JP2007205527A - Clutch disk - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To make a cushioning characteristic of a clutch disk proper. <P>SOLUTION: In the clutch disk, facings 60A, 60B are fixed by a rivet 70 with respect to both faces of a disk spring 50 formed to have irregularities in the thickness direction. On the back faces of the facings 60A, 60B facing the disk spring 50, recesses 61 are formed at parts other than the parts where a compressive stress of a certain amount or more occurs on the facings 60A, 60B, in the case a load is applied to the disk spring 50 in the thickness direction. The facings 60A, 60B have groove parts 62 on the surface and incorporates base fiber bundles. The recesses 61 are formed to have a depth to secure at least the thickness of the base fiber bundles in a part corresponding to the groove part 62. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a clutch disk for a friction clutch for a vehicle, and more particularly to a clutch disk capable of optimizing cushioning characteristics.

  Friction clutches for vehicles, such as automobiles, transmit rotational torque by both frictional resistances when the driven clutch disk is clamped between the drive flywheel and the pressure plate, and the clamping pressure is released. By doing so, it has a structure that blocks transmission of rotational torque.

  In some clutch disks, the facings are connected to each other's facing surfaces of the pair of facings via a disk spring fixed by a rivet so that they can contact each other. The pair of facings each have an annular plate shape and are overlapped in the axial direction, and the surfaces opposite to the opposing surfaces are friction surfaces. A plurality of facings are provided for each predetermined interval in the circumferential direction, and a stepped hole that penetrates in the plate thickness direction with a large-diameter hole opening in the friction surface and a small-diameter hole opening in the facing surface of the facing is provided. Have. The facing is provided on the opposing surface and has a receiving hole for receiving the caulking portion of the rivet when the facing is brought into contact with each other against the elastic force of the disc spring. The disk spring is provided between the facings and forms a predetermined interval therebetween. The rivet includes a small diameter hole portion of the stepped hole and a shaft portion through which the disc spring is inserted, a head portion provided at one end of the shaft portion and positioned in the large diameter hole portion of the stepped hole, and The other end has a caulking portion that is caulked to the disc spring, and the disc springs are respectively fixed to the facing surfaces of the facing to connect the facings to each other via the disc spring.

  In conventional clutch discs, concave portions with a depth that does not reach the wear limit of each friction surface are formed on the joint surface with the disc spring, which is the back surface of the friction surfaces of both facings. What is formed in such a pattern is disclosed (see Patent Document 1).

Japanese Utility Model Publication No. 58-9528

  From the recess pattern described in Patent Document 1, proper cushioning characteristics cannot be obtained, and there is a risk of facing creeping. In other words, since there is no recess in the portion where the load is applied to the joining surface of the facing and the disk spring, the surface pressure on the facing side is increased, and facing creep may occur. As a result, the amount of cushioning due to the indentation of the disk spring is insufficient, making it difficult for the clutch to be engaged, and abnormal noise may occur.

  Moreover, about the depth of the recessed part described in patent document 1, in the depth which does not reach an abrasion limit value, a moldability is bad as an actual problem, and there exists a possibility that a facing cannot be manufactured. That is, generally, a groove portion for preventing sticking is formed on the friction surface side of the facing. When there is a concave portion on the back surface corresponding to the groove portion, the concave portion is the thinnest plate thickness portion. Considering that it is necessary to ensure the minimum thickness of the base fiber (for example, glass fiber) included in the facing, the concave portion is the minimum base fiber bundle required at a depth that does not reach the wear limit value. The thickness of the minute may not be secured.

  The main object of the present invention is to optimize the cushioning characteristics of the clutch disk.

  In a viewpoint of the present invention, a clutch disk in which facings are fixed to both sides of a disk spring formed so as to have irregularities in a thickness direction, the facing is provided on a back surface facing the disk spring. A concave portion is formed in a portion other than a portion where a compressive stress of a certain level or more is generated in the facing when a load is applied to the disk spring in the thickness direction.

  In the clutch disk of the present invention, when the facing has a groove portion on the surface and incorporates a base fiber bundle, and the concave portion is formed in a portion corresponding to the groove portion, at least the thickness of the base fiber bundle. It is preferable that it is formed at a depth that ensures the thickness.

  In the clutch disk of the present invention, it is preferable that the recess is not cut on the back surface.

  In the clutch disk of the present invention, it is preferable that a positioning portion corresponding to the position of the concave portion is formed on the surface, the outer peripheral portion, or the inner peripheral portion of the facing.

  In the clutch disk of the present invention, it is preferable that the concave portion is formed at a predetermined depth or less at an edge of a hole formed in the facing.

  According to the present invention (claims 1-5), it is possible to secure an appropriate value of the initial characteristic of cushioning and prevent a change with time. This is because the occurrence of creep can be prevented because there is no recess in the load-loading portion between the facing and the disc spring. Further, clutch slippage can be prevented. This is because there is no recess in the load-loading portion between the facing and the disk spring, so that the surface pressure of the friction surface can be equalized and the friction coefficient μ can be obtained stably. Furthermore, it is possible to prevent the cushioning characteristic from changing with time, to prevent uneven surface pressure, and to prevent the friction coefficient μ from being lowered. This is because the occurrence of creep can be prevented because there is no recess in the load-loading portion between the facing and the disc spring.

  According to the present invention (claim 2), the moldability is improved. That is, the base fiber is not cut or broken, and molding defects due to insufficient compression are eliminated. Further, since the amount of the high-strength base fiber can be kept above a certain amount, the rotational burst strength is ensured. This is because the recess is formed with a depth that allows for the thickness of the base fiber bundle.

  According to the present invention (Claim 3), cost can be reduced. This is because the two facings are shared, so that the assembling property is improved. In addition, after forming the facing with the mold, the material can be reduced to the amount of the concave portion and the polishing allowance in the finished shape of the facing by not cutting (polishing) the back surface of the facing.

  According to the present invention (Claim 4), the workability of drilling is improved. This is because the positioning part can be aligned with the recess.

  According to the present invention (Claim 5), the rotational burst strength is ensured. This is because stress generated at the inner peripheral edge and the edge of the hole due to the centrifugal force at the time of rotational load is alleviated, and the rotational burst strength is ensured.

(Embodiment 1)
A clutch disk according to Embodiment 1 of the present invention will be described with reference to the drawings. FIG. 1A is a front view schematically showing a configuration of a clutch disk according to Embodiment 1 of the present invention, and FIG. FIG. 2 is an enlarged partial cross-sectional view taken along the line BB ′ of FIG. 1 schematically showing the configuration of the clutch disk according to the first embodiment of the present invention. 3A is a front view and FIG. 3B is a rear view schematically showing a facing configuration in the clutch disk according to the first embodiment of the present invention. FIG. 4 is a partial cross-sectional view between (a) CC ′ in FIG. 3B schematically showing the configuration of the facing in the clutch disk according to Embodiment 1 of the present invention, and (b) DD ′. It is a partial sectional view between, (c) Partial sectional view between EE ', (d) It is a partial sectional view between FF'. FIG. 5 is a diagram schematically showing the corresponding positions of the groove on the front side of the facing and the recess on the back side of the clutch disk according to the first embodiment of the present invention.

  Referring to FIG. 1, a clutch disk 1 is a component part of a friction clutch for a vehicle such as an automobile, and is sandwiched between a flywheel (not shown) and a pressure plate (not shown). The rotational power of an engine (not shown) is transmitted to a transmission (not shown). The clutch disk 1 has a torsional cushioning function, and includes a clutch hub 10, a disk plate 20, a thrust member 30, a coil spring 40, a disk spring 50, and a facing 60.

  The clutch hub 10 is spline-fitted to the shaft end of an input shaft (not shown) of a transmission (not shown) at the inner periphery. The clutch hub 10 has a flange 11 extending in the radial direction. Here, a type in which the flange 11 of the clutch hub 10 is integrated with the hub portion is employed. However, a small spring is disposed between the flange 11 and the hub portion, and the flange 11 It is good also as a structure which can absorb a minute torsional vibration between hub parts. The clutch hub 10 has a notch 12 that is notched radially outward of the flange 11. The notch 12 is configured such that the outer peripheral surface side of the spring seats 41 and 42 is located on the radially outer side than the outer peripheral surface of the flange 11.

  The disc plate 20 is disposed on both surfaces of the clutch hub 10 so as to be coaxial with the clutch hub 10 and relatively rotatable. The disk plate 20 includes a first disk plate 20A and a second disk plate 20B that are disposed on both axial sides of the clutch hub 10. The first disk plate 20A and the second disk plate 20B are connected by a rivet 80 on the outer peripheral side thereof. The disk plates 20 </ b> A and 20 </ b> B have a window hole 21 for connecting the outer peripheral side of the coil spring 40.

  The thrust member 30 is a member made of washer-like resin interposed between the contact surfaces of the clutch hub 10 and the disk plate 20. The thrust member 30 is interposed between the contact surface of the first thrust member 30A interposed between the clutch hub 10 and the first disk plate 20A, and the contact surface of the clutch hub 10 and the second disk plate 20B. And a second thrust member 30B.

  The coil springs 40 are accommodated in the notches 12 and the window holes 21 formed at positions where the clutch hub 10 and the disk plates 20A and 20B are opposed to each other. The coil spring 40 is used. Each coil spring 40 is accommodated in the notch 12 and the window hole 21 while being supported by a pair of spring seats 41 and 42.

  The disc spring 50 has an annular plate shape and is an elastic member made of spring steel having a notch and a bent portion formed at predetermined positions along the circumferential direction so as to have irregularities in the thickness direction. (See FIGS. 1 and 2). Further, the disc spring 50 receives a pressing force from both sides thereof, and when a load is applied in a direction to be crushed, the disc spring 50 is deformed into a flat shape and generates a restoring force to return to an uneven shape when no load is applied. That is, a force that opposes the pressing force from both sides is generated. In the present embodiment, the unevenness in the thickness direction of the disc spring 50 is regularly formed along the circumferential direction. However, even if the disc spring 50 is irregularly arranged, excessive stress concentration occurs with respect to the pressing force. If it can avoid. In this embodiment, the disc spring 50 has a continuous annular shape, but may have a structure in which divided plate springs are arranged. Further, the inner peripheral portion of the disc spring 50 is connected by a rivet 80 at the outer peripheral portion of the second disc plate 20B.

  The facings 60A and 60B are wear-resistant members each having an annular plate shape and the same plate thickness (see FIGS. 1 to 5).

  The facings 60A and 60B include base fiber, resin, and a friction modifier. A base fiber consists of fibers, such as glass fiber, carbon fiber, organic fiber, and inorganic fiber, for example. The resin is impregnated between the base fibers and is made of, for example, a resin such as a thermosetting resin (for example, a phenol resin) or rubber. The friction modifier is contained in the resin and includes, for example, additives such as cashew dust and a peroxide (for example, manganese dioxide).

  The facings 60A and 60B are disposed on both sides in the axial direction of the disc spring 50, and are fixed to the disc spring 50 by rivets 70 (see FIG. 1). The facings 60A and 60B are formed with rivet holes 63 fixed by the rivets 70 and through holes 64 not fixed by the rivets 70 (see FIG. 3). The facings 60A and 60B can be clamped between a flywheel (not shown) and a pressure plate (not shown).

  In the facings 60A and 60B, there is a back surface with which the disk spring 50 comes into contact with a surface that frictionally engages a flywheel (not shown) or a pressure plate (not shown). On the surfaces of the facings 60A and 60B, there are grooves 62 formed in the radial direction and the circumferential direction. The facings 60 </ b> A and 60 </ b> B have recesses 61 in portions other than a predetermined portion of the disk spring 50 on the back surface.

  Here, the predetermined portion of the disc spring 50 is fixed to the facings 60A and 60B when a load is applied in a direction in which the disc spring 50 is crushed by the facings 60A and 60B among the contact portions of the disc spring 50 and the facings 60A and 60B. The part where the above compressive stress occurs is said. Even if the disk spring 50 is in contact with the facings 60A and 60B, a portion where no compressive stress above a certain level is generated in the facings 60A and 60B when a load is applied in the direction in which the disk spring 50 is crushed by the facings 60A and 60B Is not included in a predetermined portion of the disc spring 50.

  The recess 61 has a shallow portion of the rib portion 61a and a deep portion of the bottom portion 61b. The rib part 61a is formed in the part corresponding to the groove part 62 of facing 60A, 60B. This is for securing the thickness of the built-in base fiber bundle and preventing molding defects. Further, the rib portion 61 a may be formed in a portion other than the portion corresponding to the groove portion 62 when the region where the concave portion 61 can be formed can be set large. Thereby, surface rigidity can be improved and the surface pressure of a friction surface can be made uniform. This has an effect of preventing increase in wear and decrease in μ. The depth of the bottom 61b is set in consideration of increasing the amount of dents and taking into account the wear allowance and variation so that no hole is opened in the member.

  Two facings 60A and 60B are used in one clutch disk assembly. However, since the contact portions with the disk spring 50 are different from each other, two types can be formed by setting a concave shape to avoid the contact portions. This is also effective for producing a concave effect. In consideration of mass productivity, it is preferable to set a shape that can be shared in order to improve the productivity of the facings 60A and 60B and reduce the cost by improving the assembly of the clutch disk 1 assembly.

  It is preferable that the recess 61 remains in the mold-molded state, that is, does not perform post-processing (cutting) in a black skin state (a state immediately after mold formation). This is because the polishing allowance can be reduced and the input material can be reduced. Further, since the base fiber is not cut, there is no decrease in strength and rigidity.

  Drilling of the rivet holes 63 and the through holes 64 of the facings 60A and 60B is performed after the mold forming process and the front and back process. A positioning part (not shown) such as a notch corresponding to the position of the recess 61 is preferably formed on the inner peripheral part or the outer peripheral part on the basis of the positioning of the rivet hole 63 and the through hole 64. Further, as another pattern, a radial groove portion 62 or a positioning portion such as a concave shape peculiar to an island-shaped friction surface may be formed.

  The concave portion 61 secures the rotational burst strength and reduces the strength reduction of the facings 60A and 60B as much as possible, and the inner peripheral edge and the outer peripheral edge of the facings 60A and 60B, the rivet holes 63 and the through holes. It is preferable not to form at the edge of the hole 64, and even when it is formed, it is preferable to make it shallower than the depth of the bottom 61b.

  According to the first embodiment, it is possible to secure an appropriate value of the initial characteristic of cushioning and prevent a change with time. The reason is that since the concave portion 61 is not formed in a predetermined portion of the contact portion between the facings 60A and 60B and the disc spring 50, the occurrence of creep can be prevented. Further, clutch slippage can be prevented. This is because the concave portion 61 is not formed in a predetermined portion of the contact portion between the facings 60A and 60B and the disc spring 50, so that the surface pressure of the friction surface is equalized and the friction coefficient μ is stably obtained. It is. Furthermore, the friction coefficient μ can be prevented from decreasing by preventing the cushioning characteristic from changing with time and preventing the non-uniform surface pressure. The reason is that since the concave portion 61 is not formed in a predetermined portion of the contact portion between the facings 60A and 60B and the disc spring 50, the occurrence of creep can be prevented.

BRIEF DESCRIPTION OF THE DRAWINGS It is the (a) notch front view which showed typically the structure of the clutch disk which concerns on Embodiment 1 of this invention, (b) It is sectional drawing between AA '. FIG. 2 is an enlarged partial cross-sectional view taken along the line BB ′ of FIG. 1 schematically showing the configuration of the clutch disk according to Embodiment 1 of the present invention. It is the (a) front view and the (b) rear view which showed typically the structure of the facing in the clutch disk which concerns on Embodiment 1 of this invention. FIG. 3A is a partial cross-sectional view taken along the line C-C ′ in FIG. 3, and FIG. 3B is a partial cross-sectional view taken along the line D-D ′. c) Partial sectional view between EE ′ and (d) Partial sectional view between FF ′. It is the figure which showed typically the corresponding position of the groove part of the surface side of the facing, and the recessed part of a back surface side in the clutch disc which concerns on Embodiment 1 of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Clutch disc 10 Clutch hub 11 Flange 12 Notch 20 Disc plate 20A 1st disc plate 20B 2nd disc plate 21 Window hole 30 Thrust member 30A 1st thrust member 30B 2nd thrust member 40 Coil spring 41, 42 Spring seat 50 Disc Spring 60, 60A, 60B Facing 61 Recess 61a Rib 61b Bottom 62 Groove 63 Rivet hole 64 Through hole 70, 80 Rivet

Claims (5)

A clutch disk in which facings are fixed to both sides of a disk spring formed to have irregularities in the thickness direction,
In the facing, a recess is formed in a portion other than a portion where a compressive stress of a certain level or more is generated in the facing when a load is applied to the disk spring in the thickness direction on the back surface facing the disk spring. A clutch disk characterized by The facing has a groove on the surface and incorporates a base fiber bundle,
2. The clutch disk according to claim 1, wherein when the recess is formed in a portion corresponding to the groove, the recess is formed at a depth that secures at least a thickness of the base fiber bundle.   The clutch disk according to claim 1, wherein the recess is not cut on the back surface.   4. The clutch disk according to claim 1, wherein a positioning portion corresponding to the position of the concave portion is formed on a surface, an outer peripheral portion, or an inner peripheral portion of the facing. 5.   The clutch disk according to any one of claims 1 to 4, wherein the recess is formed at a predetermined depth or less at an edge of a hole formed in the facing.

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