JPH0756294B2 - Damper disk - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to an improvement of a damper disk that provides a two-stage hysteresis torque by providing a sub plate so as to sandwich a hub flange of a spline hub.

(Prior Art and its Problems) Conventionally, a damper disk has been known which exhibits a two-step hysteresis torque by providing a sub-plate so as to sandwich a hub flange of a spline hub (Japanese Patent Application No. 55-133812).
issue).

In this type of damper disk, the stud pin integrated with the sub-plate is pressed against the edge of the window hole of the hub flange, and the sub-plate is twisted, so that the first-stage torsional characteristics X1 and X2 as shown in FIG. Demonstrates the twist characteristic X2.

By the way, when the above disc is applied to a clutch disc for tracks, there are the following problems.

For trucks, the power take-off device (Power Take Of
f) is provided, and a part of engine power guided from this power take-off device may be used to drive bodywork machinery such as a crane, but when a power take-out device is provided in the transmission, , Idle noise is generated.

That is, as shown in FIG. 8, when the power take-off device is not operating, idle starting noise does not occur because the operation starting point of the rotational fluctuation is in the region Y1, but when the power take-out device is operating, The load increases accordingly, and the area Y2
The starting point of movement moves to the second stage, and the second-stage torsional characteristic X2 is generated from the initial state of the torsion, and the rotational fluctuation is amplified and an abnormal noise is generated.

(Object of the Invention) The present invention has been made to solve the above problems, and it is an object of the present invention to provide a damper disk capable of preventing abnormal noise even when a load is applied in an idle state. Has an aim.

(Structure of the Invention) (1) Technical Means The present invention relates to a damper disc that exhibits a two-step hysteresis torque by providing a side plate and a sub plate so as to sandwich the hub flange of a spline hub. The stud pin tightens the sub plate. And an intermediate elastic member is provided at the end of the elongated slot of the hub flange through which the stud pin penetrates in the disc torsion direction. The intermediate elastic member is a boundary region between the first stage hysteresis torque and the second stage hysteresis torque. An intermediate hysteresis torque that is larger than the second-stage hysteresis torque and smaller than the second-stage hysteresis torque is generated, the stud pin is pressed against the intermediate elastic member by the twisting of the disk, and the elasticity of the intermediate elastic member causes the first-stage hysteresis torque characteristics and the second-stage hysteresis torque In the boundary area of eye hysteresis torque characteristics, prevent impact With a damper disk being characterized in that so as to exert an intermediate hysteresis torque characteristics.

(2) Action The intermediate hysteresis torque generated by the intermediate elastic member prevents generation of abnormal noise in the boundary region between the two hysteresis characteristics.

(Example) In FIG. 1 (I-O-I cross-sectional view of FIG. 2) showing a case where the present invention is applied to a clutch disc for an automobile, 10 is a spline hub. Spline inner teeth 12 are formed on the inner surface of the spline hub 10, and the spline inner teeth 12 are spline-fitted to the input shaft 14 (only the center line is shown) when viewed from the transmission (not shown) in the subsequent stage. It has become. A substantially annular hub flange 16 extends integrally outward of the spline hub 10 in the radial direction.

A clutch plate 18 is provided on the left side surface of the hub flange 16 via a bush 17, and a friction washer 20 and a friction plate are provided on the right side surface of the hub flange 16.
A retaining plate 26 is provided via a wave spring 24 and a wave spring 24. Sub-plates 28 and 30 are arranged axially outward of the clutch plate 18 and the retaining plate 26 (side plate).
A friction washer 32 and a friction plate 34 are interposed between 18 and the sub plate 28. A friction washer 32, a friction washer 36 for generating TH2 (FIG. 3), a friction plate 38, and a cone spring 40 are sequentially interposed between the retaining plates 26 and 30, like the friction washer 32.

A cushioning plate 44 is fixed to the outer periphery of the retaining plate 26 with rivets 42, and facings with rivets 46 on both sides of the cushioning plate 44.
48 is fixed.

The clutch plate 18 and the retaining plate 26 are
The stop pins 50 are integrally connected to each other on the outer peripheral portion, and the stop pins 50 arranged at four places at 90 ° intervals in the circumferential direction pass through the notches 52 (FIG. 2) of the hub flange 16. . Therefore, the clutch plate 18 and the retaining plate 26 are rotatable with respect to the hub flange 16 within the range of the circumferential length of the notch 52 and the stop pin 50.
After press-contacting the edge of the notch 52, the hub flange 16, the clutch plate 18, and the retaining plate 26 rotate together.

Further, sub-pins 54 are provided on the inner peripheral portions of the clutch plate 18 and the retaining plate 26 at three positions spaced 120 ° apart, and the heads 55 at both ends of the sub-pin 54 have the clutch plate 18 and the retaining plate 26. It is press-fitted into the hole 56 of the. The sub pin 54 has an elliptical hole 57 (second
(See Figure). The friction washer 50 to the wave spring 24 and the bush 17 are fitted so as to rotate integrally with the sub pin 54, and the friction washer 20 to the wave spring 24 has a weak first-stage hysteresis torque TH1 (in a small twist angle range). (Fig. 3) is generated.

Further, stud pins 60 are provided at three positions at 120 ° intervals at different circumferential positions from the sub pin 54, and the stud pins 60 tighten the sub plates 28 and 30 in the axial direction. As shown in FIG. 2, the stud pin 60 penetrates the elongated hole 61 of the hub flange 16, and the reverse R side end surface of the elongated hole 61, that is, the inner peripheral portion of the left end surface of FIG. A rubber piece 62 (intermediate elastic member) is provided.

The rubber piece 62 is fitted in the hole 63 so that a part of the outer peripheral surface of the rubber piece 62 projects from the end surface of the elongated hole 61 by a predetermined amount. The hole 63 is formed continuously with the long hole 61, and has a cylindrical rubber piece 62.
Are fixed to the hole 63 by press fitting. The amount of protrusion and the hardness of the rubber piece 62 from the end face of the long hole 61 are determined by the elasticity of the rubber piece 62 when the stud pin 60 is in pressure contact with the intermediate hysteresis torque TB3 (Fig. 3: TH1> TH3). > TH
2) is set to occur.

In addition, the stud pin 60 includes the clutch plate 18, the retaining plate 26, the friction washer 20, the friction plate 22, and the elliptical hole (second hole) of the wave spring 24.
(Fig.) And through the elliptical hole of the bush 17, bush 17, friction washers 32, 36, friction plates 34, 3
8. It is fitted together with the cone spring 40.

On the outer peripheral portion of the hub flange 16, window holes 65 and 66 are alternately formed at four places at 90 ° intervals. First, the first-stage torsion spring 70 and the second-stage torsion spring 71 are accommodated in the window hole 65, and the second-stage torsion spring 71, 3 and 3 are accommodated in the window hole 66.
A step torsion spring 72 is housed.

Clutch plate 18 corresponding to each of these springs,
Window holes 74, 75 are formed in the retaining plate 26, and notches 76, 77 are formed in the sub plates 28, 30.

A projection 81 that presses a spring seat 80 for the first-stage torsion spring 70 is formed on the end surface of the window hole 65 on the reverse R side, and a projection 81 is formed between the end surface of the second-stage torsion spring 71 and the end surface of the window hole 65. Is separated by a distance L1. Further, a spring seat 82 for the third-stage torsion spring 72 is provided on the R-side end surface of the window hole 66.
Is formed, and a space L2 is formed between the spring seat 82 and the recess 83.

Next, the operation will be described. When torque in the R direction (FIG. 2) is introduced from the facing 48 on the outer peripheral portion of the clutch disc as described above, the Kratz plate 18 and the retaining plate 26 are twisted with respect to the hub flange 16.

By this twisting operation, the protrusion 81 pushes the spring seat 80,
When the step torsion spring 70 is compressed, 0 ° to θ in FIG.
In the range of 1, the first stage torsional characteristic A is generated. At the same time, the sub-pin 54 causes the friction washer 20 to the wave spring 24 and the bush 17 (Fig. 1) to move to the clutch plate 1.
8. Because it twists together with the retaining plate 26, the first-stage torsion characteristic A has a slight first-stage hysteresis torque TH1.
Occurs.

When the torsion angle reaches θ1, the interval L1 in FIG. 2 becomes zero, the second-stage torsion spring 71 begins to be compressed, and
The second stage torsional characteristic B occurs at θ2. At this time, the stud pin 60 is pressed against the long hole 61 and the sub plates 28 and 30 are twisted together with the hub flange 16, so that the friction washer 3
2, friction plate 34, friction washer 36
~ The second stage hysteresis torque TH2 is generated in the cone spring 40 (Fig. 1).

When the torsion angle reaches θ2, the interval L2 in FIG. 2 becomes zero, the third-stage torsion spring 72 is compressed, and the third-stage torsion characteristic C is generated. Regarding the sub-plate type two-step hysteresis characteristic as described above, the above-mentioned Japanese Patent Application No. 55-1338.
See No. 12 for details.

In the boundary region between the first-step torsion characteristic A and the second-step torsion characteristic B, that is, in the minute angle range of the twist angles θ1 to θ1 ′, the long hole 61 is formed.
When the stud pin 60 is pressed against the rubber piece 62, the intermediate twist characteristic D is generated between the first-step twist characteristic A and the second-step twist characteristic B. This intermediate torsional characteristic D reduces the impact when the stud pin 60 collides with the elongated hole 61 and prevents abnormal noise when the torsional operation starting point moves within the region Y2 (FIG. 8).

That is, the amount of protrusion of the rubber piece 62 from the end surface of the long hole 61 is such that, when the stud pin 60 is in pressure contact with the rubber piece 62, the elasticity of the rubber piece 62 causes the intermediate hysteresis torque TH3 (TH1>TH3> in FIG. 3). TH2) is set so that the intermediate hysteresis torque TH3 prevents abnormal noise even when the load from the PTO device is applied during idling, for example, when the torsion operation starting point moves within the region Y2.

(Effect of the Invention) As described above, the damper disk according to the present invention is
A stud pin 60 for tightening the sub plates 28 and 30 is provided,
The long hole 61 of the hub flange 16 through which this stud pin 60 passes
An intermediate elastic member (for example, a rubber piece 62) is provided at the end portion of the disk torsion direction of the disk, and the intermediate elastic member is a boundary region between the first stage hysteresis torque TH1 and the second stage hysteresis torque TH2.
Intermediate hysteresis torque TH3 that is larger than the second stage hysteresis torque TH1 and smaller than the second stage hysteresis torque TH2
Occurs, the stud pin 60 is pressed against the intermediate elastic member by the twisting of the disk, and the elasticity of the intermediate elastic member causes the first-stage hysteresis torque TH1 and the second-stage hysteresis torque TH2.
In the boundary area of, the impact is prevented and the intermediate hysteresis torque TH3 is exerted. Therefore, the load by the PTO device is applied at the time of idling, for example, when the starting point of the torsion operation moves to the area Y2 shown in FIG. Even in the case, the intermediate hysteresis torque TH3 can prevent abnormal noise.

Therefore, conventionally, it was necessary to use a specially-made disc having a twisting characteristic capable of preventing the abnormal noise caused by the PTO device. However, the disc according to the present invention has one type of disc regardless of the presence or absence of the PTO device. You can use a disc.

(Another Example) (1) The intermediate elastic member of the present invention is not limited to the rubber piece 62, and as shown in FIG. 4, a rubber having a predetermined thickness is formed on the inner peripheral portion and the outer peripheral portion of the end face of the elongated hole 61. The plate 85 may be fixed.

In addition, as shown in FIG. 5, a roll pin 86 made of spring steel is bored.
The intermediate hysteresis torque TH3 (FIG. 3) shown in FIG. 3 may be exerted by fitting with 63 and by the frictional force of the stud pin 60 of the roll pin 86 and the frictional force associated with the deformation of the roll pin 86 itself.

Further, as shown in FIG. 6, the stud pin 60 may be sandwiched between the leaf springs 88 having the throttle portion 87, and the intermediate hysteresis torque TH3 may be exerted by the frictional force in the throttle portion 87.

Further, as shown in FIG. 7, both ends of the leaf spring 89 are grooved 90.
The intermediate hysteresis torque TH3 can be exerted by the frictional force generated between both ends of the leaf spring 89 and the groove 90.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view of a clutch disc for an automobile adopting the present invention, FIG. 2 is a view taken in the direction of arrow II in FIG. 1, FIG. 3 is a graph of torsion angle-transmitted torque, FIG. 4, and FIG. , FIG. 6 and FIG. 7 are schematic structural views showing different embodiments, and FIG. 8 is a graph of torsion angle-transmitted torque of a conventional example. 10 …… Spline hub, 16 …… Hub flange, 18 …… Clutch plate, 26 …… Retaining plate, 28,30 …… Sub plate, 60 …… Stud pin, 61 …… Long hole, 62 …… Rubber piece , 70, 71, 73 …… Torsion spring, 85 …… Rubber plate, 88, 89 …… Leaf spring

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yasunobu Fukaya 1-1-1, Kida Motomiya, Neyagawa City, Osaka Prefecture Daikin Co., Ltd. (72) Inventor Mitsuhiko Takenaka 1-1-1, Kida Motomiya, Neyagawa City, Osaka Prefecture Issue inside Daikin Seisakusho Co., Ltd. (56) Bibliographic references Sho 59-194636 (JP, U)

Claims (1)

[Claims] Claim: What is claimed is: 1. A damper disk which has a side plate and a sub plate so as to sandwich a hub flange of a spline hub and which exhibits a two-step hysteresis torque.
A tod pin for tightening the sub plate is provided, and an intermediate elastic member is provided at an end of the elongated hole of the hub flange through which the stud pin penetrates in the disc twisting direction. The intermediate elastic member has a first stage hysteresis torque and a second stage hysteresis torque. In the boundary region of, the intermediate hysteresis torque that is larger than the first stage hysteresis torque and smaller than the second stage hysteresis torque is generated, the stud pin is pressed against the intermediate elastic member by the twisting of the disk, and the first stage is generated by the elasticity of the intermediate elastic member. A damper disk, which is configured to prevent an impact and exhibit an intermediate hysteresis torque characteristic in a boundary region between the hysteresis torque characteristic and the second stage hysteresis torque characteristic.