WO2009084355A1

WO2009084355A1 - Clutch release bearing and clutch release bearing device with the same

Info

Publication number: WO2009084355A1
Application number: PCT/JP2008/071715
Authority: WO
Inventors: Yasumitsu Ishikawa; Yasuyuki Katayama; Seiya Inoue
Original assignee: Ntn Corporation
Priority date: 2007-12-28
Filing date: 2008-11-28
Publication date: 2009-07-09

Abstract

A clutch release bearing in which, without making the shape of an outer ring complex, a seal member is prevented as much as possible from coming out of an opening between both rings. The clutch release bearing (10) has as main structural members the inner and outer rings (11, 12) and first and second seal members (15, 16). The inner and outer rings (11, 12) are arranged so as to be rotatable relative to each other with balls (13) retained between the inner and outer rings. The first and second seal members (15, 16) have outer-diameter ends fitted by pressure and fixed to an inner-diameter surface (12a1) of the outer ring (12) and seal the rear side and the front side, respectively, of an annular space formed between the inner and outer rings (11, 12). A retaining member (19) for restricting axially outward movement of an outer-diameter end (15a) of the first seal member (15) is fitted on the outer-diameter surface (12a2) of the outer ring (12).

Description

Clutch release bearing and clutch release bearing device including the same

The present invention relates to a clutch release bearing incorporated in a clutch device of a vehicle such as an automobile, and a clutch release bearing device including the same.

The clutch release bearing device is disposed between the engine and the transmission of the manual transmission vehicle, and moves in the axial direction in accordance with the operation of the clutch pedal to switch the clutch ON / OFF. As shown in FIG. 13, for example, the clutch release bearing incorporated in the clutch release bearing device includes an inner ring 301 and an outer ring 302 that are rotatably provided via rolling elements (balls) 305. A flange 304 is provided that contacts a rotating member (diaphragm spring) of the clutch device that does not. In addition, the annular space formed between the inner ring 301 and the outer ring 302 is filled with a lubricant (for example, grease), and both wheels are used to prevent external leakage of the filled grease and entry of foreign matter into the annular space.

Seal members

306 and 306 are disposed between them.

In the clutch release bearing 300 shown in FIG. 13, the outer diameter end portion of the seal member 306 is press-fitted and fixed to the inner diameter surface 303 of the outer ring 302 formed in a cylindrical surface extending in the axial direction. In such a configuration, it is possible to simplify the shape of the outer ring and to easily assemble the seal member 306, which is preferable in reducing the manufacturing cost. 13 is a so-called contact type in which the inner diameter end portion (seal lip) contacts the inner ring 301 over the entire circumference in a state where the outer diameter end portion is fixed to the outer ring 302. For example, see Patent Document 1).

The seal member assembled to the outer ring 302 in the above-described mode is not limited to the contact type described above, and the outer diameter end portion is fixed to the inner diameter surface of the outer ring. There is also a so-called non-contact type that faces through a directional gap (see, for example, Patent Document 2).
JP 2006-189086 A JP-A-11-270583

In recent years, various attempts have been made to improve the sealing performance between the inner and outer rings in order to stably maintain the desired bearing performance even under harsh usage environments. However, if the sealing performance is increased, the reaction is that the bearing internal pressure tends to increase due to rolling resistance during bearing operation, grease agitation resistance, etc., and the seal member is pulled out from the opening of the annular space due to the increase in the internal pressure. There is a risk of removal.

By the way, in order to improve the sealing performance (sealability), it is effective to use the sealing member as a contact type. As shown in FIG. 13, the contact-type seal member includes a cored bar 307 and a rubber covering portion 308 that covers the surface of the cored bar. In order to further improve the sealing performance when using such a seal member, it is conceivable to adopt means such as increasing the number of lips slidingly contacting the outer diameter surface of the inner ring or increasing the contact allowance of the lip. In this case, the bearing torque is remarkably increased, and the function of the clutch device may be lowered.

A first problem of the present invention is to provide a clutch release bearing that can prevent the sealing member from being pulled out of the opening between both wheels without complicating the outer ring shape, and boasts high sealing performance. It is to provide.

Also, a second object of the present invention is to provide a clutch release bearing with further improved sealing performance without increasing bearing torque.

In order to solve the first problem, according to the present invention, as a first configuration, a clutch release bearing having a contact portion with a rotating member of a clutch device is provided so as to be relatively rotatable through a rolling element. The inner ring and the outer ring, and a seal member that seals the opening of the annular space formed between the inner ring and the outer ring, and the outer diameter end of the seal member is press-fitted and fixed to the inner diameter of the opening of the outer ring. A clutch release bearing is provided in which an outer ring is fitted with a retaining member for restricting movement of the outer diameter end portion of the seal member to the outside in the axial direction.

As described above, if a retaining member that restricts the outer end of the outer diameter of the sealing member from moving outward in the axial direction is fitted to the outer ring, the sealing member can be accompanied with an increase in internal pressure without complicating the outer ring shape. It is possible to prevent the seal member from being pulled out of the opening as much as possible. In addition, since the tightening margin (diameter tightening margin in the radial direction) of the seal member with respect to the inner diameter of the opening of the outer ring can be reduced, deformation of the seal member can be suppressed or prevented, and a stable sealing function can be ensured. . In addition, since the axial movement of the seal member is restricted by the retaining member, it is possible to shorten the axial length of the region of the outer ring where the seal member is fixed, that is, to reduce the size of the bearing. it can.

The retaining member can include a cylindrical portion fitted to the outer diameter surface of the outer ring, and a flange portion extending from one end of the cylindrical portion and bent inward in the radial direction. In this case, by disposing the inner diameter end portion of the flange portion on the outer side in the axial direction of the outer diameter end portion of the seal member, the movement of the seal member to the outer side in the axial direction can be restricted. With this configuration, it is possible to effectively restrict the axial movement of the seal member (the outer diameter end portion) while suppressing the weight increase caused by providing the retaining member as much as possible. In addition, the inner diameter end portion of the flange portion of the retaining member can be arranged so that the tip thereof is in contact with the outer diameter end portion of the seal member. It can also arrange | position so that a clearance gap may be formed. In the former configuration, since the minute axial movement of the outer diameter end portion of the seal member can be restricted, it is preferable for stably maintaining the desired sealing performance.

The flange portion of the retaining member may be provided over the entire circumference (formed in a ring shape) or intermittently in the circumferential direction. In particular, the latter configuration is suitable because the bearing can be reduced in weight and size.

In order to prevent the retaining member itself from being detached from the outer ring, it is desirable to provide a step portion on the outer diameter surface of the outer ring and engage the end portion of the retaining member with the step portion.

The present invention is particularly suitable for a clutch release bearing that employs a so-called contact-type seal member in which an inner diameter end is brought into contact with the inner ring over the entire circumference. This is because the contact-type seal member can ensure high sealing performance as compared with the so-called non-contact type seal member, but the internal pressure is likely to rise due to the high sealability, and the outer ring is likely to be removed. .

In order to solve the first problem, in the present invention, as a second configuration, a clutch release bearing having an abutting portion with a rotating member of the clutch device, which is relatively rotatable via a rolling element. An inner ring and an outer ring provided, and a seal member that seals an opening of an annular space formed between the inner ring and the outer ring, and the outer diameter end of the seal member is press-fitted into the inner diameter surface of the outer ring extending in the axial direction The fixed member is composed of a cored bar and a rubber coated part covering the surface thereof, and the outer diameter end of the sealing member is a part of the outer peripheral surface of which the cored bar is exposed on the inner diameter surface of the outer ring. A clutch release bearing is provided in which a covering portion provided in a different axial direction from a part of the outer peripheral surface is pressed against the inner diameter surface of the outer ring.

By pressing the metal core constituting the seal member against the inner surface of the outer ring as described above, the fixing member can be fixed to the outer ring without increasing the shape of the outer ring, and the seal member can be increased as the internal pressure increases. Can be prevented as much as possible from moving in the axial direction. However, it is not easy to bring the metals into close contact with each other without any gaps, and therefore there remains a risk that defects such as grease leakage may occur from the gaps formed between them. In this regard, in the present invention, the core provided as a part of the outer diameter end portion of the seal member and the covering portion provided in a different axial position are in pressure contact with the inner diameter surface of the outer ring. The coating portion is closely attached to the inner diameter surface of the outer ring by its elastic restoring force. Therefore, even if a gap is formed between the outer ring and the metal core, it is possible to reliably prevent problems such as grease leakage. Furthermore, in order to realize the above-described effects, it is only necessary to appropriately set the formation position and thickness of the covering portion.

In the second configuration, the outer diameter end portion of the seal member is in contact with the inner diameter surface of the outer ring on the opening side of the annular space, and the core metal is disposed on the inner diameter surface of the outer ring on the opposite side of the annular space. It is desirable to press contact with. This is because the outer ring has a better adhesion to the inner surface of the outer ring than the core, and the sealing performance against entry of foreign matter from the outside is preferably the above-described mode.

The inner ring surface of the outer ring can be provided with a concave annular groove that is retracted to the outer diameter side from other places, and the annular groove and the covering portion can be fitted. With this configuration, since the annular groove and the covering portion are engaged in the axial direction, the axial movement of the seal member is more effectively prevented, and a predetermined sealing performance can be obtained more stably.

The covering portion of the sealing member is a known rubber material suitable for forming this type of sealing member, such as nitrile rubber (NBR), hydrogenated nitrile rubber (H-NBR), heat-resistant nitrile rubber, polyacrylic rubber, ethylene Although it can be formed using propylene rubber (EPDM), fluorine rubber (FKM), or the like, it is desirable to form with hydrogenated nitrile rubber or heat-resistant nitrile rubber that is particularly excellent in water resistance and wear resistance.

The second configuration according to the present invention is particularly suitable for a clutch release bearing that employs a so-called contact seal in which an inner diameter end portion of a seal member is brought into contact with an outer diameter surface of an inner ring. This is because the contact seal can ensure a high sealing performance as compared with a so-called non-contact seal, but because the sealing performance is high, the bearing internal pressure is likely to increase, and the axial movement of the seal member is likely to occur.

Further, the present invention is suitable for a clutch release bearing in which an outer ring on which an outer diameter end portion of a seal member is press-fitted and fixed is press-molded. This is because press molding is advantageous for lowering the manufacturing cost, but it is disadvantageous in forming each part with high precision, and a gap is easily formed between the seal member (the core metal) and the inner ring surface of the outer ring. .

In order to solve the above second problem, according to the present invention, there is provided a clutch release bearing having an abutting portion with a rotating member of a clutch device, and an inner ring and an outer ring provided so as to be relatively rotatable via rolling elements. And a seal member that seals the opening of the annular space formed between the inner ring and the outer ring, and a cover member that extends in the radial direction and faces the seal member in the axial direction at one end of the inner ring. A clutch release bearing is provided in which a labyrinth seal extending in a radial direction is formed between the cover member and the seal member.

In the above configuration, a labyrinth seal that is a non-contact seal is additionally provided on the outer side of the bearing with respect to the seal portion formed in cooperation with the seal member and the inner ring (or outer ring). Therefore, the sealing performance can be improved without increasing the bearing torque. Further, the member on one side forming the labyrinth seal is a cover material (separate from the inner ring) fixed to one end of the inner ring, and the cover material has a strength that can prevent the sealing member from being pulled out. It is sufficient if it is provided with the strength required for the main part of the inner ring. Therefore, the cover material can be formed of, for example, a thin steel plate or resin having a high degree of freedom in shape (easily processed), and thus this type of labyrinth seal can be simplified while reducing the weight of the bearing. Can be formed.

The labyrinth seal can be extended linearly in the radial direction. In the labyrinth seal having such a configuration, an annular ridge is provided on at least one of the cover member or the seal member, and at this ridge (between the ridge and the ridge provided on the counterpart member or the counterpart member, the ridge is provided. ) Can be formed.

The labyrinth seal can be extended linearly in the radial direction, or in a meandering manner in the radial direction. In this case, since the entire length of the labyrinth seal can be increased as compared with the above-described configuration, the sealing performance can be further improved. The labyrinth seal having such a configuration is provided with one or a plurality of annular protrusions on the cover material, and the seal member is provided with one or a plurality of annular protrusions with different radial positions from the annular protrusion of the cover material. It can be formed by the protrusion and the annular protrusion of the seal member. The form of the annular protrusion (position, number, cross-sectional shape, etc.) is arbitrary as long as the labyrinth seal can be formed, and the required sealing performance and bearing type (outer ring rotation type, inner ring rotation type) It can be set accordingly. Furthermore, the labyrinth seal extending in a meandering manner in the radial direction is not limited to one in which concave arcs and convex arcs are alternately continued.

The clutch release bearing according to the present invention described above includes, for example, a fixed body, and a movable body provided so as to be movable in the axial direction along the fixed body due to a volume variation of a variable volume chamber formed between the fixed body and the fixed body. The movable body is provided with a clutch release bearing. In short, it can be suitably used by being incorporated in a hydraulically driven clutch release bearing device.

As described above, according to the present invention, it is possible to prevent the sealing member from being pulled out from the opening between the two wheels as much as possible without complicating the outer ring shape. Thereby, it is possible to provide a clutch release bearing that boasts high sealing performance.

Further, according to the present invention, it is possible to provide a clutch release bearing with further improved sealing performance without increasing bearing torque.

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

FIG. 1 is a clutch release bearing device incorporating a clutch release bearing to which the first configuration of the present invention is applied, and more specifically, a cross-sectional view showing an example of a hydraulically driven clutch release bearing device driven by hydraulic pressure. It is. The figure shows a state in which the clutch is engaged. A clutch release bearing device 1 shown in FIG. 1 is provided with a fixed body 30 attached to a casing 50 of a gear box, and is provided so as to be movable in the axial direction with respect to the fixed body 30. The main part is composed of the movable body 20 forming 40. 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. For convenience, 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.

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 one end on the rear side, and an outer diameter side end of the radial edge 34 fitted in a groove 32 provided on the inner diameter surface. A main portion is constituted by the cylindrical outer body 31.

The movable body 20 is disposed on the piston 22 that is externally fitted to the guide tube 33 via the piston support tube 21 and the front end of the piston 22, and is a rotary member of a clutch device (not shown) (hereinafter referred to as a diaphragm spring). And a clutch release bearing 10 having a contact portion with the main component. The piston 22 projects outwardly from the outer cylindrical portion 22a and the inner cylindrical portion 22b extending in the axial direction, an annular portion 22c that connects the two cylindrical portions at one end on the front side, and a base end of the outer cylindrical portion 22a. And a protrusion 22d. Of the piston 22, the inner cylindrical portion 22 b is inserted into the inner periphery of the outer body 31 to form a variable volume chamber 40 with the fixed body 30, and the protrusion 22 d is disposed on the outer periphery of the outer cylindrical portion 22 a. It plays a role of locking one end on the front side of the preload spring 24. One end on the front side of the piston support tube 21 extends slightly beyond the annular portion 22c of the piston 22, and a centering ring (disc spring) 23 is fitted into an annular groove 21a formed on the outer diameter surface of the extended portion. Is done. The aligning ring 23 has a spring force for elastically supporting the clutch release bearing 10 (the inner ring 11 thereof) in cooperation with the annular portion 22c of the piston 22, and the clutch release bearing 10 Alignment is allowed by being pressed toward the piston 22 by the spring force of the ring 23.

In the clutch release bearing device 1 configured as described above, the behavior of each member when the clutch is released will be briefly described. First, when the oil in the variable volume chamber 40 is pressurized by a hydraulic pressure generator (not shown), the volume of the variable volume chamber 40 increases, and the piston 22 moves to the front side accordingly. The piston 22 operates the clutch release bearing 10 during movement. When the clutch release bearing 10 is actuated, a thrust force is applied to a diaphragm spring (not shown), thereby releasing the clutch.

Hereinafter, the clutch release bearing 10 which is the gist of the present invention will be described in detail. The clutch release bearing 10 in the illustrated example is a so-called angular ball bearing, and as shown in an enlarged view in FIG. 2, an inner ring 11 and an outer ring 12 provided so as to be relatively rotatable via a plurality of rolling elements (balls) 13. , A cage 14 that is incorporated between the two wheels and holds the balls 13 at predetermined intervals in the circumferential direction, and first and second openings respectively disposed in the rear side and front side openings of the annular space formed between the two wheels.

Seal members

15 and 16 and a retaining member 19 that is fitted to the outer diameter surface of the outer ring 12 and restricts the movement of the first seal member 15 in the axially outer side (rear side) are formed between the two wheels. The annular space is filled with grease as a lubricant. The illustrated clutch release bearing 10 is an outer ring rotating type bearing in which an inner ring 11 is a stationary side and an outer ring 12 is a rotating side.

The inner ring 11 is a press-formed product of a steel plate, has a substantially cylindrical shape extending in the axial direction, a cylindrical portion 11a in which a rolling surface of the ball 13 is formed on the outer diameter surface, and one end on the front side of the cylindrical portion 11a. From the rear end of the cylindrical portion 11a to the outer diameter side, the first flange portion 11b extending between the annular portion 22c of the piston 22 and the aligning ring 23. Is integrally formed with a second flange portion 11c facing the rear end surface of the first seal member 15 via an axial gap. The rear side end surface of the first flange portion 11b is formed in a flat surface in a direction perpendicular to the axis, corresponding to the end surface shape of the annular portion 22c of the piston 22 with which the first flange portion 11b abuts. In addition, the 2nd collar part 11c can also be comprised by fixing another member of substantially the same shape to the rear side one end of the cylindrical part 11a among the components of the inner ring | wheel 11.

The outer ring 12 is a press-formed product of a steel plate like the inner ring 11, has a substantially cylindrical shape extending in the axial direction, and a cylindrical portion 12a in which the rolling surface of the ball 13 is formed on the inner diameter surface 12a1, and the cylindrical portion 12a. It has a flange 12b that extends from one end of the front side to the inner diameter side and serves as a contact portion with a diaphragm spring (not shown). Of the inner diameter surface 12a1 of the cylindrical portion 12a, a region where both the

seal members

15 and 16 are fixed is formed on a cylindrical surface parallel to the axis. The flange portion 12b is always in contact with the diaphragm spring by a preload spring 24 acting between the outer body 31 and the flange portion 22d of the piston 22, and its cross-sectional shape is in line contact with the diaphragm spring (point contact in the sectional view). ), A convex arc shape protruding to the front side.

As the steel plate for forming the inner ring 11 and the outer ring 12, for example, a carburized steel plate can be used. Examples of the carburized steel that can be used include nickel chrome steel (SNC), nickel chrome molybdenum steel (SNCM), chrome steel (SCr), and chrome molybdenum steel (SCM). In addition, either one or both of the inner ring 11 and the outer ring 12 may be a press-formed product of a steel plate as described above, a forged product, or a machined product such as cutting.

The second seal member 16 is composed of a core bar 17 having a substantially L-shaped cross section and a rubber cover 18 vulcanized and bonded to cover the surface of the core bar 17. The second seal member 16 has an inner diameter of the outer ring 12 by pressing the covering portion 18 constituting the outer diameter end portion 16a against the inner diameter surface 12a1 (strictly speaking, the inner diameter surface on the front side) of the outer ring cylindrical portion 12a. It is press-fitted and fixed to the surface 12a1. When the outer diameter end portion 16a is press-fitted and fixed to the inner diameter surface 12a1 of the outer ring 12, the inner diameter end portion 16b (lip) contacts the outer diameter surface of the inner ring 11 over the entire circumference, and a seal portion S formed of a so-called contact seal. Is formed. Thereby, the front side opening part of the annular space formed between both the

wheels

11 and 12 is sealed.

Similar to the second seal member 16, the first seal member 15 is composed of a core bar 17 having a substantially L-shaped cross section, and a rubber cover 18 that is vulcanized and bonded to cover the surface of the core bar 17. Thus, the covering portion 18 constituting the outer diameter end portion 15a is press-fitted to the inner diameter surface 12a1 of the outer ring 12 by being brought into pressure contact with the inner diameter surface 12a1 (strictly speaking, the inner diameter surface on the rear side) of the outer ring cylindrical portion 12a. Is done. When the outer diameter end portion 15a is press-fitted and fixed to the inner diameter surface 12a1 of the outer ring 12, the inner diameter end portion 15b (lip) contacts the outer diameter surface of the inner ring 11 over the entire circumference, and a seal portion S formed of a so-called contact seal. Form. Thereby, the rear side opening part of the annular space formed between the two

wheels

11 and 12 is sealed.

As a rubber material used for forming the covering portion 18 constituting both the

seal members

15 and 16, a known rubber material having excellent wear resistance, for example, nitrile rubber (NBR), hydrogenated nitrile rubber (H-NBR), heat resistance Nitrile rubber, polyacrylic rubber, ethylene propylene rubber (EPDM), fluorine rubber (FKM), etc. can be used. Among these, hydrogenated nitrile rubber or heat-resistant nitrile rubber exhibiting excellent water resistance (weather resistance) characteristics. Is particularly preferred.

The retaining member 19 has a substantially cylindrical shape extending in the axial direction, and includes a cylindrical portion 19a fitted to the outer diameter surface 12a2 of the outer ring 12 (cylindrical portion 12a), and one end (rear side end) of the cylindrical portion 19a. Part) and a flange part 19b extending radially inward. In the present embodiment, the flange portion 19 b has a ring shape as shown in FIG. 3A, and the inner diameter end portion 19 b 1 is located on the outer side in the axial direction of the outer diameter end portion 15 a of the first seal member 15. An inner diameter end portion 19b1 of the flange portion 19b is bent to the front side, and a tip thereof is in contact with an outer diameter end portion 15a of the first seal member 15 (strictly speaking, an outer peripheral corner portion of the outer diameter end portion 15a). Yes.

The retaining member 19 is fixed to the outer ring 12 by fitting a steel plate material press-molded in the above-described manner to the outer diameter surface 12a2 of the outer ring 12. In the present embodiment, a stepped portion 12a3 having a tapered surface that is gradually reduced in diameter toward the front side is formed on the outer diameter surface 12a2 of the tubular portion 12a of the outer ring 12, and the cylinder of the retaining member 19 is formed on the stepped portion 12a3. By fitting the other end (front end portion) of the shape portion 19a, the retaining member 19 is effectively prevented from being detached from the outer ring 12. For example, after fitting a cylindrical steel plate material extending in the axial direction to the outer diameter surface 12 a 2 of the outer ring 12, the steel plate material is bent along the shape of the outer ring 12, thereby preventing the retaining member 19. Formation and assembly to the outer ring 12 can also be performed. In order to secure the fixing strength of the retaining member 19 with respect to the outer ring 12, an adhesive may be interposed therebetween.

As described above, if the retaining member 19 that restricts the outer diameter end portion 15a of the first seal member 15 from moving outward in the axial direction is fitted to the outer ring 12 (the outer diameter surface 12a2 thereof), the outer ring 12 It is possible to prevent the first seal member 15 from moving in the axial direction as the internal pressure rises without complicating the shape, and thus to prevent the first seal member 15 from being pulled out of the opening between the two wheels as much as possible. be able to. In particular, in the present embodiment, since both the sealing

members

15 and 16 are so-called contact types that can ensure a relatively good sealing performance, the internal pressure is reduced by the rolling resistance of the balls 13 during the bearing operation. It is easy to rise, and therefore there is a high risk of the seal member (particularly the first seal member 15) being pulled out. However, by applying the configuration of the present invention, it is possible to reliably prevent the outer ring 12 from being pulled out.

Although not clearly shown in the illustrated example, the outer diameter end portion of the first seal member 15 can be prevented as much as possible by adopting the above-described configuration. The axial length of 15a, that is, the length of the fixed portion of the first seal member 15 with respect to the outer ring 12, and the axial length of the rear-side inner diameter surface 12a1 of the outer ring 12 can be shortened. As a result, the bearing can be made compact.

Also, since the removal of the first seal member 15 can be prevented as much as possible, the radial interference between the first seal member 15 and the outer ring 12 can be made smaller than before. Thereby, the deformation | transformation of the rear side edge part of the outer ring | wheel 12 (cylindrical part 12a) which is a press-molded product can be suppressed or prevented.

The extension dimension of the retaining member 19 to the inner diameter side of the flange portion 19b is arbitrary as long as the axial movement of the first seal member 15 (the outer diameter end portion 15a thereof) can be restricted. As the length increases, the retaining member 19 and thus the clutch release bearing 10 become heavier. In this respect, in the present embodiment, the flange portion 19 is extended to the inner diameter side so that the inner diameter end portion 19b1 is positioned on the outer side in the axial direction of the outer diameter end portion 15a of the first seal member 15, so that the first seal While preventing the removal of the member 15 as much as possible, the weight of the clutch release bearing 10 due to the provision of the retaining member 19 can be suppressed as much as possible.

Further, since the inner diameter end portion 19b1 of the flange portion 19b of the retaining member 19 is brought into contact with the outer peripheral corner portion of the first seal member 15, the movement of the first seal member 15 to the rear side opening is effective. The desired sealing performance is stably maintained.

Although the case where the flange portion 19b of the retaining member 19 is formed in a ring shape (formed over the entire circumference) has been described above, it is possible to prevent the first seal member 15 from being detached. For example, the flange portion 19b can be formed intermittently in the circumferential direction as shown in FIG. 3B. With this configuration, it is possible to reduce the weight of the retaining member 19 and thus the clutch release bearing 10 as compared to the above-described embodiment.

In the above description, the case where the retaining member 19 is formed of a metal material such as a steel plate has been described. However, the configuration of the present invention is not limited to this. That is, the retaining member 19 can be formed of a resin material or ceramics as long as the first seal member 15 can be prevented from moving in the axial direction (withdrawal).

In the above description, the case where the first configuration according to the present invention is applied to the outer ring rotation type clutch release bearing has been described. For example, the inner ring rotation type bearing structure as described in Patent Document 2 above is described. More specifically, in the case where a bearing structure is formed in which a flange portion that is a contact portion with a diaphragm spring is formed at one end on the front side of the inner ring 11 and a flange portion is not provided on one end on the front side of the outer ring 12. The flange portion 19b fits the retaining member 19 provided at one end on the front side of the cylindrical portion 19a to the outer diameter surface of the outer ring 12, whereby the front side opening is sealed with the flange portion 19b. It is also possible to prevent the second seal member 16 from being removed.

In the above description, the clutch release bearing in which both of the

seal members

15 and 16 are so-called contact type has been described. However, either or both of the

seal members

15 and 16 are so-called non-contact type clutch release bearings. Of course, it is possible to apply the configuration of the present invention to the bearing.

FIG. 4 is a clutch release bearing device incorporating a clutch release bearing to which the second configuration of the present invention is applied. In detail, FIG. 4 is a sectional view showing an example of a hydraulically driven clutch release bearing device driven by hydraulic pressure. is there. This figure shows a state in which the clutch is engaged. A clutch release bearing device 101 shown in the figure is provided with a fixed body 130 attached to a casing 150 of a gear box, and is provided so as to be movable in the axial direction with respect to the fixed body 130. The movable body 120 forming 140 forms a main part. A control hydraulic pressure generator (not shown) is connected to the variable volume chamber 140, and the chamber 140 is filled with oil as a control fluid. For convenience, 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.

The fixed body 130 has a guide tube 133 provided with a radial edge 134 constituting the bottom of the variable volume chamber 140 at one end on the rear side, and an outer diameter side end of the radial edge 134 fitted in a groove 132 provided on the inner diameter surface. A main part is constituted by the cylindrical outer body 131.

The movable body 120 is disposed at the front end of the piston 122 that is externally fitted to the guide tube 133 via the piston support tube 121, and is in contact with a rotating member (diaphragm spring) of a clutch device (not shown). A clutch release bearing 110 having a portion is provided as a main constituent member. The piston 122 includes an outer cylindrical portion 122a and an inner cylindrical portion 122b that extend in the axial direction, an annular portion 122c that connects both cylindrical portions at one end on the front side, and an outer diameter side that extends from the base end portion of the outer cylindrical portion 122a. And an existing flange portion 122d. Of the piston 122, the inner cylindrical portion 122b is inserted into the inner periphery of the outer main body 131 to form a variable volume chamber 140 between the fixed body 130 and the flange portion 122d is an outer periphery of the outer cylindrical portion 122a (piston 122). It plays the role which latches the front side one end of the preload spring 124 arrange | positioned by this. One end on the front side of the piston support tube 121 extends slightly beyond the annular portion 122c of the piston 122, and a centering ring (disc spring) 123 is fitted into an annular groove 121a formed on the outer diameter surface of the extended portion. Is done. The alignment ring 123 has a spring force for elastically supporting the clutch release bearing 110 (the inner ring 111 thereof) in cooperation with the annular portion 122c of the piston 122. The clutch release bearing 110 Alignment is allowed by being pressed toward the piston 122 by the spring force of the ring 123.

In the clutch release bearing device 101 configured as described above, the behavior of each member when the clutch is released will be briefly described. First, when the oil in the variable volume chamber 140 is pressurized by a hydraulic pressure generator (not shown), the volume of the variable volume chamber 140 increases, and accordingly, the piston 122 moves to the front side. The piston 122 operates the clutch release bearing 110 during movement. When the clutch release bearing 110 is operated, a thrust force is applied to a diaphragm spring (not shown), thereby releasing the clutch.

Hereinafter, the clutch release bearing 110 will be described in detail. The clutch release bearing 110 in the illustrated example is a so-called angular ball bearing, and as shown in an enlarged view in FIG. 5, an inner ring 111 and an outer ring 112 provided so as to be relatively rotatable via a plurality of rolling elements (balls) 113. A cage 114 that is incorporated between the two wheels and holds the balls 113 at predetermined intervals in the circumferential direction, and first and second seal members 115 disposed at both ends of an annular space formed between the two wheels. 116, and an annular space formed between the two wheels is filled with grease as a lubricant. The illustrated clutch release bearing 110 is an outer ring rotation type bearing in which the inner ring 111 constitutes a stationary side and the outer ring 112 constitutes a rotation side.

The inner ring 111 is a press-molded product obtained by subjecting a molded product obtained by pressing a steel plate to a heat treatment from the viewpoint of suppressing manufacturing costs. The inner ring 111 has an inner diameter side from a front-side end of a substantially cylindrical portion extending in the axial direction. A first flange 111a having a distal end portion interposed between the annular portion 122c of the piston 122 and the aligning ring 123; a cylindrical portion extending from the rear side end to the outer diameter side; The rear end of the seal member 115 and the second flange 111b facing each other with a gap in the axial direction are integrally provided. The rear side end surface of the first flange portion 111a is formed in a flat surface in a direction perpendicular to the axis line, corresponding to the shape of the end surface of the annular portion 122c of the piston 122 with which the first flange portion 111a contacts. In addition, the 2nd collar part 111b can also be comprised by fixing another member to the rear side end of a cylindrical part.

The outer ring 112 is a press-formed product of a steel plate like the inner ring 111, and extends from the one end on the front side of the substantially cylindrical portion extending in the axial direction to the inner diameter side, and a flange portion 112a serving as a contact portion with a diaphragm spring (not shown). Are integrated. Of the inner diameter surface 112b of the outer ring 112, a region where both the

seal members

115 and 116 are fixed is formed in a cylindrical surface extending in the axial direction. The flange portion 112a of the outer ring 112 is always in contact with the diaphragm spring by a preload spring 124 acting between the outer main body 131 and the flange portion 122d of the piston 122, and its cross-sectional shape is in line contact with the diaphragm spring (cross-sectional view). In this case, a convex arc shape projecting to the front side is formed so as to make point contact.

In addition, as a steel plate for forming the inner ring 111 and the outer ring 112, for example, a carburized steel plate can be used. Examples of the carburized steel that can be used include nickel chrome steel (SNC), nickel chrome molybdenum steel (SNCM), chrome steel (SCr), and chrome molybdenum steel (SCM). In addition, either or both of the inner ring 111 and the outer ring 112 can be a press-formed product of a steel plate as described above, a forged product, or a machined product such as cutting.

As shown in FIG. 5, the second seal member 116 includes a core metal 117 having a substantially L-shaped cross section, and a rubber covering portion 118 vulcanized and bonded to cover the surface of the core metal 117. The outer diameter end portion 119 is press-fitted and fixed to the inner diameter surface 112b (strictly speaking, the inner diameter surface on the front side) of the outer ring 112 extending in the axial direction. Specifically, the outer diameter end portion 119 of the second seal member 116 is covered with the covering portion 118 on the entire surface of the core metal 117, and the outer ring 112 is brought into pressure contact with the inner diameter surface 112 b of the outer ring 112. The inner surface 112b is press-fitted and fixed. When the outer diameter end portion 119 is press-fitted and fixed to the inner diameter surface 112b of the outer ring 112, the lip provided at the inner diameter end portion comes into contact with the outer diameter surface of the inner ring 111 over the entire circumference, and a seal composed of a so-called contact seal. Part S1 is formed. Thereby, the front side opening of the annular space formed between the two

wheels

111 and 112 is sealed.

Similar to the second seal member 116, the first seal member 115 includes a core metal 117 having a substantially L-shaped cross section, and a rubber covering portion 118 that is vulcanized and bonded to cover the surface of the core metal 117. The outer diameter end portion 119 is press-fitted and fixed to the inner diameter surface 112b (strictly speaking, the inner diameter surface on the rear side) of the outer ring 112 extending in the axial direction. The outer diameter end portion 19 of the first seal member 115 has a covering portion 118 formed so as to cover a part of the outer peripheral surface of the core metal 117 on the opening side (rear side). Therefore, the press-fitting and fixing of the first seal member 115 to the inner diameter surface 112b of the outer ring 112 is performed by using the covering portion 118 formed in a predetermined region on the opening side (rear side) and in a predetermined region on the opposite opening side (front side). The exposed core metal 117 is pressed against the inner diameter surface 112b of the outer ring 112, respectively. When the outer diameter end portion 119 is press-fitted and fixed to the outer ring inner diameter surface 112b, the lip provided at the inner diameter end portion comes into contact with the outer diameter surface of the inner ring 111 over the entire circumference, and a seal composed of a so-called contact seal. Part S1 is formed. Thereby, the rear side opening of the annular space formed between the two

wheels

111 and 112 is sealed.

The rubber material used for forming the covering portion 118 may be a known rubber material suitable for forming this type of seal member, for example, 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, but hydrogenated nitrile rubber or heat-resistant nitrile rubber with excellent water resistance (weather resistance) and wear resistance Is particularly preferable, and is formed using hydrogenated nitrile rubber in this embodiment.

As described above, of the outer diameter end portion 119 of the first seal member 115, the cored bar 117 exposed in a partial region (externally), and the covering portion 118 provided with a different axial position from this. If both are pressed against the inner diameter surface 112b of the outer ring 112, the fixing strength of the outer diameter end portion 119 of the first seal member 115 with respect to the outer ring 112 is set so that only the covering portion 118 is pressed against the inner diameter surface 112b of the outer ring 112. Compared to the conventional configuration, it can be increased.

However, it is difficult to make the outer ring 112 and the metal core 117, both of which are made of a metal material, adhere to each other without any gaps. In the present embodiment in which the outer ring 112 is a press-molded product, in particular, between the two. A gap is likely to occur. In this regard, in the present invention, the rubber cover 118 provided at a different axial position from the core metal 117 constituting a part of the outer diameter end 119 of the first seal member 115 is provided with the inner diameter surface 112 b of the outer ring 112. In this pressure contact portion, the covering portion 118 is in close contact with the inner diameter surface 112b of the outer ring 112 in an excellent manner by its elastic restoring force. In particular, as in the present embodiment, the covering portion 118 is pressed against the inner diameter surface 112 b of the outer ring 112 on the opening (rear opening) side of the annular space formed between the inner ring 111 and the outer ring 112. This is effective against the entry of foreign matter from the outside, and is suitable for satisfying the high muddy water resistance demanded in recent years.

Furthermore, the above-described operational effects can be obtained simply by appropriately setting the formation position, thickness, and the like of the covering portion 118 that is vulcanized and bonded to the core metal 117, and it is not necessary to complicate the shape of the outer ring 112. From the above, according to the present invention, due to the above, there is insufficient fixing force between the outer ring 112 and the outer diameter end portion 119 of the first seal member 115, and the first seal against the inner diameter surface 112b of the outer ring 112. With a simple structure, it is possible to reliably prevent the deterioration of the sealing performance due to the poor adhesion of the outer diameter end portion 119 of the member 115, that is, the occurrence of unexpected problems such as grease leakage and foreign substance intrusion.

The case where the outer diameter end portion 119 of the first seal member 115 is press-fitted and fixed to the inner diameter surface 112b of the outer ring 112 formed in a straight cylindrical surface extending in the axial direction has been described above. For example, FIG. As shown in the figure, a concave annular groove 112c that is retracted to the outer diameter side from the other part is provided in the vicinity of the rear side opening portion in the inner diameter surface 112b of the outer ring 112, and the first seal member 115 is provided in the annular groove 112c. It is also possible to fit the covering portion 118 constituting the outer diameter end portion 119. With such a configuration, since the annular groove 112c and the covering portion 118 are engaged in the axial direction, the axial movement of the first seal member 115 is more effectively prevented, and a predetermined sealing performance can be obtained more stably. It is done.

In the present embodiment, the second seal member 116 has a part of one end face (front side end face) in contact with the flange 112a of the outer ring 112, and therefore, the second seal member accompanying an increase in internal pressure or the like. The movement of 116 toward the opening (front opening) is prevented. For this reason, the outer diameter end portion 119 of the second seal member 116 has the same configuration as the conventional one, but this type of backup function cannot be obtained due to the shape of the outer ring 112 and the like, and the same shaft as the first seal member 115 is used. When the direction movement is likely to occur, the outer diameter end portion 119 of the second seal member 116 can be configured similarly to the outer diameter end portion 119 of the first seal member 115.

In the above description, the clutch release bearing in which both the

seal members

115 and 116 are so-called contact type has been described. However, either or both of the

seal members

115 and 116 are so-called non-contact type clutch release bearings. It is also possible to apply the configuration of the present invention to the bearing.

In the above description, the clutch release bearing in which the outer ring 112 is provided with the flange that is in contact with the diaphragm spring has been described. However, the flange extending to the outer diameter side is provided at one end (one end on the front side) of the inner ring 111. Of course, it is also possible to apply the configuration of the present invention to a clutch release bearing provided with this flange portion as a contact portion with a diaphragm spring.

FIG. 7 is a cross-sectional view showing an example of a clutch release bearing device incorporating a clutch release bearing to which the third configuration of the present invention is applied, and more specifically, an example of a hydraulically driven clutch release bearing device driven by hydraulic pressure. This figure shows a state in which the clutch is engaged. A clutch release bearing device 201 shown in FIG. 1 is provided with a fixed body 230 attached to a casing 250 of a gear box, and is provided so as to be movable in the axial direction with respect to the fixed body 230. The main part is composed of the movable body 220 forming 240. A control hydraulic pressure generator (not shown) is connected to the variable volume chamber 240, and the chamber 240 is filled with oil as a control fluid. For convenience, 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.

The fixed body 230 has a guide tube 233 provided with a radial edge 234 constituting the bottom of the variable volume chamber 240 at one end on the rear side, and an outer diameter side end of the radial edge 234 fitted in a groove 232 provided on the inner diameter surface. The main part is composed of the cylindrical outer body 231.

The movable body 220 is disposed on the piston 222 that is externally fitted to the guide tube 233 via the piston support tube 221 and a front end of the piston 222, and is a rotary member of a clutch device (not shown) (hereinafter referred to as a diaphragm spring). And a clutch release bearing 210 having a contact portion with the main component. The piston 222 protrudes from the base end of the outer cylindrical portion 222a to the outer diameter side, the outer cylindrical portion 222a and the inner cylindrical portion 222b extending in the axial direction, the annular portion 222c connecting the two cylindrical portions at one end on the front side. And a protrusion 222d. Of the piston 222, the inner cylindrical portion 222b is inserted into the inner periphery of the outer body 231 to form a variable volume chamber 240 with the fixed body 230, and the protrusion 222d is disposed on the outer periphery of the outer cylindrical portion 222a. It plays a role of locking one end on the front side of the preload spring 224. One end on the front side of the piston support tube 221 extends slightly beyond the annular portion 222c of the piston 222, and a centering ring (disc spring) 223 is fitted into an annular groove 221a formed on the outer diameter surface of the extended portion. Is done. The aligning ring 223 has a spring force for elastically supporting the clutch release bearing 210 (the inner ring 211 thereof) in cooperation with the annular portion 222c of the piston 222. Alignment is allowed by being pressed toward the piston 222 by the spring force of the ring 223.

In the clutch release bearing device 201 configured as described above, the behavior of each member when the clutch is released will be briefly described. First, when oil in the variable volume chamber 240 is pressurized by a hydraulic pressure generator (not shown), the volume of the variable volume chamber 240 increases, and the piston 222 moves to the front side accordingly. The piston 222 operates the clutch release bearing 210 during movement. When the clutch release bearing 210 is operated, a thrust force is applied to a diaphragm spring (not shown), thereby releasing the clutch.

Hereinafter, the clutch release bearing 210 will be described in detail. The clutch release bearing 210 of the illustrated example is a so-called angular ball bearing, and as shown in an enlarged view in FIG. 8, an inner ring 211 and an outer ring 212 provided so as to be relatively rotatable via a plurality of rolling elements (balls) 213. , A cage 214 which is incorporated between the two wheels and holds the balls 213 at predetermined intervals in the circumferential direction, and first and second openings respectively disposed in the rear side and front side openings of the annular space formed between the two wheels.

Seal members

215 and 216 and a cover member 219 fixed to one end on the rear side of the inner ring 211 are provided. An annular space formed between the two

wheels

211 and 212 is filled with grease as a lubricant. In the illustrated example, the clutch release bearing 210 is an outer ring rotation type bearing in which the inner ring 211 is stationary and the outer ring 212 is rotating.

The inner ring 211 is, for example, a press-formed product of a steel plate, has a substantially cylindrical shape extending in the axial direction, a cylindrical portion 211a in which a rolling surface 211a1 of the ball 213 is formed on the outer diameter surface, and a front surface of the cylindrical portion 211a. A flange portion 211b that extends radially inward from one end of the side and has a tip portion interposed between the annular portion 222c of the piston 222 and the aligning ring 223 is integrally provided. The rear side end surface of the flange portion 211b is formed in a flat surface in a direction perpendicular to the axis line, corresponding to the end surface shape of the annular portion 222c of the piston 222 with which the flange portion 211b abuts.

The outer ring 212 is a press-formed product of a steel plate like the inner ring 211, has a substantially cylindrical shape extending in the axial direction, and a cylindrical portion 212a in which a rolling surface 212a1 of the ball 213 is formed on the inner diameter surface, and the cylindrical portion 212a. A flange portion 212b that extends from one end of the front side to the inner diameter side and serves as a contact portion with a diaphragm spring (not shown) is integrally provided. Of the inner diameter surface of the cylindrical portion 212a, the region where the

seal members

215 and 216 are fixed is formed on the cylindrical surface 212a2 parallel to the axis. The flange portion 212b is always in contact with the diaphragm spring by a preload spring 224 that acts between the outer body 231 and the flange portion 222d of the piston 222, and its cross-sectional shape is in line contact with the diaphragm spring (point contact in the cross-sectional view). ), A convex arc shape protruding to the front side.

As the steel plate for forming the inner ring 211 and the outer ring 212, for example, a carburized steel plate can be used. Examples of the carburized steel that can be used include nickel chrome steel (SNC), nickel chrome molybdenum steel (SNCM), chrome steel (SCr), and chrome molybdenum steel (SCM). Note that one or both of the inner ring 211 and the outer ring 212 can be a press-formed product of a steel plate as described above, a forged product, or a machined product such as cutting.

The second seal member 216 includes a core bar 217 having a substantially L-shaped cross section and a rubber cover 218 that is vulcanized and bonded so as to cover the surface of the core bar 217, and the rear side is opened as a whole. It has a substantially U-shaped cross section. In the second seal member 216, the outer diameter end portion 216a is press-fitted and fixed to the cylindrical surface 212a2 of the outer ring 212 (strictly speaking, the front cylindrical surface 212a2), and in this state, the inner diameter end portion 216b (lip) has the entire circumference. It contacts the outer diameter surface of the inner ring 211 over the entire area. As a result, a seal portion S10 made of a so-called contact seal is formed, and the front side opening of the annular space formed between the two

wheels

211 and 212 is sealed.

Similar to the second seal member 216, the first seal member 215 is composed of a core metal 217 having a substantially L-shaped cross section, and a rubber covering portion 218 vulcanized and bonded to cover the surface of the core metal 217. As a whole, it has a substantially U-shaped cross section with the front side opened. In the first seal member 215, the outer diameter end 215a is press-fitted and fixed to the cylindrical surface 212a2 of the outer ring 212 (strictly speaking, the rear cylindrical surface 212a2), and in this state, the inner diameter end 215b (lip) has the entire circumference. In contact with the cylindrical outer diameter surface 211a2 of the inner ring 211, a seal portion S10 made of a so-called contact seal is formed.

As a rubber material used for forming the covering portion 218 constituting both

seal members

215 and 216, known rubber materials excellent in wear resistance and water resistance (weather resistance), for example, 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.

The cover material 219 has a substantially disk shape extending in the radial direction as a whole, and is fixed to the rear side end of the inner ring 211 by fitting an inner diameter end portion 219b bent to the front side to the inner diameter surface of the inner ring 211. The The cover member 219 has an annular portion 219a facing the rear side end face of the first seal member 215 via a predetermined axial gap, and a predetermined area on the outer diameter side of the annular portion 219a on the front side. And a raised portion 219c formed by raising a predetermined amount. The raised portion 219c is closer to the first seal member 215 than the annular portion 219a, and the labyrinth seal S2 whose front side end surface extends linearly in the radial direction between the front side end surface and the rear side end surface of the first seal member 215. Form.

In the present embodiment, the cover material 219 is a press-formed product obtained by press-forming a thin steel plate material from at least each part of the inner ring 211. Thus, the cover material 219 can be formed of a thin steel plate because the first seal member 215 is formed from the rear side opening of the annular space in accordance with an increase in internal pressure during bearing operation. This is because it is sufficient if the strength is sufficient to prevent removal, and the strength required for the inner ring 211 (the cylindrical portion 211a and the flange portion 211b) is not necessary. In order to increase the fixing strength between the cover member 219 and the inner ring 211, for example, an adhesive may be interposed between the inner diameter end 219b of the cover member 219 and the inner ring 211.

The two

wheels

211 and 212 are composed of a seal portion S10 formed by the cooperation of the first seal member 215 and the inner ring 211, and a labyrinth seal S2 formed by the cooperation of the cover member 219 and the first seal member 215. The rear side opening of the annular space formed therebetween is sealed (sealed).

As described above, in the clutch release bearing 210 according to the present invention, from the seal portion S10 formed by the cooperation of the inner diameter end portion 215b of the first seal member 215 and the outer diameter surface (cylindrical surface 211a2) of the inner ring 211. In addition, a labyrinth seal S2 that is a non-contact seal is additionally provided on the outer side of the bearing. Therefore, it is possible to improve the sealing performance at the rear side opening portion of both the opening portions of the annular space formed between the two

wheels

211 and 212 without increasing the bearing torque. The member on one side forming the labyrinth seal S2 is formed of a steel plate material that is thinner than the inner ring 211. Such a thin steel plate has a high degree of freedom in shape and is lightweight. Therefore, it is possible to easily form the labyrinth seal S2 while reducing the weight of the clutch release bearing 210. From the above, according to the present invention, it is possible to simply provide the clutch release bearing 210 that has higher sealing performance while being light weight and low torque.

In the above description, the raised portion 219c is provided in the cover material 219, and the labyrinth seal that extends linearly in the radial direction between the end surface of the raised portion 219c and the end surface of the first seal member 215 opposite to the raised portion 219c. Although S2 is formed, the means for forming the labyrinth seal S2 of this aspect is not limited to this. That is, for example, the covering portion 218 constituting the first seal member 215 is provided with a protruding portion that protrudes more to the rear side than the other portion, and the gap between the end surface of the protruding portion and the end surface of the cover material 219 opposite to this ( Alternatively, it is also possible to form a labyrinth seal S2 extending linearly in the radial direction (between the end surfaces of the raised portions 219c provided on the cover material 219). The covering portion 218 of the first seal member 215 is vulcanized and bonded, and the form of the covering portion 218 can be easily changed simply by changing the shape of the molding die. Therefore, this type of labyrinth seal S2 can be easily formed without causing a particular increase in cost.

As mentioned above, although one Embodiment of the clutch release bearing 210 to which the 3rd structure of this invention was applied was described, the 3rd structure of this invention is not limited to this. Hereinafter, modifications of the clutch release bearing to which the third configuration of the present invention is applied will be described, but members / parts having substantially the same functions as those described above are denoted by common reference numerals, Duplicate explanation is omitted.

FIG. 9 shows a second embodiment of the clutch release bearing 210 to which the third configuration of the present invention is applied. The main difference of the clutch release bearing 210 shown in FIG. 8 from that shown in FIG. 8 is that the

annular protrusions

219d and 219d are provided at two locations separated in the radial direction of the cover member 219 and the first seal member 215 is formed. An annular protrusion 215c is provided on the covering portion 218 so as to have a radial position different from the annular protrusion 219d provided on the cover material 219 (strictly, between the

annular protrusions

219d and 219d). The point is that the

annular protrusions

215c and 219d form a labyrinth seal S2 extending in a meandering manner in the radial direction. In such a configuration, the overall length of the labyrinth seal S2 can be increased as compared with the first embodiment in which the labyrinth seal S2 extending linearly in the radial direction is formed, so that the sealing performance can be further improved. Since the covering portion 218 constituting the first seal member 215 is vulcanized and bonded (molded) to the surface of the cored bar 217, a special increase in cost due to the formation of the annular protrusion 215c on the covering portion 218 is Does not occur.

FIGS. 10 to 12 show third to fifth embodiments of the clutch release bearing 210 to which the third configuration of the present invention is applied, respectively, and are modifications of the clutch release bearing 210 shown in FIG. First, the main difference between the embodiment shown in FIG. 10 and that shown in FIG. 9 is that the annular protrusion 219d provided on the outer side in the radial direction is omitted from the two annular protrusions 219d provided on the cover member 219 shown in FIG. It is in the point. 11 is different from that shown in FIG. 9 in that the cover member 219 is provided with one annular projection 219d and the annular projection 219d is sandwiched between the first seal member 215 and the first seal member 215. The portion 218 is provided with two annular protrusions 215c and 215c. 12 is different from the embodiment shown in FIG. 9 in that the annular projection 219d provided on the radially inner side of the two

annular projections

219d and 219d provided on the cover member 219 shown in FIG. It is in the point that is omitted.

In the above, the case where the present invention is applied to the clutch release bearing 210 in which the inner ring 211 is the stationary side and the outer ring 212 is the rotating side has been described. On the contrary, the inner ring 211 is the rotating side and the outer ring. Of course, it is also possible to apply the configuration of the present invention to the clutch release bearing 210 having 212 as a stationary side. In this case, however, the abutting portion with the diaphragm spring is a flange provided to extend radially outward at one end on the front side of the inner ring 211 (not shown). In this case, the collar provided at the front end of the outer ring 212 is not necessary.

Further, in the clutch release bearing 210 shown in each of the embodiments of FIGS. 9 to 12, a serpentine labyrinth seal S2 in which concave arcs and convex arcs are alternately formed is formed. It is also possible to form a labyrinth seal S2 meandering in a rectangular wave shape. Such a configuration can be easily obtained, for example, by forming the

annular protrusions

219d and 215c provided on the cover member 219 and the first seal member 215 in a rectangular cross section (not shown). Moreover, each embodiment mentioned above is an illustration to the last, and the position of the

annular protrusions

219d and 215c provided on the cover material 219 and the first seal member 215, the number, the cross-sectional shape, etc. are appropriately changed according to the required sealing performance and the like. Is possible.

In the above, the case where the cover material 219 is formed of a thin steel plate material has been described, but the material for forming the cover material 219 is not particularly limited, and can be formed of a resin material or ceramics. In this case, the clutch release bearing can be further reduced in weight.

Although not shown, the third configuration of the present invention described above can be applied to the clutch release bearing 10 shown in FIG. 2 and the clutch release bearing 110 shown in FIG. That is, in the clutch release bearing shown in FIGS. 2 and 5, a labyrinth seal can be formed between the rear side end face of the first seal member and the inner ring collar portion facing the rear end face. Of course, in the clutch release bearing shown in FIGS. 2 and 5, the flange provided on the rear side of the inner ring has a separate structure as shown in FIG. 8, that is, the rear side flange of the inner ring is omitted, as shown in FIG. It is also possible to fix the cover member 219 shown in FIG. 4 to one end on the rear side of the inner ring and form a labyrinth seal between the cover member 219 and the first seal member.

In the above description, the clutch release bearing in which both of the

seal members

215 and 216 are so-called contact type has been described. However, either or both of the

seal members

215 and 216 are so-called non-contact type clutch release bearings. It is also possible to apply the third configuration of the present invention to the bearing.

The clutch release bearing to which each configuration of the present invention is applied has been described above. However, the present invention is not limited to the above-described embodiment, and various forms are possible without departing from the gist of the present invention. Of course, it can be carried out in 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.

It is sectional drawing which shows the whole structure of the clutch release bearing apparatus incorporating the clutch release bearing to which the 1st structure of this invention is applied. It is an expanded sectional view of the clutch release bearing shown in FIG. It is a front view at the time of seeing the retaining member from the X direction in FIG. It is a figure which shows the other example of a retaining member. It is sectional drawing which shows the whole structure of the clutch release bearing apparatus incorporating the clutch release bearing to which the 2nd structure of this invention is applied. It is an expanded sectional view of the clutch release bearing shown in FIG. FIG. 6 is an enlarged cross-sectional view of a main part showing a modification of the clutch release bearing shown in FIG. 5. It is sectional drawing which shows the whole structure of the clutch release bearing apparatus incorporating the clutch release bearing to which the 3rd structure of this invention is applied. It is an expanded sectional view of the clutch release bearing shown in FIG. It is a modification of the clutch release bearing shown in FIG. It is a modification of the clutch release bearing shown in FIG. It is a modification of the clutch release bearing shown in FIG. It is a modification of the clutch release bearing shown in FIG. It is sectional drawing which shows notionally the clutch release bearing of a conventional structure.

Explanation of symbols

10, 110, 210 Clutch release bearing 11, 111, 211

Inner ring

12, 112, 212

Outer ring

13, 113, 213 Ball (rolling element)
15, 115, 215

First seal member

16, 116, 216

Second seal member

17, 117, 217

Core metal

18, 118, 218 Cover portion 19 Retaining member

19b Flange portion

20, 120, 220

Movable body

30, 130, 230

Fixed body

40, 140, 240 Volume variable chamber 215c Annular protrusion 219 Cover material 219c Raised part 219d Annular protrusion S, S1, S10 Seal part S2 Labyrinth seal

Claims

A clutch release bearing having a contact portion with a rotating member of a clutch device, an inner ring and an outer ring provided so as to be relatively rotatable via rolling elements, and an opening portion of an annular space formed between the inner ring and the outer ring A seal member that seals the outer diameter end of the seal member is press-fitted and fixed to the inner diameter of the opening of the outer ring.
A clutch release bearing characterized in that a retaining member for restricting movement of the outer diameter end portion of the seal member to the outside in the axial direction is fitted to the outer ring.
The retaining member includes a cylindrical portion fitted to the outer diameter surface of the outer ring and a flange portion extending radially inward from one end of the cylindrical portion, and the inner diameter end portion of the flange portion is a seal member. The clutch release bearing according to claim 1, wherein the clutch release bearing is disposed on an outer side in an axial direction of an outer diameter end portion of the outer peripheral portion.
The clutch release bearing according to claim 2, wherein the flange portion of the retaining member is provided intermittently in the circumferential direction.
2. The clutch release bearing according to claim 1, wherein a step portion is provided on an outer diameter surface of the outer ring, and an end portion of a retaining member is engaged with the step portion.
2. The clutch release bearing according to claim 1, wherein an inner diameter end portion of the seal member contacts the inner ring over the entire circumference.
A clutch release bearing having a contact portion with a rotating member of a clutch device, an inner ring and an outer ring provided so as to be relatively rotatable via rolling elements, and an opening portion of an annular space formed between the inner ring and the outer ring A seal member that seals the outer diameter of the seal member, and the outer diameter end of the seal member is press-fitted and fixed to the inner diameter surface of the outer ring extending in the axial direction. Consists of parts
The outer diameter end portion of the seal member has a core portion exposed at a part of the outer peripheral surface thereof pressed against the inner diameter surface of the outer ring and a covering portion provided at a different axial position from the outer peripheral surface. A clutch release bearing, wherein the clutch release bearing is press-contacted to the inner diameter surface of the shaft.
The clutch release bearing according to claim 6, wherein the covering portion is pressed against the inner diameter surface of the outer ring on the opening side of the annular space, and the core metal is pressed against the inner diameter surface of the outer ring on the opposite side of the annular space.
8. A clutch release bearing according to claim 7, wherein a concave annular groove which is recessed toward the outer diameter side from other places is provided on an inner diameter surface of the outer ring, and a covering portion is fitted into the annular groove.
The clutch release bearing according to claim 6, wherein the rubber material forming the covering portion is hydrogenated nitrile rubber or heat-resistant nitrile rubber.
The clutch release bearing according to claim 6, wherein the seal member has an inner diameter end in contact with an outer diameter surface of the inner ring.
The clutch release bearing according to claim 6, wherein the outer ring is a press-formed product.
A clutch release bearing having a contact portion with a rotating member of a clutch device, an inner ring and an outer ring provided so as to be relatively rotatable via rolling elements, and an opening portion of an annular space formed between the inner ring and the outer ring And a sealing member that seals
A cover material that extends in the radial direction and faces the seal member in the axial direction is fixed to one end of the inner ring, and a labyrinth seal that extends in the radial direction is formed between the cover material and the seal member. A clutch release bearing characterized by the above.
The clutch release bearing according to claim 12, wherein the labyrinth seal is linearly extended.
The clutch release bearing according to claim 13, wherein an annular ridge is provided on at least one of the cover member or the seal member, and the labyrinth seal is formed by the ridge.
The clutch release bearing according to claim 12, wherein the labyrinth seal is extended in a meandering manner.
The cover member is provided with one or a plurality of annular protrusions, and the seal member is provided with one or a plurality of annular protrusions in a radial position different from that of the cover member, and the cover member and the annular protrusions The clutch release bearing according to claim 15, wherein the labyrinth seal is formed by an annular protrusion of a seal member.
A fixed body and a movable body provided so as to be movable in the axial direction along the fixed body by a volume variation of a volume variable chamber formed between the fixed body and the movable body. A clutch release bearing device provided with the clutch release bearing according to claim 1.