JPH0232905Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to an improvement of a torsional damper disk in which a belt is wound around a plurality of rollers to vary torsional torque.

(Prior art and its problems) As shown in FIG.
A roller 12 provided on the hub flange 10,
Roller 16 provided on disk plate 14
We have developed a torsional damper disk in which a belt 18 is wound around these rollers 12 and 16 to generate torsional torque between the hub flange 10 and the disk plate 14, and have already filed a patent application. No. 59-1056, filing date: January 1980
6th of the month).

However, with the above prior art, the increase in torsional torque in response to the increase in rotational speed is insufficient. Therefore, at low rotational speeds, a small torsional torque with a wide twisting angle is used to prevent rattle noise at idle, and at high rotational speeds, large torsional torque is prevented. There is a need for a damper disk that can effectively absorb torsional vibrations due to torque.

(Purpose of the invention) An object of the invention is to provide a torsion damper disk that can greatly vary the amount of torsional torque that can be absorbed in response to changes in rotational speed.

(Structure of the invention) (1) Technical means The present invention provides a damper disk in which a central hub having an outward flange rotatably supports a disk plate substantially perpendicular to the center line of the hub. and a plurality of locking portions are provided on one side of the disc plate so as to be movable in long holes formed in the radial direction of the damper disk, and a plurality of locking portions are provided on the other of the flange and the disk plate between the locking portions in the circumferential direction of the disk. A flexible member is provided between each locking portion, and the pressing portion is brought into pressure contact with the flexible member between the locking portions,
The pressing part is provided with a friction member for generating hysteresis torque, and the tension of the flexible member is increased at high rotation speeds by movement of the locking part along the long hole due to changes in centrifugal force. It is a torsional damper disk.

(2) Effect During high rotation, centrifugal force moves the locking part along the long hole, increasing the tension of the flexible member and increasing the torsional torque that can be absorbed.

(Embodiment) FIG. 1 is a schematic front view showing a case where a damper disk according to the present invention is adopted as a clutch disk for an automobile. The central hub 20 has a spring 22 on its inner peripheral surface for fitting to the output shaft.
A flange 24 radially protrudes in three directions on the outer peripheral surface.
are integrally formed.

As shown in FIG. 2, the flanges 24 are provided in three sets, two at a time, facing each other at intervals in the direction of the disk center line 01-01. A pin 2 parallel to the center line 01-01 is provided between each set of flanges 24.
6 is installed, and the pin 26 is fixed to the flange 24 in a non-rotating state. A roller 30 (pressing portion) is rotatably fitted to the outer periphery of the pin 26 via a friction member 28 .

The friction member 28 is a cylindrical member made of, for example, rubber, and is designed to generate a predetermined amount of friction force when the roller 30 rotates, thereby producing hysteresis torque.

A disk plate 32 parallel to the flange 24 is rotatably fitted and supported on the outer peripheral surface of the hub 20, and a clutch plate 34 and a retaining plate 36, which constitute the disk plate 32, sandwich the flange 24 from both sides. They are facing each other. The clutch plate 34 and retaining plate 36 are integrally connected by a pin 38 parallel to the center line 01-01. Both ends of the pin 38 are connected to the clutch plate 34 and the retaining plate 3.
It is slidably fitted into an elongated hole 40 bored to a predetermined length in the radial direction of 6. A roller 42 (locking portion) is rotatably fitted into the center portion of the pin 38 in the width direction, and a spacer 44 is interposed between the roller 42, the clutch plate 34, and the retaining plate 36. .

The inner circumferential portion of a radially projecting cushioning plate 46 is fixed to the outer circumferential portion of the retaining plate 36, and facings 48 are fixed to both ends of the cushioning plate 46.

As shown in FIG. 1, three pins 38 are provided on the same circumference at equal intervals, and accordingly, three elongated holes 40 and three rollers 42 are also provided. The inner peripheral surface of an annular steel belt 50 (flexible member) is wound around each roller 42, and the outer peripheral surface of the steel belt 50 is pressed by the roller 30 between each roller 42, and the hub 20 It is held in a bent position towards the

As shown in FIG. 3, the steel belt 50 employs an annular belt-like member in which thin wires are combined in a braided manner as a core material 52.
Both sides are molded with elastic bodies 54, 56 (for example, rubber). For example, the thickness of the core material 52 is 0.6 mm.
The overall thickness of the steel belt 50 is approximately 5.
It is about mm. Therefore, the steel belt 50 is flexible and has an elastic surface.

Next, the effect will be explained. Since the torsion between the disk plate 32 and the hub 20 is relative, for convenience of explanation it is assumed that the disk plate 32 is fixed and the hub 20 receives torsional torque in the X1 direction.

FIG. 1 shows a neutral state, in which the tension of the steel belt 50 is at its lowest, that is, the roller 30 is placed at the center of each roller 42 in the circumferential direction of the disc, and the state is stable. . At low rotations when the hub 20 begins to twist in the X1 direction relative to the disk plate 32,
The roller 30 rolls on the outer peripheral surface of the steel belt 50 in the X1 direction. Roller 30 is roller 4
2, the steel belt 50 comes to be strongly pressed, and the elastic bodies 54, 56 (FIG. 3) of the steel belt 50 are compressed accordingly.

When the roller 30 reaches the position indicated by the imaginary line 30a in FIG. 1 and comes into contact with the roller 42 via the steel belt 50, the twisting will no longer proceed.
The twist angle θ1 at this time corresponds to the maximum twist angle. Steel belt 50 if the torsional torque is resolved
The roller 30 is twisted to the neutral position by the elasticity of the roller 30, but in this process, a hysteresis torque is generated due to the frictional force generated in the friction member 28, and vibration energy is absorbed.

The same operation occurs when the hub 20 is twisted in the reverse X1 direction, and the time when the roller 30 comes to the position of the imaginary line 30b corresponds to the maximum twisting angle (-θ1: not shown). Regarding the above-mentioned operation, if the relationship between the above-mentioned torsion angle θ and torsion torque T is plotted as a graph, it will be as shown in A in FIG. 4 (the hysteresis torque is not shown).

When the disk is rotating at high speed, the first
Since the roller 42 shown in the figure is moved over a relatively long range by centrifugal force toward the outer circumference of the disk along the elongated hole 40, the tension of the steel belt 50 is significantly increased compared to the conventional case. As a result, the value of torsional torque T with respect to torsion angle θ becomes larger than that at low speed rotation,
For example, the characteristics shown in B in FIG. 4 are obtained.

These A and B exhibit a gentle inclination in a range of a larger twist angle θ compared to conventional A1 and B1,
It gently absorbs small vibrations at low rotations, and uses strong torsional rigidity to absorb large vibrations at high rotations.

(Effects of the invention) As explained above, in the torsion damper disk according to the invention, the pin 38 of the roller 42 is connected to the long hole 40.
As shown in FIG. 4, it is possible to obtain a wider torsion angle characteristic than in the past, as shown in FIG. Moreover, characteristics A and B are different from those of conventional A.
1. Compared to B1, it shows a gentle slope in the range of larger torsion angle θ, and the torsion torque T at low rotation
It is possible to absorb vibrations with a small amount and a large amplitude with ease, and at the same time, the torsional torque T at high rotation is large and vibrations with a small amplitude can be absorbed with strong torsional rigidity.

Furthermore, since the torsional torque T changes progressively as the torsional angle θ increases, the torsional vibration absorbing ability is excellent.

(Another embodiment) (1) As shown in FIG. 5 and FIG. 5a, the roller 3
0 can be provided on the disk plate 32 side, and the roller 42 can be provided on the flange 24 on the hub 20 side. In this case, a long hole 40 is formed in the flange 24, and a friction member 28 is provided in the roller 42.

(2) Instead of setting the maximum twisting angle by bringing the rollers 30 and 42 into contact with each other, a stopper mechanism for limiting the twisting of the disk may be provided separately.

(3) By arranging the roller 30 on the inner circumferential side than the roller 42, it is possible to avoid contact between the roller 30 and the roller 42 and further increase the maximum twisting angle.

(4) The core material of the steel belt 50 may be a thin plate or a wire. Further, the steel belt 50 does not have to be annular, and the steel belt 50 may be fixed between the locking parts.

(5) Although the flange 24 also serves to prevent the steel belt 50 from coming off, grooves may be formed on the rollers 30 and 42 to sandwich the steel belt 50 therebetween. Also steel belt 50
If a wire is used as the roller, an annular groove may be formed in the rollers 30 and 42.

(6) The flange 24 may be formed into a disk shape.

(7) The locking portion and the pressing portion do not need to be formed in the shape of a roller, and may simply be provided with a protrusion or a pin, for example.

(8) A friction damper may be provided between the clutch plate 34, retaining plate 36, and flange 24.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional front view of a damper disk according to the present invention, and FIGS. 2 and 3 are respectively -
4 is a graph showing torsion angle-torsion torque characteristics; FIG. 5 is a longitudinal sectional front view of a damper disk showing another embodiment;
Figure a is a sectional view taken along the line a-a in Figure 5, and Figure 6 is a partial longitudinal sectional view showing a conventional example. 20...Hub, 24
... flange, 28 ... friction member, 30 ... roller, 32 ... disk plate, 40 ... long hole, 50 ... steel belt.

Claims (1)

[Scope of utility model registration request] In a damper disk in which a disk plate substantially perpendicular to the center line of the hub is rotatably supported on a central hub having an outward flange, a plurality of locking portions are provided on one of the flange and the disk plate, and the damper A pressing part is provided in the elongated hole formed in the radial direction of the disk so as to be freely movable, and a pressing part is provided on the other of the flange and the disc plate to be disposed between the locking parts in the circumferential direction of the disk. A flexible member is hung between the locking parts, and a pressing part is brought into pressure contact with the flexible member between the locking parts, and a friction member for generating hysteresis torque is provided on the pressing part, so that the locking part along the elongated hole is caused by a change in centrifugal force. A torsion damper disk characterized in that the tension of the flexible member is increased at high rotation speeds by the movement of the disk.