JP2009138804A - 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, preventing as much as possible malfunctions from originating in pressure differentials of pressures inside and outside the bearing while securing a high sealing performance, with a simple structure. <P>SOLUTION: The ball bearing 10 comprises an inner ring 11 and an outer ring 13 and sealing members 16, 17 disposed between the inner ring 11 and the outer ring 13. A first and a second concave portion 18a, 18b on the head 17a located in the external diameter side of the second seal member 17 and a concave part 19 is provided on a first lip part 17b situated in the inner diameter side. Each of the concave parts 18, 19 are composed of air flow passages T1, T2 for interconnecting the inside and outside of the bearing. Since air can flow between the inside and outside of the bearing through the air flow passages T1, T2, a pressure imbalance between the inside and outside is effectively prevented. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

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

  The clutch release bearing device is disposed between the engine and the transmission of a manual transmission vehicle (MT vehicle) and moves axially along the front cover of the transmission in accordance with the operation of the clutch pedal, and turns the clutch on / off. It is to switch.

  FIG. 6 shows an example of a clutch release bearing device incorporated in a clutch device, and more specifically, an example of a self-aligning clutch release bearing device incorporated in a so-called pull type clutch device and its peripheral mechanism. The clutch release bearing device A shown in FIG. 1 includes a ball bearing 100, a sleeve 200, a side plate 300, and a cover 400 that are externally attached to a front cover 700 of a transmission. When a deviation occurs between the center and the center, the ball bearing 100 moves in the radial direction according to the amount of deviation, so that the misalignment between the two axes can be automatically aligned. In this clutch release bearing device A, when a release fork (not shown) engaged with the side plate 300 swings (arc motion) by depressing a clutch pedal (not shown), the diaphragm spring 600 is shown in the drawing via the ball bearing 100. Pulled in the direction of arrow F, the clutch is turned off.

  As shown in FIG. 7, the ball bearing 100 also holds the inner ring 101 and the outer ring 103, a plurality of balls 104 that are rotatably incorporated between the raceway grooves of the inner and outer rings, and the balls 104 at equal intervals in the circumferential direction. And a cage 105. The inner ring 101 is integrally provided with a cylindrical mounting portion 102 extending in the axial direction, and the ball bearing 100 is provided with a diaphragm spring 600 via a wedge collar 500 fixed to the outer diameter surface of the mounting portion 102 of the inner ring 101. It is connected to the inner diameter part of.

The ball bearing 1 includes an outer diameter surface of the inner ring 101 and an outer ring 103 for the purpose of preventing external leakage of grease filled in the bearing and preventing foreign matter such as wear powder, sand, and water from entering the bearing. A first seal member 106 that seals (seals) between the inner diameter surface at one end side and a second seal member 107 that seals at the other end side are provided. The first and second seal members 106 and 107 have, for example, outer diameter end portions fixed to the inner diameter surface of the outer ring 103, and in this state, the inner diameter end portions pass through a predetermined radial gap (labyrinth gap). (See, for example, Patent Document 1).
JP-A-11-270583

  A so-called non-contact type seal structure in the ball bearing shown in FIG. 7 is widely adopted, but it is a clutch release bearing for an automobile, for example, a four-wheel drive vehicle, which is expected to be used under particularly severe environmental conditions. Ball bearings incorporated in the device are required to have higher sealing performance. In order to respond to such a demand for improved sealing performance, for example, the outer diameter end of the seal member is fixed to the inner diameter surface of the outer ring, and the inner diameter end is contacted with the outer diameter surface of the inner ring over the entire circumference. A mold seal structure may be employed. However, when such a seal structure is adopted, the sealing performance is extremely good, and therefore the pressure difference between the inside and outside of the bearing becomes excessive, and there is a possibility that unintentional adsorption of the seal member (increase in bearing torque) and grease leakage may occur. . Adsorption of the seal member (increase in bearing torque) and grease leakage are major factors that cause a decrease in bearing performance and further a decrease in the function and durability of the clutch device.

  The present invention has been made in view of the above-mentioned problems, and the object of the present invention is to provide various problems caused by the pressure difference between the inside and outside of the bearing with a simple structure while having high sealing performance. It is an object of the present invention to provide a ball bearing for a clutch release bearing device that can be prevented.

  In order to solve the above-described problems, the present invention provides a ball bearing for a clutch release bearing device that can move in the axial direction along the front cover of a transmission in accordance with the operation of a release fork. A seal member disposed, and press-fit and fix one end portion of the seal member to either the outer diameter surface of the inner ring or the inner diameter surface of the outer ring, and the other end portion of the seal member to the other side over the entire circumference. By sealing the gap between the outer diameter surface of the inner ring and the inner diameter surface of the outer ring, the fixing portion between the one end portion of the seal member and the one ring, and the other end portion of the seal member and the other ring The ball bearing for the clutch release bearing device is characterized in that at least one of the contact portions is partially non-contact and the inside and outside of the bearing can communicate with each other via the non-contact portion.

  As described above, in the ball bearing according to the present invention, since the inside and outside of the bearing communicate with each other through the non-contact portion that is partially non-contact among the fixed portion and the contact portion, there is a pressure difference between the inside and the outside of the bearing. This can be prevented as much as possible. Therefore, it is possible to prevent seal member adsorption (increase in bearing torque) and grease leakage as much as possible due to the pressure difference between the inside and outside of the bearing. On the other hand, since the non-contact portion is partially provided (in the circumferential direction), there is almost no problem such as foreign matter entering through the non-contact portion, and the sealing performance is as high as the contact seal. It will be of level.

  As an example of specific means for realizing the above configuration, it is possible to provide a recess in at least one of the one end and the other end of the seal member. It can be considered to be provided in a partial region in the direction. The means for forming the recess is not particularly limited, and for example, it can be molded at the time of molding the seal member. Such a configuration is effective when one end and the other end of the seal member are made of rubber. That is, since a rubber seal member is generally vulcanized, a seal member having a recess can be easily obtained by providing a protrusion corresponding to the recess shape in the mold used at this time. Of course, the means for forming the recess is not limited to this, and it can be formed by machining such as cutting after the seal member is formed.

  Further, as another example of specific means for realizing the above configuration, it is possible to provide a recess in at least one of the outer diameter surface of the inner ring and the inner diameter surface of the outer ring. In other words, the recess is retracted radially outward from other places. It is conceivable to provide the portion in a partial region in the circumferential direction. Although the inner ring and the outer ring are generally made of metal, it is preferable to form the recesses by press work so that the recesses can be easily formed. Of course, even when the inner ring and the outer ring are provided with recesses, the recesses can be provided by machining such as cutting.

  As described above, according to the present invention, a ball bearing for a clutch release bearing device capable of preventing various problems caused by a pressure difference between the inside and outside of the bearing as much as possible with a simple structure while having high sealing performance. Can be provided. Thereby, it is possible to prevent as much as possible the deterioration of the function and the life of the clutch device.

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

  FIG. 1 is a cross-sectional view showing an overall configuration of a clutch release bearing device incorporating a ball bearing according to the present invention, more specifically, a clutch release bearing device incorporated in a pull type clutch device. The clutch release bearing device shown in FIG. 1 includes a ball bearing 10, a sleeve 20, a side plate 30, a cover 40, and an elastic member 50. The main parts are extrapolated to the front cover 60 of the transmission. Has been.

  The sleeve 20 includes a cylindrical portion 22 located on the inner diameter side of the ball bearing 10 and a flange portion 24 extending from one end of the cylindrical portion 22 to the outer diameter side. In the sleeve 20 of the present embodiment, the flange portion 24 is made of a steel plate, the flange portion 24 is inserted, and the cylindrical portion 22 is injection-molded with resin. One end of the cylindrical portion 22 is bent toward the outer diameter side, and a flange portion 24 is provided so as to extend from the bent end portion 26 toward the outer diameter side. The flange portion 24 has an annular shape and has two flat portions 21 and 23 that are stepped. The sleeve 20 may be entirely press-formed from a steel plate.

  The side plate 30 is made of a steel plate and has a cylindrical holding portion 32 that covers the outer periphery of the ball bearing 10 and fits with the outer diameter surface of the flange portion 24 of the sleeve 20. A first collar 34 that is bent toward the inner diameter side is formed at one end of the holding part 32, and a second collar part 36 that is bent toward the outer diameter side is formed at the other end of the holding part 32. Engaging portions 38 that protrude toward the outer diameter side and engage with a release fork (not shown) are formed at two locations in the circumferential direction facing the holding portion 32 in the radial direction.

  The cover 40 is formed of a steel plate in a ring shape, and has a caulking portion 41 for connecting the cover 40 and the side plate 30. The caulking portion 41 is formed by bending the outer peripheral edge portion of the cover 40 toward the second flange portion 36 side of the side plate 30. An annular projecting portion 42 projecting toward the flange portion 24 side of the sleeve 20 is formed at a substantially central portion in the radial direction of the cover 40.

  The elastic member 50 is interposed between the flat portion 23 of the flange portion 24 of the sleeve 20 and the protruding portion 42 of the cover 40 and elastically presses both in a direction away from each other. Examples of the elastic member 50 that exhibits such a function include a wave washer.

  As shown in an enlarged view in FIG. 2, the ball bearing 10 includes an inner ring 11 and an outer ring 13, a plurality of balls 14 that are rotatably incorporated between raceway grooves of the inner and outer rings, and the balls 14 in a circumferential direction or the like. The cage 15 is held at intervals, and annular first and second seal members 16 and 17 are provided on both sides in the axial direction of the ball 14 and seal the opening between the inner and outer rings 11 and 13. The inner ring 11 is integrally provided with a cylindrical mounting portion 12 extending in the axial direction, and the ball bearing 10 is a wedge collar fixed to the outer diameter surface of the mounting portion 12 of the inner ring 11 (see FIG. 6). ) To the inner diameter portion of the diaphragm spring (see FIG. 6). The ball bearing 10 is filled with grease as a lubricant.

  The inner surface of the outer ring 13 has a first inner peripheral surface 13a having a raceway groove for the ball 14 and a second inner peripheral surface located on both axial sides of the first inner peripheral surface 13a and having a larger diameter than the first inner peripheral surface 13a. The surface 13b is partitioned into arcuate surfaces 13c and 13d located between the first inner peripheral surface 13a and the second inner peripheral surface 13b. On the other hand, the outer diameter surface of the inner ring 11 is located on the first outer peripheral surface 11a having the raceway groove of the ball 14 and one axial direction side (right side in the figure; transmission side) of the first outer peripheral surface 11a. Is divided into a second outer peripheral surface 11b having a larger diameter and a circular arc surface 11c positioned between the first outer peripheral surface 11a and the second outer peripheral surface 11b.

  The first seal member 16 on the left side (engine side) in the figure is a so-called elastic seal formed by vulcanizing a rubber material so as to cover the core metal, and has a head portion 16a at an outer diameter end portion thereof, First and second lip portions 16b and 16c are provided at the inner diameter end portion. The first seal member 16 has a head 16a that is press-fitted and fixed with respect to the arc surface 13c of the outer ring 13, and the first and second lip portions 16b and 16c are all around the first outer peripheral surface of the inner ring 11 when fixed. 11a is contacted. That is, the first and second lip portions 16 b and 16 c of the first seal member 17 constitute a contact-type seal with the inner ring 11. As a result, the left (engine side) opening in the figure between both wheels 11 and 13 is sealed, and leakage of grease and entry of foreign matter through this opening is prevented as much as possible.

  The second seal member 17 on the right side in the figure is a so-called elastic seal in which the cored bar is covered with an elastic material such as rubber like the first seal member 16, and has a head portion 17a at the outer diameter end portion thereof, The inner diameter end portion has first and second lip portions 17b and 17c. In the second seal member 17, the head portion 17 a is press-fitted and fixed to the inner diameter surface of the outer ring 13, and the first lip portion 17 b comes into contact with the arc surface 11 c of the inner ring 11 when fixed. In a fixed state, the outer surface (a part) of the head 17a extends to the arc surface 13d, and the end surface on the bearing inner side extends from the arc surface 13d toward the first inner peripheral surface 13a. The second lip portion 17c is in close contact with the straight portion, and is opposed to the second outer peripheral surface 11b of the inner ring 11 via a predetermined radial clearance. That is, the first lip portion 17 b of the second seal member 17 forms a contact-type seal with the inner ring 11, and the second lip portion 17 c forms a non-contact seal (labyrinth seal) with the inner ring 11. . As a result, the right side (transmission side) opening in the figure between both wheels 11 and 13 is sealed, and leakage of grease and entry of foreign matter through this opening are prevented as much as possible.

  The head portion 17a is provided with first recesses 18a opened at both end faces of the head portion 17a at one or a plurality of locations in the circumferential direction (see FIGS. 3A and 3B). The head 17a and the arcuate surface 13d of the outer ring 13 are not in contact with each other in the circumferential region where the recess 18a is provided. The head 17a is provided with one or more second recesses 18b opened in the inner and outer diameter surfaces of the head 17a at one or more locations in the circumferential direction so as to be out of phase with the first recess 18a ( In the circumferential region where the second recess 18b is provided, the head 17a and the linear portion of the outer ring 13 are not in contact with each other. Further, an annular gap over the entire circumference is interposed between the outer diameter surface of the head portion 17a and the circular arc surface 13d of the outer ring 13 (see FIG. 3A). On the radial end side, a series of air passages T1 including the first concave portion 18a, the annular gap, and the second concave portion 18b are formed, and the inside and outside of the bearing can communicate with each other through the air passage T1 (FIG. 4 ( see a)).

  As shown in FIGS. 3 (c) and 3 (d), the first lip portion 17 b is provided with concave portions 19 opened in the inner and outer diameter surfaces of the first lip portion 17 b at one or more locations in the circumferential direction. In the circumferential region where the recess 19 is provided, the first lip portion 17b and the arc surface 11c of the inner ring 11 are not in contact with each other. A ventilation path T2 that passes through the recess 19 is formed on the inner diameter end side of the second seal member 17, and the inside and outside of the bearing can be communicated with each other via the ventilation path T2 (see FIG. 4B). ).

  Each of the recesses 18a, 18b, and 19 is molded simultaneously with the molding (vulcanization molding) of the second seal member 17 by using a molding die provided with a convex portion corresponding to each recess shape. Of course, after the second seal member 17 is formed, each recess can be formed by machining such as cutting and cutting. In addition, the cross-sectional shape of each recessed part to show in figure is an example to the last, Of course, it is possible to take another arbitrary form.

  As described above, by providing the concave portions 18a and 18b in the head portion 17a, the head portion 17a and the arc surface 13d of the outer ring 13 are not in contact with each other in the circumferential region where the concave portions are provided. Since the circumferential length of the non-contact portion with respect to the contact portion with 13 is minute, the adverse effect on the sealing performance is negligibly small. Further, by providing the concave portion 19 in the first lip portion 17b, the first lip portion 17b and the arc surface 11c of the inner ring 11 are not in contact with each other in the circumferential region where the concave portion 19 is provided. Since the circumferential length of the non-contact portion with respect to the contact portion between the lip portion 17b and the arc surface 11c of the inner ring 11 is very small, the adverse effect on the sealing performance is negligibly small.

  As described above, according to the configuration of the present invention, air can flow back and forth inside and outside the bearings through the above-described recesses 18a, 18b, and 19 (ventilating passages T1 and T2). Adsorption (increase in bearing torque) of the seal members 16 and 17 and grease leakage can be prevented as much as possible. On the other hand, since each recess is partially provided in the circumferential direction, there is almost no problem such as foreign matter entering through these recesses, and the obtained sealing performance is as high as that of a contact seal. It will be of level.

  In particular, as in the present embodiment, if the second seal member 17 whose outside is covered by the flange portion 24 of the sleeve 20 is provided with a recess (air passages T1 and T2), the entry of foreign matter through each air passage is This is preferable because the first seal member 16 is effectively suppressed as compared with the case where this kind of recess (air passage) is provided. In addition, if the second seal member 17 located on the transmission side is provided with a recess, the adverse effect on the clutch function when grease leaks through the recess is caused by the grease leak from the first seal member 16 located on the engine side. This is preferable because it can be lighter than the case where the above occurs. Of course, if the above-described adverse effects are so slight that they can be ignored, a recess (air passage) may be provided in the first seal member 16 instead of the second seal member 17, or both the seal members 16. , 17 can also be provided.

  In the present embodiment, the concave portions are provided in both the outer diameter end portion (head portion 17a) and the inner diameter end portion (first lip portion 17b) of the second seal member 17, but the concave portion is provided in only one of them. Just fine.

  Further, the case where the recess is provided in the seal member has been described above. However, the inner diameter end portion and the inner ring of the seal member are not provided by providing the recess on the outer diameter surface of the inner ring or the inner diameter surface of the outer ring. At least one of the contact portion with the outer diameter surface and the fixing portion between the outer diameter end portion of the seal member and the inner diameter surface of the outer ring may be partially non-contact in the circumferential direction. In this case, the concave portion can be formed by press working or machining such as cutting.

  In the above, a ball adopting a seal structure (contact seal) in which the outer diameter end portion of the seal member is press-fitted and fixed to the inner diameter surface of the outer ring and the inner diameter end portion of the seal member is brought into contact with the outer diameter surface of the inner ring. The bearing has been described, but on the contrary, the inner diameter end portion of the seal member is press-fitted and fixed to the outer diameter surface of the inner ring, and the outer diameter end portion of the seal member is in contact with the inner diameter surface of the outer ring. The configuration of the present invention can also be applied to a ball bearing that employs a structure.

  In the above, the case where the configuration of the present invention is applied to a ball bearing for a clutch release bearing device incorporated in a so-called pull type clutch device has been described. However, the present invention is incorporated in a so-called push type clutch device. The present invention can also be suitably applied to ball bearings for clutch release bearing devices. In addition, as shown in FIG. 5, for example, the ball bearing for the clutch release device incorporated in the push type clutch device has a flange portion in which the inner ring 11 extends radially outward at one end thereof (strictly, one end on the engine side). 12 'is integrally or separately (the illustrated example is a separate body). In this type of clutch device, ON / OFF of the clutch is switched by bringing the flange portion 12 'into contact with the diaphragm spring.

  The present invention has been described above. However, the present invention is not limited to the above-described embodiment, and can of course be implemented in various forms without departing from the gist of the present invention. It is. The scope of the present invention is defined by the terms of the claims, and includes the equivalent meanings recited in the claims and all modifications within the scope.

It is sectional drawing which shows the whole structure of the clutch release bearing apparatus incorporating the ball bearing which concerns on this invention. It is an expanded sectional view of the ball bearing shown in FIG. (A) The figure is the X section enlarged sectional view of FIG. 2, (b) The figure is AA sectional drawing in (a) figure, (c) The figure is the Y section enlarged sectional view of (d) figure (C) It is BB sectional drawing in a figure. (A) The figure shows notionally the communication mode in the X section of FIG. 2, (b) The figure conceptually shows the communication mode in the Y section of FIG. It is sectional drawing which shows other embodiment of the ball bearing which concerns on this invention. It is sectional drawing which shows the peripheral device of a clutch release bearing apparatus. It is an expanded sectional view of the conventional clutch release bearing device and the front cover.

Explanation of symbols

10 (for clutch release bearing device) 11 Ball bearing 11 Inner ring 13 Outer ring 14 Ball 16 First seal member 17 Second seal member 17a Head 17b First lip 17c Second lip 18a First recess 18b Second recess 19 , T2 air passage

Claims (6)

A ball bearing for a clutch release bearing device that can move in the axial direction along the front cover of the transmission in accordance with the operation of the release fork. The ball bearing includes an inner ring and an outer ring, and a seal member disposed between the two rings. One end portion of the seal member is fixed to either the outer diameter surface of the outer ring or the inner diameter surface of the outer ring, and the other end portion of the seal member is brought into contact with the other end over the entire circumference, whereby the outer diameter surface of the inner ring and the outer ring In what is sealed between the inner diameter surface of
At least one of the fixing portion between the one end portion of the seal member and the one ring and the contact portion between the other end portion of the seal member and the other ring is partially non-contacted via the non-contact portion. A ball bearing for a clutch release bearing device, characterized in that the inside and outside of the bearing can communicate.   The ball bearing for a clutch release bearing device according to claim 1, wherein at least one of the fixed portion and the contact portion is partially non-contacted by providing a recess in at least one of the one end portion and the other end portion of the seal member.   The ball bearing for a clutch release bearing device according to claim 2, wherein the concave portion is molded when the seal member is molded.   The ball bearing for a clutch release bearing device according to claim 1, wherein at least one of the fixed portion and the contact portion is partially non-contacted by providing a recess in at least one of the outer diameter surface of the inner ring and the inner diameter surface of the outer ring. .   The ball bearing for a clutch release bearing device according to claim 4, wherein the recess is formed by press working.   The ball bearing for a clutch release bearing device according to claim 2 or 4, wherein the recess is formed by machining.

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