JP2008224026A - Rolling bearing and its cage - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing cage having high axial load property and moment resistant property for preventing the noises of the cage or the deformation and breakage of the cage, and to provide a rolling bearing. <P>SOLUTION: The rolling bearing 1 comprises an annular outer ring 3 having outer ring raceway grooves 19, 21 in the inner peripheral face, an annular inner ring 5 arranged concentrically with the outer ring inward in the radial direction and having inner ring raceway grooves 23, 25 in the outer peripheral face, a plurality of rolling elements 7, 9 for rolling between the outer ring raceway groove and the inner ring raceway groove, and the cages 15, 17 each having a recessed portion for rollingly storing the plurality of rolling elements at equal spaces in the peripheral direction, and a pawl portion for holding the rolling elements in the recessed portion. Groove shoulders 31, 35, 33, 27, 41, 39 at both ends of the raceway grooves are different in height, and the pawl portion of the cage is inclined at a predetermined angle δ to the axial direction so as to tend toward the lower groove shoulder. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an improvement in a rolling bearing having a plurality of rolling elements that roll between an outer ring raceway groove and an inner ring raceway groove, and a rolling bearing retainer.

  Conventionally, double row angular contact ball bearings have been used as rolling bearings for pumps, compressors and the like that require axial load capacity and moment resistance. A conventional double-row angular contact ball bearing will be described with reference to FIGS. 3 and 4. FIG. 3 is a longitudinal sectional view showing a part of a conventional double-row angular rolling bearing. FIG. 4 is a perspective view of the cage shown in FIG.

  The double-row angular ball bearing 101 includes an outer ring 103, an inner ring 105, a plurality of rolling elements 107, 109 arranged in two rows, and two cages 115, 117 that hold the rolling elements 107, 109. Two rows of outer ring raceway grooves 119 and 121 are provided on the inner peripheral surface of the outer ring 103, and two rows of inner ring raceway grooves 123 and 125 are provided on the outer peripheral surface of the inner ring 105. Moreover, the rolling elements 107 and 109 are accommodated in the pockets 127 of the holders 115 and 117, respectively, so that they can roll.

  As shown in FIG. 3, the double-row angular ball bearing 101 has a symmetrical structure with respect to the radial direction, so the components located on the right side in the figure will be described. The groove shoulder height I1 of the inner groove shoulder 135 disposed inward in the axial direction of the outer ring raceway groove 119 of the outer ring 103 is greater than the groove shoulder height I0 of the outer groove shoulder 131 disposed outward in the axial direction. Is also high. Also, the groove shoulder height i0 of the outer groove shoulder 137 disposed outward in the axial direction of the inner ring raceway groove 123 of the inner ring 105 is the groove shoulder height of the inner groove shoulder 141 disposed inward in the axial direction. It is higher than i1. Thus, one action line y1 of the bearing is configured to be inclined by a predetermined angle (contact angle e) with respect to the radial direction.

  4 has a predetermined thickness 129 and extends in the axial direction of the double-row angular ball bearing 101 (horizontal direction in FIG. 1). The thickness 129 of the claw 143 is dimensioned so as not to contact the inner groove shoulder 135, the outer groove shoulder 131 of the outer ring 103, the inner groove shoulder 141 of the inner ring 105, and the outer groove shoulder 137. .

On the other hand, in FIG. 3, the outer ring raceway groove 121 of the outer ring 103, the inner ring raceway groove 125 of the inner ring 105, the outer groove shoulder 133 and the inner groove shoulder 135 of the outer ring 103, which are the left side components of the bearing 101. As described above, the lateral groove shoulder 139 and the inward groove shoulder 141 have a symmetric positional relationship with the right component in the radial direction. The other action line y2 of the bearing 101 has a contact angle f (angle −e) with respect to the radial direction. Accordingly, the double-row angular contact ball bearing 101 is equivalent to a configuration in which single-row angular contact ball bearings are connected to each other on the back (see, for example, Patent Document 1).
JP 2001-59523 (FIG. 1 etc.)

  As disclosed in Patent Document 1, in the conventional double-row angular contact ball bearing, when a moment load is applied to the cage, the contact angles e with respect to each of a plurality of rolling elements arranged on the same track are different. As a result, a speed difference is generated in each of the plurality of rolling elements, and tensile stress or compressive stress by the rolling elements may be applied to the cage.

  Therefore, it is conceivable to use an iron cage from the viewpoint of axial load capacity and moment resistance. However, it is desirable to use a plastic cage from the viewpoint of weight reduction, noise reduction, and seizure life.

  Also, when designing angular contact ball bearings, the inner ring shoulder of the outer ring, the outer groove shoulder of the outer ring, the inner groove shoulder of the inner ring, and the outer groove shoulder of the inner ring according to the axial load and moment load received by the angular ball bearing. It is necessary to consider the groove height. In addition, the cage is designed according to the axial load and moment load, and the thickness of the claw that extends horizontally in the cage should not touch the inner groove shoulder of the outer ring and the outer groove shoulder of the inner ring. Need to be dimensioned. Therefore, when the cage is made of plastic, the cage is not sufficiently thick and the required rigidity cannot be obtained, and there is a risk of cage noise generation, cage deformation, and damage. Moreover, if the thickness of the claw portion of the cage is designed to ensure the rigidity of the cage, it may be necessary to increase the overall size of the double-row angular ball bearing.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a rolling bearing cage and a rolling bearing that can secure high axial load characteristics and moment resistance characteristics, and can prevent generation of cage noise and deformation and breakage of the cage.

  In order to solve the above problems, a rolling bearing according to the present invention has an annular outer ring having an outer ring raceway groove on an inner peripheral surface, and is arranged concentrically radially inward of the outer ring, and has an inner ring raceway groove on an outer peripheral surface. An annular inner ring, a plurality of rolling elements that roll between the outer ring raceway groove and the inner ring raceway groove, a recess that accommodates the plurality of rolling elements in a circumferential direction so as to allow rolling, and the recess A retainer having a claw portion for holding the rolling element therein, groove shoulder heights at both ends of each raceway groove are different, and the claw portion of the retainer has a groove shoulder height. A rolling bearing characterized by being inclined at a predetermined angle with respect to the axial direction so as to be directed to a low shoulder of the groove.

  In the rolling bearing, the outer ring raceway groove and the inner ring raceway groove are arranged in a double row in the axial direction, and the double row angular contact ball bearing or the outer ring raceway groove having two cages for holding two rows of rolling elements, and It is preferable that the inner ring raceway groove is a single row angular contact ball bearing in which the inner ring raceway grooves are arranged in a single row.

  In the rolling bearing, a radius ratio (r ′ / D) between a groove radius (r ′) of at least one of the inner ring raceway groove and the outer ring raceway groove and a diameter (D) of the ball member may be 52% or less. preferable. As a result, the area of the inner ring raceway groove and / or outer ring raceway groove that comes into contact with the ball member is increased, and the stress on the raceway groove is reduced, so that a high load on the bearing can be realized.

  In addition, it is preferable that grease is filled as the lubricant, and the condition of the grease (an index indicating the viscosity of the grease) is in the range of 200 to 280.

  A rolling bearing retainer according to the present invention includes an annular outer ring having an outer ring raceway groove on an inner peripheral surface, an inner ring having an inner ring raceway groove on an outer peripheral surface, concentrically disposed radially inward of the outer ring, and the outer ring. A plurality of rolling elements that roll between the raceway groove and the inner ring raceway groove, a recess that accommodates the plurality of rolling elements in a circumferential direction so as to be capable of rolling at equal intervals, and the rolling element is held in the recess. A cage having a claw portion, and the cage for a rolling bearing having different groove shoulder heights at both ends of each raceway groove, wherein the claw portion of the cage has the groove shoulder. It is characterized in that it is inclined at a predetermined angle with respect to the axial direction so as to be directed to the groove shoulder having a low height.

  According to the present invention, since the claw portion of the cage faces the groove shoulder having a low groove shoulder height and is inclined at a predetermined angle with respect to the axial direction, the claw portion and the groove are compared with the claw portion extending parallel to the axial direction. Interference with the shoulder is suppressed, and the degree of freedom in designing the nail thickness is expanded. Therefore, the present invention provides a rolling bearing and a rolling bearing retainer having high axial load characteristics and moment resistance characteristics that can withstand tensile stress and compressive stress due to moment load, and can prevent generation, deformation, and breakage of cage noise. be able to.

  Hereinafter, an embodiment in which the rolling bearing of the present invention is applied to a double-row angular ball bearing will be described with reference to the drawings. In the drawings, the same elements are denoted by the same reference numerals.

  <First Embodiment>

  The double row angular contact ball bearing which is 1st Embodiment is demonstrated referring FIG. 1, FIG. FIG. 1 is a view showing a part of the double-row angular contact ball bearing according to the first embodiment in a cross section along the axial direction. FIG. 2 is a perspective view of the cage shown in FIG.

  As shown in FIG. 1, the double-row angular contact ball bearing 1 includes an annular outer ring 3, a radially inner side of the outer ring 3, an annular inner ring 5 that is concentrically arranged with the outer ring 3 and is relatively rotatable. A plurality of rolling elements or ball members 7 and 9 arranged in a double row between the outer ring 3 and the inner ring 5 and a pair of cages 15 and 17 that hold the ball members 7 and 9 rotatably are provided.

  On the inner peripheral surface of the outer ring 3, two concave portions extending in the circumferential direction, that is, outer ring raceway grooves 19 and 21 are provided. Similarly, on the outer peripheral surface of the inner ring 5, two concave portions extending in the circumferential direction, that is, inner ring raceway grooves 23 and 25 are provided. A plurality of ball members 7 and 9 roll on the first track 24 formed by the outer ring raceway groove 19 and the inner ring raceway groove 23 and on the second raceway 26 formed by the outer ring raceway groove 21 and the inner ring raceway groove 25, respectively. Arranged as possible. Further, the radius of curvature of each raceway groove 19, 21, 23, 25 is slightly larger than the radius of curvature of the ball members 7, 9. Therefore, the ball member 7 rolls on the first track 24, and the ball member 9 rolls on the second track 26. Thus, the outer ring 3 and the inner ring 5 are configured to be relatively rotatable by the ball member 9.

  Further, members constituting the first track 24 and peripheral elements thereof will be described. An outer groove shoulder 31 and an inner groove shoulder 35 are formed at both axial ends of the outer ring raceway groove 19. The groove shoulder height H 0 of the outer groove shoulder 31 is dimensioned lower than the groove shoulder height H 1 of the inner groove shoulder 35. On the other hand, an outer groove shoulder 27 and an inner groove shoulder 41 are formed at both axial ends of the inner ring raceway groove 23. The groove shoulder height h 0 of the outer groove shoulder 27 is dimensioned higher than the groove shoulder height h 1 of the inner groove shoulder 41. Here, the groove shoulder height is the radial distance of the bearing from the bottom of the raceway groove to the top surface of the groove shoulder.

  In addition, the action line Y1 intersects the radial line X1 in the figure at a contact angle a and extends away from the rolling bearing 1 as it goes radially inward. Therefore, the inner groove shoulder 35 and the outer groove shoulder 27 are on the side receiving the load.

  Further, the outer ring raceway groove 21, the inner ring raceway groove 25, and the cage 17 constituting the second raceway 26 are the same as the outer ring raceway groove 19, the inner ring raceway groove 23, the cage 15 and the radial center line of FIG. The positional relationship is symmetrical with respect to x ′. Accordingly, the action line Y2 intersects the radial line X2 at the contact angle b, and extends away from the rolling bearing 1 as it goes inward in the radial direction. Therefore, the inner groove shoulder 35 and the outer groove shoulder 39 are on the side receiving the load. The inclinations of the contact angles b and a are opposite to each other, but the magnitudes of the angles are equal to each other.

  Next, the cage will be described in detail. The resin cages 15 and 17 have the same shape and the same dimensions, and the difference is the direction in which they are arranged. Therefore, only the cage 15 will be described with reference to FIG. The retainer 15 includes an annular main portion 15a, a column portion 15b that protrudes upward from the main portion 15a at a predetermined angle δ with respect to the axial direction, and pockets 18 that are recessed portions at equal intervals in the circumferential direction. A claw portion 15c that is continuous with the portion 15b and protrudes from both ends of the pocket 18 to hold the ball member 7 in the pocket 18. The curved surfaces in contact with the ball member 7 of the claw portion 15c have substantially the same radius of curvature as the curved surfaces constituting the pocket 18, and are smoothly continuous with each other. In the above-described configuration, the ball member 7 is mounted in the pocket 18 by bending the pair of claw portions 15c arranged to face each other via the pocket 18 in a direction away from each other.

  Further, the outer peripheral surfaces of the main portion 15a, the column portion 15b, and the claw portion 15c of the cage 15 are inclined with an angle δ with respect to the line L parallel to the rotation axis. That is, the cage 15 is configured to reduce in diameter toward the tip of the claw portion 15c.

  According to the double-row angular ball bearing 1 of FIGS. 1 and 2, an annular space is formed by the inner peripheral surface of the outer ring 3 and the outer peripheral surface of the inner ring 5 by inclining the outer peripheral surface of the cage 15 as described above. Even if there are irregularities inside, the thickness 29 of the main portion 15a, the column portion 15b, and the claw portion 15c of the cage 15 can be set to the maximum dimension.

  That is, in the conventional cage (see FIG. 3), since the pillar portion and the claw portion of the cage extend in parallel to the rotation axis, the inner groove shoulder 135 of the outer ring and the outer groove shoulder of the inner ring 137 had to be dimensioned so as not to contact the cage, and the degree of freedom in design was narrow. However, as in the cage 15 of the present embodiment, the main portion 15a, the column portion 15b, and the claw portion 15c of the cage 15 are inclined so that the thickness 29 (FIG. 1) of the cage 15 is reduced. Even if it is larger (see FIG. 3), the cage 15 does not contact and interfere with the inner groove shoulder 35 of the outer ring 3 and the outer groove shoulder 27 of the inner ring 5, so that the dimensions of the cages 15 and 17 are designed. Can be greatly expanded.

  Therefore, even when the cages 15 and 17 are made of plastic, the cage thickness 29 can be sufficiently secured and necessary rigidity can be obtained. Fear can be prevented. Moreover, it is not necessary to increase the overall dimensions of the double-row angular contact ball bearing.

  Further, when designing the angular ball bearing and the cage according to the axial load and the moment load, the inner groove shoulder 35 of the outer ring 3, the groove heights of the outer groove shoulders 31 and 33, and the inner groove of the inner ring 5. The degree of freedom in dimensional design for each groove height of the shoulder 41 and the outer groove shoulders 27 and 39 is widened, and the degree of freedom in dimensional design such as the thickness of the cage is widened. Therefore, high axial load characteristics and moment resistance in angular ball bearings Characteristics can be secured.

  In the above embodiment, the height of the outer groove shoulder of the outer ring is lower than the height of the inner groove shoulder of the outer ring, and the height of the outer groove shoulder of the inner ring is higher than the height of the inner groove shoulder of the inner ring; However, the present invention is not limited to this configuration. For example, the height of the outer groove shoulder of the outer ring may be higher than the height of the inner groove shoulder of the outer ring, and the height of the outer groove shoulder of the inner ring may be lower than the height of the inner groove shoulder of the inner ring. In the case of such a rolling bearing, the outer peripheral surface of the cage, that is, the outer peripheral surfaces of the main portion, the column portion, and the claw portion is inclined with respect to the line L by an angle −δ. In other words, the cage is configured to expand toward the tip of the claw portion.

  In the present embodiment, all of the main part, the column part, and the claw part are inclined by a predetermined angle δ, but this angle depends on the outer groove shoulder of the outer ring and the inner ring, and the dimensions and shape of the inner groove shoulder. Needless to say, it can be changed as appropriate. Moreover, it is good also as a structure which inclines only any one or two of a main part, a pillar part, and a nail | claw part.

  <Second Embodiment>

  FIG. 5 is a cross-sectional view (a) of a single row angular contact ball bearing (showing each ring and ball member when the radius ratio is 52% or less) according to the second embodiment and a conventional radial ball bearing (radius ratio is It is sectional drawing (b) of each track ring and ball member when it exceeds 52%. In FIG. 5, for convenience of explanation, the cage is not shown.

  As shown in FIG. 5A, a single row angular contact ball bearing 50 according to the present embodiment includes an outer ring 52 having an outer ring raceway groove 51, an inner ring 54 having an inner ring raceway groove 53, and a plurality of ball members 55. And a cage 15 (FIG. 2) for holding each ball member 55 in each pocket 18 at a uniform position so as to roll freely, and a plurality of ball members between the inner ring raceway groove 53 and the outer ring raceway groove 51. 55 is arranged to roll freely.

  Groove shoulders 52a and 52b are formed at both axial ends of the outer ring raceway groove 51, and the groove shoulder 52b is higher than the groove shoulder 52a. A groove shoulder 54a and a groove shoulder 54b are formed at both axial ends of the inner ring raceway groove 53, and the groove shoulder 54a is higher than the groove shoulder 54b. The action line Y intersects the radial line X at the contact angle m, and the groove shoulder 52b and the groove shoulder 54a are on the side receiving the load.

  5A, the inner ring raceway groove 53 of the inner ring 54 has a groove shape having a groove radius r53, and the radius between the groove radius r53 and the diameter D of the ball member 55. In the single-row angular contact ball bearing 50 of FIG. The ratio (r53 / D) is 52% or less. Similarly, the outer ring raceway groove 51 of the outer ring 52 has a groove shape having a groove radius r51, and the radius ratio (r51 / D) between the groove radius r51 and the diameter D of the ball member 55 is 52% or less.

  As described above, in the single row angular contact ball bearing 50 according to the present embodiment, the groove radius r53 of the inner ring raceway groove 53 of the inner ring 54, the groove radius r51 of the outer ring raceway groove 51 of the outer ring 52, and the diameter of the ball member 55 are set. By making the radius ratio (r53 / D, r51 / D) smaller than 52% applied in the conventional case as shown in FIG. 5 (b), on the grooves of the raceway grooves 51, 53 with which the ball member 55 contacts. The stress is reduced.

  5B, the radius ratio (r63 / D) between the groove radius r63 of the inner ring raceway groove 63 and the diameter D of the ball member 55 exceeds 52%. Similarly, the groove of the outer ring raceway groove 61 The radius ratio (r61 / D) between the radius r61 and the diameter D of the ball member 55 exceeds 52%. For this reason, since the area which contacts the ball member 55 in each track groove 61 and 63 becomes small, the stress on the groove of each track groove 61 and 63 will become large, whereas FIG. According to a), each radius ratio (r53 / D, r51 / D) is 52% or less, and the area in contact with the ball member 55 in the inner ring raceway groove 53 and the outer ring raceway groove 51 is increased. The stress on the grooves 51 and 53 is reduced. For this reason, the single-row angular contact ball bearing 50 of the present embodiment enables a high load in the applied bearing device and can achieve a high load.

  In addition, as in FIG. 1, high axial load characteristics and moment resistance characteristics are secured in the single-row angular contact ball bearings, and the degree of freedom in dimensional design such as the thickness of the cage is widened. Since it can be secured and the required rigidity can be obtained, it is possible to prevent the occurrence of cage noise, the deformation and breakage of the cage, and it is also necessary to increase the overall size of the single-row angular contact ball bearing. Absent.

  The radius ratios (r53 / D, r51 / D) described above are preferably 50% or more. Moreover, it is needless to say that the configuration of FIG. 5A is preferably applied to the double-row angular ball bearing 1 of FIG.

  6 is a view showing an example of the shape of the pocket 18 of the cage 15 of FIG. 2, and is a view of the inclined pocket 18 as seen from the front in the inclined direction n of FIG. As shown in FIG. 6, the pocket 18 that is a concave portion is a spherical concave surface portion 20 a having a radius r1 (r1> r (r: radius of the ball member 55)) whose lower portion is centered on the center O of the ball member 55. The opened upper portion is a spherical concave surface portion 20c having a radius r2 (r2> r) centered on the center O of the ball member 55, and the middle portion is a cylindrical axial centered on the rolling center axis v of the ball member 55. It is comprised in the shape which is the cylindrical concave-surface part 20b. Further, as indicated by the broken line in FIG. 6, the spherical concave surface portion 20a has a radius centered on the point O1 shifted from the center O on the rolling center axis v, and the spherical concave surface portion 20c has a center on the rolling center axis v. It is good also as a structure which has the radius centering on the point O2 shifted | deviated from O. In FIG. 6, between the pocket 18 of the cage 15 and the ball member 55, the vicinity of the boundary between the spherical concave surface portion 20a and the cylindrical concave surface portions 20b, 20b, and the spherical concave surface portions 20c, 20c and the cylindrical concave surface portions 20b, 20b. In the vicinity of the boundary, lubricant reservoir portions A and B having relatively large spaces are formed.

  The double-row angular contact ball bearing 1 of FIG. 1 and the single-row angular contact ball bearing 50 of FIG. 5A are used with a lubricant filled therein, but it is preferable to use grease as the lubricant. In this case, the grease preparation (an index indicating the viscosity of the grease) is preferably in the range of 200 to 280. When using relatively hard grease as a lubricant in this way, if the cage pocket shape is a single spherical shape, it will easily return to the pocket once the grease is pushed out of the pocket while the bearing is in use. Although it is difficult and lubrication failure is likely to occur in the cage, in this embodiment, grease is collected between the pocket 18 and the ball member 55 by using the cage 15 as shown in FIG. Since it is held by the portions A and B and is difficult to be pushed out of the pocket 18 and is easily returned to the pocket 18 even if pushed out, the lubricating performance by the grease can be exhibited and maintained.

  In addition, as a plastic material used for the above-mentioned cage, polyamide resin or the like is preferable. Furthermore, the rolling bearing and its cage of the present invention are not limited to the double-row angular ball bearing of the first embodiment, the single-row angular ball bearing of the second embodiment, and their cages. Needless to say, the present invention can be applied to combination angular contact ball bearings used in combination with two single-row angular combinations, cages thereof, and the like.

  In the said embodiment, although the structure of the ball bearing using a ball member as a rolling element was demonstrated, this invention is not limited to this. For example, the ball bearing cage of the present invention can be applied to any rolling bearing having an outer ring and an inner ring that can rotate relative to the outer ring, such as a cylindrical roller bearing or a needle roller bearing.

  The present invention can be embodied in many forms without departing from its essential characteristics. Therefore, it is needless to say that the above-described embodiment is exclusively for description and does not limit the present invention.

It is a longitudinal section of a double row angular contact ball bearing of an embodiment by a 1st embodiment. It is a perspective view of the holder | retainer shown in FIG. It is longitudinal direction sectional drawing of the conventional double row angular contact ball bearing. It is a perspective view of the holder | retainer shown in FIG. Sectional view (a) of a single-row angular contact ball bearing according to the second embodiment (showing each bearing ring and ball member when the radius ratio is 52% or less) and a conventional radial ball bearing (radius ratio exceeding 52%) It is sectional drawing (b) of each track ring and a ball member in the case of a case. It is a figure which shows the example of a shape of the pocket 18 of the holder | retainer 15 of FIG. 2, and is the figure which looked at the inclined pocket 18 to the front from the inclination direction n of FIG.

Explanation of symbols

1 Double-row angular contact ball bearing 3 Outer ring 5 Inner ring 7, 9 Ball member (rolling element)
15, 17 Cage 19, 21 Outer ring raceway groove 23, 25 Inner ring raceway groove 50 Single row angular contact ball bearing 51 Outer ring raceway groove 52 Outer ring 53 Inner ring raceway groove 54 Inner ring 55 Ball member

Claims (5)

A rolling bearing,
An annular outer ring having an outer ring raceway groove on the inner peripheral surface;
An annular inner ring that is concentrically disposed radially inward of the outer ring and has an inner ring raceway groove on the outer peripheral surface;
A plurality of rolling elements rolling between the outer ring raceway groove and the inner ring raceway groove;
A retainer having a recess that accommodates the plurality of rolling elements so as to be capable of rolling at equal intervals in the circumferential direction, and a claw that holds the rolling element in the recess.
The groove shoulders at both ends of each raceway groove have different groove shoulder heights, and the claw portions of the cage are inclined at a predetermined angle with respect to the axial direction so as to face the groove shoulders with a low groove shoulder height. Rolling bearing.   The outer ring raceway groove and the inner ring raceway groove are arranged in a double row in the axial direction, and a double row angular contact ball bearing having two cages for holding two rows of rolling elements or the outer ring raceway groove and the inner ring raceway groove are provided. The rolling bearing according to claim 1, which is a single-row angular contact ball bearing arranged in a single row.   The radius ratio (r '/ D) between the groove radius (r') of at least one of the inner ring raceway groove and the outer ring raceway groove and the diameter (D) of the rolling element is 52% or less. The rolling bearing described. Fill the bearing with grease as a lubricant,
The rolling bearing according to claim 1, 2 or 3, wherein the grease has an adjustment in a range of 200 to 280. An annular outer ring having an outer ring raceway groove on an inner peripheral surface, an inner ring having an inner ring raceway groove concentrically disposed radially inward of the outer ring, and between the outer ring raceway groove and the inner ring raceway groove A plurality of rolling elements that roll, a retainer that accommodates the plurality of rolling elements in a circumferential direction so as to be capable of rolling at equal intervals, and a cage having a claw portion that holds the rolling elements in the recess. The cage for a rolling bearing having different groove shoulder heights at both ends of each raceway groove,
The cage for a rolling bearing, wherein the claw portion of the cage is inclined at a predetermined angle with respect to the axial direction so as to face the groove shoulder having a low groove shoulder height.

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