JPH06129444A - Clutch disk - Google Patents

Abstract

PURPOSE:To build a clutch disk whose hysteresis torque varies according to a twist angle. CONSTITUTION:A relative rotation is produced in space between a plate 4 and a dish member 10 through a relative rotation between plates 2, 4 and a hub 3 conformed to transfer torque, and at this time, the dish member 10 alters the extent of compressive allowance of a disk spring 8 by means of a cam action between the plate 4 and the member 10, thereby altering the pressing frictional force of two washers 6, 7 with a flange 3a, namely, a hysteresis torque.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch disc used for a dry clutch in a manual transmission and a lockup clutch in an automatic transmission.

[0002]

2. Description of the Related Art A clutch of this type is appropriately frictionally engaged with one rotating body and is drivingly coupled to the other rotating body in order to transmit or stop power transmission between two rotating bodies. With a clutch disc. The clutch disk is usually constructed as shown in FIG. 6 as disclosed in Japanese Patent Laid-Open No. 58-77926.

That is, the drive plate 2 frictionally engaged with the one rotating body through the clutch facing 1.
And a hub 3 drivingly coupled to the other rotating body,
The retaining plate 4 is arranged on the side of the hub flange 3a opposite to the drive plate 2. The drive plate 2 and the retaining plate 4 are integrally connected by a rivet (not shown), and the rivet and the hub flange 3a.
The drive plate 2 and the retaining plate 4 cooperate with an unillustrated notch formed on the outer peripheral edge of the drive plate 2 and the retaining plate 4.
And the relative rotation with the hub 3 is limited to a predetermined angle.

Further, the drive plate 2 and the retaining plate 4 and the hub flange 3a are drive-engaged in a buffered manner via a well-known torsion spring 5.
As a result, the change characteristic of the torsion torque Tq with respect to the relative rotation (twist angle) θ between the drive plate 2 and the retaining plate 4 and the hub 3 becomes as shown by the broken line in FIG. 7, and the gradient (torsion rigidity) of the torsion torque Tq. It depends on the spring constant of the spring 5. Thus, the torque transmission by the clutch disc can be prevented from becoming steep, and the clutch engagement shock can be reduced.

On the other hand, the torsion spring 5 is
Drive plate 2 and retaining plate 4,
There is a tendency to cause rotational vibration with the hub 3, and the following measures have been taken conventionally to prevent this. That is, the friction washers 6 and 7 are interposed between the drive plate 2 and the hub flange 3a and between the retaining plate 4 and the hub flange 3a, respectively, and between the friction washer 7 and the retaining plate 4. Further, the disc spring 8 and the friction plate 9 are interposed.

As a result, the disc spring 8 presses the friction washer 7 against the hub flange 3a through the friction plate 9 and makes frictional contact with the hub flange 3a, and on the other hand, the reaction force causes the friction washer 7 through the retaining plate 4 and the drive plate 2 to cause friction. Replace the washer 6 with the hub flange 3a
And press it into frictional contact. Due to these frictional contacts, the drive plate 2 and the retaining plate 4
And frictional resistance is imparted to the relative rotation between the hub and the hub 3, and as shown by the solid line in FIG.
By setting _f , the above rotational vibration can be damped.

[0007]

However, in such a conventional hysteresis torque setting structure, regardless of the relative rotational position between the drive plate 2 and the retaining plate 4 and the hub 3, the retaining plate 4 and the friction. Since the clearance between the plates 7, that is, the compression margin of the disc spring 8 does not change, the hysteresis torque T _f is also shown in FIG.
As shown in (3), when the hysteresis torque that is the same in all the twist angle regions and changes according to the twist angle θ is required, there arises a problem that the demand cannot be met.

An object of the present invention is to provide a clutch disc which can satisfy such requirements.

[0009]

To this end, the invention is drivably coupled to a plate frictionally engaged to one rotating body and to the other rotating body so that power can be transmitted between the two rotating bodies. Relative rotation of a plate and a hub in a clutch disc that includes a hub, and rotationally engages between the plate and the hub in a buffered manner to impart a hysteresis torque to the relative rotation of the plate and the hub by a frictional force. A cam mechanism for changing the frictional force according to the above is provided.

[0010]

When the plate is frictionally engaged with one of the rotating bodies, the clutch disk transmits power between the one rotating body and the other rotating body via the plate and the hub. At this time, since the plate and the hub are rotatably engaged with each other in a buffered manner, torque fluctuations during power transmission are absorbed, and the power transmission can be smoothly performed without shock. Further, since the hysteresis torque due to the frictional force is applied to the relative rotation between the plate and the hub that occurs during this buffering action, it is possible to reliably damp the rotational vibration between them.

Meanwhile, the cam mechanism changes the frictional force according to the relative rotation between the plate and the hub. Therefore, even when a different hysteresis torque is required depending on the relative rotation between the plate and the hub, this requirement can be surely satisfied, and the application range of the clutch disc can be significantly expanded.

[0012]

Embodiments of the present invention will now be described in detail with reference to the drawings. FIG. 1 shows an embodiment of the clutch disc of the present invention. In this figure, the same parts as in FIG. 6 are designated by the same reference numerals.

In this embodiment, a dish member 10 which constitutes a main part of the cam mechanism of the present invention is further interposed between the retaining plate 4 and the disc spring 8. The member 10 is constructed in detail as shown in FIG. That is,
A plurality of (four in the illustrated example) claws 10a are preferably arranged at equal intervals in the circumferential direction on the outer circumference of the annular disc, and these claws are extended in the axial direction. A plurality of (four in the illustrated example) cam projections 10 are preferably arranged at equal intervals in the circumferential direction on the side of the annular disc opposite to the extending direction of the claws 10a.
b is formed.

The dish member 10 has a claw 10a.
1 are arranged so as to engage with corresponding notches 3b formed in the hub flange 3a, and are interposed between the retaining plate 4 and the disc spring 8. And
At this time, the same number of cam protrusions 10a as the cam protrusions 4a shown in the development view of FIG. 2 are provided on the side of the retaining plate 4 that cooperates with the cam protrusions 10b. However, these cam projections 4a
Is arranged so that the clutch disc is positioned between the cam projections 10b as shown in FIG. 2 in a neutral state in which power is not transmitted, and when the retaining plate 4 and the dish plate 10 rotate relative to each other as shown by an arrow in FIG. , So that both cam projections 4a and 10b work together.

The operation of the above embodiment will be described below. In transmitting power between the two rotating bodies, the clutch facing 1 is pressed against one rotating body and frictionally engaged therewith. As a result, the clutch disc can transmit power between the one rotating body and the other rotating body splined in the hub 3. Since the drive plate 2, the retaining plate 4, and the hub 3 are drivingly coupled to each other via the torsion spring 5, this power transmission is performed in a buffered manner through the bending of the torsion spring. Therefore, the change characteristic of the torsion torque Tq with respect to the relative rotation (torsion angle) θ between the drive plate 2 and the retaining plate 4 and the hub 3 is shown in FIG.
As shown by the broken line (the gradient is determined by the spring constant of the torsion spring 5), the torque transmission by the clutch disc can be prevented from becoming steep, and the shock at the time of clutch engagement can be reduced.

The shock absorbing function is obtained by the relative rotation of the drive plate 2 and the retaining plate 4 and the hub 3 through the bending of the torsion spring 5. The rotational vibration between the drive plate 2 and the retaining plate 4 and the hub 3 is caused by the relative rotation. It is attenuated as follows.

That is, on the one hand, the disc spring 8 presses the friction washer 7 against the hub flange 3a through the friction plate 9 to make frictional contact with this, and on the other hand, by the reaction force, the dish member 10, the retaining plate 4 and the drive plate. The friction washer 6 is pressed against the hub flange 3a via 2 and brought into frictional contact therewith. Due to these frictional contacts, frictional resistance is given to the relative rotation between the drive plate 2 and the retaining plate 4 and the hub 3, and the hysteresis torques T _f1 and T _f2 are set as shown by the solid lines in FIG. The above-mentioned rotational vibration can be damped.

By the way, as the transmission torque of the clutch disk increases, the relative rotation between the drive plate 2 and the retaining plate 4 and the hub 3 increases, and the dish member 10 that rotates together with the hub 3.
Relative rotation, which increases with the transmission torque of the clutch disc, also occurs between the retaining plate 4 and the retaining plate 4. This relative rotation causes the cam projections 4a and 10b to approach from the position shown in FIG. 2 as shown by the arrow, and finally they work together.

In the small transmission torque range before the start of this cooperation, that is, in the small torsion angle range on the horizontal axis of FIG. 5, the dish member 10 is closest to the retaining plate 4 as shown in FIG. Since the distance between the friction plate 9 and the dish member 10 is the maximum and the compression margin (spring force) of the disc spring 8 is the minimum, the frictional resistance determined by this spring force, and thus the hysteresis torque, is T _f1 in FIG. Small as shown.

When the above-mentioned cooperation starts, however, the relative rotation (twisting angle θ in FIG. 5) between the drive plate 2 and the retaining plate 4 and the hub 3 is increased due to the increase of the clutch disc transmission torque. As the number of cams increases, the cam projections 4a and 10b ride on each other as shown in FIG. 4, and the dish plate 10 is gradually moved away from the retaining plate 4. As a result, the distance between the friction plate 9 and the dish member 10 is gradually reduced, and the compression margin (spring force) of the disc spring 8 is gradually increased. Therefore, the hysteresis torque determined by this spring force is directed to the upper limit value indicated by T _f2 in FIG. It increases and finally keeps this upper limit.

As described above, in the structure of this embodiment, the friction washers 6, 7 with respect to the hub flange 3 are moved in accordance with the relative rotation between the drive plate 2 and the retaining plate 4 and the hub 3 (torsion angle θ in FIG. 5). Due to the structure in which the pressing force (friction force) changes, even when a different hysteresis torque is required depending on the transmission torque of the clutch disc, this requirement can be satisfied with certainty, and the application range of the clutch disc is remarkably increased. Can be expanded.

[0022]

As described above, the clutch disk according to the present invention has a plate which is frictionally engaged with one of the two rotating bodies for power transmission and the other rotating body. Since a cam mechanism that changes the frictional force for setting the hysteresis torque between the hub and the drive-coupled hub is variable according to the relative rotation, the hysteresis torque characteristic with respect to the twist angle of the clutch disc can be arbitrarily set. Even if a different hysteresis torque is required depending on the transmission torque of the clutch disc in view of various circumstances, this requirement can be surely satisfied, and the range of application of the clutch disc can be greatly expanded.

[Brief description of drawings]

FIG. 1 is a sectional view showing an embodiment of a clutch disc of the present invention.

FIG. 2 is a developed cross-sectional view showing the same example as a cross section taken along the line AA in FIG.

FIG. 3 is a perspective view showing a dish member in the same example.

FIG. 4 is an enlarged cross-sectional view of a main part used for explaining the operation of the cam mechanism in the same example.

FIG. 5 is a change characteristic diagram of hysteresis torque in the same example.

FIG. 6 is a sectional view showing a conventional clutch disc.

FIG. 7 is a hysteresis torque characteristic diagram of the same.

[Explanation of symbols]

 1 Clutch Facing 2 Drive Plate 3 Hub 3a Hub Flange 3b Notch 4 Retaining Plate 4a Cam Protrusion 5 Torsion Spring 6 Friction Washer 7 Friction Washer 8 Disc Spring 9 Friction Plate 10 Dish Member 10a Claw 10b Cam Protrusion

Claims (1)

[Claims] 1. A plate comprising a plate frictionally engaged with one rotating body and a hub drivingly connected to the other rotating body so that power can be transmitted between the two rotating bodies. In a clutch disc that is rotationally engaged in a buffer to give a hysteresis torque to a relative rotation of the plate and the hub by a frictional force, a cam mechanism that changes the frictional force according to the relative rotation of the plate and the hub is provided. A clutch disc characterized by being provided.