JP2000329158A - Flywheel spacer assembly and twin clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To stabilize the friction coefficient of a mechanism for adjusting wear in a lever mechanism in a twin clutch. SOLUTION: This flywheel spacer assembly 7 is used for a twin clutch. The flywheel spacer assembly 7 is provided with a flywheel spacer body 7f fixedly connected between the axial directions of a flywheel and a clutch cover 8, and a lever mechanism 26. The lever mechanism 26 is a mechanism for regulating the axial moving amount of an intermediate plate 11 to the axial moving quantity of a pressure plate 10, and is provided with a lever member 27 with an R1 side end 27a journalled to the flywheel spacer body 7f so as to make an R2 side end 27b axially movable, and a wear compensating mechanism 29 disposed between the R2 side end 27b and R1 side end 27a of the lever member 27 and frictionally locked in the axially movable manner to the lever member 27.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch for transmitting and interrupting torque from a flywheel to a transmission shaft, and more particularly to a twin clutch in which two frictional connecting portions are arranged with an intermediate member interposed therebetween, and a twin clutch. The present invention relates to a flywheel spacer assembly used for a clutch.

[0002]

2. Description of the Related Art A clutch is a device for transmitting and interrupting torque between an engine side flywheel and a transmission shaft. The clutch mainly includes a clutch disk assembly and a clutch cover assembly. The clutch disk assembly has a friction disk provided on an outer peripheral portion and a hub engaged with an input shaft of a transmission on an inner peripheral portion. The friction disk and the hub are connected by a plurality of plates and elastic members. The clutch cover assembly releases the clutch by pressing the friction disk of the clutch disk assembly against the flywheel or releasing the pressing force. The clutch cover assembly mainly includes a clutch cover fixed to the flywheel and covering the clutch disk assembly from the outer periphery, a pressure plate disposed on the transmission side of the friction disk and capable of rotating integrally with the clutch cover, and a clutch cover. And a pressing mechanism for applying a pressing force to the pressure plate.

When a large torque transmission capacity must be ensured in a limited space, a twin clutch with two friction disks is used. The twin clutch includes a first clutch disk assembly having a first friction disk, a second clutch disk assembly having a second friction disk disposed on the transmission side of the first friction disk, and first and second friction disks. And a strap plate for biasing the intermediate plate in a direction away from the flywheel. The intermediate plate is mounted so as not to rotate relative to the flywheel and to be movable in the axial direction. Friction surfaces for the first and second friction disks are formed on both side surfaces.

When the clutch is connected, the pressure plate of the clutch cover assembly is pressed toward the flywheel by a pressing mechanism including a diaphragm spring or the like.
A first friction disc is sandwiched between the flywheel and the intermediate plate, and a second friction disc is sandwiched between the intermediate plate and the pressure plate. When the clutch is released, the pressure on the pressure plate is released, and the pressure plate and the intermediate plate are separated from the flywheel by the strap plate. As a result, the connection between the friction disks is released.

[0005] In the twin clutch described above,
It is preferable that the first friction disk and the second friction disk are simultaneously connected during a clutch operation (clutch connection, clutch release). Further, in the clutch disengagement characteristics, it is preferable that the lift amount of the intermediate plate relative to the lever stroke is always １ ／ of that of the pressure plate in all regions. If the intermediate plate is too close to or too far from the pressure plate, it means that the intermediate plate is in contact with the first or second friction disc and deteriorates the disengagement performance of the clutch.

The twin clutch disclosed in Japanese Patent Application Laid-Open No. 63-235724 is provided with a lever mechanism for achieving the above two objects. The lever mechanism mainly includes a lever member. One end of the lever member is swingably supported by the clutch cover, and the other end is movable in the axial direction. The other end is operably contacted with the pressure plate from the flywheel side. The intermediate plate is provided with a contact portion that contacts the intermediate portion of the lever member from the flywheel side. With this structure, during the operation of the clutch, the axial movement amount of the intermediate plate is always の of the axial movement amount of the pressure plate, and the coupling and release of the clutch are performed simultaneously.

In this lever mechanism, the contact portion is frictionally locked to the intermediate plate so as to be movable in the axial direction. As a result, when the wear amount of the second friction disk becomes larger than that of the first friction disk, the lever member moves the contact portion toward the flywheel in the axial direction with respect to the intermediate plate. Thereby, the movement of the pressure plate toward the flywheel side in the axial direction is not limited by the lever mechanism, and as a result, a sufficient pressing load on the second friction disc can be secured.

[0008]

In the lever mechanism described above, the contact portion is frictionally locked to the intermediate plate.
The friction coefficient of the friction sliding surface (the contact surface between the contact portion and the intermediate plate) tends to change due to the heat transmitted from the intermediate plate. In particular, since the intermediate plate is in contact with both the first friction disk and the second friction disk, heat is easily generated, and the frictional sliding surface has a large load due to heat.

An object of the present invention is to stabilize the friction coefficient of a mechanism for adjusting wear in a lever mechanism in a twin clutch.

[0010]

SUMMARY OF THE INVENTION A flywheel spacer assembly according to the present invention is used in a twin clutch for transmitting and interrupting torque from a flywheel having a friction surface to a transmission shaft. The twin clutch includes first and second clutch disc assemblies, an intermediate member, a pressure plate, a pressing mechanism, a biasing member, and a clutch cover. First
And the second clutch disk assembly include first and second friction coupling portions, respectively. The intermediate member may be disposed between the first frictional connection portion and the second frictional connection portion in the axial direction. The pressure plate may be located on the transmission side of the second friction connection. The pressing mechanism is a member for applying a pressing force to the pressure plate. The urging member is a member for urging the intermediate member in a direction away from the friction surface. The clutch cover is the first
And the second clutch disc assembly. The flywheel spacer assembly has a flywheel spacer body and a lever mechanism. The flywheel spacer body is fixedly connected between the flywheel and the clutch cover in the axial direction. The lever mechanism is a mechanism for regulating the axial movement amount of the intermediate member with respect to the axial movement amount of the pressure plate. The lever mechanism includes a lever member whose base end can be axially supported by the clutch cover so that the front end can be moved in the axial direction, and is disposed between the front end and the base end of the lever member so that the lever member can move in the axial direction. And a locking member frictionally locked. A pressure plate comes into contact with the tip of the lever member from the transmission side. An intermediate member comes into contact with the locking member from the flywheel side.

In the flywheel spacer assembly according to the first aspect, the lever mechanism causes the pressure plate and the intermediate member to abut on the distal end and the intermediate portion of the lever member, respectively, and uses the base end of the lever member as a fulcrum. , The axial movement amount of the intermediate member is regulated. In this case, the frictional connection between the locking member and the lever member can be achieved by frictionally locking the locking member at the intermediate portion of the lever member where the influence of heat by the frictional connection portion is small so as to be movable in the axial direction. The friction coefficient of the sliding surface can be stabilized.

A flywheel spacer assembly according to a second aspect of the present invention is the flywheel spacer assembly according to the first aspect, wherein the lever member has a hole between the distal end and the proximal end, and the locking member. Has a bush frictionally locked in the hole, and a support member sandwiched between the flywheel-side end surface of the bush and the intermediate member. In the flywheel spacer assembly according to the second aspect, the support member transmits the urging force of the urging member to the lever member, and transmits the pressing force of the pressing mechanism to the intermediate member.

According to a third aspect of the present invention, there is provided a flywheel spacer assembly according to the first or second aspect, wherein the supporting member has an abutting surface which abuts on the intermediate member. The surface is convex toward the intermediate member.
In the flywheel spacer assembly according to claim 3,
The lever member can rotate in the axial direction about the contact surface of the support member.

According to a fourth aspect of the present invention, there is provided a twin clutch for transmitting and interrupting torque from a flywheel having a friction surface to a transmission shaft, wherein a first clutch disk assembly and a second clutch disk are provided. An assembly, a clutch cover, an intermediate member, a pressure plate, a pressing mechanism, a biasing member, and a flywheel spacer assembly according to any one of claims 1 to 3 are provided. The first clutch disc assembly has a first friction coupling portion disposed close to the friction surface, and is capable of transmitting torque to the shaft. The second clutch disc assembly has a second friction coupling portion disposed on the transmission side of the first friction coupling portion, and is capable of transmitting torque to the shaft. A clutch cover is fixed to the flywheel and covers the first and second clutch disc assemblies. The intermediate member is disposed axially between the first friction connection portion and the second friction connection portion, and is rotatable integrally with the flywheel. The pressure plate is arranged on the transmission side of the second friction coupling portion, and is rotatable integrally with the clutch cover. The pressing mechanism is a member that is supported by the clutch cover and applies a pressing force to the pressure plate. The urging member is a member for urging the intermediate member in a direction away from the friction surface.

In the twin clutch according to the fourth aspect, when the pressing of the pressure plate toward the flywheel by the pressing mechanism is released, the pressure plate is moved to the second position.
Away from the friction connection, the intermediate member is separated from the friction surface of the flywheel by the biasing member. As a result, transmission of power from the flywheel to the transmission shaft via the first and second clutch disc assemblies is shut off. During this clutch release, the axial movement amount of the intermediate member is limited to a predetermined amount by the lever mechanism of the flywheel spacer assembly. Specifically, the intermediate member abuts on the locking member of the lever member, so that the intermediate member does not approach the pressure plate more than necessary. As a result, the disengagement performance of the clutch is improved. Further, when the clutch is connected, 2
Simultaneous connection of the two clutch disk assemblies can be maintained, and stable torsional characteristics are maintained.

Further, when a greater amount of wear is generated in the second frictional connection portion than in the first frictional connection portion when the clutch is engaged, a force from the pressure plate acts on the lever member, and the shaft is moved between the lever member and the locking member. Slip occurs in the direction. As a result, the lever member keeps satisfactorily abutting on the pressure plate and the intermediate member irrespective of the deviation of the degree of wear of the two frictional connection parts. Further, since a mechanism for compensating wear of the second frictional connection portion is provided not on the intermediate member but on the lever member, the heat load on the frictional sliding portion between the lever member and the locking member is small, and the frictional sliding is reduced. The friction coefficient of the part becomes stable.

A twin clutch according to a fifth aspect is the twin clutch according to the fourth aspect, wherein the clutch cover and the flywheel spacer assembly are formed as separate members and fixedly connected to each other.

[0018]

FIG. 1 shows a vehicle M (for example, a large vehicle or a tractor) provided with a twin clutch 1 according to the present invention. The vehicle M is provided with a twin clutch 1 between the flywheel 2 on the engine E side and the transmission T for connecting the two. The twin clutch 1 and the transmission T are connected by a shaft T1.

OO in FIG. 2 is a rotation axis.
The arrow R1 side in FIG. 3 is the rotation direction of the flywheel 2 and the twin clutch 1, and the arrow R2 is the opposite rotation direction. Note that the left side of FIG. 2 is the first axial direction side (engine side), and the right side of FIG. 2 is the second axial direction side (transmission side). In FIG. 2, the twin clutch 1
Is a member for transmitting and interrupting torque from the flywheel 2 having the friction surface 2a to the shaft T1 (FIG. 1) of the transmission T. The twin clutch 1 mainly includes a first clutch disc assembly 3, a second clutch disc assembly 4, and a clutch cover assembly 5 fixed to the flywheel 2.

The first clutch disk assembly 3 and the second clutch disk assembly 4 both have a spring for damping torsional vibration and a damper composed of a sliding member, and have a transmission shaft T1 (FIG. 2). Are omitted) in the center. Each of the two clutch disk assemblies 3 and 4 has first and second friction disks 3a and 4a formed of friction facing and capable of transmitting torque to the shaft T1 at the outer peripheral portions.
First friction disc 3a of first clutch disc assembly 3
Are arranged close to the friction surface 2 a of the flywheel 2. The second friction disc 4a of the second clutch disc assembly 4 is arranged on the transmission T side of the first friction disc 3a.

The clutch cover assembly 5 is a mechanism for connecting or disconnecting the friction disks 3a and 4a so as to rotate integrally with the flywheel 2. The clutch cover assembly 5 mainly includes a clutch cover 8, a pressure plate 10, an intermediate plate 11, a first strap plate 22, a pressing mechanism 12, and a flywheel spacer assembly 7. The clutch cover 8 is a disk-shaped and annular member fixed to the flywheel 2, and includes first and second clutch disc assemblies 3, 3.
4 is arranged so as to cover the outer peripheral side.

On the flywheel 2 side of the clutch cover 8, a flywheel spacer assembly 7 is disposed. The flywheel spacer assembly 7 has a flywheel spacer body 7f fixedly connected between the outer peripheral portion 8b of the clutch cover 8 and the outer peripheral portion of the flywheel 2 in the axial direction, and a lever mechanism 26 described later. ing. The flywheel spacer body 7f is a cylindrical member that covers the outer peripheral sides of the intermediate plate 11 and the second friction disc 4a.
The flywheel spacer body 7f is provided with a plurality of holes 7d penetrating in the axial direction. The first bolt 9a penetrating through the hole 7d fixes the outer peripheral portion 8b of the clutch cover 8 to the outer peripheral portion of the flywheel 2. The axial position of the clutch cover 8 with respect to the flywheel 2 is determined by the flywheel spacer body 7f. That is, in the present embodiment, the clutch cover 8 and the flywheel spacer assembly 7 are formed as separate members, and are fixedly connected to each other by the second bolt 9b. The second bolt 9b has a shorter axial dimension than the first bolt 9a, and is screwed into a bolt hole 7e (FIG. 4) provided in the flywheel spacer body 7f. The flywheel spacer body 7f is a member fixed to the flywheel 2 together with the clutch cover 8, and is a clutch cover in a broad sense. First flywheel spacer body 7f
The axial end surface 7a is in contact with a protruding portion 2b (FIG. 2) provided in an arc shape on the outer peripheral side of the flywheel 2. FIG.
As shown in the figure, the flywheel spacer body 7f includes:
Notch 7b for disposing a lever mechanism 26 and the like to be described later
Is provided. The notch 7b is open on the first axial side (the lower side in FIG. 4). A plurality of notches 7b are formed at equal intervals in the circumferential direction.

The pressing mechanism 12 shown in FIG. 2 mainly includes a plurality of coil springs 13 and a release lever 43. The coil spring 13 extends in the axial direction, and has one end supported by the clutch cover 8 and the other end supported by the pressure plate 10. Thus, the coil spring 13 applies a pressing force to the pressure plate 10 in the first axial direction. On both axial sides of the coil spring 13, covers 14 are provided to cover the outer periphery of the coil spring 13.

The release lever 43 is a member for releasing the pressing force on the pressure plate 10 by a clutch operating mechanism (not shown). Release lever 43
Consists of a plurality of members arranged at equal intervals in the circumferential direction. Each release lever 43 extends radially, and has a fulcrum 44 swingably supported by a support 46 extending from the clutch cover 8, and an action portion 45 swingably engaged with the pressure plate 10. When a release device (not shown) applies a force to the radially inner end 43a of the release lever 43 from the second axial direction side, the release lever 43 swings about a fulcrum 44, and the action portion 45 moves to the second axial direction side. Go to That is, the pressure plate 10
When the force greater than the force from the coil spring 13 acts on the pressure plate 10, the pressure plate 10
Move in the direction away from a.

The pressure plate 10 is an annular member arranged on the transmission side of the second friction disc 4a. The pressure plate 10 can rotate integrally with the clutch cover 8 and can move in the axial direction. Specifically, the pressure plate 10 is fixed to the clutch cover 8 by a plurality of second strap plates 18 arranged in the circumferential direction. Each second strap plate 1
Reference numeral 8 is disposed radially outside the coil spring 13 in the clutch cover 8. The R1 side end of the second strap plate 18 is fixed to the clutch cover 8 by a rivet 19. Second strap plate 18
Of the pressure plate 10 is fixed to a protruding portion 10 a provided on an outer peripheral portion of the pressure plate 10 by a bolt 20. A hole 8a is formed in the clutch cover 8 at a portion corresponding to the head of the bolt 20.

As shown in FIG. 4, the pressure plate 10 has a contact plate 36 fixed to the outer peripheral surface. The contact plate 36 is a pressure plate 10
A fixed portion 36a fixed to the outer peripheral surface of the flywheel by two bolts 37, and an extended portion extending radially outward from the first axial side end of the fixed portion 36a and extending into the notch 7b of the flywheel spacer body 7f. 36b. The contact plate 36 is attached to the pressure plate 10 by bolts 37 and operates as a part of the pressure plate 10. The bolt 37 is provided with a notch 7b of the flywheel spacer body 7f from the radial outside.
Through the pressure plate 10.

The intermediate plate 11 includes the first friction disc 3
and a ring-shaped plate disposed between the second friction disc 4a and the second friction disc 4a in the axial direction. The intermediate plate 11 has friction surfaces facing the first and second friction disks 3a, 4a on both axial side surfaces, and can rotate integrally with the flywheel 2. The contact member 30 is attached to the intermediate plate 11 by a bolt 33 and operates as a part of the intermediate plate 11. The bolt 33 is detachable from the radially outer side of the intermediate plate 11 through the notch 7b of the flywheel spacer body 7f.

The intermediate plate 11 is integrally rotatable and axially movable with respect to the flywheel spacer body 7f. Specifically, the intermediate plate 11 is fixed to the flywheel spacer main body 7f by a plurality of first strap plates 22 provided side by side in the circumferential direction. The first strap plate 22 includes the intermediate plate 11
Is arranged in the vicinity of the flywheel 2 in the outer peripheral portion. Each first strap plate 22 is a leaf spring, and is arranged in the notch 7b of the flywheel spacer body 7f. The first strap plate 22 has an R
One end is fixed to the first axial side end surface 7a of the flywheel spacer body 7f by bolts 23, and the R2 end is fixed to the first axial side end surface of the protruding portion 11a provided on the intermediate plate 11 by bolts 24. Have been. In the clutch connected state shown in FIG. 4, the first strap plate 22
It bends in the axial direction, and applies an urging force to the intermediate plate 11 in a direction away from the flywheel 2. The protruding portion 11a extends radially outward from the outer peripheral portion of the intermediate plate 11, and extends into the notch 7b of the flywheel spacer body 7f.

The lever mechanism 26 of the flywheel spacer assembly 7 is a mechanism for regulating the axial movement of the intermediate plate 11 to a predetermined ratio with respect to the axial movement of the pressure plate 10 during the operation of the clutch. . Each lever mechanism 26 has a notch 7 in the flywheel spacer body 7f.
b. The lever mechanism 26 mainly includes a lever member 27 and a wear compensation mechanism 29. The lever member 27 is a member extending in a direction tangential to the outer periphery of the twin clutch 1. The lever member 27 is made of sheet metal.

The R1 side end 27a of the lever member 27 is
The side end 27b is pivotally supported by the flywheel spacer body 7f so as to be movable in the axial direction. Specifically, the R1 side end 27a of the lever member 27 is supported by the flywheel spacer main body 7f by a swing pin 47 that penetrates the flywheel spacer main body 7f in the radial direction. As a result, the R2 side end 27b of the lever member 27 is movable in the axial direction. The contact plate 36 of the pressure plate 10 contacts the R2 end 27b of the lever member 27 from the second axial direction side. Lever member 2
7, an abutment member 30 of the intermediate plate 11 abuts from the first axial direction side via an abrasion compensation mechanism 29 described later on an intermediate portion 27c disposed between the R1 side end 27a and the R2 side end 27b. ing. The ratio between the length between the R1 side end 27a and the R2 side end 27b and the length between the R1 side end 27a and the intermediate portion 27c is 1: 0.5. That is, the contact member 30
Is in contact with an intermediate portion 27c located at an intermediate position of the lever member 27.

Next, the wear compensation mechanism 29 will be described.
The wear compensating mechanism 29 is disposed at an intermediate portion 27c of the lever member 27. As shown in FIGS. 4 and 5, the wear compensating mechanism 29 includes a substantially cylindrical roll pin 40 frictionally engaged with the intermediate portion 27c, and a stud pin 39 fitted into the roll pin 40 from the first axial direction side. ing. The intermediate portion 27c has a cylindrical tubular portion 2 protruding toward the second axial direction.
7d is formed. A roll pin 40 is frictionally locked in the hole of the cylindrical portion 27 d so as to be axially movable with respect to the lever member 27. The contact member 30 contacts the stud pin 39 of the wear compensation mechanism 29 from the first axial direction side.

The roll pin 40 is a member extending in the axial direction and further including a slit extending in the axial direction.
By pressing itself against the inner surface of the cylindrical portion 27d,
It is frictionally locked in the hole of the cylindrical portion 27d. That is, the roll pin 40 cannot move with respect to the cylindrical portion 27d until a force equal to or more than a predetermined force acts in the first axial direction. The stud pin 39 includes a head portion 39a and a cylindrical portion 39b extending therefrom in the second axial direction. Head 39a
Is larger in diameter than the cylindrical portion 39b. The head 39 a is sandwiched between the first axial end face of the roll pin 40 and the contact member 30. The first axial side end surface of the head 39 a is a contact surface that contacts the contact member 30, and the contact surface is a spherical surface that is convex toward the contact member 30. The cylindrical portion 39b extends inside the roll pin 40 and penetrates the roll pin 40 and the cylindrical portion 27d. Thus, the stud pin 39
Receives the force from the lever member 27 during the clutch release operation and transmits the force to the first axial end surface of the roll pin 40, or the lever member 27 during the clutch coupling operation.
This is a member for transmitting the force from the intermediate plate 11 to the intermediate plate 11.

Next, the movement of each member at the time of a normal clutch connection operation and a clutch release operation will be described with reference to FIGS. 6 to 9 are schematic diagrams for explaining the operation. When a pressing load acts on the release lever 43 from a release device (not shown) in the clutch engagement state shown in FIGS. 6 and 8, the state shifts to the state shown in FIG. Specifically, the radial inner end 43a of the release lever 43 is pushed toward the first axial direction, and the action portion 45 moves toward the second axial direction. That is, the pressure plate 10
Moves in a direction away from the second friction disc 4a. Accordingly, the intermediate plate 11 is moved in a direction away from the first friction disc 3a, that is, toward the pressure plate 10 by the urging force from the first strap plate 22. At this time, due to the operation of the lever mechanism 26, the axial movement amount of the intermediate plate 11 is half of the axial movement amount of the pressure plate 10 over the entire lever stroke. That is, the gap between the pressure plate 10 and the intermediate plate 11 and the gap between the intermediate plate 11 and the flywheel 2 are kept equal in the entire stroke range.

The mechanism for realizing the above operation will be described in more detail. The intermediate plate 11 pushes the intermediate portion 27c of the lever member 27 toward the second axial direction by the contact member 30. At this time, the axial movement amount of the intermediate portion 27c is limited by the movement amount of the R2 side end 27b. That is, the axial movement amount of the intermediate portion 27c is half of the axial movement amount of the R2 side end 27b (equal to the axial movement amount of the pressure plate 10).
The amount of axial movement of the intermediate plate 11 does not exceed half the amount of axial movement of the pressure plate 10. At this time, the friction coefficient is set so that no slippage occurs between the cylindrical portion 27d and the roll pin 40 in the wear compensation mechanism 29.

As described above, since the intermediate plate 11 has a half allowance of the pressure plate 10 over the entire release area, the disconnection characteristics of the clutch can be well maintained. From the clutch release state shown in FIG. 7 and FIG.
When the pressure is released, the state shifts to the clutch engaged state shown in FIGS. Specifically, the pressing of the release lever 43 on the radially inner end 43a in the first axial direction is released, and the pressure plate 10
To move in the first axial direction. At this time, the intermediate plate 11 starts moving at the same time as the pressure plate 10 due to the operation of the lever mechanism 26. The moving amount of the intermediate plate 11 is half of the moving amount of the pressure plate 10 over the entire stroke area. That is, the gap between the pressure plate 10 and the intermediate plate 11 and the gap between the intermediate plate 11 and the flywheel 2 are reduced uniformly, and finally the connection is completed simultaneously. The pressure plate 10 always moves the intermediate plate 11 toward the first axial direction by の of its own axial movement amount via the lever mechanism 26.

The mechanism for realizing the above operation will be described in more detail. Pressure plate 10
The contact member 3 via the intermediate portion 27c of the lever member 27.
0 (that is, the intermediate plate 11) is pushed toward the first axial direction. At this time, in the lever member 27 of the lever mechanism 26, the axial movement amount of the intermediate portion 27c is half of the axial movement amount of the R2 side end 27b (equal to the axial movement amount of the pressure plate 10). As a result, the intermediate portion 27
c is equal to R2.
This is half of the axial movement amount of the pressure plate 10 that contacts the side end 27b. Thereby, particularly, the amount of movement of the intermediate plate 11 in the axial direction is reduced by the pressure plate 1.
Since it does not become less than half of the axial movement of zero, a good connection of the clutch is ensured. At this time, a friction coefficient is set between the cylindrical portion 27d of the wear compensation mechanism 29 and the roll pin 40 so as not to cause slippage.

As described above, the first friction disc 3
a and the second friction disc 4a are simultaneously connected. For this reason, the other clutch disk assembly is connected in a state where the clutch disk assembly connected earlier is twisted due to the time difference of the clutch connection, and the angle of the torsional characteristic in each clutch disk assembly 3 and 4 is shifted. Such a problem can be prevented.

Next, the operation of the wear compensation mechanism 29 when the first friction disk 3a and the second friction disk 4a are worn will be described with reference to FIGS. In addition,
10 to 12 are schematic diagrams for explaining the operation,
13 and 14 are partially enlarged views thereof. The clutch connection state shown in FIG. 10 corresponds to FIG. 6 and FIG. From this state, when the first friction disk 3a and the second friction disk 4a are both worn and the wear amount is the same, the state shown in FIG. 11 is obtained. That is, the intermediate plate 11 moves toward the flywheel 2 by the wear amount of the first friction disc 3a, and the pressure plate 10 moves by the sum of the wear amount of the first friction disc 3a and the wear amount of the second friction disc 4a. Move to the flywheel 2 side. First
Since the wear amount of the friction disk 3a is equal to the wear amount of the second friction disk 4a, the axial movement amount of the pressure plate 10 is twice the axial movement amount of the intermediate plate 11. As a result, the axial movement amount of the contact plate 36 provided on the pressure plate 10 is twice as large as the axial movement amount of the contact member 30 provided on the intermediate plate 11. R1 end 27a and R2 end 2
7b and the span ratio between the R1 end 27a and the intermediate portion 27c is 1: 0.5, so that the R2 end 2
Reference numeral 7b is adapted to move twice as much as the axial movement amount of the intermediate portion 27c abutting on the intermediate plate 11. The lever member 27 includes the pressure plate 10 and the intermediate plate 11.
The head 3 of the stud pin 39 follows the axial movement of
It rotates in the axial direction about 9a. As a result, the stud pin 39 and the end surface of the contact member 30 on the second axial direction side and the R
The second side end 27b and the first axial side end surface of the contact plate 36 are kept in contact with each other, so that even if the first and second friction disks 3a, 4a are worn, the initial cutting characteristics and the connection characteristics. Is held. At this time, no slippage occurs between the roll pin 40 and the cylindrical portion 27d, and the state shown in FIG. 13 is maintained.

Next, the operation of the wear compensation mechanism 29 when the wear amount of the second friction disk 4a is larger than the wear amount of the first friction disk 3a will be described. In this case, FIG.
13 and the state shown in FIG. At this time, the axial movement amount of the pressure plate 10 is
This is larger than twice the axial movement amount of the intermediate plate 11. That is, the R2 end 27b of the lever member 27 must move in the axial direction by a distance that is at least twice the axial movement amount of the intermediate portion 27c. Therefore, the pressing force of the coil spring 13 in the first axial direction causes a slip between the cylindrical portion 27d and the roll pin 40. As shown in FIG. 14, the stud pin 39 is attached to the head 39 with respect to the contact member 30.
a, and the cylindrical portion 27d is
It moves while sliding in the axial direction with respect to. The maximum frictional resistance generated between the cylindrical portion 27d and the roll pin 40 is set to be smaller than the pressing force acting on the pressure plate 10 from the coil spring 13, and the pressure plate 10 is moved to an intermediate position by the wear of the second friction disc 4a. If the axial movement of the plate 11 must be twice or more the axial movement distance, the cylindrical portion 27 d slides with respect to the roll pin 40. The cylindrical portion 27d is provided between the R2 side end 27b and the R1 side end 27a, and the intermediate portion 27c and the R1 side end 27a.
roll pin 4 until the ratio with respect to a is 1: 0.5.
0, the stud pin 39 and the second axial side end surface of the contact member 30, the R2 side end 27b and the contact plate 36
Is maintained in contact with the first axial side end surface, and a sufficient pressing force from the pressure plate 10 to the second friction disc 4a is secured. As a result, even if the second friction disc 4a wears more than the first friction disc 3a, the initial cutting characteristics and the connection characteristics are maintained.

In the wear compensation mechanism 29, the wear compensation mechanism 29 which operates when the wear amount of the second friction disk 4a is larger than the wear amount of the first friction disk 3a is provided in the intermediate portion 27c of the lever member 27. . Since the lever member 27 does not abut against the frictional connection portion where heat is likely to be generated, and the amount of heat generated at the frictional connection portion is very small, thermal expansion deformation is unlikely to occur in each member of the wear compensation mechanism 29. As a result, the friction coefficient of the friction sliding surface formed by the wear sliding portion of the wear compensation mechanism 29, specifically, the cylindrical portion 27d and the roll pin 40 is stabilized. As a result, problems such as slippage in a state where wear does not occur and sticking when wear occurs are less likely to occur.

(Other Embodiments) In the above embodiment, the flywheel spacer assembly 7 and the clutch cover 8 are formed as separate members and fixedly connected to each other. It may be integrally formed as.

[0042]

In the lever mechanism of the twin clutch according to the present invention, since the mechanism for adjusting wear is provided on the lever member, the friction coefficient of the friction sliding portion is stabilized.

[Brief description of the drawings]

FIG. 1 is a schematic view of a vehicle provided with a twin clutch according to the present invention.

FIG. 2 is a schematic longitudinal sectional view of a twin clutch as one embodiment of the present invention.

FIG. 3 is a partially cutaway front view of the twin clutch of FIG. 2;

FIG. 4 is a partial view taken along the arrow III in FIG. 2;

FIG. 5 is an exploded perspective view of a roll pin.

FIG. 6 is a schematic view of a release lever for explaining a clutch connection state.

FIG. 7 is a schematic diagram of a release lever for explaining a clutch release state.

FIG. 8 is a schematic diagram of a lever mechanism for explaining a clutch release state.

FIG. 9 is a schematic view of a release lever for explaining a clutch connection state.

FIG. 10 is a schematic diagram of the lever mechanism for explaining the operation of the lever mechanism in a clutch connected state.

FIG. 11 is a diagram corresponding to FIG. 10 in a case where the wear amounts of the first friction disk and the second friction disk are equal.

FIG. 12 is a view corresponding to FIG. 10 when the amount of wear of the second friction disk is larger than the amount of wear of the first friction disk.

FIG. 13 is a partially enlarged view of the wear compensation mechanism when the first friction disk and the second friction disk are not worn, or when the first friction disk and the second friction disk have the same amount of wear.

FIG. 14 is a partially enlarged view of the wear compensation mechanism when the wear amount of the second friction disk is larger than the wear amount of the first friction disk.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Twin clutch 2 Flywheel 3 1st clutch disc assembly 4 2nd clutch disc assembly 5 Clutch cover assembly 7 Flywheel spacer assembly 26 Lever mechanism 27 Lever member 27d Tube part 29 Wear compensation mechanism 39 Stud pin (support member) ) 40 Roll pin (Bushing)

Claims (5)

[Claims] 1. A twin clutch for transmitting and interrupting torque from a flywheel having a friction surface to a shaft of a transmission, comprising: a first clutch disc assembly having a first friction connection portion; and a second friction connection portion. A second clutch disc assembly, an intermediate member that can be disposed axially between the first friction connection portion and the second friction connection portion, and a pressure plate that can be disposed on the transmission side of the second friction connection portion. A pressing mechanism for applying a pressing force to the pressure plate, a biasing member for biasing the intermediate member in a direction away from the friction surface, and the first and second clutch disk assemblies. A flywheel spacer assembly for use in a twin clutch, comprising: A flywheel spacer body fixedly connected between the pressure plate and the clutch cover in an axial direction, and a mechanism for regulating an axial movement amount of the intermediate member with respect to an axial movement amount of the pressure plate. A lever member whose base end is pivotally supported by the flywheel spacer body so that the front end can be moved in the axial direction, wherein the pressure plate abuts on the front end from the transmission side; and the front end and the base end of the lever member A lever member having a locking member arranged between the lever member and being axially movably frictionally locked to the lever member and the intermediate member abutting from the flywheel side.
Flywheel spacer assembly. 2. The lever member has a hole between the distal end and the proximal end, the locking member includes a bush frictionally locked in the hole,
The flywheel spacer assembly according to claim 1, further comprising a support member sandwiched between the flywheel-side end surface of the bush and the intermediate member. 3. The flywheel spacer according to claim 1, wherein the support member has a contact surface that comes into contact with the intermediate member, and the contact surface is convex toward the intermediate member. Assembly. 4. A twin clutch for transmitting and interrupting torque from a flywheel having a friction surface to a transmission shaft, the twin clutch having a first friction coupling portion disposed close to the friction surface, A first clutch disc assembly capable of transmitting torque to a shaft; and a second clutch disc capable of transmitting torque to the shaft, the second clutch disc having a second friction coupling portion disposed on the transmission side of the first friction coupling portion. An assembly, a clutch cover fixed to the flywheel, and covering the first and second clutch disk assemblies; and a clutch cover disposed between the first friction connection portion and the second friction connection portion in the axial direction. An intermediate member rotatable integrally with a flywheel; and an intermediate member disposed on the transmission side of the second frictional connection portion; A pressure plate that is rotatable about the body, a pressing mechanism that is supported by the clutch cover and applies a pressing force to the pressure plate, and an urging force that urges the intermediate member in a direction away from the friction surface. A twin clutch, comprising: a member; and the flywheel spacer assembly according to claim 1. 5. The twin clutch according to claim 4, wherein the clutch cover and the flywheel spacer assembly are formed as separate members and are fixedly connected to each other.