JPS6056939B2 - damper disk - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a damper disk suitable for installation in industrial applications, between an engine and a clutch in an automobile, or between an engine and a torque converter or other transmission. The purpose of this invention is to widen the range of low torsional angles and to exhibit sufficiently high torsional rigidity against impact torque.

Part of the objective is to be able to compactly accommodate a friction washer that provides high hysteresis. Conventionally, damper disks having a structure similar to clutch disks have been widely used.

That is, a plurality of rectangular window holes extending in the circumferential direction are formed in the hub plate, a coil spring (torsion spring) is fitted into each window hole with its center line facing in the circumferential direction, and the supporting surface of each coil spring end surface is The hub plate is sandwiched between a pair of retaining plates with One side is connected to the driving side member, and the other side is connected to the driven side member. However, as a design condition for coil springs, it is necessary to keep the deflection amount below a certain amount, so if coil springs are arranged on the same circumference as in the past, the necessary non-linear torsional characteristics cannot be obtained. This was extremely difficult.
In other words, when the springs are arranged on the same circumference, the soft torsional characteristic A
When trying to increase the torsion angle range L that provides the angle (FIG. 1), it is advantageous to make the effective radius of arranging the springs small, and the rigidity (gradient in FIG. 1) becomes low. In order to obtain the characteristics shown in FIG. 1A when the effective radius is large, it is necessary to make the spring longer, which causes problems such as the abdomen of the spring protruding outward due to centrifugal force. Also, the twist angle is large!
In order to obtain a stiff spring characteristic B, if the coil springs are arranged at a location with a small effective radius, springs with high rigidity will be required, making spring design difficult. Therefore, as shown in FIG. 1, a soft torsion characteristic A is provided in the wide torsion angle range L1, and the torsion angle is further increased! Even if a plurality of two types of coil springs with different torsional rigidities are arranged on the same circumference and the two types of coil springs are operated sequentially in a relay system in order to give the stiff spring characteristic B, the spring and The support members (retaining plate, hub plate, etc.) are unreasonable, and considering the required values of characteristics and durability, it is impossible to achieve this from a design standpoint. In the present invention, the hub plate is divided into two parts, the inner and outer parts, and these are arranged on the same plane, and a coil spring that provides hard torsional characteristics is installed in the window hole of the outer hub plate, and a coil spring that provides a soft torsional characteristic is installed in the window hole of the inner hub plate. The coil springs that provide the characteristics were fitted with their center lines facing in the circumferential direction, and both hub plates were sandwiched between a pair of retaining plates having support surfaces for the end faces of each coil, and fixed to both retaining plates. In the range L1 where the stop pin is inserted into the long hole in the circumferential direction of the inner hub plate and the torsion angle is low, the inner soft coil spring is bent and the torsion angle further increases! In this case, the outer hard coil spring is bent, and the non-linear characteristics A and B shown in FIG. 1 can be obtained by such a relay system. Examples are shown in FIGS. 2 and below.

Figure 2 is a partially cutaway front view, and Figure 3 is a partially cutaway front view.
In the ■-■ cross-sectional view of the figure, 12 in Figure 3 is the drive side member, 14
1 is a driven side member, and 15 is a damper disk according to the present invention.

The damper disk 15 is provided with annular hub plates 1 and 2 on the outside and inside, and the outside hub plate 1 is fastened to the protrusion 17 at the corresponding position of the movable side member 12 by a plurality of bolts 16 (see Fig. 4). ), the inner hub plate 2 is spline fitted to the driven member, and the tip of the member 14 (shaft) fits within the bearing 10 in the center of the member 12. Therefore, both the inner and outer hub plates 1 and 2 are concentric on the center line 0.
Both hub plates 1 and 2 are provided with a plurality of generally rectangular window holes 20 and 21 (FIG. 2) extending in the circumferential direction, and each window hole 20 is provided with a short torsion spring (coil spring) 5 with high rigidity. However, a long rigid torsion spring (coil spring) 6 is fitted into the window hole 21 with its center line facing in the circumferential direction. That is, both end surfaces 5a of the coil spring 5 are pressed against edges 20a at both circumferential ends of the window hole 20, and both end surfaces 6a of the torsion spring 6 are similarly pressed against edges 21a at both circumferential ends of the window hole 21. The retaining plates 3, 4, which sandwich both hub plates 1, 2 on both sides via annular friction washers 7, 7, have window holes 24, 25 into which torsion springs 5, 6 fit. The torsion spring end face 5a is provided with both retaining plates 3.
, 4 of the window hole 24 (FIG. 2), and the torsion spring end surface 6a is pressed against the edge 25a of the window hole 25.

Reference numeral 8 denotes a stop pin, which passes through a long hole 27 extending in the circumferential direction of the inner hub plate 2, and has small diameter portions at both ends fitted into the holes of the retaining plates 3 and 4, and then engaged on the outside thereof. By machining, the friction washers 7, 7 are pressed against the surfaces of both the inner and outer hub plates 1, 2.

The friction washers 7, 7 are annular bodies having the same shape that pass between the torsion springs 5, 6 as shown in FIG.
The stop pin 8 fits into the hole provided in the plurality of inward projecting portions 23a, and thereby both friction washers 7,
7 rotates together with both retaining plates 3 and 4.
Also, the friction washers 7 and 7 are attached to the outer hub plate 1.
The retaining plates 1 and 2 are pressed against the inner peripheral edge of the side surface of the inner hub plate 2 and the outer peripheral edge of the side surface of the inner hub plate 2, and apply a frictional force to both retaining plates 3 and 4 when the hub plates 1 and 2 rotate relative to each other. The stop pin 8 is moved from the center point in the longitudinal direction of the elongated hole 27 in the rotational direction (
When the outer hub plate 1 on the drive side rotates by an angle L1 (Fig. 1) in the direction of arrow D with respect to the inner hub plate 2 on the driven side, the stop pin 8 collides with the elongated hole tip 27a, and when rotated in the opposite direction by an angle L1, collides with the opposite tip 27b, playing the role of determining the torsional angle range (Ll, Ll'') that provides soft torsional characteristics. In FIG. 5, which shows the V-V cross section of FIG. Maintains the distance between retaining plates 3 and 4,
The central large diameter portion passes through a notch 28 in the outer hub plate 1.

Therefore, the outer hub plate 1 is connected to both retaining plates 3.
, 4 relative to the angle L2 or! The stop pin 9, which has rotated by '' (Fig. 1), abuts against the edge of the notch 28 and keeps the deflection of the torsion spring 5 below a certain amount. It is transmitted to the outer hub plate 1 through a plurality of bolts 16, and the edge 20a of the window hole 20 of the hub plate 1 connects both retaining plates 3 and 4 via the torsion spring 5 to the edge 24 of the window hole 24.
Both retaining plates 3 and 4 drive the inner hub plate 2 from the edge 25a of the inner window hole 25 via the torsion spring 6, and the rotational force of the inner hub plate 2 is generated by the spline. It is transmitted to the driven side member 14 through the.

Since the outer torsion spring 5 has a high rigidity, it deflects only a small amount in the torsion angle range L, and during that time, the inner torsion spring 6, which has a small rigidity, deflects exclusively, and the soft torsion characteristics shown in FIG. 1A are obtained. Stop pin 8 is at the end of the long hole 2
7a, the outer torsion spring 5 is deflected, and the angular range L2 until the stop pin 9 abuts against the edge of the notch 28 results in the hard torsion characteristics shown in FIG. 1B. As described above, according to the present invention, the hub plate is divided into two parts, the outer hub plate 1 and the inner hub plate 2, and the torsion spring 5 with high rigidity is installed in the window hole 20 of the outer hub plate 1. A torsion spring 6 with low rigidity is attached to the window hole 21 of the inner hub plate 2, and the stop pin 8 fixed to the retaining plates 3 and 4 is passed through the long hole 27 of the inner hub plate 2, so that the mounting position has a small effective radius. The soft torsion spring 6 allows a large torsion angle range Ll, Ll'' with soft torsion characteristics, and since the torsion spring 6 is mounted close to the center, the influence of centrifugal force is reduced.

Furthermore, since the effective mounting radius of the torsion spring 5 is large, a hard torsional characteristic B can be easily obtained without increasing the rigidity. The action of the stop pin 8 allows the deflection of the torsion spring 6 to be kept below a certain amount, and if the stop pin 9 is further provided, the deflection of the torsion spring 5 can also be kept below a certain amount. As described above, according to the present invention, the torsion springs 5, 6, the hub plates 1, 2, and the retaining plates 3, 4 supporting the torsion springs 5, 6 can have the desired torsional characteristics without being forced to do so.
It is possible to easily provide a damper disk having non-linear torsional characteristics with a wide angular range and particularly soft torsional characteristics. Further, according to the present invention, there is an advantage that the friction washer 7 which provides a large hysteresis can be housed in a compact manner. That is, the narrow annular friction washer 7 is applied using the inner peripheral surface of the side surface inside the window hole 20 of the outer hub plate 1 and the outer peripheral edge of the side surface outside the window hole 21 of the inner hub plate 2. Therefore, although the width of the friction washer 7 is narrow, a wide pressure contact surface can be secured, and a sufficiently large resistance can be provided during the relative rotation of the inner and outer hub plates 2 and 1. Moreover, since the surface pressure can be reduced, wear is also reduced. In addition, since the inward projecting portion 23a of the friction washer 7 is locked to the stop pin 8, the inward projecting portion 23a
is the adjacent window hole 21 of the inner hub plate 2 together with the elongated hole 27,
The friction washer 7 and the elongated hole 27 that determines the twisting angle L1 that provides soft torsional characteristics are fixed to both the retaining plates 3 and 4. The mechanism can be housed compactly, which has the advantage that the inner hub plate 2 is not bulky. That is, since the torsion spring 5 that provides hard torsional characteristics is supported by the outer hub plate 1, the adjacent window holes 21 of the inner hub plate 2,
This has the advantage that the elongated hole 27, the inward projecting portion 23a1 of the friction washer 7, the stop pin 8, etc. can be compactly incorporated between the holes 21 and 21. When embodying the present invention, the torsion springs 5 and 6 may be replaced by rubber springs, disc springs, or a combination thereof, instead of the coil springs shown.

[Brief explanation of the drawing]

Figure 1 is a graph showing the relationship between torsion torque and torsion angle.
Figure 2 is a partially cutaway front view, and Figure 3 is a partially cutaway front view.
4 is a cross-sectional view taken along the line ■-■ in FIG. 2, and FIG. 5 is a cross-sectional view taken along the line V--■ in FIG. 1, 2...Hub plate, 3, 4...
Retaining plate, 5, 6... Torsion spring, 8... Stop pin, 12...
・Drive side member, 14... Driven side member, 20, 2
1... Window hole, 24a, 25a... Edge of window hole, 27... Long hole.

Claims (1)

[Claims] 1 The inner and outer annular hub plates 2, 1 are disposed in the same plane and connected one to the driving side member 12 and the other to the driven side member 14, and each hub plate 2, 1 has a rectangular shape extending in the circumferential direction. A torsion spring 5 is provided with a plurality of window holes 21 and 20 to provide hard torsion characteristics to the window hole 20 of the outer hub plate 1, and a torsion spring provides soft torsion characteristics to the window hole 21 of the inner hub plate 2. 6 with their center lines facing in the circumferential direction, sandwich both hub plates 2 and 1 between a pair of retaining plates 3 and 4 that have support surfaces for the end faces of each torsion spring, and then The fixed stop pin 8 is inserted into the long hole 27 in the circumferential direction between adjacent window holes of the inner hub plate 2 to determine a twisting angle that provides soft torsional characteristics.
An annular friction washer 7 is provided with one side facing the outer peripheral edge of the side surface and the inner peripheral edge of the side surface of the outer hub plate 1, and the other side facing the retaining plate. A damper disk characterized in that a protrusion 23a is locked to a stopper 8.