JP2009168201A - Clutch release bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a clutch release bearing preventing inclination when a sleeve slides and preventing occurrence of abnormal noise, by improving the roundness of the inner peripheral surface of the wall thickness portion of the sleeve. <P>SOLUTION: This clutch release bearing CRB includes: the resin sleeve 10 axially slidably supported by a power transmission shaft 61; a flange member 20 having an inside diameter end buried in the sleeve 10, and pushed at an outside diameter end to one side in an axial direction by the release fork 62 of a clutch mechanism; and a bearing portion 30 retained by the sleeve 10 in order to be positioned between the flange member 20 and the diaphragm spring 63 of the clutch mechanism and push-pressing the diaphragm spring 63 in association with the sliding of the sleeve 10 to the one side in the axial direction. The sleeve 10 is formed with the wall thickness portion 12 for regulating the inclination of the flange member 20 to the other side in the axial direction. The extended wall 42d of the inner portion 42 of a cover 40, as a reinforcing metal fitting, is buried in the wall thickness portion 12. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a clutch release bearing, and more particularly to a clutch release bearing provided with a resin sleeve that slides in the axial direction on a power transmission shaft.

  This type of clutch release bearing constitutes a clutch mechanism for intermittently connecting an engine output shaft and a power transmission shaft. The clutch mechanism will be briefly described. As shown in FIG. 6A, when the clutch pedal 101 is not depressed, the flywheel 103 rotates around the axis along with the engine output shaft 102 (drive shaft). The clutch plate 104 is pressed against the flywheel 103 via the pressure plate 106 by the elastic force of the diaphragm spring 105 (clutch connected state). In this state, as shown in FIG. 6B, when the clutch pedal 101 is depressed, pressure oil is supplied from the master cylinder 107 to the release cylinder 108, and the release fork 109 is rotated about the support shaft 110 as a fulcrum. As the release fork 109 rotates, the clutch release bearing 111 slides on the power transmission shaft 112 in one axial direction, and urges the diaphragm spring 105 in the direction in which the inclination is opposite. As a result, the pressure plate 106 moves to the other side in the axial direction, the clutch plate 104 is separated from the flywheel 103 (clutch disengaged state), and the transmission speed switching operation can be performed.

  Specifically, as described in, for example, Patent Document 1 below, the clutch release bearing has a resin sleeve supported on the power transmission shaft so as to be slidable in the axial direction, and an inner diameter end portion embedded in the sleeve. The flange portion, the anvil member fixed to the outer diameter end portion of the flange portion and pushed to one side in the axial direction by the release fork, and the sleeve are held so as to be positioned between the flange portion and the diaphragm spring, And a bearing (bearing portion) that presses the diaphragm spring as the sleeve slides in one axial direction. For the clutch release bearing described in Patent Document 1, as described in Patent Document 2 below, for example, a flange portion and an anvil member are formed by a single flange member, and the flange member is formed in the radial direction of the flange member. There is also known one in which the extending main body is formed in a planar shape and an annular shape. According to the clutch release bearing described in Patent Document 2, the number of parts can be reduced, and the front end surface of the inner ring of the bearing portion (contact surface with the diaphragm spring) and the rear surface of the flange member (the release fork) It is possible to sufficiently cope with dimensional constraints between the contact surfaces.

JP 2002-310186 A JP 2003-222162 A

  By the way, when the main body of the flange member is formed in a flat and annular shape as in the clutch release bearing described in the above-mentioned Patent Document 2, a means for restricting the collapse of the flange member toward the other side in the axial direction. In some cases, a thick portion is formed on the sleeve. However, if the thick portion is formed on the sleeve, the roundness of the inner peripheral surface of the thick portion may deteriorate due to sink marks or the like during the molding of the thick portion. The accuracy of the gap between the shaft and the sleeve is deteriorated, and the inclination of the sleeve is easily promoted when the sleeve is slid, and the possibility that abnormal noise (judder noise) is generated increases.

  The present invention has been made to solve the above problems, and its purpose is to prevent the inclination of the sleeve during sliding by improving the roundness of the inner peripheral surface of the thick portion of the sleeve. And it is providing the clutch release bearing which can prevent generation | occurrence | production of abnormal noise.

Means for Solving the Problems and Effects of the Invention

  In order to solve the above-described problems, the present invention provides a clutch release bearing included in a clutch mechanism that intermittently connects an engine output shaft and a power transmission shaft, and is made of a resin that is slidably supported on the power transmission shaft in the axial direction. Between the flange member and the diaphragm spring of the clutch mechanism, the inner diameter end of which is embedded in the sleeve, and is pushed to the axial direction by the release fork of the clutch mechanism on the outer diameter end side. And a bearing portion that presses the diaphragm spring as the sleeve slides toward one side in the axial direction, and the sleeve restricts the flange member from tilting toward the other side in the axial direction. A thick portion is formed, and a metal reinforcing bracket extending in the axial direction is embedded in the thick portion.

  According to this, it is possible to form the thick part thinner than the thick part of the sleeve of the prior art by the reinforcing member. By forming the thick portion thinly, sink marks during the molding of the thick portion can be effectively prevented (improved thermal conductivity, etc.). For this reason, the roundness of the inner peripheral surface of the thick portion is improved, the accuracy of the gap between the power transmission shaft and the sleeve is improved, and the inclination when the sleeve is slid is prevented. Generation | occurrence | production can be prevented favorably.

  In carrying out the present invention, the flange member has an annular main body portion extending in the radial direction, and a cylindrical base end portion extending from the inner diameter end of the main body portion to one side in the axial direction. It is good to be bent so that the outer peripheral part and inner peripheral part of this base end part may be covered.

  According to this, since the coupling between the flange member and the sleeve is reinforced by the reinforcing metal fitting, it is possible to satisfactorily prevent the sleeve body from being deformed when the flange member falls to the other side in the axial direction. Further, since the sleeve is reinforced at the middle portion in addition to the thick portion by the reinforcing metal fitting, the thickness of the middle portion of the sleeve can be formed thinner than the thickness of the middle portion of the sleeve of the prior art, and the power The gap between the transmission shaft and the intermediate portion of the sleeve can be set small, and the roundness of the inner peripheral surface in a wide range of the sleeve can be improved.

  In carrying out the present invention, the reinforcing metal fitting is preferably formed such that the end portion in the thick portion is bent outward in the radial direction of the sleeve. According to this, since the thick part of the sleeve is reinforced in the radial direction by the reinforcing metal fitting, it is possible to satisfactorily prevent deformation of the thick part when the flange member falls even if the thick part is formed thin. Can do.

  In carrying out the present invention, the reinforcing metal fitting may be provided with a through hole that allows inflow of a resin constituting the sleeve when the sleeve is molded. According to this, since the coupling between the reinforcing metal fitting and the sleeve is reinforced by the resin flowing into the through hole, it is possible to prevent the reinforcing metal fitting from being displaced from the sleeve.

  In carrying out the present invention, the reinforcing bracket is formed by the inner diameter end portion of the cover that supports the alignment spring for automatically aligning the shaft center of the bearing portion with the shaft center of the power transmission shaft. It is good to be. According to this, the conventionally used cover can be diverted effectively, and the reinforcing bracket can be formed at a low cost.

a. First Embodiment Hereinafter, a first embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a partial front view of a clutch release bearing CRB according to a first embodiment of the present invention, and FIG. 2 is a sectional view taken along line 2-2 of FIG. The clutch release bearing CRB includes a sleeve 10, a flange member 20, a bearing portion 30 and a cover 40.

  The sleeve 10 is a synthetic resin molded product formed in a stepped cylindrical shape, and is supported on the power transmission shaft 61 so as to be slidable in the axial direction.

  The flange member 20 is made of a steel plate press, and is integrated with the sleeve 10 by, for example, insert molding. The inner diameter end portion is embedded in the sleeve 10, and the outer diameter end portion side is axially one side by the release fork 62 ( In FIG. 2, it is pushed to the left side (hereinafter also referred to as the front side). Specifically, the flange member 20 includes an annular main body portion 21 that extends in the radial direction, a cylindrical base end portion 22 that extends from the inner diameter end of the main body portion 21 to one side in the axial direction, and a symmetrical position in the main body portion 21. A pair of projecting portions 23, 23 having a substantially L-shaped cross section extending radially outward from both outer diameter ends, and a base end portion 22 is embedded in the intermediate portion 11 of the sleeve 10, and each projecting portion The release fork 62 is pushed to one side in the axial direction at a contact portion from 23 to the main body 21. The sleeve 10 is formed with a thick portion 12 at the other end in the axial direction in order to restrict the fall of the flange member 20 toward the other side in the axial direction (the right side in FIG. 2, also referred to as the rear side in the following). .

  A plurality of through holes 22a that allow inflow of the synthetic resin constituting the sleeve 10 are formed in the base end portion 22 of the flange member 20 in the circumferential direction, and the rotation of the flange member 20 with respect to the sleeve 10 is prevented. .

  Further, a clip 50 as an elastic body is attached along the outer circumference (half circumference) of the front end surface (the surface on the one side in the axial direction) of the main body 21 in the flange member 20. The clip 50 elastically holds the release fork 62 in cooperation with a contact portion (surface on the other side in the axial direction) extending from each protrusion 23 to the main body 21 in the flange member 20.

  In the bearing portion 30, a ball 33 (rolling element) and a cage 34 are disposed between an inner ring 31 and an outer ring 32 each having a raceway surface, and are sealed by seal members 35 and 36. The bearing portion 30 is held on the sleeve 10 via the cover 40 by the elastic force of the wave spring 37 supported by the outer ring 32 and the cover 40.

  An outer flange portion 31a extending outward in the radial direction is integrally formed at the front end portion of the inner ring 31, and a diaphragm spring 63 is in contact with the outer flange portion 31a. That is, the bearing portion 30 is configured such that the inner ring 31 rotates relative to the outer ring 32 as the diaphragm spring 63 rotates. In this case, when a deviation (eccentricity) occurs between the rotation center of the diaphragm spring 63 and the rotation center of the bearing portion 30, the deviation is automatically absorbed by the elastic deformation of the wave spring 37. The rotation center is aligned so that it matches the rotation center of the diaphragm spring 63.

  The cover 40 is made of a steel plate press, and is integrated with the sleeve 10 by, for example, insert molding. The cover 40 covers the front and sides (radially outer side) of the outer ring 32 with a predetermined gap therebetween, and also has an annular outer part 41 that covers the rear of the bearing part 30 in contact with the rear end surface of the outer ring 32. And a double cylindrical inner portion 42 that is embedded in the intermediate portion 11 of the sleeve 10 and covers the proximal end portion 22 of the flange member 20.

  The rear end surface of the outer portion 41 is in contact with the front end surface of the main body portion 21 in the flange member 20, and the tilt of the flange member 20 to the front side is restricted.

  The inner portion 42 is bent and formed so as to cover the outer peripheral portion and the inner peripheral portion of the base end portion 22 in the flange member 20. Specifically, the inner portion 42 includes an outer wall 42 a that covers the outer peripheral portion of the base end portion 22, a bottom wall 42 b that covers the front end of the base end portion 22, and an inner wall 42 c that covers the inner peripheral portion of the base end portion 22. And an extending wall 42d extending rearward from the rear end of the inner wall 42c and reaching the thick portion 11 of the sleeve 10. Through holes 42a1 and 42c1 are formed in the outer side wall 42a and the inner side wall 42c corresponding to the through holes 22a of the base end portion 22 of the flange member 20, respectively.

  That is, in the first embodiment, the extending wall 42d of the inner portion 42 of the cover 40 is embedded in the thick portion 11 of the sleeve 10, so that the thick portion 11 is compared with the thick portion of the sleeve of the prior art. And can be formed thin. By forming the thick part 11 thinly, sink marks during the molding process of the thick part 11 can be effectively prevented (improvement of thermal conductivity, etc.). Thereby, the roundness of the inner peripheral surface of the thick portion 11 is improved, the accuracy of the gap between the power transmission shaft 61 and the sleeve 10 is improved, and the inclination when the sleeve 10 slides is prevented. The occurrence of abnormal noise can be satisfactorily prevented.

  In the first embodiment, the inner portion 42 of the cover 40 is bent so as to cover the outer peripheral portion and the inner peripheral portion of the base end portion 22 of the flange member 20, and the outer wall 42a, the bottom wall 42b, and the inner wall 42c. Are integrally formed.

  Thereby, since the coupling | bonding of the flange member 20 and the sleeve 10 is strengthened, the deformation | transformation of the sleeve 10 at the time of the fall of the flange member 20 to the other axial direction can be prevented favorably. Further, the thickness of the intermediate portion 11 of the sleeve 10 can be made thinner than the thickness of the intermediate portion of the sleeve of the prior art, and the gap between the power transmission shaft 61 and the intermediate portion 11 of the sleeve 10 is set small. Therefore, the roundness of the inner peripheral surface in a wide range of the sleeve 10 can be improved.

  The outer wall 42a and the inner wall 42c are formed with through holes 42a1 and 42c1 corresponding to the through holes 22a of the base end portion 22 of the flange member 20, respectively. As a result, the synthetic resin constituting the sleeve 10 flows into the through hole 22a of the base end portion 22 of the flange member 20 when the sleeve 10 is molded, and also flows into the through holes 42a1 and 42c1 of the outer wall 42a and the inner wall 42c, respectively. Therefore, the coupling among the sleeve 10, the flange member 20, and the cover 40 can be further strengthened.

  Further, since the inner portion 42 is formed by utilizing the inner diameter end portion of the cover 40, a conventionally used cover can be effectively used, and the inner peripheral surface of the sleeve 10 can be used with an inexpensive configuration. Circularity can be improved.

(Modified embodiment)
In the first embodiment, the inner portion 42 of the cover 40 is bent so as to cover the outer peripheral portion and the inner peripheral portion of the base end portion 22 of the flange member 20, and the outer wall 42a, the bottom wall 42b, and the inner wall 42c are integrated. In addition to these, for example, as shown in FIG. 3, for example, it extends from the intermediate portion of the bottom wall 42b to one side in the axial direction and reaches the front end portion 13 of the sleeve 10, and the other side in the folded axial direction. A double cylindrical extending wall 42e that extends to the front end of the inner wall 42c and connects to the front end may be formed integrally. Other configurations are the same as those in the first embodiment.

  According to this modified embodiment, the thickness of the front end portion 13 of the sleeve 10 can be made thinner than the thickness of the front end portion of the sleeve of the prior art, and the distance between the power transmission shaft 61 and the front end portion 13 of the sleeve 10 can be reduced. Therefore, the roundness of the inner peripheral surface of the sleeve 10 in a wider range can be improved.

b. Second Embodiment In the first embodiment, the extending wall 42d of the inner portion 42 of the cover 40 is shaped to extend to the other side in the axial direction at the thick portion 11 of the sleeve 10, but in addition to this, for example, FIG. As shown in FIG. 4, the end 42 d 1 of the extending wall 42 d may be bent outward in the radial direction of the sleeve 10. Other configurations are the same as those in the first embodiment.

  According to the second embodiment, the thick portion 12 of the sleeve is reinforced in the radial direction by the end portion 42d1 of the extending wall 42d. It is possible to satisfactorily prevent the thick portion 12 from being deformed when it falls to the side.

(Modified embodiment)
In the modified embodiment of the first embodiment, the extending wall 42d of the inner portion 42 of the cover 40 is shaped to extend to the other side in the axial direction at the thick portion 11 of the sleeve 10, but is the same as the second embodiment. For example, as shown in FIG. 5, the end 42 d 1 of the extending wall 42 d may be bent outward in the radial direction of the sleeve 10. Other configurations are the same as those of the modified embodiment of the first embodiment.

  In the said 1st and 2nd embodiment and each modification embodiment, although the inner part 42 of the cover 40 was fulfilling the function as a reinforcement metal fitting, it is good also as a separate body not only in this but the cover 40 and a reinforcement metal fitting. In this case, if the reinforcing metal fitting corresponding to the extending wall 42d is embedded in the thick portion 13 of the sleeve 10, the reinforcing metal fitting corresponding to the extending wall 42d, the outer wall 42a, the bottom wall 42b, and the inner wall 42c. A reinforcing metal fitting corresponding to the above may be formed integrally, or may be formed separately.

The partial front view of the clutch release bearing which concerns on 1st Embodiment of this invention. 2-2 sectional drawing of FIG. The fragmentary longitudinal cross-sectional view of the clutch release bearing which concerns on the deformation | transformation embodiment of 1st Embodiment. The fragmentary longitudinal cross-sectional view of the clutch release bearing which concerns on 2nd embodiment of this invention. The fragmentary longitudinal cross-sectional view of the clutch release bearing which concerns on the deformation | transformation embodiment of 2nd Embodiment. (A) is operation | movement explanatory drawing in case a clutch is in a connection state in a general clutch mechanism. FIG. 6B is an operation explanatory diagram when the clutch is in a disengaged state in the clutch mechanism of FIG.

Explanation of symbols

CRB Clutch release bearing 10 Sleeve 11 Middle portion 12 Thick portion 13 Front end portion 20 Flange member 21 Main body portion 22 Base end portion 22a Through hole 23 Projection portion 30 Bearing portion 31 Inner ring 32 Outer ring 33 Ball 34 Cage 35, 36 Seal member 37 Wave spring 40 Cover 41 Outer part 42 Inner part (reinforcing metal fittings)
42a Outer wall 42a1 Through hole 42b Bottom wall 42c Inner wall 42c1 Through hole 42d Extension wall 42d1 Extension wall end 42e Extension wall 50 Clip 61 Power transmission shaft 62 Release fork 63 Diaphragm spring

Claims (5)

In a clutch release bearing included in a clutch mechanism for intermittently connecting an engine output shaft and a power transmission shaft,
A resin sleeve supported on the power transmission shaft so as to be slidable in the axial direction;
An inner diameter end portion embedded in the sleeve, and a flange member that is pushed to one side in the axial direction by a release fork of the clutch mechanism on the outer diameter end side;
A bearing portion that is held by the sleeve so as to be positioned between the flange member and the diaphragm spring of the clutch mechanism, and that presses the diaphragm spring as the sleeve slides in one axial direction;
The sleeve is formed with a thick portion for restricting the fall of the flange member toward the other side in the axial direction, and a metal reinforcing metal member extending in the axial direction is embedded in the thick portion. A featured clutch release bearing.   The flange member has an annular main body portion extending in the radial direction, and a cylindrical base end portion extending from the inner diameter end of the main body portion to one axial direction, and the reinforcing metal fitting is a base of the flange member. The clutch release bearing according to claim 1, wherein the clutch release bearing is bent so as to cover an outer peripheral portion and an inner peripheral portion of the end portion.   3. The clutch release bearing according to claim 1, wherein an end portion of the thickened portion is bent outward in a radial direction of the sleeve.   The clutch release bearing according to claim 2 or 3, wherein the reinforcing metal fitting includes a through hole that allows an inflow of a resin constituting the sleeve when the sleeve is molded.   The reinforcing bracket is formed by an inner diameter end portion of a cover that supports a centering spring for automatically aligning the shaft center of the bearing portion with respect to the shaft center of the power transmission shaft. Item 5. The clutch release bearing according to any one of Items 2 to 4.

Images