JPH06159386A - Clutch disk - Google Patents

Abstract

PURPOSE:To secure larger effective wear margin without increasing the thickness of facing plate its. CONSTITUTION:Projecting portions consisting of projecting portions 70, 72 projecting to housing hole 62 sides are provided around stepped holes 60 at facings 34, 36 and a plate spring 32, and at the same time recessed places 74 to house the projecting portions 72 that constitute parts of the projecting portions at the time of facings 34, 36 being stuck closely, are provided around housing holes 62 at the opposite surface 46, 48 of the facings 34, 36. The projecting sizes of the projecting portions 70, 72 and the depth sizes of the large diameter hole portions 56 of the stepped holes 60 are decided so that depth sizes (a), (b) may become approximately the same mutually.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch disc which is one component of a friction clutch for automobiles and the like.
The present invention relates to a clutch disc including a pair of facings (friction materials) that are connected to each other via leaf springs so as to be in close contact with each other.

[0002]

2. Description of the Related Art Generally, a friction clutch of an automobile or the like transmits a rotational torque based on frictional contact of a driven side flywheel and a pressure plate between a driven side flywheel and a pressure plate. However, it has a structure that cuts off the transmission of the rotational torque by releasing the clamping pressure.

One type of the above-mentioned clutch disc is a pair of facings, which are annular plates and are stacked in the axial direction, and the surfaces opposite to each other are friction surfaces. A plurality of stepped holes are provided at predetermined intervals in the circumferential direction, each having a large-diameter hole opening on the friction surface of the facing and a small-diameter hole opening on the facing surface of the facing and penetrating in the plate thickness direction. , A leaf spring provided between the facings and forming a predetermined interval between them, a small-diameter hole portion of the stepped hole and a shaft portion through which the leaf spring is inserted, and provided at one end of the shaft portion. It has a head located in the large-diameter hole portion of the stepped hole and a caulking portion crimped to the leaf spring at the other end of the shaft portion, and the leaf spring is fixed to the facing surface of the facing, respectively. By A plurality of rivets connecting the facings of each other through the leaf springs, and the rivets when the facings are brought into close contact with each other against the elastic force of the leaf springs. There is a type having a housing hole for housing the caulking portion. For example, the one disclosed in Japanese Utility Model Laid-Open No. 61-69527, which was previously filed by the applicant of the present invention, is such a clutch disk. According to such a clutch disc, a pair of facings are provided between the flywheel and the pressure plate. When is pinched, the leaf springs sandwiched between the facings are elastically deformed according to the pinching force between the flywheel and the pressure plate, so a uniform contact pressure is obtained over the entire circumference of the friction surface of the facing. It has the feature that the clutch is connected smoothly.

[0004]

By the way, in the conventional clutch disc as described above, it is normally housed in the housing hole when the facing of the rivet is located at the depth position from the facing friction surface and the facing. The depth position from the facing friction surface of the caulking portion of the rivet is relatively different from each other, and the former depth position is usually shallower than the latter depth position. Therefore, the effective wear allowance (allowable limit wear amount) of the facing is determined by the depth position of the smaller one, so that the effective wear allowance and thus the wear life are sufficiently secured without increasing the facing plate thickness. It was difficult.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide facings to each other via leaf springs fixed by rivets on mutually facing surfaces of a pair of facings. It is an object of the present invention to provide a clutch disc in which the clutch discs that are connected so as to be in close contact with each other can secure a larger effective wear margin without increasing the thickness of the facing plate.

[0006]

SUMMARY OF THE INVENTION To achieve the above object, the gist of the present invention resides in that in a clutch disc of the above type, the housing is provided around the facing hole and the stepped hole of the leaf spring. The convex portion protruding toward the hole is provided, and the concave portion for accommodating the convex portion when the facing is brought into close contact is provided around the accommodating hole on the facing surface of the facing.

[0007]

With this configuration, the convex portion protruding toward the accommodation hole is provided around the facing hole and the stepped hole of the leaf spring, and the convex portion is provided around the accommodation hole on the facing surface of the facing. Since a recess for accommodating the convex portion is provided when the facing is in close contact, the crimped portion of the rivet is accommodated in the accommodation hole and the convex portion is accommodated in the recess when the clutch disc is pressed. Thus, the pair of facings are brought into close contact with each other via the leaf spring. In this case, the depth position from the facing friction surface of the head of the rivet located in the large diameter hole portion of the stepped hole and the depth from the facing friction surface of the caulking portion of the rivet housed in the housing hole. If the dimension of the protruding portion in the protruding direction and the depth dimension of the large diameter hole portion of the stepped hole are determined so that the positions are substantially the same as each other, the effective wear allowance is increased without increasing the facing plate thickness. It is possible to secure a larger size and to improve the wear life. Further, when the facing and the portion of the leaf spring constituting the above-mentioned convex portion are fitted to each other so as not to move relative to each other in the facing circumferential direction, the facing and the leaf spring are perpendicular to the rivet by the facing and the leaf spring when transmitting the rotational torque. It is possible to preferably prevent the application of a large shearing force.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described in detail below with reference to the drawings.

FIG. 5 shows a friction clutch provided with a clutch disc 10 according to an embodiment of the present invention and provided in a power transmission path of an automobile. In the figure, a clutch cover 16 is fixed to a flywheel 14 fixed to the shaft end of a crankshaft 12 of an engine (not shown). Inside the clutch cover 16, a pressure plate 18 is attached to the flywheel 14. On the other hand, an input shaft 20 of a transmission (not shown) is inserted while being provided so as to be movable in the axial direction and rotatable with the flywheel 14. A diaphragm spring 21 is provided between the clutch cover 16 and the pressure plate 18.

The clutch disc 10 has an input shaft 20.
22 that is spline-fitted to the shaft end of the
The disc plate 26 and the sub-plate 28, which are integrally provided with each other by a plurality of rivets 24 (only one is shown in FIG. 5) so as to sandwich 2 from both sides in the axial direction.
And the disc plate 26 and the sub-plate 2
8 and the hub 22 and a torsion rubber spring 30 for transmitting torque, and is integrally attached to the outer peripheral portion of the disc plate 26 so as to extend further radially outward from the outer peripheral edge thereof, as shown in FIG. As described above, the plurality of leaf springs 32 arranged in the circumferential direction and the leaf springs 32 each having an annular plate shape and having the same plate thickness are stacked in the axial direction while sandwiching the plate spring 32. A pair of facings 34 and 36 are connected to each other via a leaf spring 32, and the facings 34 and 36 sandwiching the leaf spring 32 are interposed between the flywheel 14 and the pressure plate 18. The facings 34, 36 are mainly composed of a heat-resistant and wear-resistant substance such as asbestos or graphite.

In the friction clutch having such a structure, when the operating force is not applied to the clutch pedal (not shown), the pressure plate 18 is pressed toward the flywheel 14 side according to the urging force of the diaphragm spring 38, and the pressure plates 18 are not pressed. 18 and flywheel 1
The clutch disc 10 is pinched between the clutch disc 4 and the clutch disc 10, and the clutch disc 10 is brought into a connected state (a state shown in FIG. 5) for transmitting the rotational torque. Clutch release bearing (not shown) driven based on the applied hydraulic pressure
By pushing the inner peripheral portion of the diaphragm spring 38 toward the flywheel 14 side, the pressure plate 18 is separated from the flywheel 14 and is in a cutoff state in which torque is not transmitted.

As shown in FIGS. 1 to 3, the leaf spring 32 is integrally formed with a corrugated plate-shaped pressing portion 40 which is pressed between the facings 34 and 36 and an inner peripheral edge of the pressing portion 40. The fixing portion 42 is provided, and is fixed to the facing surface 46 of the facing 34 facing the facing 36 of the facing 34 by a rivet 44 at one end side of the pressing portion 40 in the circumferential direction of the clutch disc 10. Is fixed to the facing surface 48 of the facing 36 facing the facing 34 by the same rivet 44 on the other end side in the circumferential direction, and is fixed to the outer peripheral portion of the disc plate 26 by the pair of rivets 50 in the fixing portion 42. Has been done. A predetermined space is formed between the facings 34 and 36 by the leaf spring 32, and when the clutch disc 10 is pinched, the facing 34, 36
The members 36 are arranged to be in close contact with each other against the elastic force of the leaf spring 32. The surface of the facing 34 opposite to the facing surface 46 is a friction surface 52 with the flywheel 14.
The surface of the facing 36 opposite to the facing surface 48 is a friction surface 54 with the pressure plate 18.

As shown in FIGS. 1, 2 and 4, the facings 34 and 36 have large-diameter holes 56 that open to the friction surfaces 52 and 54 and small-diameter holes 58 that open to the facing surfaces 46 and 48. And a stepped hole 60 having a through hole in the plate thickness direction,
A plurality of sets of stepped holes 60 and accommodating holes 62, which are provided at predetermined intervals in the circumferential direction of the clutch disc 10 and penetrate in the plate thickness direction, are provided at predetermined intervals in the circumferential direction (FIGS. 1 and 2). In FIG. 1, one set of holes is provided for the facing 34, and the stepped hole 60 of the facing 34 and the accommodation hole 62 of the facing 36 face each other, and the accommodation hole 62 of the facing 34 and the stepped hole 60 of the facing 36 are provided.
And are facing each other.

The leaf spring 32 is fixed to the facings 34 and 36 by the rivets 44 in the stepped hole 60. The rivet 44 is provided with a small diameter hole portion 58 of the stepped hole 60 and a shaft portion 64 through which the leaf spring 32 is inserted, and a large diameter hole portion 5 of the stepped hole 60 provided at one end of the shaft portion 64.
6 has a head 66 located inside 6 and a caulking portion 68 crimped to the leaf spring 32 at the other end of the shaft portion 64. As shown in FIG. The caulking portion 68 is housed in the housing hole 62.

In the present embodiment, further, around the stepped holes 60 of the facings 34 and 36, as shown in FIGS. 1, 2 and 4, a housing hole 62 opposed to the stepped holes 60 is provided. Protruding portions 70 having a trapezoidal cross section in the projecting direction and a substantially rectangular planar shape are provided, and the facing surfaces 46 and 48 of the facings 34 and 36 of the leaf spring 32 are provided. As shown in FIGS. 1 to 3, the portion fixed to the portion (the portion located around the stepped hole 60) is also provided with the protruding portions 72 protruding toward the accommodation hole 62 side by the same size as the protruding portion 70. The facing portions 70 of the facings 34 and 36 are provided so that
In the recess inside the second protrusion 72, the clutch disk 10 is inserted in a state in which the tip end surface of the protrusion 70 contacts the bottom surface of the recess.
Are fitted so that they cannot move relative to each other in the circumferential and radial directions. In this embodiment, the protrusion 70 and the protrusion 72 form a protrusion. Also, facing 32, 34
Around the accommodation hole 62 of the facing surfaces 46 and 48 of the protrusion 7
Recesses 74 having the same depth as the protrusions 0 and 72 and accommodating the protrusions 72 that form part of the protrusions when the facings 34 and 36 are in close contact are provided. The protrusion 72 is fitted in the recess 74 such that the clutch disc 10 cannot move in the circumferential direction.

The depth dimension a from the friction surfaces 52, 54 of the facings 34, 36 of the head 66 of the rivet 44 located in the large diameter hole 56 of the stepped hole 60, and the facing 3
As shown in FIG. 2, the depth dimension b from the friction surfaces 52, 54 of the facings 34, 36 of the caulking portion 68 of the rivet 44 accommodated in the accommodating hole 62 when the four and 36 are in close contact with each other is substantially the same. It is said that.

6 and 7 are views showing an example of a conventional clutch disk 80. FIG. 6 corresponds to FIG. 1 of this embodiment and FIG. 7 corresponds to FIG. 2 of this embodiment. Is. The clutch disc 80 differs from the clutch disc 10 of this example in the following points. That is, the protrusions 70, 72 and the recess 74 are not provided, the large-diameter hole portion 56 of the stepped hole 60 is relatively shallow, and the friction surface 52 of the head 66 of the rivet 44, 5
The depth dimension a from 4 is relatively small and the facing 3
Caulked portion 68 of rivet 44 when 4, 36 are in close contact
Is different from the clutch disk 10 in that the depth dimension b from the friction surfaces 52 and 54 is relatively large and there is a relatively large difference c between the depth dimensions a and b. In such a conventional clutch disc 80, the facing 3
Since the effective wear allowance (allowable limit wear amount) of 4, 36 is determined by the smaller one of the depth dimensions a, b, that is, the depth dimension a, the effective wear is increased without increasing the plate thickness of the facings 34, 36. It was difficult to secure enough money. 6 and 7, the same reference numerals as in the case of the clutch disc 10 are used.

On the other hand, in the clutch disc 10 of this embodiment, the protruding portions 70 of the facings 34 and 36 are provided.
And the projecting dimension of the projecting portion 72 of the leaf spring 32 are set to dimensions approximately corresponding to half of the difference c in the conventional clutch disc 80, and the large diameter hole portion 56 of the stepped hole 60 is formed. The depth is made deeper than in the case of the conventional clutch disc 80 by a dimension substantially corresponding to half of the difference c, and the projecting portion 72 of the leaf spring 32 is accommodated in the recess 74 when the facings 34 and 36 are in close contact with each other. By doing so, as described above, the head 6 of the rivet 44 is
6 is the depth dimension a from the friction surfaces 52 and 54 and the caulking portion 6 of the rivet 44 when the facings 34 and 36 are in close contact with each other.
8 and the depth dimension b from the friction surfaces 52 and 54 are substantially the same. As a result, the effective wear allowance can be further increased without increasing the plate thickness of the facings 34, 36, and the wear life can be further improved.

Incidentally, when the depth dimension a of the head portion 66 of the rivet 44 is 1.5 mm and the depth dimension b of the caulked portion 68 of the rivet 44 is 2.5 mm in the conventional clutch disc 80, The effective wear allowance of the clutch disc 80 is 1.5 mm, which is the smaller of the depth dimensions a and b, and the difference c between the depth dimensions a and b is 1.0 mm. In, for example, the projecting dimensions of the projecting portions 70 and 72 and the depth dimension of the recess 74 are each set to 0.5 mm which is half the difference c, and the large diameter hole portion 56 of the stepped hole 60 is The depth is made 0.5 mm deeper than in the case of the clutch disc 80. As a result, the clutch disc 1 of this example
At 0, the depths a and b are both 2.0 mm and the effective wear allowance is 2.0 mm, so the effective wear allowance is increased by 0.5 mm compared to the conventional clutch disc 80. . FIG. 8 is a graph showing an example of the results of a so-called bench wear test by a testing machine for the clutch disc 10 of this embodiment in which the facings 34 and 36 each have a plate thickness of 3.5 mm. Represents the number of clutch connections, and the horizontal axis represents the amount of wear of the facings 34, 36 (wear dimension in the plate thickness direction). As can be seen from this graph, in the clutch disc 10 of this example, 18.1 ×
The wear amount of 2.0 mm, which is equivalent to the effective wear allowance, was reached after about 10 ⁴ times of connection. In this graph, the wear amount is 1.5
mm (equivalent to the effective wear allowance of the conventional clutch disc 80)
Since the number of connection times reaches about 13.6 × 10 ⁴ times, the clutch disc 10 of the present example has a wear life of about 33% in terms of the number of clutch connections compared to the conventional clutch disc 80. It can be said to improve.

Further, according to this embodiment, the facing 3
The projections 70 of the plate springs 4, 36 and the projections 72 of the leaf springs 32 are fitted so as to be relatively immovable in the circumferential direction of the clutch disc 10, and the projections 72 of the leaf springs 32 and the recesses 74 of the facings 34, 36 are provided. Are fitted so as not to move relative to each other in the circumferential direction, so that it is possible to reliably prevent the facings 34, 36 and the leaf spring 32 from being displaced in the circumferential direction during torque transmission. It is possible to prevent the shear force from acting.

Further, according to this embodiment, the facing 3
Since the protruding portions 70 of the blades 4, 36 and the protruding portion 72 of the leaf spring 32 are fitted so as not to move relative to each other in the circumferential direction and the radial direction of the clutch disc 10, the leaf spring 32 and the facing 3 are arranged.
There is an advantage that the leaf spring 32 and the facings 34 and 36 can be easily positioned when fixing them to each other.

Although one embodiment of the present invention has been described above with reference to the drawings, the present invention can be applied to other modes.

For example, in the above-described embodiment, even when the projecting portions 70 of the facings 34 and 36 and the projecting portion 72 of the leaf spring 32 are fitted so as to be relatively movable in the circumferential direction of the clutch disc 10, the rivet 44 can be moved. Head 6
6 is the depth dimension a from the friction surfaces 52 and 54 and the caulking portion 6 of the rivet 44 when the facings 34 and 36 are in close contact with each other.
Since the depth dimension b from the friction surfaces 52 and 54 of 8 is substantially the same, a large effective wear allowance of the facings 34 and 36 can be secured, and the effect of improving the wear life is obtained.

Further, in the above embodiment, even when the depth dimension a and the depth dimension b are relatively different from each other, the projecting portions 70 and 72 are relatively immovable from each other in the circumferential direction of the clutch disc 10. By being fitted, etc.
It is possible to obtain an effect that it is possible to prevent the shear force from acting on the rivet 44.

Further, in the above embodiment, the depth dimension of the recess 74 is the same as the protrusion dimension of the protrusions 70, 72, but it may be larger than the protrusion dimension of the protrusions 70, 72, or It is also possible that the recess does not have a bottom portion and is formed so as to penetrate in the thickness direction of the facing.
In the latter case, the recess also serves as the accommodation hole.

Further, in the above embodiment, the fixing position of the leaf spring 32 with respect to the facings 34 and 36 is the facing 3
The positions of the leaf springs 4 and 36 are spaced apart by a predetermined distance in the circumferential direction, but the leaf springs may be fixed to the facing at a position spaced apart by a predetermined distance in the radial direction.

Further, the present invention is not limited to the friction clutch as shown in FIG. 5, but can be applied to clutch discs of other various friction clutches. In short, a clutch disk of a type in which facings are in close contact with each other via leaf springs fixed by rivets on the facing surfaces of a pair of facings, the effect can be obtained by applying the present invention. It is possible.

Besides, the present invention can be variously modified without departing from the spirit thereof.

[Brief description of drawings]

FIG. 1 is a view corresponding to an enlarged view of a main part of a cross section taken along the line I-I of FIG. 3, showing a state in which a pair of facings are separated by a leaf spring.

FIG. 2 is a diagram showing a state in which the pair of facings in FIG. 1 are in close contact with each other against the elastic force of a leaf spring.

FIG. 3 is a view showing a part of the clutch disc of FIG. 5 as seen from the pressure plate side, and is a view showing a part of the clutch disc.

FIG. 4 is a view of one of the facings in FIG. 1 viewed from the other facing side, showing a main part.

FIG. 5 is a cross-sectional view showing a main part of a friction clutch provided with a clutch disc that is an example of the present invention.

FIG. 6 is a view showing an example of a conventional clutch disc and is a view corresponding to FIG. 1.

7 is a diagram showing a close contact state of the facing shown in FIG. 6, and is a diagram corresponding to FIG. 2;

FIG. 8 is a graph showing an example of a result of a wear test of the clutch disc of the present invention.

[Explanation of symbols]

 10: Clutch disc 32: Leaf spring 34, 36: Facing 44: Rivets 46, 48: Opposing surfaces 52, 54: Friction surface 56: Large diameter hole portion 58: Small diameter hole portion 60: Stepped hole 62: Receiving hole 64: Shaft 66: Head 68: Caulking {70, 72: Projection} Convex 74: Recess

Claims (1)

[Claims] 1. A pair of facings, each of which has an annular plate shape and is overlapped in the axial direction, and the surfaces opposite to each other and the surfaces opposite to each other are friction surfaces, and a predetermined distance in the circumferential direction between the facings. Between each of the facings and a stepped hole having a large-diameter hole opening on the friction surface of the facing and a small-diameter hole opening on the opposite surface of the facing, and a plurality of holes provided in each facing direction. A leaf spring that is provided and forms a predetermined space between them, a small-diameter hole portion of the stepped hole and a shaft portion that passes through the leaf spring, and a stepped hole that is provided at one end of the shaft portion. A head located in the large-diameter hole and a caulking portion crimped to the leaf spring at the other end of the shaft portion are provided, and the facing is fixed by fixing the leaf spring to the facing surface of the facing. A plurality of interconnected pieces are connected via the leaf springs. A clutch of a type provided with a rivet and an accommodation hole which is provided on an opposite surface of the facing and which accommodates the caulked portion of the rivet when the facing is brought into close contact with each other against the elastic force of the leaf spring. In the disk, a convex portion protruding toward the accommodation hole is provided around the facing hole and the stepped hole of the leaf spring, and the convex portion is provided around the accommodation hole on the facing surface of the facing when the facing is in close contact. A clutch disc having a recess for accommodating.