JP2008038985A - Bearing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing device capable of effectively restraining following rotation of a fixed wheel, and capable of rapidly performing alignment. <P>SOLUTION: When force is applied to an outer ring 11 in a following rotation direction, the outer ring 11 is rocked while having a pin 21a as a rotation center, and unnecessary displacement is restrained, and a groove part 11a and the pin 21a perform relative sliding which is necessary, and rapid displacement to the alignment position can be achieved. The pin 21a is cylindrical, and rocking of the outer ring 11 is not obstructed. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a bearing device capable of alignment.

  When operating a clutch that is a power interrupting device mounted on a vehicle or the like using a friction plate, the release fork that is an input member presses the diaphragm spring of the clutch cover that is a rotating member in the direction of the axial force. The power transmission is disconnected by releasing the urging force from the friction plate.

By the way, the release fork is usually arranged on the fixed side of the vehicle body or the like, but the clutch cover is attached to a flywheel or the like of the engine and rotates integrally therewith. Therefore, when the release fork directly presses the diaphragm spring of the clutch cover, wear of the contact portion is caused. Therefore, a clutch release bearing including a rotating wheel that abuts on the diaphragm spring and rotates integrally, and a non-rotating bearing holding member configured to hold the bearing in a predetermined state and receive an input from the release fork. For example, as shown in Patent Document 1, a clutch release bearing device is provided between a diaphragm spring and a release fork.
Japanese Utility Model Publication No.59-115130 Japanese Utility Model Publication No. 63-35818

  Here, in the conventional clutch release bearing device, in order to align the rotating wheel (in the example, the inner ring) with the center of the diaphragm spring, the bearing is movable in the radial direction and further maintains the aligned position. For this purpose, the fixed ring is pressed against the flange portion by a spring force such as a wave spring. However, if the spring force is reduced or dust, oil, or moisture enters the pressed surface, the friction coefficient μ will decrease, or if the drag torque increases due to deterioration of the bearing over time, the fixed ring will rotate. There is a risk of starting. When the rotation of the fixed ring starts, heat generation and wear occur, which accelerates deterioration of the bearing. In addition, the technique disclosed in Patent Document 2 is provided with a groove extending in the axial direction in the outer ring to prevent creep, and a pin provided on the case is engaged with the groove. The object and structure of the invention are different.

  The present invention has been made in view of the above-described problems of the prior art, and it is an object of the present invention to provide a bearing device that can effectively suppress the rotation of a fixed ring and perform alignment quickly.

  The bearing device according to the present invention includes an outer ring, an inner ring, and a rolling element disposed between the two rings. The outer ring is held so as to be movable in a radial direction with respect to a case. A groove extending in the radial direction is formed to engage with the protrusion provided on the surface.

  According to the bearing device of the present invention, the outer ring is held so as to be movable in the radial direction with respect to the case, and a radially extending groove that engages with a protrusion provided on the case is formed. Therefore, the accompanying rotation of the outer ring can be effectively suppressed by suppressing the displacement of the outer ring in the direction intersecting the extending direction of the groove.

When the inner diameter of the case is dh, the outer diameter of the outer ring is Db, the width of the groove is L, and the width of the protrusion is SL, the following equation is established.
dh−Db ≧ L−SL ≧ (dh−Dd) / 2 (1)

  In the groove, the maximum displacement δ of the protrusion in the width direction of the groove is represented by L-SL. Here, when δ ≧ (dh−Dd) / 2, since the protrusion abuts on the groove during alignment, the bearing performs an arc motion around the protrusion. Can be reached quickly. On the other hand, if the maximum displacement amount δ is too large, the accompanying suppression effect is reduced, so it is desirable that dh−Db ≧ δ. Note that the amount of alignment of the bearing is usually 1 to 2 mm in terms of runout.

  The bearing device is preferably a clutch release bearing device, but may be a normal bearing device.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a perspective view of a bearing device according to a first embodiment. FIG. 2 is a view of the bearing device shown in FIG. 1 as viewed in the direction of arrow II in the assembled state. In FIG. 1, the bearing device 10 includes an outer ring 11, an inner ring 12, a ball 13 that is a rolling element disposed between both the wheels 11 and 12, and a cage 14 that holds the ball 13. The outer ring 11 is disposed in a fixed case 20. The inner ring 12 is fitted on a shaft (not shown).

  The case 20 has a flange portion 21 and a hollow cylindrical portion 22 extending in the axial direction from the outer edge thereof. The inner diameter dh of the hollow cylindrical portion 22 is dh with respect to the outer shape Dh of the outer ring 11 included therein. > Dh. A groove portion 11 a extending in the radial direction is formed on an end surface of the outer ring 11 facing the flange portion 21. On the other hand, a cylindrical pin 21a, which is a projection, is implanted at a position facing the groove 11a of the flange portion 21. When the case 20 is made of metal, a hole is formed in the flange portion 21, and the tip of a separate pin 21a may be press-fitted therein. When the case 20 is made of resin, the pins 21a can be integrally formed by injection molding or the like.

  As shown in FIG. 2, the outer diameter (that is, the width) SL of the pin 21a is in a relationship of L> SL with respect to the width L of the groove 11a. When the bearing 10 is assembled to the case 20, the pin 21a is engaged in the groove 11a.

  FIG. 3 is a diagram showing a relative displacement relationship between the pin 21a of the case 20 and the outer ring 11 when viewed in the axial direction of the bearing. According to the bearing device 10 of the present embodiment, a shaft (not shown) can be rotatably supported with respect to the case 20. At this time, when the shaft (not shown) is misaligned with respect to the case 20, the outer ring 11 swings around the axis of the case 20. Here, if the pin 21a does not exist, it takes time until the outer ring 11 is aligned with the axis of the case 20. On the other hand, according to the present embodiment, when the outer ring 11 receives a force in the touching direction, as shown in FIG. 3, the outer ring 11 swings around the pin 21a, and unnecessary displacement is suppressed, Furthermore, the groove portion 11a and the pin 21a can be quickly displaced to the alignment position by performing the necessary relative sliding. In particular, since the pin 21a has a cylindrical shape, the swinging of the outer ring 11 is not hindered.

  Next, a clutch release bearing device according to a second embodiment will be described. FIG. 4 is a view of the clutch release bearing device according to the present embodiment as viewed from the release fork side. FIG. 5 is an axial sectional view of the clutch release bearing device of FIG. 4 cut along the line V-V and viewed in the direction of the arrow. FIG. 6 is a perspective view of the spring member.

  In FIG. 5, the clutch release bearing device includes a clutch release bearing 110, a guide sleeve 120 as a case, and a spring member 130 as a connecting member. The clutch release bearing 110 includes an outer ring 112, an inner ring 111 having an inner ring flange portion 111 a extending radially inward at the left end in FIG. 5 and concentrically enclosed by the outer ring 112, and the inner ring 111 and the outer ring. A plurality of rolling elements, which are arranged so as to be able to roll between them, a retainer 116 for holding the balls 115 at a predetermined interval, and provided on both sides in the axial direction of the balls 115 in a dustproof and oiltight manner. It consists of seals 117 and 118 that exert a sealing function.

  On the other hand, the guide sleeve 120 is made of resin or metal and has a cylindrical main body 121 that is a cylindrical portion, and a flange portion 122 that extends in the radial direction from the outer periphery near the center of the main body 121. A guide shaft (not shown) extends inward of the main body 121, and the main body 121 is slidable on the guide shaft. An enlarged diameter portion 124 is provided inside the main body 121. The enlarged diameter portion 124 functions so as not to bite foreign matter when the main body 121 slides on the guide shaft. The main body 121 forms a pair of flat portions 121a parallel to each other on the outer peripheral surface. The flat portion 121a serves as a guide surface for guiding a bifurcated release fork (not shown).

  Also in the present embodiment, a cylindrical protrusion 122 a is formed on the flange portion 122 of the guide sleeve 120 and engages with a groove portion 112 a formed on the opposite end surface of the outer ring 112 of the clutch release bearing 110. . The protrusion 122a and the groove 112a have the same dimensional relationship as that of the first embodiment.

  As is apparent from FIG. 4, the two spring members 130 having the same shape have a function of attaching the clutch release bearing 110 to the guide sleeve 120. The spring member 130 is formed by punching a single spring steel plate such as SK5 with a press, bending it, and then quenching it. The spring member 130 is provided between the base portion 131 that contacts the flange portion of the guide sleeve 120, the pressing portion 132 that contacts the outer ring 112 of the bearing, the base portion 131, and the pressing portion 132, and the pressing portion 132. And a beam portion 133 for applying an elastic force for urging the outer ring 112. The pressing part 132 has an inclined part 132a inclined outward so as not to contact the seal 117 and to facilitate the assembly of the spring member 130.

  The spring member 130 has a convex portion 134 formed so as to protrude in the radial direction substantially in the middle of the beam portion 133, and the convex portion 134 is an end portion of the flange portion 122 (FIG. 1) of the guide sleeve 120. 122h is engaged. Further, in the spring member 130, a notch 137 is formed in the vicinity of the lower end of both side portions 131a of the base portion 131, and a relatively large central notch 138 is formed in the center of the base portion 131.

  The substantially disk-shaped reinforcing member 140 includes a flange portion 141 that is in close contact with the flange portion 122 of the guide sleeve 120 and an anvil portion 142 that receives an input of a release fork (not shown), and is a relatively thin plate. Is formed by pressing and then quenching. This prevents significant wear from occurring at the contact portion with the release fork.

  When the clutch release bearing device is assembled, the clutch release bearing 110 is disposed around the main body 121 of the guide sleeve 120, and then the two spring members 130 are inserted from the inside in the radial direction of the main body 121, respectively. The spring member 130 rides over the axial protrusion 122c provided on the flange portion 122 of the guide sleeve 120 while being elastically deformed, the notch 137 engages with the protrusion 122c, and the central notch 138 has the flange portion 122 of the guide sleeve 120. Assembling is completed by abutting against the stopper 122g provided on the surface. At this time, the spring member 130 sandwiches the flange portion 122 and the outer ring 112 in the axial direction by its elastic force.

  Next, the operation of the clutch release bearing device according to the embodiment of the present invention will be described below. In FIG. 5, a release fork (not shown) pivots, and its tip abuts against the flange portion 122 of the guide sleeve 120 via the anvil portion 142 of the reinforcing member 140 to apply a constant load. The clutch release bearing device slides in the axial direction on a guide shaft (not shown) in response to an input from a release fork, and a diaphragm spring (a rotating member of the clutch device) (not shown) contacts an inner ring flange portion 111a of the inner ring 111. Make contact. Even if the diaphragm spring is rotating, the inner ring 111 is rotatable, so that it rotates together with the diaphragm spring after contact, and the bearing device moves in the axial direction so that the diaphragm spring is pressed and the clutch is It is supposed to be operated.

  Since the spring member 130 has an appropriate plate thickness and supports the clutch release bearing 110 with respect to the guide sleeve 120 only by the frictional force acting between the pressing portion 132 and the outer ring 112, the bearing 110 is The guide sleeve 120 is movable in the radial direction. Therefore, when the inner ring flange portion 111a of the inner ring 111 comes into contact with the diaphragm spring, if there is an eccentricity between the two, a known force is generated to place the bearing 110 concentrically, thereby causing the bearing 110 to move in the radial direction. The self-alignment will be achieved.

  According to the present embodiment, when the outer ring 112 receives a force in the direction of touching during alignment, the outer ring 112 swings around the protrusion 122a, unnecessary displacement is suppressed, and the groove 112a and the protrusion 122a are required. By performing relative sliding, it can be quickly displaced to the alignment position. In particular, since the protrusion 122a has a cylindrical shape, the swinging of the outer ring 112 is not hindered.

  The present invention has been described above with reference to the embodiments. However, the present invention should not be construed as being limited to the above-described embodiments, and can be changed or improved as appropriate. For example, the groove portion and the protrusion may not be one combination but may be a plurality of combinations. Furthermore, a protrusion may be formed on the outer ring of the bearing device, and a groove may be formed on the case.

It is a perspective view of the bearing device concerning a 1st embodiment. It is the figure which looked at the bearing apparatus shown in FIG. 1 in the arrow II direction in the assembled | attached state. It is the figure which showed the relative displacement relationship of the pin 21a of the case 20, and the outer ring | wheel 11 when it sees in the axial direction of a bearing. It is the figure which looked at the clutch release bearing device concerning this embodiment from the release fork side. FIG. 5 is an axial sectional view of the clutch release bearing device of FIG. 4 cut along the line V-V and viewed in the direction of the arrow. It is a perspective view of a spring member.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Bearing apparatus 11 Outer ring 11a Groove part 12 Inner ring 13 Ball 14 Cage 20 Case 110 Clutch release bearing 111 Inner ring 111a Inner ring flange part 112 Outer ring 112a Groove part 115 Ball 116 Cage 117, 118 Seal 120 Guide sleeve 121 Body 121a Flat part 122 Flange part 122a Protrusion 122c Axial protrusion 122g Stopper 122h End 124 Expanded portion 130 Spring member 131 Base portion 131a Both sides 132 Pressing portion 132a Inclined portion 133 Beam portion 134 Protruding portion 137 Notch 138 Central notch 140 Reinforcing member 141 Flange portion 142 Anvil Part

Claims (3)

  In a bearing device having an outer ring, an inner ring, and rolling elements arranged between the two rings, the outer ring is held so as to be movable in a radial direction with respect to the case, and is engaged with a protrusion provided on the case. A bearing device characterized in that a groove extending in a radial direction is formed. The following formula is established, where the inner diameter of the case is dh, the outer diameter of the outer ring is Db, the width of the groove is L, and the width of the protrusion is SL. Bearing device.
dh−Db ≧ L−SL ≧ (dh−Dd) / 2 (1) The bearing device according to claim 1, wherein the bearing device is a clutch release bearing device.

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