JP2009047255A - Clutch-release bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a clutch-release bearing capable of enhancing the reliability by improving the sealability, and simplifying the assembly workability. <P>SOLUTION: A cover formed of a corrosion-resistant steel sheet is attached to an end of an inner ring 3. The cover comprises a first cover 12 having a base part 12a to be abutted on an end face 3e of the inner ring 3, a cylindrical part 12b extending therefrom in the axial direction, a vertical plate part 12c extending outwardly in the radial direction, and a cylindrical umbrella part 12d, and a second cover 13 having a fixed part 13a to be fitted to an inner circumference of an end of the inner ring 3, and a disk part 13b extending outwardly therefrom in the radial direction. The base part 12a of the first cover 12 is fixed in a held state by the disk part 13b of the second cover 13 and the end face 3e of the inner ring 3, and an annular recess 16 is formed in an outer circumference of the end of the outer ring 15. The umbrella part 12d of the first cover 12 is stored in the recess 16 to constitute a labyrinth seal opposite thereto via a space in the radial direction. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a clutch release bearing mounted on a clutch portion of a manual transmission such as an automobile, and more particularly to a clutch release bearing incorporated in a direct cylinder type clutch release bearing device driven by hydraulic pressure or the like.

  In general, this type of clutch release bearing device is interposed between an automobile engine and a transmission, and is used in a clutch portion that transmits and blocks power from the engine to the transmission. The clutch release bearing device 50 shown in FIG. 4 is an example, and a cylindrical and coaxial outer body 51, a fixed part 53 including a guide tube 52, and a sliding movement coaxially with the fixed part 53. And a piston 55 that internally includes a variable volume chamber 54 connected to the control hydraulic pressure generator. The outer body 51 has a groove on its inner side surface 56, and a radial edge 57 formed at one end of the guide tube 52 is inserted into the groove. The guide tube 52 constitutes the bottom of the variable volume chamber 54.

  The fixed structure includes a fixed part 53 for attaching the clutch release bearing device 50 to the casing 58 of the gear box, and a movable part including a piston 55 having an annular shape as a whole. The movable part is formed in an annular shape so as to slide in the axial direction in a cavity 59 formed in a part. The cavity 59 is closed and oil is pressurized and depressurized as a control fluid. That is, the volume variable chamber 54 is configured by the piston 55 in the cavity 59.

  When the control fluid in the variable volume chamber 54 is pressurized by the pressure generator, the piston 55 is displaced to the left in the figure so that the volume of the variable volume chamber 54 increases. The piston 55 operates the clutch release bearing 60 during traveling, and the clutch release bearing 60 engages and disengages with an inner end portion of a finger of a diaphragm (not shown) to transmit and shut off power.

  The piston support tube 61 extends slightly beyond the front end of the piston 55, and an annular groove 62 is formed on the outer periphery. An aligning ring 63 is attached to the annular groove 62. The aligning ring 63 is conical before mounting (natural state), and a pair of elastically deformable nibs 64 are formed on the inner periphery thereof, and all the nibs 64 together with the annular portion of the aligning ring 63 are formed. The two curved planes are the same.

  When the clutch release bearing 60 is attached to the clutch release bearing device 50, the alignment ring 63 is installed on the axis of the piston support tube 61 and is pushed into the annular groove 62 by the ram 65. The end of the nib 64 is deformed and engages with the annular groove 62.

  A flange portion 66a of the inner ring 66 of the clutch release bearing 60 abuts on the front surface 55a of the piston 55, and the flange portion 66a of the inner ring 66 serves as a backup member during such operation. After the mounting operation, the aligning ring 63 pressurizes the inner ring 66 of the clutch release bearing 60 with a desired spring force to allow the clutch release bearing 60 to align.

  Here, the clutch release bearing 60 is an angular ball bearing, and includes a cup-shaped outer ring 67 formed by pressing a steel plate and an inner ring 66 inserted into the outer ring 67 via a plurality of balls 68. Yes. A flange 67a extending radially inward is formed at one end of the outer ring 67, and this flange 67a is in constant contact with the fingers of the diaphragm by a preload spring 69 acting between the fixed component 53 and the piston 55. Yes. The preload spring 69 is configured to cooperate with the inner ring 66 of the clutch release bearing 60.

A shield plate 70 is mounted on the flange 67 a side of the outer ring 67, and a seal 71 is fitted to the outer diameter of the inner ring 66 to seal the annular space between the inner ring 66 and the outer ring 67. This prevents leakage of the lubricating grease enclosed in the bearing and prevents rainwater, dust, etc. from entering the bearing from the outside.
Special table 2003-520334 gazette

  In such a conventional clutch release bearing 60, a shield plate 70 is mounted on the flange 67a side of the outer ring 67, and a seal 71 is fitted to the outer diameter of the inner ring 66, so that an annular space between the inner ring 66 and the outer ring 67 is obtained. However, the shield plate 70 on the flange 67a side is a labyrinth seal formed with a gap between the inner ring 66 and the leakage of grease to the outside, and the rainwater from the outside to the inside of the bearing. Or foreign matter such as dust may enter. On the other hand, since the seal 71 fitted to the inner ring 66 is in contact with the inner peripheral surface of the outer ring 67 serving as the rotation side member, the peripheral speed of the contact portion is increased, wear is promoted, and the sealing performance is lowered. There is a risk that the temperature of the bearing will rise due to heat generation, and that the grease will deteriorate, leading to a short life of the bearing.

  The present invention has been made in view of such a conventional problem, and an object of the present invention is to provide a clutch release bearing with improved sealing performance and improved reliability.

  In order to achieve such an object, the invention according to claim 1 of the present invention includes an outer ring that is integrally formed with a flange portion that extends radially inward at an end portion on the outer side and that abuts against a diaphragm spring. An inner ring integrally formed with a flat collar that faces the collar and extends inward in the radial direction, a plurality of balls that are rotatably accommodated between the inner ring and the outer ring, and the inner and outer rings In a clutch release bearing having a seal attached to an opening of an annular space formed therebetween, a cover formed by press working from a steel plate having corrosion resistance is attached to an inner side end of the inner ring. A cylindrical umbrella portion is formed on the outer side in the radial direction of the cover, and is opposed to the outer periphery of the inner side end portion of the outer ring via a predetermined radial clearance to constitute a labyrinth seal.

  As described above, the outer ring that extends radially inwardly at the outer end and the flange that contacts the diaphragm spring is integrally formed, and the flat flange that faces the flange and extends radially inward. Are integrally formed, a plurality of balls accommodated in a freely rolling manner between the inner ring and the outer ring, and a seal attached to an opening of an annular space formed between the inner and outer rings. In the clutch release bearing, a cover formed by press working from a steel plate having corrosion resistance is attached to the inner ring end of the inner ring, and a cylindrical umbrella portion is formed radially outward of the cover. The labyrinth seal is configured to face the outer circumference of the inner end through a predetermined radial clearance, so that the seal can be prevented from being directly exposed to foreign matter such as rainwater, dust, or muddy water. The seal It is possible to suppress Worn, it is possible to improve the sealing performance without increasing the rotational torque of the bearing.

  Preferably, as in the invention described in claim 2, if an annular recess is formed in the outer periphery of the inner side end portion of the outer ring, and the umbrella portion is accommodated in the recess, the compactness is achieved. At the same time, the sealing performance can be further improved, and the reliability can be improved over a long period of time.

  According to a third aspect of the present invention, the cover includes a base portion that abuts on an inner side end surface of the inner ring, a cylindrical portion that extends in an axial direction from the base portion, and a radially outward portion from the cylindrical portion. A first cover including an upright plate portion extending from the upright plate portion and the umbrella portion extending in the axial direction; a fixed portion fitted to an inner periphery of an inner side end of the inner ring; and A second cover having a disk portion extending radially outward, and the base portion of the first cover being sandwiched between the disk portion of the second cover and the end face of the inner ring. If it is fixed in the axial direction, the shape of the cover can be simplified, the workability can be improved, and the cost can be reduced.

  According to a fourth aspect of the present invention, the cylindrical portion and the upright plate portion of the first cover are opposed to each other on the inner peripheral surface of the inner ring and the seal through a slight gap, and the labyrinth seal. The sealing performance can be further improved without increasing the rotational torque of the bearing.

  Further, as in the invention described in claim 5, the inner seal of the seals is fitted to the inner periphery of the inner ring end of the outer ring, and the cross section is formed into a substantially L shape by pressing from a steel plate. And a seal member that is integrally joined to the core, extends inwardly in the radial direction, and has a pair of seal lips engaged with the outer peripheral surface of the inner side end of the inner ring. One seal lip of the pair of seal lips is in sliding contact with the outer peripheral surface of the inner ring through a predetermined shimiro, and the other seal lip is opposed to the outer peripheral surface through a slight radial clearance. If a labyrinth seal is configured, even if one seal lip wears, the other seal lip can compensate for the wear, suppressing lip wear and heat generation at the sliding contact portion, and high sealing over a long period of time. Maintain sex While, it is possible to prevent the deterioration of the grease prolong the life of the bearing.

  Further, as in the invention described in claim 6, the outer seal of the seal is fitted to the inner periphery of the outer end of the outer ring, and the cross section is formed in a substantially L shape by pressing from a steel plate. And a sealing member having a sealing lip that is integrally joined to the core and extends in the axial direction. The sealing lip is in sliding contact with the outer peripheral surface of the inner ring and the corner of the flange. If it is done, it is possible to reduce the size and improve the reliability without causing the seal lip to be turned up by assembling the inner ring.

  The clutch release bearing according to the present invention has an outer ring that extends radially inwardly at the outer end and is integrally formed with a flange that comes into contact with the diaphragm spring, and is opposed to the flange and radially inward. An inner ring integrally formed with an extending flat flange, a plurality of balls rotatably accommodated between the inner ring and the outer ring, and an opening of an annular space formed between the inner and outer rings In a clutch release bearing provided with a mounted seal, a cover formed by pressing a corrosion-resistant steel plate is mounted on the inner side end of the inner ring, and a cylindrical shape is formed radially outward of the cover. Is formed, and a labyrinth seal is formed on the outer periphery of the outer ring on the inner side through a predetermined radial clearance, so that the seal is protected against foreign matter such as rainwater, dust, or muddy water. Can be prevented from being exposed contact, it is possible to suppress the wear of the seal, it is possible to improve the sealing performance without increasing the rotational torque of the bearing.

  This is a clutch release bearing incorporated in a direct cylinder type clutch release bearing device driven by hydraulic pressure or the like, and has a flange portion that extends radially inwardly at the outer end and abuts against a diaphragm spring. An outer ring, an inner ring that is integrally formed with a flat flange that faces the flange and extends radially inward, and a plurality of balls that are rotatably accommodated between the inner ring and the outer ring; A clutch release bearing provided with a seal mounted in an opening of an annular space formed between the inner and outer rings, and a cover formed by pressing a corrosion-resistant steel plate at an inner side end of the inner ring. A base portion that is mounted and abuts against an inner end face of the inner ring, a cylindrical portion that extends in an axial direction from the base portion, and a radial direction from the cylindrical portion A first cover provided with an upright plate portion extending in the direction, an umbrella portion extending in the axial direction from the upright plate portion, a fixed portion fitted to the inner periphery of the inner side end of the inner ring, and the fixed portion A second cover having a disk portion extending radially outward from the second cover, with the base portion of the first cover being sandwiched between the disk portion of the second cover and the end face of the inner ring. While being fixed in the axial direction, an annular recess is formed in the outer periphery of the inner side end of the outer ring, and the umbrella portion of the first cover is accommodated in this recess via a predetermined radial clearance. Confronts the labyrinth seal.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing a first embodiment of a clutch release bearing according to the present invention, and FIG. 2 is an explanatory view showing an assembling procedure of the clutch release bearing. In the following description, the diaphragm spring side is referred to as the outer side (left side in the drawing) and the center side is referred to as the inner side (right side in the drawing) in a state where it is assembled to the clutch portion.

  This clutch release bearing 1 is integrally formed with an outer ring 2 having an outer raceway surface 2a formed on the inner periphery, and an outer ring end 2b extending radially inward at the outer end. An inner ring 3 integrally having a flange 3b extending radially inward and having an inner raceway surface 3a facing the outer raceway surface 2a on the outer periphery, and a cage 4 between the two raceway surfaces. An angular ball bearing comprising a plurality of balls 5 accommodated so as to roll freely.

  The flange 2b of the outer ring 2 engages / disengages with a diaphragm spring (not shown) to transmit / cut off power. A first seal 6 and a second seal 7 are attached to the opening of the annular space formed between the outer ring 2 and the inner ring 3, and leakage of the lubricating grease enclosed in the bearing and the bearing from the outside. Prevents rainwater and dust from entering inside. Here, the flange portion 2b of the outer ring 2 is formed on a flat surface extending vertically, but is not limited thereto, and may be formed on a convex arc surface.

  The outer ring 2 and the inner ring 3 are manufactured from a material made of a carburized steel sheet through a process of pressing, carburizing and quenching, grinding of a rolling surface, and the like. Examples of the material include SNC (nickel chromium) steel, SNCM (nickel chromium molybdenum) steel, SCr (chromium) steel, and SCM (chromium molybdenum) steel. Among these, SNC steel and SNCM steel are materials that are less prone to excessive carburization and are excellent in mechanical properties, but are somewhat difficult in terms of cost because they contain expensive nickel Ni as an alloy element. is there. Considering the mechanical characteristics required for the inner and outer rings 3 and 4, SNC steel and SNCM steel have a feeling of excessive quality and cannot be balanced in terms of cost. On the other hand, SCM steel is hard to cause excessive carburization and has good hardenability, and is relatively inexpensive compared to SNC steel and SNCM steel. Further, the mechanical characteristics required for the inner and outer rings 3 and 2 of the clutch release bearing 1 can be sufficiently satisfied. For this reason, it is preferable to use SCM steel as the material for the inner and outer rings 4 and 3. SCM steel includes SCM415, SCM418, SCM420, SCM421, and SCM822 depending on the carbon content, and among them, SCM415 is most preferable.

  Here, the 1st seal | sticker 6 is fitted to the outer peripheral edge part inner periphery of the outer ring | wheel 2, and consists of the metal core 8 and the sealing member 9 joined to this metal core 8 by vulcanization adhesion etc. integrally. . The core 8 has a cross-section of a corrosion-resistant steel plate such as a cold-rolled steel plate (JIS standard SPCC type) or austenitic stainless steel plate (JIS standard SUS304 type) subjected to rust prevention by pressing. It is formed in a substantially L shape, and is formed in an annular shape as a whole. The seal member 9 is made of synthetic rubber such as nitrile rubber, and has a seal lip 9a extending in the axial direction. The seal lip 9a is in sliding contact with the outer peripheral surface 3c on the outer side of the inner ring 3 and the corner of the flange 3b. By adopting the seal 6 having such a configuration, it is possible to reduce the size and improve the reliability without the seal lip 9a being turned up by assembling the inner ring 3.

  The second seal 7 includes a cored bar 10 fitted to the inner circumference of the inner side end of the outer ring 2 and a seal member 11 integrally joined to the cored bar 10 by vulcanization adhesion or the like. The core bar 10 has a cross-section of a corrosion-resistant steel plate such as a cold-rolled steel plate (JIS standard SPCC type) or austenitic stainless steel plate (JIS standard SUS304 type) subjected to rust prevention by pressing. It is formed in a substantially L shape, and is formed in an annular shape as a whole. The seal member 11 is made of synthetic rubber such as nitrile rubber, and has a pair of seal lips 11 a and 11 b that extend inwardly in the radial direction and engage with the outer peripheral surface 3 d on the inner side of the inner ring 3. is doing. One seal lip 11a of the pair of seal lips 11a and 11b is in sliding contact with the outer peripheral surface 3d via a predetermined shimiro, and the other seal lip 11b is opposed to the outer peripheral surface 3d with a slight radial clearance. And constitutes a labyrinth seal. Here, even if one seal lip 11a is worn, the other seal lip 11b can compensate for the wear. By adopting the seal 7 having such a configuration, lip wear and heat generation at the sliding contact portion are suppressed, high sealing performance is maintained over a long period of time, and grease is prevented from deteriorating to extend the life of the bearing. be able to.

  Furthermore, in the present embodiment, in addition to the seals 6 and 7 described above, the first cover 12 and the second cover 13 are attached to the inner side end of the inner ring 3. These first and second covers 12 and 13 are made of corrosion-resistant steel plates, for example, cold-rolled steel plates (JIS standard SPCC system) and austenitic stainless steel sheets (JIS standard SUS304 system) that have been rust-proofed. ) Etc. are formed by press working.

  The first cover 12 includes a base portion 12a that is in contact with the inner end surface 3e of the inner ring 3, a cylindrical portion 12b that extends in the axial direction from the base portion 12a, and a standing plate portion 12c that extends radially outward from the cylindrical portion 12b. And a cylindrical umbrella portion 12d extending in the axial direction from the standing plate portion 12c. The cylindrical portion 12b, the upright plate portion 12c, and the umbrella portion 12d are opposed to the outer peripheral surface 3d on the inner side of the inner ring 3 and the seal 7 and the outer periphery of the inner side end of the outer ring 2 through a slight gap, It constitutes a labyrinth seal.

  The second cover 13 includes a fixing portion 13a that is fitted to the inner periphery of the inner side end of the inner ring 3, and a disk portion 13b that extends radially outward from the fixing portion 13a. The first cover 12 is fixed in the axial direction in a state where the base portion 12a of the first cover 12 is sandwiched between the disc portion 13b and the end surface 3e on the inner side of the inner ring 3. As described above, in the present embodiment, by using separate first and second covers 12 and 13 as the cover, the shape can be simplified, the workability can be improved, and the cost can be reduced.

  Further, a preload spring (not shown) is attached to the inner diameter portion of the inner ring 3 and is fixed by a bent piece 13 c formed at the inner end of the fixing portion 13 a of the cover 13. Note that a piston (not shown) and a preload spring are sealed in an annular recess formed between the upright plate portion 12c of the first cover 12 and the disc portion 13b of the second cover 13. Boots (not shown) are attached.

  Thus, in this embodiment, since the 1st and 2nd covers 12 and 13 are attached to the inner side of the 2nd seal 7, the 2nd seal 7 is foreign substances, such as rain water, dust, or muddy water. The seal lip 11a can be prevented from being directly exposed to the surface, and the sealing performance can be greatly improved without increasing the rotational torque of the bearing.

Next, the assembly procedure of the clutch release bearing 1 of this embodiment will be described with reference to FIG.
First, as shown in (a), the first seal 6 is fitted to the inner periphery of the outer end of the outer ring 2, and the ball cassette composed of the balls 5 held by the cage 4 is moved outwardly from the outer ring 2. It is fitted in the surface 2a. Thereafter, the second seal 7 is fitted to the inner circumference of the inner side end of the outer ring 2.

  Next, as shown in (b), a predetermined amount of grease is injected from the inner diameter side of the ball 5 toward the outer rolling surface 2a, and the inner ring 3 is inserted from the inner side of the outer ring 2. Here, the grease may be injected from the inner side of the ball 5 toward the outer rolling surface 2a before the second seal 7 is fitted. Thereafter, as shown in (c), the first cover 12 and the second cover 13 are sequentially attached to the inner end of the inner ring 3 to complete the assembly.

  In the present embodiment, a first seal 6, a ball cassette and a second seal 7 are sequentially fitted into the outer ring 2, the inner ring 3 is inserted from the axial direction of the outer ring 2, and the first and Since the second covers 12 and 13 can be attached, the assembly workability can be simplified, the assembly can be automated, and the cost can be reduced.

  FIG. 3 is a longitudinal sectional view showing a second embodiment of the clutch release bearing according to the present invention. The second embodiment is basically different from the first embodiment (FIG. 1) described above only in the configuration of the outer ring. Other parts, parts having the same function, parts or parts have the same function. The same reference numerals are assigned and detailed description is omitted.

  The clutch release bearing 14 integrally has a flange 2b extending radially inward at the outer end, an outer ring 15 having an outer rolling surface 2a formed on the inner periphery, and an outer end. An inner ring 3 having a flange 3b extending inward in the radial direction and having an inner rolling surface 3a opposite to the outer rolling surface 2a formed on the outer periphery, and a cage 4 between both rolling surfaces. And a plurality of balls 5 accommodated so as to roll freely.

  The outer ring 15 is formed by press working from a material made of a carburized steel plate, like the outer ring 2 described above, and is manufactured by grinding the outer rolling surface 2a after carburizing and quenching. An annular recess 16 is formed on the outer periphery of the inner side end of the outer ring 15 by a cutting process such as turning. In addition, a first cover 17 and a second cover 13 are attached to the inner side end of the inner ring 3 as in the above-described embodiment.

  The first cover 17 is a steel plate having corrosion resistance, for example, a rust-proof cold rolled steel plate (JIS standard SPCC) or austenitic stainless steel plate (JIS standard), similar to the first cover 12 described above. SUS304 system) or the like is formed by pressing, and a base portion 12a that abuts on the inner side end surface 3e of the inner ring 3, a cylindrical portion 12b that extends in an axial direction from the base portion 12a, and a radially outward direction from the cylindrical portion 12b And a cylindrical umbrella portion 17a extending in the axial direction from the standing plate portion 12c. And this umbrella part 17a is accommodated in the recess 16 of the outer ring | wheel 15, and it opposes to the outer peripheral surface via a predetermined | prescribed radial clearance, and comprises the labyrinth seal. As a result, it is possible to achieve downsizing and further enhance the sealing performance to improve the reliability over a long period of time.

  The embodiment of the present invention has been described above, but the present invention is not limited to such an embodiment, and is merely an example, and various modifications can be made without departing from the scope of the present invention. Of course, the scope of the present invention is indicated by the description of the scope of claims, and further, the equivalent meanings described in the scope of claims and all modifications within the scope of the scope of the present invention are included. Including.

  The clutch release bearing according to the present invention can be applied to a direct cylinder type clutch release bearing device driven by hydraulic pressure or the like.

1 is a longitudinal sectional view showing a first embodiment of a clutch release bearing according to the present invention. It is explanatory drawing which shows an assembly procedure same as the above. It is a longitudinal cross-sectional view which shows 2nd Embodiment of the clutch release bearing which concerns on this invention. It is a longitudinal cross-sectional view which shows the conventional clutch release bearing apparatus.

Explanation of symbols

1, 14 ... Clutch release bearings 2, 15 ... Outer ring 2a ... Outer rolling surface 2b, 3b ...・ Ring 3 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner ring 3a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner rolling surface 3c ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outer peripheral surface 3d ・ ・... Inner side outer peripheral surface 3e ... Inner side end face 4 ... Retainer 5 ... ····· Ball 6 ·················································································· 9, 11... Seal members 9a, 11a, 11b ... Seal lips 12, 17 ... First cover 12a ... Base 12b ... .... Cylinder part 12c ... Standing plate portion 12d, 17a ... Umbrella portion 13 ... Second cover 13a ... Fixing portion 13b ... Disc part 13c ..... bent piece 50 ........ clutch release bearing 51 ........ outer body 52 ..... ·························································· Fixed part 54 ·································・ ・ ・ ・ ・ Front side 56 ・ ・ ・ ・ ・ Inner side surface 57 ・ ・ ・ ・ ・ Radial edge 58 ・ ・ ・ ・ ・ Case 59・ ・ ・ ・ Cavity 60 ・ ・ ・ ・ ・ ・ Clutch release bearing 61 ・ ・ ・ ・ ・ ・ Piston support tube 62 ・ ・ ・ ・ ・ ・ annular groove 6・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Aligning ring 64 ・ ・ ・ ・ ・ Nib 65 ・ ・ ・ ・ ・ Ram 66 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner ring 66a , 67a .. collar part 66b... Seal land part 67 .. outer ring 68... Ball 69. ..... Pressure spring 70 ..... Shield plate 71 ..... Seal

Claims (6)

An outer ring extending inward in the radial direction at the end on the outer side and integrally formed with a flange that contacts the diaphragm spring;
An inner ring integrally formed with a flat flange that faces the flange and extends radially inward;
A plurality of balls accommodated in a freely rollable manner between the inner ring and the outer ring;
In a clutch release bearing comprising a seal attached to an opening of an annular space formed between the inner and outer rings,
A cover formed by pressing from a steel plate having corrosion resistance is attached to the inner side end of the inner ring,
A cylindrical umbrella portion is formed on the outer side in the radial direction of the cover, and a labyrinth seal is configured to face the outer periphery of the inner side end portion of the outer ring through a predetermined radial clearance. Clutch release bearing.   2. The clutch release bearing according to claim 1, wherein an annular recess is formed in an outer periphery of an inner side end portion of the outer ring, and the umbrella portion is accommodated in the recess. The cover is in contact with an inner end face of the inner ring, a cylindrical portion extending in the axial direction from the base portion, a standing plate portion extending radially outward from the cylindrical portion, and an axial direction from the standing plate portion A first cover comprising the umbrella portion extending to
A fixing portion fitted to the inner periphery of the inner side end of the inner ring, and a second cover including a disk portion extending radially outward from the fixing portion;
The clutch release bearing according to claim 1 or 2, wherein the base part of the first cover is sandwiched between the disc part of the second cover and the end face of the inner ring and is fixed in the axial direction.   4. The clutch release according to claim 3, wherein the cylindrical portion and the upright plate portion of the first cover are opposed to the inner peripheral surface of the inner ring and the seal via a slight clearance to form a labyrinth seal. bearing. An inner side seal among the seals is fitted to an inner periphery of an inner side end of the outer ring, and a metal core having a substantially L-shaped cross section formed by pressing from a steel plate;
It is integrally joined to this mandrel, and consists of a seal member having a pair of seal lips extending inwardly in the radial direction and engaged with the outer peripheral surface of the inner side end of the inner ring,
One seal lip of the pair of seal lips is in sliding contact with the outer peripheral surface of the inner ring via a predetermined shimiro,
The clutch release bearing according to any one of claims 1 to 4, wherein the other seal lip is opposed to the outer peripheral surface through a slight radial clearance to form a labyrinth seal. The outer side seal of the seal is fitted to the inner periphery of the outer side end of the outer ring, and a core bar having a substantially L-shaped cross section formed by pressing from a steel plate;
It consists of a seal member that is integrally joined to this mandrel and has a seal lip extending in the axial direction,
The clutch release bearing according to any one of claims 1 to 5, wherein the seal lip is in sliding contact with an outer peripheral surface of the inner ring and a corner portion of the flange portion.

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