WO2018199285A1

WO2018199285A1 - Angular ball bearing retainer and angular ball bearing

Info

Publication number: WO2018199285A1
Application number: PCT/JP2018/017177
Authority: WO
Inventors: 翔平橋爪
Original assignee: Ntn株式会社
Priority date: 2017-04-28
Filing date: 2018-04-27
Publication date: 2018-11-01
Also published as: JPWO2018199285A1; DE112018002227T5; JP7142629B2

Abstract

This angular ball bearing retainer sandwiches a raceway surface (2a) with respect to an inner diameter surface of an outer ring (2), and has a retainer guide surface (2b) on one side in the axial direction and a counter bore (5) on the other side. A retainer (4) is a cylindrical shape having, in the middle in the axial direction, a plurality of pockets (6) for retaining rolling bodies (3). A weight increasing part (7) is provided extending further outward in the axial direction than a surface section to be guided (4a) which is to be guided by the guide surface (2b) of the outer ring (2) in the outer circumferential surface of the retainer (4). The outer circumferential surface of this weight increasing unit (7) constitutes a relief surface (7a) further separated from the inner diameter surface of the outer ring (2) than the surface section to be guided (4a).

Description

Angular contact ball bearing cage and angular contact ball bearing

Related applications

This application claims the priority of Japanese Patent Application No. 2017-089173 filed on Apr. 28, 2017, which is incorporated herein by reference in its entirety.

The present invention relates to an angular contact ball shaft used for a machine tool spindle bearing and other equipment, and a retainer thereof.

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

JP 2011-132999 A

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

An object of the present invention is to provide an angular contact ball bearing retainer and an angular contact ball bearing that are capable of suppressing high-speed performance, suppressing intense swinging of the retainer, and reducing abnormal noise.

The angular ball bearing cage of the present invention has a guide surface for guiding the cage on one side in the axial direction of the bearing sandwiching the raceway surface on the inner diameter surface of the outer ring, and the angular ball bearing having a counter bore on the other side. The cage is cylindrical, a plurality of pockets formed in the middle of the cage in the axial direction to hold the rolling elements of the bearing, and the outer ring on the outer circumferential surface of the cage. A guided surface portion guided by the guide surface, a weight increasing portion extending outward in the axial direction from the guided surface portion, and an inner diameter surface of the outer ring formed on the outer peripheral surface of the weight increasing portion rather than the guided surface portion And a relief surface spaced from the

According to this configuration, the weight of the entire cage increases by having the weight increasing portion extending outward in the axial direction from the guided surface portion. Therefore, intense swinging of the cage caused by a large frictional force generated by contact between the outer ring inner diameter surface and the cage outer diameter surface can be suppressed, and abnormal noise can be prevented. Since the outer ring counterbore side portion of the cage is not guided by any of the inner and outer rings, the effect of suppressing swirling cannot be expected even if the weight of the counterbore side portion is increased. In the said structure, since the weight by the side of a guide surface is increased, the effect which suppresses a whirling is realizable.

Further, since the outer diameter surface of the weight increasing portion of the cage constitutes a relief surface that is separated from the inner diameter surface of the outer ring than the guided surface portion, the width (axial dimension) of the cage is increased. Thereby, the fluidity | liquidity of lubricating oil improves and it can prevent the heat_generation | fever of a bearing. As a result, higher speed operation is possible. In addition, there is no change in the configuration relating to the guide between the outer ring inner diameter surface and the cage outer diameter surface, and there is no dimensional change in the pocket portion of the cage, so that the cage having the above configuration can be easily applied to an existing bearing.

In the angular ball bearing cage of the present invention, the relief surface may be tapered so as to be separated from the inner diameter surface of the outer ring toward the cage 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 cage width surface. When the relief surface is tapered, it is possible to increase the weight of the cage by increasing the weight increasing portion while ensuring a good flow of the lubricating oil. Further, unlike the case of the stepped shape, the tapered shape is less likely to cause stress concentration even if the cage swings, and the cage strength is also excellent.

In the angular ball bearing cage of the present invention, the inner circumferential surface of the weight increasing portion may bulge to the inner diameter side of the inner circumferential surface of the cage width direction portion constituting 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. Thereby, since the weight of a cage | basket can be further increased, the effect of the whirling suppression by the increase in weight improves.

In the angular ball bearing cage of the present invention, the inner peripheral surface of the cage on the counter bore side may bulge toward the inner diameter side from the pocket forming portion toward the outer side in the axial direction. Here, the “pocket formation portion” refers to a portion in the axial direction range where the pocket in the cage is formed. According to this configuration, even on the side of the cage that is not guided by the inner diameter surface of the outer ring, the weight increases due to the increase in dimensions. Thereby, the weight balance with the side to be guided is improved, and touching can be more stably suppressed. The axial dimension of the portion on the width surface side of the pocket on the counterbore side may be larger than the dimension required for strength design. Thereby, a weight increases further and a weight balance can be improved further.

In the angular ball bearing cage of the present invention, a convex portion protruding radially outward toward the outer ring is formed on the outer diameter surface on the counter bore side of the cage, and the outer diameter surface of the convex portion A straight surface portion that supports guidance with the inner diameter surface of the outer ring may be formed.

In the conventional bearing shown in FIG. 9, the cage may be touched or tilted due to lean lubrication or entry of foreign matter. If such contact and tilt occur, the cage may be deformed. According to this configuration, since the convex portion is provided, the weight of the cage increases and the rigidity of the cage also increases. As a result, deformation of the cage can be suppressed.

When the straight surface portion is provided, a radial gap between the straight surface portion and the inner diameter surface of the outer ring is larger than a radial gap between the guided surface and the inner diameter surface of the outer ring, and the guided surface and the You may set to 2 times or less of the radial direction clearance with the internal diameter surface of an outer ring | wheel. According to this configuration, since the balance is achieved between the guide side and the counterbore side of the cage, it is possible to suppress touching and tilting of the cage.

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 guide side volume of the cage is set to be the same as the counter bore side volume. May be. According to this configuration, since the balance is achieved between the guide side and the counterbore side of the cage, it is possible to suppress touching and tilting of the cage.

When the convex portion is provided, a plurality of the convex portions may be provided apart from each other in the circumferential direction. According to this configuration, an increase in the contact area between the outer ring and the cage can be suppressed on the counter bore side. As a result, it is possible to suppress heat generation in the bearing and heat accumulation in the bearing space.

The angular contact ball bearing of the present invention is an angular contact ball bearing having a guide surface for guiding the cage on one side in the axial direction of the bearing sandwiching the raceway surface on the inner diameter surface of the outer ring, and having a counter bore on the other side, The cage of the present invention is provided. According to the angular ball bearing of this configuration, the same operation and effect as the angular ball bearing cage of the present invention can be obtained.

Any combination of at least two configurations disclosed in the claims and / or the specification and / or the drawings is included in the present invention. In particular, any combination of two or more of each claim in the claims 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 present invention. The scope of the invention is defined by the appended claims. In the accompanying drawings, the same part numbers in a plurality of drawings indicate the same or corresponding parts.
It is a fragmentary sectional view of the angular ball bearing concerning a 1st embodiment of this invention. It is explanatory drawing which compares and shows the angular ball bearing and the conventional angular ball bearing. It is sectional drawing which shows the angular ball bearing and the outer ring spacer with a nozzle. It is an outer ring both shoulder guide angular contact ball bearing. It is a fragmentary sectional view of the angular ball bearing which concerns on 2nd Embodiment of this invention. It is explanatory drawing which compares and shows the angular ball bearing and the conventional angular ball bearing. It is the front view which looked at the retainer of the angular ball bearing from the Kaunder bore side. It is a perspective view which shows the holder. It is sectional drawing of a prior art example.

A first embodiment of the present invention will be described with reference to FIGS. In this angular 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 cage 4. The rolling element 3 is, for example, a ball. The raceway surface 1a of the inner ring 1 and the raceway surface 2a of the outer ring 2 are formed so that a contact angle θ is generated. The inner ring surface of the outer ring 2 is formed with a guide surface 2b for guiding the cage 4 on one side (left side in FIG. 1) in the axial direction C of the bearing across the raceway surface 2a, and the other side (in FIG. 1). On the right side, a counterbore 5 is formed.

The cage 4 is cylindrical. The axial center of the cage 4 is parallel to the axial direction C of the bearing. A plurality of pockets 6 for holding the rolling elements 3 are formed in an intermediate portion in the axial direction C of the cage 4. The pockets 6 are arranged at regular intervals in the circumferential direction of the cage 4. The pocket 6 has, for example, a cylindrical surface extending in the radial direction. The cage 4 is a cut-out product of a resin such as a laminated phenol resin. However, the material of the cage 4 is not limited to this, and may be made of metal or titanium alloy. In the following description, the axial direction C may be referred to as the width direction of the cage 4.

In this embodiment, a weight increasing portion 7 is provided on the guide surface 2 b side of the outer ring 2 in the cage 4. Further, a weight balance portion 8 is provided on the counter bore 5 side of the outer ring 2 in the cage 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 cage 4. In FIG. 1, a cage width direction portion formed by the guided surface portion 4a is indicated by a range a. The weight increasing portion 7 is a portion extending outward in the width direction (axial direction C) from the guided surface portion 4a. The outer peripheral surface of the weight increasing portion 7 constitutes a relief surface 7a that is further away from the inner diameter surface of the outer ring 2 than the guided surface portion 4a. The shape of the relief surface 7 a is a taper shape that is away from the inner diameter surface of the outer ring 2 toward the width surface 4 b (left end surface in FIG. 1) of the cage 4.

Further, the weight increasing portion 7 has a cross-sectional shape that swells toward the inner diameter side of the cage width direction portion a. In other words, the inner peripheral surface of the weight increasing portion 7 bulges toward the inner diameter side of the inner peripheral surface of the cage width direction portion a. In this embodiment, the inner peripheral surface of the weight increasing portion 7 gradually bulges toward the inner diameter side from the cage width direction portion a toward the width surface 4b of the cage 4 (the left end surface in FIG. 1). Thereby, the cross-sectional dimension is larger in the width direction and the radial direction than the cage 4A of FIG. For comparison, both the

retainers

4 and 4A are shown in a superimposed manner in FIG. The cross-sectional shape of the inner peripheral surface of the weight increasing portion 7 is a tapered shape that gradually decreases in diameter toward the width surface 4 b of the cage 4.

The weight balance portion 8 is a portion on the width surface 4c side (right side in FIG. 1) from the pocket 6 in the cage 4, and is a portion in which the width direction dimension is larger than the dimension necessary for strength design. Specifically, the weight balance portion 8 is a portion of the retainer 4 on the counter bore 5 side of the outer ring 2 and on the side of the width surface 4 c (right end surface in FIG. 1) from the pocket 6. The weight balance portion 8 bulges toward the inner diameter side from the pocket forming portion of the cage 4 toward the outer side in the width direction (right side in FIG. 1). Here, the “pocket formation portion” refers to a portion in the range in the width direction (axial direction C) where the pocket 6 in the cage 4 is formed.

The inner diameter surface of the weight balance portion 8 is inclined toward the inner diameter side from the pocket forming portion toward the width surface 4c (the end surface on the right side in FIG. 1), and is most at the small diameter portion 8a at the intermediate portion in the cage width direction (axial direction C). It has a small diameter and is inclined toward the outer diameter side 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 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 outer ring spacer 10 with the nozzle is inserted between the inner ring 1 and the cage 4 on the guide surface 2b side of the outer ring 2, and air oil is discharged from the nozzle hole 11a. The

According to this configuration, the cage 4 has the weight increasing portion 7 extending outward in the width direction (left side in FIG. 1) from the guided surface portion 4a, so that the weight of the entire cage increases. Therefore, intense swinging of the cage 4 due to 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 can be suppressed, and abnormal noise can be prevented. The portion of the retainer 4 on the counter bore 5 side (right side in FIG. 1) of the outer ring 2 is not guided to either the inner or

outer ring

1 or 2. Therefore, even if the weight of the counterbore portion is increased, the effect of suppressing the swing cannot be expected. However, in the above configuration, the weight on the guide surface 2b side (the left side in FIG. 1) is increased. The effect which suppresses is acquired.

Further, the outer diameter surface of the weight increasing portion 7 of the cage 4 is a relief surface 7a that is separated from the inner diameter surface of the outer ring 2 rather than the guided surface portion 4a. Thereby, the dimension of the cage in the width direction is increased, the fluidity of the lubricating oil is improved, and heat generation of the bearing can be prevented. Therefore, higher speed operation of the bearing becomes possible. In addition, since there is no change in the configuration for guiding the cage 4 by the guide surface 2b of the outer ring 2 and there is no change in the dimensions of the pocket 6 in which the pocket 6 is formed, the cage 4 of this embodiment is used as an existing bearing. Easy to apply to.

In addition, the width direction dimension (axial direction C) of the weight increase part 7 should just be the width direction dimension which does not protrude from the width surface of the inner and outer ring |

wheels

1,2. Specifically, the

width direction

4b, 4c of the cage 4 may be a width direction size close to the width surface of the inner and

outer rings

1, 2, and the width direction size is small within a range that can contribute to an increase in the overall weight of the cage 4. It is good.

Since the relief surface 7a of the weight increasing portion 7 is tapered, the weight increasing portion 7 can be enlarged and the weight of the cage 4 can be increased while ensuring a good flow of the lubricating oil. The relief surface 7a of the weight increasing portion 7 may be stepped away from the inner surface of the outer ring in a stepwise manner than the guided surface portion 4a. However, if the tapered surface is tapered, the cage 4 swings more than the stepped shape. Even if it exists, stress concentration hardly occurs and the cage strength is also excellent.

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

Further, the cage 4 is provided with a weight balance portion 8, and the inner peripheral surface of the cage 4 is directed from the pocket forming portion to the outside in the axial direction C (right side in FIG. 1) on the non-guided side of the cage 4. It bulges to the inner diameter side. For this reason, even on the non-guided side of the cage 4, the weight increases due to an increase in cross-sectional dimensions, and the weight balance with the guided side is improved. As a result, the effect of suppressing touching is further improved.

Although the above-described embodiment is an outer ring one-shoulder guide method, it can also be applied to an outer ring both-shoulder plan method as shown in FIG. 4 as a reference proposal example. In this case, the weight increasing portions 7 may be provided on both sides of the cage 4 in the axial direction, 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 present invention will be described with reference to FIGS. In the second embodiment, the shape of the cage 4 on the side of the counter bore is different from that of the first embodiment. Parts having the same configurations as those of the first embodiment are denoted by the same reference numerals and description thereof is omitted.

In the second embodiment, a convex portion 20 protruding outward in the radial direction toward the outer ring 2 is formed on the outer diameter surface of the cage 4 on the counter bore 5 side (right side in FIG. 5). The 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 cage 4 toward the outer side in the axial direction C (right side in FIG. 5) so as to approach the inner surface of the outer ring 2. That is, the taper surface portion 22 is inclined radially outward toward the outer side in the axial direction C (width surface 4c). The tapered surface portion 22 constitutes a relief surface with the inner diameter surface of the outer ring 2 on the counter bore side.

The straight surface portion 24 is continuous with the tapered surface portion 22 and extends toward the outside in the axial direction C (the right side in FIG. 5). That is, the straight surface portion 24 is substantially parallel to the axial direction C and extends parallel to the inner diameter surface of the outer ring 2 on the counter bore side. The straight surface portion 24 is a portion having the smallest radial clearance with the inner diameter surface of the outer ring 2 on the counter bore 5 side. The straight surface portion 24 supports the guide between the cage 4 and the inner diameter surface.

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

The radial gap between the guided surface 4a and the inner diameter surface of the outer ring 2 is δa, and the radial gap between the straight surface portion 24 and the inner diameter surface of the outer ring 2 on the counter bore 5 side is δb. In this case, δb is preferably larger than δa and not more than twice δa (δa <δb ≦ 2δa).

The axial length of the guided surface portion 4a on the counter-bore side (left side in FIG. 5) is A1, and the axial length of the straight surface portion 24 on the counter bore side (right side in FIG. 5) is A2. In this case, A1 and A2 are preferably the same (A1 = A2). Further, the volume on the counter-bore side (guide side) in the cage 4 is V1, and the volume on the counter-bore side in the cage 4 is V2. In this case, V1 and V2 are preferably the same (V1 = V2).

As shown in FIG. 7, the convex part 20 is provided with two or more spaced apart in the circumferential direction. In other words, a cage outer peripheral surface 25 without a convex portion is formed between adjacent convex portions 20 on the outer peripheral surface of the cage 4, and the convex portions 20 and the cage outer peripheral surface 25 are alternately arranged in the circumferential direction. Has been.

Specifically, as shown in FIG. 8, the convex portions 20 are formed every other pocket 6. That is, the convex part 20 is formed in the area | region of the two pockets 6 adjacent to the pocket 6 in which the holder outer peripheral surface 25 without a convex part is formed. Similarly, a cage outer peripheral surface 25 without a convex portion is formed in an area of two pockets 6 adjacent to the pocket 6 where the convex portion 20 is formed.

According to 2nd Embodiment, since the convex part 20 is formed in the outer diameter surface by the side of the counterbore in the holder | retainer 4, as shown in FIG. 6, the width | variety of the holder | retainer 4 rather than the conventional holder | retainer 4A. The cross-sectional dimension is large in the direction and radial direction. Therefore, the weight of the cage 4 increases and the rigidity of the cage 4 also increases. As a result, it is possible to suppress the cage 4 from being deformed.

Further, the radial gap 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 gap δa between the guided surface 4a and the inner diameter surface of the outer ring 2 and not more than twice the radial gap δa. Has been. 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 cage is set to be the same as the counterbore side volume V2. . Thereby, since the balance is achieved on the guide side and the counterbore side of the cage, the contact and inclination of the cage can be suppressed.

As shown in FIG. 7, the convex part 20 is provided with two or more spaced apart in the circumferential direction. Thereby, it can suppress that the contact area of the outer ring | wheel 2 and the holder | retainer 4 becomes large in the counterbore side. As a result, it is possible to suppress heat generation in the bearing and heat accumulation in the bearing space.

As described above, the preferred embodiments have been described with reference to the drawings. However, the present invention is not limited to the above embodiments, and various additions and modifications can be made without departing from the gist of the present invention. Or it can be deleted. For example, in the above-described embodiment, the outer ring guide type cage has been described, but the present invention can also be applied to a rolling element guide type cage. Therefore, such a thing is also included in the scope of the present invention.

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

[Aspect 1]
A cage according to aspect 1 of the present invention is an angular contact ball bearing having a guide surface for guiding the cage 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 counter bore on the other side. A cage,
The cage is cylindrical;
A plurality of pockets formed in the middle of the cage in the axial direction and holding 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 cage;
A convex portion formed on the outer diameter surface on the counter bore side of the cage and projecting radially outward toward the outer ring;
A straight surface portion that is formed on the outer diameter surface of the convex portion and supports the guide with the inner diameter surface of the outer ring.

In conventional bearings, contact and tilt of the cage may occur due to dilute lubrication or foreign material intrusion. If such contact and tilt occur, the cage may be deformed. According to this configuration, since the convex portion is provided, the weight of the cage increases and the rigidity of the cage also increases. As a result, deformation of the cage can be suppressed.

[Aspect 2]
In aspect 1, 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 and the inner diameter surface of the outer ring, and the inner diameter surface of the guided surface and the outer ring. And may be set to be twice or less of the radial gap between. According to this configuration, since the balance is achieved between the guide side and the counterbore side of the cage, it is possible to suppress touching and tilting of the cage.

[Aspect 3]
In

aspect

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, the guide side volume of the cage is set to be the same as the counter bore side volume. Good. According to this configuration, since the balance is achieved between the guide side and the counterbore side of the cage, it is possible to suppress touching and tilting of the cage.

[Aspect 4]
In any one of aspects 1 to 3, a plurality of the convex portions may be provided apart from each other in the circumferential direction. According to this configuration, an increase in the contact area between the outer ring and the cage can be suppressed on the counter bore side. As a result, it is possible to suppress heat generation in the bearing and heat accumulation in the bearing space.

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

DESCRIPTION OF SYMBOLS 1 Inner ring 1a Raceway surface 2 Outer ring

2a Raceway surface

2b Guide surface 3 Rolling body 4 Cage 4a Guided surface 5 Counter bore 6 Pocket 7 Weight increase part 7a Relief surface 8 Weight balance part 10 Outer ring spacer 11 Nozzle 20 Protrusion part 24 Straight Surface A1 Axial length A2 of guided surface A2 Axial length V1 of straight surface V1 Volume on guide side of cage C2 Volume on counterbore side of cage δa Radial clearance δb between guided surface and inner diameter surface of outer ring Radial clearance between straight surface and inner ring surface of outer ring

Claims

A cage of an angular ball bearing having a guide surface for guiding the cage on one side in the axial direction of the bearing sandwiching the raceway surface on the inner diameter surface of the outer ring, and having a counter bore on the other side,
The cage is cylindrical;
A plurality of pockets formed in the middle of the cage in the axial direction and holding 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 cage;
A weight increasing portion extending outward in the axial direction from the guided surface portion;
An angular ball bearing retainer provided with an escape surface formed on an outer peripheral surface of the weight increasing portion and spaced from an inner diameter surface of the outer ring than the guided surface portion.
2. The angular ball bearing cage according to claim 1, wherein the relief surface is a tapered shape that is separated from the inner diameter surface of the outer ring toward the cage width surface.
The angular ball bearing retainer according to claim 1 or 2, wherein an inner peripheral surface of the weight increasing portion bulges toward an inner diameter side from an inner peripheral surface of a cage width direction portion constituting the guided surface portion. Ball bearing cage.
The angular ball bearing retainer according to any one of claims 1 to 3, wherein an inner peripheral surface of the retainer on the counter bore side swells toward an inner diameter side from a pocket forming portion toward an outer side in the axial direction. Angular contact ball bearing cage.
The angular ball bearing retainer according to any one of claims 1 to 4, wherein a convex portion that protrudes radially outward toward the outer ring is formed on the outer diameter surface of the retainer on the counter bore side.
An angular ball bearing cage in which a straight surface portion that supports guidance with the inner diameter surface of the outer ring is formed on the outer diameter surface of the convex portion.
The angular ball bearing retainer according to claim 5, wherein a radial clearance between the straight surface portion and an inner diameter surface of the outer ring is larger than a radial clearance between the guided surface and the inner diameter surface of the outer ring, and An angular ball bearing cage that is set to be not more than twice the radial clearance between the guided surface and the inner diameter surface of the outer ring.
The angular ball bearing retainer according to claim 5 or 6, wherein an axial length of the guided surface portion is set to be the same as an axial length of the straight surface portion, and a guide-side volume of the retainer is set on a counter bore side. Angular contact ball bearing cage set to the same volume.
The angular ball bearing retainer according to any one of claims 5 to 7, wherein a plurality of the convex portions are provided apart from each other in the circumferential direction.
An angular ball bearing having a guide surface for guiding a cage on one side in the axial direction of the bearing sandwiching the raceway surface on the inner diameter surface of the outer ring, and having a counter bore on the other side,
An angular ball bearing comprising the cage according to any one of claims 1 to 8.