JPS63289327A - Torsional vibration damping apparatus - Google Patents

Abstract

PURPOSE:To make the title damping apparatus exhibit an effective damping action by obtaining multistage elasticity in such a manner that a variation of dimensions is given to respective dimensions in the circumferential direction of windows including at least two windows provided on the plate portion of a hub, and the windows provided on a driving plate facing thereto. CONSTITUTION:Out of windows 19, 21 formed on the plate portion 3 of a hub 1, the dimension of the window 21 for accommodating the third compression spring 7 is larger in its circumferential direction than of the window 20 formed on a driving plate 4a, 4b facing thereto. However, the dimension of the window for accommodating the second compression spring 6 is smaller in circumferential direction than that of the window 18 formed on the driving plate 4a, 5b facing thereto. Consequently, the strength of the plate portion 3 of the hub 1 can be secured and for each of compression springs 5, 6, 7, any spring with large deflection length can be employed. Thereby, torsional characteristics to be able to exhibit an effective damping action can be obtained in the whole range of the input torque.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a torsional vibration damping device used in a clutch disk or the like constituting a power transmission device of an automobile.

Conventional technology A torsional vibration damping device for a clutch disc consists of a compression spring acting in an arc shape and a friction damping means as main elements, and effectively absorbs torsional vibration caused by torque fluctuations of an engine, etc., and improves the power transmission system. To prevent undesirable vibrations or noise from occurring. In recent years, torsional vibration damping devices for clutch discs have been designed to provide excellent vibration absorption and damping ability and to achieve sufficient torque transmission. It has been proposed that the torque can be sufficiently transmitted with high torsional rigidity for a large input torque fluctuation range, and that the damping capacity of the friction means can be changed according to the input torque (for example, in Japanese Patent Application Laid-Open No. Showa 59
(Refer to Publication No. 1816).

Such a torsional vibration damping device is constructed as shown in FIG. 4 in order to change the torsional characteristics in three stages (see FIG. 3) depending on the magnitude of input torque. That is, the first compression spring 35 acting in the first stage I
The window 4 of the drive plate 39 is formed with the same dimensions in the circumferential direction corresponding to the window of the plate portion 37.
0 and are accommodated in each window without any play in the circumferential direction. Then, the second compression spring 41 that acts in the second stage ■
is accommodated in the window c formed in the drive plate 39 without a gap in the circumferential direction, but in the window 43 formed in the plate portion 37 of the hub 36 corresponding to this window 42, the circumferential The first compression spring 35 is accommodated with a desired gap in the direction so that it acts with a delay with respect to the first compression spring 35. Next, a third compression spring 44 acting in the third stage m is formed in the drive plate 39 and a second compression spring 44 is formed in the upper window 45.
1, the second compression spring 41 and the second compression spring are housed in the window 46 formed in the plate portion 37 of the knob 36 corresponding to this window opening. 41
The second compression spring 41 is accommodated with a larger gap in the circumferential direction than the window 43 that accommodates the second compression spring 41.

Problems to be Solved by the Invention As described above, the second compression spring 41 and the third compression spring 44
Six windows 43 and 46 are provided in the plate portion 37 of the hub 36 to accommodate the second compression spring 41 or the third compression spring 44, respectively, in order to accommodate the second compression spring 41 or the third compression spring 44 with a desired gap in the circumferential direction. The six windows 43.46 are formed to have a larger dimension in the circumferential direction than the six windows 42.45 of the drive plate 39, which correspond to the six windows 43.46. Therefore, if we try to give each spring a long deflection amplitude in order to obtain an excellent vibration absorption and damping effect, especially if the intervals between the six windows 38, 43, and 46 formed in the plate part 37 are narrow, This causes a problem that the mechanical strength becomes weak.

Therefore, it is an object of the present invention to provide a torsional vibration damping device that can eliminate the problems of the prior art.

Means for Solving the Problems The alternative vibration damping device of the present invention achieves the above objects by:
A nose having a plate portion and a pair of drive plates facing each other on both sides of the plate portion of the knob are elastically engaged for relative rotation by compression springs each housed in a plurality of windows formed therein. The above-mentioned
It is possible to obtain multi-stage elasticity by giving a desired difference in circumferential dimension between at least two of the windows provided in the plate portion of the drive plate and a corresponding window not provided in the drive plate. wherein one of the at least two windows provided in the plate portion has a circumferential dimension larger than that of the window of the drive plate formed corresponding to the window. The other window provided in the plate portion is formed to be shorter in the circumferential direction than the window of the drive plate formed corresponding to this window by a desired dimension.

The rotational drive torque input from the operating drive plate causes relative rotation between the hub and the drive plate, and is accommodated in the window formed at the position corresponding to the plate portion of the knob 1 and the drive plate portion. The vibration is output to the hub while being subjected to a stepwise vibration absorption effect by the compression spring. At this time, the circumferential dimension of the six windows housing each compression spring is
A large amount of mechanical strength can be secured without reducing the mechanical strength of the knob, and each compression spring housed in these windows has a longer deflection length than the conventional example, so the entire torsional vibration damping device is longer. The deflection amplitude provides effective vibration absorption over the entire input torque range.

Example Embodiments of the present invention will be described in detail below with reference to the drawings.

Figures 1 and 2 are drawings showing a clutch disc to which the torsional vibration damping device of the present invention is applied. A spline S for connecting to the shaft is carved. Reference numerals 4a and 4b denote a pair of drive plates disposed facing each other on both sides of the plate portion 30 of the hub 1, and these drive plates J an 4 b and the plate portion 3 of the hub 1 are provided with multi-stage elasticity so that they can rotate relative to each other. For the connection, a plurality of windows can be formed in corresponding positions, in which compression springs 5.6.7 are arranged. 8a,
Reference numeral 8b denotes a pair of sub-plates arranged on both sides of the plate portion 30, and the inner peripheral ends of the sub-plates 8a and sb are rotatably fitted onto the outer periphery of the boss portion 2 of the hub 1, and the outer peripheral ends are fitted with a stopper. They are interconnected and fixed by bins 9. A first friction means 10 is disposed between these sub-plates 8IIL, 8'b and the plate portion 3 of the hub 1, and a second friction means 11 is disposed between the drive plates 4a, 4b. It is set up. Here, 12 is a substantially dish-shaped first spring member, and this first spring member 12 is attached to the nose 1.
A sub-play (8a) disposed on one side of the plate portion 3 of
sb, and the first
A desired spring force is applied to the friction means 10. Also, 1
4 is a second spring member, and this second spring member 14 has a substantially dish shape like the first spring member 12, is arranged adjacent to the inside of the drive plates 4a and 4b, and is connected to the retainer 15.
A desired spring force is applied to the second friction means 11 via.

Here, the compression spring indicated by reference numeral 5 is the first compression spring that acts in the first stage I to the second stage ■ of the multi-stage torsion characteristic shown in FIG. 8b
It is accommodated without any play in the circumferential direction in the window 16 formed in the plate part 3 of the knob 1 and in the window 17 formed in the plate part 3 of the knob 1, preferably with the desired compressive load. And 6 is the second
Due to the second compression spring acting from stage (2) to third stage (m), this second compression spring 6 is formed in the drive plates 4a, 4b and the window 18 formed in the plate part 3 corresponds to the second compression spring 6. It is housed within 19. Among these windows, the window 19 formed in the plate portion 3 is a drive plate) 4a,
The second compression spring 6 is formed to have a smaller size in the circumferential direction than the window 18 formed in the drive plate 4b, and is therefore engaged with the circumferential direction of the window 19 of the plate portion 3 without any play. , 4b with an angle of play of 01 in one direction of relative rotation. Reference numeral 7 denotes a third compression spring that acts from the first stage I to the third stage m, and this third compression spring 7 acts in the circumferential direction of the window 20 formed in the drive plates 4a, 4b and correspondingly. The sub-plate 8a is formed in the plate portion 3 of the hub 1 and accommodated in the upper window 21, and has larger dimensions than the sub-plate 8a.
A notch is formed at the outer circumferential end of 8b and is elastically engaged with the circumferential groove 22. The difference in the circumferential dimensions of these windows 20° and 21 is larger than the difference in the dimensions of the windows 18 and 19 in which the second compression spring 6 acting in the second stage is accommodated, and the window 20 can be maintained without play in the circumferential direction. The combined third compression spring 7 can be secured to the window 21 with an angle of play θ2 greater than θ1. The window 19 formed in the plate portion 3 of the hub 1 in this way
．． Among the windows 21, the window 21 that accommodates the third compression spring 7 is correspondingly formed to have a larger circumferential dimension than the window 20 formed in the drive plate 4ae4b.
The window 19 accommodating the second compression spring 6 is correspondingly smaller in circumferential dimension than the window 18 formed in the drive plates 4a, 4b.

Therefore, sufficient strength of the plate portion 30 of the hub 1 is ensured, and each compression spring 5, 6, 7 can have a long deflection length, thereby achieving an effective vibration absorption effect over the entire input torque range. It is possible to obtain torsional characteristics that can be exhibited.

Reference numerals 23 and 24 denote circumferential grooves formed at the inner circumferential ends of the windows 19 and 21 of the plate portion 3 of the hub 1, and the stop pins 9 are inserted into the circumferential grooves 23 and 24 in one direction of relative rotation. It is an engaging type with a play angle of 0.02.

Note that 25 is a stop pin that connects and fixes the drive plates 4a and 4b disposed on both sides of the plate portion 30 of the hub 1, and this stop pin 25 has a notch in the outer peripheral end of the plate portion 3 of the hub 1. 0 in the formed circumferential groove 26
They are engaged with a play angle θ3 larger than 2.

n is a friction plate, and this friction plate n is connected to the drive plate 4a via a cushioning plate 28.

According to the above embodiment structure, when engine torque is transmitted to the clutch disc, the drive plates 4a and 4b rotate together with the friction plate 27, so that the first to third compression springs are rotated.
The compression springs 5, 6, 7 are compressed in sequence and the torque is applied to the hub 1.
transmitted to. At this time, drive plate 4 a +
When 4b rotates, first the drive plate 4a
, 4b and the sub-plates 8a, 8b are integrally connected via the third compression spring 7, which has a larger spring constant than the first compression spring 5, so the sub-plates 8a, 8b also act as drive brakes 4a, The third compression spring 7 and the first compression spring 5 act in series via the sub-plates 8a and 8b, and at the same time, the plate portion 3 of the hub 1 rotates integrally with the rotation of the hub 4b. and the sub-plates 8a, 8b, and a first friction means (low friction means) 10 interposed between them acts to generate a friction torque Fl,
The torsional characteristics of the first stage I shown in FIG. 3 are obtained. next,
When the drive plates 4a, 4b rotate by a predetermined angle 01, the second compression spring 6
8.18 and acts in parallel on the spring group consisting of the third compression spring 7 and the first compression spring 5. At this time, the sub-plates 8a and sb still rotate together with the drive plates 4a and 4b, and the first friction means 10 acts, so that the torsional characteristics of the second stage (3) are obtained. Furthermore, a drive plate 4a.

4b rotates to a predetermined angle θ2, the third compression spring 7 comes into contact with the side edge of the window 21 of the plate portion 3 of the hub 1, and at the same time, the stop pin 9 that connects and fixes the sub-plates 8a and 8b to each other The plate portion 3 of the hub 1 is in contact with the side edges of the circumferential grooves 23 and 24 cut out in the inner peripheral end of the window 19, 21 of the plate portion 3 of the hub 1, and the relative rotation between the sub plates 8a and 8b and the plate portion 3 of the hub 1 is prevented. As a result, the sub-players 8a, 8'b and the plate portion 3 begin to rotate together. the result,
The action of the first compression spring 5 is stopped, and the second compression spring 6 and the third
The compression spring 7 cooperates and acts in parallel, and the second friction means (high friction means) 11 interposed between the drive plates 4a, 4b and the sub-plates 8a, 8b acts to generate a friction torque F2. , and the torsional characteristics of the third stage (3) are obtained. The vibration absorption and damping action in the third stage (3) is performed by rotating the drive plates 4a, 4b to a predetermined angle θ3,
The stop pin 9 contacts the circumferential groove 26 formed in the plate portion 3 of the hub 1 and the drive plate 4a.
, 4b continues until it stops.

Although this embodiment has been described using a clutch disk as an example, it is of course applicable to torsional vibration damping devices for various power transmission systems such as a lock-up piston of a torque converter. Furthermore, the present invention is not limited to those with three-stage torsional characteristics, but can also be applied to those with multi-stage torsional characteristics.

Effects of the Invention As described above, according to the present invention, one of the at least two windows formed in the plate portion for accommodating the compression spring has a drive formed in correspondence with the window. The window of the plate is longer than the window of the plate by a desired dimension in the circumferential direction, and the other window of the at least two windows formed in the plate part is longer than the window of the drive plate formed corresponding to this window. Since it is formed so that the circumferential dimension is shorter than the window by the desired dimension, the deflection length of each compression spring can be made sufficiently long without impairing the strength of the plate portion of the hub. This makes it possible to obtain torsional characteristics that can exhibit an effective vibration absorption effect over the entire input torque range.

[Brief explanation of drawings]

Fig. 1 is a front view of a torsional vibration damping device showing an embodiment of the present invention, Fig. 2 is a sectional view taken along line A-A in Fig. 1, Fig. 3 is a torsion angle-torsion torque diagram, and Fig. 4 is a front view of a conventional torsional vibration damping device. 1...Hub, 3...Plate part, 4a+4ba・
・・Drive plate, 5, 6.7 ・・Compression spring, 1
6.17.18.19.20.21 @...window. 2 other people Figure 2 Makoto angle (e) □

Claims (1)

[Claims] A hub having a plate portion and a pair of drive plates facing each other on both sides of the plate portion of the hub are elastically engaged for relative rotation by compression springs each housed in a plurality of windows formed therein. At least two of the windows provided in the plate portion of the hub and the corresponding windows provided in the drive plate are provided with a desired difference in circumferential dimension to provide multi-stage elasticity. A torsional vibration damping device that makes it possible to obtain a torsional vibration damping device, wherein one of at least two windows provided in the plate portion of the hub is a window of a drive plate formed corresponding to the window. The other window provided in the plate portion is formed to be longer in the circumferential direction by a desired dimension than the window of the drive plate formed corresponding to this window. A torsional vibration damping device characterized by being formed to have a short length.