JP2010112532A - 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 surely improving muddy water resistance without increase the number of components. <P>SOLUTION: A front side seal member 17 has a cross section in a doglegged shape, and is closely attached over from a foundation part 29 to a flange 20 of an inner ring 15 by fixing an attachment end 17c (outside diameter end) to an outer surface 24 of the foundation part 29 of the inner ring 15. An inside diameter end of the front side seal member 17 is extended to an inner peripheral surface side of a flange 19 of an outer ring 14, and a shielding part 27 is obtained. A bearing opening 40 is covered by the shielding part 27. A lip 28 brought into contact with an inner surface 19c of the flange 19 of the outer ring 14 is provided in a portion between the attachment end 17c and the shielding part 27. An inner peripheral surface 27a of the shielding part 27 is formed in the shape wherein a tapered enlargement diameter part having a radial dimension from a rotating axis X increasing toward a distal end side from the inner ring side and a straight line part extending along the rotating axis X are continued in order from the distal end side. The attachment end 17c of the front side seal member 17 is pressed in and fitted in a recession 29a formed on the outer surface 24 of the foundation part 29 of the inner ring 15. <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 radial misalignment occurs between the engine-side shaft center and the transmission-side shaft center, this ball bearing moves in the radial direction in accordance with this misalignment, and automatically adjusts both shaft centers. To be mindful.

  FIG. 8 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: Intrusion of muddy water (foreign matter) into 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.
JP 2006-189086 A

  Since the bearing 112 described in Patent Document 1 shown in FIG. 8 uses contact-type seal members 117 and 118, muddy water (foreign matter) trying to enter the inside of the bearing is the inner diameter end portion of the seal members 117 and 118 ( It is blocked by the main lips 117a, 118a). Therefore, it is difficult for muddy water to enter the bearing.

  However, in an environment such as an off-road course in which muddy water is extremely likely to enter, the bearing 112 may not be sufficient in muddy water resistance (foreign matter blocking function).

  As a means for solving the above problems, a method of providing a plurality of annular seal members 117 and 118 in the direction from the bearing outer side to the bearing inner side can be considered.

  However, in this case, since a plurality of seal members are used, there is a problem that the number of parts of the bearing increases and the cost necessary for manufacturing the bearing increases.

  The present invention has been made in view of the above circumstances, and an object thereof is to provide a ball bearing for a clutch release bearing device that can easily improve muddy water resistance (foreign matter blocking function) without increasing the number of parts. And

  A ball bearing for a clutch release bearing device according to the present invention for solving the above-mentioned problems is an outer ring that is a rotating ring, an inner ring that is a stationary ring, and a ball that is interposed between the outer ring and the inner ring, A seal member that forms a sealed space between the outer ring and the inner ring, and an end of the outer ring extends radially inward to form a flange, and an end of the flange of the outer ring and the inner ring A ball bearing for a clutch release bearing device in which a bearing opening is formed between the seal member, one end of which forms an attachment end fixed to the inner ring, and the other end of the seal member A cylindrical shielding portion is provided which extends toward the inner peripheral surface side of the flange portion of the outer ring and covers the bearing opening.

  In this way, even if muddy water (foreign matter) tries to enter the inside of the bearing from the inner diameter side of the bearing through the bearing opening, this muddy water is blocked by the shielding portion that covers the bearing opening. Thereby, it is possible to prevent muddy water from entering the bearing.

  It is desirable to provide an annular lip in contact with the inner surface of the flange portion of the outer ring at a portion between the mounting end portion of the seal member and the shielding portion.

  In this case, even if the muddy water cannot be blocked by the shielding portion, the muddy water is blocked by the lip. Thereby, the infiltration of muddy water into the bearing can be efficiently prevented, and the muddy water resistance (foreign matter blocking function) of the bearing can be greatly improved.

  It is desirable to provide a plurality of the lips in the direction from the bearing outer side to the bearing inner side. As a result, even if the muddy water cannot be blocked by the shielding portion, the muddy water is blocked by the plurality of lips. Thereby, the muddy water resistance of a bearing can be improved reliably.

  Further, in the invention having a lip, it is desirable that the lip is in axial contact with the inner surface of the flange portion of the outer ring.

  Axial contact has a smaller contact pressure than radial contact (radial contact). Therefore, even if the air inside the bearing expands due to the temperature rise of the bearing 112 due to the rotation of the outer ring, the lip can easily release the bearing internal pressure by releasing contact with the inner surface of the flange portion of the outer ring. . For this reason, it is possible to prevent the bearing torque (the force required to rotate the bearing) from increasing due to an excessive increase in the bearing internal pressure, and to smoothly transmit the power of the bearing.

  In the above invention having a lip in the shielding portion, it is desirable to provide an annular seal portion that protrudes toward the inside of the bearing and is disposed between the shielding portion of the seal member and the lip at the flange portion of the outer ring.

  In this case, a labyrinth gap is formed between the shielding portion of the seal member and the lip. Therefore, even if the muddy water cannot be blocked by the shielding portion, the muddy water hardly reaches the lip due to the labyrinth gap. Therefore, the infiltration of muddy water into the bearing can be prevented very efficiently, and the muddy water resistance of the bearing can be greatly improved.

  In the above invention having the seal part on the flange part of the outer ring, it protrudes toward the flange part of the outer ring at a portion between the shielding part and the lip, and is closer to the bearing inside than the seal part of the flange part of the outer ring. It is desirable to provide an annular auxiliary lip for placement.

  In this case, a labyrinth gap having a longer distance from the bearing outer side to the bearing inner side is formed between the shielding portion of the seal member and the lip than when there is no auxiliary lip. Therefore, the action and effect of the invention in which the labyrinth gap is formed can be improved.

  The auxiliary lip is preferably brought into contact with the inner surface of the flange portion of the outer ring. In this case, even if the muddy water cannot be blocked by the shielding portion, the muddy water is blocked by the auxiliary lip. Due to this action and the action of the labyrinth gap formed by the auxiliary lip, the muddy water prevention performance of the auxiliary lip can be improved.

  Further, it is desirable that the auxiliary lip is in axial contact with the inner surface of the flange portion of the outer ring.

  Axial contact (axial contact) has a smaller contact pressure than radial contact (radial contact). Therefore, in the case of the present invention, the auxiliary lip remains on the outer ring 14 even if the outer ring rotates and the bearing internal pressure rises, as in the already described invention in which the seal member is in axial contact with the inner surface of the flange portion of the outer ring. The internal pressure of the bearing can be easily released by releasing the contact with the part. As a result, the bearing torque can be prevented from increasing.

  In the inventions described so far, it is desirable to provide a diameter-expanded portion on the inner peripheral surface of the shielding portion from the inner ring side toward the tip end side so that the radial dimension from the rotation shaft of the bearing increases. Here, “providing the enlarged diameter portion” means providing the enlarged diameter portion on the inner surface of the shielding portion without reducing the radial dimension from the rotating shaft of the bearing from the inner ring side toward the distal end side. .

  In this case, when the muddy water (foreign matter) adhering to the inner peripheral surface of the shielding portion is affected by the centrifugal force generated by the relative rotation of the outer ring and the inner ring, the enlarged diameter portion of the shielding portion leads to the tip side (outside of the bearing). Since it becomes easy to flow (move), it is easy to be splashed to the outside of the bearing. As a result, the already-described muddy water blocking function of the blocking unit can be improved.

  In the present invention, it is desirable that the enlarged diameter portion has a tapered shape. In this case, the muddy water splashed on the inner peripheral surface of the shielding portion smoothly flows toward the tip portion along the shape. In other words, the muddy water splashed on the inner surface of the shielding part is likely to flow on the inner peripheral surface of the shielding part and be splashed to the outside of the bearing. As a result, the muddy water blocking function (foreign material blocking function) of the shielding unit can be greatly improved.

  Or it is desirable to bend the front-end | tip part of the said shielding part fixed to an inner ring | wheel to the inner diameter side. In this case, the muddy water adhering to the inner peripheral surface of the shielding portion is less likely to flow to the outer peripheral surface of the shielding portion due to the bent tip portion. As a result, the already-described muddy water blocking function of the blocking unit can be improved.

  The ball bearing for the clutch release bearing device of the present invention has one end portion (attachment end portion) fixed to the inner ring, and the other end portion having a bearing opening formed between the end portion of the flange portion of the outer ring and the inner ring. The shielding part is covered. Thereby, the muddy water (foreign matter) trying to enter the inside of the bearing from the inner diameter side through the bearing opening is blocked by the shielding portion. As a result, the infiltration of muddy water into the bearing can be prevented, and the muddy water resistance (foreign matter blocking function) of the bearing can be easily improved.

  Moreover, in the case of this invention, a shielding part is provided in a sealing member and the muddy water resistance of a bearing is improved without increasing the number of sealing members. Therefore, the number of parts of the bearing can be reduced, and the cost required for manufacturing the bearing can be suppressed.

  Embodiments of the present invention will be described below with reference to the accompanying drawings (FIGS. 1 to 7).

  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. As the outer ring 14 rotates with reference to the rotation axis X of the bearing 12 (indicated by the alternate long and short dash 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, in addition to nitrile rubber (NBR), wear-resistant fluorine-based rubber (FKM) can also be used.

  The rear side sealing member 18 has a U-shaped cross section. The rear side sealing 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. The 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. Due to the radial contact, intrusion of muddy water (foreign matter) into the bearing is prevented. Further, the auxiliary lip 18b makes it difficult for muddy water to reach the main lip 18a, and the above-described function of the main lip 18a is improved.

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

  The front-side seal member 17 has a cross-sectional shape and is attached in close contact from the base portion 29 of the inner ring 15 (a portion extending along the rotation axis X shown in FIG. 2) to the flange portion 20. .

  The front-side seal member 17 has an attachment end 17c, which is an outer diameter end, fixed to the outer surface 24 of the base portion 29 of the inner ring 15, and an inner diameter end extending along the flange 20 of the inner ring 15, The flange portion 19 is extended to the inner peripheral surface 19 a side (hereinafter referred to as the inner peripheral surface side) to form a shielding portion 27. As a result, the bearing opening 40 between the flange portion 19 of the outer ring 14 and the inner ring 15 is covered with the shielding portion 27, and the inner peripheral surface 19 a of the flange portion 19 of the shielding portion 27 and the outer ring 14. A seal gap 41 is formed between the two.

  Thus, in the present embodiment, the inner diameter end of the front side seal member 17 is extended to the inner peripheral surface side of the flange portion 19 of the outer ring 14 to be a shielding portion 27, and the bearing opening 40 is formed by the shielding portion 27. cover. For this reason, it is possible to prevent the muddy water from entering the inside of the bearing by blocking the muddy water entering the inside of the bearing from the inner diameter side of the bearing 12 through the bearing opening 40 by the shielding portion 27. As a result, the muddy water resistance (foreign matter blocking function) of the bearing 12 can be improved.

  Further, as described above, the shielding part 27 is provided on the front side seal member 17, and the muddy water resistance of the bearing 12 can be improved without increasing the number of the front side seal members 17. Therefore, the number of parts of the bearing 12 can be reduced, and the cost required for manufacturing the bearing 12 can be suppressed.

The inner peripheral surface 27a of the shielding part 27 has a taper-shaped diameter expansion in which the radial dimension from the rotation axis X (see FIG. 2) increases from the inner ring 15 side (hereinafter referred to as the inner ring side) to the tip side. The portion 27a ₁ and the linear portion 27a ₂ extending along the rotation axis X are formed into a continuous shape in order from the front side.

Thus, muddy water deposited on the inner peripheral surface 27a of the shielding section 27 (foreign matter) is when affected by the centrifugal force generated by the rotation of the outer ring 14, smooth distally along the tapered shape of the enlarged diameter portion 27a ₁ Since it flows (moves) to the front, it is easy to jump to the front side (the bearing outer side). As a result, the already-described muddy water blocking function of the blocking unit 27 can be greatly improved. As in the present embodiment, the diameter-enlarged portion is such that the radial dimension from the rotation axis X (see FIG. 2) on the inner peripheral surface 27a of the shielding portion 27 does not decrease from the inner ring side toward the tip side. It is necessary to provide in. In this way, since the muddy water that is going to flow from the inner ring side toward the tip side is not blocked by the reduced diameter portion, it is possible to surely obtain the action and effect of the already described enlarged diameter portion.

  Furthermore, the inner peripheral surface 27a of the shielding part 27 may be only a diameter-expanded part in which the radial dimension from the rotation axis X (see FIG. 2) increases from the inner ring side end part to the tip part. In this case, the muddy water adhering to the inner peripheral surface 27a of the shielding part 27 is more likely to flow to the tip side than the case where the diameter-enlarged part is partially provided on the inner peripheral surface 27a of the shielding part 27. The muddy water blocking function is greatly improved. Even in this case, it is desirable that the enlarged diameter portion has a tapered shape as described above.

  In the front-side seal member 17, a lip 28 that contacts the inner surface 19 c of the flange portion 19 of the outer ring 14 is provided between the attachment end portion 17 c and the shielding portion 27. In this case, even if the muddy water cannot be blocked by the shielding portion 27, the muddy water is blocked by the lip 28. As a result, the infiltration of muddy water into the bearing can be efficiently prevented, and the muddy water resistance of the bearing 12 can be greatly improved.

  The lip 28 makes axial contact (axial contact) with the inner surface 19c of the flange portion 19 of the outer ring 14. Further, a seal gap 41 is formed between the inner peripheral surface 19 c of the flange portion 19 of the outer ring 14 and the shielding portion 27 of the front side seal member 17.

  Axial contact has a smaller contact pressure than radial contact (radial contact). Therefore, even if the air inside the bearing expands due to the temperature rise of the bearing 12 due to the rotation of the outer ring 14, the lip 28 releases contact with the inner surface 19 c of the flange portion 19 of the outer ring 14 to easily release the bearing internal pressure. Cheap. The cooperation between the axial contact and the seal gap 41 allows the bearing internal pressure to be easily released even if the bearing internal pressure increases. For this reason, bearing torque (force that rotates the outer ring 14) increases due to an excessive increase in the bearing internal pressure, and it is possible to reliably prevent slippage at the contact portion between the diaphragm spring 30 and the flange portion 19 of the outer ring 14. it can. As a result, power transmission between the diaphragm spring 30 and the flange portion 19 (bearing 12) of the outer ring 14 can be made smooth.

  The mounting end 17c (outer diameter end) of the front seal member 17 is press-fitted into a recess 29a extending to the rear side formed in the outer surface 24 at the front end of the base portion 29 of the inner ring 15.

  Further, the attachment end 17c of the front side seal member 17 is formed by extending the core 31 constituting the front side seal member 17 to the rear side. In this case, since the hardness and rigidity of the attachment end portion 17c can be ensured, the attachment end portion 17c can be easily fixed to the inner ring 15, and the state after fixation can be stabilized.

  The shielding part 27 and the lip 28 are formed by extending a rubber member 33 constituting the front side sealing member 17. Thereby, since it is not necessary to use another part as the shielding part 27 and the lip 28, the number of parts of the bearing 12 can be reduced, and the cost required for manufacturing the bearing 12 can be suppressed.

  The shape of the front-side seal member 17 according to the present invention is not limited to this embodiment, and various changes can be made. The embodiment will be described below.

  FIG. 3 shows a second embodiment (bearing 62) of the present invention. In addition, since the basic structure of the bearing of embodiment described below is the same as 1st Embodiment shown in FIG. 1, the description is abbreviate | omitted or simplified about the overlapping structure, an effect | action, an effect.

  In the present embodiment, the distal end portion 50 of the shielding portion 27 of the front side seal member 17 is bent toward the inner diameter side. If it does in this way, since the muddy water adhering to the internal peripheral surface 27a of the shielding part 27 will become difficult to flow to the outer peripheral surface 27b of the shielding part 27 by the bent front-end | tip part 50, the muddy water interruption | blocking function already mentioned of the shielding part 27 is mentioned. Can be improved.

  FIG. 4 shows a third embodiment (bearing 72) of the present invention. In the present embodiment, the distal end portion 19 b of the flange portion 19 of the outer ring 14 is extended to the rear side (bearing inner side) to form an annular seal portion 51. Accordingly, the seal portion 51 is disposed between the shielding portion 27 and the lip 28 of the front side seal member 17.

  In this case, a labyrinth gap is formed between the shielding part 27 and the lip 28 of the front side seal member 17. Therefore, even if the shielding part 27 cannot block the muddy water from the inner diameter side of the bearing 72, the muddy water hardly reaches the lip 28 due to the labyrinth gap. Thereby, since the infiltration of muddy water into the bearing can be prevented very efficiently, the muddy water resistance of the bearing 72 can be greatly improved.

  Further, since the seal portion 51 can be formed at the same time as the outer ring 14 is forged, it is not necessary to use a separate part as the seal portion 51. For this reason, the number of parts of the bearing 72 can be reduced, and the cost required for manufacturing the bearing 72 can be suppressed.

  In addition, you may make it provide the cyclic | annular seal | sticker part 51 in the multiple places of the direction which connects the bearing exterior (bearing outer side rather than the bearing opening part 40) and the bearing inside. In this case, since the distance from the bearing outer side to the bearing inner side of the labyrinth gap formed by the seal portion 51 is longer than that in the case of one seal portion 51, the above-described operation and effect of the labyrinth gap is improved. be able to.

  FIG. 5 shows a fourth embodiment (bearing 82) of the present invention. In the present embodiment, the lips 28 are provided at a plurality of locations (two locations) in the direction in which the outside of the bearing communicates with the inside of the bearing. Thereby, the infiltration of muddy water into the bearing can be prevented, and the muddy water resistance of the bearing 82 can be reliably improved. That is, the operation and effect of the first embodiment shown in FIG. 1 can be improved.

  FIG. 6 shows a fifth embodiment (bearing 92) of the present invention. In the present embodiment, in the bearing of the third embodiment shown in FIG. 4, an annular projecting toward the flange portion 19 of the outer ring 14 is provided at a portion between the seal portion 27 and the lip 28 of the front side seal member 17. An auxiliary lip 52 is provided. Thereby, the auxiliary lip 52 is disposed on the outer diameter side (bearing inner side) with respect to the seal portion 51 provided on the flange portion 19 of the outer ring 14.

  In this case, a labyrinth gap having a longer distance from the bearing outer side to the bearing inner side is formed between the shielding portion 27 of the front side seal member 17 and the lip 28 than in the case of the third embodiment shown in FIG. . Therefore, the action and effect of the labyrinth gap described in the third embodiment shown in FIG. 4 can be reliably obtained.

  In this embodiment as well, as in the first embodiment shown in FIG. 1, the front side end of the inner ring 15 (base portion 29) extends radially inward to form a flange portion 20. The front-side seal member 17 is attached to the inner ring 15 in a state of facing (or closely contacting) these portions over the flange portion 20.

  Thereby, the distance between the collar part 19 of the outer ring | wheel 14 and the front side seal member 17 becomes shorter than the case where a front side seal member is fixed to the inner ring | wheel which does not have a collar part. Therefore, the auxiliary lip 52 provided on the front seal member can be easily brought into contact with the inner surface 19c of the flange portion 19 of the outer ring 14.

  The auxiliary lip 52 is formed by extending the rubber member 33 constituting the front side seal member 17. Thereby, since it is not necessary to use another part as the auxiliary lip 52, the number of parts of the bearing 92 can be reduced and the cost required for manufacturing the bearing 92 can be suppressed.

  In addition, you may make it provide the auxiliary | assistant lip 52 in multiple places of the direction which connects the bearing exterior and a bearing inside. In this case, the distance from the bearing outer side to the bearing inner side of the labyrinth gap is longer than in the case of one auxiliary lip 52. Therefore, the action and effect of the labyrinth gap described in the third embodiment shown in FIG. 4 can be greatly improved.

  FIG. 7 shows a sixth embodiment (bearing 102) of the present invention. In the present embodiment, in the bearing of the fifth embodiment shown in FIG. 6, the tip end portion 52 a of the auxiliary lip 52 extends radially outward, and the inner surface 19 c of the flange portion 19 of the outer ring 14, similar to the lip 28. Axial contact.

  In this case, even if the muddy water from the inner diameter side of the bearing 102 cannot be blocked by the shielding portion 27, this muddy water can be blocked by the auxiliary lip 52. Due to this action and the action of the labyrinth gap described in the fifth embodiment shown in FIG. 6 formed by the auxiliary lip 52, the muddy water prevention performance of the auxiliary lip 52 can be improved.

  The operation and effect of the auxiliary lip 52 due to the axial contact described above is the same as the case where the lip 28 is in axial contact with the inner surface 19c of the flange portion 19 of the outer ring 14 (see the description of the first embodiment shown in FIG. 1). Therefore, detailed description thereof is omitted.

  In the embodiments described so far, it is desirable that the outer peripheral surface 27b of the shielding portion 27 is provided with a diameter-expanded portion whose radial dimension from the rotation axis X (see FIG. 2) increases from the inner ring side toward the tip side. . “Providing an enlarged diameter portion” here means providing an enlarged diameter portion without reducing the radial dimension from the rotating shaft on the outer peripheral surface 27b of the shielding portion 27 from the inner ring side toward the distal end side. means.

  In this case, even if muddy water (foreign matter) adhering to the inner peripheral surface 27 a of the shielding portion 27 flows (moves) to the outer peripheral surface 27 b, the muddy water is affected by the centrifugal force due to the rotation of the outer ring 14, and thus the shielding portion. Since the diameter-enlarged portion of the outer peripheral surface 27b of the cylinder 27 is likely to flow toward the tip side (outside of the bearing), it is likely to jump off the outside of the bearing. As a result, it is possible to contribute to the improvement of the already described muddy water blocking function of the blocking unit 27. In addition, it is desirable that the above-mentioned enlarged diameter portion has a tapered shape. In this case, since the flow of muddy water adhering to the outer peripheral surface of the shielding portion toward the front end side becomes smooth, the above-described actions and effects can be easily obtained.

  Alternatively, it is desirable that the outer peripheral surface 27b of the shielding portion 27 is constituted only by a diameter-expanded portion that increases in the radial direction from the rotating shaft of the bearing from the inner ring side end portion to the tip end portion. In this case, the muddy water adhering to the outer peripheral surface 27b of the shielding part is more likely to flow to the tip side than when the enlarged diameter part is partially provided on the outer peripheral surface 27b of the shielding part 27. It becomes easy to be done. For this reason, it can contribute greatly to the improvement of the muddy water blocking function of the shielding part. Even in this case, it is desirable that the enlarged diameter portion has a tapered shape for the reason already described.

  In the present embodiment, the members provided on the front side seal member (shielding portion 27, lip 28, auxiliary lip 52) and the members provided on the flange portion 19 of the outer ring 14 (seal portion 51) are the front side seal member 17 or Although formed integrally with the flange portion 19 of the outer ring 14, it may be formed separately.

  However, if each of the above members is a separate body, there is a problem that the number of parts of the bearing increases and the cost required for manufacturing the bearing increases. In addition, since a separate process for providing the above-described individual members on the front-side seal member 17 or the flange portion 19 of the outer ring 14 is required, the number of manufacturing processes of the bearing is increased, and work for manufacturing the bearing is performed. There is a problem that efficiency decreases. Therefore, as in the embodiment described here, the members provided on the front seal member (shielding portion 27, lip 28, auxiliary lip 52) and the members provided on the flange portion 19 of the outer ring 14 (seal portion 51) It is desirable to form integrally with the side seal member 17 or the flange portion 19 of the outer ring 14.

  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.

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 6th 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, 62, 72, 82, 92, 102 Ball bearing 14 for clutch release bearing device 14 Outer ring (rotating ring)
15 Inner ring (stationary ring)
16 Ball 17 Front side seal member 18 Rear side seal members 17c, 18c Mounting end (outer diameter end)
19 Buttocks (outer ring)
20 Buttocks (inner ring)
26 Cage 27 Shielding portion 27a Inner peripheral surface 27a ₁ Expanded portion (tapered shape)
27a ₂ linear part 27b outer peripheral surface 28 lip 29 foundation part (inner ring)
29a Recess 40 Bearing opening 41 Seal gap 50 Tip (shielding part)
51 Sealing part (outer ring collar)
52 Auxiliary lip (shielding part)
52a Tip (auxiliary lip)

Claims (11)

An outer ring that is a rotating wheel, an inner ring that is a stationary ring, a ball that is interposed between the outer ring and the inner ring, and a seal member that forms a sealed space between the outer ring and the inner ring, A ball bearing for a clutch release bearing device in which an end portion of an outer ring extends radially inward to form a flange portion, and a bearing opening is formed between the end portion of the flange portion of the outer ring and the inner ring. And
The sealing member has a cylindrical shielding portion whose one end portion is an attachment end portion fixed to the inner ring and whose other end portion extends to the inner peripheral surface side of the flange portion of the outer ring and covers the bearing opening. A ball bearing for a clutch release bearing device.   The ball bearing for a clutch release bearing device according to claim 1, wherein an annular lip that is in contact with the inner surface of the flange portion of the outer ring is provided at a portion between the mounting end portion and the shielding portion of the seal member.   The ball bearing for a clutch release bearing device according to claim 2, wherein the lip is provided at a plurality of locations in a direction in which the outside of the bearing communicates with the inside of the bearing.   The ball bearing for a clutch release bearing device according to claim 2 or 3, wherein the lip is in axial contact with an inner surface of a flange portion of the outer ring.   The clutch release according to any one of claims 2 to 4, wherein the flange portion of the outer ring has an annular seal portion that protrudes toward the inside of the bearing and is disposed between the shielding portion and the lip of the seal member. Ball bearings for bearing devices.   The seal member has an annular auxiliary lip that protrudes toward the flange portion of the outer ring at a portion between the shielding portion and the lip and is disposed on the bearing inner side of the seal portion of the flange portion of the outer ring. A ball bearing for a clutch release bearing device according to claim 5.   The ball bearing for a clutch release bearing device according to claim 6, wherein the auxiliary lip is in contact with an inner surface of a flange portion of the outer ring.   The ball bearing for a clutch release bearing device according to claim 6 or 7, wherein the auxiliary lip is in axial contact with an inner surface of a flange portion of the outer ring.   The clutch release bearing according to any one of claims 1 to 8, wherein an inner peripheral surface of the shielding portion includes a diameter-expanding portion in which a radial dimension from a rotation shaft of the bearing increases from an inner ring side toward a tip side. Ball bearing for equipment.   The ball bearing for a clutch release bearing device according to claim 9, wherein the enlarged diameter portion has a tapered shape.   The ball bearing for a clutch release bearing device according to any one of claims 1 to 8, wherein a tip portion of the shielding portion is bent toward an inner diameter side.

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