JPS5952295B2 - clutch plate - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides that, on each side of the boss flange of the boss, one disk can be rotated within certain limits relative to the boss flange against the force of a spring device and under the action of friction. of the type in which the clutch facings are fixedly connected to one disc, the spring devices being arranged in the boss flange and in the windows of both discs; , relates to a clutch disc, commonly known as a damped clutch disc.

This type of latch disk is constructed between both disks (one of which holds the clutch facing) provided on both sides of the boss flange and the boss flange, so that these disks and the boss flange are relative to each other. It has a large number of coil springs (spring devices) that act during rotation, and these coil springs as a whole produce a spring characteristic curve that changes stepwise.

In this case, a friction member is axially tensioned between the boss flange and the two disks, so that friction occurs during relative rotation and damps the rotational movement.

The coil springs are distributed irregularly to some extent;
Due to the different rotation angles when the individual coil springs begin to act, the disk rotates to some extent with respect to the boss and also performs an arc-shaped turning movement, resulting in radial play of the disk with respect to the boss. becomes zero, and the hole in the center of the disk hits the concentric dust of the boss, which may cause some uncontrollable rubbing motion of the disk against the boss.

When a torque impact occurs in the opposite direction, the hole at the center of the disk first moves away from the outer circumferential surface of the boss (centered dust), and both disks pivot in an arc with respect to the boss, and the center of the disk The hole hits the boss on the other side.

The addition of these uncontrollable rotational resistances to the frictional action produced by the axially tensioned friction member impairs and irregularly dampens the damping action, preventing the desired damping action from being produced. do not have.

Furthermore, when the torque is replaced, the disc hits the centering dust of the boss, causing early damage to the clutch disc.

The purpose of the present invention is to eliminate such drawbacks of conventional clutch discs, and to eliminate the centering dust of the boss when a relative rotational movement occurs between the boss and both discs that are tightly connected to the clutch facing. and the central hole of at least one of the discs is to be created from the beginning by means of defined friction and by very simple means.

In order to produce this defined frictional effect, an embodiment of the invention provides that, in a clutch disc of the type mentioned at the outset, a friction member for absorbing radial forces is provided between the hub and at least one of the discs. is arranged, and at least one spring device is installed in a direction offset from the tangential direction with respect to the boss flange.

In order to achieve the same object, a further development of the invention provides that in a clutch disc of the first-mentioned type, a friction element is arranged between the hub and at least one of the two discs, which receives the radial force. and at least one of the spring devices is mounted so as to act rotationally oppositely to the remaining spring devices, thereby creating a radial force component acting on the friction member. did.

Due to the force component produced by the inventive mounting of at least one of the spring devices, that is to say due to the tensioning force acting at least approximately in the radial direction, from the beginning of the relative pivoting movement at least one of the discs is positioned in the boss. between the boss and the discs by arranging a friction member that is pushed or attracted towards the centered dust of the hub and acts radially between the boss and at least one of both discs. A defined frictional or damping effect in the radial direction always takes place, that is to say from the beginning of the relative pivoting movement.

In the following, the configuration of the present invention will be specifically explained based on the embodiments shown in the drawings.

In the clutch disc shown in FIG. 1, a clutch facing 1 is fixed to a main plate 2, which is one disc.

The other disc, auxiliary plate 4, is coupled to the main plate 2 by rivets 3 so as to be relatively unrotatable.

These main plate 2 and sub-plate 4 are provided within a certain limit relative to the boss and its flange 6, and springs (spring devices) are provided in the notches of the flange 6 and the main plate 2 and sub-plate 4. ) can be rotated against the action of

In the clutch disc according to the invention, the frictional moment for damping is generated in the following manner.

That is, during the relative rotation, an at least approximately radially oriented force is exerted between the centering hole 7 of the boss 5 and the inner edge 8 of the central hole in the main plate 2 and the secondary plate 4.

For this purpose, it is possible, for example, for spring 12 of springs 9 to 12 to act in the direction of rotation in the opposite direction to the remaining springs, resulting in a distribution of moments that differs from the usual distribution of moments symmetrical about the axis. .

In this case, when the boss rotates relative to the clutch facing, the springs 9 and 11 are rotated in the same direction (counterclockwise) and have the same magnitude of moment distribution, or M1□ These moments act only as rotational moments and do not give rise to any radial force component.

The spring 10 still exerts a moment M1o in the counterclockwise direction, but if the spring 12 is adapted to act clockwise, a moment of the same magnitude in the counterclockwise direction corresponds to this moment M1o. is not generated, so that simultaneously with the pivoting moment a relative displacement force in the radial direction corresponding to the moment (MIO) of the spring 10 is generated.

As a result, the main plate 2 and the sub-plate 4 are pushed toward the centering plate 7 of the boss 5, and a friction moment is created between the centering plate 7 and the inner edges 8 of the main plate 2 and the sub-plate 4, which is directly proportional to the force of the spring 10. is soaked raw.

Distributing the moment asymmetrically with respect to the axis of the clutch disc in this way can also be achieved by arranging the spring 12 in a direction offset from the tangential direction to the boss flange, as shown in FIG. When the main plate 2 and the sub-plate 4 rotate relative to the boss 5, the force of the spring 12 does not act in the tangential direction at its point of action, but has a force component in the radial direction, and this force The component loads the radially centered dust between the main plate 2 and the sub-plate 4 and the boss 5.

A clutch disc constructed in this way can have a damping effect that can be varied in more than one way, for example as will be explained in conjunction with FIG.

In FIG. 2, the abscissa axis represents the relative rotation angle, and the abscissa axis represents the rotational moment that occurs during the relative rotation.

Furthermore, the range to the left of the ordinate axis is the range in which the output side of the clutch drives the input side (engine braking range), and the range to the right of the ordinate axis is the range in which the clutch input side drives the output side (normal operating range).

The spring characteristic curve 13 has a linear course in the engine braking range, which, viewed in the clockwise direction in FIG.
This is based on the fact that all the side edges 14 of the notch formed in the main plate 2 and the secondary plate 4 match all the side edges 15 of the notch formed in the main plate 2 and the secondary plate 4 to accommodate the spring 9312. It is something.

At the other end of the cutout, the side edge 16 of the cutout in the flange 6 for the spring 12 is connected to the main plate 2 and the subplate 4.
The side edge 18 of the notch in the flange 6 for the springs 9 to 11 is recessed in the counterclockwise direction from the side edge 17 of the notch in the main plate 2 and the secondary plate. This is less than the extent to which the cutout in the plate 4 is recessed relative to the side edge 19 when viewed in a counterclockwise direction.

As a result, the spring characteristic curve 13 extends in a straight line from the intersection of the ordinate and abscissa axes along the abscissa to range A, and then has a spring characteristic with a gentle slope since it is installed at a position different from the tangential position. The spring characteristic curve 13 increases with a gentle slope over the section up to range B, where only the spring 12 having do.

In a known manner, an axial frictional force acts between the flange 6 of the boss 5 and the main plate 2 and the secondary plate 4.

This frictional force is caused, for example, by the axial tension between the main plate 2 and the sub-plate 4, and is indicated by the dashed curve 20 in FIG.

The frictional force produced by the force component acting in the radial direction between the centering dust 7 of the boss 5 and the inner edges 8 of the main plate 2 and the sub-plate 4 is shown by a dashed line curve 21.

As can be seen from Figure 2, within the normal operating range, the radial force component does not increase at all from the intersection of the vertical and horizontal axes to range A, whereas when range A is exceeded, the radial force component This results in an increase in frictional force.

In a clutch disc constructed in this way, the transition between the various sections of the characteristic curve of the friction value occurs continuously and smoothly, rather than dramatically, and the friction value varies depending on the angle of relative rotation. increase

The clutch disc according to the invention can be adapted to almost all practical working conditions, since its characteristic curve and friction values can be varied very widely.

As can be seen from FIG. 3, the inner edge portion 8 of at least one of the main plate 2 and the sub-plate 4 has a cylindrical appended portion in the axial direction, and a space between this appended portion and the centering dust 7 of the boss 5. Friction member 2
2 is provided.

The friction member 22 can also be constructed integrally with a friction member 23 that generates a friction force corresponding to the curve 2o in FIG.

The present invention is not limited to the illustrated embodiments, but can be implemented in various ways.

[Brief explanation of drawings]

FIG. 1 is a partial front view of one embodiment of the present invention, FIG. 2 is a graph showing the damping characteristic curve of the clutch disc according to the present invention, and FIG. 3 is a cross section taken along line III-III in FIG. FIG. 4 is a partial front view of another embodiment of the present invention. 1: Clutch facing, 2: Main plate, 3: Rivet,
4: Sub-plate, 5: Boss, 6: Flange, 7: Centering dust, 8:
Inner edge, 9-12: Spring, 13: Spring characteristic curve, 14-
19: side edges, 2o and 21: curved lines, 22 and 23: friction members.

Claims (1)

[Scope of Claims] 1. On each side of the boss flange of the boss, a disk is attached to the boss such that it can rotate within a certain limit with respect to the boss flange against the force of a spring device and under the action of friction. A clutch disk of the type in which a plurality of clutch facings are connected in a relatively rotationally fixed manner to one of the disks, and a spring device is arranged in the boss flange and in the window of both disks, The boss 5 and at least one of the discs (
2 or 4), a friction member 22 for receiving a radial force is disposed, and at least one spring device is incorporated in a direction offset from the tangential direction with respect to the boss flange. clutch disc. 2. On each side of the boss flange of the boss, a disk is mounted on the boss in a manner that is rotatable within certain limits relative to the boss flange against the force of a spring device and under the action of friction; In a clutch disc of the type in which a plurality of clutch facings are coupled in a relatively unrotatable manner to the disc of the boss 5 and a spring device is disposed in the boss flange and the window of both discs, the boss 5 and at least one The disk (
2 or 4), a friction member 22 for receiving radial forces is arranged, and at least one spring device is integrated in such a way that it acts in a different direction of rotation than the remaining spring devices. A clutch disc characterized by: