JP2010031911A - 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 capable of stabilizing the installation state of an installation member when operating a bearing, when a vehicle vibrates, and so forth. <P>SOLUTION: A cutout 36 is formed, for example, in four places at equal intervals in the peripheral direction at a rear side end of an inner race 15 of a stationary ring, and a projection 37 cut and raised to the front side is arranged, for example, in two places at an equal interval in the peripheral direction in a diametrically expanded part 35b of the installation member 35 fitted to the rear side end of the inner race 15. The projection 37 is fitted to the cutout 36 formed at the rear side end of the inner race 15, and this recess-projection fitting is made to serve as a position regulating means 38 of the installation member 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. .

  When shutting off the power from the engine to the transmission, the clutch release bearing device is moved in the axial direction and the clutch disc is separated from the flywheel. The clutch release bearing device is pushed and pulled in this direction of axial movement. It can be roughly divided into types. 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 (Patent Documents 1 and 2).

  The ball bearing 112 is mainly composed of 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 129 that holds the ball 116. It is configured. The engine-side end (the left side in the drawing) of the outer ring 114 extends radially inward to form a flange 119, and the engine-side end of the inner ring 115 extends radially inward to form a flange 120. . The flange portion 119 is in a state of being always in contact with the diaphragm spring 130 by the preload spring 121. The preload spring 121 is attached to the inside of an attachment member 135 that is fitted into the rear end portion of the inner ring 115 by press fitting.

  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 128 and 131 to the core bars 126 and 127.

  A seal member 117 (hereinafter referred to as a front side seal member) on the front side (engine side: left side of the drawing) has an inverted U-shaped cross section. The front-side seal member 117 has an outer diameter end fixed to the inner surface 123 of the outer ring 114 and an inner diameter end in radial contact (radial contact) with the outer surface 124 of the inner ring 115. This prevents muddy water from entering the inside of the bearing (the center between the outer ring 114 and the inner ring 115 where the ball 116 is interposed).

  A seal member 118 (hereinafter referred to as a rear seal member) on the rear side (transmission side: right side of the drawing) has a U-shaped cross section. The rear seal member 118 has an outer diameter end 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. The main lip 118 a is in radial contact with the outer surface 124 of the inner ring 115. This prevents muddy water from entering the bearing. Further, the auxiliary lip 118b makes it difficult for muddy water to reach the main lip 118a, and the above-described function of the main lip 118a is improved.

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 2005-163943 A JP 2006-189086 A

  The mounting member 135 of the bearing 112 shown in FIG. 7 does not rotate itself. However, the preload applied to the bearing 112 (force received from the preload spring 121) and the load change due to the operation of the bearing 112 (rotation of the outer ring 114) and the fluctuation of the external load, or the vehicle on which the bearing 112 is mounted vibrates. Then, the tightening margin of the mounting portion (fitting portion) between the inner ring 115 and the mounting member 135 is repeatedly changed, and the mounting force between the inner ring 115 and the mounting member 135 (the fitting force between the inner ring 115 and the mounting member 135). The above force may be applied to the attachment member 135 in the circumferential direction. Here, since the attachment member 135 is attached to the inner ring 115 only by internal fitting by press-fitting, the attachment member 135 may rotate in the circumferential direction when a circumferential force is applied as described above. When the mounting member 135 rotates in the circumferential direction in this way, the mounting member 135 moves in the axial direction (rear side) due to vibration caused by rotation and comes off from the inner ring 115, or the rotational force of the mounting member 135 causes the mounting member 135 to rotate. In addition to the preload spring 121 attached to the preload spring 121, the preload spring 121 may be damaged.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a ball bearing for a clutch release bearing device capable of stabilizing the mounting state of the mounting member during operation of the bearing or vibration of the vehicle. To do.

  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, and a ball interposed between the rotating wheel and the stationary wheel, A ball bearing for a clutch release bearing device in which an attachment member is mounted on the stationary wheel, wherein the stationary wheel and the attachment member are provided with position restricting means for the attachment member. Here, the mounting member is provided with a preload spring. The preload spring applies a preload to the bearing, and between the rotating wheel of the bearing and the diaphragm spring in contact with the rotating wheel. It enables power transmission.

  In this case, the preload and load applied to the bearing fluctuate due to the operation of the bearing (rotation of the rotating wheel) and fluctuation of the external load, or the vehicle on which the bearing is mounted vibrates, so that the stationary wheel and the mounting member Even when a large force in the circumferential direction is applied to the mounting member (a force greater than the mounting force between the stationary wheel and the mounting member), the position restricting means The attachment member can be restricted from rotating in the circumferential direction.

  The position restricting means is preferably a concave-convex fitting. In this case, when the position restricting means is provided, the stationary wheel and the mounting member can be easily processed. Moreover, the operation | work at the time of attaching an attachment member to a stationary wheel becomes easy.

  The concave-convex fitting is possible by fitting a convex portion provided on the mounting member into a concave formed in the stationary ring. Or the said uneven | corrugated fitting is possible by fitting the convex part provided in the said stationary ring in the recess formed in the said attachment member. In addition, a recess can be made into a notch, for example.

  In the invention described so far, it is desirable to provide a plurality of the position restricting means in the circumferential direction. In this case, it is easier to restrict the rotation of the mounting member in the circumferential direction than when only one position restricting means is used during operation of the bearing or vibration of the vehicle on which the bearing is mounted. The mounting state of the member is easy to stabilize. Thus, by restricting the mounting member from rotating in the circumferential direction, it is possible to prevent the mounting member from moving from the stationary wheel in the axial direction due to vibration caused by the rotation. Further, since the attachment member rotates and the rotational force is not applied to the preload spring attached to the attachment member, there is no possibility that the preload spring is damaged. As a means for providing a plurality of position regulating means in the circumferential direction, for example, a plurality of the recesses and the projections are formed in the circumferential direction on the stationary ring or the mounting member, and the projections are fitted into the recesses. There is a way to do it.

  In the above invention, it is desirable that the position restricting means be provided at equal intervals in the circumferential direction. In this case, the mounting member can be prevented from rotating in the circumferential direction during operation of the bearing or during vibration of the vehicle on which the bearing is mounted, and the mounting state of the mounting member with respect to the stationary wheel is uniform throughout the circumferential direction. Can be stabilized. As a result, it is possible to reliably prevent the mounting member from moving in the axial direction due to vibration caused by its rotation and coming off the stationary wheel. Further, since the attachment member rotates and the rotational force is not applied to the preload spring attached to the attachment member, it is possible to reliably prevent the preload spring from being damaged. In addition, as means for providing the position restricting means at equal intervals in the circumferential direction, the recesses and the protrusions are provided at equal intervals in the circumferential direction on the stationary ring or the mounting member, and a plurality of recesses are provided in the plurality of recesses. There is a method for fitting the convex portions.

  The ball bearing for a clutch release bearing device of the present invention is provided with a position restricting means for the mounting member between a stationary wheel and a mounting member attached to the stationary wheel. Therefore, the preload and load applied to the bearing fluctuate due to the operation of the bearing (that is, rotation of the rotating wheel) and fluctuations in the external load, or the vehicle on which the bearing is mounted vibrates. Even when a force larger than the mounting force between the stationary wheel and the mounting member is applied to the mounting member in the circumferential direction, the mounting member is rotated by the position restricting means. Rotation in the direction can be restricted. As a result, the attachment member can be prevented from moving in the axial direction due to vibration caused by the rotation thereof and coming off the stationary wheel. Further, since the attachment member rotates and the rotational force is not applied to the preload spring attached to the attachment member, the preload spring is not likely to be damaged.

  Furthermore, since the mounting member can be positioned with respect to the inner ring by the position restricting means when mounted on the inner ring, the workability (ease of work, work efficiency) when mounting the mounting member on the inner ring is improved. Can be made.

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

  FIG. 4 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 attached to the inside of the attachment member 35 that is press-fitted into the rear side end portion of the inner ring 15 of the bearing 12, it 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 constituted by the cage 29 to be held. As the outer ring 14 rotates, the outer ring 14 and the inner ring 15 rotate relative to each other. A front side end portion of the outer ring 14 extends radially inward 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.

  The outer ring 14 and the inner ring 15 are sealed with 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 inside the bearing (in the space between the outer ring 14 and the inner ring 15 and in the central portion where the ball 16 is interposed) is external to the bearing 12 (hereinafter referred to as bearing outer). )) Can be prevented.

  Since the sealing members 17 and 18 are formed by vulcanizing and welding rubber members 28 and 31 made of hydrogenated nitrile rubber (H-NBR) to the cores 26 and 27, 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 front-side seal member 17 has an inverted U-shaped cross section. The front-side seal member 17 has an outer diameter end portion fixed to the inner surface 23 of the outer ring 14 and an inner diameter end portion in radial contact with the outer surface 24 of the inner ring 15. Thereby, it is possible to prevent muddy water from entering the bearing.

  The rear side sealing member 18 has a U-shaped cross section. The rear-side seal member 18 has an 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. The operation and effect of the main lip 18a and the auxiliary lip 18b are the same as those of the conventional example shown in FIG.

  The attachment member 35 has a cylindrical shape whose diameter is increased stepwise toward the rear side along the axial direction. A mounting portion 35a which is the innermost diameter portion of the mounting member 35 and extends in the axial direction is fitted into the rear end portion of the inner ring 15 by press fitting. Thereby, the attachment member 35 can be attached to the rear side end portion of the inner ring 15. In addition, the front view which looked at the inner ring | wheel 15 from the rear side was shown to FIG. 3 (A), and the front view which looked at the attachment member 35 from the front side was shown to FIG. 3 (B). Further, FIGS. 3A and 3B are shown by omitting the solid lines except for the main parts for easy understanding of the drawings, and the cross-sectional views of the inner ring 15 and the mounting member 35 shown in FIG. It is an AOB cross section of (A) and FIG. 3 (B).

  The points that characterize this embodiment will be described below.

  A notch 36 (recess) extending from the local end surface 15a to the front side along the axial direction is formed in the rear side end portion of the inner ring 15. Further, the notches 36 are formed, for example, at four locations at equal intervals in the circumferential direction.

  The attachment member 35 is provided with a projecting portion 37 (convex portion) by cutting the local portion of the enlarged diameter portion 35b extending radially outward from the rear side end portion of the attachment portion 35a to the front side. Further, the protruding portions 37 are provided at two locations, for example, at equal intervals in the circumferential direction in the enlarged diameter portion 35b. This projecting portion 37 is fitted into a notch 36 formed in the inner ring 15, and this concave / convex fitting is used as a position regulating means 38 of the mounting member 35. 2A shows an enlarged view of the notch 36 formed in the inner ring 15, and FIG. 2B shows an enlarged view of the protruding portion 37 provided on the mounting member 35. As shown in FIG.

  In this case, due to the operation of the bearing 12 (rotation of the outer ring 14), fluctuations in the external load, etc., the preload and load applied to the bearing 12 fluctuate, or the vehicle on which the bearing is mounted vibrates. The tightening allowance of the mounting portion (fitting portion) with the member 35 repeatedly fluctuates, whereby a large force in the circumferential direction is applied to the mounting member 35 (the rear side end portion of the inner ring 15 and the mounting portion 35a of the mounting member 35). Even if a force greater than the mounting force between the two is applied, the position restricting means 38 can regulate the rotation of the mounting member 35 in the circumferential direction, so that the mounting state of the mounting member 35 can be stabilized. . As a result, it is possible to prevent the attachment member 35 from moving in the axial direction due to vibration caused by the rotation thereof and coming off from the inner ring 15 to the rear side. Further, since the attachment member 35 rotates and the rotational force is not applied to the preload spring 21 attached to the attachment member 35, the preload spring 21 is not likely to be damaged.

  In the present embodiment, as shown in FIG. 3A, a plurality of (four) notches 36 are formed in the rear side end of the inner ring 15, and as shown in FIG. A plurality of (two) projecting portions 37 are provided in 35, and the projecting portions 37 are fitted into the notches 36, whereby two position restricting means are provided between the rear end portion of the inner ring 15 and the mounting member 35. 38 is provided. Therefore, it becomes easier to restrict the rotation of the attachment member 35 in the circumferential direction than in the case of one position restriction means 38, and the stability of the mounting state of the rear end of the inner ring 15 and the attachment member 35 is improved. Therefore, the operation and effect of the above-described embodiment can be improved.

  Furthermore, in order to provide the position restricting means 38 of the mounting member 35 at equal intervals in the circumferential direction by the notches 36 and protrusions 37 provided at equal intervals in the circumferential direction on the rear side end of the inner ring 15 and the mounting member 35. The mounting member 35 can be prevented from rotating in the circumferential direction, and the mounting state of the mounting member 35 on the rear side end of the inner ring 15 can be uniformly stabilized over the circumferential direction. Therefore, it is possible to reliably prevent the attachment member 35 from coming off the inner ring 15 to the rear side due to vibration caused by the rotation. Further, since the attachment member 35 rotates and the rotational force is not applied to the preload spring 21 attached to the attachment member 35, the preload spring 21 can be reliably prevented from being damaged.

  And since the position control means 38 makes uneven fitting with the notch 36 formed in the inner ring | wheel 15 and the protrusion 37 provided in the attachment member 35, the process of the inner ring | wheel 15 and the attachment member 35 becomes easy. In addition, the work when the attachment member 35 is attached to the rear side end portion of the inner ring 15 is facilitated.

  Since the mounting member 35 can be positioned with respect to the rear side end portion of the inner ring 15 by the position restricting means 38 when the mounting member 35 is fitted into the rear side end portion of the inner ring 15, the mounting member 35 is positioned on the rear side of the inner ring 15. The workability at the time of internal fitting at the side end can be improved. Further, as in the present embodiment, when the number of the notches 36 (four) formed in the rear end of the inner ring 15 is larger than the number (two) of the protrusions 37 provided on the mounting member 35, the inner ring When the attachment member 35 is fitted into the rear end portion of the rear end 15, the circumferential position of the protrusion 37 and the notch 36 are easily aligned in the circumferential direction. Therefore, the workability when fitting the attachment member 35 to the rear side end of the inner ring 15 can be greatly improved.

  The size, shape, or position of the recesses formed in the inner ring 15 and the protrusions provided in the attachment member 35 can be variously changed. An example is shown in FIG. In the second embodiment, parts having the same parts, functions, and forms as those in the first embodiment shown in FIGS. 1 to 4 are denoted by the same reference numerals, and detailed description thereof is omitted. Detailed descriptions of the same operations and effects as those of the first embodiment are also omitted.

  A ball bearing 52 for a clutch release bearing device according to the second embodiment shown in FIG. 5 has a notch 76 (in the rear side end portion of the inner ring 15 so as to extend from the local end surface 15a to the front side along the axial direction. Forming a recess). The notches 76 are formed, for example, at four equal intervals in the circumferential direction at the rear side end of the inner ring 15. Further, the enlarged diameter portion 35b of the attachment member 35 is provided with a projection 77 (convex portion) that locally protrudes to the front side. This protrusion 77 does not cut and raise the local part of the enlarged diameter part 35b like the protruding part 37 described in the first embodiment shown in FIG. 1, but protrudes the local part of the enlarged diameter part 35b to the front side. Make it thick. Further, the protrusions 77 are formed at two locations, for example, at equal intervals in the circumferential direction on the diameter-expanded portion 35b. This projection 77 is fitted into a notch 76 formed at the rear side end of the inner ring 15, and this concave / convex fitting serves as a position regulating means 78 of the mounting member 35. The details of the position restricting means 78 are the same as those in the first embodiment shown in FIG. An enlarged view of the notch 76 formed at the rear end of the inner ring 15 is shown in FIG. 6A, and an enlarged view of the protrusion 77 provided on the mounting member 35 is shown in FIG. 6B.

  In the second embodiment and the first embodiment already described, between the rear side end of the inner ring 15 and the mounting member 35, the rear side end of the inner ring 15 and the mounting portion 35a of the mounting member 35 are provided. Position restricting means 78 for the attachment member 35 is provided at a site different from the mounting portion (fitting portion). However, this position restricting means can also be provided in the mounting portion between the rear side end portion of the inner ring 15 and the mounting portion 35 a of the mounting member 35.

  Thus, as a method of providing the position restricting means at the mounting portion between the rear end of the inner ring 15 and the attachment member 35, for example, a recess is provided on the inner peripheral surface of the rear end of the inner ring 15, and this recess There is a method of fitting a protruding portion (convex portion) provided by cutting and raising the local portion of the mounting portion 35a of the mounting member 35 radially outward (not shown). In this case, the action and effect of the present invention described above can be obtained, and the attachment member 35 can be restricted from moving in the axial direction other than by rotation in the circumferential direction. It can be surely prevented.

  The embodiment of the present invention has been described above, but the present invention is not limited to this, and can be arbitrarily changed within the meaning and content of the claims.

  For example, in the present embodiment, a recess is provided at the rear side end of the inner ring 15 and a convex part is provided at the enlarged diameter portion 35b of the attachment member 35. However, a convex part is provided at the rear side end of the inner ring 15 and attached. You may make it provide a recess in the enlarged diameter part 35b of the member 35. FIG.

  Further, the position restricting means can be separated from the stationary wheel and the mounting member. In addition, when the convex part for comprising a position control means is provided in a stationary wheel or an attachment member like embodiment mentioned here, this convex part shall be made into the said stationary ring and the said attachment member separately. You can also.

  Further, in the present embodiment, since the inner ring 15 is a stationary ring, the position restricting means for the attachment member 35 is provided between the rear end portion of the inner ring 15 and the attachment member 35. However, when the outer ring 14 is a stationary wheel, a position restricting means may be provided between the rear side end of the outer ring 14 and the mounting member 35.

  The means for attaching the mounting member to the stationary wheel is not limited to fitting by press-fitting as in the embodiment described here, it can be attached by caulking, or another part can be attached. It is also possible to install using.

It is sectional drawing which shows the 1st Embodiment of this invention. (A) is an enlarged view of the notch shown in FIG. (B) is an enlarged view of the protruding part shown in FIG. (A) is a front view of the inner ring shown in FIG. (B) is a front view of the attachment member shown in FIG. 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. (A) is an enlarged view of the notch shown in FIG. FIG. 6B is an enlarged view of the protrusion shown in FIG. 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, 52 Ball bearing 14 Outer ring (rotating ring)
15 Inner ring (stationary ring)
16 Ball 17, 18 Seal member 29 Cage 35 Mounting member 36, 76 Notch (recess)
37 Projection (convex)
77 Projection (convex part)
38, 78 Position restricting means (concave fitting)

Claims (7)

A ball bearing for a clutch release bearing device comprising a rotating wheel and a stationary wheel that rotate relative to each other, and a ball interposed between the rotating wheel and the stationary wheel, and an attachment member mounted on the stationary wheel,
A ball bearing for a clutch release bearing device, wherein the stationary member and the attachment member are provided with a position restricting means for the attachment member.   The ball bearing for a clutch release bearing device according to claim 1, wherein the position restricting means is an uneven fitting.   3. The ball bearing for a clutch release bearing device according to claim 2, wherein the concave-convex fitting is performed by fitting a convex portion provided on the mounting member into a recess formed in the stationary ring.   3. The ball bearing for a clutch release bearing device according to claim 2, wherein the concave-convex fitting is performed by fitting a convex portion provided on the stationary ring into a recess formed in the mounting member.   The ball bearing for a clutch release bearing device according to claim 3 or 4, wherein the recess is a notch.   The ball bearing for a clutch release bearing device according to any one of claims 1 to 5, wherein a plurality of the position regulating means are provided in the circumferential direction.   The ball bearing for a clutch release bearing device according to claim 6, wherein the position restricting means is provided at equal intervals in the circumferential direction.

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