JP2008057762A - Ball bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a ball bearing having improved wear resistance while preventing the edge contact of the guide face of a cage with a bearing ring during operating the bearing even when the cage is inclined to the cross center of the bearing. <P>SOLUTION: The ball bearing 10 comprises a plurality of balls 30 rollingly held by the cage 20 and incorporated between the pair of bearing rings 11, 12. On the cage 20, a flange portion 21 having the protruded guide face 21a formed as a curved face is protruded to the side of one bearing ring 12. The flange portion 21 guides the cage 20 to one bearing ring 12 with the guide face 21a being guided to one bearing ring 12. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a ball bearing in which a plurality of balls, which are rotatably held by a cage, are incorporated between a pair of bearing rings, and more particularly, in a cage for a bearing ring guide, the guide of the cage with respect to the bearing ring. The present invention relates to a structure of a cage for preventing perimeter edges of a surface.

  Ball bearings that are widely used in general are rolling bearings in which a plurality of balls that are rotatably held by a cage are incorporated between an outer ring and an inner ring. In recent years, with the demands for weight reduction, noise reduction, speeding up, etc., synthetic resin-made cages are frequently used as cages for rolling bearings.

  As an example, Patent Document 1 and Patent Document 2 each disclose a ball bearing using a synthetic resin cage of a raceway guide effective in a high speed range.

  FIG. 6 is a cross-sectional view showing a ball bearing disclosed in Patent Document 1. As shown in FIG.

  Referring to FIG. 6, the cage 101 constituting the ball bearing 100 is made of a heat-resistant synthetic resin and has a crown shape. The outer diameter surface is close to the inner diameter surface of the outer ring 102 and is rotated by the outer ring guide. It is supported freely. Even when each pocket holding the ball 103 expands due to thermal expansion, the cage 101 rotates while being guided by the inner diameter surface of the outer ring 102 and is prevented from being displaced in the radial direction by the inner diameter surface of the outer ring 102. Therefore, even when used in a high-speed rotation and high-temperature environment, the vibration of the cage 101 does not increase.

  FIG. 7 is a cross-sectional view showing a ball bearing disclosed in Patent Document 2. As shown in FIG.

  Referring to FIG. 7, the ball bearing 110 is configured such that an annular cage 113 is incorporated between inner and outer rings 111 and 112, and balls 115 are accommodated in pockets 114 of the annular cage 113. The annular cage 113 is guided by the outer ring 112, and the radial gap (guide gap) α with respect to the outer ring 112 is less than or equal to the axial gap (pocket gap) β of the inner wall surface of the pocket 114 with respect to the ball 115 (guide gap α ≦ The pocket clearance β) is set. In FIG. 7, α1 + α2 = guide gap α and β1 + β2 = pocket gap β. Thereby, even when the annular cage 113 rotates eccentrically, the interference between the inner wall surface of the pocket 114 and the ball 115 is suppressed, and the behavior is stabilized.

  In the ball bearings 100 and 110 using the bearing ring (outer ring) guide cages 101 and 113 as described in Patent Document 1 and Patent Document 2 described above, the outer peripheral surface of the cages 101 and 113 and the outer rings 102 and 112 are used. Therefore, there is a problem in that it is difficult for the lubricating oil to be discharged from the bearing and good lubricity cannot be obtained. Further, when the cages 101 and 113 are inclined with respect to the center in the bearing width direction during the bearing operation, an edge load is generated between the outer peripheral surfaces of the cages 101 and 113 and the raceway surface ends of the outer rings 102 and 112. However, there is a problem that the friction increases and the cage vibration and the cage noise increase.

  Therefore, in Patent Document 3, as shown in FIGS. 8 and 9, a guided surface 126 is formed on the cage 123 of the bearing ring (outer ring 122) guide, thereby improving lubricity and reducing cage vibration. The rolling bearing 120 which aimed at is described.

  8 is a cross-sectional view showing a rolling bearing disclosed in Patent Document 3, and FIG. 9 is a plan view of a main part of a cage of the rolling bearing shown in FIG.

  Referring to FIGS. 8 and 9, the rolling bearing 120 is configured such that a cage 123 is incorporated between inner and outer rings 121 and 122, and a plurality of balls 125 are accommodated and held in pockets 124 of the cage 123. The cage 123 is guided by a guided surface 126 formed on the outer diameter side in proximity to a guide surface 122b that is separated from the raceway surface 122a having the width W1 on the inner peripheral surface of the outer ring 122.

  The guided surface 126 of the cage 123 is provided with a guided portion 127, a circumferential recess 128, and a concave scallop groove 129 that are close to the guiding surface 122 b of the outer ring 122.

  The circumferential recess 128 is formed along the circumferential direction with a width W2 in the axial direction, and the width W2 of the circumferential recess 128 is larger than the width W1 of the raceway surface 122a of the outer ring 122. As a result, the guided portion 127 does not come into contact with the end portion 122c of the raceway surface 122a of the outer ring 122 during the bearing operation, generation of edge load is suppressed, wear is reduced, and cage vibration is suppressed. The cage sound is prevented.

The concave scallop groove 129 is formed in the guided portion 127 along the circumferential direction, and allows the circumferential concave portion 128 to communicate with the cage end surface 123a. The concave scallop groove 129 discharges excess oil that has moved to the outer ring 122 side by centrifugal force to the outside of the bearing, reduces the torque in a short time, and suppresses torque fluctuation. Thereby, cage vibration is suppressed.
JP 2002-295480 A (page 4, FIG. 1) JP 2002-235750 A (page 3, FIG. 1) Japanese Patent Laying-Open No. 2005-90657 (pages 4-6, FIG. 1)

  In the rolling bearing 120 described in Patent Document 3 described above, the width W2 of the circumferential recess 128 of the cage 123 is larger than the width W1 of the raceway surface 122a of the outer ring 122, so that the bearing is held with respect to the center in the bearing width direction during the bearing operation. Even when the cage 123 is tilted, the guided portion 127 of the cage 123 does not come into contact with the end portion 122c of the raceway surface 122a of the outer ring 122, and the occurrence of edge load at the portion is suppressed.

However, in a state where the cage 123 is inclined with respect to the center in the bearing width direction, the guided portion 127 of the cage 123 does not contact the end 122c of the raceway surface 122a of the outer ring 122, but the guide surface 122b of the outer ring 122. There was a problem that it hits the edge. And there was a problem that the wear significantly progressed due to the edge contact and the durability was greatly lowered.
In addition, the guided portion 127 of the cage 123 is a flat surface, and particularly when the amount of lubricating oil supplied is small, it is liable to be insufficiently lubricated with the guide surface 122b of the outer ring 122, resulting in wear. There was also a problem of end up.

10 and 11 show a conventional ball bearing in which a cage having the same structure as that of the cage 123 described in Patent Document 3 is incorporated.
That is, referring to FIG. 10 and FIG. 11, the cage 131 of the ball bearing 130 is guided to the flange portion 132 in a state inclined with respect to the center in the bearing width direction (state shown in FIG. 10 → state shown in FIG. 11). The surface 132a contacts the inner peripheral surface of the outer ring 133 per edge (see the inside of the ellipse D in FIG. 11).

10 and 11 are guided on both sides in the axial direction with respect to the outer ring 133. In FIGS. 12 to 14, the cage is guided on one side in the axial direction with respect to the outer ring. An example is shown.
That is, referring to FIGS. 12 to 14, the cage 141 of the ball bearing 140 is formed with a flange portion 143 having a guide surface 143 a close to the inner peripheral surface of the outer ring 142 only on the right side in FIG. 12. The outer ring 142 is guided on one axial side (right side in FIG. 12).

  In such a ball bearing 140 as well as the cage 123 of the rolling bearing 120 shown in FIGS. 8 and 9 and the cage 131 of the ball bearing 130 shown in FIGS. Insufficient lubrication between the edge of the guide surface 143a of the flange portion 143 with respect to the inner peripheral surface of the outer ring 142 (state shown in FIG. 14) and between the guide surface 143a of the flange portion 143 and the inner peripheral surface of the outer ring 142 There was a problem that.

  In particular, in recent automobiles and the like, the speed of the rotating portion has been increased, and the number of rotations of the bearing used in the rotating portion has increased, and thus the above-described problems are becoming apparent.

  The present invention can prevent the edge of the guide surface of the flange portion of the cage from contacting the edge of the bearing ring even when the cage is inclined with respect to the center in the bearing width direction due to the revolution of the cage during bearing operation. An object of the present invention is to provide a ball bearing capable of improving wear resistance.

  The above object of the present invention is achieved by the following configurations.

(1) In a ball bearing in which a plurality of balls held by a cage in a freely rolling manner are incorporated between a pair of raceways,
In the cage, a flange portion having a convex guide surface made of a curved surface protrudes on one side of the raceway, and the guide surface is guided by the one raceway on the flange portion. A ball bearing characterized in that the cage is guided to one of the race rings.

  (2) The ball bearing according to (1), wherein the cage is made of a synthetic resin.

  In the ball bearing described in the above (1), the guide surface of the flange portion of the cage is a convex shape formed of a curved surface. Therefore, during the bearing operation, the guide surface of the flange portion becomes one of the guide surfaces of the flange portion along with the revolution of the cage. When friction occurs between the bearing ring and the cage, the gap between the cage and the cage and the bearing ring causes the cage to tilt with respect to the bearing width direction center. Edge contact of the guide surface of the flange portion with respect to one raceway is prevented. In addition, the clearance between the flange portion of the cage and one of the races is increased, and the lubricating oil can easily enter the bearing.

  In the ball bearing described in (2), since the cage is made of synthetic resin, the friction is reduced, the mass is reduced, and the cage is aligned. Due to the aligning action, even when the cage swings, the impact force accompanying the contact between the guide surface and the race is reduced. Moreover, the damage resulting from peeling of the heat treatment hardened layer accompanying the progress of wear is prevented, and secondary damage due to wear is prevented.

  As the synthetic resin material, for example, polyamide, polyphenylene sulfide, polyacetal, polybutylene, polyoxymethylene, polytetrafluoroethylene, and econol are preferably used in consideration of low friction, self-lubricity, strength, and heat resistance. It is not limited.

According to the ball bearing of the present invention, even when the cage revolves with respect to the center of the bearing width direction during the bearing operation, the edge contact of the guide surface of the cage with respect to the raceway ring is prevented. Wear resistance can be improved.
The ball bearing obtained by the present invention is used for automobiles, industrial machines, and the like, and is particularly suitably used for supporting rotating parts of automobile transmissions when high durability is required.

Embodiments of the present invention will be described below with reference to the accompanying drawings.
FIG. 1 is a cross-sectional view showing a ball bearing according to a first embodiment of the present invention, and FIG. 2 is an enlarged cross-sectional view of a main part of the ball bearing of FIG. 3 is an enlarged cross-sectional view of a main part showing a state in which the cage is inclined with respect to the center in the bearing width direction from the state shown in FIG.

  1 to 3, the ball bearing 10 is transferred to a cage 20 between an inner ring raceway surface 11 a formed on the outer peripheral surface of the inner ring 11 and an outer ring raceway surface 12 a formed on the inner peripheral surface of the outer ring 12. A plurality of balls 13 held in a freely movable manner are assembled at predetermined intervals in the circumferential direction.

  The cage 20 is made of synthetic resin, and is guided on one side in the axial direction (right side in FIG. 1). That is, the flange portion 21 projects from the outer ring 12 side at the right end portion in FIG. The flange portion 21 guides the retainer 20 to the outer ring 12 by guiding a convex guide surface 21 a (semicircular cross-sectional shape in the present embodiment) formed of a curved surface to the inner peripheral surface 12 b of the outer ring 12. To do.

  Since the guide surface 21a of the flange portion 21 of the cage 20 has a semicircular cross-sectional shape, the guide surface 21a of the flange portion 21 becomes the inner peripheral surface 12b of the outer ring 12 along with the revolution of the cage 20 when the bearing 10 is operated. 3 due to the gap between the cage 20 and the ball 13 and between the cage 20 and the inner and outer rings 11 and 12, as shown in FIG. Even when the cage 20 is inclined relative to the inner ring 12, the edge of the guide surface 21 a of the flange portion 21 against the inner peripheral surface 12 b of the outer ring 12 is prevented.

  Further, the hemispherical guide surface 21a of the flange portion 21 of the cage 20 increases the gap with the inner peripheral surface 12b of the outer ring 12 as shown in FIG. 2, and an intrusion path is indicated by an arrow A in FIG. As described above, the lubricating oil can easily enter the bearing 10.

  FIG. 4 is a sectional view showing a ball bearing according to the second embodiment of the present invention. FIG. 5 is a cross-sectional view showing a state in which the cage is tilted with respect to the center in the bearing width direction in the ball bearing of FIG. 4, wherein (a) is on the left side with respect to the center in the bearing width direction, and (b) Indicates a state in which an inclination is generated on the right side with respect to the center in the bearing width direction.

  Referring to FIGS. 4 and 5, in the ball bearing 30, the cage 40 is guided on both sides in the axial direction (right and left sides in FIG. 4). That is, the flange portions 41 are provided on the outer ring 31 side at the left and right ends in FIG. Each flange portion 41 guides the retainer 40 to the outer ring 31 by guiding a guide surface 41 a formed in a semicircular cross-sectional shape to the inner peripheral surface 31 a of the outer ring 31.

When the guide surface 41a of each flange portion 41 is formed in a semicircular cross-sectional shape, the cage 40 is inclined with respect to the center in the bearing width direction, that is, as shown in FIG. The inner peripheral surface of the outer ring 31 is tilted to the left with respect to the bearing width direction center and when the cage 40 is tilted to the right with respect to the bearing width direction center as shown in FIG. Edge contact of the guide surface 41a of the flange portion 41 with respect to 31a is prevented (see the inside of the ellipse B in FIG. 5A and the inside of the ellipse C in FIG. 5B).
Other configurations and operations are the same as those in the first embodiment.

As described above, according to the embodiments described above, in the ball bearings 10 and 30, the guide surfaces 21a and 41a of the flange portions 21 and 41 of the cages 20 and 40 are formed in a semicircular cross-sectional shape.
Therefore, when the bearings 10 and 30 are operated, when the guide surfaces 21a and 41a of the flange portions 21 and 41 generate friction with the outer rings 12 and 31 as the cages 20 and 40 revolve, the cages 20 and 40 are generated. Even when the cages 20 and 40 are inclined with respect to the center in the bearing width direction due to the gap between the balls 13 and the balls 13 and between the cages 20 and 40 and the inner and outer rings 11, 12 and 31, the outer ring 12. , 31 can be prevented from hitting the guide surfaces 21a, 41a of the flange portions 21, 41 of the cages 20, 40 with respect to the inner peripheral surface of the cages 20, 40. Thereby, the wear resistance of the cages 20 and 40 and the outer rings 12 and 31 can be improved, and high bearing durability can be ensured.

  Moreover, the clearance gap between the flange parts 21 and 41 of the holder | retainers 20 and 40 and the internal peripheral surfaces 12b and 31a of the outer ring | wheels 12 and 31 can be increased, and lubricating oil is shown by the arrow A in FIG. It is possible to easily enter the bearings 10 and 30 from the path. Thereby, the supply amount of the lubricating oil into the bearings 10 and 30 can be increased, and the friction can be reduced.

  In addition, in each said embodiment, although the guide surfaces 21a and 41a of the flange parts 21 and 41 of the holder | retainer 20 and 40 are formed in a semicircular cross-sectional shape, it is not limited to this, It is the convex shape comprised by the curved surface. For example, the guide surface may be constituted by a combination of a plurality of curved surfaces having different curvatures.

It is sectional drawing which shows the ball bearing which is 1st Embodiment of this invention. It is a principal part expanded sectional view of the ball bearing of FIG. It is a principal part expanded sectional view which shows the state which the inclination of the cage | basket produced with respect to the bearing width direction center from the state shown in FIG. It is sectional drawing which shows the ball bearing which is 2nd Embodiment of this invention. 5 is a cross-sectional view showing a state in which the cage is inclined with respect to the center in the bearing width direction in the ball bearing of FIG. It is sectional drawing which shows the ball bearing currently disclosed by patent document 1. FIG. It is sectional drawing which shows the ball bearing currently disclosed by patent document 2. FIG. It is sectional drawing which shows the rolling bearing currently disclosed by patent document 3. FIG. It is a principal part top view of the cage of the rolling bearing of FIG. It is sectional drawing which shows the conventional ball bearing. It is principal part sectional drawing which shows the state which the cage of the ball bearing of FIG. 10 inclined. It is sectional drawing which shows the other example of the conventional ball bearing. It is a principal part expanded sectional view of the ball bearing of FIG. It is a principal part expanded sectional view which shows the state in which the holder | retainer of the ball bearing of FIG. 12 inclined.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Ball bearing 11 Inner ring 11a Inner ring raceway surface 12 Outer ring 12a Outer ring raceway surface 12b Inner peripheral surface 13 Ball 20 Cage 21 Flange part 21a Guide surface

Claims (2)

In a ball bearing in which a plurality of balls held in a cage so as to roll freely are incorporated between a pair of race rings,
In the cage, a flange portion having a convex guide surface made of a curved surface protrudes on one side of the raceway, and the guide surface is guided by the one raceway on the flange portion. A ball bearing characterized in that the cage is guided to one of the race rings.   The ball bearing according to claim 1, wherein the cage is made of a synthetic resin.

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