted to the transmission side.
In such a clutch device, when the wear amount of the friction facing exceeds a certain level, the friction facing wears down and becomes unusable, or the posture of the diaphragm spring of the clutch cover changes and the pressing load changes. Therefore, it becomes necessary to replace the clutch disc assembly. It has been conventionally required to extend the replacement period, that is, to prolong the life of the clutch.

In order to achieve a long clutch life,
In a clutch disc assembly, it is important to increase the effective thickness of friction facings. Therefore, a method of fixing the friction facing to the cushioning plate without using a rivet or the like is used. In the clutch cover assembly, it is necessary to return the posture of the diaphragm spring to the initial state when the friction facing is worn. Therefore, the wear amount of the friction facing is detected, and a member (a fulcrum ring on the pressure plate side or a support mechanism on the clutch cover side) that supports the diaphragm spring is moved according to the wear amount. This maximizes the friction facing of the clutch disc assembly.

In the clutch cover assembly disclosed in Japanese Unexamined Patent Publication No. 6-42553, the wear-following mechanism mainly includes a fulcrum ring arranged between the clutch cover and the diaphragm spring, and a direction in which the fulcrum ring is separated from the pressure plate. The urging mechanism that urges the fulcrum ring and the regulation mechanism that prevents the fulcrum ring from moving away from the pressure plate and allows the fulcrum ring to move axially from the pressure plate by the amount of wear when the friction facing wears. have.

The regulating mechanism shown in FIG. 7 of JP-A-6-42553 is housed inside the pressure plate. Specifically, a hole is formed in the pressure plate on the side opposite to the friction surface, a friction bush is arranged in the hole, and a wear sensor member is arranged inside the bush. The wear sensor member frictionally engages the friction bush and immovably engages the friction facing side with respect to the clutch cover, and further limits the movement of the fulcrum ring toward the clutch cover side.

When abrasion occurs in the friction facing, the pressure plate moves, and relative movement occurs between the pressure plate and the wear sensor member engaged with the clutch cover. As a result, a gap corresponding to the amount of wear is formed between the wear sensor member and the fulcrum ring. Next, when the release operation is performed, the fulcrum ring is urged by the urging mechanism and moves until it comes into contact with the sensor member. As a result, the posture of the diaphragm spring becomes the same as when it is not worn.

[0007]

In the above-mentioned conventional wear following mechanism, the friction engagement portion between the friction sensor member and the friction bush is arranged inside the pressure plate. Therefore, the friction engagement portion is easily affected by the heat transmitted from the friction surface of the pressure plate. As a result, the sliding resistance generated at the friction engagement portion is difficult to stabilize.

An object of the present invention is to stabilize the sliding resistance of a friction engagement portion in a wear follow-up mechanism of a clutch cover assembly for a long period of time.

[0009]

According to a first aspect of the present invention, there is provided a clutch cover assembly for urging a friction facing of a clutch disc assembly toward a flywheel to connect a clutch. It is provided with a plate, a fulcrum ring, a pressing member, a biasing mechanism, and a regulating mechanism. The clutch cover is fixed to the flywheel and has a facing portion facing the friction facing. The pressure plate is disposed between the friction facing and the facing portion in proximity to the friction facing, and has a first side surface on the friction facing side and a second side surface on the facing portion side.
With sides. The fulcrum ring is arranged to face the second side surface of the pressure plate. The pressing member is supported by the clutch cover and applies a pressing force to the pressure plate side to the fulcrum ring. The urging mechanism is arranged between the pressure plate and the fulcrum ring and applies an urging force to the fulcrum ring in a direction away from the pressure plate in the axial direction. The regulation mechanism prohibits the fulcrum ring from moving in the axial direction when there is no wear in the friction facing, detects the amount of wear when the friction facing faces wear, and prevents the fulcrum ring from moving in the axial direction according to the amount of wear. It is a mechanism for forgiveness. The wear amount detection mechanism includes a first member and a second member. The first member is fixed to the second side surface of the pressure plate and extends in the axial direction. The second member is frictionally locked to the first member so as to be movable in the axial direction with respect to the first member when a load larger than a predetermined value is applied, and can abut against the clutch cover from the side opposite to the friction facing side. Has an abutting part,
Limit the movement of the fulcrum ring away from the pressure plate. The second member has one end
It is in contact with the surface of the clam ring on the opposite side.

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

When the friction facing is worn when the clutch is engaged, the pressure plate and the fulcrum ring move to the friction facing side by the wear amount. At this time, the second member of the restricting mechanism has the contact portion in contact with the clutch cover, and relative movement occurs between the second member and the pressure plate. That is, the second member slides in the axial direction with respect to the first member, and a gap corresponding to the amount of wear is formed between the fulcrum ring and the second member. Next, when the clutch release operation is performed, the fulcrum ring moves in the direction away from the pressure plate until it comes into contact with the second member to stop the movement in the axial direction. When the clutch release operation is further continued, the pressure plate separates from the friction facing and the clutch connection is released. Next, when the clutch is engaged, the posture of the pressing member is returned to the initial state, and the initial pressing load is applied to the pressure plate and the fulcrum ring. In the structure described above, since the first member and the second member of the regulation mechanism are provided on the second side surface side of the pressure plate, these members are less likely to be adversely affected by the heat generated on the first side surface of the pressure plate. . As a result, the sliding resistance generated between the first member and the second member is stable for a long period of time.

A clutch cover assembly according to a second aspect of the present invention is the clutch cover assembly according to the first aspect, wherein the first member is rod-shaped, and the second member is formed with slits and is tightly fitted around the outer periphery of the first member. Consists of. The second member is easily bent and deformed, and sliding resistance generated between the second member and the first member is stable .

According to a third aspect of the present invention, in the clutch cover assembly according to the second aspect , a first axial hole is formed in the facing portion of the clutch cover, and the fulcrum ring corresponds to the first axial hole. A second axial hole is formed. One end of the first member is detachably fixed to the second side surface of the pressure plate, and is disposed in the first and second axial holes. The second member is first in the first axial bore.
The contact portion is tightly fitted to the outer periphery of the member, and the contact portion that contacts the surface of the clutch cover facing portion opposite to the friction facing side is formed at the other end.

According to the clutch cover assembly of the third aspect , in the second aspect, the first member and the second member can be easily attached and detached from other parts of the clutch cover assembly. Specifically, with the second member assembled to the first member, the first axial direction hole and the second axial direction hole are passed from the outside, and one end of the first member is fixed to the pressure plate. Reverse the operation when removing. In this way, the regulation mechanism is completed by winding the second member around the first member before attaching it to the clutch cover assembly. That is, the sliding resistance of the friction engagement portion can be set outside the clutch cover assembly. Therefore, it is easy to set the sliding resistance.

A clutch cover assembly according to a fourth aspect of the present invention is the clutch cover assembly according to the third aspect, wherein the other end of the first member is formed with a head having a diameter larger than that of a portion passing through the first axial hole.
The head is axially separated from the contact portion by a predetermined distance. As the friction facing wears and the wear is adjusted, the axial distance between the head portion of the first member and the contact portion of the second member becomes shorter. Since this axial distance can be observed from the outside of the clutch cover assembly, the operator can easily determine when to replace the clutch cover assembly.

A clutch cover assembly according to a fifth aspect of the present invention is the clutch cover assembly according to the third or fourth aspect, wherein the fulcrum ring has a protruding portion formed integrally with the annular portion and protruding radially outward from the annular portion. A second axial hole is formed in the protrusion. A clutch cover assembly according to a sixth aspect is the clutch cover assembly according to any one of the first to fifth aspects, further including a plate-like elastic member having one end fixed to the clutch cover and the other end fixed to the fulcrum ring. Since the fulcrum ring, not the pressure plate, is connected to the clutch cover so as not to rotate relative to the clutch cover, the posture of the plate-like elastic member does not change even if abrasion occurs and is kept constant. As a result, the biasing force from the plate-like elastic member becomes constant. This is because, unlike the pressure plate, the fulcrum ring does not change its axial position with respect to the flywheel and the clutch cover even if the clutch disc wears.

A clutch cover assembly according to a seventh aspect of the present invention is the clutch cover assembly according to any one of the first to sixth aspects, wherein the biasing mechanism has inclined surfaces arranged between the pressure plate and the fulcrum ring and extending in the circumferential direction. It has a pair of abutting wedge mechanisms and a biasing member that biases the pair of wedge mechanisms in the circumferential direction to bias the fulcrum ring axially away from the pressure plate. .

A clutch cover assembly according to an eighth aspect of the present invention is the clutch cover assembly according to any one of the first to sixth aspects, wherein the biasing mechanism is the first.
It has an annular member, a second annular member, and a biasing member. The first annular member is fixed to the surface of the annular portion of the fulcrum ring on the pressure plate side and has a plurality of first inclined surfaces. The second annular member has a plurality of second inclined surfaces rotatably arranged on the second side surface of the pressure plate and abutting the plurality of first inclined surfaces. The urging member urges the second annular member toward the first annular member in the circumferential direction to urge the second inclined surface toward the first inclined surface, thereby axially connecting the first annular member and the fulcrum ring. Try to move in the direction. Since the first and second annular members integrally having the plurality of inclined surfaces are provided, the axial movement amount of the first annular member and the fulcrum ring becomes constant in the circumferential direction.

A clutch cover assembly according to a ninth aspect is the clutch cover assembly according to any one of the first to fifth aspects, wherein the fulcrum ring is coupled to the clutch cover so as to elastically and integrally rotate in the axial direction. Is further equipped. The fulcrum ring is engaged with the first member so as to be movable in the axial direction and immovable in the circumferential direction . Since the fulcrum ring is connected to the clutch cover so that it cannot rotate relative to the clutch cover, the attitude of the connecting member does not change even if wear occurs and is kept constant. As a result, the urging force from the connecting member to the fulcrum ring becomes constant. This is because, unlike the pressure plate, the fulcrum ring does not change its axial position with respect to the flywheel and the clutch cover even when the clutch disc is worn.

The fulcrum ring rotates integrally with the clutch cover by the connecting member. The torque of the fulcrum ring is transmitted to the pressure plate via the first member. Since the torque is transmitted from the fulcrum ring to the pressure plate using the first member constituting the regulation mechanism as described above, the number of parts is small and the cost is low. The clutch cover assembly according to claim 1 0, claims 3 to
5 is further provided with a connecting member that connects the fulcrum ring to the clutch cover so as to elastically and integrally rotate in the axial direction. The first member is engaged with the second axial hole of the fulcrum ring so as to be movable in the axial direction and immovable in the circumferential direction.

Since the fulcrum ring, rather than the pressure plate, is connected to the clutch cover so that it cannot rotate relative to the clutch cover, the attitude of the connecting member does not change even if wear occurs and is kept constant. As a result, the urging force from the connecting member to the fulcrum ring becomes constant. This is because, unlike the pressure plate, the fulcrum ring does not change its axial position with respect to the flywheel and the clutch cover even when the clutch disc is worn.

The fulcrum ring rotates integrally with the clutch cover by the connecting member. The torque of the fulcrum ring is transmitted to the pressure plate via the first member. Since the torque is transmitted from the fulcrum ring to the pressure plate using the first member constituting the regulation mechanism as described above, the number of parts is small and the cost is low.

[0023]

BEST MODE FOR CARRYING OUT THE INVENTION First Embodiment Configuration FIGS. 1 to 3 show a clutch cover assembly 1 in which an embodiment of the present invention is adopted. The clutch cover assembly 1 is used in vehicles, especially large vehicles such as trucks. The clutch cover assembly 1 is a device for transmitting or blocking the torque transmitted from the flywheel 2 of the engine to the clutch disc assembly 3, and is attached to the flywheel 2. In this clutch device, two clutch disc assemblies 3 are provided, and an intermediate plate 5 is arranged between the friction discs 4 of both clutch disc assemblies 3. The present invention can also be applied to a clutch device provided with only one clutch disc assembly.

The clutch disc assembly 3 is mainly composed of a friction disc 4 and a hub 7 connected to the friction disc 4 via a coil spring 6. The friction disc 4 is a disc-shaped plate 9
It is composed of a plurality of friction plates 8 which are fixed on both sides of the outer peripheral portion of the. Each friction plate 8 is composed of a core plate 10 fixed to a disc-shaped plate 9 with rivets 12 and a friction facing 11 fixed to the core plate 10. In this embodiment, the friction facing 11 is made of a ceramic metal sintered material.

The R ₁ direction in FIG. 1 is the rotational direction of the clutch, and the R ₂ direction is the second support plate 3 described later.
2 is the rotation direction during wear adjustment. 2 and 3
An engine (not shown) is arranged on the left side of and a transmission (not shown) is arranged on the right side. The clutch cover assembly 1 mainly includes a clutch cover 21 and
Pressure plate 22 and fulcrum ring 23
The biasing mechanism 24, the regulating mechanism 25, the clutch pressing mechanism 27, the drive mechanism 26, and the release device 28.

The clutch cover 21 is a flywheel 2
It is a dish-shaped member that can be attached to. The clutch cover 21 has an outer peripheral cover portion 21 a that covers the outer peripheral side of the clutch disc assembly 3, and a disc-shaped portion 21 b that faces the transmission side of the clutch disc assembly 3. Further, an annular facing portion 21c that axially faces the friction disc 4 is formed on the outer peripheral portion of the disc-shaped portion 21b. In the facing portion 21c (that is, the outer peripheral portion of the disc-shaped portion 21b), four first axial holes 21d are formed at equal intervals in the circumferential direction. Also,
On the transmission side of the first axial hole 21d, the first
A recess 21e having a diameter larger than that of the axial hole 21d is formed.

The pressure plate 22 is arranged inside the outer peripheral cover portion 21a of the clutch cover 21, and the friction disk 4 and the facing portion 21 of the clutch cover 21.
It is arranged close to the friction disc 4 with respect to c. The pressure plate 22 is an annular member, and is made of cast iron or the like. The pressure plate 22 has a friction surface 22 facing the friction disc 4.
a (first side surface) and second side surface 2 facing the facing portion 21c
2b and. Second of the pressure plate 22
On the side surface 22b, a groove 22c extending annularly on the inner peripheral side
Are formed. A biasing mechanism 24, which will be described later, is provided in the groove 22c. Furthermore, the pressure plate 2
4 on the outer peripheral portion of the second side surface 22b on the second side at equal intervals in the circumferential direction.
An engagement recess 22d recessed from the second side surface 22b is formed at the location. Further, a screw hole 22e is formed on the R ₂ direction side of each engagement recess 22d.

The fulcrum ring 23 is arranged on the second side surface 22b side of the pressure plate 21. The fulcrum ring 23 is a member that receives a load from the lever member 46 and moves together with the pressure plate 22 toward the flywheel 2 side. The fulcrum ring 23 includes an annular portion 23a and three protruding portions 23b that extend radially outward from the annular portion 23a. The annular portion 23 a is the groove 2 of the pressure plate 22.
It is arranged so as to face 2c at a predetermined interval in the axial direction. The protruding portion 23b is in contact with the second side surface 22b of the pressure plate 21. As is apparent from FIG. 1, the protruding portion 23b extends in the circumferential direction by a predetermined angle, a second axial hole 23c is formed on the R ₂ side, and a third axial hole is formed on the R ₁ side. 23d is formed. The second axial hole 23c and the third axial hole 23d are
The screw hole 22e of the pressure plate 22 and the engaging recess 2
2d respectively. Also, the second axial hole 23
c corresponds to the first axial hole 21d and has a smaller diameter than the first axial hole 21d.

The fulcrum ring 23 and the pressure plate 22 rotate integrally with the clutch cover 21, that is, the flywheel 2 by the drive mechanism 26. The drive mechanisms 26 are provided at four locations side by side in the circumferential direction, and each of them has a strap plate 42, a bolt 43, and a block 4
4 and. The strap plate 42 is
It is a member for connecting the fulcrum ring 23 to the clutch cover 21 so as to be non-rotatable and axially movable. The strap plate 42 is a plate-shaped elastic member formed by stacking three plate members and extending in the circumferential direction (generally tangential direction). The end of the strap plate 42 in the R ₁ direction is fixed to the clutch cover 21. Strap plate 42
The R ₂ -direction end of is fixed to the fulcrum ring 23 by a bolt 43. The bolt 43 passes through the third axial hole 23d of the fulcrum ring 23 and its tip is screwed into the block 44. The R ₂ direction end of the strap plate 42 is sandwiched between the protruding portion 23 b and the head of the bolt 43. The block 44 is inserted into the engagement recess 22d of the pressure plate 22. The block 44 is movable to the transmission side from the state of FIG. 3 with respect to the engagement recess 22d. By this block 44, the fulcrum ring 23 and the pressure plate 22 are connected such that they cannot rotate relative to each other and can move relative to each other in the axial direction.

The biasing mechanism 24 is used for the pressure plate 2
2 groove 22c and annular portion 23a of the fulcrum ring 23
It is located in the annular space between and. Biasing mechanism 24
Is a mechanism for applying an urging force to the fulcrum ring 23 in the direction away from the pressure plate 22 (transmission side). The urging mechanism 24 mainly includes a first support plate 31 (first annular member) and a second support plate 31.
The support plate 32 (second annular member) and a plurality of return springs 33 are mainly configured. The first and second support plates 31 and 32 are annular sheet metal members, as is apparent from FIGS. 6, 7, and 9. First
The second support plates 31 and 32 include a plurality of first and second inclined surfaces 31a extending in the circumferential direction by a predetermined distance.
32a is formed. In the initial state, the first support plate 31 and the second support plate 32 are as shown in FIG.
The state is as shown in. That is, the first inclined surface 31a and the second inclined surface 32a are in contact with each other. Note that, as shown in FIG. 7, the first inclined surface 3 of the first support plate 31.
1a has a higher R ₂ direction (projects toward the engine side) and has a lower R ₁ direction end. First and second
The inclination angle of the inclined surfaces 31a and 32a (angle formed by the inclined surface and the groove 22c) is preferably in the range of 10 to 15 degrees, and most preferably in the range of 12 to 14 degrees. The second inclined surface 32a of the second support plate 32 is formed and arranged so as to come into complementary contact with the first inclined surface 31a. The first and second support plates 31 and 32 are formed with outer peripheral cylindrical portions 31b and 32b that are bent to the outer peripheral portions, respectively. The outer peripheral cylindrical portion 32b of the second support plate 32 is formed in the groove 22c of the pressure plate 22.
It is possible to contact the outer peripheral wall of the. Further, the outer peripheral cylindrical portion 31b of the first support plate 31 can contact the inner peripheral surface of the annular portion 23a of the fulcrum ring 23. The second support plate 32 is arranged movably in the circumferential direction within the groove 22c. The first support plate 31 is fixed to the annular portion 23a of the fulcrum ring 23 by a plurality of rivets 34 (FIG. 3). First support plate 31
The second support plate 32 and the second support plate 32 respectively have a plurality of spring engaging portions 31c, 3 which are cut and raised in the axial direction on the inner peripheral side portion.
2c is formed. The spring engagement portions 31c and 32c are formed with holes 31d and 32d penetrating in the radial direction. Both ends of the return spring 33 connect the spring engaging portions 31c and 32c, which are located at different positions in the circumferential direction. Both ends of the return spring 33 have spring engaging portions 3
It is inserted in the holes 31d and 32d of 1c and 32c.
In the initial state as shown in FIG. 7, the return spring
The ring 33 pulls the second support plate 32 with respect to the first support plate 31 in the R ₂ direction. The first support plate 31 and the fulcrum ring 23 are constantly urged in the axial direction by the wedge mechanism including the inclined surfaces 31a and 32a.

The biasing mechanism 24 is the pressure plate 22.
The urging mechanism 24 is easy to operate because it is disposed on the inner peripheral portion of the and is exposed on the inner peripheral side. For example, the return spring 33 can be easily attached and detached. In addition, the first and second support plates 31 and 32 are sheet metal products manufactured by pressing, and have a plurality of inclined surfaces 31.
Since a and 31b are formed at the same time, the cost is low.
In addition, the spring engaging portion 3 that locks the return spring 33
1c and 32c are first and second support plates 31 and 3
Since it is formed integrally with the 2, the entire structure is simplified. Further, since the inclined surfaces 31a and 32a are formed as an integral member, the amount of movement of the second inclined surface 32a in the circumferential direction does not vary. As a result, the fulcrum ring 23
The axial projection amount of the is kept constant in the circumferential direction.

A friction material (friction coefficient adjusting material) for increasing the friction coefficient as compared with the conventional case is coated on either or both of the engine side surface of the second support plate 32 and the groove 22c of the pressure plate 22. Good. As a result, under-adjustment is unlikely to occur even under conditions of severe vibration. Under-adjust means vibration when the clutch is engaged, that is, when force is applied axially to the fulcrum ring 23 and as a result force is applied axially from the first inclined surface 31a to the second inclined surface 32a of the wedge mechanism. By this, the force acting on the second support plate 32 in the circumferential direction increases, and the second support plate 32 slides in the R ₁ direction. There, the position of the fulcrum ring 23 does not correspond to the wear amount.

As another method for preventing the above-mentioned under-adjustment, the first inclined surface 31a and the second inclined surface 32 are also included.
It is also possible to make the angle of a small. In that case, the circumferential component of the force acting in the axial direction from the first inclined surface to the second inclined surface can be reduced. However, if the angle is made extremely small, the following problems occur and it is difficult to put it into practical use. First, during clutch release, the second support ring 32 rotates more than necessary in the R ₂ direction, causing the fulcrum ring 23 to move axially more than the amount of wear (overadjustment). Secondly, the rotation angle of the second support plate 32 becomes large for the same amount of wear. If this happens, the tensile load of the return spring 33 will be extremely reduced, which is not desirable, and it is difficult to design the return spring 33 to prevent this.

That is, the present application suppresses under-adjustment without making the inclination angle of the inclined surface extremely small. Further, in the present application, the slipperiness of the second support plate 32 is adjusted by a simple method by coating the friction material. The regulation mechanism 25 prohibits the fulcrum ring 23 from moving in the axial direction when the friction facing 11 is not worn, detects the amount of wear when the friction facing 11 is worn, and detects the amount of wear according to the amount of wear.
It is a mechanism for allowing 3 to move in the axial direction. The regulation mechanism 25 includes a screw hole 22e of the pressure plate 22.
Corresponding to the second axial holes 23c of the fulcrum ring 23, they are provided at four locations at equal intervals in the circumferential direction. The members constituting the regulating mechanism 25 are two members at each location, that is, the bolt 38 (first member) and the bush 39 (second member). In this way, the regulation mechanism 25 is composed of two simple members.

The bolt 38 includes a main body 38a and a main body 38a.
It is composed of a screw portion 38b and a head portion 38c formed at the tip of the. The screw portion 38b is the pressure plate 2
It is screwed into the second screw hole 22e. As a result, the bolt 38 is fixed integrally with the pressure plate 22. The main body 38a of the bolt 38 is the fulcrum ring 2
3 through the second axial hole 23c and the first axial hole 21d of the clutch cover 21. The main body 38a has a gap between the first axial hole 21d and the second axial hole 23c. The head portion 38c is arranged at a distance from the facing portion 21c of the clutch cover 21 on the transmission side. The first member fixed to the pressure plate 22 may be another rod-shaped member such as a pin instead of the bolt.

As shown in FIG. 5, the bush 39 is a tubular member and can be expanded / contracted or elastically deformed in the radial direction. The bush 39 includes a tubular portion 39a and a disc-shaped flange 39b extending from one end of the tubular portion 39a to the outer peripheral side. A slit 39c extending in the axial direction is formed in the tubular portion 39a and the flange 39b. As shown in FIG. 4, the bush 39 is provided in the first axial hole 21d of the facing portion 21c of the clutch cover 21 and the bolt 38.
Is arranged on the outer periphery of the main body 38a. The bush 39 is tightly fitted to the main body 38a. In addition, the tubular portion 39a
Has one end abutted on the engine-side surface of the protruding portion 23b of the fulcrum ring 23. A gap is secured between the outer peripheral surface of the tubular portion 39a and the first axial hole 21d of the clutch cover 21. The flange 39b has a facing portion 21c.
It is arranged in contact with the bottom surface of the concave portion 21e. Axial gap A between the flange 39b and the head 38c of the bolt 38
Is secured to be approximately equal to or more than the wear allowance of the friction facing 11. Since the bush 39 is an elastic tubular body having a slit formed therein, it is easily deformed by bending and the sliding resistance generated between the bush 39 and the bolt 38 is stable.

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

The retainer 47 is an annular member arranged on the outer circumference of an input shaft (not shown) of the transmission. The retainer 47 is engaged with a release device 28 described later. The retainer 47 includes a cylindrical main body 47a,
It is mainly composed of a flange 47b extending from the transmission side end to the outer peripheral side. The retainer 47
A pin 52 fixed to the inner peripheral portion of the disk-shaped portion 21b of the clutch cover 21 is engaged with the pin 52 so as not to be rotatable relative to the pin 52 but to be movable in the axial direction.

The diaphragm spring 51 has a substantially disk shape. The diaphragm spring 51 has an annular elastic portion 51a on the outer peripheral side, and a large number of lever portions 51b extend on the inner peripheral side from the elastic portion 51a. That is, the diaphragm spring 51 has a large-diameter center hole and a plurality of slits 51c radially extending from the inner peripheral edge thereof. An oval hole 51d, which is wider in the circumferential direction than the slit 51c, is formed at the radially outer end of the slit 51c, that is, at the root of the lever portion 51b. The outer peripheral portion of the diaphragm spring 51 is supported by the clutch cover 21, and the inner peripheral end thereof applies a predetermined pressing force to the retainer 47 to urge the retainer 47 toward the engine. Split pins 53 fixed to the retainer 47 are inserted between the lever portions 51b of the diaphragm spring 51 at a plurality of positions in the circumferential direction. As a result, the diaphragm spring 51 rotates integrally with the retainer 47.

The lever member 46 is a pressing member for increasing the pressing force of the diaphragm spring 51 according to the lever ratio and transmitting it to the fulcrum ring 23. The lever members 46 are radially arranged at equal intervals in the circumferential direction. Each lever member 46 is formed by bending a strip-shaped plate member, for example. The outer side portion of the lever member 46 in the radial direction is bent so as to project to the transmission side. A hole 46b extending in the circumferential direction is formed in that portion. An engagement protrusion 21f extending from the clutch cover 21 is engaged in the hole 46b. As a result, the lever member 46 moves the clutch cover 21.
Rotates together with. Circumferentially opposite sides of the hole 46b are fulcrums 46a that swingably contact the clutch cover 21. Further, the lever member 46 is formed with an action point 46c projecting to the engine side at the radially outer side portion and contacting the annular portion 23a of the fulcrum ring 23. A force point 46d protruding toward the transmission is formed on the inner side of the lever member 46 in the radial direction. The power point 46d is arranged on the transmission side of the flange 47b of the retainer 47. Flange 47b
The cone spring 60 and the plate 48 are disposed between the force point 46d and the force point 46d of the lever member 46. The cone spring 60 is compressed between the flange 47b and the force point 46d to be flat in the clutch engagement state shown in FIGS. 2 and 3. The force point 46d of the lever member 46 is in contact with the engine side of the disk-shaped plate 48.
The contact plate 49 is fixed to the transmission side of the outer periphery of the main body 47a of the retainer 47 by a snap ring 50. The outer peripheral portion of the contact plate 49 is a bent portion protruding toward the transmission. In the clutch connected state shown in FIG. 2, a predetermined gap is secured between the bent portion and the lever member 46 in the axial direction.

The release device 28 includes the clutch pressing mechanism 2
7 is a device for releasing the pressing force applied to the pressure plate 22 by 7 to release the clutch. The release device 28 includes a release bearing 54 and a quill 55.
It is composed of a cylindrical member 56, a support ring 57, a snap ring 58, and a coil spring 59. The release bearing 54 is composed of an inner race, an outer race, and a plurality of rolling elements arranged between the races. Quill 55 is release bearing 5
4 is arranged on the outer circumference of the outer race 4 and is fixed to the outer race so as not to rotate relative to it. The cylindrical member 56 is fixed to the inner race, and its tip is arranged on the inner peripheral side of the retainer 47. The support ring 57 is fixed to the cylindrical member 56 by a snap ring 58 fixed to the outer peripheral portion of the distal end of the cylindrical member 56. The support ring 57 is in contact with the inner peripheral surface of the retainer 47 on the engine side. The contact surface between the support ring 57 and the retainer 47 has a spherical shape, and misalignment can be absorbed. The coil spring 59 is arranged on the outer periphery of the cylindrical member 56. The coil spring 59 is arranged in a compressed state between the inner race and the retainer 47. Operation [Clutch Connection] In the clutch connected state shown in FIGS. 2 to 4, the diaphragm spring 51 urges the retainer 47 toward the engine side, and the retainer 47 is further connected to the lever member 46.
The fulcrum ring 23 is urged to the engine side via. As a result, the pressure plate 22 holds the friction disc 4 of the clutch disc assembly 3 and the intermediate plate 5 together with the flywheel 2. As a result, the clutch is connected.

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

The cone spring 60 serves as a cushioning plate when shifting to the clutch connected state. [Clutch Release] During clutch release, the quill 55 is moved to the transmission side, and the release bearing 54, the cylindrical member 56, and the retainer 47 are moved to the transmission side. When the bent portion of the contact plate 49 contacts the lever member 46, the lever member 46 is moved to the transmission side thereafter. At this time, the distance from the portion of the lever member 46 where the contact plate 49 abuts to the action point 46c is the force point 46d to the action point
Since it is shorter than the distance to 6c, the point of action 46c
Quickly leaves the fulcrum ring 23. That is, the clutch disengagement performance is improved.

Since the pressing force of the diaphragm spring 51 is set small, the load applied to the retainer 47 by the diaphragm spring 51 at the time of release is small. Therefore, the release load is small. In addition, the cone spring 60 is not attached to the retainer 47 with respect to the retainer 4.
Since the load is applied in the moving direction of 7 (transmission side), the release load is further reduced. As a result,
The clutch pedal force is significantly reduced.

When the action point 46c of the lever member 46 moves away from the fulcrum ring 23, the strap plate 42
The fulcrum ring 23 moves to the transmission side by the reaction force of. At this time, the fulcrum ring 23
And the pressure plate 22 move together in the axial direction. This is because the sliding resistance generated between the bolt 38 and the bush 39 is set to be larger than the total of the reaction force of the strap plate 42 and the urging force from the urging mechanism 24. This is because slippage does not occur. That is, the fulcrum ring 23 moves the pressure plate 22 in the axial direction via the regulation mechanism 25. As a result, from the pressure plate 22 to the friction disc 4 of the clutch disc assembly 3.
The pressing force against is released.

The sliding resistance generated between the bolt 38 and the bush 39 is preferably much larger than the total of the reaction force of the strap rate 42 and the urging force from the urging mechanism 24, and is twice or more. Is preferred. With such a setting, when the vibration is transmitted from the flywheel 2 to the pressure plate 22, no slip occurs between the bolt 38 and the bush 39, and the strap plate 42 bends. That is, the tracking of the wear amount is accurately maintained. [Abrasion Occurrence] When the friction facing 11 is worn when the clutch is engaged, the pressure plate 22 and the fulcrum ring 23 move to the friction facing 11 side by the wear amount. At this time, the bolt 38 of the regulation mechanism 25 moves to the engine side together with the pressure plate 22. However, in the bush 39, the flange 39b has the facing portion 21c.
Since they are in contact with each other, they cannot move. Therefore, the bolt 38 moves in the axial direction with respect to the bush 39. As a result, as shown in FIG. 10, a gap B equal to the wear amount of the friction facing 11 is formed between the protruding portion 23b of the fulcrum ring 23 and the tip of the tubular portion 39a of the bush 39. Flange 39b of bush 39 and bolt 38
The axial clearance with the head portion 38c of A is shortened by the amount of wear and becomes A '(AB).

Next, when the clutch release operation is performed, the fulcrum ring 23 moves to the transmission side by the urging force from the urging mechanism 24 until it comes into contact with the bush 39. The fulcrum ring 23 has a protruding portion 23b.
When abuts on the tubular portion 39a of the bush 39, it does not move further in the direction away from the pressure plate 22. As described above, this is the bolt 38 and the bush 3.
This is because the sliding resistance generated between the strap rate 42 and 9 is set to be larger than the total of the reaction force of the strap rate 42 and the biasing force from the biasing mechanism 24. As a result, over-adjustment of the wear amount (the fulcrum ring 23 moves with respect to the pressure plate 22 more than the wear amount) is unlikely to occur.

As a result of the above operation, as shown in FIG.
A gap C equal to the above-described wear amount (B) is formed between the second side surface 22b of the pressure plate 22 and the fulcrum ring 23. When the clutch engagement operation is performed from this state, the state shifts to the state shown in FIG. Comparing FIG. 12 and FIG. 2, a gap C is formed between the pressure plate 22 and the fulcrum ring 23, and a gap A ′ between the flange 39b of the bush 39 and the head portion 38c of the bolt 38 is formed.
Is shorter than the initial clearance A by the amount (B) of the previous wear amount. [Effect] In the structure of the regulation mechanism 25, since the bolt 38 and the bush 39 for detecting the wear amount are provided outside the pressure plate 22, the friction engagement portion for regulating the movement of the fulcrum ring 23 is pressured. It is unlikely to be adversely affected by heat generated on the friction surface 22a side of the plate 22. As a result, the bolt 38 and the bush 39
The magnitude of the sliding resistance generated between the two becomes stable over a long period of time.

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

It is easy to attach and detach the regulating mechanism 25 to and from the clutch cover assembly 1. Each regulating mechanism 25 is arranged from the engine side of the clutch cover 21 to the transmission side of the clutch plate 21 with the screw hole 22e of the pressure plate 22, the second axial hole 23c of the fulcrum ring 23 and the first axial hole 21d of the clutch cover 21 aligned. It can be installed and removed.

Further, since the head 38c is formed on the bolt 38, as the friction facing 11 is worn and the wear adjusting operation is performed, the head 38 of the bolt 38 is formed.
The gap A between c and the flange 39b of the bush 39 becomes shorter. Since this gap A can be observed from the outside of the clutch cover assembly 1, the operator can easily determine when to replace the clutch cover assembly 1.

Since the fulcrum ring 23 is connected by the strap plate 42 so as to be relatively rotatable and axially movable, even if the friction facing 11 is worn, the posture of the strap plate 42 does not change and is kept constant. . This is because the axial position of the fulcrum ring 23 with respect to the flywheel 2 and the clutch cover 21 does not change. When the strap plate is fixed to the pressure plate, the posture of the strap plate also changes as the pressure plate moves due to wear of the friction facing. Second Embodiment Configuration FIGS. 13 to 16 show a clutch cover assembly 61 in which an embodiment of the present invention is adopted. The clutch cover assembly 61 is used in vehicles, particularly small vehicles such as passenger cars. The clutch cover assembly 61 is a device for transmitting or interrupting the torque transmitted from the flywheel 62 of the engine to the clutch disc assembly, and is attached to the flywheel 62.

The clutch disc assembly is mainly composed of a flexinshin disc 64 and a hub connected to the flexincin disc 64 via a coil spring. The friction disk 64 is composed of friction facings fixed to both surfaces of the outer peripheral portion of the disk-shaped plate. In this embodiment, the friction facing is made of a friction material made of an organic material.

The R ₁ direction in FIG. 13 is the rotation direction of the clutch, and the R ₂ direction is the support plate 92 described later.
Is the direction of rotation when the wear of is adjusted. 15 and 1
An engine (not shown) is arranged on the left side of 6, and a transmission (not shown) is arranged on the right side.
The clutch cover assembly 81 mainly includes the clutch cover 8
1, a pressure plate 82, a fulcrum ring 83, a biasing mechanism 84, a restricting mechanism 85, a diaphragm spring 90 (pressing member), and a drive mechanism 86.
It consists of and.

The clutch cover 81 is a flywheel 6
It is a dish-shaped member that is attached to No. 2. The clutch cover 81 has an outer peripheral cover portion 81a that covers the outer peripheral side of the clutch disc assembly, and a disc-shaped portion 81b that faces the transmission side of the clutch disc assembly.
Three first axial holes 81d (FIG. 15) are formed in the disc-shaped portion 81b at equal intervals in the circumferential direction. Also, the first
A recess 81e having a diameter larger than that of the first axial hole 21d is formed on the transmission side of the axial hole 81d.

The pressure plate 82 is disposed inside the outer peripheral cover portion 81a of the clutch cover 81, and is located between the friction disk 64 and the disk-shaped portion 81b of the clutch cover 81 and close to the friction disk 64. It is arranged. The pressure plate 82 is an annular member and has a friction surface 82a (first side surface) facing the friction disc 64 and a second side surface 82b facing the disc-shaped portion 81b. An annular groove 82c is formed on the second side surface 82b of the pressure plate 82. A biasing mechanism 84 described later is provided in the groove 82c. Further, engagement portions 82d that project in the radial direction are formed at three locations at equal intervals in the circumferential direction on the outer peripheral portion of the pressure plate 82 on the second side surface 82b side. A screw hole 82e is formed in each engaging portion 82d.

The fulcrum ring 91 is arranged on the second side surface 82b side of the pressure plate 82. The fulcrum ring 91 is a diaphragm spring 90.
And is urged by the diaphragm spring 90 toward the flywheel 62 side together with the pressure plate 82. The fulcrum ring 91 includes an annular portion 91a and three protruding portions 9 extending radially outward from the annular portion 91a.
1b and. The annular portion 91a is arranged so as to face the groove 82c of the pressure plate 82 at a predetermined interval in the axial direction. Annular portion 91
An annular convex portion is formed on the transmission side of a. In addition, the protruding portion 91b is formed by the pressure plate 82.
Is in contact with the second side surface 82b. As is apparent from FIG. 13, the protrusion 91b extends in the circumferential direction by a predetermined angle, and a second axial hole 91c is formed on the R ₂ direction side. The second axial hole 91c is formed by the pressure plate 82.
Of the screw hole 82e and the first axial hole 81d of the flywheel 81. The diameter of the second axial hole 91c is smaller than that of the first axial hole 81d.

The fulcrum ring 91 and the pressure plate 82 rotate integrally with the clutch cover 81, that is, the flywheel 62 by the drive mechanism 86. The drive mechanisms 86 are provided in three places side by side in the circumferential direction,
Each is mainly composed of a strap plate 71. The strap plate 71 is a fulcrum ring 9
It is a member for connecting 1 to the clutch cover 81 so as not to rotate and to be movable in the axial direction. The strap plate 71 is a plate-shaped elastic member formed by stacking a plurality of plate members and extending in the circumferential direction (generally tangential direction). The end of the strap plate 71 in the R ₁ direction is fixed to the clutch cover 81 by a rivet 72. The end of the strap plate 71 in the R ₂ direction is fixed to the R ₁ side of the protruding portion 91 b of the fulcrum ring 91 by the rivet 73.

The biasing mechanism 84 is used for the pressure plate 8
2 groove 82c and annular portion 91a of fulcrum ring 91
It is located in the annular space between and. Biasing mechanism 84
Is a mechanism for applying an urging force to the fulcrum ring 91 in the direction away from the pressure plate 82 (transmission side). The biasing mechanism 84 mainly includes a part of the fulcrum ring 91, a support plate 92, a plurality of return springs 93, and a friction plate 9.
4 and. The fulcrum ring 91 and the support plate 92 are formed with a plurality of first and second inclined surfaces extending in the circumferential direction by a predetermined distance. The first inclined surface and the second inclined surface are in contact with each other. The inclination angle of the first inclined surface and the second inclined surface (the angle formed by the inclined surface and the groove 82c) is preferably in the range of 10 to 15 degrees.
Most preferably, it is in the range of 2 to 14 degrees. The first inclined surface has a high end in the R ₂ direction (projects toward the engine side) and a low end in the R ₁ direction. The second inclined surface of the support plate 92 is formed and arranged so as to come into complementary contact with the first inclined surface. The support plate 92 is arranged movably in the circumferential direction within the groove 82c.

The fulcrum ring 91 and the support plate 92 are each formed with a plurality of spring engaging portions. Both ends of the return spring 93 are connected to spring engaging portions that are located at different positions in the circumferential direction. The return spring 93 pulls the support plate 92 with respect to the fulcrum ring 91 in the R ₂ direction. First
The fulcrum ring 91 is always urged in the axial direction by the wedge mechanism including the second inclined surface.

The friction plate 94 (friction coefficient adjusting material) is arranged between the support plate 92 and the groove 82c. The friction plate 94 is an annular friction lining as shown in FIG. 17, and is made of a material having a higher friction coefficient than the pressure plate 82 and the support plate 92. The friction plate 94 is
Those having excellent heat resistance and abrasion resistance and having a desired friction coefficient are preferable. An example of the friction plate 94 is a trade name NAH44 (Nippon Bulker). The friction plate 94 may be fixed to one of the groove 82c of the pressure plate 82 or the fulcrum ring 91. Further, as shown in FIG. 18, the friction plate 94 may be composed of divided arc-shaped plates 94A to improve the material yield.
The friction plate 94 may be attached to one of the groove 82c of the support plate 92 or the pressure plate 82.

By providing the friction plate 94, the friction plate 94
Support plate 92 and pressure plate without provision
When the groove 82c of 82 is in direct contact,
The friction between the shear plate 82 and the support plate 92
The friction coefficient is increasing. As a result, under conditions of severe vibration
However, under-adjustment is unlikely to occur. Anda
-Adjust means when the clutch is engaged,
Axial direction from diaphragm spring 90 to mulling 91
Force is applied to the wedge mechanism, and as a result, from the first inclined surface of the wedge mechanism to the second inclined surface.
When vibration is applied to the inclined surface in the axial direction,
The force acting on the support plate 92 in the circumferential direction is
Larger, support plate 92 is R ₂The current slipping direction
It is an elephant.

As a method of preventing the above-mentioned under-adjustment, it is conceivable to reduce the angle between the first inclined surface and the second inclined surface. In that case, the circumferential component of the force acting in the axial direction from the first inclined surface to the second inclined surface can be reduced. However, if the angle is made extremely small, the following problems occur and it is difficult to put it into practical use. First, during clutch release, the support plate 92 rotates more than necessary in the R ₂ direction, and the fulcrum ring 91 is apt to move axially more than the amount of wear (overadjustment). Second, the rotation angle of the support plate 92 becomes large for the same amount of wear. If this happens, the tensile load of the return spring 93 will be extremely reduced, which is not desirable.
3 is difficult to design.

That is, in the present application, the tilt angle is not made extremely small, and the under-adjustment is hard to occur. Further, in the present application, the slipperiness of the support plate 92 is adjusted by a simple method by installing the friction plate 94. In order to satisfy the above-mentioned condition of the coefficient of friction between the pressure plate 82 and the support plate 92, the friction plate 94 is eliminated, and the engine side surface of the support plate 92 and / or the groove 82c of the pressure plate 82 are provided. Further, a friction material for increasing the friction coefficient as compared with the conventional one may be coated.

The regulation mechanism 85 is provided for the friction disc 6
When there is no wear in No. 4, the fulcrum ring 91 is prohibited from moving in the axial direction, and when the friction disk 64 is worn, the amount of wear is detected and the fulcrum ring 91 is allowed to move in the axial direction according to the amount of wear. It is a mechanism for. The restriction mechanism 85 includes a screw hole 82e of the pressure plate 82 and a second axial hole 9 of the fulcrum ring 91.
Corresponding to 1c, they are provided at three locations at equal intervals in the circumferential direction. The members constituting the regulating mechanism 85 are two members, that is, a bolt 98 (first member) and a bush 99 (second member) at each location. In this way, the regulation mechanism 85
It is composed of two simple members.

The bolt 98 includes a main body 98a and a head 98c.
And a threaded portion 98b formed at the tip of the main body 98a. The screw portion 98b is screwed into the screw hole 82e of the pressure plate 82. As a result, the bolt 98 is fixed integrally with the pressure plate 82. The body 98a of the bolt 98 has a second axial hole 91c of the fulcrum ring 91 and a first portion of the clutch cover 81.
It penetrates through the axial hole 81d. Although a gap is secured between the main body 98a and the first axial hole 81d, the main body 9a
8a is in circumferential contact with the second axial hole 91c. The head portion 98c is the disk-shaped portion 81 of the clutch cover 81.
It is arranged at a distance from b to the transmission side. The member fixed to the pressure plate 82 may be another rod-shaped member such as a pin instead of the bolt.

The bush 99 is a tubular member and can be expanded / contracted or elastically deformed in the radial direction. Bush 99
Is composed of a tubular portion 99a and a disc-shaped flange 99b extending from one end of the tubular portion 99a to the outer peripheral side. Tube part 9
A slit extending in the axial direction is formed in 9a and the flange 99b. This bush 99 is used for the clutch cover 8
It is arranged in the first axial hole 81d of the first disk-shaped portion 81b and on the outer periphery of the main body 98a of the bolt 98. The bush 99 is tightly fitted to the main body 98a. In addition, one end of the tubular portion 99 a is provided with the protruding portion 9 of the fulcrum ring 91.
It is in contact with the engine side surface of 1b. A gap is secured between the outer peripheral surface of the tubular portion 99a and the first axial hole 81d of the clutch cover 81. The flange 99b is arranged in contact with the bottom surface of the concave portion of the disk-shaped portion 81b. The axial clearance between the flange 99b and the head portion 98c of the bolt 98 is secured to be approximately the same as or larger than the wear allowance of the friction disc 64. Since the bush 99 is an elastic tubular body having a slit formed therein, it is easily deformed by bending and the sliding resistance generated between the bush 99 and the bolt 98 is stable.

An O-ring 90 as a cushioning member is arranged around the bush 99 on the engine side. The O-ring 90 is fitted in a recess formed in the protrusion 91b of the fulcrum ring 91, and a part of the O-ring 90 protrudes toward the transmission by the other surface of the protrusion 91b. When the fulcrum ring 23 and the pressure plate 82 approach the clutch cover 81 due to vibration during clutch release, the fulcrum ring 23 and the pressure plate 82 function as a cushioning member that absorbs a shock of collision.

The plate 95 is a member sandwiched between the clutch cover 81 and the head portion 98c of the bolt 98, and prevents slippage between the bolt 98 and the bush 99 when the clutch cover assembly 61 is conveyed. It is a member of. The diaphragm spring 90 is a disk-shaped thin plate member, and is a member for urging the pressure plate 82 and the fulcrum ring 91 toward the flywheel 62 side by an elastic force. The diaphragm spring 90 includes an annular elastic portion 88a and a plurality of lever portions 88b extending inward in the radial direction from the inner peripheral edge of the elastic portion 88a. The inner peripheral portion of the elastic portion 88a is supported on both axial sides by two wire rings 87 supported by a plurality of bending tabs 81c formed on the inner peripheral side of the clutch cover 81. As a result, the diaphragm spring 90 can swing about the two wire rings 87 as fulcrums. The outer peripheral portion of the elastic portion 88 a is in contact with the convex portion of the fulcrum ring 91. A release device (not shown) is engaged with the tip of the lever portion 88b. Operation [Clutch Connection] In the clutch connected state, the diaphragm spring 90 urges the fulcrum ring 91 toward the engine. As a result, the pressure plate 8
The reference numeral 2 holds a friction disk 64 of a clutch disk assembly between the flywheel 62 and the flywheel 62. As a result, the clutch is connected. [Clutch Release] During clutch release, a release device (not shown) moves to the engine side and pushes the lever 88b of the diaphragm spring 90 toward the engine. Then, the outer peripheral end of the elastic portion 88a moves to the transmission side, and the urging force on the fulcrum ring 91 is released. As a result, the pressing force of the pressure plate 82 on the friction disc 64 of the clutch disc assembly is released.

The sliding resistance generated between the bolt 98 and the bush 99 is preferably much larger than the total of the reaction force of the strap plate 71 and the urging force from the urging mechanism 84, and is twice or more. Is preferred. With such a setting, the flywheel 62 to the pressure plate 8
2, when the vibration is transmitted to the bolt 98 and the bush 9
No slippage occurs between 9 and 9, and the strap plate 71 bends. That is, the tracking of the wear amount is accurately maintained. [Abrasion] Friction disk 6 when clutch is engaged
4 is worn, the pressure plate 82 and the fulcrum ring 91 wear the friction disc 6 by the amount of wear.
Move to side 4. At this time, the bolt 98 of the regulation mechanism 85
Moves to the engine side together with the pressure plate 82. However, the bush 99 is immovable because the flange 99b is in contact with the disc-shaped portion 81a. Therefore, the bolt 98 moves in the axial direction with respect to the bush 99. As a result, the protrusion 91b of the fulcrum ring 91 is formed.
A gap equal to the amount of wear of the friction disc 64 is formed between and the tip of the tubular portion 99a of the bush 99.
Flange 99b of bush 99 and head 98 of bolt 98
The axial clearance with c is shortened by the amount of wear.

Next, when the clutch release operation is performed, the fulcrum ring 91 is moved to the transmission side by the urging force from the urging mechanism 84 until it comes into contact with the bush 99. The fulcrum ring 91 has a protruding portion 91b.
When abuts on the tubular portion 99a of the bush 99, it does not move further in the direction away from the pressure plate 82. This is the bolt 98 and the bush 9 as described above.
This is because the sliding resistance generated between 9 and 9 is set to be larger than the total of the reaction force of the strap rate 71 and the urging force from the urging mechanism 84. As a result, the wear amount is not over-adjusted (the fulcrum ring 91 is moved with respect to the wear amount or more with respect to the pressure plate 82).

As a result of the above operation, a gap equal to the above-mentioned amount of wear is formed between the second side surface 82b of the pressure plate 82 and the fulcrum ring 91. When the clutch engagement operation is performed from this state, the pressure plate 8
A gap is formed between the 2 and the fulcrum ring 91,
Flange 99b of bush 99 and head 98 of bolt 98
The gap with c is shorter than the initial gap by the previous wear amount. [Effect] In the structure of the regulation mechanism 85, since the bolt 98 and the bush 99 for detecting the wear amount are provided on the second side surface 82b side of the pressure plate 82, the friction member for regulating the movement of the fulcrum ring 91. The joint portion is unlikely to be adversely affected by heat generated on the friction surface 82a side of the pressure plate 82. As a result, the magnitude of the sliding resistance generated between the bolt 98 and the bush 99 is stable for a long period of time.

Further, since the bolt 98 and the bush 99 are members independent of the pressure plate 82 and the clutch cover 81, it is easy to set the sliding resistance of the friction engagement portion. The restricting mechanism 85 includes the clutch cover assembly 61.
The bush 98 is wound around the bolt 98 to be completed before being mounted on. That is, the sliding resistance of the friction engagement portion can be set outside the clutch cover assembly 61. Further, since the friction engagement portion is not provided on the pressure plate or the flywheel, it is easier to set the sliding resistance at the friction engagement portion. In the conventional example in which the friction engagement portion is provided on the pressure plate or the clutch cover, it is necessary to adjust the load in the holes formed in those members, which makes setting difficult.

Clutch cover assembly 61 of regulation mechanism 85
Is easy to install and remove. Each restricting mechanism 85 includes the screw hole 82e of the pressure plate 82, the second axial hole 91c of the fulcrum ring 91, and the first axial hole 81d of the clutch cover 81 in a combined state from the engine side of the clutch cover 81 to the transmission side. It can be installed and removed.

Since the head 98c is formed on the bolt 98, the head 98c of the bolt 98 and the flange 99b of the bush 99 are separated between the head 98c and the flange 99b of the bush 98 as the friction disk 64 is worn and the wear adjusting operation is performed. The gap between is getting shorter. This gap is provided by the clutch cover assembly 61.
Since it can be observed from the outside, the operator can easily determine when to replace the clutch cover assembly 61.

Since the fulcrum ring 91 is connected by the strap plate 71 so as to be relatively rotatable and axially movable, even if the friction disc 64 is worn, the posture of the strap plate 71 does not change and is kept constant. . This is because the fulcrum ring 91 does not change its axial position with respect to the flywheel 62 and the clutch cover 81. Pressure plate 82
When the strap plate 71 is fixed to the strap plate 71, the posture of the strap plate also changes as the pressure plate moves due to wear of the friction facing. Third Embodiment As shown in FIG. 19, in the clutch cover assembly 1 of the first embodiment, the groove 222c and the second support ring 31 are provided.
A friction plate 75 may be disposed between Also in this case
The same effect as that of the embodiment can be obtained.

[0077]

According to the clutch cover assembly of the present invention,
Since the first member and the second member of the regulation mechanism are provided outside the pressure plate, these members are less likely to be adversely affected by heat generated on the first side surface of the pressure plate. As a result, the sliding resistance generated between the first member and the second member can be stabilized for a long period of time.

[Brief description of drawings]

FIG. 1 is a plan view of a clutch cover assembly as an embodiment of the present invention.

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

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

FIG. 4 is a partially enlarged view of FIG.

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

FIG. 6 is a partial plan view of a first support plate.

FIG. 7 is a partial sectional development view of the biasing mechanism.

FIG. 8 is a view corresponding to FIG. 7, showing an operating state of the biasing mechanism.

9 is a sectional view taken along line IX-IX in FIG.

FIG. 10 is a schematic vertical sectional view showing an operating state of the clutch device.

FIG. 11 is a schematic vertical sectional view showing an operating state of the clutch device.

FIG. 12 is a schematic vertical sectional view showing an operating state of the clutch device.

FIG. 13 is a plan view of the clutch cover assembly according to the second embodiment.

FIG. 14 is a view on arrow XIV in FIG. 13.

FIG. 15 is a sectional view taken along line XV-XV in FIG.

16 is a sectional view taken along line XVI-XVI of FIG.

FIG. 17 is a plan view of a friction plate.

FIG. 18 is a plan view of a friction plate according to a modification.

FIG. 19 is a schematic vertical sectional view of a clutch cover assembly according to a third embodiment.

[Explanation of symbols]

1 Clutch cover assembly 2 flywheel 3 Clutch disc assembly 4 friction discs 5 Intermediate plate 6 coil spring 21 Clutch cover 22 Pressure plate 23 Falkrum Ring 24 Biasing mechanism 25 Regulation mechanism 26 Drive mechanism 27 Clutch pressing mechanism 28 Release device 38 Volts 38a body 38b screw part 38c head 39 Bush 39a tube 39b flange 39c slit 61 Clutch cover assembly 62 flywheel 64 friction disc 81 Clutch cover 82 Pressure plate 84 Bias mechanism 85 Regulatory mechanism 86 drive mechanism 94 friction plate 98 volts 98a body 98b screw part 98c head 99 bush

Continuation of the front page (56) Reference JP-A-61-274122 (JP, A) JP-A-8-82331 (JP, A) JP-A-7-317802 (JP, A) JP-A-7-243452 (JP , A) (58) Fields investigated (Int.Cl. ⁷ , DB name) F16D 13/75

Claims (10)

(57) [Claims] 1. A clutch cover assembly for connecting a clutch by urging a friction facing of a clutch disc assembly to a flywheel side, the clutch cover assembly having a facing portion fixed to the flywheel and facing the friction facing. A clutch cover, an annular pressure plate that is disposed between the friction facing and the facing portion and is close to the friction facing, and has a first side surface on the friction facing side and a second side surface on the facing portion side; A fulcrum ring arranged to face the second side surface of the pressure plate, a pressing member supported by the clutch cover and applying a pressing force to the fulcrum ring to the pressure plate side, the pressure plate and the annular shape. The fulcrum placed between the An urging mechanism that applies an urging force in a direction away from the pressure plate in the axial direction to the ring, prohibits the fulcrum ring from moving in the axial direction when the friction facing has no wear, and wears the friction facing when worn. A first member fixed to the second side surface of the pressure plate and extending in the axial direction, which is a mechanism for detecting the amount and allowing the fulcrum ring to move in the axial direction according to the amount of wear. The second member includes a second member frictionally locked to the first member so as to be movable in the axial direction with respect to the first member when the above-mentioned load acts, and the second member frictionally contacts the clutch cover. The fulcrum ring has a contact portion that can contact from the side opposite to the facing side, and prevents the fulcrum ring from moving in a direction away from the pressure plate. To, and a regulation mechanism, the second member has one end the pair of the fulcrum ring
The clutch cover assembly is in contact with the surface of the facing portion side . 2. The clutch cover according to claim 1, wherein the first member is rod-shaped, and the second member is made of an elastic cylindrical body having a slit formed and interference-fitted to an outer periphery of the first member. Assembly. 3. A first axial hole is formed in the facing portion of the clutch cover, and a second axial hole corresponding to the first axial hole is formed in the fulcrum ring. The first member is disposed in the first and second axial holes, one end is detachably fixed to the second side surface of the pressure plate, and the second member is in the first axial hole. 3. The contact portion, which is interference-fitted to the outer periphery of the first member and which contacts the surface of the clutch cover facing portion opposite to the friction facing side, is formed at the other end. Clutch cover assembly. 4. A head having a diameter larger than that of a portion passing through the first axial hole is formed at the other end of the first member,
The clutch cover assembly according to claim 3 , wherein the head portion is axially separated from the abutting portion by a predetermined distance. Wherein said fulcrum ring has a protrusion protruding radially outward from said annular portion, said second axial hole in the projecting portion is formed, according to claim 3 or 4 The clutch cover assembly described in. 6. one end fixed to the clutch cover, the other end is further provided with a plate-shaped elastic member fixed to said fulcrum ring, a clutch cover assembly according to any one of claims 1 to 5 . 7. The biasing mechanism comprises a pair of wedge mechanisms disposed between the pressure plate and the annular portion of the fulcrum ring, in which inclined surfaces extending in the circumferential direction come into contact with each other, and the pair of wedge mechanisms. and a biasing member which biases the fulcrum ring in the direction axially away from the pressure plate by biasing each other between wedge mechanism circumferentially, to one of the claims 1-6 The described clutch cover assembly. 8. The urging mechanism is rotatably mounted on a surface of the fulcrum ring on the pressure plate side and having a plurality of first inclined surfaces, and a second side surface of the pressure plate. A second annular member having a plurality of second inclined surfaces arranged and abutting the plurality of first inclined surfaces, and the second annular member being urged toward the first annular member in the circumferential direction to the second annular member. an inclined surface to urge said first inclined surface, and the said fulcrum ring and the first annular member and a biasing member tending to move in the axial direction, any one of claims 1 to 6 The clutch cover assembly described in. 9. The fulcrum ring is further provided with a connecting member that connects the fulcrum ring to the clutch cover so as to elastically and integrally rotate in the axial direction, and the fulcrum ring is movable in the axial direction with respect to the first member. And is immovably engaged in the circumferential direction,
Clutch cover assembly according to any one of claims 1-5. 10. A coupling member for coupling the fulcrum ring to the clutch cover so as to elastically and integrally rotate in the axial direction, wherein the first member engages the second axial hole of the fulcrum ring. The clutch cover assembly according to any one of claims 6 to 10 , which is engaged so as to be movable in the axial direction and immovable in the circumferential direction.