JP7142629B2 - Angular contact ball bearing cage and angular contact ball bearing - Google Patents

Description

Related application

This application claims priority from Japanese Patent Application No. 2017-089173 filed on April 28, 2017, and is incorporated herein by reference in its entirety.

The present invention relates to an angular contact ball shaft and its retainer used for machine tool main shaft bearings and other equipment.

Angular contact ball bearings for machine tool spindles are required to rotate stably at high speeds. Air-oil lubrication, oil mist lubrication, and grease lubrication are used for lubrication of the bearings. FIG. 9 shows a relatively commonly used air-oil lubricated bearing. As shown in FIG. 9, in many air-oil lubricated bearings, the retainer 4A is guided by the outer ring 2 (for example, Patent Document 1).

Japanese Unexamined Patent Application Publication No. 2011-132999

In the case of the retainer 4A of the outer ring guide type as shown in FIG. 9, the retainer 4A rotates while touching slightly. When the lubricating oil is extremely small and thin, a large frictional force is generated on the guide surface 2b on the inner diameter surface of the outer ring, which guides the outer diameter surface of the cage, and the cage 4A may be violently touched. Due to the whirling, the contact between the outer diameter surface of the retainer 4A and the inner diameter surface of the outer ring 2 becomes stronger, which may lead to noise in the bearing.

SUMMARY OF THE INVENTION An object of the present invention is to provide an angular contact ball bearing retainer and an angular contact ball bearing capable of suppressing violent whirling of the retainer and reducing abnormal noise while maintaining high speed performance.

The angular contact ball bearing retainer of the present invention has guide surfaces for guiding the retainer on one side in the axial direction of the bearing sandwiching the raceway surface on the inner diameter surface of the outer ring, and has a counterbore on the other side. The retainer is cylindrical and has a plurality of pockets formed in the axial middle of the retainer for retaining the rolling elements of the bearing, and the outer ring on the outer peripheral surface of the retainer. a guided surface portion guided by a guide surface; a weight-increasing portion extending outwardly in the axial direction from the guided surface portion; and a relief surface spaced from the

According to this configuration, the weight-increasing portion extending outward in the axial direction from the guided surface portion increases the weight of the cage as a whole. Therefore, the whirling of the cage due to the large frictional force generated by the contact between the inner diameter surface of the outer ring and the outer diameter surface of the cage can be suppressed, and abnormal noise can be prevented. Since the portion of the cage on the outer ring counterbore side is not guided by either of the inner and outer rings, the effect of suppressing whirling cannot be expected even if the weight of the counterbore side portion is increased. In the above configuration, since the weight of the guide surface side is increased, it is possible to achieve the effect of suppressing whirling.

In addition, since the outer diameter surface of the weight-increased portion of the retainer constitutes a relief surface spaced apart from the inner diameter surface of the outer ring more than the guided surface portion, the width (axial dimension) of the retainer is increased. As a result, the fluidity of the lubricating oil is improved, and heat generation of the bearing can be prevented. As a result, higher speed operation becomes possible. In addition, since there is no change in the configuration of the guide between the inner diameter surface of the outer ring and the outer diameter surface of the retainer, and there is no change in the dimensions of the pocket portions of the retainer, the retainer having the above configuration can be easily applied to existing bearings.

In the angular contact ball bearing retainer of the present invention, the relief surface may be tapered away from the inner diameter surface of the outer ring toward the retainer width surface. Further, the relief surface may have a stepped shape that gradually separates from the inner diameter surface of the outer ring toward the retainer width surface. When the relief surface is tapered, it is possible to increase the weight of the cage by enlarging the weight-increasing portion while ensuring good flow of lubricating oil. Moreover, unlike the case of a stepped shape, the tapered shape makes it difficult for stress concentration to occur even when the retainer whirles, resulting in excellent retainer strength.

In the angular contact ball bearing retainer of the present invention, the inner peripheral surface of the increased weight portion may protrude toward the inner diameter side from the inner peripheral surface of the retainer width direction portion forming the guided surface portion. According to this configuration, the size can be increased not only in the axial direction but also in the radial direction by forming the weight-increasing portion. As a result, the weight of the retainer can be further increased, so that the effect of suppressing whirling due to the increase in weight is improved.

In the angular contact ball bearing retainer of the present invention, the inner peripheral surface of the retainer on the counterbore side may bulge radially outward from the pocket forming portion toward the outside in the axial direction. Here, the "pocket forming portion" refers to a portion of the axial range in which the pocket is formed in the retainer. According to this configuration, even the side of the retainer that is not guided by the inner diameter surface of the outer ring also increases in weight due to the increase in size. As a result, the weight balance with the side to be guided is improved, and it is possible to more stably suppress the contact. The axial dimension of the portion closer to the width than the pocket on the counterbore side may be larger than the dimension required for strength design. This further increases the weight and further improves the weight balance.

In the angular contact ball bearing retainer of the present invention, a convex portion protruding radially outward toward the outer ring is formed on the outer diameter surface of the retainer on the counterbore side, and the outer diameter surface of the convex portion includes the A straight surface portion may be formed to support guidance with the inner diameter surface of the outer ring.

In the conventional bearing shown in FIG. 9, lean lubrication and entry of foreign matter may cause the cage to rotate or tilt. Such contacting and tilting may cause deformation of the retainer. According to this configuration, since the convex portion is provided, the weight of the retainer is increased, and the rigidity of the retainer is also increased. As a result, deformation of the retainer can be suppressed.

When the straight surface portion is provided, the radial clearance between the straight surface portion and the inner diameter surface of the outer ring is larger than the radial clearance between the guided surface and the inner diameter surface of the outer ring, and It may be set to twice or less the radial clearance between the inner diameter surface of the outer ring. According to this configuration, since the guide side and the counterbore side of the retainer are balanced, it is possible to suppress wobbling and inclination of the retainer.

When the straight surface portion is provided, the axial length of the guided surface portion is set to be the same as the axial length of the straight surface portion, and the volume on the guiding side of the retainer is set to be the same as the volume on the counterbore side. may According to this configuration, since the guide side and the counterbore side of the retainer are balanced, it is possible to suppress wobbling and inclination of the retainer.

When the convex portion is provided, a plurality of the convex portions may be provided so as to be spaced apart in the circumferential direction. According to this configuration, it is possible to suppress an increase in the contact area between the outer ring and the retainer on the counterbore side. As a result, it is possible to suppress the heat generation of the bearing and the accumulation of heat in the bearing space.

An angular contact ball bearing according to the present invention has a guide surface for guiding a retainer on one side in the axial direction of the bearing sandwiching a raceway surface of an inner diameter surface of an outer ring, and a counterbore on the other side, Equipped with the retainer of the present invention. According to the angular contact ball bearing of this configuration, the same actions and effects as those of the angular contact ball bearing retainer of the present invention can be obtained.

Any combination of at least two configurations disclosed in the claims and/or the description and/or the drawings is included in the invention. In particular, any combination of two or more of each claim is included in the invention.

The present invention will be more clearly understood from the following description of preferred embodiments with reference to the accompanying drawings. However, the embodiments and drawings are for illustration and description only and should not be used to define the scope of the invention. The scope of the invention is defined by the appended claims. In the accompanying drawings, the same part number in multiple drawings indicates the same or corresponding part.
1 is a partial cross-sectional view of an angular contact ball bearing according to a first embodiment of the invention; FIG. It is explanatory drawing which shows the same angular contact ball bearing and the conventional angular contact ball bearing in comparison. It is sectional drawing which shows the same angular contact ball bearing and an outer ring spacer with a nozzle. This is an outer ring double shoulder guided angular contact ball bearing. FIG. 6 is a partial cross-sectional view of an angular contact ball bearing according to a second embodiment of the invention; It is explanatory drawing which shows the same angular contact ball bearing and the conventional angular contact ball bearing in comparison. It is the front view which looked at the retainer of the same angular contact ball bearing from the counter bore side. It is a perspective view which shows the same retainer. FIG. 11 is a cross-sectional view of a conventional example;

A first embodiment of the invention will be described with reference to FIGS. 1 to 3. FIG. In this angular contact ball bearing, a plurality of rolling elements 3 are interposed between an inner ring 1 and an outer ring 2 and these rolling elements 3 are held by a retainer 4 . The rolling bodies 3 are, for example, balls. The raceway surface 1a of the inner ring 1 and the raceway surface 2a of the outer ring 2 are formed so as to form a contact angle θ. The inner diameter surface of the outer ring 2 is formed with a guide surface 2b for guiding the retainer 4 on one side (the left side in FIG. 1) in the axial direction C of the bearing across the raceway surface 2a, and on the other side (the left side in FIG. 1). right side) is formed with a counterbore 5 .

The retainer 4 is cylindrical. The axis of the retainer 4 is parallel to the axial direction C of the bearing. A plurality of pockets 6 for holding the respective rolling elements 3 are formed in an intermediate portion of the retainer 4 in the axial direction C. As shown in FIG. The pockets 6 are arranged at equal intervals in the circumferential direction of the retainer 4 . The pocket 6 is, for example, a cylindrical surface extending in the radial direction. The retainer 4 is, for example, a machined product of resin such as laminated phenolic resin. However, the material of the retainer 4 is not limited to this, and may be metal or titanium alloy. In the following description, the axial direction C may be referred to as the width direction of the retainer 4 .

In this embodiment, a weight increasing portion 7 is provided on the guide surface 2b side of the outer ring 2 in the retainer 4 . A weight balance portion 8 is provided on the counterbore 5 side of the outer ring 2 in the retainer 4 . A guided surface portion 4 a guided by the guide surface 2 b of the outer ring 2 is formed on the outer peripheral surface of the retainer 4 . In FIG. 1, a range a indicates a retainer width direction portion formed by the guided surface portion 4a. The increased weight portion 7 is a portion that extends outward in the width direction (axial direction C) from the guided surface portion 4a. The outer peripheral surface of the weight-increasing portion 7 forms a relief surface 7a spaced further from the inner diameter surface of the outer ring 2 than the guided surface portion 4a. The shape of the relief surface 7a is tapered away from the inner diameter surface of the outer ring 2 toward the width surface 4b (left end surface in FIG. 1) of the retainer 4. As shown in FIG.

Further, the weight-increasing portion 7 has a cross-sectional shape that bulges toward the inner diameter side from the retainer width direction portion a. In other words, the inner peripheral surface of the weight-increasing portion 7 protrudes toward the inner diameter side from the inner peripheral surface of the retainer width direction portion a. In this embodiment, the inner peripheral surface of the increased weight portion 7 gradually bulges radially inward from the retainer width direction portion a toward the width surface 4b of the retainer 4 (the left end surface in FIG. 1). As a result, the cross-sectional dimensions in the width direction and the radial direction are larger than those of the retainer 4A of FIG. Both cages 4, 4A are shown superimposed in FIG. 2 for comparison. The cross-sectional shape of the inner peripheral surface of the weight increasing portion 7 is tapered such that the diameter gradually decreases toward the width surface 4 b of the retainer 4 .

The weight balance portion 8 is a portion of the retainer 4 closer to the width surface 4c (right side in FIG. 1) than the pocket 6, and is a portion whose width dimension is larger than the dimension required for strength design. Specifically, the weight balance portion 8 is a portion of the retainer 4 on the side of the counterbore 5 of the outer ring 2 and on the side of the width surface 4 c (the end surface on the right side in FIG. 1 ) of the pocket 6 . The weight balance portion 8 bulges radially outward from the pocket forming portion of the retainer 4 toward the outside in the width direction (to the right in FIG. 1). Here, the “pocket forming portion” refers to a portion of the retainer 4 in the width direction (axial direction C) where the pocket 6 is formed.

The inner diameter surface of the weight balance portion 8 is inclined radially inwardly from the pocket forming portion toward the width surface 4c (the end surface on the right side in FIG. 1), and is greatest at the small diameter portion 8a in the intermediate portion in the cage width direction (axial direction C). It has a small diameter and is inclined radially outward from the small diameter portion 8a toward the width surface 4c (the end surface on the right side in FIG. 1).

The lubrication type of the angular contact ball bearing of this embodiment is air-oil lubrication. An example is shown in FIG. As shown in FIG. 3, the nozzle 11 provided in the nozzle-equipped outer ring spacer 10 is inserted between the inner ring 1 and the retainer 4 on the guide surface 2b side of the outer ring 2, and air oil is discharged from the nozzle hole 11a. be.

According to this configuration, since the retainer 4 has the weight-increasing portion 7 extending outward (to the left in FIG. 1) in the width direction from the guided surface portion 4a, the weight of the entire retainer increases. Therefore, it is possible to suppress violent whirling of the cage 4 caused by a large frictional force generated by the contact of the guide surface 2b of the outer ring 2 with the outer diameter surface of the cage, thereby preventing abnormal noise. A portion of the retainer 4 on the counterbore 5 side of the outer ring 2 (on the right side in FIG. 1) is not guided by either of the inner and outer rings 1 and 2 . Therefore, even if the weight of the counterbore side portion is increased, the effect of suppressing whirling cannot be expected. can be obtained.

Further, the outer diameter surface of the weight-increased portion 7 of the retainer 4 is a relief surface 7a spaced further from the inner diameter surface of the outer ring 2 than the guided surface portion 4a. As a result, the width dimension of the retainer is increased, the fluidity of the lubricating oil is improved, and the heat generation of the bearing can be prevented. Therefore, higher speed operation of the bearing is possible. In addition, since there is no change in the configuration of the guide of the cage 4 by the guide surface 2b of the outer ring 2, and there is no change in the dimensions of the locations where the pockets 6 of the cage 4 are formed, the cage 4 of this embodiment can be used in existing bearings. can be easily applied to

The widthwise dimension (axial direction C) of the weight-increasing portion 7 may be any widthwise dimension that does not protrude from the width surfaces of the inner and outer rings 1 and 2 . Specifically, the widthwise dimension of the cage 4 may be such that the widthwise surfaces 4b and 4c of the cage 4 are close to the widthwise surfaces of the inner and outer rings 1 and 2. may be

Since the escape surface 7a of the weight-increasing portion 7 is tapered, the weight-increasing portion 7 can be enlarged to increase the weight of the retainer 4 while ensuring good flow of lubricating oil. The relief surface 7a of the weight increasing portion 7 may have a stepped shape that separates from the inner diameter surface of the outer ring in stages from the guided surface portion 4a. Even if there is, it is difficult for stress concentration to occur, and the strength of the cage is also excellent.

The dimensions of the retainer 4 are increased not only in the width direction (axial direction C) but also in the radial direction due to the formation of the increased weight portion 7 . As a result, the weight can be further increased, and the effect of suppressing whirling due to the increase in weight is improved.

Further, the cage 4 is provided with a weight balance portion 8, and even on the non-guided side of the cage 4, the inner peripheral surface of the cage 4 extends outward in the axial direction C (right side in FIG. 1) from the pocket forming portion. It bulges out on the inner diameter side. Therefore, the weight of the non-guided side of the retainer 4 also increases due to the increased cross-sectional dimension, and the weight balance with the guided side is improved. As a result, the effect of suppressing contact and rotation is further improved.

Although the above-described embodiment employs the outer ring single-shoulder guide system, it can also be applied to the outer ring double-shoulder system as shown in FIG. 4 as a reference proposal. In this case, the weight increasing portions 7 may be provided on both axial sides of the cage 4, or the weight increasing portion 7 may be provided on one side and the weight balance portion 8 may be provided on the other side as in the embodiment of FIG. good.

A second embodiment of the invention will be described with reference to FIGS. 5 to 8. FIG. In the second embodiment, the shape of the retainer 4 on the counter bore side is different from that in the first embodiment. Parts having the same configuration as in the first embodiment are denoted by the same reference numerals, and descriptions thereof are omitted.

In the second embodiment, a convex portion 20 that protrudes radially outward toward the outer ring 2 is formed on the outer diameter surface of the retainer 4 on the counterbore 5 side (right side in FIG. 5). An outer diameter surface of the convex portion 20 has a tapered surface portion 22 and a straight surface portion 24 .

The tapered surface portion 22 extends from the pocket-forming portion of the retainer 4 outward in the axial direction C (to the right in FIG. 5) so as to approach the inner surface of the outer ring 2 . That is, the tapered surface portion 22 is inclined radially outward toward the outside in the axial direction C (the width surface 4c). The tapered surface portion 22 constitutes a relief surface with respect to the inner diameter surface of the outer ring 2 on the counterbore side.

The straight surface portion 24 is continuous with the tapered surface portion 22 and extends outward in the axial direction C (to the right in FIG. 5). That is, the straight surface portion 24 extends substantially parallel to the axial direction C and parallel to the inner diameter surface of the outer ring 2 on the counterbore side. The straight surface portion 24 has the smallest radial clearance from the inner diameter surface of the outer ring 2 on the counterbore 5 side. The straight surface portion 24 supports guidance between the retainer 4 and the inner diameter surface.

FIG. 6 shows both the retainer 4 of the second embodiment and the conventional retainer 4A superimposed. A conventional retainer 4A is indicated by a solid line, and a retainer 4 of the second embodiment is indicated by a broken line. As is clear from the figure, the retainer 4 of the second embodiment has larger cross-sectional dimensions in the width direction (axial direction) and radial direction than the conventional retainer 4A. The retainer 4 in FIG. 5 and the retainer 4 indicated by broken lines in FIG. 6 have different cross sections. Specifically, the retainer 4 in FIG. 5 is a cross section taken along line VV in FIG. 7, and the retainer 4 indicated by broken lines in FIG. 6 is a cross section along line VI-VI in FIG.

Let δa be the radial clearance between the guided surface 4a and the inner diameter surface of the outer ring 2, and δb be the radial clearance between the straight surface portion 24 and the inner diameter surface of the outer ring 2 on the counterbore 5 side. In this case, δb is preferably larger than δa and not more than two times δa (δa<δb≦2δa).

Let A1 be the axial length of the guided surface portion 4a on the counterbore side (left side in FIG. 5), and let A2 be the axial length of the straight surface portion 24 on the counterbore side (right side in FIG. 5). In this case, A1 and A2 are preferably the same (A1=A2). The volume of the retainer 4 on the counterbore side (guide side) is V1, and the volume of the retainer 4 on the counterbore side is V2. In this case, V1 and V2 are preferably the same (V1=V2).

As shown in FIG. 7, a plurality of protrusions 20 are provided at intervals in the circumferential direction. In other words, the retainer outer peripheral surface 25 without protrusions is formed between the adjacent protrusions 20 on the outer peripheral surface of the retainer 4, and the protrusions 20 and the retainer outer peripheral surfaces 25 are alternately arranged in the circumferential direction. It is

Specifically, as shown in FIG. 8, the protrusions 20 are formed every other pocket 6 . That is, the projections 20 are formed in the regions of the two pockets 6 adjacent to the pocket 6 in which the retainer outer circumferential surface 25 without projections is formed. Similarly, in the region of the two pockets 6 adjacent to the pocket 6 in which the projection 20 is formed, a cage outer circumferential surface 25 without projections is formed.

According to the second embodiment, since the convex portion 20 is formed on the outer diameter surface of the retainer 4 on the counterbore side, as shown in FIG. Large cross-sectional dimensions in the direction and radial direction. Therefore, the weight of the retainer 4 increases, and the rigidity of the retainer 4 also increases. As a result, deformation of the retainer 4 can be suppressed.

Further, the radial clearance δb between the straight surface portion 24 and the inner diameter surface of the outer ring 2 is set to be larger than the radial clearance δa between the guided surface 4a and the inner diameter surface of the outer ring 2, and not more than twice the radial clearance δa. It is Furthermore, the axial length A1 of the guided surface portion 4a is set to be the same as the axial length A2 of the straight surface portion 24, and the guide-side volume V1 of the retainer is set to be the same as the counterbore-side volume V2. . As a result, the guide side and the counterbore side of the retainer are balanced, so that it is possible to suppress wobbling and inclination of the retainer.

As shown in FIG. 7, a plurality of protrusions 20 are provided at intervals in the circumferential direction. As a result, it is possible to suppress an increase in the contact area between the outer ring 2 and the retainer 4 on the counterbore side. As a result, it is possible to suppress the heat generation of the bearing and the accumulation of heat in the bearing space.

As described above, preferred embodiments have been described with reference to the drawings, but the present invention is not limited to the above embodiments, and various additions and modifications can be made without departing from the scope of the present invention. or can be deleted. For example, in the above-described embodiments, an outer ring guide type retainer has been described, but the present invention can also be applied to a rolling element guide type retainer. Accordingly, such are also included within the scope of this invention.

The application example of the present invention can also be applied to a retainer that does not have a relief surface 7a. Application examples include aspects 1 to 5 below.

[Aspect 1]
A retainer according to aspect 1 of the present invention is an angular contact ball bearing having a guide surface for guiding the retainer on one side in the axial direction of the bearing sandwiching the raceway surface of the inner diameter surface of the outer ring, and having a counterbore on the other side. a retainer,
The retainer is cylindrical,
a plurality of pockets formed axially in the middle of the retainer for retaining the rolling elements of the bearing;
a guided surface portion guided by the guide surface of the outer ring on the outer peripheral surface of the retainer;
a projection formed on the counterbore-side outer diameter surface of the retainer and protruding radially outward toward the outer ring;
A straight surface portion is formed on the outer diameter surface of the convex portion and supports guidance with the inner diameter surface of the outer ring.

In conventional bearings, lean lubrication and intrusion of foreign matter may cause cage wobbling and inclination. Such contacting and tilting may cause deformation of the retainer. According to this configuration, since the convex portion is provided, the weight of the retainer is increased, and the rigidity of the retainer is also increased. As a result, deformation of the retainer can be suppressed.

[Aspect 2]
In aspect 1, the radial clearance between the straight surface portion and the inner diameter surface of the outer ring is larger than the radial clearance between the guided surface and the inner diameter surface of the outer ring, and the guided surface and the inner diameter surface of the outer ring may be set to twice or less of the radial gap between. According to this configuration, since the guide side and the counterbore side of the retainer are balanced, it is possible to suppress wobbling and inclination of the retainer.

[Aspect 3]
In mode 1 or 2, even if the axial length of the guided surface portion is set to be the same as the axial length of the straight surface portion, and the volume on the guiding side of the retainer is set to be the same as the volume on the counterbore side. good. According to this configuration, since the guide side and the counterbore side of the retainer are balanced, it is possible to suppress wobbling and inclination of the retainer.

[Aspect 4]
In any one of modes 1 to 3, a plurality of the protrusions may be provided spaced apart in the circumferential direction. According to this configuration, it is possible to suppress an increase in the contact area between the outer ring and the retainer on the counterbore side. As a result, it is possible to suppress the heat generation of the bearing and the accumulation of heat in the bearing space.

[Aspect 5]
The angular contact ball bearing of aspect 5 is an angular contact ball bearing having a guide surface for guiding a retainer on one side in the axial direction of the bearing sandwiching the raceway surface of the inner diameter surface of the outer ring and a counterbore on the other side, A retainer according to any one of modes 1 to 4 is provided. According to the angular contact ball bearing having this configuration, the same functions and effects as those of the angular contact ball bearing cages of modes 1 to 4 can be obtained.

1 Inner ring 1a Raceway surface 2 Outer ring 2a Raceway surface 2b Guide surface 3 Rolling element 4 Cage 4a Guided surface 5 Counterbore 6 Pocket 7 Weight increase portion 7a Relief surface 8 Weight balance portion 10 Outer ring spacer 11 Nozzle 20 Convex portion 24 Straight Surface portion A1 Axial length of guided surface portion A2 Axial length of straight surface portion V1 Guide side volume of cage V2 Cage counterbore side volume δa Radial clearance δb between guided surface and inner diameter surface of outer ring Radial clearance between the straight surface portion and the inner diameter surface of the outer ring

Claims (7)

An outer ring guide retainer for an angular contact ball bearing having a guide surface for guiding the retainer on one side in the axial direction of the bearing sandwiching the raceway surface of the inner diameter surface of the outer ring, and a counterbore on the other side,
The retainer is cylindrical,
a plurality of pockets formed axially in the middle of the retainer for retaining the rolling elements of the bearing;
The pocket is formed on one side in the axial direction of the pocket, has the smallest radial clearance between the outer peripheral surface of the retainer and the guide surface of the outer ring, and is guided by the guide surface of the outer ring and is continuous on the entire peripheral surface. a guided surface portion;
a weight increasing portion extending from the guided surface portion to one side in the axial direction;
a relief surface formed on the outer peripheral surface of the weight increasing portion and spaced further from the inner diameter surface of the outer ring than the guided surface portion;
An angular contact ball bearing retainer in which the axial dimension of the weight-increasing portion is larger than the axial dimension of the guided surface portion . 2. The angular contact ball bearing retainer according to claim 1, wherein said relief surface is tapered continuously along the entire peripheral surface away from the inner diameter surface of said outer ring toward the retainer width surface. A retainer for an angular contact ball bearing having a guide surface for guiding the retainer on one side in the axial direction of the bearing sandwiching the raceway surface on the inner diameter surface of the outer ring and a counterbore on the other side,
The retainer is cylindrical,
a plurality of pockets formed axially in the middle of the retainer for retaining the rolling elements of the bearing;
a guided surface portion guided by the guide surface of the outer ring on the outer peripheral surface of the retainer;
a weight increasing portion extending outward in the axial direction from the guided surface portion;
a relief surface formed on the outer peripheral surface of the weight increasing portion and spaced further from the inner diameter surface of the outer ring than the guided surface portion;
An angular contact ball bearing retainer in which the inner peripheral surface of the weight-increasing portion protrudes radially inward from the inner peripheral surface of the portion in the width direction of the retainer that constitutes the guided surface portion. A retainer for an angular contact ball bearing having a guide surface for guiding the retainer on one side in the axial direction of the bearing sandwiching the raceway surface on the inner diameter surface of the outer ring and a counterbore on the other side,
The retainer is cylindrical,
a plurality of pockets formed axially in the middle of the retainer for retaining the rolling elements of the bearing;
a guided surface portion guided by the guide surface of the outer ring on the outer peripheral surface of the retainer;
a weight increasing portion extending outward in the axial direction from the guided surface portion;
a relief surface formed on the outer peripheral surface of the weight increasing portion and spaced further from the inner diameter surface of the outer ring than the guided surface portion;
An angular contact ball bearing retainer in which an inner peripheral surface of the retainer on the counterbore side protrudes radially outward from the pocket forming portion toward the outside in the axial direction. A retainer for an angular contact ball bearing having a guide surface for guiding the retainer on one side in the axial direction of the bearing sandwiching the raceway surface on the inner diameter surface of the outer ring and a counterbore on the other side,
The retainer is cylindrical,
a plurality of pockets formed axially in the middle of the retainer for retaining the rolling elements of the bearing;
a guided surface portion guided by the guide surface of the outer ring on the outer peripheral surface of the retainer;
a weight increasing portion extending outward in the axial direction from the guided surface portion;
a relief surface formed on the outer peripheral surface of the weight increasing portion and spaced further from the inner diameter surface of the outer ring than the guided surface portion;
A protrusion projecting radially outward toward the outer ring is formed on the outer diameter surface of the retainer on the counterbore side,
A straight surface portion is formed on the outer diameter surface of the convex portion to support guidance with the inner diameter surface of the outer ring,
A radial clearance between the straight surface portion and the inner diameter surface of the outer ring is larger than a radial clearance between the guided surface portion and the inner diameter surface of the outer ring, and a radial clearance between the guided surface portion and the inner diameter surface of the outer ring. Angular contact ball bearing retainer set to less than twice the clearance. A retainer for an angular contact ball bearing having a guide surface for guiding the retainer on one side in the axial direction of the bearing sandwiching the raceway surface on the inner diameter surface of the outer ring and a counterbore on the other side,
The retainer is cylindrical,
a plurality of pockets formed axially in the middle of the retainer for retaining the rolling elements of the bearing;
a guided surface portion guided by the guide surface of the outer ring on the outer peripheral surface of the retainer;
a weight increasing portion extending outward in the axial direction from the guided surface portion;
a relief surface formed on the outer peripheral surface of the weight increasing portion and spaced further from the inner diameter surface of the outer ring than the guided surface portion;
A protrusion projecting radially outward toward the outer ring is formed on the outer diameter surface of the retainer on the counterbore side,
A straight surface portion is formed on the outer diameter surface of the convex portion to support guidance with the inner diameter surface of the outer ring,
An angular contact ball bearing retainer in which the axial length of the guided surface portion is set to be the same as the axial length of the straight surface portion, and the volume on the guide side of the retainer is set to be the same as the volume on the counterbore side. An angular contact ball bearing having a guide surface for guiding a retainer on one side in the axial direction of the bearing sandwiching the raceway surface on the inner diameter surface of the outer ring, and a counterbore on the other side,
An angular contact ball bearing comprising the retainer according to any one of claims 1 to 6 .

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