JPH0534342Y2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Field of Application) The present invention relates to a clutch facing used, for example, in a friction clutch of an automobile.

(Prior Art) Conventionally, in order to prevent the friction material from peeling off from the clutch disk or being damaged due to the rotational breaking force applied to the clutch facing of the clutch disk, the rotational breaking strength of the facing 100 has been increased as shown in FIG. In order to improve the friction material 101
It is known that an annular metal plate 102 is bonded to one surface of the metal plate.

(Problem to be solved by the invention) However, in such a structure, since the mass of the facing 100 itself increases, the inertia torque of the clutch disk increases, resulting in problems such as the inability to smoothly switch the transmission gear. occurs. Furthermore, as shown by a two-dot chain line 103, there was also a problem in that distortion occurred during molding due to the difference in shrinkage rate between the friction material 101 and the metal plate 102.

In order to prevent such problems, a metal reinforcing ring 111 is provided concentrically and _integrally on the outer periphery of the friction material 110 as shown in FIG. One of the applicants has proposed a structure with a thickness shorter than the thickness T _f of 110 (Utility Application No. 62-
142259).

By employing the above structure, it is possible to provide a clutch facing that has low inertia to a certain extent, has high rotational fracture strength, and is lightweight.
However, the metal reinforcing ring 111 is the friction material 110.
Because it is placed on the outer periphery of the inertia, the inertia increases slightly.

In addition, as shown in FIG. 9, the friction surface 12 of the pressure plate 120 is
1 may be formed in a tapered shape that slightly approaches the friction surface 112 side of the friction material 110 as it goes toward the outer circumference. In that case, the friction surface 121 of the pressure plate 120 is the friction surface 1 of the friction material 110.
Since the outer periphery of the friction material 110 is unevenly contacted, only the outer periphery of the friction material 110 wears more as shown by the two-dot chain line 122 in FIG. The life of the clutch facing will be shortened as it wears out quickly.

The present invention relates to improvements in clutch facings used under conditions such as those described above.

(Means for Solving the Problems) In order to solve the above problems, the first invention of the present invention integrates at least the outer peripheral part of a metal reinforcing ring with the inner peripheral part of an annular friction material having a large diameter hole in the center. The clutch facing has a width dimension of the metal reinforcing ring set shorter than a thickness dimension of the friction material to provide a friction allowance on the friction surface side of the friction material, the clutch facing comprising: The ring consists of a lateral flange extending in the clutch axial direction, an outward flange extending radially outward from the opposite end of the lateral flange to the friction surface, and a reinforcing flange extending diagonally toward the friction surface from the joint of both flanges. It is characterized by consisting of.

Furthermore, the second invention of the present invention is such that at least the outer peripheral part of the metal reinforcing ring is integrally cast into the inner peripheral part of the annular friction material having a large diameter hole in the center, and the width dimension of the metal reinforcing ring is set to The clutch facing has a friction allowance on the friction surface side of the friction material, which is set shorter than the thickness of the material, and a movement allowance for the metal reinforcing ring is provided on the opposite friction surface side of the friction material. , a convex portion that allows the reinforcing ring to move toward the anti-friction surface side when the metal reinforcing ring is directly subjected to the rotational force or pressing force of a member that rubs against the friction material after the wear allowance has disappeared; It is characterized by being provided on the outer periphery of a metal reinforcing ring.

(Function) The inner peripheral part of the clutch facing is integrally connected with the reinforcing ring by casting a metal reinforcing ring. Therefore, the inner circumferential part of the clutch facing is integrally connected with the reinforcing ring, so that the inner peripheral part of the clutch facing is connected to the reinforcing ring integrally with the reinforcing ring. The resistance to centrifugal force (rotational destructive force) is improved.

(First Embodiment) FIG. 1 is a schematic vertical cross-sectional view of a clutch disk employing a clutch facing 20 of the present invention, with the left side of FIG. 1 being assumed to be the front.

As shown in Figure 1, the clutch facing 2
0 is an annular friction material 21 with a large diameter hole in the center,
22 in order from the front. Friction material 21, 2
2 is formed by impregnating a base material such as glass fiber or graphite with a phenol resin as a binder.

Reference numerals 30 and 31 denote metal reinforcing rings, which are annular integrally molded parts cast into the inner peripheries of the friction materials 21 and 22, respectively. The material used is steel, duralumin, stainless steel, aluminum alloy, or the like.

Reference numerals 32 and 33 indicate horizontal flanges that serve as the base of each reinforcing ring 30 and 31, and extend in the direction of the axis C of the clutch shaft 11 (transmission input shaft). From the end of each sideways flange 32, 33 on the opposite friction surface side (the mounting surface 23, 24 side of each friction material 21, 22), outward flanges 34, 35 project outward in the radial direction of the clutch facing 20. extends in one piece. and each horizontal flange 32,3
From the joint between 3 and outward flanges 34 and 35,
The reinforcing flanges 36 and 37 are connected to the friction surfaces 25 and 37, respectively.
It faces 26 and extends diagonally, reinforcing ring 3
0 and 31 are constituted by these flanges 32 to 37. In the first embodiment, the cross sections of the reinforcing flanges 36 and 37 are tapered. In addition, as shown in FIG.
8 to 40 may be provided to obtain more connecting surfaces during molding.

Lateral flange 33 as shown on the right side of FIG.
The width dimension W _r (in the following description, the subscript r indicates a ring, and the subscript f indicates a friction material) is set shorter than the thickness dimension T _f of the friction material 22. When the flanges 33, 35, and 37 of the reinforcing ring 31 are cast into the friction material 22, the friction material 22 is molded in a state in which it extends to both sides of the reinforcing ring 31 (in the direction of the center line C). As a result, on the friction surface 26 side of the friction material 22,
A friction allowance L _f is formed. Note that the reinforcing ring 31 may be arranged close to the outer peripheral edge of the mounting surface 24 of the friction material 22. This allows the wear allowance L _f to be set large. Of course, the above dimensional settings also apply to the relationship between the friction material 21 and the reinforcing ring 30.

The reinforcing rings 30 and 31 are connected to the friction materials 21 and 31, respectively.
22, first place the reinforcing ring casting 0 or the reinforcing ring 31 in a mold for molding the friction material (not shown), and then place the friction material 21 or the friction material 22 on the outer periphery of the reinforcing ring cast 0 or the reinforcing ring 31.
Pressure sinter and shape. As a result, the reinforcing ring 30, 3
1 is integrally cast into the inner peripheral portion of the friction material 21 or the friction material 22, respectively. In the present invention, the reinforcing rings 30, 31 are replaced by the horizontal flanges 32, 33.
, outward flanges 34 and 35, and reinforcing flanges 36 and 37, so the friction material 2
1 and 22 can be connected to each other.

In FIG. 1, 41 is a hub spline-fitted to the clutch shaft 11, 42 is an outer peripheral flange of the hub 41, and 43 and 44 are side plates arranged on both sides of the outer peripheral flange 42, which are integrally connected by pins (not shown). It is fixed and fitted to the outer circumferential portion of the hub 41 so as to be rotatable relative to the outer circumferential flange 42 . Reference numerals 45, 46, and 47 indicate window holes provided at opposing positions of the outer peripheral flange 42 and the side plates 43 and 44, respectively; 48 indicates each window hole 45 to 47;
A torsion spring 50 disposed within the cushioning plate 49 and the side plate 43
51 is the flywheel on the engine side, 52 is the clutch facing 2
0 to the flywheel 51. In the first embodiment, in order to increase the transmitted torque, the friction surface 53 of the pressure plate 52 is formed into a tapered shape that slightly approaches the front friction material 22 as it goes toward the outer circumference.

The clutch facing 20 of the present invention is
Cushioning plate 49 with rivets 60
Fixed.

According to the above structure, the pressure plate 52 presses the clutch facing 20 against the flywheel 51 by operating a clutch connection/disconnection mechanism (not shown). Then, the rotational force of the flywheel 51 is transmitted to the clutch facing 20, and from the clutch facing 20 to the cushioning plate 49, the side plate 43,
44, a torsion spring 48, an outer peripheral flange 42, and a hub 41 to be transmitted to the clutch shaft 11.

At this time, radially outward centrifugal force (rotational destructive force) is applied to the clutch facing 20 due to the impact when the clutch is engaged and the transmission of rotational force from the engine.
Reinforcement rings 30 and 31 are clutch facing 2
0 friction materials 21 and 22, and are integrally connected, the rotational fracture strength of the clutch facing 20 is improved, and problems such as peeling or damage of the friction materials 21 and 22 are avoided. Does not occur. Moreover, in this invention, the reinforcing ring 3
0 and 31, horizontal flanges 32 and 33, outward flanges 34 and 35, and reinforcing flanges 36 and 3
7, more connecting surfaces can be obtained.

Furthermore, by casting at least the outer circumferential parts (flanges 32 to 37) of the reinforcing rings 30, 31 into the inner circumferential parts of the friction materials 21, 22, the inertia is increased compared to the case where reinforcing rings of the same mass are cast in the outer circumferential parts. can be effectively prevented. Therefore, by employing the clutch facing 20 of the present invention, it is possible to increase rotational breaking strength, reduce inertia, and smoothly switch transmission gears.

Furthermore, by casting at least the outer peripheral parts of the reinforcing rings 30, 31 into the inner peripheral parts of the friction materials 21, 22, even when the pressure plate 52 shown in FIG. As shown in , since the amount of wear on the inner circumference is smaller than on the outer circumference, the reinforcing ring 31 does not come into contact with the pressure plate 52 for a long period of time, and the clutch facing 20 lasts a long time.

When the pressure plate 52 shown in FIG. 1 is used, when the friction material 22 is worn and the friction margin L _f disappears, the friction surface 53 of the pressure plate 52 rubs against the tip of the reinforcing flange 37. The reinforcing flange 37 emits a friction sound, which serves as a warning sound to notify the driver of the wear of the friction material 22, thereby providing a wear warning effect.

(Second embodiment) Reinforcement rings 70, 7 shown in FIG. 3 or 4
1 are cast in the inner circumferential portions of the friction members 72 and 73, respectively, at a distance from the cushioning plate 74 by a travel distance M _f (on the right side in FIG. 3). The outer peripheral surface of each reinforcing ring 70, 71 has a male thread 7.
5 and 76 (an example of a convex portion) are provided. For example, when the rotating direction of the flywheel 77 is counterclockwise when viewed from the back of the flywheel 77, the winding direction of the male threads 75 and 76 is a right-handed thread. , when the reinforcing ring 71 cast into the friction material 73 on the pressure plate 78 side is a left-handed thread (external thread 76 in FIG. 4), and the rotating direction of the flywheel 77 is clockwise when viewed from the back. , the reinforcing ring 70 has a left-handed thread, and the reinforcing ring 71 has a right-handed thread.

According to the structure shown in FIGS. 3 and 4, the friction material 72,
73 wears out and the friction allowance L _f becomes O, and when the flywheel 77 and the reinforcing ring 70 (or the pressure plate 78 and the reinforcing ring 71) rub, the reinforcing rings 70 and 71 make a friction noise due to the rotational force. while moving in the respective screw directions, that is, toward the cushioning plate 74 side. Therefore, this friction sound becomes an alarm sound to notify the driver of the wear of the friction materials 72 and 73. and reinforcing rings 70, 71
continues to move, and finally the cushioning plate 7
It comes into contact with the side surface of the inner peripheral part of No. 4 and stops. Therefore, the flywheel 77 will not idle for a while after the reinforcing rings 70 and 71 start emitting the alarm sound, and the driver will be able to control the flywheel 77.
It is possible to know when to replace the clutch facing 80 before it becomes idle.

(Third Embodiment) Reinforcement rings 90, 9 shown in FIG. 5 or 6
1 is provided with protrusions 92 and 93 (an example of a protrusion) having a rectangular cross section extending perpendicularly to the circumferential direction on the outer peripheral surface thereof. Reinforcement rings 90, 91
When protrusions 92 and 93 are provided, friction materials 94 and 95
Even if the wear allowance L _f becomes 0 due to wear, the reinforcing ring 9
0 and 91 are respectively shown in FIG.
Move to the 6 side by the moving distance M _f . Therefore, Figure 5,
The structure shown in FIG. 6 also has the same effect of preventing the flywheel from spinning as the reinforcing rings 70 and 71 shown in FIGS.
A warning sound is generated to notify the driver of the wear of the clutch facings 96 and 4,95.

(Effects of the invention) As explained above, according to the invention, the inner peripheral part of the clutch facing is integrally connected with the reinforcing ring by casting the metal reinforcing ring. Improves resistance to

Furthermore, by casting at least the outer circumferential portion of the reinforcing ring into the inner circumferential portion of the friction material, an increase in inertia can be more effectively prevented than when a reinforcing ring of the same mass is cast into the outer circumferential portion. Therefore, by adopting the clutch facing of this invention,
Rotational breaking strength can be increased, and inertia can be reduced so that transmission gears can be switched smoothly. Moreover, in the reinforcing ring of the present invention, at least the outer circumferential portion is molded on the inner circumferential portion of the friction material, so that the friction surface 53 of the pressure plate 52 increases as the friction surface 53 of the pressure plate 52 moves toward the outer circumferential side, as shown in FIG. Even when the clutch facing 20 is formed into a tapered shape that approaches the material 22 side, the amount of wear on the inner peripheral portion of the friction material 22 is less than that on the outer peripheral portion, so that the clutch facing 20 can be used for a long period of time.

Moreover, according to the first invention of the present invention, as shown in FIG.
2, 33, outward flanges 34, 35, and reinforcing flanges 36, 37, more connecting surfaces can be obtained.

Furthermore, according to the second invention of the present invention, as explained in FIGS. 3 to 6, the metal reinforcing rings 70, 7
1 or 90, 91 (external threads 74, 75 or protrusions 92, 93) allows the reinforcing ring 70, 71 or 90, 91 to move toward the anti-friction surface side (retaining plate 74 or 86 side) Therefore, it is possible to prevent the flywheels 77 and 96 from spinning idly, and also to provide a wear warning function to notify the driver of the wear of the friction materials 72 and 73 or the friction materials 94 and 95.

[Brief explanation of the drawing]

FIG. 1 is a partial schematic longitudinal cross-sectional view showing a first embodiment of the present invention, FIG. 2 is a partial schematic view in the direction of arrows in FIG. 1, and FIG. 4 is a schematic view of a portion taken in the direction of the arrow in FIG. 3, FIG. 5 is a partial schematic view of a longitudinal section showing a third embodiment of the present invention, FIG. 6 is a view taken in the direction of the arrow of FIG. 5, and FIG. FIGS. 8 and 9 are schematic vertical cross-sectional views of the clutch facing, showing the completion process of the present invention. 20, 80, 96...clutch facing, 21, 22, 72, 73, 9
4,95...friction material, 30,31,70,71,
90, 91...Metal reinforcement ring, 32, 33...
... Lateral flange, 34, 35... Outward flange, 36, 37... Reinforcement flange, 75, 76...
...Male thread (an example of a convex part), 92,93...Protrusion (an example of a convex part), W _r ...Width dimension of the reinforcing ring, T _f
...Friction material thickness dimension, L _f ...Friction allowance, M _f ...
Reinforcement ring movement cost.

Claims (1)

[Claims for Utility Model Registration] (1) At least the outer periphery of a metal reinforcing ring is integrally cast into the inner periphery of an annular friction material having a large diameter hole in the center, and the width of the metal reinforcing ring is The clutch facing has a dimension shorter than the thickness of the friction material to provide a friction allowance on the friction surface side of the friction material, and the metal reinforcing ring has a horizontal flange extending in the clutch axial direction. , a clutch facing characterized by comprising an outward flange extending radially outward from an end on the side opposite to the friction surface of the lateral flange, and a reinforcing flange extending diagonally toward the friction surface from the joint of both flanges. (2) At least the outer periphery of a metal reinforcing ring is integrally cast into the inner periphery of an annular friction material having a large diameter hole in the center, and the width dimension of the metal reinforcing ring is equal to the thickness of the friction material. A clutch facing having a friction allowance on the friction surface side of the friction material, which is set shorter than the dimensions of the clutch facing, wherein a movement allowance for the metal reinforcing ring is provided on the opposite friction surface side of the friction material,
When the above-mentioned wear allowance disappears and the above-mentioned metal reinforcing ring directly receives the rotational force or pressing force of a member that rubs against the friction material, a protrusion that allows the above-mentioned reinforcing ring to move toward the non-friction surface side is attached to the above-mentioned metal. A clutch facing characterized by being provided on the outer periphery of a reinforced ring.