JPS59212534A - Damper disc - Google Patents

Abstract

PURPOSE:To facilitate generation of high hysteresis torque by furnishing a coil spring at its center with a damper mechanism, which expands or contracts in compliance with expansion/contraction of the coil sring when a flange and a side plate make relative rotation. CONSTITUTION:A damper mechanism 11 to expands and contracts in compliance with expansion/contraction of coil spring 10 is accommodated in each coil spring 10 at its center. The coil springs 10 are installed in contracted state in window holes 8a, 8b, 8c, and the ends of each spring in the disc circumferential direction are put in pressure contact with the end faces 14, 15, 14', 15', 14'', 15'' of each window hole 8a, 8b, 8c through seats 16, 17 of the damper mechanism 11. Also the end faces 12, 13 of a window hole 7 shall be contacted through these seats 16, 17 for coil spring 10 formed in the window hole 8a. Thereby the damper mechanism 11 expands and contracts when a flange 3 and a side plate 5 make relative rotation. Thus high hysteresis torque is generated easily.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates primarily to a damper disk suitable for automatic military clutch disks.

Damper discs for clutch discs have multi-stage torsional rigidity and multi-stage hysteresis that are effective for absorbing abnormal noise in automobile drive systems.
Due to other problems, it has not yet reached its final form.
.

For example, a damper disk used in conventional clutch disks has a flange formed integrally with a central hub, which is sandwiched between a pair of side plates from both sides, and the flange and side plates are connected via circumferential coil springs. In addition to elastically connecting the flange and the side plate to allow relative rotation, a friction member (damper mechanism) such as a cone spring or friction damper is interposed on the inner circumferential side between the flange and the side plate. ) is designed to generate hysteresis torque. There is also known a clutch disk that employs a configuration in which another friction member and a sub-plate are interposed on the inner peripheral side between the flange and the side plate to generate multi-stage hysteresis torque.

However, the conventional configuration described above has the following problems.

(1) Since the friction member is provided on the inner peripheral side, it is difficult to obtain high stealth torque.

(11) It is difficult to obtain stable hysteresis torque due to large variations in the load applied to the friction member.

(Iii) In order to obtain a multi-stage hysteresis)/reflector, it is not necessary to have a complicated structure as in the latter example above, and it is not a stupid structure that inevitably increases costs, but also a 14V that has many causes of failure.
) Since the friction member acts completely separately from the compression of the coil spring, it is difficult to obtain a timely hysteresis torque change in accordance with the operation of the spring.

In view of the above problems, the present invention can easily generate stable high hysteresis torque, easily generate multi-stage hysteresis torque that changes in a timely manner,
The present invention will now be described with reference to the drawings, with the aim of obtaining a damper disk with a simple structure and fewer failure factors at a low cost.

FIG. 1 is a partial longitudinal sectional view of a damper disk according to the present invention employed in an automatic military clutch disk.

In FIG. 1, a central spline hub 1 has a spline 2 on its inner peripheral surface that fits into an output shaft (not shown), and an annular flange 3 on its outer peripheral surface. A pair of annular side plates 5 are integrally connected to both sides of the flange 3 via stop pins 4 parallel to the center line 0□-〇.
6 (clutch plate and retaining plate), and the flange 3 and both plates 5.6 have multiple sets of window holes 7.8.9 (only one of each shown) spaced apart in the disk circumferential direction. They are set apart. The window holes 7.8.9 are formed at opposite positions in the front-rear direction, and compression coil springs lo are fitted into each set of three window holes 7.81.9. Each spring 1o extends in the circumferential direction of the flange 3 and both plates 5.6.
are elastically connected by a spring lO so as to be relatively rotatable in the circumferential direction. That is, the window hole 7 of the flange 3 is a substantially rectangular hole bored in the flange 8 and extending in the circumferential direction.
A central portion of the spring 1o is arranged. The window holes 8.9 of both plates 5.6 are substantially rectangular holes extending in the circumferential direction that are bored in the plates 5.6, into which the front and rear ends of the ring 100 (left and right ends in the figure) fit. At the same time, the outer peripheral edge and the inner peripheral edge of the window hole 8.9 are slightly extended to surround the spring 10 to prevent the spring 10 from flying out. Further, a damper mechanism 11 is housed in the center of the spring 10, and expands and contracts as the spring IO expands and contracts.

As shown in FIG. 2, four window holes 7 are provided at equal intervals in the circumferential direction, and both end surfaces 12 and 18 in the circumferential direction are curved in a concave shape. Four sets of window holes 8 (9) are provided at positions facing the window hole 7, and both end surfaces 14.15 in the circumferential direction are curved in a concave shape having the same curvature as the end surface 12.13.

Among the four sets of window holes 8 (9), the window hole 8a located at the top of the second prong is the longest in the circumferential direction, and both circumferential end surfaces 14, 15. 12.18 is consistent in the free state. The window hole 8b on the opposite side of the window hole 8a through the center o0 is at a distance L, L1 from the window hole 8a.
2 is set shorter in the circumferential direction, and the distance L1,
Both end faces 14', 15' are circumferentially spaced from end face 12.18 by L2. In addition, the remaining windows go and gQ are set to be shorter in the circumferential direction, and both end surfaces 14' of the window hole 8c are
, 15' are spaced from the end face 12.18 by a distance Lj, L4.

The coil spring 1o, which is compressed in the substantially circumferential direction in each window hole 8a, 8b, 8c, has both ends in the disk circumferential direction connected to each window hole 8a through the seat part 16.17 of the damper mechanism 11.
, 8b, 80 (7) end face 14.15.14', 15',
Press and tee 14' and 15'. The spring 10 in the window hole 8a also contacts both end surfaces 12,18 of the window hole 7 via the seats 16 and 17. Seat part 16.17
The side surfaces that come into contact with the end surfaces 14, 15, 14', 14', and 15' are corresponding convex curved surfaces,
A cylindrical cylinder part 18 is formed integrally at the center of one seat 16, and a cylindrical colored piston part 19 is formed integrally at the center of the other seat 17. and are slidably fitted together. Therefore, a closed space is formed in the cylinder part 18 by the piston part 19, and the closed space communicates with the outside only through a small gap between the cylinder part 18 and the piston part 19. Note that the seat portions 16 and 17 forming the damper mechanism 11, the cylinder portion 18,
The piston portion 19 is made of metal such as iron or aluminum, or resin.

Furthermore, the inner circumference of a cushioning brake 20 (only one is shown) is fixed to the outer circumference of the plate 5 (clutch plate), and annular facings 2 are attached to both sides of the brake 20.
1 is attached.

Also, a stop pin 4 integrally connects both plates 5 and 6.
is fitted into a notch 22 formed on the outer periphery of the cylinder 8.

Next, the operation will be explained. When the facing 21 is pressed against the flywheel of the engine by a pressure plate (not shown) in FIG. 1, torque from the flywheel is applied to the facing 21. plate 20, plate 5.6,
The spring 101 is transmitted to the output shaft via the flange 8 and the hub 1.

For example, facing 2 for spline hub l.
When a torsional torque in the direction of the arrow X□ in FIG. 2 is applied to the motor 1, the torque vibration is absorbed by the following operation. In FIG. 8 showing the torsion angle θ vs. torsion torque T characteristic, the side plate 5.6 is moved from the neutral state to x with respect to the flange 3.
When twisting in one direction (Figure 2), the twist angle θ is 0~
Between θ (first stage), only the spring 10 in the window hole ga (same on the window hole 9 side) among the eight types of window holes 8 (9) is compressed. As a result, the damper mechanism 11 is compressed between the end surface 15 of the window hole 8a and the end surface 12 of the window hole 7 (the piston section 19 is deeply fitted into the cylinder section 18), and the air in the cylinder section 18 is simultaneously compressed. The third
The relationship A in the figure is obtained.

At this time, on the other hand, the distances 2 and H3 in the remaining window holes 8b and 8C become shorter as the torsion angle θ increases,
When the seat portion 16 comes into contact with the end surface 12 of the window hole 8b having the shorter distance L, the twist angle θ becomes θ1. Next, when the torsion angle θ is between θ and θ2 (second stage), the window hole 3a
, gb are compressed, and the damper mechanisms 11 disposed within these springs 10 are compressed, thereby obtaining the relationship B in FIG. 8. When the distance L3 becomes zero within the window hole 7 having the longest distance Lj, H4, the twist angle θ becomes θ2. Furthermore, the torsional torque T increases and the cylinder 8 and side plate 5.6
When the twist progresses between 02 and θ3 (the 8th
During this period, the springs 10 in all the window holes 7 are compressed. Therefore, when all the damper mechanisms 11 are compressed, the relationship C in FIG. 8 is obtained from K. When the torsion angle θ reaches 03, the stop pin 4 comes into contact with the circumferential end face of the notch 22, and the facing 21 and the hub 1 are integrally connected via the stop pin 4.

When returning from the maximum post-multiple angle θ3, it operates in the opposite direction to the above operation and each damper mechanism 11 extends, so the eighth
The relationships C', B', and A' in the figure are obtained.

That is, in the first stage operation (0 to θ,), only the damper mechanism 11 inside the window hole 8a operates, so the obtained hysteresis torque Ha is small. In the second stage (01 to θ2), the window hole 8
Since the damper mechanism 11 in the window a and the window hole 8b works, the obtained hysteresis torque Hb is larger than the torque H8. In the third stage (θ2 to θ3), all damper mechanisms 11
Because it works, the biggest historicalist! H8 can be obtained.

Even in the case of twisting in the reverse X direction, the same operation can be performed to obtain a similar change in hysteresis Fμ.

However, in the case of , the shorter the distance HE LX,L, the more the hysteresis)
, Hb, and Ho operate to increase.

As described above, according to the present invention, the annular flange 8 is integrally formed on the central hub 1, and the two annular side plates 5, 6 are integrally connected to each other on both sides of the flange 80.
window holes 7.8.9 are provided at mutually opposing positions in the flange 3 and each side plate 5.6, and the window holes 7.
．． In the damper disk in which a substantially circumferential coil spring 1O is fitted in the damper disk 8.9 to elastically connect the 7 langes 8 and the side plate 5.6 so as to be relatively rotatable in the circumferential direction, the coil spring Since a damper mechanism 11 that expands and contracts as the coil spring 10 expands and contracts during relative rotation between the flange 3 and the side plate 5.6 is provided at the center of the flange 3 and the side plate 5.6, the inner periphery between the flange 3 and the side plate 5.6 Compared to the conventional configuration in which a friction member is interposed on the side,
A stable high hysteresis torque can be easily generated, and a multistage hysteresis torque that changes in a timely manner according to the operation of the spring 10 can be easily generated. Moreover, compared to the conventional structure in which a sub-plate or another friction material is added to generate multi-stage hysteresis torque, the structure is much more hourly, and there is an advantage that a damper disk with fewer failure factors can be obtained at a low cost.

Note that when implementing the present invention, the following configuration may also be adopted.

(a) Instead of sucking and discharging the air in the cylinder part 18 through the gap between the cylinder part 18 and the piston part 119 of the damper mechanism 11, for example, a hole for air passage is provided in the cylinder part 18 or the piston part 19. may be provided separately. At this time, a check valve may be provided in the hole to restrict only the discharge of air so that the damper mechanism 11 can be smoothly extended.

Further, the damper mechanism is not limited to the one shown in FIG. 2, but may be one that generates hysteresis torque, such as one that utilizes the orifice principle using fluid such as air or oil as a medium, or one that uses friction. When employing the damper mechanism 11 as shown in FIG. 2, the stop pin 4 can be eliminated and the maximum twisting angle can be limited by the damper mechanism 11.

(To) A damper mechanism 23 as shown in FIG. 4 may be adopted. At the center of one of the spring seats 24 of the damper mechanism 23, there is a conical portion 2 in a position protruding into the spring 10.
A collet-shaped portion 28 having a split groove 27 is formed at the center of the other spring seat portion 26, and the tip of the portion 28 is elastically pressed against the outer peripheral surface of the portion 25. . Here, the seat portion 24 and the portion 25 are made of resin or metal such as iron, and the seat portion 26 and the portion 28 are made of an elastic material such as spring steel. In this case, hysteresis occurs as the portion 28 slides on the portion 25 as the spring 10 is compressed. By changing the shape of the portion 25, for example, as shown in FIGS. 5(a) to (6), various hysteresis torque changes can be obtained. Alternatively, a hole in the compression direction may be formed in the portion 25, and the portion 28 may be elastically pressed against the inner peripheral surface of the hole.

(C) A damper mechanism 29 as shown in FIG. 6 may be employed. A cylindrical externally threaded portion 3 is located at the center of one seat portion 8o of the damper mechanism 29 in a position that projects into the spring 10.
1 is formed, and a cylindrical internally threaded portion 85 is formed in the center of the spring seat portion 32 of the capacity to be screwed into the portion 31. These are made of metal such as iron or resin, and the pitch of the threads formed is large. Therefore, when the spring 10 is compressed, the portion 31 is screwed into the portion 38, causing hysteresis due to the friction between the drawing portions 81 and 38 and the friction between the window holes 7 (8, 9) and the seats 80 and 82. Torque is generated.

In this case, the hysteresis torque can be easily changed by changing the pitch of the screw.

2) Fit the damper mechanism 23.29 shown in FIGS. 4 and 6 into the rounded window hole 7.8 (9) shown in FIG. The contact surface may have a corresponding curved shape.

(e) The sliding surfaces of the damper mechanisms 23 and 29 in FIGS. 4 and 6 may be coated to obtain a stable coefficient of friction.

(f) When generating multi-stage hysteresis torque, instead of uniformly providing the damper mechanisms 11, 23, and 29, for example, the damper mechanisms 23 shown in FIG. An annular spacer may be interposed, and a conventional 7-reaction washer,
It is also possible to use a conventional hysteresis generating mechanism by interposing a cone spring or the like.

(b) The damper mechanisms 11, 23, 29 may be provided in the torsion spring portion of a damper disk of a type that generates multi-stage hysteresis by interposing a sub-plate between the flange 8 and the side plate 5, 6.

(1) Damper mechanism for all stages of torsion angle θ 11.28.
It is not necessary to operate the 29, and for example, the steresis torque can be obtained by a conventional configuration in the first stage and the second stage.

(j) Changes in hysteresis torque are not limited to 8 steps,
For example, the relationship between window hole 7 and window hole 8.9 (distances L1, L2,
. . ) or by changing the numbers of the window holes 7, 8, 9 and the springs 10, it is possible to obtain changes of one, two, or four or more stages.

[Brief explanation of the drawing]

FIG. 1 is a partial vertical sectional view of the damper disk according to the present invention when adopted as a clutch disk, FIG. 2 is a sectional view taken along line I-1 in FIG. 1, and FIG. 8 is a graph showing torsion angle-torsion torque characteristics. 4 and 6 are views corresponding to the I-I cross section of FIG. 1 showing different embodiments, and FIG.
FIG. 4 is a partial view showing a modification of the damper mechanism shown in the figure, viewed in the same direction as FIG. 4; ■...Hub, 3...Flange, 5
．． 6... Side plate, 7.8.9... Window hole, 1
0...Coil spring, 11, 2B, 29...Damper mechanism Patent applicant Okine Seisakusho Co., Ltd. Agent Patent attorney Tadashi Omori lj'1, Ib-

Claims (1)

[Claims] An annular 7-lunge is integrally formed on the central hub, and both sides of the flange are sandwiched between two annular side plates that are integrally connected to each other, and window holes are formed at opposing positions of the 7-lunge and each side plate. A damper guy and a suspension member are provided in which a coil spring is fitted in a window hole in a substantially circular direction to elastically connect a flange and a side plate so as to be relatively rotatable in a circumferential direction. A damper disk characterized in that it is provided with a damper mechanism that expands and contracts as a coil spring expands and contracts during relative rotation between the flange and the side plate.