JPH0534343Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a torsional vibration absorbing device, and in particular to a vibration absorbing device used in a flywheel, clutch disk, or drive shaft system to absorb torque fluctuations of a combustion engine. This relates to a shock absorber.

(Prior Art) This type of device includes a drive plate connected to a drive source, a driven plate connected to a driven member, and an elastic means provided between the two plates. It is well known that the plates are elastically compressed to cause the two plates to rotate in a predetermined manner, and that they are particularly applied to clutch discs of clutches for automobiles.

The relationship between the transmission torque and torsion angle of the power transmission device, which is affected by the elasticity of various components of the automobile drive system, has a natural frequency with a substantially linear correlation, and within a predetermined rotational speed range. This causes resonance and vibration, which generates undesirable vibrations and noise.

For this reason, in the past, a friction type damper device was used as an additional member, or elastic members with different rigidities were appropriately combined to adjust the characteristics of torsional torque with respect to relative rotational displacement between the drive plate and the driven plate depending on the degree of relative rotational displacement. Measures were taken to reduce vibration, noise, etc. by moving the In this case, it has been known to use an elastic body such as rubber instead of or in combination with the spring.
(For example, the one described in Japanese Patent Application Laid-open No. 59-200816 is
Since the spring seat is disposed between the end of the coil spring and the resilient member receiving portions of both plates, there are problems such as a disadvantage in terms of space when the thickness of the seat increases. ) (Problems to be Solved by the Invention) There is a torsional vibration absorbing device that uses rubber as the elastic body and sheets attached to both ends of the rubber as the elastic means. An example of a case where such an elastic means is used instead of a coil spring is as shown in FIG. 4, for example. In that case, the adhesive surface 43 of the sheet 41 with the rubber 42 is a flat surface, and the back surface 44 thereof is also a flat surface. Furthermore, the barrel diameter of the rubber 42 is uniform. As a result, when a pressing force is applied to the sheet, stress is concentrated on the adhesive surface of the sheet rubber, resulting in a drawback that this adhesive surface has poor durability. As a result, problems such as peeling of the rubber at the adhesive surface occur.

In addition, since the back surface of the sheet is flat, as shown in FIG. 5, the contact A between the sheet back surface 44 and the mating surface 51 hits a line in the vertical direction of the figure, and the pressing force applied to the sheet is concentrated and the sheet is There are disadvantages such as easy wear.

SUMMARY OF THE INVENTION An object of the present invention is to eliminate the above-mentioned drawbacks and provide a torsional vibration absorbing device having a novel vibration damping device.

(Means for Solving Problems by Invention) The torsional vibration absorbing device of the present invention is the torsional vibration absorbing device described at the beginning, and includes an elastic means consisting of a rubber-like elastic body and receiving members adhered to both ends of the elastic body, and the torsional vibration absorbing device of the present invention has The receiving member of the means is characterized in that an adhesive protruding surface is disposed at the center of the end face, leaving a peripheral edge portion of one end face, and the other end face of the receiving member forms a tapered back surface. Preferably, the diameter of the body of the rubber-like elastic body is made smaller at the center than at both ends.

In general, the strength of rubber is affected by its deflection rate, and the lower the deflection rate, the higher the strength. The deflection rate when rubber is subjected to compressive load is expressed by the following formula.

Deflection rate = amount of deflection/free length x 100 (%) Therefore, when the amount of deflection is the same, the rate of deflection can be made smaller by increasing the free length. Alternatively, the deflection rate can also be lowered by reducing the amount of deflection itself. As a result, strength can be increased.

The height H of the protruding surface disposed at the center of the end face of the receiving member in the elastic means is preferably 5 to 15% of the trunk length _L1 of the rubber-like elastic body (see FIG. 1).

Further, it is preferable that the size ΔR of the remaining portion on the end face of the receiving member from the outer periphery of the rubber-like elastic body is approximately the same size as H.

In a preferred embodiment using the present invention, the elastic means is formed from a coil spring arranged in a relative rotation direction and a rubber-like elastic member loosely fitted into the inner cavity of the coil spring, and A resin sheet having a diameter larger than the outer diameter of the rubber-like elastic member when compressed is firmly fixed to both ends of the coil spring and fitted into the inner cavity of the coil spring, so that the inner circumference of the coil spring and the rubber-like elastic member are connected to each other. There are some people who have been advised not to come into contact with them. Such a combination allows the advantages of the rubber-like elastic member to be utilized to the maximum extent possible.

(Example) Hereinafter, an example of the present invention will be described based on the drawings. FIG. 2 is a partially cutaway front view of the clutch disk provided with the elastic means of this embodiment.

The hub 1 has a spline 1a formed on its inner periphery, and is connected to an output shaft (not shown) via the spline 1a. A radially extending flange 2 is formed at the center of the outer circumference of the hub 1 . A main disk plate 3 and an auxiliary disk plate 4 are arranged at the outermost side so as to sandwich the flange 2 therebetween. These disk plates 3 and 4 are fixed to each other by stopper pins 5 at several locations near the outer periphery, so that the disk plates 3 and 4 can rotate together as a whole. A plurality of leaf springs 7 to which facings 6 are fixed are mounted on the outer periphery of the main disc plate 3 with rivets 19.
Fixed by This facing 6 transmits or blocks torque to both disk plates 3 and 4 by contacting and separating from a flywheel (not shown) that is a part of the input shaft. That is, both disk plates 3 and 4 are connected to the facing 6.
Torque is introduced from the outside via.

A friction material 20 and a thrust plate 21 are provided on the side surface of the hub flange 2 and pinch the hub flange 2 via a disc spring 22.

As mentioned above, the main and auxiliary plates 3 and 4 are arranged concentrically on both sides of the flange 2, and the pin 5 that integrally fixes these plates 3 and 4 has a notch 23 provided on the outer periphery of the flange. Since the main/auxiliary plates 3, 4 and the hub 1 are penetrated, the main/auxiliary plates 3, 4 and the hub 1 can freely rotate relative to each other as long as the pin 5 does not come into contact with the end face of the notch 23.

A plurality of elastic means 11, 17 for transmitting torque from the disk plates 3, 4 to the flange 2 are formed in window portions 8a, 9a, 10a, 8b, 9b corresponding to both the disk plates 3, 4 and the flange 2,
10b, respectively. 11 is
The elastic means of this embodiment is shown, and the coil spring 1
Window portions 8a, 9a, 10a are loosely fitted concentrically to 2.
It is inserted and arranged in.

Reference numeral 17 denotes elastic means consisting of a double elastic member of a first coil spring 24 and a second coil spring 25, which is inserted into the windows 8b, 9b, and 10b.

FIG. 1 is an enlarged view of the elastic means 11 of this embodiment. This elastic means 11 has rubber 1 on the sheet 13.
4 is vulcanized and bonded. This sheet 1
A protruding surface 15 is formed on the adhesive surface of No. 3 to the rubber. This protruding surface 15 is formed by providing a convex surface with a height H in the central portion, leaving the peripheral edge of the sheet adhesive surface. The periphery is covered with rubber 1 on the adhesive surface of the sheet.
It remains until the position is ΔR inside the body diameter of No. 4. As a result, the rubber 14 is formed with a portion 14a having a trunk length _L1 and a protruding portion 14b having a trunk length _L2 .

Further, the back surface 18 of the sheet 13 is tapered with a size θ, and the seat back surface 18 forms a tapered back surface. The magnitude of θ is appropriately selected so that the back surface 18 comes into surface contact with the abutting windows 8a, 9a, and 10a as the relative torsional movement progresses.

What is shown in FIG. 7 is another embodiment of the invention.

In the figure, the diameter of the rubber 31 is not uniform and the body is constricted. That is, the center part is thinner than both ends. By adopting such a shape, the change in deflection at the center portion becomes large, and as a result, the deflection at both ends can be reduced.

(Operation of the Embodiment) In FIG. 2, when the facing 6 is pressed against the flywheel side of the input shaft, torque is introduced into both the disk plates 3 and 4. This introduction torque causes the main and auxiliary plates 3 and 4 to move around the hub flange 2.
When rotated relative to the first spring 24, the first spring 24 contracts. Next, the second spring 25 and the elastic means 1
The coil spring 12 at 1 also contracts. When the coil spring 12 contracts, the side surfaces of the windows 10a and 8a provided in both the disk plates 3 and 4 come into contact with the back surface 18 of one of the seats of the elastic means 11.
By pressing this, the other seat back surface of the elastic means 11 comes into contact with the side surface of the window 9a provided in the flange 2 of the hub, and the elastic means 11 is compressed. Thereafter, the pin 5 comes into contact with the end face of the flange notch 23, so the main/auxiliary plates 3, 4 and the hub 1 rotate integrally. In this way, torque is transmitted from the input shaft to the output shaft.

In FIG. 1, elastic means 11 are used for shock absorption due to clutch engagement or for torque transmission.
A compressive load is applied to the rubber 14 . This compressive load causes a certain amount of deflection in the rubber 14. Regarding the deflection rate, the deflection rate differs between the portion 14a having the body length _L1 and the protruding portion 14b having the body length _L2 due to the difference in the free lengths L1 _{and L2} .
The deflection rate of the protruding portion 14b having a free length of L ₂ (L ₂ >L ₁ ) becomes small, and as a result, the strength becomes high.

In another embodiment of the present invention, which adopts the constricted rubber cylinder shape shown in FIG _. This reduces the deflection rate. As a result, the strength of the adhesive surface is further increased than that of the elastic means of this embodiment shown in FIG.

In the relative torsional movement of the clutch disk, the seat back 18 of the elastic means 11 is exposed to the windows 8a, 9a,
It comes into contact with the side surface of 10a. Since the seat back surface 18 is formed with a tapered surface, during contact and relative torsional movement, as shown in FIG.
become.

(Effects) According to the present invention, as described above, the bonding surface can be strengthened by increasing the free length of the rubber, or by simultaneously changing the shape of the rubber cylinder. As a result, the inconvenience caused by the adhesive surface of the rubber peeling off is eliminated. Furthermore, by forming a tapered surface on the back surface of the seat, it is possible to achieve surface contact with the side surface of the clutch disk window. As a result, concentration of the pressing force on one point on the sheet is avoided, and concentration of the pressing force on the peripheral portion of the rubber can be more reliably prevented, and wear on the sheet can also be prevented.

[Brief explanation of drawings]

Fig. 1 is an enlarged view of an elastic means according to an embodiment of the present invention, Fig. 2 is a partially cutaway front view of a clutch disk equipped with an elastic means according to an embodiment of the present invention, and Fig. 3 2 is a sectional view taken along the line in FIG. 2, FIG. 4 is an enlarged view showing the conventional elastic means, FIG. 5 is a diagram showing the operating state of the conventional elastic means, and FIG. 6 is an embodiment of the present invention. A diagram showing the operating state of the example elastic means,
FIG. 7 shows an enlarged view of the elastic means showing another embodiment of the present invention. 11... Elastic means, 13... Sheet, 14...
Rubber, 15... protruding surface, 18... seat back.

Claims (1)

[Claims for Utility Model Registration] (1) Consisting of a drive plate connected to a driving source, a driven plate connected to a driven member, and an elastic means provided between the two plates, the elastic means A torsional vibration absorbing device in which both the plates elastically contract and cause a predetermined relative rotation, comprising an elastic means consisting of a rubber-like elastic body and a receiving member adhered to both ends of the elastic member, and one end surface of the receiving member of the elastic means. A torsional vibration absorbing device characterized in that an adhesive protruding surface is disposed at the center of the end face except for the peripheral edge, and the other end face of the receiving member forms a tapered back surface. (2) The body diameter of the rubber-like elastic body is narrower at the center than at both ends.
Apparatus described in section. (3) The device according to claim 1 or 2, wherein the height H of the adhesive protruding surface of the receiving member is 5 to 15% of the trunk length _L1 of the rubber-like elastic body.