JPS62278321A - Oscillation suppressing structure for clutch disc - Google Patents

Abstract

PURPOSE:To suppress a noise from being generated when a clutch is placed in a half-clutch condition, by providing a vibration suppressing member, which presses a projection part of a cushioning plate in the depressing direction, so that the resonance of the cushioning plate is suppressed. CONSTITUTION:A cushioning plate 25 is equipped with the first part 25b, which extends existing on the same plane to a clutch plate 16, and the second part 25b which rises to the side of a pressure plate 33 from the first part 25a. And facings 28a, 28b are fixed by a rivet 27 respectively to the side of a flywheel 32 of the first part 25a and the side of the pressure plate 33 of the second part 25b. In the above constitution, a clutch disc, which protrusively provides toward its center side an overhanging part 35 from the second part 25b, forces the overhanging part to come into contact with a reverse side of the clutch plate 16, thus resilient force is applied in the direction reducing the projection of the second part 25b. And the resonance by the second part 25b is suppressed by the facing 28b suppressing the oscillation.

Description

DETAILED DESCRIPTION OF THE INVENTION 3. Detailed Description of the Invention (Field of Industrial Application) The present invention relates to a vibration damping structure of a latch disk, which is mainly suitable for automobile clutches.

(Prior art) In general, a clutch disc has a friction facing fixed to a cushioning plate on its outer periphery, which is arranged between a flywheel on the engine side and a pressure plate connected to the clutch pedal. . Also, I! HQ! When the casing is held between the flywheel and the pressure plate, torque from the flywheel side is transmitted to the central output shaft via the clutch disc.

Torque from the engine is transmitted to the clutch disc, but at the same time, various vibrations from the engine are also transmitted. This imaging is simultaneously transmitted to the pressure plate via the we facing or 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 when the clutch is engaged in a so-called half-clutch state.

(Structure of the Invention) The cushioning plate that connects the disc-shaped clutch plate on the output side and the input side facing on the outer peripheral side thereof is provided with a first part that is flush with the part fixed to the clutch plate or rIA fitted to the flywheel side, and a first part that is attached to the flywheel side. A3 is attached to a clutch disc with a second part raised toward the pressure plate side than the first part, and a friction facing fixed to the flywheel side of the first part and the pressure plate side of the second part,
This clutch disc damping/vibration structure is characterized in that the clutch plate is provided with a damping member that presses the raised second portion of the cushioning plate in a downward direction.

r! ! Torque input from the engine-side flywheel is transmitted to the output-side clutch plate via the cushioning plate. At the same time a! The rough facing also transmits imaging based on various factors from the flywheel side. The vibration is also transmitted to the cushioning plate, but 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. 7 An annular friction member 14.15 is arranged on the inner periphery of both sides of the flange 13, and a pair of disc-shaped clutch plates 16 and retaining plates are arranged on both sides of the flange 13 with the FJ friction member 14.15 in between. 17 are arranged.

A plurality of window holes 19, 20, 21 (only one of each window hole is shown) are provided at intervals in the clutch circumferential direction in portions of the flange 13 and both plates 16, 17 near the outer periphery. A torsion spring 22 is fitted into each set of five window holes 19.20121 in a posture extending in the clutch circumferential direction. Further, the outer peripheral portions 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 engages with a notch 23 formed in the outer circumference of the flange 13 with play in the clutch circumferential direction.

An inner circumferential portion of a cushioning plate 25 is fixed to an outer circumferential portion of the clutch plate 16 with a rivet 26 . A plurality of cooking plates 25 are arranged on the clutch plate at equal intervals on the circumference. Each cushioning plate 25 has a first portion 25a that extends substantially on the same plane as the clutch plate 16 (this portion may be biased toward the flywheel 32 side), and is closer to the pressure plate 33 than the first portion 25a. Raised 1ζ second part 2
5b, the facing 28a is fixed to the flywheel 32 side of the first portion 25a by a rivet 27, and the facing 28a is fixed to the flywheel 32 side of the first portion 25a, and the facing 28a is fixed to the flywheel 32 side of the first portion 25a, and the facing 28a is fixed to the flywheel 32 side of the first portion 25a. Seven acings 28b are similarly fixed to the ledge V plate 33 side with rivets 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 can exert a spring action when the seven acings 28a, 28b on both sides are compressed toward each other.

The circumferential widths of the first portion 25a and second portion 25b of the cushioning plate 25 are Ll and L2 (Figs. 2 and 3), and the axial stiffness of both sections is 13 in Fig. 3. .

In the embodiment of FIG. 2, the cushioning plate 2
A projecting portion 35 integrally projects from the second portion 25b of the clutch plate 16 toward the center of the clutch disk, and this projecting portion 35 is formed on the back side of the clutch plate 16, that is, when the cushioning plate fixing portion 29 is in contact with the clutch plate 16. The second portion 25b is pressed against the outer periphery on the opposite side (the back side in FIG. 2) of the pressure plate, thereby applying elasticity in the direction of reducing the protrusion of the second portion 25b protruding toward the pressure plate side. In other words, when the clutch is half-engaged, a control action is exerted on the pressure plate side facing 28b which tends to vibrate in the axial direction together with the pressure plate, and the cushioning plate 25 is subjected to an axial deflection ff1.
Despite the provision of L3, it is possible to suppress the co-creation phenomenon caused by the raised second portion 2bb.

In the embodiments shown in FIGS. 4 and 6, the tip of the presser plate 36 collinear with the cushioning plate fixing portion 29 touches the pressure plate side surface of the second portion 25b raised toward the pressure plate side. It is pressed in a direction that reduces the prominence. 37 in FIG. 4 is the second portion 25 that is in pressure contact with the presser plate 36.
This is a notch provided in the facing 28b to expose the portion b. In this case, since it is necessary to apply the presser plate 36 to the second portion 25b, the facing 28b on the Blessisse plate side
Noj! The whitening area is reduced by the portion of the notch 37. Note that the pressure plate 33 in FIG. 1 is a clutch cover (not shown) fixed to the flywheel 32.
The clutch is connected to the clutch via a strap (not shown) extending in the circumferential direction of the clutch, and is therefore 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 presses the facing 28 against the flywheel 32. I-shift release lever
By bending the dicephram spring, the brace V plate 33 can be released from the facing 28 and the ramp can be cut. Next, work #J will be explained. In FIG. 1, when the facing 28 is pressed against the flywheel 32 by the pressure plate 33, the torque from the flywheel 32 is applied to the facing 28, the cushioning plate 25, the clutch plate 16, the torsion spring 22, the flange 13,
The signal is transmitted to an output shaft (not shown) via the spline hub 11. In that case, both plates 16
．． 17 and the flange 13, the surfaces of the friction members 14, 15 slip. This slip 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 the force is applied in the direction of pressing against the back surface of the clutch and reducing the protrusion, it is possible to suppress the vibration of the brake plate 33g5 based on the bias ff1L3 when the axial scratch (nljtL3 is not crushed) is in the half-clutch state. Therefore, it is possible to reliably prevent a cooing noise (abnormal noise) at the time of starting.Also, if the structure shown in FIG. Therefore, similar effects can be expected, and vibrations of the facing 28 and pressure plate 33 are suppressed, and clutch squeal is reduced.

Figure 5 shows the results of the additional photography test. The horizontal axis in FIG. 5 is the frequency H applied to the flywheel 32 in the direction of the crud center line.
2. The vertical axis is the acceleration G of the pressure plate 33 generated by resonance. As is clear from FIG. 5, compared to characteristic A of the conventional configuration, characteristic B of the configuration shown in FIG. 1 significantly reduces the acceleration of the pressure plate 33 and reduces clutch squeal.

(Effects of the Invention) According to the present invention, due to the axially biased suspension 3 provided to give a spring action to the cushioning plate 25, the pressure plate 33 becomes The phenomenon in which the pressure plate side facing 28b both vibrates 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.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal cross-sectional view of a clutch disc adopting the vibration damping structure according to the present invention, and Fig. 2 is a partially cutaway view of the clutch disc.
3 is a schematic view of FIG. 2 in the direction of the arrow. FIGS. 4 and 6 are drawings corresponding to a part of FIG. 2 to show another embodiment. FIG. 5 is a diagram showing the frequency. It is a graph showing the relationship between acceleration and acceleration. 16...Clutch plate, 25...Cushioning plate, 25a...First part, 25b...
2nd part, 28... facing, 29... fixed part, 35... overhanging part (vibration damping member), 36... presser foot (
Vibration damping member) Patent applicant: Daikin Seisakusho Co., Ltd. Agent: Patent attorney: Tadataka Oshiki - Procedural amendment I! (
Spontaneous) September 19, 1985 2 Name of the invention Clutch disk vibration damping structure 3 Relationship with the amendment case Notes from patent applicant Address 1-1-1 Kida Motomiya, Neyagawa City Name Dai Co., Ltd. Gold Seisakusho Representative Director and President: Masaru Sadatsu 4, Agent Address: 7th Floor, East Building, Chiyoda Building, 2-9-4 Higashitenma, Kita-ku, Osaka (No. 530) 5. Date of Amendment Order (Date of Shipment): Month, Day 6, 1920. ,
Counterprint of amendment Description and drawings, 7. Contents of amendment (1) The claims are amended as shown in the attached sheet. (2) Add the following statement between lines 2 and 3 on page 11 of the specification. [(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. (3) 11
Add 1 and Figure 7 J next to "Figure 6" on page 7 line. (4) Add attached Figure 7 to the drawings. 8. Attachment 1l11 Catalog of claims (1) Claims 1 copy (2)
Additional drawings (Figure 7) One or more Claims (1) The cushioning plate that connects the disc-shaped clutch plate on the output side and the input side facing on the outer periphery thereof has a surface that is flush with the part fixed to the clutch plate or a fly. A clutch disc having a first part biased toward the wheel side and a second part raised toward the pressure plate side from the first part, and a friction facing fixed to the flywheel side of the first part and the pressure plate side of the second part. In,
A vibration damping structure for a clutch disc, characterized in that a vibration damping member i that presses a raised second portion of a cushioning plate in a downward direction is removed. (2) A clutch disk according to claim 1, wherein a projecting portion is provided closer to the center of the tardage disk than the raised portion, and this projecting portion is engaged with the clutch plate to push down the second raised portion. vibration damping structure. (3) The vibration damping structure for a clutch disk according to claim 1, wherein the tip of the presser plate collinear with the cushioning plate fixing portion is pressed against the raised second portion. U

Claims (3)

[Claims] (1) The cushioning plate that connects the disc-shaped clutch plate on the output side and the input side facing on the outer periphery side has a first part that is flush with the part fixed to the clutch plate or biased toward the flywheel side, and a first part that is biased toward the flywheel side. In the clutch disc, a second portion is provided that protrudes toward the pressure plate side, and a friction facing is fixed to the first portion on the flywheel side and the second portion on the pressure plate side,
A vibration damping structure for a clutch disc, characterized in that the clutch plate is provided with a damping member that presses the raised second portion of the cushioning plate in a downward direction. (2) A clutch disc according to claim 1, wherein a projecting portion is provided closer to the center of the clutch disk than the raised portion, and the projecting portion is engaged with the clutch plate to push down the second raised portion. Vibration damping structure. (3) The clutch disk vibration damping structure according to claim 1, wherein the tip of the presser plate, which is fastened together with the cushioning plate fixing portion, is pressed against the second raised portion.