JPH029208B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a damper disk used as a clutch disk for automobile clutches and the like.

As a damper disk of this type, the structure shown in FIG. 1 has already been proposed in order to increase the torsional angle and provide multi-stage torsional characteristics. In FIG. 1, a spline hub 1 and an annular flange 2 outside the spline hub 1 are separate bodies, and have a structure that allows them to be connected by radial claws 3 and 4. A pair of sub-plates 5 are arranged on both sides of the flange 2, and a pair of side plates (a clutch plate and a retaining plate) are provided on the outside of both sub-plates 5, although not shown. The sub-plate 5 is integrally connected to the flange 2 by a sub-pin 6, and is also connected to a weak torsion spring 9.
It is connected to the hub 1 via. The flange 2 is connected to the side plate via a strong torsion spring 8. According to this structure, while the transmitted torque is small (section O-a in FIG. 2), the spring 9 is compressed, the transmitted torque and the torsion angle reach the predetermined values T _a and θ _a , and the pawl 4 hits the pawl 3. After contact, the spring 8 is compressed, so the transmitted torque-torsion angle characteristic becomes as shown in FIG. 2, and the torque vibration absorption effect can be enhanced by increasing the characteristics and increasing the torsion angle. However, according to the above structure, when the claws 3 and 4 collide, there is a risk that an abnormal sound (so-called "clicking sound") may be generated. Furthermore, since the pawls 3 and 4 protrude in the radial direction from the outer peripheral edge of the hub 1 and the inner peripheral edge of the flange 2, respectively, there is a risk that the pawls 3 and 4 will be damaged in the event of a collision. If the gap S between the pawls 3 and 4 or the length of the window hole for the spring 9 in the hub 1 (initial length of the spring 9) are set large, there is a problem in that the strength of the pawls 3 and 4 is significantly reduced. .

In order to solve the above problems, the present invention integrates a hub and a flange, and configures each part so that the sub-plate is twisted relative to the hub flange while the twist angle is small.The present invention is constructed as follows. There is.

That is, in the present invention, a pair of side plates into which torque is introduced into the outer periphery are arranged on both sides of a hub flange integrally formed with a hub, and a pair of sub-plates are arranged between the hub flange and both side plates. , a sub-pin connecting both sub-plates is passed through a notch long in the circumferential direction of the hub flange, and a gap corresponding to the first torsion angle is provided between the sub-pin and the side edge of the notch in a non-twisted state. , a first torsion spring mechanism for connecting the sub-plate and the hub flange in the circumferential direction is accommodated in the window hole of the sub-plate and the hub flange, and a second torsion spring mechanism for connecting the side plate and the hub flange in the circumferential direction. A spring mechanism is housed in the window hole of the side plate, sub-plate, and hub flange, and in a non-twisted state, both ends of the first torsion spring mechanism are circularly attached to the side edges of the window hole of the sub-plate and hub flange in which the mechanism is housed. At the same time, both ends of the second torsion spring mechanism are engaged in the circumferential direction with the side edges of the window hole of the side plate and sub-plate in which the mechanism is accommodated, and the second torsion spring mechanism is engaged with the side edges of the window hole of the hub flange. The spring constant of the second torsion spring mechanism is set to be larger than the spring constant of the first torsion spring mechanism, and the second torsion spring mechanism is placed in a pre-compressed state. It is characterized by being incorporated into the above-mentioned window hole.

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

FIG. 3 is a partial vertical cross-sectional view of an embodiment of the present invention, and FIG. 4 is a partially cut-away partial cross-sectional view of FIG.
In FIG. 3, a spline hub 10 spline-fitted to an output shaft (not shown) is integrally provided with an annular hub flange 11 facing outward in the radial direction.
A pair of annular side plates 13 are provided on both sides of 1 with a sub-plate 12 in between. The left side plate 13 in FIG. 3 is a clutch plate, and a cushioning plate to which a friction facing is attached is fixed to the outer periphery (not shown). For example, three locations on the outer peripheries of both side plates 13, 13 are connected by stop pins 15 shown in FIG. The flange 11 and the sub-plate 12 are provided with circumferentially long notches 16 and 17 on the outer periphery through which the stop pin 15 passes.
There is a space between the side edges 19, 19' of the notch 16 and the stop pin 15 in the disk rotation direction R and in the opposite direction in the non-twisted state shown in FIG.

The illustrated disk is provided with a total of three second torsion spring mechanisms 22 on the inside of the stop pin 15 when viewed in the radial direction. Each spring mechanism 22 has a large diameter and a small diameter compression coil spring 24, 2 arranged concentrically.
Flange 1 with 5 extending in the disk circumferential direction.
1. Both sub-plates 12, both side plates 13
In the illustrated non-twisted state, both ends of the springs 24, 25 are inserted into the window holes 27, 28 of the sub-plate 12 and the side plate 13 via the spring receivers 32. side edge 3
0, 31, and gaps L, L' corresponding to the first torsion angles θ ₁ , θ' ₁ (FIG. 5), which will be described later, are made with respect to the side edges 29, 29' of the window hole 26 of the flange 11. Separated. The springs 24 and 25 are fitted into the window holes 27 and 28 in a pre-compressed state, and the pre-compression force in that case is the first torque T _{1 , T' 1} , T' ₁ in FIG.
That is, the transmission torques T ₁ and T' ₁ corresponding to the first torsion angles θ ₁ and θ' ₁ are taken into account and set as described later.

In FIG. 4, the adjacent second spring mechanism 22 (1
A first spring mechanism 21 is provided between the two (only one is shown). Each spring mechanism 21 has a window hole 35 provided in a portion near the outer periphery of the flange 11 and sub-plate 12;
36 (or notch) one compression coil spring 37
In the non-twisted state shown in the figure, both ends of the spring 37 are in contact with the side edges of the window holes 35 and 36. The spring 37 is the same as the springs 24 and 25.
window holes 35, 3 in an uncompressed state.
It is incorporated in 6. Also, as shown in FIG. 3, the side plate 13 does not have a window hole for the spring 37.
Spring 37 is oriented in the disk axis direction (horizontal direction in Figure 3)
It prevents you from moving to.

As shown in FIG. 4, the window hole 35 of the flange 11 extends further toward the center of the disk than the window hole 36 of the sub-plate 12, and the extension portion forms a notch 40 through which the sub-pin 41 passes. The sub-pin 41 integrally connects both sub-plates 12 as shown in FIG. 3, and in the non-twisted state as shown in FIG.
42' are separated by gaps l and l' corresponding to the first torsional angles θ ₁ and θ' ₁ .

As shown in FIG. 3, a wave spring 43 is interposed in a compressed state between the inner periphery of the sub-plate 12 and the flange 11, and an annular friction spring 43 is interposed between the inner periphery of the sub-plate 12 and the side plate 13. A washer 44 is interposed.

Explain the action. When a facing (not shown) comes into pressure contact with the engine flywheel, torque is transmitted to the side plate 13. When the torsional angle of the side plate 13 with respect to the flange 11 is less than a predetermined value θ ₁ (or θ′ ₁ : Fig. 5), the spring receiver 3
2 is not in contact with the window hole side edges 29, 29' of the flange 11, the torque is transferred from the side plate 13 to the springs 24, 25, the sub-plate 12, and the spring 37.
from the flange 11 to the hub 10 to the output shaft. In this operation, the sum of the precompression force of the springs 24 and 25 and the frictional force _of the friction washer ₄₄ shown in _FIG . ₁ , so springs 24 and 25 are not compressed (or hardly compressed) and spring 3
7 is compressed, resulting in side plate 13
and the sub-plate 12 are integrated to form the flange 11.
The transmission torque increases (O-
T ₁ , O−T′ ₁ ), the torsion angle increases significantly. (O-θ ₁ , O-θ′ ₁ ). Also, during this period, slipping occurs on the surface of the wave spring 43 shown in FIG. 3, and although not shown, a small hysteresis corresponding to this slipping results in the torsional characteristics (section O--) shown in FIG.
A, O-A').

The torsion angle and transmission torque are respectively predetermined values θ ₁ ,
When the sub-pin 41 increases to T ₁ (θ' ₁ , T' ₁ ), the sub-pin 41 touches the notch side edge 42 (or 42') of the hub flange 11.
Thereafter, the twisting of the sub-plate 12 with respect to the flange 11 and the compression operation of the spring 37 are stopped, and the side plate 13 is twisted with respect to the flange 11 and the sub-plate 12. On the other hand, when the torsion angle reaches the above-mentioned predetermined values θ ₁ and θ' ₁ , the spring receiver 32 moves toward the window hole side edge 29 (or 2
9'), and thereafter the torque is applied from the side plate 13 to the flange 1 via the springs 24 and 25.
1, and the springs 24 and 25 are compressed. As a result, the rate of increase in the torsion angle corresponding to the increase in torque becomes low, as shown in the section A-B (A'-B') in FIG. Also, during this operation, the friction washer 4 in Fig.
4, a large hysteresis (not shown) corresponding to the slip is added to the torsional characteristics (sections A-B, A'-B') of FIG. 5.

When the twist angle reaches the maximum value θ ₂ (or θ' ₂ ), the stop pin 15 shown in FIG. 4 comes into contact with the notched side edge 19 (or 19') of the flange 11, and further twisting is prevented.

As explained above, according to the present invention, a pair of side plates 13 into which torque is introduced into the outer circumference are arranged on both sides of the hub flange 11 formed integrally with the hub 10, and the hub flange 11 and both side plates 13 are A pair of sub-plates 12 are arranged between them,
A sub-pin 41 connecting both sub-plates 12 is passed through a notch 40 long in the circumferential direction of the hub flange 11, and a first torsion angle θ is formed between the sub-pin 41 and the notch side edges 42, 42' in a non-twisted state. ₁ , θ' ₁ are provided, and in the torsion region less than the first torsion angle, the sub-plate 12 and the hub flange 11 are connected by the first torsion spring mechanism 21 with a low spring constant, and the spring The sub-plate 12 and the side plate 1 are connected by the second torsion spring mechanism 22 with a high constant.
3 and the side plate 13 and hub flange 11 in the torsional region where the first torsional angle θ, θ _'
are connected by a second torsion spring mechanism 22. In this way, the hub 10 and flange 11 are integrated, and the sub-plate 12 and flange 11 are connected at the first torsion angle θ ₁ , θ' ₁ by the sub-pin 41 that connects both sub-plates 12 and the notch 40 of the hub flange 11 As a result, the strength of the connecting portion can be increased and the durability can be improved compared to the case where conventional claws 3 and 4 (FIG. 1) are used. Furthermore, even if the window holes 26, 35, etc. are lengthened in the circumferential direction, sufficient strength can be obtained for practical use, so the spring 2 is longer than the conventional one.
4, 25, and 37, the maximum torsion angles θ ₂ and θ′ ₂ can be set large, and the torque vibration absorption effect can be enhanced. Furthermore, since the impact caused by the collision between the sub-pin 41 and the notch side edge 42 can be alleviated by slight elastic deformation of the sub-plate 12, etc., the collision noise (clicking sound) can be reduced.
It can also be expected to have the effect of reducing

Note that when embodying the present invention, the notch 41 may be provided separately from the window hole 35.

[Brief explanation of drawings]

Figure 1 is a partially cutaway front partial view of the conventional example;
The figure is a graph showing the transmission torque per torsion angle characteristic of a conventional damper disk, Figure 3 is a partial cross-sectional view of the embodiment of the present invention, and Figure 4 is a partially cutaway view of Figure 3.
FIG. 5, a partial cross-sectional view, is a graph of the transmission torque per torsion angle characteristic of the damper disk according to the embodiment of the present invention. DESCRIPTION OF SYMBOLS 10...Hub, 11...Hub flange, 12...Sub plate, 13...Side plate, 21...First torsion spring mechanism, 22...Second torsion spring mechanism, 40...Notch, 41...Sub pin, 42, 42'...Notch Notched side edge.

Claims (1)

[Claims] 1 A pair of side plates to which torque is introduced to the outer periphery are placed on both sides of a hub flange formed integrally with the hub, a pair of sub-plates are placed between the hub flange and both side plates, and both sub-plates are placed between the hub flange and both side plates. Pass the sub-pin that connects the hub flange into a long notch in the circumferential direction of the hub flange, provide a gap corresponding to the first torsion angle between the sub-pin and the side edge of the notch in the non-twisted state, and connect the sub-plate. A first torsion spring mechanism for connecting the hub flange in the circumferential direction is accommodated in the window hole of the sub-plate and the hub flange, and a second torsion spring mechanism for connecting the side plate and the hub flange in the circumferential direction is housed in the window hole of the sub-plate and the hub flange. The first torsion spring mechanism is accommodated in the window holes of the plate, the sub-plate, and the hub flange, and in a non-twisted state, both ends of the first torsion spring mechanism are engaged in the circumferential direction with the side edges of the window holes of the sub-plate and hub flange in which the mechanism is accommodated. At the same time, both ends of the second torsion spring mechanism are engaged in the circumferential direction with the side edges of the window hole of the side plate and sub-plate in which the second torsion spring mechanism is accommodated, and are also engaged with the side edges of the window hole of the hub flange. The spring constant of the second torsion spring mechanism is set to be larger than the spring constant of the first torsion spring mechanism, and the second torsion spring mechanism is inserted into the window hole in a pre-compressed state. A damper disc characterized by being incorporated into.