JPH0578695B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a vibration damping structure for a clutch disk, which is mainly suitable for automobile clutches.

(Prior Art) In general, a clutch disk has a structure in which a friction facing fixed to a cushioning plate on its outer periphery is arranged between a flywheel on the engine side and a pressure plate that is linked to a clutch pedal. There is. Furthermore, when the friction facing is held between the flywheel and the pressure plate, torque from the flywheel side is transmitted to the central output shaft via the clutch disk.

Torque from the engine is transmitted to the clutch disc, but at the same time, various vibrations from the engine are also transmitted. This vibration is simultaneously transmitted to the pressure plate via the friction facing and the like.
This vibration causes the cushioning plate and the pressure plate to resonate, and a squeal (cooing noise) is likely to occur particularly when the vehicle starts from a half-clutch state.

(Object of the Invention) The present invention aims to solve the problem that "squeal" occurs due to the resonance of the cushioning plate and the pressure plate, especially in the so-called half-clutch state when the clutch is connected. .

(Structure of the Invention) The cushioning plate that connects the disc-shaped clutch plate on the output side and the facing on the input side on the outer periphery thereof includes a first portion that is flush with a portion fixed to the clutch plate or is biased toward the flywheel side, and a first portion that is offset toward the flywheel side. In the clutch disk, a second part is provided which is raised toward the pressure plate side than the first part, and friction facings are fixed to the flywheel side of the first part and the pressure plate side of the second part. This is a vibration damping structure for a clutch disk characterized in that a damping member is provided on the clutch plate or cushioning plate for pressing the second raised portion in a direction that pushes the second raised portion downward toward the flywheel.

Torque input to the friction facing from the engine-side flywheel is transmitted to the output-side clutch plate via the cushioning plate. At the same time, vibrations caused by various factors are also transmitted to the friction facing from the flywheel side. This vibration is also transmitted to the cushioning plate,
The damping member suppresses the resonance of the cushioning plate, thereby suppressing the occurrence of squealing when the clutch is in a so-called half-clutch state.

(Example) In FIG. 1, a spline hub 11 has a spline 12 on its inner peripheral surface that fits into an output shaft (not shown), and integrally has a disk-shaped flange 13 on its outer peripheral part. Annular friction members 14 and 15 are arranged on the inner periphery of both sides of the flange 13, and the friction members 1
A pair of disc-shaped clutch plates 16 and retaining plates 17 are arranged on both sides of the flange 13 with 4 and 15 in between.

A plurality of window holes 19 and 2 are provided in the flange 13 and the outer periphery portions of both plates 16 and 17, respectively.
0 and 21 (only one of each is shown) are provided at intervals in the clutch circumferential direction. A torsion spring 22 is fitted into each set of three window holes 19, 20, 21 so as to extend in the circumferential direction of the clutch. Further, the outer peripheries of the clutch plate 16 and the retaining plate 17 are integrally connected to each other by a stop pin 18 parallel to the clutch centerline. The stop pin 18 is connected to the flange 13
The clutch is engaged with a notch 23 formed on the outer periphery of the clutch with play in the circumferential direction.

The inner circumferential portion of a cushioning plate 25 is fixed to the outer circumferential portion of the clutch plate 16 by a rivet 26. Cushioning plate 25
are arranged on the clutch plate at equal intervals on the circumference. Each clutching plate 25 has a first portion 25a extending substantially coplanar with the clutch plate 16 (this portion includes the flywheel 3
The second portion 25b is protruded toward the pressure plate 33 side than the first portion 25a, and the facing 28a is fixed to the flywheel 32 side of the first portion 25a by a rivet 27. Similarly, a facing 28b is fixed to the pressure plate 33 side of the second portion 25b by a rivet 27. Since the cushioning plate 25 includes a first portion 25a and a second portion 25b and is curved in a substantially wave shape on the circumference, the cushioning plate 25 is curved in a substantially waveform on the circumference. ning plate 25
can exert a spring action.

First portion 25a of cushioning plate 25
The circumferential widths of the second portion 25b and the second portion 25b are L1 and L2 (FIGS. 2 and 3), and the axial deviation amount of both portions is the third
This is L3 in the figure.

In the embodiment shown in FIG. 2, a projecting portion 35 integrally projects from the second portion 25b of the clutch plate 25 toward the center of the clutch disk. 16, the cushioning plate fixing portion 29 is pressed against the outer circumferential portion of the side opposite to the abutting surface (the side shown in FIG. Adds elasticity in the direction of decreasing it. In other words, the pressure plate side facing 28 tends to vibrate in the axial direction together with the pressure plate when the clutch is half-engaged.
b exerts a damping effect on the cushioning plate 25, so that the resonance phenomenon caused by the raised second portion 25b can be suppressed even though the cushioning plate 25 is provided with an axial deflection amount L3.

In the embodiments shown in FIGS. 4 and 6, the tip of the presser plate 36 that is fastened together with the cushioning plate fixing portion 29 is attached to the pressure plate of the second portion 25b which is raised toward the pressure plate side. The side surfaces are pressed in a direction that reduces protuberance. Reference numeral 37 in FIG. 4 is a notch provided in the facing 28b to expose the second portion 25b of the presser plate 36 that comes into pressure contact. In this case, since it is necessary to contact the second portion 25b of the presser plate 36, the friction area of the pressure plate side facing 28b is reduced by the portion of the notch 37. The pressure plate 33 in FIG. 1 is connected to a clutch cover (not shown) fixed to the flywheel 32 via a strap (not shown) extending in the circumferential direction of the clutch.
Therefore, it is supported so as to be swingable in the direction of the clutch centerline. Also, a spring force from a diaphragm spring (not shown) acts on the pressure plate 33, and normally the facing 28 is pushed against the flywheel 3.
However, by bending the diaphragm spring using a release lever linked to the clutch pedal, the pressure plate 33 can be released from the facing 28 and the clutch can be disconnected.

Next, the operation will be explained. In FIG. 1, when the facing 28 is pressed against the flywheel 32 by the pressure plate 33, the flywheel 3
2 is transmitted to an output shaft (not shown) via the facing 28, the cushioning plate 25, the clutch plate 16, the torsion spring 22, the flange 13, and the spline hub 11. In that case, torsion occurs between the plates 16, 17 and the flange 13 in response to the transmitted torque, so the surfaces of the friction members 14, 15 slip. This slippage generates hysteresis torque, which absorbs torque fluctuations. On the other hand, vibrations occur in the flywheel 32 due to various causes. This vibration is transmitted to the facing 28, and mainly via the facing 28 to the pressure plate 33.
It is also transmitted to However, according to the configuration shown in FIG.
Since a force is applied in the direction of pressing the 2nd side surface and reducing the protrusion, when the axial deflection L3 is not crushed and the clutch is half-clutched, the vibration of the pressure plate 33 etc. based on the deflection L3 is reduced. Therefore, it is possible to reliably prevent a cooing sound (abnormal noise) at the time of starting. Furthermore, when the structure shown in FIG. 4 is adopted, since the presser plate 36 presses the second portion 25b in a direction to reduce the protrusion, a similar effect can be expected, and the pressure plate 33 Vibration is suppressed and clutch squeal is reduced.

Figure 5 shows the results of the vibration test. The horizontal axis in FIG. 5 is the frequency Hz applied to the flywheel 32 in the direction of the clutch center line, and the vertical axis is the acceleration G of the pressure plate 33 that resonates. As is clear from FIG. 5, in comparison with characteristic A in the conventional configuration, in characteristic B in the configuration shown in FIG. 1, the acceleration of the pressure plate 33 is significantly reduced and the squeal of the clutch is reduced.

(Effects of the Invention) According to the present invention, due to the axial deflection amount L3 provided for imparting a spring action to the compression plate 25, the pressure plate 33 is in a half-clutch state that occurs when starting, etc. The phenomenon in which both the pressure plate side facing 28b vibrate in the axial direction can be effectively suppressed by the projecting portion 35, the presser plate 36, etc., and there is an advantage that generation of squeal can be prevented.

(Other Embodiments) Instead of the presser plate 36 shown in FIG. 6, a ring-shaped presser plate 40 as shown in FIG. 7 may be used.

[Brief explanation of drawings]

Fig. 1 is a longitudinal cross-sectional view of a clutch disk employing the vibration damping structure according to the present invention, Fig. 2 is a partially cutaway front view as seen from the arrow in Fig. 1, and Fig. 3 is a schematic view as seen from the arrow in Fig. 2. , FIG. 4, FIG. 6, and FIG. 7 are drawings corresponding to a part of FIG. 2 to show another embodiment, and FIG. 5 is a graph showing the relationship between frequency and acceleration. 16... Clutch plate, 25... Cushioning plate, 25a... First part, 25b... Second part, 28... Facing, 29... Fixing part, 35...
Projection portion (damping member), 36... Pressing plate (damping member).

Claims (1)

[Claims] 1. A cushioning plate that connects the disc-shaped clutch plate on the output side and the facing on the input side on the outer periphery thereof has a first portion that is flush with the part fixed to the clutch plate or that is offset toward the flywheel side;
In a clutch disk, a second portion is provided which is raised toward the pressure plate side than the first portion, and friction facings are fixed to the flywheel side of the first portion and the pressure plate side of the second portion. A vibration damping structure for a clutch disk, characterized in that a damping member is provided on a clutch plate or a cushioning plate to press a second raised portion of the bump in a direction toward the flywheel.