JP2011163361A - Clutch release bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a clutch release bearing with superior sealing performance, capable of stably holding at all times a fixed state of a stationary ring and a holding member. <P>SOLUTION: A rear side end of an inner ring 11 being the stationary ring is a fixed part A fixed with the holding member 71 holding a pre-load spring 70 energizing the inner ring 11 to a front side in an inner diameter part, and the fixed part A has a seal part forming face B sealing a rear side opening of an annular space K in cooperation with a second seal member 16. The seal part forming face B is composed of an outer diameter face 11a1 of the rear side end of a cylindrical part 11a of the inner ring 11. Of the fixed part A, a projection 11c as an engagement part to be engaged with the holding member 71 in a circumferential direction is provided on an opposing face, in this case an inner diameter face 11a2, with the holding member 71 provided excluding the seal part forming face B. Displacement in the circumferential direction of the holding member 71 is regulated as a recessed part 71b to which the projection 11c is fitted is provided in an attachment part 71a of the holding member 71, and the projection 11c is engaged with the recessed part 71b in the circumferential direction. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a clutch release bearing incorporated in a clutch device of a vehicle including an automobile.

  The clutch release bearing device is interposed between an engine and a transmission of a manual transmission vehicle (MT vehicle), and moves in the axial direction as the clutch pedal is operated to turn the clutch on / off (power from the engine to the transmission). Transmission or interruption). For example, Patent Document 1 shown below discloses a direct cylinder type clutch release bearing device driven by hydraulic pressure.

  FIG. 6 shows a schematic structure around the clutch release bearing incorporated in the clutch release bearing device. A clutch release bearing 100 shown in FIG. 1 includes an outer ring 101 that is a rotating wheel, an inner ring 102 that is a stationary wheel, a ball 103 that is rotatably disposed between both wheels, and a cage 104 that holds the ball 103. This is the outer ring rotation type provided as the main component. In this clutch release bearing 100 (inner ring 102), the flange 101a provided at the front side (left side in the figure) end of the outer ring 101 which is a rotating wheel is always in contact with the rotating member (diaphragm spring) 111 of the clutch device. Further, it is urged to the front side by a preload spring 110 as urging means. The rear side (right side in the figure) end portion of the inner ring 102 that is a stationary wheel functions as a fixed portion of a holding member 112 that holds the preload spring 110 at the inner diameter portion, and the holding member 112 is located on the inner periphery of the fixed portion. It is press-fitted and fixed.

  Further, both end openings of the annular space 105 defined between the outer ring 101 and the inner ring 102 are sealed by seal members 106 and 107. Thereby, external leakage of a lubricant (for example, grease) filled in the annular space 105 and entry of foreign matters into the annular space 105 are prevented as much as possible.

JP 2006-289086 A

  In the clutch release bearing 100, the holding member 112 is basically not rotated because it is attached to the inner ring 102, that is, the stationary ring. However, since the holding member 112 is only fixed to the fixed portion of the inner ring 102 by press-fitting, the holding member 112 is circumferentially moved to the holding member 112 due to preload acting on the bearing 100, fluctuation of axial load, vehicle vibration, and the like. When a load is applied, the holding member 112 may rotate in the circumferential direction. When the holding member 112 rotates in the circumferential direction, the holding member 112 may be detached from the inner ring 102 due to vibration caused by the rotation. Such a situation causes damage to the preload spring 110 held on the inner diameter portion of the holding member 112. obtain. For this reason, it is desired that a fixing strength is secured between the inner ring 102 and the holding member 112 so as to stably maintain a predetermined mounting state. However, in the existing clutch release bearing 100, sufficient consideration is given to this. It is the actual situation that has not been made.

  In order to increase the fixing force of the holding member 112 with respect to the inner ring 102, for example, it has been studied to devise a structural device between the inner ring 102 and the holding member 112. In particular, it is necessary not to adversely affect the sealing performance of the rear side opening.

  In view of the above, an object of the present invention is to make it possible to stably maintain the fixed state of the stationary wheel and the holding member without adversely affecting the sealing performance in this type of clutch release bearing.

  The present invention, which has been made to solve the above technical problem, has a stationary wheel and an abutting portion that contacts the rotating member of the clutch device at one end in the axial direction, and rotates relative to the stationary wheel via a ball. A holding member holding a urging means for urging the stationary wheel toward the rotating member is provided at an end of the stationary wheel on the side opposite to the rotating member. Of the two openings formed between the two wheels, a seal portion is formed to seal the opening on the anti-rotation member side in cooperation with the seal member disposed in the opening on the anti-rotation member side. In the clutch release bearing, an engaging portion that engages with the holding member at least in the circumferential direction is provided on a surface of the fixed portion of the stationary wheel that faces the holding member. Here, “at least the circumferential direction” means that the holding member and the engaging portion are engaged only in the circumferential direction, and the holding member and the engaging portion are engaged in both the circumferential direction and the axial direction. It is a concept that includes cases.

  As described above, in the clutch release bearing according to the present invention, the fixed portion of the holding member provided on the stationary wheel is provided with the engaging portion that engages with the holding member at least in the circumferential direction. According to such a configuration, the circumferential displacement (rotation) of the holding member is effective even when a circumferential load is applied to the holding member due to a change in preload or axial load acting on the bearing, vibration of the vehicle, or the like. Can be deterred. Therefore, it is possible to avoid that the holding member is detached from the stationary wheel due to vibration caused by the rotation of the holding member, and further, damage to the urging means can be avoided. Further, among the fixed parts provided on the stationary ring, the engagement part is provided on the surface facing the holding member (the surface excluding the seal part forming surface that forms the seal part). There is no change in the structure of the seal portion formed in cooperation, and therefore the seal performance is not adversely affected. As described above, according to the present invention, in this type of clutch release bearing, it is possible to always stably maintain the mounting state of the stationary wheel and the holding member without deteriorating the sealing performance.

  When the seal structure as shown in FIG. 6 is adopted, when the internal pressure of the bearing increases as the temperature rises during the operation of the bearing, the seal lip provided at the inner diameter end of the seal member becomes the seal of the stationary ring. It is pressed against the part forming surface (the outer diameter surface of the inner ring 102 in FIG. 6). In this case, at first glance, it is considered that the sealing performance is further enhanced, and external leakage of grease and the like can be further reliably prevented. However, in this case, it is difficult to release the internal pressure, the internal pressure increases excessively, and the seal member may be removed. Moreover, there is a possibility that the rotational torque is unduly increased when the seal lip is strongly pressed against the seal portion forming surface.

  In view of such a situation, a seal lip extending in the axial direction is provided at one end in the radial direction of the seal member, and the end of the seal lip on the counter-rotating member side (one end on the bearing outer side) is a seal portion forming surface. It is desirable that the end portion of the seal lip on the rotating member side (one end on the bearing inner side) is not in contact with the seal portion forming surface. In this way, in a state where the internal and external pressures are balanced, the opening of the annular space can be reliably sealed by the contact seal structure on the bearing outer side and the non-contact seal structure on the bearing inner side, When the internal pressure increases, the seal lip is easily expanded, and the internal pressure can be easily released. Therefore, it is possible to avoid the removal of the seal member and the unduly increased rotational torque.

  The present invention described above can be preferably applied to a clutch release bearing in which a holding member is fixed to a fixed portion of a stationary wheel by simple means, for example, press fitting or caulking. In addition, the present invention can be preferably applied even when the holding member is fixed to the fixed portion of the stationary wheel via another member.

  Further, the present invention described above is a so-called outer ring rotation type clutch release bearing in which the stationary wheel is formed of an inner ring having an inner track, or a so-called inner ring rotation type in which the stationary wheel is formed of an outer ring having an outer track. It can be applied to any clutch release bearing. In the former case, the seal portion forming surface and the engaging portion can be provided on the outer diameter surface and the inner diameter surface of the inner ring, respectively. On the other hand, in the latter case, the seal portion forming surface and the engaging portion can be provided on the inner diameter surface and the outer diameter surface of the outer ring, respectively.

  In the above configuration, the engaging portion can be constituted by a protrusion (convex portion). In this case, if the concave portion into which the protrusion is inserted is formed in the holding member, the holding member in the circumferential direction with respect to the stationary wheel It is possible to regulate the circumferential displacement of the holding member only by positioning. Moreover, since the above protrusions and recesses can be formed easily and at low cost, an increase in the cost of the stationary wheel and the holding member due to the provision thereof is suppressed as much as possible. For example, when a projection as an engaging portion is provided on the inner diameter of the fixed portion of the inner ring, the projection can be formed by partially plastically deforming the inner diameter of the fixed portion of the inner ring.

  In addition, in the above configuration, the engaging portion can be formed by a depression. In this case, if a protrusion that can be fitted into the depression is formed on the holding member, the periphery of the holding member with respect to the stationary wheel is similarly formed. The displacement in the circumferential direction of the holding member can be restricted only by positioning in the direction.

  The clutch release bearing according to the present invention described above is suitable for a so-called hydraulically driven clutch release bearing device. The hydraulically driven clutch release bearing device is, for example, a movable body that is provided so as to be movable in the axial direction along the fixed body due to a volume variation of a volume variable chamber formed between the fixed body and the fixed body. And a clutch release bearing is attached to the movable body.

  As described above, according to the present invention, in this type of clutch release bearing, it is possible to always stably maintain the fixed state of the stationary wheel and the holding member without adversely affecting the sealing performance.

It is an expanded sectional view of a clutch release bearing concerning one embodiment of the present invention. It is a whole schematic sectional drawing of the clutch release bearing apparatus provided with the clutch release bearing shown in FIG. (A) is a schematic front view when the inner ring shown in FIG. 1 is viewed from the rear side, and (B) is a schematic front view when the holding member shown in FIG. 1 is viewed from the front side. (A) is an enlarged cross-sectional view of a clutch release bearing according to another embodiment, and (B) is a schematic front view when the holding member shown in (A) is viewed from the front side. It is a principal part expanded sectional view of the clutch release bearing which concerns on other embodiment. It is sectional drawing of the conventional clutch release bearing.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  First, FIG. 2 shows a schematic cross-sectional view of a clutch release bearing device 1 including a clutch release bearing 10 according to an embodiment of the present invention. The clutch release bearing device 1 is a direct cylinder type that switches ON / OFF of a clutch by being driven by hydraulic pressure, and includes a fixed body 30 attached to a casing 50 of a gear box, and a shaft along the fixed body 30. The main part is constituted by the movable body 20 that moves in the direction and forms the variable volume chamber 40 in cooperation with the fixed body 30 and the preload spring 70. A control hydraulic pressure generator (not shown) is connected to the variable volume chamber 40, and the chamber 40 is filled with oil as a control fluid. That is, in such a clutch release bearing device 1, the ON / OFF state of the clutch is switched by moving the movable body 20 in the axial direction along the fixed body 30 as the oil in the chamber 40 is pressurized or depressurized. It is done. In the following description, the left side in the figure is referred to as the front side and the right side in the figure is referred to as the rear side for the sake of convenience in order to indicate the directionality in the axial direction.

  The fixed body 30 has a guide tube 33 provided with a radial edge 34 constituting the bottom of the variable volume chamber 40 at the rear side end, and an outer diameter end portion of the radial edge 34 fitted in a groove portion 32 provided on the inner diameter surface. The substantially cylindrical outer main body 31 constitutes a main part.

  The movable body 20 includes a piston 22 that is externally fitted to the guide tube 33 via the piston support tube 21, and a clutch release bearing 10 that is attached to the outer diameter portion of the front side end of the piston 22. The The piston 22 is inserted into the inner periphery of the outer body 31 to form a variable volume chamber 40 with the fixed body 30. The piston support tube 21 extends slightly beyond one end on the front side of the piston 22, and a disc spring 23 is fitted into an annular groove 21a formed on the outer diameter surface of the extended portion. The disc spring 23 has a spring force for elastically supporting the clutch release bearing 10 (the inner ring 11 thereof) in cooperation with the piston 22. The clutch release bearing 10 is a spring force of the disc spring 23. Alignment is allowed by being pressed toward the piston 22 side.

  The preload spring 70 acts between the movable body 20 and the fixed body 30 (strictly, between the piston 22 and the outer body 31) to urge the clutch release bearing 10 to the front side. Thereby, in the clutch release bearing 10, the ring-shaped flange portion 12a provided at the front side end portion of the outer ring 12, which is a rotating wheel, always comes into contact with a diaphragm spring 60 as a rotating member of the clutch device. (See FIG. 2). The preload spring 70 is held (attached) to an inner diameter portion of a holding member 71 fixed to the rear side end portion of the inner ring 11 so as to cooperate with the inner ring 11 which is a stationary ring of the clutch release bearing 10.

  A clutch release bearing 10 shown in an enlarged manner in FIG. 1 is a so-called outer ring rotation type ball bearing, and can freely roll between an inner ring 11 that is a stationary ring, an outer ring 12 that is a rotating ring, and both wheels 11 and 12. A plurality of disposed balls 13 and a retainer 14 disposed between the wheels 11 and 12 and holding the balls 13 at predetermined intervals in the circumferential direction are provided as main components. An annular space K defined between the inner ring 11 and the outer ring 12 is filled with grease as a lubricant for internal lubrication.

  The inner ring 11 is a press-formed product of, for example, a steel plate, and has a cylindrical part 11a having an inner track, a radially inner side extending from a front side end part of the cylindrical part 11a, and an inner diameter end part including a piston 22 and a disc spring 23. And a ring-shaped flange portion 11b interposed therebetween. As described above, the holding member 71 is fixed to the rear side end portion of the inner ring 11 (rear side end portion of the cylindrical portion 11a). Further, as will be described later, the outer diameter surface of the rear side end portion of the cylindrical portion 11 a is a seal for sealing the rear side opening portion of the annular space K in cooperation with the inner diameter end portion of the second seal member 16. Forming part. Therefore, the rear side end portion of the cylindrical portion 11a functions as the fixed portion A referred to in the present invention, and the outer diameter surface 11a1 of the cylindrical portion 11a (strictly, the outer diameter surface 11a1 of the rear side end portion) seals. It functions as a part forming surface B.

  The outer ring 12 is a press-formed product of a steel plate like the inner ring 11 and extends radially inward from the front side end of the cylindrical part 12a having the outer raceway and the cylindrical part 12a, and is always in contact with the diaphragm spring 60. It has the flange part 12b as a contact part integrally.

  In order to prevent external leakage of grease filled in the annular space K and entry of foreign matter into the annular space K as much as possible, first and second seal members 15 are provided at the front and rear openings of the annular space K. , 16 are respectively arranged. The first seal member 15 includes a cored bar 17 and an elastic part 18 covering the surface of the cored bar 17, and its outer diameter end (outer diameter surface) is attached and fixed to the inner diameter surface of the cylindrical part 12 a of the outer ring 12. In this state, a contact seal portion S1 is configured by bringing the inner diameter end portion (seal lip) into contact with the front-side outer diameter surface 11a1 of the inner ring tubular portion 11a, and the front-side opening portion of the annular space K is sealed. .

  The second seal member 16 includes a metal core 17 and an elastic portion 18 covering the surface of the metal core 17, and the inner diameter of the second seal member 16 is fixed in a state where the outer diameter end is attached and fixed to the inner diameter surface of the cylindrical portion 12 a of the outer ring 12. The rear side opening is sealed in cooperation with the substantially cylindrical seal lip 19 formed of the elastic portion 18 provided at the end and the fixed portion A (seal portion forming surface B) of the inner ring 11. The seal lip 19 has a main lip 19a and a sub lip 19b at the rear side and front side ends, respectively. The main lip 19a contacts the seal portion forming surface B of the inner ring 11 to form the contact seal portion S1, and the sub lip 19b. The lip 19b is disposed so as to face the seal portion forming surface B through a minute gap to constitute a non-contact seal portion S2.

  The elastic portions 18 of the seal members 15 and 16 are made of a rubber material. As the rubber material, nitrile rubber (NBR), hydrogenated nitrile rubber (H-NBR), heat resistant nitrile rubber, polyacrylic rubber, ethylene propylene rubber (EPDM), fluorine rubber (FKM), etc. can be used. Among these, fluororubber, hydrogenated nitrile rubber or nitrile rubber having excellent wear resistance and water resistance is preferable. The elastic part 18 can also be formed of an elastic material other than a rubber material, for example, a thermoplastic elastomer.

  If the sealing structure as described above is employed, the opening portions at both ends of the annular space K can be reliably sealed in a state where the internal and external pressures are balanced. On the other hand, when the internal pressure increases, the seal lip 19 (main lip 19a) of the second seal member 16 expands, and the annular space K communicates with the atmosphere between the seal lip S and the seal portion forming surface B. A communicating path is formed. As a result, air can travel back and forth through this communication path, so that the internal / external pressure difference of the bearing can be eliminated at an early stage, and the internal / external pressure can be balanced. Therefore, also in the present embodiment in which the opening portions at both ends of the annular space K are sealed with the contact seal structure, the removal of the first or second seal member 15 or 16 due to the excessive increase in the internal pressure is effectively eliminated. . Further, it is possible to avoid an unreasonable increase in rotational torque.

  The holding member 71 has a stepped cylindrical shape as a whole, and a cylindrical mounting portion 71a provided at the front side end portion thereof is press-fitted into the inner periphery of the rear side end portion (fixed portion A) of the inner ring cylindrical portion 11a. Thus, the inner ring 11 is fixed.

  Here, the rear end portion of the cylindrical portion 11a of the inner ring 11, that is, the fixed portion A of the holding member 71 has an engaging portion that engages with the holding member 71, in this case, a protrusion 11c protruding radially inward. Provided. This protrusion 11c is a surface of the fixed portion A excluding the outer diameter surface 11a1 that functions as the seal portion forming surface B and is a surface facing the holding member 71, here, the inner diameter surface 11a2 and the circumferential direction of the rear end surface. It is formed by applying plastic working to a partial area. In the present embodiment, as shown in FIG. 3A, protrusions 11c are provided at two locations in the circumferential direction with different 180 ° phases.

  On the other hand, the attachment portion 71 a of the holding member 71 is provided with a recess 71 b into which the protrusion 11 c of the inner ring 11 can be fitted. In the present embodiment, as shown in FIG. 3B, recesses 71b are provided at four locations in the circumferential direction with different 90 ° phases. Each recess 71b is a notch that extends from the base end of the mounting portion 71a to the free end and opens to the inner and outer diameter surfaces of the mounting portion 71a. From the above configuration, when the mounting portion 71a of the holding member 71 is press-fitted into the inner periphery of the fixed portion A of the inner ring 11 while the phase of the recess 71b of the holding member 71 and the protrusion 11c of the inner ring 11 is adjusted, the protrusion 11c The recess 71b engages in the circumferential direction. Thereby, the circumferential displacement of the holding member 71 is restricted (the holding member 71 is prevented from rotating).

  In the present embodiment, as described above, the number of protrusions 11c provided on the inner ring 11 is different from the number of recesses 71b into which the protrusions 11c provided on the holding member 71 are fitted. Also good. However, if more recesses 71b are provided than the projections 11c as in the present embodiment, phase alignment in the circumferential direction of both can be simplified, and there is a merit that assembly workability can be improved. is there.

  As described above, in the present invention, the fixed portion A of the inner ring 11 that is a stationary wheel is provided with the protrusion 11c as an engaging portion that engages with the holding member 71 in the circumferential direction. According to such a configuration, even if a circumferential load is applied to the holding member 71 due to a preload acting on the clutch release bearing 10, fluctuations in the axial load, vehicle vibration, or the like, the circumferential direction of the holding member 71 Displacement (rotation) can be effectively suppressed. Therefore, it is possible to prevent the holding member 71 from moving out in the axial direction due to vibration caused by the rotation and coming off from the inner ring 11 as much as possible. Further, since the holding member 71 rotates and the rotational force is not applied to the preload spring 70 as the biasing means attached to the holding member 71, damage to the preload spring 70 is prevented as much as possible. The

  Further, the protrusion 11c as the engaging portion is formed by performing plastic working on the surface of the fixed portion A of the inner ring 11 facing the holding member 71, here, the inner diameter surface 11a2 and the rear side end surface. The sealing performance of the contact seal portion S1 and the non-contact seal portion S2 formed jointly with the second seal member 16 is not changed by forming the protrusion 11c. That is, although illustration is omitted, for example, when the holding member 71 is provided with a protrusion and the fixed portion A is provided with a notch (concave portion) as an engaging portion that engages with the protrusion of the holding member 71, the second If a notch (concave portion) is formed in a region facing the seal lip 19 provided at the inner diameter end of the seal member 16, an appropriate gap is formed between the seal lip 19 of the second seal member 16 and the seal portion forming surface B. This is because it becomes difficult to form a seal structure.

  In particular, in this embodiment, the seal lip 19 of the second seal member 16 extends to the rear side as compared with the conventional one shown in FIG. 6, and the portion extending to the rear side is connected to the seal portion forming surface B of the inner ring 11. Since the main lip 19a constituting the contact seal portion S1 is provided therebetween, the above problem is likely to occur. In other words, as in the present invention, the engaging portion that engages with the holding member 71 is the surface of the fixed portion A of the inner ring 11 that faces the holding member 71, that is, the surface excluding the seal portion forming surface B. By forming the first, the merit by adopting the second seal member 16 having the above-mentioned configuration for the first time can be surely obtained.

  FIG. 4A is a cross-sectional view showing a clutch release bearing 10 according to a second embodiment of the present invention. The main difference of the clutch release bearing 10 shown in FIG. 1 from that shown in FIG. 1 is that a through hole-like recess 71b is formed in the mounting portion 71a of the holding member 71 as shown in FIG. This is in that a projection 11c as an engaging portion provided in the fixed portion A of the inner ring 11 is fitted therein. In this case, since the protrusion 11c is engaged with the recess 71b both in the circumferential direction and in the axial direction, it is possible to reliably prevent the holding member 71 from being detached from the inner ring 11. Since other configurations are the same as those in the embodiment shown in FIG. 1, common reference numerals are given and redundant description is omitted.

  The clutch release bearing 10 according to the embodiment of the present invention has been described above, but the present invention is not limited to the above embodiment, and various modifications can be made.

  For example, in the clutch release bearing 10 according to the embodiment described above, both the seal members 15 and 16 are so-called contact types, but either one or both of the seal members 15 and 16 may be so-called contact types. good. In this case, although there is a possibility that the sealing performance is slightly lowered as compared with the above-described embodiment, there is an advantage that the torque can be reduced. Further, in the case of the non-contact type, the seal member can be composed of only the cored bar 17, so that the cost of the seal member and thus the clutch release bearing can be reduced compared to the contact type in which the elastic portion 18 needs to be provided. There is also an advantage that you can.

  Further, as shown in FIG. 5, the attachment portion 71 a of the holding member 71 is provided with a protrusion (convex portion) 71 c extending radially outward, and the attachment portion 71 a of the inner ring 11 is fixed to the inner diameter surface 11 a 2 of the fixed portion A. You may make it provide the hollow 11d which can insert the processus | protrusion 71c. As a result, the holding member 71 is prevented from rotating with respect to the inner ring 11, and the seal structure formed by the cooperation of the seal portion forming surface B configured by the outer diameter surface of the fixed portion A and the second seal member 16. The performance will not be adversely affected.

  In the above description, the case where the present invention is applied to the outer ring rotation type clutch release bearing 10 in which the inner ring 11 is a stationary ring has been described. However, the present invention also applies to a so-called inner ring rotation type clutch release bearing 10. Can be applied. Although illustration of the inner ring rotation type clutch release bearing is omitted, in this case, a contact portion that contacts the diaphragm spring 60 is provided at the front side end portion of the inner ring 11 that is a rotating wheel. Further, the rear side end portion of the tubular portion 12 a of the outer ring 12 that is a stationary wheel functions as the fixed portion A of the holding member 71. In this case, the holding member 71 is fixed to the outer diameter surface of the fixed portion A (outer ring tubular portion 12a) by, for example, press-fitting. Therefore, an engaging portion (for example, a protrusion) that engages with the holding member 71 is provided on the outer diameter surface of the fixed portion A. Further, a seal portion forming surface B that forms a seal portion with the second seal member 16 is provided on the inner diameter surface of the fixed portion A.

  Further, in the above, the present invention is applied when the holding member 71 is press-fitted and fixed to the stationary wheel. However, the present invention can be applied to the case where the stationary wheel and the holding member 71 are fixed by caulking, or through a separate part. Thus, the present invention can be preferably applied to the case where the stationary wheel and the holding member 71 are fixed.

  The present invention has been described above. However, the present invention is not limited to the above-described embodiment, and can of course be implemented in various forms without departing from the gist of the present invention. It is. The scope of the present invention is defined by the terms of the claims, and includes the equivalent meanings recited in the claims and all modifications within the scope.

DESCRIPTION OF SYMBOLS 1 Clutch release bearing apparatus 10 Clutch release bearing 11 Inner ring 11a Cylindrical part 11c Protrusion (engagement part)
12 outer ring 12b collar (contact part)
13 Ball 15 First seal member 16 Second seal member 17 Core 18 Elastic part 19 Seal lip 60 Diaphragm spring (rotary member of clutch device)
70 Preload spring (biasing means)
71 Holding member 71a Mounting part 71b Recessed part K Annular space S1 Contact seal part S2 Non-contact seal part

Claims (9)

The stationary wheel has a contact portion that contacts the rotating member of the clutch device at one end in the axial direction, and a rotating wheel that rotates relative to the stationary wheel via the ball. The fixed portion of the holding member that holds the urging means for urging the stationary wheel to the rotating member side is provided in the portion, and this fixed portion is counter-rotating of two openings formed between the two wheels. A clutch release bearing that forms a seal portion for sealing the member-side opening in cooperation with a seal member disposed in the opening on the counter-rotating member side,
A clutch release bearing, wherein an engagement portion that engages with the holding member at least in the circumferential direction is provided on a surface of the fixed portion of the stationary wheel that faces the holding member.   A cylindrical seal lip extending in the axial direction is provided at one end in the radial direction of the seal member, and the end of the seal lip on the counter-rotating member side is brought into contact with the seal portion forming surface of the fixed portion. The clutch release bearing according to claim 1, wherein an end portion of the rotating member side is not in contact with a seal portion forming surface of the fixed portion.   The clutch release bearing according to claim 1 or 2, wherein the holding member is fixed to the fixed portion of the stationary wheel by press-fitting.   The clutch release bearing according to claim 1 or 2, wherein the holding member is fixed to the fixed portion of the stationary wheel by caulking. The stationary ring is composed of an inner ring having an inner track,
The clutch release bearing according to any one of claims 1 to 4, wherein a seal portion forming surface is provided on an outer diameter surface of the inner ring and the engagement portion is provided on an inner diameter surface of the inner ring. The stationary ring is composed of an outer ring having an outer track,
The clutch release bearing according to any one of claims 1 to 4, wherein a seal portion forming surface is provided on an inner diameter surface of the outer ring and the engagement portion is provided on an outer diameter surface of the outer ring.   The clutch release bearing according to any one of claims 1 to 6, wherein the engaging portion is constituted by a protrusion, and a concave portion into which the protrusion is inserted is formed in the holding member.   The clutch release bearing according to any one of claims 1 to 6, wherein the engaging portion is configured by a recess, and a protrusion that can be fitted into the recess is formed on the holding member.   The clutch release bearing according to any one of claims 1 to 8, which is used for a hydraulically driven clutch release bearing device.

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