JP2010112533A - Ball bearing for clutch release bearing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a ball bearing for a clutch release bearing device which improves the resistance to muddy water without excessively depending on seal members. <P>SOLUTION: A shield portion 35 is arranged on the rear side of the rear side end portion 14a of an outer ring 14 integrally with a rear side seal member 18 by extending a rubber member 34 of the rear side seal member 18 radially outward, further extending it to the rear side. A hydrogenated nitrile rubber is used for the rubber member 34 of the rear side seal member 18 constituting the shield portion 35. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

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

  The clutch release bearing device is used to transmit or cut power from the engine to the transmission by operating a clutch pedal in a manual vehicle (MT vehicle) or the like, and is interposed between the engine and the transmission. .

  The power from the engine to the transmission is cut off by moving the clutch release bearing device in the axial direction to separate the clutch disk from the flywheel. The clutch release bearing device can be broadly classified into a push type and a pull type in the direction of the axial movement. The push type is for moving the clutch release bearing device in the axial direction to the engine side when the power from the engine is cut off, and the pull type is for moving the clutch release bearing device in the axial direction to the transmission side. This clutch release bearing device includes a ball bearing.

  When a deviation occurs between the engine-side shaft center and the transmission-side shaft center, the ball bearing moves in the radial direction in accordance with the deviation and automatically aligns both shaft centers.

  FIG. 7 illustrates a ball bearing used in a direct cylinder type (hydraulic push type) clutch release bearing device (see Patent Document 1).

  The ball bearing 112 includes an outer ring 114 that is a rotating wheel, an inner ring 115 that is a stationary ring, a ball 116 that is interposed between the outer ring 114 and the inner ring 115, and a cage 126 that holds the ball 116. Is configured. The end of the outer ring 114 on the engine side (left side of the drawing: hereinafter referred to as the front side) extends radially inward (lower side of the drawing) to form a flange 119, and the front side end of the inner ring 115 is It extends radially inward to form a flange 120. The flange portion 119 is in a state of being in constant contact with the diaphragm spring 130 by a preload spring (not shown) attached to the inner ring 115.

  The outer ring 114 and the inner ring 115 are sealed by annular seal members 117 and 118. The seal members 117 and 118 are formed by vulcanizing and welding rubber members 133 and 134 to the core bars 131 and 132.

  A front-side seal member 117 (hereinafter referred to as a front-side seal member) has an inverted U-shaped cross section. The front-side seal member 117 has an outer diameter end portion 117c fixed to the inner surface 123 of the outer ring 114, and has a main lip 117a and an auxiliary lip 117b at the inner diameter end portion. The main lip 117a is in radial contact with the outer surface 124 of the inner ring 115, whereby the inside of the bearing 112 (the central portion where the ball 116 is interposed in the space between the outer ring 114 and the inner ring 115: Muddy water is prevented from entering the Further, the auxiliary lip 117b makes it difficult for muddy water to reach the main lip 117a, and the above-described function of the main lip 117a is improved.

  A transmission side (right side of the drawing: hereinafter referred to as rear side) seal member 118 (hereinafter referred to as rear side seal member) has a U-shaped cross section. The rear-side seal member 118 has an outer diameter end portion 118c fixed to the inner surface 123 of the outer ring 114, and has a main lip 118a and an auxiliary lip 118b at the inner diameter end portion. The main lip 118 a is in radial contact with the outer surface 124 of the inner ring 115. The operation and effect of the main lip 118a and the auxiliary lip 118b are the same as those of the main lip 117a and the auxiliary lip 117b of the front side seal member 117 described above, and thus detailed description thereof is omitted.

  In this bearing 112, the transmission of power from the engine to the transmission is such that the flange portion 119 of the outer ring 114 and the diaphragm spring 130 are in constant contact with each other, whereby the clutch disk (not shown) is flywheel (not shown). It is possible to make it in a state of being in close contact with. Further, the power from the engine to the transmission can be interrupted by pulling the clutch disc (not shown) away from the flywheel (not shown) by pressing the flange 119 of the bearing 112 against the diaphragm spring 130.

As described above, the bearing 112 described in Patent Document 1 uses a contact type contact member in which the inner diameter end portions (main lips 117 a and 118 a) are brought into contact with the outer surface 124 of the inner ring 115 as the seal members 117 and 118. . However, as a sealing member, a method using a non-contact type in which the inner diameter end portion is not brought into contact with the outer surface 124 of the inner ring 115 is also known (see Patent Document 2).
JP 2006-189086 A Japanese Patent Application Laid-Open No. 11-270583

  Since the bearing 112 described in Patent Document 1 shown in FIG. 7 uses contact-type seal members 117 and 118, muddy water entering the inside of the bearings has an inner diameter end (main lip 117 a) of the seal members 117 and 118. , 118a). Therefore, it is difficult for muddy water to enter the bearing, and the muddy water resistance is excellent.

  However, if the seal members 117 and 118 are contact type as described above, when the air inside the bearing expands due to the temperature rise due to the rotation of the outer ring 114 and the bearing internal pressure rises, the expanded air inside the bearing is It is difficult to release the bearing internal pressure by escaping. For this reason, there is a problem that the bearing internal pressure increases excessively and the bearing torque (the force for rotating the outer ring 114) increases. As a result, there is a problem that sliding occurs at the contact portion between the diaphragm spring 130 and the flange portion 119 of the outer ring 114, and the diaphragm spring 130 and the flange portion 119 of the outer ring 114 are worn.

  Further, when the seal members 117 and 118 are of the contact type, the muddy water that has penetrated to the vicinity of the inner diameter end portions (main lips 117a and 118a) is difficult to be discharged to the outside of the bearing, or the muddy water is less likely to be discharged to the inner diameter end portions (main lip 117a 118a) and the outer surface 124 of the inner ring 115, there is a problem of stagnation. Further, the inner diameter end portions (main lips 117a and 118a) may be worn by contact with the outer surface 124 of the inner ring 115, and the sealing performance of the seal members 117 and 118 may be deteriorated.

  On the other hand, when the seal members 117 and 118 are non-contact type as in the ball bearing for the clutch release bearing device described in Patent Document 2, even if the outer ring 112 rotates and the bearing internal pressure rises, the seal members 117 and 118 are used. The internal pressure of the bearing can be easily released by allowing the air inside the bearing to escape to the outside of the bearing through a non-contact portion (gap) between the inner diameter end portion of the inner ring 115 and the inner ring 115. Thereby, it is possible to prevent the bearing torque from increasing due to an excessive increase in the bearing internal pressure, and to prevent slippage at the contact portion between the diaphragm spring 130 and the flange portion 119 of the outer ring 115. As a result, power transmission between the diaphragm spring 130 and the flange portion 119 of the outer ring 112 can be made smooth.

  However, if the seal members 117 and 118 are of a non-contact type as described above, muddy water may enter the bearings via non-contact portions (gap) between the seal members 117 and 118 and the inner ring 115.

  This invention is made | formed in view of said situation, and provides the ball bearing for clutch release bearing apparatuses which can improve a muddy water tolerance, without being overly dependent on a sealing member.

  A ball bearing for a clutch release bearing device according to the present invention for solving the above-described problems includes a rotating wheel and a stationary wheel that rotate relative to each other, a ball interposed between the rotating wheel and the stationary wheel, and the rotation A ball for a clutch release bearing device comprising a seal member that forms a sealed space between a ring and the stationary ring, wherein one end of the seal member forms an attachment end fixed to the rotating wheel or the stationary ring In the bearing, at least one of the rotating wheel, the stationary wheel, and the seal member has a shielding portion that extends along the rotation axis of the bearing and is disposed on the outer side of the bearing with respect to the other end portion of the seal member. It is characterized by that.

  In this case, the muddy water entering the inside of the bearing from the outside of the bearing through the other end of the seal member is arranged on the outer side of the bearing from the other end of the seal member before reaching the other end of the seal member. Is blocked by the shield. That is, before reaching the other end portion of the seal member, it is blocked by the shielding portion. As a result, the muddy water hardly reaches the other end of the seal member, and the muddy water resistance of the bearing can be improved without depending on the seal member excessively.

  In the above invention, the shielding portion may be provided at a site between the attachment end and the other end of the seal member. Alternatively, the shielding portion may be provided by extending an end portion of the rotating wheel or the stationary wheel.

  It is desirable that one end portion of the shielding portion is fixed to the rotating wheel or the stationary wheel, and the other end portion protrudes from an end portion of the rotating wheel or the stationary wheel.

  In this case, the muddy water from the outside of the bearing can be blocked by the other end of the shielding portion protruding, and the muddy water resistance of the bearing can be improved.

  In this invention, it is desirable that the one end portion of the shielding portion is sandwiched between the rotating wheel or the stationary wheel and the seal member.

  In this case, the one end portion of the shielding portion can be fixed to the rotating wheel or the stationary wheel at the same time as the attachment end portion of the seal member is fixed to the rotating wheel or the stationary wheel. For this reason, it is possible to improve the assemblability of the bearing (working efficiency at the time of assembling the bearing). Moreover, since a shielding part can be fixed with a sealing member, the attachment state of a shielding part can be stabilized.

  In the invention in which the other end portion of the shielding portion is protruded from the rotating wheel or the stationary wheel, the shielding portion extends from the one end portion in the direction along the rotation axis to the radially outer side. You may make it comprise with an intermediate part and the other end part of the large diameter side extended in the direction along a rotating shaft from this intermediate part.

  Further, in the invention in which the other end portion of the shielding portion is protruded from the rotating wheel or the stationary wheel, a recess is formed in the rotating wheel or the stationary wheel, and one end portion of the shielding portion is fixed at the recess. It is desirable to do.

  In this case, since the shielding portion is housed in a recess formed in the rotating wheel or stationary wheel and does not protrude from the rotating wheel or stationary wheel, the appearance of the bearing is not impaired. Further, since the shielding portion does not protrude from the rotating wheel or the stationary wheel, the protruding portion of the shielding portion does not contact the peripheral member of the bearing when the bearing is assembled to the vehicle. Therefore, the assembly of the bearing to the vehicle becomes easy.

  In this invention, you may make it the one end part of the said shielding part fit in the said recess. Or you may make it the one end part of the said shielding part weld to the said recess. When one end portion of the shielding portion is fitted into the recess, it is easy to position and fix the one end portion of the shielding portion to the rotating wheel or the stationary wheel, so that the assembly of the bearing can be improved. .

  In the inventions described so far, it is desirable that the shielding portion is molded integrally with a member for providing the shielding portion. In this case, since the number of parts of the bearing can be reduced, the cost required for manufacturing the bearing can be suppressed. Here, the “member that provides the shielding portion” refers to any of an outer ring, an inner ring, and a seal member.

  In this invention, the end of the rotating ring or the end of the stationary ring is extended and the shielding part is provided integrally with these members. There is a method of extending the end of the stationary ring or the end of the stationary ring. In this case, since the shielding part can be provided simultaneously with the forming of the rotating wheel or the stationary wheel by forging or the like, a separate process for providing the shielding part becomes unnecessary, and the number of bearing manufacturing processes can be reduced. it can. As a result, the cost required for manufacturing the bearing can be suppressed.

  In the inventions described so far, the shielding portion can be formed of one material selected from rubber, resin, and metal. As the rubber, hydrogenated nitrile rubber (H-NBR), nitrile rubber (NBR), fluorine rubber (FKM), and the like can be used. Moreover, as the resin, synthetic resins such as polyamide can be used. Furthermore, iron, stainless steel, etc. can be used as a metal.

  When rubber is used in the above invention, it is desirable to use hydrogenated nitrile rubber (H-NBR). Since the hydrogenated nitrile rubber is excellent in water resistance, the shielding portion can be provided with muddy water resistance.

  In the inventions described so far, it is desirable that the seal member be a non-contact type. In this case, since the seal member is not brought into contact with the peripheral member (for example, the rotating wheel or the stationary wheel), even if the rotating wheel and the stationary wheel rotate relative to each other and the bearing internal pressure rises, the seal member and the peripheral member It is possible to easily release the bearing internal pressure by letting the air inside the bearing escape to the outside of the bearing from the non-contact portion (gap) therebetween. For this reason, it is possible to prevent the bearing internal pressure from rising excessively and to prevent the bearing torque (force to rotate the rotating wheel) from increasing. As a result, the power transmission of the bearing can be made smooth.

  A ball bearing for a clutch release bearing device according to the present invention is disposed on at least one of a rotating wheel, a stationary wheel, and a seal member, extending along the rotation shaft and disposed on the bearing outer side from the other end of the seal member. With a shield. For this reason, even if the muddy water splashed on the bearing tries to enter the inside of the bearing through the other end portion of the seal member, the muddy water is blocked by the shielding portion before reaching the other end portion of the seal member. It becomes difficult to reach the other end of the seal member. As a result, it is difficult for muddy water to enter the bearing, and the muddy water resistance of the bearing can be improved without depending on the seal member excessively. Thereby, the life of the seal member can also be extended.

  Further, since the shielding portion is a non-contact type, the bearing internal pressure can be easily released even if the rotating wheel and the stationary wheel rotate relative to each other. Therefore, it is possible to prevent the bearing internal pressure from increasing excessively and prevent the bearing torque from increasing. As a result, friction loss in the bearing (slippage between the diaphragm spring and the bearing can be prevented, and both can be worn) can be prevented.

  Furthermore, even when a contact type seal member is used, the shielding portion makes it difficult for muddy water to reach the other end portion of the seal member, so that the sealing performance of the seal member can be stabilized. Further, since the muddy water does not easily reach the other end of the seal member, the problem described in the conventional example (FIG. 7) when the contact type is used as the seal member does not occur. In addition, the shielding part of the present invention can prevent foreign matters (flying objects) from entering the inside of the bearing other than muddy water.

  Embodiments of the present invention will be described below with reference to the accompanying drawings (FIGS. 1 to 6).

  FIG. 2 shows a direct cylinder type clutch release bearing device mounted on an FR vehicle and provided with a ball bearing according to the present invention. The bearing device 1 includes a cylindrical outer main body 2, a fixed component 3, a piston 4, and a ball bearing 12 as main parts.

  The outer body 2 is fixed to the casing 22 on the transmission side (right side in the drawing: hereinafter referred to as rear side), and has a cavity 8 extending to the engine side (left side in the drawing: hereinafter referred to as front side). On the inner peripheral side of the cavity 8, an annular piston 4 and an annular fixed part 3 are sequentially arranged so as to be axially movable.

  The fixed component 3 includes a guide tube 5 extending in the axial direction, and the front side extends to the outside of the outer body 2. The piston 4 is disposed so as to be movable in the axial direction with respect to the fixed component 3, and is supported by a piston support tube 13 interposed between the piston 4 and the fixed component 3. A preload spring 21 is disposed on the outer peripheral surface of the piston 4. Since the preload spring 21 is mounted inside a mounting member (not shown) that is press-fitted into the rear end of the inner ring 15 of the bearing 12, the preload spring 21 cooperates with the inner ring 15 of the bearing 12.

  The outer body 2 has a groove 10 formed in the inner peripheral surface 9 of the rear side portion, and a radial edge 11 formed by extending the rear end of the guide tube 5 radially outward in the groove 10. Is fitted.

  The radial edge 11, the cavity 8, and the piston 4 constitute a hollow variable volume chamber 6. The variable volume chamber 6 is filled with a control fluid such as oil, and the inside of the cavity 8 is pressurized and depressurized by the control fluid. The variable volume chamber 6 is connected to a control hydraulic pressure generator (not shown).

  The bearing 12 according to the first embodiment of the present invention includes an outer ring 14 that is a rotating wheel, an inner ring 15 that is a stationary ring, a ball 16 that is interposed between the outer ring 14 and the inner ring 15, and the ball 16. The main part is comprised with the cage 26 to hold | maintain. When the outer ring 14 rotates with reference to the rotation axis X (indicated by a one-dot chain line in the figure), the outer ring 14 and the inner ring 15 rotate relative to each other. The front side end portion of the outer ring 14 extends radially inward (lower side in the drawing) to form a flange portion 19. A front side end portion of the inner ring 15 extends radially inward to form a flange portion 20. Note that the flange portion 19 of the outer ring 14 is in a state of being in constant contact with the diaphragm spring 30 by the preload spring 21.

  A sealed space is formed between the outer ring 14 and the inner ring 15 by annular seal members 17 and 18 as shown in an enlarged view in FIG. Due to the seal members 17 and 18, a lubricating component such as grease enclosed in the inside of the bearing 12 (in the space between the outer ring 14 and the inner ring 15, the central portion where the ball 16 is interposed: hereinafter referred to as the inside of the bearing). It is possible to prevent leakage to the outside of the bearing 12 (hereinafter referred to as the bearing outside).

  The seal members 17 and 18 are formed by vulcanizing and welding rubber members 33 and 34 made of hydrogenated nitrile rubber (H-NBR) to the cores 31 and 32, so that the water resistance and wear resistance are improved. It has. As the rubber material, nitrile rubber (NBR) or fluorine rubber (FKM) having heat resistance and wear resistance can also be used.

  The front-side seal member 17 has an inverted U-shaped cross section. The front-side seal member 17 has a mounting end 17c (outer diameter end) fixed to the inner surface 23 of the outer ring 14 and a contact lip 17a at the inner diameter end (other end). The contact lip 17 a is in axial contact with the outer end surface 25 of the flange 20 of the inner ring 15. Thereby, it is possible to prevent muddy water from entering the bearing. Further, since the contact pressure of the axial contact is smaller than that of the radial contact, the contact lip 17a can easily release the above-described axial contact when the outer ring 14 rotates and the bearing internal pressure rises. Therefore, it is possible to prevent an excessive increase in the bearing internal pressure and to prevent an increase in bearing torque. As a result, it is possible to prevent slippage at the contact portion between the flange portion 19 of the outer ring 14 and the diaphragm spring 30, and to prevent wear of both.

  The rear side sealing member 18 has a U-shaped cross section. The rear side seal member 18 has an attachment end 18c (outer diameter end) fixed to the inner surface 23 of the outer ring 14, and has a main lip 18a and an auxiliary lip 18b at the inner diameter end (other end). The inner diameter end (main lip 18a) is in radial contact with the outer surface 24 of the inner ring 15, and the auxiliary lip 18b is not in contact. The radial contact prevents muddy water from entering the bearing. Moreover, even if the muddy water passes between the inner diameter end portion (main lip 18a) and the outer surface 24 of the inner ring 15 by the auxiliary lip 18b, this muddy water can be prevented from entering the inside of the bearing.

  Below, the point which becomes the characteristic of this embodiment is described.

  The above-described rear side sealing member 18 extends the rubber member 34 radially outward, and further extends to the rear side, thereby arranging the shielding portion 35 on the rear side of the rear side end portion 14a of the outer ring 14. Set up. Thereby, the shielding part 35 will be in the state arrange | positioned rather than the internal diameter edge part (main lip 18a) of the rear side sealing member 18 at the bearing outer side (arrow A side).

  In the present embodiment, the muddy water splashed on the rear side of the bearing 12 enters from the bearing opening side as indicated by an arrow A, and the inner diameter end (main lip 18a) of the rear side seal member 18 and the inner ring 15 It tries to enter the inside of the bearing 12 through the contact portion with the outer surface 24 of the bearing. However, before the muddy water reaches the inner diameter end portion (main lip 18a) of the rear side seal member 18, the bearing outer side (arrow A side) than the inner diameter end portion (main lip 18a) of the rear side seal member 18. It is blocked by the shielding part 35 arranged in the. That is, as shown by the arrow A, even if muddy water from the outside of the bearing reaches the inner diameter end portion (main lip 18a) of the rear side seal member 18, it is blocked by the shielding portion 35 disposed in this path. The muddy water is unlikely to reach the inner diameter end (main lip 18a) of the rear seal member. As a result, muddy water can be prevented from entering the bearing without excessively depending on the rear side seal member 18 and the muddy water resistance of the bearing 12 can be improved. Thereby, the life of the rear side sealing member 18 can be extended. In addition, the shielding part 35 can also prevent foreign matters (flying objects) other than muddy water from entering the bearing.

  Further, the shielding portion 35 makes it difficult for muddy water to reach the inner diameter end portion (main lip 18a) of the rear side seal member 18. Therefore, the sealing performance of the rear side sealing member 18 can be stabilized. Further, since the shielding portion 35 makes it difficult for muddy water to reach the inner diameter end portion (main lip 18a) of the rear side seal member 18, the muddy water penetrates to the vicinity of the inner diameter end portion (main lip 18a). The problems described in the conventional example (FIG. 7) such as being difficult to be discharged to the outside of the bearing and being stuck between the inner diameter end portion (main lip 18a) and the outer surface 24 of the inner ring 15 do not occur. .

  Since the shielding part 35 is formed integrally with the rear side sealing member 18 by extending the rubber member 34 of the rear side sealing member 18, it is not necessary to use a separate part as the shielding part 35. Thereby, since the number of parts of the bearing 12 can be reduced, the cost required for manufacturing the bearing 12 can be suppressed.

  The shielding part is not limited to the one in the present embodiment, and various changes can be made. The embodiment will be described below.

  FIG. 3 shows a ball bearing 42 for a clutch release bearing device according to a second embodiment of the present invention. In the following embodiment, the basic structure of the bearing is the same as that of the first embodiment shown in FIG. 1, and therefore, the description of the overlapping structure, operation, and effect is omitted or simplified.

  In the present embodiment, in the rear side seal member 18, the portion between the attachment end portion 18 c (outer diameter end portion) and the inner diameter end portion (main lip 18 a) is thickened along the rotation axis X. A shielding part 45 extending to the rear side (projecting to the rear side) is provided. Further, the shielding portion 45 is provided by extending the rubber member 34 of the rear side sealing member 18 to the rear side. Thereby, the shielding part 45 can be formed integrally with the rear side seal member 18 and at the bearing outer side (arrow A side: opening of the bearing) from the inner diameter end part (main lip 18a) of the rear side seal member 18. Side). For this reason, even if muddy water from the outside of the bearing reaches the inner diameter end (main lip 18a) of the rear side seal member 18 as shown by the arrow A, it is blocked by the shielding portion 45 disposed in the path. Can do.

  FIG. 4 shows a ball bearing 52 for a clutch release bearing device according to a third embodiment of the present invention.

  In the present embodiment, when the outer ring 14 is forged, the shielding portion 55 is provided by extending the rear side end portion 14a to the rear side along the direction of the rotation axis X. Thereby, the shielding part 55 can be arrange | positioned rather than the internal-diameter end part (main lip 18a) of the rear side sealing member 18 at the bearing outer side (arrow A side). That is, as shown by the arrow A, even if muddy water from the outside of the bearing tries to reach the inner diameter end portion (main lip 18a) of the rear side sealing member 18, it is blocked by the shielding portion 55 disposed in the intrusion path. Can do.

  In the case of the present embodiment, the shielding portion 55 can be formed at the same time as the outer ring 14 is forged. Therefore, a separate process for providing the shielding part 55 is not necessary, and the number of manufacturing processes of the bearing 52 can be reduced. As a result, the cost required for manufacturing the bearing 52 can be significantly reduced.

  FIG. 5 shows a ball bearing 62 for a clutch release bearing device according to a fourth embodiment of the present invention.

  In the present embodiment, a recess 66 is formed in the outer peripheral surface 14b of the rear side end portion 14a of the outer ring 14, and a shielding portion 65 extending rearward along the direction of the rotation axis X is formed on the bottom surface 66a of the recess 66. Molded integrally with the outer ring 14. As this method, there is a method of welding rubber or resin to the bottom surface 66 a of the recess 66. Thereby, the front side end portion 65 a (one end portion) of the shielding portion 65 is fixed to the recess 66 of the outer ring 14, and the rear side end portion 65 b (other end portion) of the shielding portion 65 is fixed to the inner diameter end of the rear side sealing member 18. It can be arranged on the bearing outer side (arrow A side) than the portion (main lip 18a). That is, as shown by the arrow A, even if muddy water from the outside of the bearing tries to reach the inner diameter end portion (main lip 18a) of the rear side seal member 18, the rear side end portion of the shielding portion 65 disposed in the path. It can be blocked by 65b (the other end).

  In the case of this embodiment, the shielding portion 65 is formed integrally with the outer ring 14 as in the first embodiment shown in FIG. Therefore, it is not necessary to use another part as the shielding part 65. As a result, the number of parts of the bearing 62 can be reduced, and the cost required for manufacturing the bearing 62 can be suppressed.

  In the present embodiment, the shielding portion 65 is provided on the bottom surface 66a of the recess 66 formed in the outer peripheral surface 14b of the rear side end portion 14a of the outer ring 14. In this case, since the shielding part 65 is housed in the recess 66 and does not protrude radially outward from the outer ring 14, the appearance of the bearing 62 is not impaired. Further, since the shielding portion 65 does not protrude from the outer ring 14, the protruding portion of the shielding portion 65 does not contact the peripheral members of the bearing 62 when the bearing 62 is assembled to the vehicle. Therefore, the assembly of the bearing 62 to the vehicle becomes easy.

  In addition, when using rubber | gum as a raw material of the shielding part 65, for example, hydrogenated nitrile rubber (H-NBR) and nitrile rubber (NBR) excellent in water resistance and abrasion resistance, excellent in heat resistance and abrasion resistance Fluorine rubber (FKM) can be used. Moreover, when using resin as the raw material of the shielding part 65, synthetic resins, such as polyamide, can be used, for example.

  FIG. 6 shows a ball bearing 72 for a clutch release bearing device according to a fifth embodiment of the present invention.

  In the present embodiment, a recess 76 is formed in the inner peripheral surface 23 of the rear side end portion 14 a of the outer ring 14, and a cylindrical metal shielding portion 75 is fitted into the recess 76. As the metal material, for example, iron or stainless steel can be used.

  The shielding portion 75 includes a small-diameter end portion 75a (hereinafter referred to as a small-diameter portion 75a), a middle portion 75c extending radially outward from a rear-side end portion of the small-diameter portion 75a, and a rotation axis X from the intermediate portion 75c. And the other end portion 75b on the large diameter side extending to the rear side (hereinafter referred to as the large diameter portion 75b). The above-described fitting of the shielding portion 75 is performed by fitting the small diameter portion 75 a into the recess 76. In this case, since the small diameter portion 75a can be positioned in the direction along the rotation axis X by the recess 76, it becomes easy to fix the small diameter portion 76a to the outer ring 14, and the assembling property of the bearing 72 can be improved. it can.

By this fitting, the intermediate portion 75 c is brought into close contact with the side end surface 14 a ₁ of the rear side 14 a of the outer ring 14. As a result, the large-diameter portion 75b projects from the outer ring 14 to the rear side along the rotation axis X from the rear-side end portion 14a. Furthermore, since the large-diameter portion 75b of the shielding portion 75 is disposed on the bearing outer side (arrow A side) with respect to the inner-diameter end portion (main lip 18a) of the rear-side seal member 18, this large-diameter portion 75b can block muddy water from the outside of the bearing. That is, as shown by the arrow A, even if muddy water from the outside of the bearing tries to reach the inner diameter end portion (main lip 18a) of the rear side seal member 18, the large diameter portion 75b of the shielding portion 75 disposed in the path. Can be prevented.

  Further, the small diameter portion 75a of the shielding portion 75 is nipped and fixed between the outer ring 14 (the bottom surface 76a of the recess 76) and the mounting end portion 18c (the outer diameter end portion) of the rear side seal member 18.

  In the case of this embodiment, the mounting end 18c (outer diameter end) of the rear side seal member 18 is fixed to the outer ring 14, and at the same time, the small diameter part 75a of the shielding part 75 fitted in the recess 76 of the outer ring 14. Can be fixed to the outer ring 14. Therefore, the assembling property of the bearing 72 is improved. Moreover, since the shielding part 75 can be fixed by the rear side sealing member 18, the attachment state of the shielding part 75 can be stabilized.

In the present embodiment, a recess 76 is formed in the inner surface 23 of the rear side end 14a of the outer ring 14, and the small diameter portion 75a of the shielding portion 75 is fixed in the recess 76, and the large diameter of the shielding portion 75 is fixed. The part 75c was protruded to the rear side. However, a recess is formed in the side end surface 14a ₁ of the rear side end portion 14a of the outer ring 14, and _one end portion of the cylindrical shielding portion is fitted into the recess, and the other end portion of the shielding portion is connected to the outer ring 14. The rear side end portion 14a may protrude toward the rear side along the rotation axis X (not shown).

  Alternatively, as in the fourth embodiment shown in FIG. 5, a recess is formed in the outer peripheral surface 14b of the rear side end 14a of the outer ring 14, and one end of the cylindrical shielding portion is externally fitted into this recess. At the same time, the other end portion of the shielding portion may protrude from the rear end portion 14a of the outer ring 14 to the rear side along the rotation axis X (not shown).

  In the first to fifth embodiments shown in FIG. 1 to FIG. 6 described so far, the rear-side seal member 18 has an inner ring end on the inner ring as long as the shielding portion can provide sufficient muddy water resistance to the bearing. It is possible to adopt a non-contact type that does not contact the outer surface 24 of the 15.

  In this case, even if the outer ring 14 rotates and the bearing internal pressure rises, the air inside the bearing is released from the non-contact portion (gap) between the inner diameter end of the rear side seal member 18 and the inner ring 15 to the outside of the bearing. be able to. Therefore, it is possible to prevent the bearing internal pressure from increasing excessively and prevent the bearing torque from increasing. As a result, it is possible to prevent slippage at the contact portion between the flange portion 19 of the outer ring 14 and the diaphragm spring 30, and to prevent wear of both.

  Further, as in the case where the rear-side seal member 18 is a contact type, the inner-diameter end portion is not brought into contact with the outer surface 24 of the inner ring 15, so that the rear-side seal member 18 is worn by contact with the inner ring 15, and its sealing performance Will not drop.

  Although the embodiment of the present invention has been described above, the present invention is not limited to this, and can be arbitrarily changed without departing from the technical idea described in the claims.

  For example, in the present embodiment, the present invention is applied to a bearing in which the seal members 17 and 18 are fixed to the rotating wheel (outer ring 14), but the present invention is also applied to a bearing in which the seal members 17 and 18 are fixed to the stationary ring (inner ring 15). The invention can be applied.

  Further, the rear side end portion of the inner ring 15 may be extended outward in the radial direction, and a shielding portion extending toward the front side may be provided at the extended end portion. Alternatively, the inner ring 15 may be provided with a shielding part via another bearing component (for example, a bearing cover) attached to the rear side end of the inner ring 15.

It is sectional drawing which shows the 1st Embodiment of this invention. It is sectional drawing which shows the clutch release bearing apparatus provided with the ball bearing shown in FIG. It is sectional drawing which shows the 2nd Embodiment of this invention. It is sectional drawing which shows the 3rd Embodiment of this invention. It is sectional drawing which shows the 4th Embodiment of this invention. It is sectional drawing which shows the 5th Embodiment of this invention. It is sectional drawing which shows the conventional ball bearing for clutch release bearing apparatuses.

Explanation of symbols

1 Clutch release bearing device (direct cylinder type)
12, 42, 52, 62, 72 Ball bearing for clutch release bearing device 14 Outer ring (rotating ring)
15 Inner ring (stationary ring)
16 Balls 17, 18 Seal member 17a Contact lip 18a Main lip 18b Auxiliary lips 17c, 18c Mounting end (outer diameter end)
26 Cage 35, 45, 55, 65, 75 Shield 66, 76 Recess

Claims (12)

A rotating wheel and a stationary wheel that rotate relative to each other, a ball interposed between the rotating wheel and the stationary wheel, and a seal member that forms a sealed space between the rotating wheel and the stationary wheel, One end portion of the seal member is a ball bearing for a clutch release bearing device forming an attachment end portion fixed to the rotating wheel or the stationary wheel,
At least one of the rotating wheel, the stationary wheel, and the seal member includes a shielding portion that extends along the rotation axis of the bearing and is disposed on the bearing outer side with respect to the other end portion of the seal member. Ball bearings for clutch release bearing devices.   The ball bearing for a clutch release bearing device according to claim 1, wherein the shielding portion is provided in a portion between the attachment end portion and the other end portion of the seal member.   2. The ball bearing for the clutch release bearing device according to claim 1, wherein the shielding portion is formed by extending an end portion of the rotating wheel or an end portion of the stationary wheel.   The said shield part is a ball bearing for clutch release bearing apparatuses as described in any one of Claims 1-3 currently shape | molded integrally with the member which provides the shield part.   One end of the shielding portion protrudes from the end of the rotating wheel or the end of the stationary wheel, and the other end is sandwiched between the rotating wheel or the stationary wheel and the mounting end of the seal member. A ball bearing for a clutch release bearing device according to claim 1.   The said shielding part is a ball bearing for clutch release bearing apparatuses as described in any one of Claims 1-5 currently shape | molded with the raw material selected from rubber | gum, resin, and a metal.   The ball bearing for a clutch release bearing device according to any one of claims 1 to 6, wherein the seal member is a non-contact type.   The ball bearing for clutch release bearing devices according to any one of claims 5 to 7, wherein a recess is formed in a peripheral surface of the rotating wheel or the stationary wheel, and a shielding portion is fitted in the recess.   The clutch release according to claim 8, wherein the shielding part has an inverted Z-shaped cross section including a small diameter part, an intermediate part extending radially outward from the small diameter part, and a large diameter part extending from the intermediate part. Ball bearings for bearing devices.   The ball bearing for a clutch release bearing device according to claim 4, wherein a recess is formed on an outer surface of the rotating wheel or the stationary wheel, and a shielding portion extending from the recess is formed integrally with the outer ring on a bottom surface of the recess.   The ball bearing for a clutch release bearing device according to claim 10, wherein the shielding portion and the rotating wheel or the stationary wheel are formed by welding rubber or resin to the bottom surface of the recess.   The ball bearing for a clutch release bearing device according to any one of claims 6 to 11, wherein the shielding portion is formed of hydrogenated nitrile rubber (H-NBR).

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