JPH0137226Y2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention mainly relates to a damper disk assembly suitable for a clutch disk for an automobile.

First, FIG. 1 shows a case where a general damper disk assembly is adopted as a clutch disk for an automobile. In FIG. 1, which is a partial schematic view of a longitudinal side surface, a spline hub 1 has a spline 2 on its inner circumferential surface that fits into an output shaft (not shown), and an annular flange 3 on its outer circumferential surface. Friction members 4, 5 are arranged along the inner periphery of both sides of the flange 3, and a pair of annular side plates 6, 7 (a clutch plate and a retaining plate) are arranged on both sides of the flange 3, sandwiching the friction members 4, 5. ) are placed. A plurality of window holes 9, 10, 11 (only one of each is shown) are provided at intervals in the circumferential direction of the clutch disk in the flange 3 and the outer periphery portions of both plates 6, 7, respectively. The window holes 9, 10, 11 face each other in a direction parallel to the center line of the output shaft (left-right direction in FIG. 1), and a compression coil spring 12 is installed in each set of three window holes 9, 10, 11. (Torsion spring) is fitted. Each spring 12 extends in the circumferential direction of the clutch disk, and the flange 3 and both plates 6, 7 are connected by the spring 12. The outer peripheries of both plates 6 and 7 are connected to each other by a stop pin 8. The inner circumference of a cushioning plate 13 is fixed to the outer circumference of one plate 6 (clutch plate), and annular facings 14 are attached to both sides of the plate 13. When the facing 14 is pressed against the flywheel of the engine by a pressure plate (not shown), torque is applied from the flywheel to the facing 14, the plate 13, the plates 6 and 7, the spring 12, the flange 3, and the hub 1.
is transmitted to the output shaft via. In this case, the spring 12 is compressed in response to the transmitted torque, and the side plates 6, 7 are twisted relative to the flange 3, causing the friction members 4, 5 to slip. As a result of this slippage, a hysteresis torque _h1 is generated in the torsion torque T - torsion angle θ characteristic as shown in Figure 2, and the hysteresis torque absorbs torque vibrations, preventing abnormal vibrations and noises in the power transmission mechanism. be done. In addition, the third
A configuration in which the clutch disk has nonlinear characteristics as shown in the figure is already known.

Furthermore, as an improvement on these, a configuration as shown in FIG. 4 is already known. The same reference numerals are given to the parts corresponding to those in FIG. 1, but in FIG. The outer peripheral portions of the two are integrally connected by a sub-pin 17. Also, between the inner peripheral part of the flange 3 and the plates 15 and 16, and between the plates 15 and 16
and the friction members 1 between the plates 6 and 7, respectively.
8, 19, 20, and 21 are interposed. In the configuration shown in FIG. 4, due to the combination of the torsion spring and the window hole (not shown), while the torsion angle θ is small, slippage occurs between the flange 3 and the plates 15 and 16, resulting in a small hysteresis torque h ₂ ( (Fig. 5) occurs, and if the torsion angle θ becomes large, the plates 15 and 16
Sliding occurs between the plates 6 and 7, and a large hysteresis torque _h3 (Fig. 5) is generated.

However, these conventional configurations have hysteresis torques h ₁ and h ₂ in the low torsion angle region, and on the other hand, the torsion spring that acts is set to be weak in order to smooth the twisting of the disk at low torsion angles. . Therefore, when the disk returns from the highly twisted state, the frictional force of the friction members 4, 5, 18, and 19 overcomes the rigidity of the torsion spring, and the disk's torsion angle θ does not return to O, but remains twisted in the middle. It stops in this state. Then, when it is twisted again in the same direction, the maximum torsion angle becomes substantially smaller than the designed maximum torsion angle, resulting in a problem in which the desired vibration absorption effect cannot be obtained (so-called instability phenomenon occurs).

In view of the above-mentioned problems, the present invention is aimed at preventing the occurrence of unstable phenomena and always ensuring good absorption of transmitted torque vibrations.The present invention will be described below with reference to the drawings.

In FIG. 6, which is a longitudinal cross-sectional partial view of the damper disk assembly according to the present invention, parts corresponding to those in FIG. 1 are given the same reference numerals. Furthermore, in place of the friction members 4 and 5 in FIG. 1, annular magnets 31 and 3 are provided between the flange 3 and the side plates 6 and 7 in FIG.
2, 33, and 34 are provided. These magnets 31 to 34 are attached to the flange 3, the side plate 6,
7 mutually opposing opposing surfaces 40, 41, 42, 4
It is fixed to the inner peripheral part of 3. The magnets 31 and 32 are fixed to the inner circumferential surfaces of the opposing surfaces 40 and 41 in a pair so as to face each other, and the magnets 33 and 34 are fixed to the inner circumferential portions of the opposing surfaces 42 and 43 in a pair so as to face each other. It is fixed.

The magnets 31, 32, 33, and 34 are fixed to the flange 3 and the plates 6 and 7 by effective means such as magnetic force or adhesive. The magnet 31 fixed to the side plate 6 and the magnet 32 fixed to the flange 3 with a slight gap therebetween have the same poles facing each other (N poles facing each other or S poles facing each other). ), and due to the repulsive force between both magnets 31 and 32, the side plate 6 is always aligned with the arrow X ₁ relative to the flange 3.
receiving a directional force. Similarly, due to the repulsive force of the magnets 33 and 34 provided between the flange 3 and the plate 7, the plate 7 is constantly moved toward the flange 3.
X It is receiving forces in _two directions. Therefore, both the plates 6 and 7, which are slidably fitted in the axial direction on the hub 1 and are integrally connected, are separated by the gaps formed between the magnets 31 and 32 and between the magnets 33 and 34, respectively. , and the flange 3 will no longer generate friction torque.

If the configuration shown in FIG. 6 is adopted, hysteresis torque will not occur as shown in FIG. 7, so the return of the disk will always be accurate and unstable phenomena will be prevented.

If the configuration shown in Fig. 6 is adopted for a type of disk in which a torsion spring and a window hole are combined so that the torsion torque-torsion angle characteristics shown in Fig. 3 are obtained, the characteristics shown in Fig. 8 will be obtained. , no hysteresis torque occurs, and no instability occurs.

Furthermore, the present invention is not limited to being applied to a clutch disk having a pair of side plates 6, 7 as shown in FIG. For the conventional example having a pair of inner side plates 15 and 16 that rotate relative to the flange 3 in a low torsion angle range, the configuration shown in FIG. 9 may be adopted. In Fig. 9, the sub-side plates 15, 16 and the flange 3
There are magnets 35 and 3 in the same relationship as shown in FIG.
6, 37, and 38 are provided, and gaps are formed between the magnets 35, 36 and between the magnets 37, 38, so that no hysteresis torque is generated between the plates 15, 16 and the flange 3. Therefore, if the configuration shown in FIG. 9 is adopted, the characteristics shown in FIG. 10 will be obtained, and hysteresis torque will not occur in the low torsion angle region, thereby preventing the occurrence of unstable phenomena.

As explained above, according to the present invention, the side plates 6, 7 and the annular flange 3 rotate relatively within a low torsion angle range, for example, as shown in FIG.
Opposing surfaces 40, 41, 42, 43 facing each other
Magnets 31, 32, fixed to the side plates 6, 7 and the annular flange 3, respectively, are attached to the inner periphery of the
33 and 34 are arranged with a slight gap between them so that their magnetic forces repel each other in the direction of the clutch axis.
Move the side plates 6 and 7 with the arrows using the magnetic force of 1 to 34.
It can be pushed and expanded in the X1 and X2 directions, and the side plates 6 and 7 are clamped by the stop pin 8 on the outer periphery, which prevents unnecessary hysteresis torque from occurring on the inner periphery of the opposing surfaces 40 to 43. This has the advantage that it is possible to prevent the occurrence of instability caused by this unnecessary hysteresis torque, and to obtain a damper disk assembly that can always satisfactorily absorb transmitted torque vibrations.

In implementing the present invention, the configuration according to the present invention is adopted only on one side of the flange 3, and a friction member similar to the conventional one is interposed on the other side, so that the push of the friction member is caused by the repulsive force of the magnetic force. It is also possible to obtain pressure, in which case an extremely small hysteresis torque can be obtained. It goes without saying that the shape of the magnet used is not limited to an annular shape. For example, they may be arranged intermittently on the same circumference. Further, as shown in FIGS. 11 and 12, for example, a bushing 39 made of a low-friction resin or the like is inserted between the side plate 7 and the hub 1 to reduce the friction between the side plate 7 and the hub 1. It is also possible to reduce the resistance.

[Brief explanation of the drawing]

1 and 4 are vertical cross-sectional partial views showing different conventional examples, FIGS. 2, 3, and 5 are graphs showing torsion torque-torsion angle characteristics of different conventional examples, respectively. The figure is a vertical cross-sectional partial view of the damper take assembly according to the present invention, Figures 7 and 8 are graphs showing the torsion torque-torsion angle characteristics when the embodiment of Figure 6 is adopted, and Figure 9 is a separate graph. FIG. 10 is a graph showing the torsion torque-torsion angle characteristics of the embodiment shown in FIG. 9, FIG. 11 is a longitudinal section partial view of yet another embodiment, and FIG. Figure 11 XII-XII
FIG. 1...Hub, 3...Annular flange, 6, 7, 15, 16...Side plate,
12... Torsion spring, 31, 32, 3
3, 34, 35, 36, 37, 38... magnet.

Claims (1)

[Scope of utility model registration request] A pair of integrally connected side plates that rotate relatively within a low torsion angle range are arranged on both sides of an annular flange formed integrally with the hub, and the side plates and the flange are elastically connected by a torsion spring. In the damper disk assembly which is connected to each other, magnets fixed to the side plate and the annular flange are attached to the inner periphery of the opposing surfaces of the side plate and the annular flange, respectively, so that the magnetic forces repel each other in the clutch axial direction. A damper disk assembly characterized by being arranged with a slight gap between them.