JPS6347525A - Torsional vibration damping device - Google Patents

Abstract

PURPOSE:To increase the housing space of a first and a second friction means leading to increase in the friction areas of said friction means and stabilize a friction damping performance by connecting a pair of sub-plates to each other by means of a claw which extends from one of them to the other. CONSTITUTION:When the torque of an engine is transmitted to a clutch disk, a low friction means 27a is operated generating a friction torque F1 and a friction damping action of a first stage I is carried out and, when drive plates 4a, 4b are rotated by a defined angle theta1, a friction damping action of a second stage II is carried out. Then, as the plates 4a, 4b are further rotated up to a defined angle theta2, a high friction means 27b is operated to carry out a friction damping action of a third stage III. Since sub-plates 14a, 14b are connected to each other and stopped by means of a claw 16 securing a sufficient housing space for the low friction means 27a and the high friction means 27b, the friction areas of the friction means 27a and 27b can be increased, improving durability while effecting stable friction damping action for a long time.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to torsional deviation #1 which is conveniently used in clutch discs and the like constituting power transmission devices of automobiles. Regarding the sad device.

Conventional clutch disk torsion damping devices are mainly composed of a compression spring that acts in an arc shape and a damping means, which effectively absorbs the torque caused by torque fluctuations of an engine, etc., and reduces the power. To prevent undesirable excitement or noise from occurring in a transmission system. This clutch disc twist S! In recent years, e-reducing devices have been developed in order to exhibit excellent mental suction reduction ability and to achieve sufficient torque transmission.
For small input torque fluctuation ranges, low torsional rigidity increases the moisture absorption effect of torque fluctuations, and for large input torque fluctuation ranges, high torsional rigidity enables sufficient torque transmission, and the damping ability of the friction means can be reduced manually. There have been proposals that can change the torque according to the torque (for example,
19-1816).

As shown in FIG. 4 and FIG.
10 The sub-plates 52 and 53 that determine the start of action are interconnected by a connecting rivet 57 that passes through a notched groove 56 provided in the plate portion 55 of the hub 54, and the body of this connecting rivet 57 has a notched portion. 56, the sub-plate 52.33 begins to rotate together with the hub 54, and the action of the JIIl rubbing means 31 is started.

Problem to be Solved by the Invention Since the sub-brakes 52 and 53 are connected to each other by connecting rivets having a considerable diameter, the radial space for accommodating the friction means is limited to a small extent. As a result, the friction area of the friction means becomes smaller, and this wears out quickly, resulting in a stable J1 for a long time! There were times when it was difficult to acquire the ability to dampen the wind.

SUMMARY OF THE INVENTION Therefore, the present invention provides a torsional agitation damping device which improves the durability of the friction means and makes it possible to obtain stable friction over a long period of time.

Ninth means to solve problem Y: A first friction means and a second friction means are interposed between the relatively rotatable drive plate and the plate portion of the hub, and these @1 friction means and the second friction means are interposed between the relatively rotatable drive plate and the plate portion of the hub. During the initial stage of the relative rotation between the hub and the drive plate, either one of the hub and the drive plate is engaged, and the hub and the drive plate rotate relative to the other, and at the final stage, either one of the hub and the drive plate is engaged with the other. s
It can be engaged with one side and rotated relative to the other, making it one Jl! A sub-plate that determines the action of the rubbing means is interposed, and these sub-plates are connected to each other by claws extending from one sub-plate to the other. This is the composition.

The rotational drive torque input from the drive plate causes a relative rotation between the hub and the drive plate, and the vibration is damped in stages by compression springs formed at corresponding positions on the hub rib plate and the drive plate. A hub trap is output.

At this time, due to the relative rotation between the hub and the drive plate, the first friction means and the second friction means σ] provided between the hub and the drive plate are activated at the initial stage of the relative rotation between the hub and the drive plate. In the stage, the sub-plate engages either the hub or the drive plate and rotates relative to the other, and in the final stage, the sub-plate engages with either the other and rotates relative to the other. It is controlled and controls torque transmission while exerting nine intake sensation damping functions according to the magnitude of input torque. Since the sub-plates have claws and are connected to each other, the storage space for each friction means is large, the friction area Z is large, and a stable friction damping ability can be ensured over a long period of time.

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

Figures 1 to 4 are drawings showing a clutch disc to which the torsion sluggishness device of the invention is applied. A companion σ spline S connected to the output shaft is engraved. 4a, 4b)! With drive plates facing each other on both sides of the hub 1 rib plate section 30, these drive plates 4!1.41) and the hub IC1) plate section 3 are connected to &! , these have multi-stage elasticity and are connected so that they can be rotated relative to each other, and there are multiple windows at corresponding positions! It is formed and arranged to accommodate compression springs 5, 6, and 7g. Here,
The specific compression spring indicated by reference numeral 5 is an 18E compression spring that acts at the first stage of the multi-stage torsion characteristic shown in FIG. The hub 1 is formed in the rectangular portion 3 and accommodated within the window 9 without any play and preferably with a desired compressive load t.

6 is a compression spring that acts in the second stage.
A second compression spring 6 is formed on the plate portion 3 and housed in the window 11 corresponding to the window holes 0 and 4 formed on the drive plates 4a and 4b. Of these windows, the windows 10 formed in the drive plates 4a and 4b are smaller in size in the circumferential direction than the windows 11 formed in the plate portion 3.

The second compression spring 6 that is engaged with the window 10 of the plate portion 3 without any play is θ, σ in one direction of relative rotation with respect to the ridge 11 of the plate portion 3.
Engage with an angle of play. F is a compression spring that acts in the third stage (■), and this compression spring 7 is attached to the drive plate 4a.
, 4b are formed in the plate portion 3 of the hub 1 having a dimension t larger than the circumferential dimension of n, and are accommodated in nine windows 13 degrees Celsius. These windows 12
．． The dimensional difference in the circumferential direction of 13 is larger than the dimensional difference of the compression spring 6Y housed in 7LLiO2110 acting in the second stage, and the third king compression spring 7, which is secured to the window 12 without any play, is
With respect to θ, the play angle d is greater than θ! t is also Kaisocho Ryu.

14a, 14b&'! With the sub-plates, insert the space between these sub-plates 14a, 14b and the hub lO) plate part 3! 27ag pitching, drive play)
A second friction means 27b is disposed between 4a and 4b. Here, the sub-plate 14a disposed between the hub plate part 3 and one of the drive plates 4a has its inner peripheral end externally fitted onto the boss part 2 via the bearing member J, and its outer peripheral end in the radial direction. Ninety-two-pronged fork portion 1 extending outward
5 is elastically engaged with the third compression spring 7, and the nine sub-brakes (14t) are disposed between the hub plate portion 3 and the other drive plate 4b, and the nine sub-brakes (14t) are attached to one sub-brake (14a) at the outer peripheral end. A plurality of claws 16 extending in the direction direction are bent, and a notch is formed in the inner peripheral end of the winter melon 16Y to accommodate the second compression spring 6 of the plate portion 3 of the hub 1. It is inserted into the circumference monument 17, which is cut out at the inner peripheral end of the window 13 that houses the three king compression springs 7, with a desired angle of play. An engaging protrusion m18 is notched at the tip of the claw 16CIJ, and the engagement protrusion m18 abuts against the side surface of the stepped portion 19'g of the molded base of the retaining protrusion 18 and the side surface of the sub-plate 14a. Division 18 Sub-play on one side) 1
4a is engaged with the engagement groove 20 of n, thereby interconnecting the sub-plays 14a and 14b. 21
．． 22 is a disc spring, and so on +J tenner plate 23
, 24Y via the first and second friction means 27a, 27e>
Gives a pressing spring force to.

In this case, by selecting the degree of engagement of the claws 16 that connect the sub-plays 14a and 14b with each other, the 'Jl'al between both sub-plays) 14a and 14b is adjusted.
It is possible to keep the spacing constant so that the spring forces of both disc springs 21 and 22 do not interfere with each other, or to have both spring forces act in series on R27a and 27b during each friction. In addition, 26 is a stop pin that connects and fixes the drive plates on both sides, and 28 is a friction plate fixed to the cushioning brake 29 and the drive plate 4a.

According to the structure of the above Ct) embodiment, when the engine torque is transmitted to the clutch disk, the drive plates 4a, 4b rotate together with the friction plate 28, so that the first to third compression springs 5, 8, . ? is compressed to the 111st order, and the torque is the hub 1
transmitted to. At this time, drive plates 4a, 4b
When rotates, the first compression spring 5 acts, and at the same time, the sub-plates 14a and 14b also drive play) 4a
, 4b, a relative rotation occurs between the hub plate portion 3 and the sub-plates 14a and 14b, and the low friction means 2f♂ interposed between them acts to increase the friction torque. Fs Y is generated, and the @1 stage 1 operation shown in FIG. 5 is performed. When the drive play) 4a, 4b rotates by a predetermined angle 01, the second compression spring 6 acts in cooperation with the first compression spring 5.

At this time, the first friction means (low friction means) 27a still acts to perform the second stage friction S damping action 7.

When the drive plates 4a, 4b further rotate to a predetermined angle of 0°, the third compression spring 7 comes into contact with the opening edge of the window 13 of the hub 1σ] plate portion 3 and exerts a spring action. At the same time, the pawl 16 of the sub plate 14b releases the notch shape at the circumferential end of the window 12.
5 and prevents the relative rotation of the sub-plates 14a, 14b and the hub 1 lip (V-) part 3, so the sub-plates 14a, 14b and the plate part 3 rotate integrally. It starts. Just in case, drive play) 4a.

and 4b sub-play) 14a, 14b
Friction means C (high friction means) 27b acts to generate friction torque 1
1 is generated, and the friction damping effect of the third stage (3) is performed.

And stiff! The three-stage W1 friction damping effect is achieved by rotating the drive plates 4a and 4b to a predetermined angle tJ3, and the stop pin 26 coming into contact with the plate portion 3 of the knob 1, causing the hub 1 and drive plates 4a and 4b to rotate. This continues until the relative rotation of the two stops (see figure $5).

Here, hub 1 rib plate 3 car m resup plate 14
a, 14b are connected and locked to each other by thin plate-like claws 16 formed on the -10,000 sub-plate 14fi,
The first friction means (low friction means) 27Δ and the second friction means (
By ensuring sufficient storage space for the high friction means 27b, the friction area of the low friction means 27a and the high friction means 27F3 can be increased. The durability is improved, and the friction damping effect is stable over a long period of time. In this way, the initial torque of the engine is stably and smoothly transmitted to the transmission shaft (not shown) over a long period of time.

Note that in this embodiment, the claws 16 are formed on one sub-plate 14h, but this is limited to 4) ct), and it is also possible to form the claws 16 on the other sub-plate 14a. , and both sub-plates 14a.

14t) may be provided with claws 16χ.

Furthermore, although this embodiment has been described with reference to a clutch disc brake, it is of course applicable to various power transmission systems such as a torque converter relock-up piston (1) as a torsional motion reduction device.

Effects of the Invention By interconnecting the pair of sub-plates with claws extending from one sub-plate to the other, the accommodation space for the first stage and the second friction means can be enlarged. The friction surface of each friction means can be made very large. Therefore, since early wear of each friction means can be prevented, durability can be improved and a stable friction damping effect can be obtained over a long period of time, which has a great practical effect.

[Brief explanation of drawings]

FIG. 1 shows an embodiment of the present invention.
tQ) Cross-sectional view, Fig. 2 is a solitary view of section A in Fig. 1, Fig. 3 is a view taken in the direction of arrow B, Fig. 4 is a front view of the same, Fig. 5 is a friction angle-4 retorque characteristic diagram. , FIG. 6 is a front view showing the conventional example Y of 1 construction,
FIG. 7 is a sectional view taken along the line ■-■ in FIG. 6. ! ...Hub, 2...Boss part, 3.Hub rate W, 4
a. 4b... Drive plate, 5... Channel 1 compression spring,
6... wc2 compression spring, 7... third compression spring, 14
a, 14b...subplate, 16...claw, 2
7a...First friction means, 27t)...Second M gravel means. 2 people Figure 1 Figure 2 Figure 7

Claims (2)

[Claims] (1) A hub having a plate portion and a pair of drive plates facing each other on both sides of the plate portion are coupled to each other so as to be elastically rotatable relative to each other by compression springs each housed in a plurality of windows formed therein. torsional vibration that makes it possible to obtain multistage elasticity by giving a desired difference in circumferential dimension between at least one of the windows provided on the hub and a corresponding window provided on the drive plate. The damping device includes a first friction means and a second friction means interposed between each drive plate and a plate portion of the hub, and further includes a hub between the first friction means and the second friction means. In the initial stage of the relative rotation between the hub and the drive plate, the hub and the drive plate engage one of them to rotate relative to the other, and in the final stage, the hub and the drive plate engage with the other and either one of them rotates relative to the other. A sub-plate is provided which is rotatable relative to the friction means and determines the start of action of one friction means, and the pair of sub-plates is connected by a claw piece extending from one sub-plate to the other sub-plate. A torsional vibration damping device characterized in that two parts are interconnected. (2) The sub-plate engages with the drive plate and rotates relative to the hub in the initial stage of relative rotation between the hub and drive plate, and engages with the hub in the final stage to rotate relative to the drive plate. Claim 1, which determines the start of action of the second friction means interposed between the sub-plate and the drive plate.
The torsional vibration damping device described in .