JPS624929A - Damper disc - Google Patents

Abstract

PURPOSE:To enable production of high hysteresis torque, by a method wherein a friction member for production of a high friction force is placed between the outer peripheral part of a subplate and the subplate, and a subpin, having length long enough to press the subplate, is attached to a side plate. CONSTITUTION:A thin annular friction ring 40, suitable to generation of a high friction force, is adhered to the outer peripheral edge part of a subplate 10 positioned opposite to a clutch plate 3, serving as a side plate, and a retaining plate 4. The outer peripheries of the two subplates 10 are respectively coupled in a press manner to the clutch plate 3 and the retaining plate 4 through setting of the shape and length of a subpin 30, and a friction between the subplate 10, a friction washer 12, the clutch plate 3, and the retaining plate 4 is increased over that between each of the subplates 10, a wave spring 11, and a flange part 2. The friction ring 40 is located outside a stop pin 13. This enables the generation of high hysteresis torque.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an improvement of a damper disk called a silent disk.

(Prior art and its problems) Conventionally, this type of damper disk has the following characteristics, as shown in Fig. 6:
Relatively thin sub-plates 104 are provided on both sides of the flange portion 102 of the spline hub 100.Lead plates 106 are further provided at intervals on both sides of the sub-plate 104, and the flange portion 102 and the sub-plate 104 are provided with lead plates 106 at intervals.
A wave spring 108 is interposed between the sub plate 10/I, a frixine washer 110 is interposed on the inner circumference between the sub plate 10/I and the side plate 106,
1 sub plate 10 with sub pin 112 connecting 4
4 is pressed outward, and a friction washer 110 generates a frictional force, that is, hysteresis torque.

However, since the friction washer 110 is disposed on the inner periphery, there is a problem that 1) the side plate 106 bends outward due to its own elasticity, and the hysteresis 1 that occurs in the friction washer 110 is reduced. be.

(Objective of the Invention) An object of the present invention is to provide a damper disk including a sub-plate that can generate a large hysteresis of 1 to 100 kW.

(Structure of the Invention) (1) Technical Means The present invention provides a damper disk in which a rib plate is provided on both sides of a flange portion of a spline hub that fits into an output shaft, and an I-cube plate is connected with a nub pin that passes through the flange portion. The outer periphery of leave play 1 and sub play 1.
A damper disc featuring a friction member that generates a large friction force is installed between the two side plates that sandwich the blade, and the length of the sub pin is set to a length that can press the sub plate against the leave plate. be.

(2) The working friction member is disposed on the outer periphery of the thrust plate to widen the friction surface and generate a large hysteresis torque.

(Example) A longitudinal section of a clutch disc to which the present invention is applied is shown.
In the figure, there is an annular clutch plate 3 on the outer circumferential surface of the spline hub 1 which is fitted with the spline hub 1, sandwiching the flange 2 of the spline hub 1.
The Jz and Retaining Plate 4 (both side plates) are fitted.

A cushioning plate 6 is fixed to the outer periphery of the clutch plate 3 by rivets 5, and an annular facing 8 is pasted to the rivets I to 7 on both sides of the cushioning plate 6.

Clutch play 1) 3, retaining play 1-4
An annular glue plate 10, 10 is arranged between the flange portion 2 and the flange portion 2, respectively. Wave springs 11 and 11 are disposed between the inner circumference of the clutch plate 1-10 and the flange 2, respectively, and between the clutch plate 3 and the sub-plate 10, the retaining plate 4 and Friction washers 12, 12 are arranged between the sub-plates 10, respectively.

In the figure, 13 is a stop pin that connects the outer periphery of the clutch plate 3 and the retaining plate 1.
and passes through the window holes 15 and 16 provided in the sub-plate 10. The round knee 20 is a coil spring that extends in the circumferential direction (perpendicular to the plane of the paper in FIG. It is fitted into window holes 21, 22, 23, and 24 provided at positions corresponding to the direction (left and right in FIG. 1).

As shown in FIG. 3, on the outer peripheral edge of the one-knob plate 10 facing the clutch plates 1 to 3 or the bearing plate 4, an annular friction ring/1.0 with a small thickness is attached, for example, by adhesive. It has been pasted. This friction ring 7
10 is made of an organic friction material such as an organic material,
It has a large coefficient of friction, making it suitable for generating a large frictional force, and suitable for forming a thin film.

As shown in FIG. 2, which shows a partial cross section taken in the direction of the arrow ■ in FIG. 1, the illustrated clutch disc includes three strong (high spring constant) springs 20a and one weak (low spring constant) spring 20. They are arranged at equal intervals in the circumferential direction. Each window hole 22 of clutch plates 1 to 3, each window hole 23 of retaining plate 4, and each window hole 24 of leaf plate 10
The length in the circumferential direction is equal to that of the spring 20 and the weak spring 20
The window hole 21 of the flange portion 2 and the clutch plate 3 fitted with
The window hole 21 of the flange portion 2, which has the same length in the circumferential direction as the window hole 23 of the clutch plate 3 and the window hole 23a of the retaining plate 4, has a strong spring 20 fitted therein. long.

The window hole 15.16 for inserting the stop bin 13 is long in the circumferential direction, and in the illustrated state where the clutch plate 3 is not twisted relative to the flange portion 2, the inner edge 17.17 of the window hole 16 of the sub-plate 10 - and the stop pin 13 are separated by a distance 1-1.11' in the circumferential direction, and the inner edge 18.18- of the window hole 15 of the flange portion 2 is spaced from the stop pin 13 by the distance L. 1, + 1- spacing L2.12' or wider spacing in the circumferential direction -3, shi-3'
is the separation.

As shown in FIG. 1, both rib plates 10 are connected to each other by a sub-pin 30. In the free state (before being connected with the leave pin 30), each of the 11-brakes 1-10 has a cross-sectional shape that is flat or moves away from the flange portion 2 in the radial direction, as shown in the figure. Push the sub-pin 30 so that the outer circumferential side approaches the clutch plate 3 and the inning plays 1 to 4 by 1°, and then tighten each sub-plate 1.
0. FRIXION WASHI 11-12, CLUTCH PLAY 1
-3 The frictional force between the rear lining plates 4 is calculated by -
The frictional force between the rib plate 10, wave spring 11, and flange portion 2 is also set to be large.

The leave pin 30 is inserted into the window hole 15 of the flange portion 2 as shown in FIG.
A gap L4, L4-, which is narrower than the above-mentioned gap L3, L3- in terms of the torsion angle, is provided between the corresponding inner edge of the sleeve pin 30 and the window hole 16. There is.

Next, the effect of J2 will be explained. Torsion angle 1] (Fig. 1) is Oo
In the state shown in FIGS. 1 to 3, the flushing 8
When the clutch plate 3 is held between a flywheel on the engine side (not shown) and a pressure [L-play 1-], a torque [(FIG. 4) in the direction of arrow R in FIG. 2 is introduced into the clutch plate 3.

1 - While the torque 1 is extremely small, no slippage occurs on the pressure contact surface of the friction washer 12 shown in Fig. 1, and the torque T changes from the clutch plate 3 and retaining plate 1 to the clutch plate 3, retaining plate 1, 1F-, 12, leave plate 10, It is transmitted to the flange part 2, spline hub 1, and output shaft only through the wave spring 11 (without going through the spring 20 and spring 20a), and the clutch plate 3 and retaining plate 4 are not twisted relative to the flange part 2. .

Note that the above-mentioned operation is not clearly shown in FIG. 4 because the transmitted torque T during the operation is extremely small.

When the torque exceeds T'/J<very small, slippage occurs first on the pressure contact surfaces of the wave spring 11 and then on the friction washer p-12, so the clutch plate 3 and retaining plate 4 are twisted relative to the flange portion 2. Spring 20 and spring 20a are compressed, and spring 2
Torque T is transmitted via 0,208. When the torsion angle is less than a degree at part 1 (section (1-Pi) in Figure 4),
), side edges 31 and 32 on the counter-rotation direction side (reverse arrow R direction side) of the three sets of window holes 22a and 23a of clutch plate I' and third retaining brake +-=1 in Fig. 2 are springs. 2
0a, but the side edges 33.34 of the pair of window holes 22.23 in the direction of the reverse arrow R are in pressure contact with 20, so the four springs 20. Of the spring 20a,
Torque J is transmitted from the side edge 33.34 of the window hole 22.23 of the clutch plate 3 and retaining plate 4 to the edge 3b corresponding to the window hole 21 of the flange portion 2 via only one weak spring 20. During this period, the rate of increase in the transmission torque T with respect to the torsion angle becomes low (FIG. 4).

When the torsion angle exceeds ao (P 1-r33 ”),
Clap plays 1 to 3, the side edges 31 and 32 of the window holes 22a and 23a of the retaining plate 4 are in pressure contact with the spring 20a, and in parallel with the torque transmission to the spring 20 (e), three strong springs 20a from the clutch plate 3 and the retaining plate 4 to the flange portion 2
As a result, the slope of the torsion characteristic curve shown in FIG. 4 becomes steeper.

During one or more of the torsional strokes, while the torsion angle is smaller than ao (section 0-Pl), the surface of the wave spring 11 slides as shown in Figure 5, which shows a schematic cross-sectional view of ■-v in Figure 2. occurs, and the friction washer 12 has a large frictional force.
And no slippage occurs on the surface of the friction ring 40.

Therefore, the sub-plate 10 moves together with the clutch plate 3 and retaining plate 4, and is twisted in the direction of arrow R relative to the clutch portion 2.

When the torsion angle reaches ao (Pl), the sub pin 30 moves by the distance L4 in FIG. It becomes integral with the flange portion 2.

Torque - [is a slightly larger value t from the value t2 corresponding to Pl
While increasing to 3 (P2),
No slipping occurs on the surface of 12, so the torsion angle does not increase. When the torque T exceeds the value t3, slippage occurs on the surface of the friction washer 12, and the sub-plate 10, together with the clutch plate 3 and retaining plate 4, twists with respect to the flange portion 2.

At this time, the friction ring 40, clutch plate 3, and retaining plate 4 attached to the outer peripheral edge of the sub-plate 10 are twisted relative to the sub-plate 10 that is integrated with the flange portion 2.

Furthermore, the above slip causes a second stage of hysteresis in the torsional characteristics. Since the frictional force between the friction ring 40, clutch plate 3, and retaining plate 4 is set to be large as described above, even if the inner circumferential parts of the clutch plate 3 and retaining plate 4 are pushed outward by their own elasticity. spread to
Even if the frictional force generated by the friction washer 12 is reduced, the hysteresis in the second stage increases.

When the torsion angle 1iD becomes bo, the stop pin 13 comes into contact with the inner edge 18 of the window hole 15 of the 7 flange portion 2, and from then on -1
− twisting is prevented.

In the negative l~silk region shown in the lower left part of FIG. 4, the slope of the torsional characteristic changes in two steps in each part in the same manner with one action, and the hysteresis torque also becomes two steps.

(Effects of the Invention) As explained above, the damper disk according to the present invention has one leaf plate on both sides of the flange part of the spline hub that is dimensioned to fit on the output shaft, and the leaf plates 1 to 1 on the flange part. In the damper disk connected by a sub-pin that passes through d, a friction member for generating a large frictional force is provided between the outer periphery of sub-play 1~ and two side plates that sandwich the sub-plate, and the length of the sub-pin is set between the side plates. Since the length is set to be enough to press the sub-plate, the following effects can be achieved.

Since the friction ring 40 is disposed on the outer peripheral edge of the sub-plate 10, the friction area becomes large and a large frictional force, that is, second-stage hysteresis can be generated.

Moreover, since the friction ring 40 is stuck (pushed), the sub-plate 10 is pushed outward by the sub-pin 30 toward the clutch plate 3 and retaining plate 4, so the pressing force acting on the friction ring 40 becomes large, and a frictional force can be generated on the surface.

Further, as in the embodiment, the stop pin 13 is used to tighten the outer periphery of the clutch plate 3 and the retaining plate 4 ( When the friction ring 40 is disposed in the sub-bin 30, the effect of increasing the pressure applied by the sub-bin 30 becomes even more remarkable.

(Another embodiment) 1 (1) The friction ring 40 is not limited to the case where it is attached to the beam plate 10, for example, the clutch plate 3.
, it can also be attached to the retaining plate 4.

(2) The elastic member is not limited to the friction ring 40, but may have other shapes as long as it is a member that is installed between the sub-plate 10, clutch plate 3, and retaining plate 4 and can generate a predetermined large frictional force. It may be the material.

Further, the present invention is not limited to the case where both the friction ring 40 and the friction washer 12 are provided, and it goes without saying that it is sufficient that at least the friction ring 40 is provided.

Furthermore, the present invention can also be applied to a damper disk that does not include the facing 8.

[Brief explanation of drawings]

Fig. 1 is a vertical sectional view of a clutch disc to which the present invention is applied, Fig. 2 is a partial sectional view taken in the direction of the ■ arrow in Fig. 1, and Fig. 3 is a longitudinal sectional view showing a sub-plate to which a friction ring is attached. , FIG. 4 is a graph of torque-torsion characteristics, FIG. 5 is a cross-sectional view taken along the line v--■ in FIG. 2, and FIG. 6 is a vertical cross-sectional view of the main part of the conventional example. 1...Spline hub, 2...7 lunge part,
3...Clutch plate, 4...Retaining plate, 10...Sub plate, 11...Socket bus ring, 13...S1~butu pin, 30...Zub pin, 40... Friction ring patent applicant Jinkin Manufacturing Co., Ltd. 11 et al. Q- Procedural amendment @ (spontaneous) Showa (: July 311, 1985) 1985 Patent Application No. 142870 2, name of invention damper disk 3, amendment Relationship with the scammer case Patent applicant address: 1-1-1 Kida Motomiya, Neyagawa City Name: Daikin Seisakusho Co., Ltd. Representative Director and President: Masaru Sadachi 4, Agent address: 9-4, 8i 12-chome, Todai, Kita-ku, Osaka City Chiyoda Building East Building 10th Floor (@l 530) 5, the day of the correction order~
j (Shipping date) Showa year, month, day 6, subject to amendment
Specification 7, Contents of amendment (1) “20” on page 0, line 11 of the specification is corrected to r20aJ. More than = 2-

Claims (2)

[Claims] (1) In a damper disk in which sub-plates are provided on both sides of the flange of the spline hub that fits on the output shaft, and the sub-plates are connected by sub-pins that pass through the flange, the outer periphery of the sub-plate and two pieces sandwiching the sub-plate are connected. A friction member is installed between the side plates to generate a large frictional force,
A damper disc characterized in that the length of the sub-pin is set to a length that allows the sub-plate to be pressed against the side plate. (2) The outer peripheral part of the side plate is connected by a stop pin passing through the flange part, the sub-pin is arranged near the radially inner side of the stop pin, and the friction member is arranged near the radially outer side of the stop pin. A damper disk according to claim 1.