JPH0137225Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a damper disk suitable for automobile clutch disks, etc., and particularly to a damper disk incorporating an oil-type shock absorber.

This type of damper disk has been proposed by the applicant, for example, in Japanese Patent Application Laid-open Nos. 56-120824, 56-120844, and
No. 56-131851, etc., and its structure is basically that the input side plate covers the output side hub flange in a liquid-tight state, and the internal space of the side plate is filled with oil. When twisting against the flange, the viscosity of the oil generates hysteresis torque to absorb torque vibrations. Since the inside of such a damper disk is filled with oil, it is not possible to provide a window hole in the side plate, and the torsion spring is placed in contact with the end surface of a semicircular recess provided on the inner surface of the side plate. It's summery. However, the end face of such a recess must be formed at right angles to the inner surface of the side plate other than the recess, and the entire recess must be formed by deep drawing with fixed corners (large bending angle and small bending radius). Therefore, there is a risk of drawing cracks occurring during molding.

In order to solve the above problems, the present invention covers the flanges of the spline hub in a liquid-tight manner with a pair of side plates whose outer peripheries are connected to the facing, and has a plurality of depressions circumferentially formed on the inner surface of the side plates. The recesses are formed at intervals, each recess is set in such a shape that its length in the disk radial direction and circumferential direction increases as it goes toward the flange, and a torsion spring is provided in each recess that extends generally in the disk circumferential direction. is arranged so as not to engage with the inner surface of the recess in the disc circumferential direction, the sub-plate is fixed to the inner surface of the side plate in a state that it cannot rotate relative to the inner surface of the side plate, and the torsion spring is connected between the sub-plate and the flange. It is characterized in that it has window holes into which it enters, each window hole has an edge that engages the torsion spring in the generally circumferential direction of the disc, and the internal space between both side plates is filled with oil.

Next, embodiments will be described with reference to the drawings.

FIG. 1 is a longitudinal sectional view of a clutch disk for a vehicle to which the present invention is applied, and FIG. 2 is a partially cutaway view of FIG. 1 in the direction of the arrows. In Fig. 1, a flange 2 of a spline hub 1 spline-fitted to an output shaft (not shown) is connected to a pair of side plates 3 (a clutch plate and a retaining plate) from both the left and right sides.
covered by. The plate 3 has a larger diameter than the flange 2, and its outer periphery is connected to each other via an annular ring 6 and a seal 6a by rivets 5 arranged at intervals in the circumferential direction. A cushioning plate 7 is fixed to the plate 3 on the left side in FIG. 1 using rivets 5. A facing 8 is fixed to the cushioning plate 7 by a rivet 9. Each side plate 3
is equipped with a cylindrical flange 10 on the inner peripheral edge. The flange 10 protrudes from the main body of the plate 3 on the side opposite to the flange 2, and its inner peripheral surface is slidably fitted into the annular seal 11. The seal 11 fits into a groove 11a provided on the outer peripheral surface of the spline hub 1.

An annular sub-plate 4 is fixed to the inner surface of each plate 3 (the surface facing the flange 2) by a stopper pin 13. The pin 13 passes through the notch 15 of the hub flange 2 and connects to both side plates 3.
The parts near the outer periphery of the pins 13 are connected to each other.
A sub-plate 4 is held between the large-diameter intermediate portion 13a and the side plate 3. Sub plate 4
The outer circumferential edge of the ring 6 is adjacent to the inner circumferential edge of the ring 6 with a slight gap therebetween. A spring 12 is interposed in a compressed state. Note that there are washers 14 on both ends of the pin 13.
is attached, and an O-ring 13a that fits into the pin 13 is provided between the washer 14 and the plate 3.

17 and 18 are large and small diameter compression coil springs arranged concentrically; the flange 2 and the sub-plate 4 are provided with window holes 20 and 21 into which the springs 17 and 18 fit; A semicircular recess 22 is provided to cover the springs 17 and 18 protruding from the window hole 21. As shown in FIG. 2, the disk has two sets of springs 17,
18 and two large-diameter compression coil springs 19 are arranged at equal intervals in the circumferential direction, and the springs 19 also fit into the window hole 2 of the flange 2 and the sub-plate 4.
0, 21 and is covered by a semicircular recess 22 of the side plate 3.

In the illustrated state where the flange 2 and the side plate 3 are not twisted relative to each other (twist angle D in FIG.
= O), the end of the small-diameter spring 18 on the disk rotation direction A side is connected to the protrusion 30 of the side edge 25 of the window hole 20 and the side edge of the window hole 21 via the small-diameter spring receiver 24 integrally having the guide pin 23. It is in contact with 26,
The opposite rotation direction side of the small diameter spring 18 (reverse arrow A
The end portions of the side) abut against the side edges 25 and 26 of the window holes 20 and 21 via a spring receiver 29 and a spring receiver 31 that integrally have a guide pin 28. One end of the large-diameter spring 17 is in contact with the outer circumference of the spring receiver 31, and the other end of the spring 17 is in contact with the side edge 26 of the window hole 21 via the annular spring receiver 33. The spring receiver 33 is slidably fitted on the outer circumferential surface of the spring receiver 24, and is twisted by 3 degrees with respect to the recessed portion of the window hole side edge 25 (the portion radially inward and outward from the protrusion 30). They are located across a gap corresponding to corner D. Both ends of the spring 19 are in contact with the side edge 25 of the window hole 20 via spring receivers 35 and 35'.
5, 35' and the side edge 26 of the window hole 21 are separated by gaps corresponding to torsional angles of 6° and 3°, respectively. The spring receivers 31, 33, and 35 described above have substantially the same outer circumferential shape, and are slidably in close contact with the inner circumferential surface of the recess 22 and the inner and outer circumferential edges of the window holes 20 and 21, respectively, and the inner circumferential portion 36 has a radius protrudes inward.

In FIG. 3, which is a schematic cross-sectional view of FIG. 2, 22a is the bottom wall of the depression 22, and the spring 1
It extends along the outer periphery of 7. Reference numeral 22b denotes an end wall of the recess, which is inclined so as to move away from the spring receivers 31 and 33 as it goes from the bottom wall 22a side to the flat part side of the side plate 3. The spring receivers 31 and 33 are attached to the end wall 2
It is not pressed against 2b. Spring 19 in Figure 2
The recess 22 covering the recess 22 has a similar shape to the recess 22 shown in FIG. 3, and becomes wider toward the flange 2 side.

In FIG. 3, the internal space between both side plates 3, that is, the spring installation chamber 40 facing the inner surface of the recess 22, and the area other than the recess 22 between each side plate 3 (sub-plate 4) and the flange 2. A gap 41 formed between them is filled with oil. As shown in FIG. 4, which shows the negative cross-section of FIG.
A recess 46 is provided in a portion of the bottom wall 22a near the facing 8, and an oil inlet 42 is formed by a hole provided in the recess 46. Inlet 42
A nut 44 is welded to the inner surface of the recess 46 around the recess 46, and a plug screw 4 is inserted from the outside of the recess 22.
3 is screwed into the nut 44.

Explain the operation. When the clutch is connected, torque in the direction of arrow A in FIG. The hub 1 is transmitted to the output shaft, and the spring 17, 1
8 and 19 are compressed, and the side plate 3 is twisted in the rotational direction A with respect to the flange 2 together with the sub-plate 4. In that case, when the torsion angle D is less than 3° (O-P ₁ in FIG. 5), each spring 17, 18,
Among the springs 19, only the small diameter spring 18 is involved in torque transmission and is compressed.
The spring transmission torque T for the torsion angle D is as follows.
(Torque transmitted only via springs 17, 18, 19) increases at a low rate. When the torsion angle D reaches 3°, the annular spring holder 33 comes into contact with the side edge 25 of the window hole 20, and thereafter the spring 1 continues until the torsion angle D reaches 6°.
Since the torque T is transmitted through the springs 7 and 18, the rate of increase of the spring transmission torque T with respect to the torsion angle D increases as shown in the section P ₁ -P ₂ in FIG. When the torsion angle D reaches 6 degrees, the spring receiver 35 touches the side edge 2 of the window hole 21.
6, the torque T is transmitted through all the springs 17, 18, 19 until the torsion angle D reaches 9 degrees, and the torsion angle D changes as shown in the section P ₂ - P ₃ in FIG.
The rate of increase in the spring transmission torque T relative to the current value becomes even larger. When the twist angle D reaches 9 degrees, the stopper pin 13 comes into contact with the edge of the notch 15, and further twisting is prevented. In the above operation, the recessed end wall 22b in FIG. 3 does not come into pressure contact with the spring receivers 31, 33 or the spring receiver 35 in FIG.
Compress 19.

As mentioned above, the side plate 3 is the sub-plate 4.
At the same time, when the cone spring 12 is twisted relative to the flange 2, slipping occurs on the surface of the cone spring 12, and hysteresis _h1 corresponding to the frictional force during the sliding action occurs in the torsion angle D-transmission torque T characteristic as shown in FIG. When the springs 17, 18, and 19 are compressed, the spring bearing 31 moves to the right in FIG. 3, acts as a piston, and is pushed into the gap 41 by the oil spring bearing 31 in the chamber 40. . In that case, the oil is pushed out into the gap 41 through the narrow gap between the outer periphery of the spring receivers 31 and 33 and the recess 22. Resistance force (shearing force due to viscosity) due to the flow within the gap 41 is applied to the spring receivers 31 and 33. On the other hand, the spring receiver 35 in Fig. 2
As it moves, it also receives resistance from the oil. In this way, the oil is removed from the spring bearings 31, 3.
3, 35 is transmitted to the plate 3 which is about to twist, so the actual twist angle D-transmission torque T characteristic (solid line In addition, hysteresis H, which is the sum of the hysteresis h and the hysteresis h ₁ due to the friction of the cone spring 12, occurs in the above characteristics. Note that FIG. 5 shows the characteristic X when the torsional angular velocity is constant, so the hysteresis h is constant, but as the torsional angular velocity increases or decreases, the moving speed of the spring receivers 31, 33, and 35 also increases or decreases. Since the flow velocity of the oil also increases or decreases, the resistance force due to the oil and the hysteresis h caused by it also change in accordance with the torsional angular velocity.

In FIG. 1, when the oil is compressed in the chamber 40, the oil tends to leak from around the seal 11 to the outside through the space between the sub-plate 4 and the flange 2. Only a very narrow throttle passage is left between the plate 4 and the flange 2, and from the chamber 40 to the seal 1
The hydraulic pressure applied to 1 is reduced by a spring 12. Therefore, only a low oil pressure is applied to the seal 11, and oil leakage from around the seal 11 is reliably prevented.

As explained above, according to the present invention, the sub-plate 4 is fixed to the side plate 3, and the torsion spring 1 is attached to the sub-plate 4 and the flange 2.
7, 18, 19 are provided, and a torsion spring 1 is inserted into each window hole 21, 20.
7 to 19 are provided with edges 26, 25 that engage generally in the circumferential direction of the disk. Therefore, the torsion spring 2 is placed in each recess 22 of the side plate 3.
2 are not engaged with each other, the recess 22 can be set in such a shape that its length in the disk radial direction and circumferential direction increases as it goes toward the flange side. In this way, in the present invention, the recess end wall 22b can be inclined to form the recess 22 in a shape that becomes wider as it goes toward the flange 2 side.
It is possible to prevent drawing cracks from occurring during the molding of No. 2 and simplify the molding work.

Also, as shown in FIG.
When provided on the 5 side, an advantage can be obtained that the screw 43 and the recess 46 do not interfere with the release mechanism 47 on the opposite side.

Note that when embodying the present invention, the cone spring 12 may be eliminated and hysteresis may be generated using only the viscosity of the oil.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional view of the embodiment, Fig. 2 is a partially cutaway view of Fig. 1 in the direction of the arrows, and Fig. 3 is a - of Fig. 2.
FIG. 4 is a schematic cross-sectional view of FIG. 2, and FIG. 5 is a graph showing transmission torque-torsion characteristics. 1... Spline hub, 2... Flange, 3...
...Side plate, 4...Sub plate, 8...
Facing, 17, 18, 19... Torsion spring, 20, 21... Window hole.

Claims (1)

[Scope of utility model registration request] A pair of side plates, the outer periphery of which is connected to the facing, covers the flange of the spline hub in a liquid-tight manner, and a plurality of recesses are formed on the inner surface of the side plates at intervals in the circumferential direction, and each recess is The length of the disk in the radial and circumferential directions increases toward the flange, and a torsion spring extending approximately in the circumferential direction of the disk is installed in each of the recesses in the direction of the disk circumference against the inner surface of the recess. The sub-plate is fixed to the inner surface of the side plate in such a manner that it cannot be rotated relative to the inner surface of the side plate, and a window hole into which the torsion spring enters is provided between the sub-plate and the flange, and a torsion spring is inserted into each window hole. A damper disk characterized in that an edge is provided which engages a spring in a generally circumferential direction of the disk, and an internal space between both side plates is filled with oil.