JP2001012496A - Twin clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To maintain the regulated state of axial moving quantity of an intermediate plate to the axial moving amount of a pressure plate with simple constitution even in the case of the generation of difference between the wear amount of both friction discs (both friction connecting parts) in a twin clutch. SOLUTION: This twin clutch is provided with a lever mechanism 26 and a wedge-shaped member 61. The lever mechanism 26 has a lever member 27 so constituted that one end is journalled to a flywheel spacer 7 and that the tip of a first lever part 27b is locked to a pressure plate 10, and a locking member 32 supported to an intermediate plate 11 and locked to the tip of a second lever part 27c of the lever member 27. The wedge-shaped member 61 shaped to be gradually thinner in thickness from the inside toward the outside and moved outward by centrifugal force to fill a clearance between the tip of the first lever part 27b and a first face 10b of the pressure plate 10.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD The present invention relates to a twin clutch,
In particular, the present invention relates to a twin clutch in which the amount of axial movement of the intermediate plate relative to the amount of axial movement of the pressure plate is regulated.

[0002]

2. Description of the Related Art A clutch is a device for transmitting or interrupting power between an engine-side flywheel and an input shaft of a transmission. Generally, a clutch is composed of a clutch cover assembly and a clutch disk assembly mounted on a flywheel. The clutch disk assembly has a friction disk provided on an outer peripheral portion and a hub engaged with a transmission shaft on an inner peripheral portion. The friction disk and the hub are connected by a plurality of plate-like members and elastic members. The clutch cover assembly connects and disconnects the clutch by pressing or releasing the pressing force of the friction disk of the clutch disk assembly against the flywheel. The clutch cover assembly mainly includes a clutch cover fixed to the flywheel, a pressure plate arranged in the clutch cover and arranged in close proximity to the friction disk, and a pressing force supported by the clutch cover to apply pressure to the pressure plate. And a pressure plate moving mechanism that moves in the axial direction.

By the way, when it is necessary to secure a large torque transmission capacity in a limited space,
A twin clutch with two friction disks may be used. The twin clutch has first and second friction disks and an intermediate plate disposed therebetween. The intermediate plate is attached to the flywheel spacer fixedly sandwiched between the flywheel and the clutch cover by the strap plate so as to be relatively non-rotatable and movable in the axial direction. Further, friction surfaces for the first and second friction disks are formed on both side surfaces of the intermediate plate.

In the twin clutch, when the clutch is engaged,
The pressure plate of the clutch cover assembly is pressed toward the flywheel by a pressing member such as a diaphragm spring or a coil spring, and the first friction disc is sandwiched between the flywheel and the intermediate plate.
A friction disc is sandwiched between the intermediate plate and the pressure plate. When the clutch is released, the pressure plate and the intermediate plate are separated from the flywheel, and the frictional engagement between these and the friction disks is released.

[0005]

In the twin clutch described above, it is considered preferable that the first friction disk and the second friction disk are connected almost simultaneously at the time of the clutch operation (clutch connection, clutch release). This is because if the first friction disk and the second friction disk are connected at substantially the same time, the phase shift at the damper portion of the two clutch disk assemblies will be small, and deterioration of the damper characteristics due to a phase shift can be suppressed. .

Further, from the viewpoint of the disengagement characteristics of the clutch, it is preferable that the lift amount (axial movement amount) of the intermediate plate with respect to the lever stroke is always about half of that of the pressure plate in all regions. This is because if the intermediate plate is closer to or farther from the pressure plate than this, the intermediate plate comes into contact with the first or second friction disc, and the clutch disengagement performance deteriorates.

In the twin clutch disclosed in Japanese Patent Application Laid-Open No. 63-235724, a lever mechanism is provided to achieve the above two objects. This lever mechanism mainly includes a lever member. One end of the lever member is swingably supported by a clutch cover (referred to as a clutch casing in the above-mentioned publication), and the other end is movable in the axial direction. The other end of the lever member is in contact with the pressure plate (referred to as a pressure plate in the above publication) from the flywheel side. The intermediate plate is provided with a locking member (referred to as a slider in the above-mentioned publication) that locks the intermediate portion of the lever member from the flywheel side. With such a structure, during the clutch operation, the axial movement amount of the intermediate plate is always １ ／ of the axial movement amount of the pressure plate, and both friction disks are connected almost simultaneously.

Further, in the twin clutch disclosed in the above publication, when the wear amount of the second friction disk becomes larger than the wear amount of the first friction disk, the lever member moves the locking member to the axial fly with respect to the intermediate plate. By moving to the wheel side, the cutting characteristics that both friction disks are cut almost simultaneously are maintained. However, here, a locking member and a friction holding member for holding the locking member by friction are used, so that the structure around the locking member is complicated and the occupied space is large.

An object of the present invention is to provide a twin clutch with both friction disks (both friction coupling portions) with a simple structure.
Even if a difference occurs in the amount of wear of the intermediate plate, the state in which the amount of axial movement of the intermediate plate relative to the amount of axial movement of the pressure plate is regulated is maintained.

[0010]

According to a first aspect of the present invention, there is provided a twin clutch for transmitting and interrupting torque between a flywheel having a friction surface and a transmission shaft. This twin clutch includes a first clutch disc assembly, a second clutch disc assembly, a clutch cover, a flywheel spacer, an intermediate plate, a pressure plate, a pressure plate moving mechanism, a lever mechanism, a wedge type And a member. The first clutch disc assembly includes a first clutch disc assembly disposed near the friction surface of the flywheel.
It has a friction coupling part and can transmit torque to the shaft of the torque converter. The second clutch disc assembly has a second friction connection portion disposed on the side opposite to the flywheel side of the first friction connection portion, and can transmit torque to a shaft of the torque converter. The clutch cover is arranged on the side opposite to the flywheel side of the second frictional connection part, and is fixed to the flywheel. The flywheel spacer is interposed between the flywheel and the clutch cover in the axial direction, and is fixed to the flywheel and the clutch cover. The intermediate plate is disposed axially between the first frictional connection portion and the second frictional connection portion, and rotates in conjunction with the flywheel spacer. The pressure plate is disposed axially between the second friction coupling portion and the clutch cover, and rotates in conjunction with the clutch cover. The pressure plate moving mechanism is a mechanism for moving the pressure plate in the axial direction, and is supported by the clutch cover. The lever mechanism is a mechanism for regulating the axial movement amount of the intermediate plate with respect to the axial movement amount of the pressure plate. The lever mechanism has a lever member and a locking member. One end of the lever member is supported by the flywheel spacer, and the other end is engaged with the pressure plate. The locking member is a member supported by the intermediate plate, and is locked at a central portion between one end and the other end of the lever member. The wedge-shaped member has a shape in which the thickness gradually decreases from the inside to the outside, and moves outward due to centrifugal force to form a gap between one end of the lever member and the pressure plate, or a gap between the lever member and the lever member. Fill the gap between the intermediate part and the locking member.

In the twin clutch of the present invention, the flywheel, the flywheel spacer, the clutch cover, the pressure plate, and the intermediate plate are circumferentially connected. The pressure plate and the intermediate plate are movable in the axial direction with respect to the flywheel, the flywheel spacer, and the clutch cover. When the pressure plate is moved in the axial direction by the pressure plate moving mechanism, the intermediate plate is moved in the axial direction by an amount smaller than the amount of movement of the pressure plate in the axial direction by the lever mechanism. The ratio of the axial movement amount of the pressure plate to the axial movement amount of the intermediate plate is a value determined by the position of the locking member connected to the intermediate plate at the center of the lever member. , Approximately 2: 1. As the pressure plate and the intermediate plate move in the axial direction, the first frictional connection portion is sandwiched between the flywheel and the intermediate plate, and the second frictional connection portion is sandwiched between the intermediate plate and the pressure plate. The state of torque transmission is switched between a state in which torque is transmitted and a state in which torque is interrupted in which the first frictional connection part is separated from the flywheel and the intermediate plate and the second frictional connection part is separated from the intermediate plate and the pressure plate.

As described above, the ratio between the axial movement amount of the pressure plate and the axial movement amount of the intermediate plate is kept constant by the lever mechanism, but the first frictional connection portion and the second frictional connection portion become worn. When a difference occurs in the wear amount between the two frictional connection portions, a gap is generated between one end of the lever member and the pressure plate or between the intermediate portion of the lever member and the locking member. If no countermeasures are taken against such gaps, the ratio between the axial movement of the pressure plate and the axial movement of the intermediate plate will change, and the simultaneous connection of the clutch and the disengagement of the clutch will deteriorate. I do. On the other hand, the twin clutch according to the present invention takes a measure of providing a wedge-shaped member that moves by centrifugal force. Since the wedge-shaped member has a shape in which the thickness is gradually reduced from the inside to the outside, when the above-described gap occurs, the gap can be filled by centrifugal force. That is, when a gap is formed between one end of the lever member and the pressure plate or between the intermediate portion of the lever member and the locking member due to a difference in the amount of wear between the two frictional connecting portions, the wedge-shaped member is moved outward by centrifugal force. To fill the gap.

[0013] In this case, the simple configuration of providing the wedge-shaped member as described above allows the axial direction of the intermediate plate to be increased with respect to the axially moved amount of the pressure plate even when a difference occurs in the amount of wear between the two friction coupling portions. The state of the movement amount regulation, that is, the ratio of the axial movement amount of the pressure plate to the axial movement amount of the intermediate plate is maintained. A twin clutch according to a second aspect is the twin clutch according to the first aspect, further comprising an inner biasing member that biases the wedge-shaped member inward.

Here, since the inner biasing member is provided, the wedge-shaped member returns to the inside when the twin clutch is not rotating. Further, since the biasing force of the inner biasing member is acting, even when a centrifugal force acts, the wedge-shaped member is prevented from suddenly moving outward. In addition,
As the wedge moves outward by centrifugal force,
The biasing force of the inner biasing member is set smaller than the centrifugal force.

A twin clutch according to a third aspect is the twin clutch according to the second aspect, wherein the pressure plate is
It has a first surface and a second surface. The first surface is a surface substantially orthogonal to the rotation axis of the twin clutch. The second side is the first
The surface is located inside the surface and is substantially parallel to the rotation axis of the twin clutch. The inner biasing member is supported by the pressure plate. The wedge-shaped member is movable along the first surface of the pressure plate, and is pressed against the second surface of the pressure plate by the biasing force of the inner biasing member when no centrifugal force is applied. Becomes

A twin clutch according to a fourth aspect is the twin clutch according to any one of the first to third aspects, wherein the lever member extends so as to be substantially perpendicular to the circumferential direction. Here, the lever member of the lever mechanism, which has conventionally been arranged to extend in the direction along the rotation direction (circumferential direction) of the twin clutch, is extended so as to be substantially orthogonal to the circumferential direction. That is, here, the lever member is arranged such that the lever member extends in a direction substantially along the radial direction of the twin clutch. Therefore, the moving direction of the wedge-shaped member substantially coincides with the longitudinal direction of the lever member, and the lever member does not receive a large force in a direction orthogonal to the longitudinal direction due to the movement of the wedge-shaped member due to centrifugal force. For this reason, the deformation of the lever member is small, and it is possible to suppress such a problem that the locking portion is displaced and the ratio of the axial movement amount of the pressure plate to the axial movement amount of the intermediate plate is changed.

A twin clutch according to a fifth aspect is the twin clutch according to any one of the first to fourth aspects, wherein the pressure plate moving mechanism has a pressing member and a pressure plate moving member. The pressing member is supported by the clutch cover and presses the pressure plate toward the flywheel. The pressure plate moving member is supported by the clutch cover, and can move the pressure plate to the side opposite to the flywheel side.

Here, when the pressing member presses the pressure plate toward the flywheel, the first frictional connection portion is sandwiched between the flywheel and the intermediate plate, and
The friction coupling portion is sandwiched between the intermediate plate and the pressure plate, and the torque from the flywheel is transmitted to the transmission shaft via the first and second clutch disc assemblies. Examples of the pressing member include a diaphragm spring and a coil spring.

Further, the pressure plate moving member moves the pressure plate to the side opposite to the flywheel side, so that the first frictional connection part is separated from the flywheel and the intermediate plate, and the second frictional connection part is separated from the intermediate plate and the pressure plate. As a result, the torque is cut off between the flywheel and the transmission shaft. As a pressure plate moving member,
For example, a member that pulls the pressure plate away from the flywheel based on the principle of leverage, or when the pressure plate is urged to the side opposite to the flywheel side with a force smaller than the pressing force of the pressing member to release the pressure by the pressing member A member that moves the plate to the side opposite to the flywheel side may be used.

A twin clutch according to a sixth aspect is the twin clutch according to any one of the first to fifth aspects, further comprising an urging member. The urging member urges the intermediate plate toward the flywheel. Also, the other end of the lever member is
It comes into contact with the pressure plate from the side opposite to the flywheel side. The locking member abuts a central portion between one end and the other end of the lever member from the side opposite to the flywheel side.

Here, since the biasing member biases the intermediate plate toward the flywheel, the lever member receives a force toward the flywheel from the locking member connected to the intermediate plate. When the pressure plate is pulled away from the flywheel side opposite to this force, the other end of the lever member receives a force from the pressure plate toward the flywheel side. As a result, when the other end of the lever member moves to the side opposite to the flywheel side, the lever member swings around one end of the lever member, so that the center portion of the lever member is smaller than the movement amount of the other end on the flywheel side. And move to the opposite side. Then, the locking member and the intermediate plate move by the same amount to the side opposite to the flywheel side. As a result, the intermediate plate moves in conjunction with the axial movement of the pressure plate, and the amount of movement is smaller than the amount of axial movement of the pressure plate. It is desirable that the amount of movement of the intermediate plate be approximately half the amount of movement of the pressure plate.

On the other hand, when the pressure plate moves to the flywheel side, the intermediate plate is urged toward the flywheel by the urging member, so that the lever is pulled by the locking member connected to the intermediate plate. The central part of the member also moves to the flywheel side. The amount of movement of the central portion of the lever member is determined by the amount of movement of the pressure plate that restricts the movement of the other end of the lever member to the flywheel side, but since the lever member swings around one end as a fulcrum, This is smaller than the movement amount of the pressure plate. It is desirable that the movement amount of the central portion of the lever member, that is, the movement amount of the intermediate plate be about half of the movement amount of the pressure plate.

[0023]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS <Overall Configuration of Twin Clutch> FIGS. 1 and 2 show a twin clutch 1 according to an embodiment of the present invention. The twin clutch 1 is employed in a vehicle, particularly a vehicle having a large required torque transmission capacity, such as a large vehicle or a tractor. The twin clutch 1 applies a torque from an engine side flywheel 2 to an input shaft (not shown) of a transmission. This is a device for transmitting and shutting off. OO in FIG. 1 is the rotation axis of the twin clutch 1. The arrow R1 side of FIG.
And the rotation direction of the twin clutch 1, and the arrow R2 indicates the reverse rotation direction. Hereinafter, the left side of FIG. 1 is referred to as a first axial direction side (engine side), and the right side of FIG. 1 is referred to as a second axial direction side (transmission side).

The twin clutch 1 mainly includes a first clutch
The clutch disk assembly 3 includes a clutch disk assembly 3, a second clutch disk assembly 4, an intermediate plate 11, and a clutch cover assembly 5 fixed to the flywheel 2 via a flywheel spacer 7. Further, the twin clutch 1 includes a lever mechanism 26 and a wedge-shaped member 61. The lever mechanism 26 causes the intermediate plate 11 to interlock with the axial movement of the pressure plate 10 of the clutch cover assembly 5 described later, and makes the axial movement amount of the intermediate plate 11 approximately half of the axial movement amount of the pressure plate 10. It regulates. When the friction disks 3a and 4a, which will be described later, are worn, the wedge-shaped member 61 moves following the difference in the amount of wear, and maintains the degree of regulation of the amount of movement of the intermediate plate 11 in the axial direction by the lever mechanism 26. Play a role.

<Clutch Disk Assembly> First clutch disk assembly 3 and second clutch disk assembly 4
Have a damper made of a spring or a sliding member for attenuating torsional vibration, and a transmission input shaft (not shown) is provided at a central hub portion.
Engage in spline engagement. The two clutch disk assemblies 3 and 4 each have a first friction friction facing or the like.
And the second friction disks 3a and 4a on the outer periphery. The first friction disc 3a of the first clutch disc assembly 3 is disposed close to the friction surface 2a of the flywheel 2. The second friction disk 4a of the second clutch disk assembly 4 is arranged at a position away from the first friction disk 3a in the second axial direction.

<Clutch Cover Assembly> The clutch cover assembly 5 connects the friction disks 3a and 4a to the flywheel 2 so as to rotate integrally with the flywheel 2.
Or, a mechanism for releasing the connection. The clutch cover assembly 5 includes a clutch cover 8, a pressure plate 10, and a pressure plate moving mechanism.

(Clutch Cover, Flywheel Spacer) The clutch cover 8 is an annular member, and is arranged away from the friction surface 2a of the flywheel 2 in the second axial direction. A flywheel spacer 7 is provided between the outer peripheral portion 8b of the clutch cover 8 and the outer peripheral portion of the flywheel 2.
Is arranged. The flywheel spacer 7 is a cylindrical member that covers the outside of the pressure plate 10 and the second friction disc 4a. The flywheel spacer 7 is provided with a plurality of holes 7d (see FIG. 3) penetrating in the axial direction. The outer peripheral portion 8b of the clutch cover 8 is moved to the flywheel 2 by the first bolt 9a penetrating the hole 7d.
Is fixed to the outer periphery. The axial position of the clutch cover 8 with respect to the flywheel 2 is determined by the flywheel spacer 7. The clutch cover 8 and the flywheel spacer 7 are fixed to each other by a second bolt 9b (see FIG. 3) screwed into a bolt hole 7e provided in the flywheel spacer 7, and a third bolt 9c (FIG. 6). ), The flywheel spacer 7 and the flywheel 2 are fixed to each other. Thus, the flywheel spacer 7 is a member fixed to the flywheel 2 together with the clutch cover 8 and can be regarded as a clutch cover in a broad sense.

The first axial end face 7a of the flywheel spacer 7 is in contact with a projection 2b provided in an arc shape on the outer peripheral side of the flywheel 2. A bolt hole into which the above-described first bolt 9a is screwed is formed in the protruding portion 2b. A gap is secured in the axial direction between the first axial side end face 7a and another portion of the flywheel 2 (a portion where the protrusion 2b is not formed).

Further, the flywheel spacer 7 has a first notch 7b (see FIG. 3) for assembling the second strap plate 22, and a second notch 7c for incorporating a support member 29 of the lever mechanism 26 described later. (See Fig. 6)
And The first notch 7b is open on the first axial direction side, and is formed four at equal intervals in the circumferential direction. The second notch 7c is open at the second axial side, and is formed at four positions in the circumferential direction different from the first notch 7b. The portions on both circumferential sides of the second notch 7c of the flywheel spacer 7 are the first bolt 9a and the third bolt 9c.
To the flywheel 2. A hole for fixing the support member 29 is formed in the bottom surface (the surface on the first axial direction side) of the second notch 7c, and the support member 29 is fixed to the flywheel spacer 7 by bolts 30. You.

(Pressure Plate Moving Mechanism) The pressure plate moving mechanism mainly includes a plurality of coil springs 13 and a release lever 43. The coil spring 13 extends in the axial direction. One end of the coil spring 13 contacts the clutch cover 8 from the first axial direction side, and the other end contacts the pressure plate 10 from the second axial direction side. Thereby, the coil spring 13 applies a pressing force to the pressure plate 10 in the first axial direction. A coil spring 1 is provided on both sides of the coil spring 13 in the axial direction.
3 is provided with a cover 14 for covering the outer periphery.

The release lever 43 is a member for releasing the pressing force from the pressure plate 10 on the clutch connecting portion in conjunction with the operation of a clutch operating mechanism (not shown). The four release levers 43 are arranged at equal intervals in the circumferential direction. Each release lever 4
Reference numeral 3 denotes a fulcrum 44 which extends radially and is rotatably supported by a support 46 fixed to the clutch cover 8, and an action portion 4 which rotatably engages with the pressure plate 10.
5 is provided. When a release device (not shown) of the clutch operating mechanism applies a force to the radially inner end 43a of the release lever 43 from the second axial direction to the first axial direction, the release lever 43 moves the fulcrum 44. Rotating about the center, the action portion 45 moves to the second axial direction side. That is, a force greater than the force of the coil spring 13 acts on the pressure plate 10 and the pressure plate 10
It moves away from the friction disc 4a in the second axial direction.

(Pressure Plate) The pressure plate 10 is an annular member arranged close to the second friction disk 4a in the second axial direction. The pressure plate 10 has a friction surface on the second friction disk 4a side. The pressure plate 10 is not rotatable relative to the clutch cover 8 and is movable in the axial direction. Specifically, the pressure plate 10 is fixed to the clutch cover 8 by a plurality of first strap plates 18 arranged to extend in the circumferential direction. Each first strap plate 18 is disposed radially outward of the coil spring 13 in the clutch cover 8 (see FIG. 2). R of the first strap plate 18
The one end is fixed to the clutch cover 8 by a rivet 19 as shown in FIG. An end on the R2 side of the first strap plate 18 is fixed to a protruding portion 10a provided on an outer peripheral portion of the pressure plate 10 with a bolt 20. The clutch cover 8 has a hole 8a for attachment at a portion corresponding to the head of the bolt 20.

The pressure plate 10 is provided with four notches 10d in the circumferential direction on the outer peripheral portion thereof. The notch 10d includes a first surface 10b that is orthogonal to the rotation axis OO of the twin clutch 1 and faces the second axial direction, and a second axial direction from the inner peripheral end of the first surface. A second surface 10c extending outward and facing outward is formed (see FIGS. 4 and 5).

<Wedge-shaped member> The wedge-shaped member 61 has a notch 10 of the pressure plate 10 as shown in FIG.
d, when the twin clutch 1 is not rotating, the first axial side surface is in contact with the first surface 10 b of the pressure plate 10, and the inner surface is the pressure plate 10. Is pressed against the second surface 10c. As shown in FIG. 4, the wedge-shaped member 61 has an inner side (twin) by the other end of a clip (inner biasing member) 62 whose one end is fixed to a surface on the second axial direction side of the pressure plate 10 by a screw 63. (In a direction toward the rotation axis OO of the clutch 1), and is pressed against the second surface 10c of the pressure plate 10.

The surface of the wedge-shaped member 61 on the first axial direction side is an inclined surface 61a. In other words, the wedge-shaped member 61 has a shape in which the thickness gradually decreases from the inside (the right side in FIG. 4) to the outside (the left side in FIG. 4). In a state where the wedge-shaped member 61 is moved outward by centrifugal force and the inclined surface 61a is in contact with the first lever portion 27b of the lever member 27 described later (see FIG. 7), the wedge-shaped member 61 is moved to the lever member 27. Between the end of the first lever portion 27b and the pressure plate 10, and the first lever portion 27b
Link the axial movement of the tip of. FIG. 7 shows the radial position of the wedge-shaped member 61 during rotation. In the state shown in FIG. 4, the twin clutch 1 is assembled between the flywheel 2 and the transmission. When the twin clutch 1 is actually used, the flywheel 2 is always rotating. The pressure plate 10 of the assembly 5 is also constantly rotating. Thus, the pressure plate 1
7, the wedge-shaped member 61 moves outward due to the centrifugal force as shown in FIG. 7, and the wedge-shaped member 61 is moved to the end of the first lever portion 27 b of the lever member 27 and the wedge-shaped member 61 of the pressure plate 10. The space between the first surface 10b is filled. Here, when a force along the axial direction is applied between the end of the first lever portion 27b and the pressure plate 10, an inward force acts on the wedge-shaped member 61. Face 1
0b, the radial position of the wedge-shaped member 61 is maintained.

<Intermediate Plate> The intermediate plate 11 is an annular plate disposed between the first friction disk 3a and the second friction disk 4a. This intermediate plate 11
Has a friction surface facing the first and second friction disks 3a, 4a on both axial side surfaces. Further, the intermediate plate 11 is relatively non-rotatable and axially movable with respect to the flywheel spacer 7. In particular,
The intermediate plate 11 is connected to the flywheel spacer 7 by a plurality of second strap plates 22 provided along the circumferential direction.

The second strap plate 22 is arranged near the flywheel 2 on the outer peripheral side of the intermediate plate 11. Each second strap plate 22
Is a leaf spring extending in an arc shape, and is arranged in the first notch 7 b of the flywheel spacer 7. The second strap plate 22 has an R1 side end fixed to the first axial side end surface 7a of the flywheel spacer 7 by a bolt 23, and an R2 side end provided on the intermediate plate 11 to an outwardly projecting portion 11a. Are fixed to the first axial side end face by bolts 24. In the clutch connection state shown in FIG. 3, the second strap plate 22 is flexed in the axial direction,
(First axial direction side). That is,
When no force is applied to the second strap plate 22, both ends of the second strap plate 22 have a step in the axial direction. This second strap plate 2
The urging force of No. 2 is set to be much smaller than the pressing force of the coil spring 13.

The outwardly protruding portion 11a extends radially outward from the outer peripheral portion of the intermediate plate 11, and is located within the first notch 7b of the flywheel spacer 7 (FIGS. 2 and 3).
reference). <Lever mechanism> The twin clutch 1 further has a lever mechanism 26. The lever mechanism 26 is a mechanism for interlocking the intermediate plate 11 with the axial movement of the pressure plate 10 during the clutch operation, and restricting the axial movement amount of the intermediate plate 11 to about half of the axial movement amount of the pressure plate 10. is there. The lever mechanism 26 is provided at four locations in the circumferential direction, and is arranged near the second notch 7 c of the flywheel spacer 7.

The lever mechanism 26 mainly includes a lever member 27, a locking member 32, a support member 29 and a pin 28 for attaching the lever member 27 to the flywheel spacer 7, and a torsion coil spring (restriction member) 31. It is composed of The lever member 27 includes a supported portion 27a, a first lever portion 27b extending from the supported portion 27a toward the rotation axis OO of the twin clutch 1, and a first lever portion 27.
and a second lever portion 27c extending from the supported portion 27a toward the rotation axis OO of the twin clutch 1 separately from b. The supported portion 27a has a hole through which a pin 28 extending in the circumferential direction penetrates, and is supported by the support member 29 by the pin 28. The support member 29 supports both ends of the pin 28, is accommodated in the second notch 7c of the flywheel spacer 7, and is fixed to the flywheel spacer 7 by the bolt 30 (see FIG. 6).
The inner end (tip) of the first lever portion 27b abuts on the inclined surface 61a of the wedge-shaped member 61 arranged in the notch 10d of the pressure plate 10 from the second axial direction side. The second lever portion 27c is located on the first axial direction side with respect to the first lever portion 27b, and its tip abuts on the second axial direction end portion 32a of the locking member 32 described later from the first axial direction side. . The second lever portion 27c is shorter than the first lever portion 27b, and the rotation center of the lever member 27, that is, the pin 28
Is about half the distance from the center of the pin 28 to the tip where the first lever 27b is in contact with the pressure plate 10 from the center of the pin 28 to the tip where the second lever 27c is in contact with the locking member 32. It is.

The locking member 32 is a band-shaped member, and the first axial side end is provided with a bolt 3 on the outer peripheral surface of the intermediate plate 11.
3 and extends therefrom in the second axial direction (see FIG. 4). The second axial side end 32a of the locking member 32 is bent outward and locked to the distal end of the second lever portion 27c of the lever member 27 from the second axial direction.

The torsion coil spring 31 is supported by a pin 28 as shown in FIG.
Abuts on a part of the support member 29 fixed to the second axial direction, and the other end abuts on the first lever portion 27b of the lever member 27 from the first axial direction. This torsion coil spring 31
In the assembled state, a reaction force is generated such that both ends are separated. Therefore, the lever member 27 is in a state where the first lever portion 27b is constantly receiving a force in the second axial direction,
The force and the force that the locking member 32 applies to the tip of the second lever portion 27c from the second axial direction to the first axial direction are in a state of being balanced.

<Operation of Twin Clutch> Next, the clutch connection operation and the clutch release operation will be described with reference to FIG. FIG. 12 is a cutting characteristic diagram showing the amount of axial movement of the pressure plate 10 and the intermediate plate 11 with respect to the lever stroke (the axial stroke of the distal end 43a of the release lever 43).

(Clutch Release Operation) First, the clutch release operation will be described. When a pressing force acts on the release lever 43 from the release device (not shown) to the first axial direction side from the clutch connection state shown in FIG. 8A, the pressure plate 10 first undergoes an initial loss due to elastic deformation of the clutch cover 8 and the like. Starts moving toward the second axial direction. Specifically, the tip (radial inner end) 43a of the release lever 43 is pushed toward the first axial direction,
The action part 45 moves to the second axial direction side, and the pressure plate 10 starts to move in the direction away from the second friction disc 4a.

Then, with the movement of the pressure plate 10, the tip of the first lever portion 27 b of the lever member 27 is pulled up in the second axial direction via the wedge-shaped member 61, and the lever member 27 is moved around the pin 28. Rotating, the tip of the second lever portion 27c of the lever member 27 is also pulled up in the second axial direction. Along with this, the locking member 32 and the intermediate plate 11 are also pulled up in the second axial direction. At this time, the relationship between the axial movement amounts of the pressure plate 10 and the intermediate plate 11 is determined by the pin 28 and the second lever portion 27c.
12 is about half the distance from the pin 28 to the tip of the first lever portion 27b, so that the movement of the intermediate plate 11 is about half of the movement of the pressure plate 10, as shown in FIG. Becomes

When the lever stroke is maximized, FIG.
As shown in (b), the clutch is completely disengaged (disconnected). In this series of clutch release operations, the radial position of the lever member 27 does not change. (Clutch connection operation) Next, the clutch connection operation will be described.

In the clutch release state in which the lever stroke is at the maximum as shown in FIG. 8B, when the pressing force from the release device to the distal end 43a of the release lever 43 is released, the pressure plate 10 releases the coil spring 13. It moves to the first axial direction side by the force.
Accordingly, the lever member 27 rotates about the pin 28, and the tip of the first lever portion 27b and the second lever portion 27c
Moves toward the first axial direction. Then, the intermediate plate 11 is always in the first strap position by the second strap plate 22.
Since the intermediate plate 11 and the locking member 32 are urged in the axial direction, the intermediate plate 11 and the locking member 32 also move in the first axial direction as the tip of the second lever portion 27c moves.

Finally, as shown in FIG. 8A, the second friction disc 4a is
The first friction disc 3 a is sandwiched between the intermediate plate 11 and the flywheel 2 by the pressing force of the coil spring 13. Thereby, torque is transmitted from the flywheel 2 to the input shaft of the transmission. In addition, in this series of clutch connection operations,
The radial position of the lever member 27 does not change.

(Operation of Twin Clutch When Engine Stops) Next, the operation of the twin clutch 1 when the rotation of the flywheel 2 stops due to the stop of the engine will be described. For example, FIGS. 9A and 7 show the state of the twin clutch 1 when the engine is idling and the transmission is in a neutral state. Here, both friction disks 3a, 4a are sandwiched between the pressure plate 10 and the flywheel 2 via the intermediate plate 11, and the rotation of the flywheel 2 is transmitted from both clutch disk assemblies 3, 4 to the transmission shaft. Has been communicated to.

When the engine is stopped and the rotation of the flywheel 2 is stopped, the rotation of the twin clutch 1 is also stopped, and the centrifugal force acting on the wedge-shaped member 61 disappears. As shown in FIG.
(Not shown in FIG. 9) the wedge-shaped member 6
1 moves inward (lower side in FIG. 9; right side in FIG. 4), and a gap is opened between the wedge-shaped member 61 and the end of the first lever portion 27b of the lever member 27.

(Operation of Twin Clutch When Friction Disc Wears) The twin clutch 1 operates when the first and second friction discs 3a, 4a wear and a difference occurs in the amount of wear between the two friction discs 3a, 4a. The operation is shown in FIGS. FIG. 10 shows a state in which both friction disks 3a and 4a are not worn (a), and the friction disks 3a and 4a are worn and the second friction disk 4a is worn.
Represents the operation of the twin clutch 1 when shifting to the state (b) in which the wear amount of the first friction disc 3a is larger than the wear amount of the first friction disc 3a. The operation of the twin clutch 1 here is an operation in which the radial position of the wedge-shaped member 61 shifts outward.
The amount of wear of the second friction disc 4a is less than the first friction disc 3a.
When the clutch is engaged, the axial distance between the distal end of the first lever portion 27b of the lever member 27 and the first surface 10b of the pressure plate 10 increases when the clutch is engaged. Therefore, the wedge-shaped member 6
If the wedge-shaped member 1 remains at the previous radial position, a gap is opened between the wedge-shaped member 61 and the first lever portion 27b. However, when the twin clutch 1 is used, the centrifugal force due to the rotation is always wedge-shaped member. Since the wedge-shaped member 61 acts on the outer side in the radial direction (FIG. 1) as shown in FIG.
0). Thereby, the wedge-shaped member 61
The thicker part of the gap enters between the tip of the first lever portion 27b and the pressure plate 10, and fills the gap between the tip of the increased first lever portion 27b and the first surface 10b of the pressure plate 10. Therefore, even when the wear amount of the second friction disk 4a becomes larger than the wear amount of the first friction disk 3a, the cutting characteristics shown in FIG. 12 are secured.

FIG. 11 shows a state in which both the friction disks 3a and 4a are not worn (a), and the wear amount of the first friction disk 3a is larger than the wear amount of the second friction disk 4a due to wear. The operation of the twin clutch 1 when shifting to (b) is shown. The operation of the twin clutch 1 here is an operation in which the radial position of the wedge-shaped member 61 shifts inward. When the amount of wear of the first friction disk 3a becomes larger than the amount of wear of the second friction disk 4a, when the clutch is engaged, the tip of the first lever portion 27b of the lever member 27 and the first surface 10b of the pressure plate 10 are connected. In the axial direction becomes narrower than before. Then, the wedge-shaped member 61 gradually moves inward in the radial direction as it wears. As a result, the thinner portion of the wedge-shaped member 61 fills the space between the tip of the first lever portion 27b and the pressure plate 10, and the tip of the first lever portion 27b of the lever member 27 and the pressure plate 10 The distance in the axial direction with respect to the first surface 10b is reduced. Therefore, the amount of wear of the first friction disc 3a is reduced to the second
Even when the wear amount of the friction disk 4a becomes larger than the wear amount, the cutting characteristics shown in FIG. 12 are secured.

However, in the case of the configuration of the twin clutch 1 of the present embodiment, the intermediate plate 11 and the pressure plate 1
The amount of heat radiation of the flywheel 2 is larger than the amount of heat radiation of 0, and there is a high possibility that the amount of wear of the second friction disk 4a is larger than the amount of wear of the first friction disk 3a. Therefore, the possibility of performing the operation shown in FIG. 11 is small, and the shape and dimensions of each member are determined with emphasis on ensuring the operation shown in FIG.

<Features of the Twin Clutch> (1) In the twin clutch 1 of the present embodiment, the flywheel 2, the flywheel spacer 7, the clutch cover 8, the pressure plate 10, and the intermediate plate 11
Are connected in the circumferential direction. The pressure plate 10 and the intermediate plate 11 are axially movable with respect to the flywheel 2, the flywheel spacer 7, and the clutch cover 8, which are fixed and integrated with each other. Since the amount of axial movement of the intermediate plate 11 is restricted to about half of the amount of axial movement of the pressure plate 10 by the lever mechanism 26, as shown in FIG. The three-dimensional bodies 3 and 4 are connected almost simultaneously, and the torque transmission by the two clutch disk assemblies 3 and 4 is cut off almost simultaneously at the time of clutch release.

(2) In this embodiment, the lever member of the lever mechanism, which has conventionally been arranged to extend in the circumferential direction of the twin clutch 1, is arranged to extend radially. Thus, if the supported portion 27a of the lever member 27 is supported by the flywheel spacer 7, the tip end of the first lever portion 27b naturally becomes a flywheel spacer without protruding outward from the pressure plate 10. Pressure plate 1 inside 7
It comes to a position where it can be locked to zero.

Further, since the lever member 27 extends radially inward of the twin clutch 1, the second portion of the flywheel spacer 7 provided for disposing the lever mechanism 26 is provided.
The size of the notch 7c is kept small. In addition, since the second notch 7c is provided only for disposing the lever member 27 separately from the first notch 7b, the lever member 27 that is thicker in the axial direction can be employed. For this reason, the rigidity of the lever member 27 can be set high, and the possibility that the characteristic shown in FIG. 12 is lost due to deformation of the first lever portion 27b or the second lever portion 27c is reduced.

(3) In this embodiment, the locking member 32 is not locked to the central portion of the first lever portion 27b of the lever member 27, but the second lever portion is provided separately from the first lever portion 27b. 27c is provided, and the locking member 32 is locked at the tip of the second lever portion 27c. Second lever 27
c is disposed closer to the first axial direction than the first lever portion 27b, and the locking member 32 overlapping the first lever portion 27b in plan view can be locked to the tip of the second lever portion 27c. I have. By providing the second lever portion 27c in addition to the first lever portion 27b in this manner, the locking member 32 can be attached to the central portion (the second lever portion) of the lever member 27 without making the locking member 32 complicated. 27c).

(4) In the twin clutch 1 of this embodiment, the ratio between the axial movement amount of the pressure plate 10 and the axial movement amount of the intermediate plate 11 is kept constant by the lever mechanism 26 as described above. When the first friction disk 3a and the second friction disk 4a wear and the amount of wear of the two friction disks 3a, 4a becomes different, the tip of the first lever portion 27b of the lever member 27 and the first The size of the gap with the one surface 10b changes (see FIGS. 10 and 11).

However, in the twin clutch 1 of the present embodiment, the wedge-shaped member 61 which moves by centrifugal force causes
It is possible to cope with a change in the size of the gap between the tip of the first lever portion 27b of the lever member 27 and the first surface 10b of the pressure plate 10. Thereby, the friction disk 3
Even when a and 4a are worn, the ratio of the axial movement amount of the pressure plate 10 to the axial movement amount of the intermediate plate 11 is maintained.

Further, since the clip 62 for urging the wedge-shaped member 61 toward the rotation axis OO of the twin clutch 1 is provided, even when a centrifugal force is applied to the wedge-shaped member 61, the wedge is formed. The sudden movement of the shape member 61 outward is avoided, and the impact of the collision between the inclined surface 61a of the wedge-shaped member and the first lever portion 27a of the lever member 27 is suppressed. Note that the urging force of the clip 62 is set to be much smaller than the centrifugal force so that the wedge-shaped member 61 can move outward reliably by the centrifugal force.

(5) In the twin clutch 1 of the present embodiment, since the lever mechanism 26 is provided with the torsion coil spring 31, the lever member 27 does not freely swing in the assembled state. In addition, there is always no gap between the tip of the second lever portion 27c of the lever member 27 and the locking member 32, and they do not collide with each other.

[Other Embodiments] In the above embodiment, the wedge-shaped member 61 is supported on the pressure plate 10 by the clip 62, and the wedge-shaped member 61 is connected to the tip of the first lever portion 27 b of the lever member 27 and the pressure plate 10. And the first surface 10b.

However, the wedge-shaped member 6 is not necessarily provided between the end of the first lever portion 27b and the pressure plate 10.
Even if the first disk 1 is not provided, the difference in wear between the friction disks 3a and 4a can be absorbed even if the following configuration is adopted. That is, instead of the configuration of the above-described embodiment, the tip of the first lever portion 27b of the lever member 27 is always locked to the pressure plate 10 so that the second lever portion 27
c, and the arrangement of the locking member 32 is changed so that the intermediate plate 11 holds the wedge-shaped member movably in the radial direction, and the wedge-shaped member enters between the front end of the second lever portion 27c and the locking member 32. Such a configuration is adopted. Even in the case of such a configuration, even if a difference occurs between the wear amounts of the friction disks 3a and 4a and the dimension between the locking member 32 and the tip of the second lever portion 27c changes, the wedge-shaped member is not changed. The dimensional change is absorbed by the radial movement.

[0063]

According to the present invention, the lever mechanism is provided with a simple structure in which the twin clutch is provided with a wedge-shaped member having a gradually decreasing thickness from the inside to the outside. Since the gap created is filled by centrifugal force, the ratio between the axial displacement of the pressure plate and the axial displacement of the intermediate plate is maintained even if there is a difference in the amount of wear between the friction disks. You.

[Brief description of the drawings]

FIG. 1 is a schematic longitudinal sectional view of a twin clutch according to an embodiment of the present invention.

FIG. 2 is a partially transparent plan view of the twin clutch.

FIG. 3 is a side view as viewed in the direction of the arrow III in FIG. 2;

FIG. 4 is an enlarged vertical sectional view near a lever mechanism.

FIG. 5 is an enlarged perspective plan view near the lever mechanism.

FIG. 6 is a side view as seen in the direction of arrow VI in FIG. 2;

FIG. 7 is an enlarged vertical sectional view near the lever mechanism during rotation.

FIG. 8 is a conceptual diagram of the operation of a twin clutch.

FIG. 9 is a layout view of a wedge-shaped member during rotation and non-rotation.

FIG. 10 is a diagram illustrating a change in the posture of the lever mechanism when the friction disk is worn.

FIG. 11 is a view showing a state of a posture change of a lever mechanism when a friction disk is worn.

FIG. 12 is a graph showing the disengagement characteristics of a twin clutch.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Twin clutch 2 Flywheel 3 1st clutch disk assembly 3a 1st friction disk (1st friction connection part) 4 2nd clutch disk assembly 4a 2nd friction disk (2nd friction connection part) 5 Clutch cover assembly 7 Flywheel spacer 8 Clutch cover 10 Pressure plate 11 Intermediate plate 13 Coil spring (pressing member) 26 Lever mechanism 27 Lever member 32 Locking member 43 Release lever (Pressure plate moving member) 61 Wedge-shaped member 62 Clip (Inward biasing member) )

Claims (6)

[Claims] 1. A twin clutch for transmitting and interrupting torque between a flywheel having a friction surface and a transmission shaft, comprising: a first clutch disposed in close proximity to a friction surface of the flywheel.
A first clutch disc assembly having a frictional connection portion and capable of transmitting torque to the shaft; and a second frictional connection portion disposed on a side of the first frictional connection portion opposite to the flywheel side, A second clutch disc assembly capable of transmitting torque to the shaft; a clutch cover disposed on a side of the second friction coupling portion opposite to the flywheel side and fixed to the flywheel; A flywheel spacer fixed to a clutch cover and interposed between the flywheel and the clutch cover in the axial direction; and a flywheel spacer disposed between the first frictional connection portion and the second frictional connection portion in the axial direction. An intermediate plate that rotates in conjunction with a wheel spacer; an intermediate plate that is disposed axially between the second frictional connection portion and the clutch cover; A pressure plate that rotates in conjunction with a bar; a pressure plate moving mechanism that is supported by the clutch cover and moves the pressure plate in the axial direction; and an axial movement amount of the intermediate plate with respect to an axial movement amount of the pressure plate. A lever member having one end supported by the flywheel spacer and the other end locked to the pressure plate, and a mechanism supported by the intermediate plate between one end and the other end of the lever member. A wedge-shaped member having a locking member that locks to a central portion of the wedge-shaped member, the wedge-shaped member having a gradually decreasing thickness from the inside to the outside, and is moved outward by centrifugal force to form one end of the lever member. The gap between the pressure plate or the intermediate portion of the lever member and the locking member A wedge-shaped member that fills the gap between the twin clutches. 2. The twin clutch according to claim 1, further comprising an inner urging member for urging the wedge-shaped member inward. 3. The pressure plate according to claim 1, wherein the pressure plate has a first surface substantially perpendicular to a rotation axis, and a second surface inside the first surface and substantially parallel to the rotation axis. A member is supported by the pressure plate, and the wedge-shaped member is a first member of the pressure plate.
The twin clutch according to claim 2, wherein the twin clutch is movable along a surface, and is pressed against the second surface of the pressure plate by an urging force of the inner urging member when no centrifugal force is applied. . 4. The twin clutch according to claim 1, wherein said lever member extends substantially orthogonally to a circumferential direction. 5. The pressure plate moving mechanism includes a pressing member supported by the clutch cover and pressing the pressure plate toward the flywheel, and a pressure member supported by the clutch cover and moving the pressure plate opposite to the flywheel side. The twin clutch according to any one of claims 1 to 4, further comprising a pressure plate moving member that can move the pressure plate. 6. The lever member has the other end in contact with the pressure plate from the side opposite to the flywheel side, and the locking member has a center portion between one end and the other end of the lever member. The twin clutch according to any one of claims 1 to 5, further comprising: a biasing member that abuts on a side opposite to a flywheel side and biases the intermediate plate toward the flywheel side.