JP2010164122A - Angular ball bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To enhance the flowability of grease in an angular ball bearing wherein a plurality of balls intervening between an inner race and an outer race are held by a cage, thereby stably securing the lubricity of the bearing. <P>SOLUTION: The cage 15 is guided by the outer rage 11, and grease storage grooves 19, 20 leading to a raceway groove 13 are formed axially outside of the raceway groove 13 in such a way that the surface of contact between the raceway 13 and a ball 14 is secured on an inside diameter portion of the outer race 11. A grease guide surface titled axially inward and radially outward is formed on a groove wall of the grease storage groove 19. During operation, grease collecting in the grease storage groove 19 is pressed against the grease guide surface by air pressure produced by the rotation of the cage 15 due to the rolling movement of the ball 14. Thus, the grease is moved along the grease guide surface to the raceway groove 13 in the outer race 11 and stably supplied to the raceway groove 13 to stably secure the lubricity of the bearing. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an angular ball bearing that supports a rotating shaft of various machine devices such as a spindle of various machine tools, a spindle for a turbine such as a compressor or a pump, and an outer ring for an angular ball bearing applied thereto.

  In recent years, rotating shafts of various mechanical devices are often rotated at high speeds in order to improve processing efficiency and operating efficiency, and the angular ball bearings that support the rotating shafts have high reliability such as no seizure during high-speed rotation. Sex is required. Therefore, high lubrication performance is indispensable for improving the reliability of the angular ball bearing. In addition, consideration for the environment is demanded, and during operation, there is a tendency to employ grease lubrication in which grease is filled in the bearing instead of oil lubrication that can supply lubricating oil inside the bearing.

  As an angular contact ball bearing by grease lubrication, for example, as shown in FIG. 10, a plurality of balls 34 interposed between an inner ring 30 and an outer ring 31 are held by a cage 35, and an outer ring raceway groove is formed in an inner diameter portion of the outer ring 31. A grease storage groove 36 connected to the outer ring raceway groove 33 is formed on both axial sides of the outer ring raceway groove 33, and seals 32 are provided at both ends between the inner ring 30 and the outer ring 31 (Patent Document 1). reference).

JP 2002-122149 A

  In this angular ball bearing, since the grease storage grooves 36 are formed on both sides of the raceway groove 33 of the outer ring 31, the grease can be stored in the grease storage grooves 36. Therefore, the amount of grease that can be filled in the bearing space between the inner ring 30 and the outer ring 31 is increased, and lubricity is improved as compared with the case without the grease storage groove.

  However, in the angular ball bearing described in Patent Document 1, the bottom surface 37 of the grease storage groove 36 is formed on a cylindrical surface having the bearing central axis as a cylindrical axis (see FIG. 11). For this reason, during operation, the grease accumulated in the grease reservoir groove 36 is pressed against the bottom surface 37 by the wind pressure generated by the rotation of the retainer 35 accompanying the rolling of the balls 34 and tends to stay. As a result, the fluidity of the grease to the raceway groove 33 of the outer ring 31 is lowered, it becomes difficult to supply the grease, the lubricity is lowered, and the life cannot be extended.

  Accordingly, an object of the present invention is to improve the fluidity of grease and stably ensure the lubricity of the bearing.

  In order to solve the above-mentioned problems, an angular contact ball bearing according to the present invention is an angular contact ball bearing in which a plurality of balls interposed between an inner ring and an outer ring are held by a cage, wherein the cage is constituted by the outer ring. A grease storage groove guided and connected to the outer ring raceway groove on the inner diameter portion of the outer ring is formed on the outer side in the axial direction of the raceway groove, and axially inward and radially outward of the groove wall of the grease storage groove. In this configuration, a grease guide surface that is inclined in the direction is formed.

  In this way, during operation, the grease accumulated in the grease reservoir groove is pressed against the grease guide surface by the wind pressure generated by the rotation of the cage accompanying the rolling of the balls. Since the grease guide surface is inclined, the pressed grease easily moves (flows) along the inner surface of the grease storage groove to the race groove of the outer ring, and is stably supplied to the race groove. It is possible to stably secure the lubricity of the bearing by the stably supplied grease.

  The said structure WHEREIN: The said grease guide surface can be set as the structure formed so that it might continue with the inner surface of the said track groove. In this case, the grease pressed against the grease guide surface by the wind pressure generated by the rotation of the cage moves directly to the raceway groove. For this reason, grease is stably supplied to the raceway groove more effectively.

  In addition, a configuration in which the grease guide surface includes a shading portion formed outward in the axial direction and outward in the radial direction can be employed. In this way, it is possible to increase the amount of grease that can be stored in the grease storage groove while ensuring the fluidity of the grease by the grease guide surface.

  When adopting a configuration with a relief part on the grease guide surface, the position and depth of the relief part are appropriately set according to the specifications of the angular ball bearing, and considering the workability for the outer ring and the strength of the outer ring, for example, The loose portion is located on the radially inner side of the maximum diameter portion of the inner surface of the raceway groove and from the axial central portion of the shoulder portion formed on the axially outer side of the grease storage groove of the inner diameter portion of the outer ring. May also be positioned on the inner side in the axial direction.

  Further, in the grease storage groove, when a spiral groove connected to the raceway groove of the outer ring is formed on the grease guide surface, a channel for guiding grease to the raceway groove of the outer ring is formed by the spiral groove. A sufficient amount of grease can be secured.

  When the groove wall on the outer end side in the axial direction of the grease storage groove has a tapered surface that extends outward in the axial direction and continues to the grease guide surface, the groove wall on the outer end side in the axial direction of the grease storage groove The grease adhering to the taper surface moves to the grease guide surface by the wind pressure generated by the rotation of the cage accompanying the rolling. As described above, the grease adhering to the entire inner surface of the groove wall of the grease storage groove can be moved to the race groove of the outer ring without staying.

  When the grease storage groove is formed on both sides of the raceway groove, when the grease guide surface is formed on at least one of the two grease storage grooves, the grease storage groove is formed only on one side. In comparison, the amount of grease stored in the raceway groove of the outer ring increases. The increased grease is pressed against the grease guide surface by the wind pressure generated by the rotation of the cage described above, and easily moves (flows) along the inner surface of the grease storage groove to the race groove of the outer ring.

In the angular ball bearing according to the present invention, when an axial load is generated on the inner ring and the outer ring toward the front side, for example, the ball on the inner diameter part front side of the outer ring is prevented in order to prevent the ball from running into the grease storage groove. It is possible to employ a configuration in which the grease storage groove is disposed radially inward from the radial position of the contact point with the ball in the raceway groove of the outer ring.
Here, the contact point means a nominal contact point defined in JIS B0104, and is a point on the inner surface of the raceway groove of the outer ring that is considered to be in contact with the ball when the bearing component is in a normal relative position.

  In general, an angular contact ball bearing that supports a rotating shaft of various machines is an outer ring guide type in which a cage is guided by an outer ring. For this reason, in order to stabilize the behavior of the cage during operation, it is necessary to secure a guide surface between the inner diameter portion of the outer ring and the outer diameter portion of the cage. Therefore, for example, the inner diameter portion of the outer ring includes a cage guide surface that guides the cage outside the grease storage groove in the axial direction, and the cage guide surface is half of the axial width of the cage. A configuration having an axial width of 13% or more can be employed.

  When a configuration in which a grease storage groove is formed outside the raceway groove of the outer ring, the grease guide surface is formed on a groove wall on the outer end side in the axial direction of the grease storage groove, and the grease storage groove It is possible to adopt a configuration in which a cylindrical surface with the bearing central axis as a cylinder axis is formed in the groove wall on the axially inner side of the guide surface so as to be continuous with the inner surface of the raceway groove. In this case, the grease pressed against the grease guide surface by the wind pressure generated by the rotation of the cage moves to the cylindrical surface, and the grease adhering to the cylindrical surface sequentially moves to the raceway groove of the outer ring. This grease movement ensures the lubricity of the bearing.

  As the shape of the grease guide surface of the grease storage groove, the grease guide surface may be formed as a conical surface having the bearing central axis as an axis or a circular curved surface recessed radially outward. Here, the circular curved surface means a curved surface formed by a part of a curve constituting a circle or an ellipse, or a curved surface whose curvature changes continuously or discontinuously on the axial plane.

  In order to solve the above-described problem, the outer ring for an angular ball bearing according to the present invention has grease storage grooves connected to the raceway grooves formed on both sides in the axial direction of the raceway grooves. It is possible to employ a configuration in which a grease guide surface that is inclined inward in the direction and radially outward is formed.

  As described above, the angular ball bearing according to the present invention has the grease guide surface that is inclined on the groove wall of the grease storage groove formed outside the raceway groove of the outer ring, so that the grease in the grease storage groove is It is easy to move (flow) along the grease guide surface to the race groove of the outer ring due to the wind pressure generated by the rotation of the cage, and is supplied stably to the race groove to ensure the lubricity of the bearing for a long time. Can do.

Sectional drawing which shows the angular ball bearing of 1st Embodiment Expanded sectional view showing the grease storage groove of the outer ring The expanded sectional view which shows the modification of a grease storage groove same as the above The expanded sectional view which shows the grease storage groove of the angular ball bearing of 2nd Embodiment The expanded sectional view which shows the grease storage groove of the angular ball bearing of 3rd Embodiment The expanded sectional view which shows the modification of a grease storage groove same as the above The expanded sectional view which shows the grease storage groove of the angular ball bearing of 4th Embodiment The expanded sectional view which shows the modification of a grease storage groove same as the above The expanded sectional view which shows the grease storage groove of the angular ball bearing of 5th Embodiment Sectional view showing a conventional angular contact ball bearing Expanded sectional view showing the grease storage groove of the outer ring

Hereinafter, embodiments of the present invention will be described with reference to FIGS.
As shown in FIG. 1, the angular ball bearing according to the first embodiment of the present invention includes a plurality of balls interposed between an inner ring 10, an outer ring 11, a raceway groove 12 of the inner ring 10, and a raceway groove 13 of the outer ring 11. 14, a cage 15 that holds the balls 14 at intervals in the circumferential direction, and seals 16, 16 that are provided at both ends of the inner ring 10 and the outer ring 11 and block the bearing space between the inner ring 10 and the outer ring 11, Consists of.

  The inner ring 10 is formed such that the contact angle between the raceway groove 12 and the ball 14 is a predetermined angle. In the outer diameter portion of the inner ring 10, a counter bore 17 whose outer diameter decreases toward the end face is provided on one side of the raceway groove 12. The counter bore 17 is provided in a portion on the side opposite to the axial direction of the outer diameter portion of the inner ring 10 where the contact angle is generated. In addition, a step portion 18 that is recessed inward in the radial direction is provided at an end portion of the outer diameter portion of the inner ring 10 on the side where the contact angle is generated, and a labyrinth seal is formed by a wall surface of the step portion 18 and an inner edge portion of the seal 16 Is formed.

  In the outer ring 11, grease storage grooves 19 and 20 connected to the raceway groove 13 are formed on both sides in the axial direction of the raceway groove 13 in the inner diameter portion. Of the inner diameter portion of the outer ring 11, a grease storage groove 19 is formed in a portion on the opposite side (front side portion) in the axial direction with respect to the portion on the side where the contact angle is generated (back side portion). A grease storage groove 20 is formed in the back side portion.

  In the inner diameter portion of the outer ring 11, shoulder portions 22 are formed on both axial sides of the grease storage grooves 19 and 20, and the outer diameter portion of the cage retainer 15 is guided by the shoulder portions 22. In order to stabilize the behavior of the cage 15 during operation, it is necessary for the shoulder portion 22 to secure a portion of the inner diameter surface with which the outer diameter portion of the cage 15 is in sliding contact, that is, the cage guide surface 23. For this reason, the axial direction width | variety (axial width) W1 of the holder | retainer guide surface 23 of the shoulder part 22 should just be 13% or more with respect to the half of the axial width W2 of the holder | retainer 15, for example.

  Seal grooves 28 are formed at both ends of the inner diameter portion of the outer ring 11, and the outer edge portions of the seals 16, 16 are fixed. The seals 16 and 16 may not be provided depending on the standard or application of the angular ball bearing or the properties of the grease. However, when these seals 16 and 16 are provided, it is possible to suppress the scattering of grease to the outside of the bearing and the entry of foreign matter into the bearing space.

  The grease storage grooves 19 and 20 in the inner diameter portion of the outer ring 11 are formed over the entire circumference of the inner diameter portion of the outer ring 11 in a state in which the contact surface between the race groove 13 and the balls 14 is ensured. It is in a connected state.

  In this first embodiment, as shown in FIG. 2, grease storage grooves 19 and 20 are formed on both sides of the raceway groove 13 of the outer ring 11, but depending on the standard and application of the angular ball bearing, the grease storage groove May be formed on at least one of the outer sides of the raceway groove 13. When formed on both sides as shown in FIG. 2, it is preferable because a large amount of grease can be filled in the bearing space between the inner ring 10 and the outer ring 11.

Further, as shown in FIG. 2, the grease storage groove 19 is disposed radially inward from the radial position of the contact point P with the ball 14 in the raceway groove 13 of the outer ring 11. With this arrangement, it is possible to prevent the balls 14 from getting into the grease storage groove 19 when an axial load is generated on the inner ring 10 and the outer ring 11 toward the front side.
Here, the contact point P in the raceway groove 13 of the outer ring 11 means a nominal contact point defined in JIS B0104, and the raceway groove of the outer ring that is considered to be in contact with the ball when the bearing component is in a normal relative position. The point on the inner surface of

  A grease guide surface 21 that is inclined inward in the axial direction and outward in the radial direction is formed on the bottom wall of the grease storage groove 19. The grease guide surface 21 is continuous with the inner surface of the raceway groove 13 and is formed on a conical surface having the bearing central axis as an axis. The conical surface is formed at a predetermined angle α (for example, 10 degrees) with respect to the bearing central axis.

In the grease storage groove 19, the grease guide surface 21 is formed as a conical surface, but as shown in FIG. 3, it can be formed into a circular curved surface that is recessed radially outward. In this case, as compared with the case where the grease storage groove 19 is formed on the conical surface, the grease can move smoothly at the outer end portion in the axial direction of the grease storage groove 19, and the fluidity can be further improved.
Here, the circularly curved surface means a curved surface formed by a part of a curve that forms an axial cross section of a circle or an ellipse, or a curved surface whose curvature changes continuously or discontinuously.

  Due to the grease guide surface 21, the grease accumulated in the grease storage groove 19 during operation is pressed against the grease guide surface 21 by the wind pressure generated by the rotation of the cage 15 accompanying the rolling of the balls 14. The pressed grease moves (flows) to the raceway groove 13 of the outer ring 11 along the inclined grease guide surface 21 and is stably supplied to the raceway groove 13.

  The grease storage groove 20 is also disposed radially inward from the radial position of the contact point P in the raceway groove 13 of the outer ring 11. As shown in FIG. 2, the bottom wall of the grease storage groove 20 is formed in a cylindrical surface with the bearing central axis as a cylinder axis. If necessary, the grease guide surface 21 is similar to the grease storage groove 19. Can be formed. In this case, the grease in both the grease storage grooves 19 and 20 moves (flows) to the raceway groove 13 of the outer ring 11 along the respective grease guide surfaces, and is stably supplied to the raceway groove 13 more effectively.

  As long as grease is stably supplied to the raceway groove 13 of the outer ring 11 during operation, when the grease storage grooves 19 and 20 are formed on both sides of the raceway groove 13 of the outer ring 11, the grease storage groove 19 and the grease are formed. A grease guide surface can be formed on the storage groove 20 or the bottom walls of the grease storage grooves 19 and 20. That is, a grease guide surface can be formed on at least one of the bottom walls of the grease storage grooves 19 and 20.

  Since the angular ball bearing of this embodiment stably supplies grease to the raceway groove 13 of the outer ring 11 and has a high lubricating performance, a rotating shaft that rotates at a high speed in order to improve processing and operating efficiency, for example, a spindle of a machine tool, It can be applied as a rolling bearing that supports a turbine spindle of a compressor or pump.

  In this way, when supporting the spindle of a machine tool, etc., the angular ball bearings have two or more combinations facing each other for the purpose of increasing the rigidity and rotational accuracy, and providing a negative clearance in the axial direction. It is applied in the state where the preload is applied. In general, as a method for applying this preload, two methods of a fixed position preload and a constant pressure preload are used.

A second embodiment of the present invention is shown in FIG.
The angular ball bearing according to the second embodiment is different from that of the first embodiment in that a spiral groove 24 is formed in the grease guide surface 21 of the grease storage groove 19. For other configurations, the same reference numerals are given to the configurations that are considered to be the same as those of the first embodiment, and the description thereof is omitted.

  The spiral groove 24 is formed in the grease guide surface 21 so as to be connected to the raceway groove 13 of the outer ring 11. Since the spiral groove 24 is formed in the grease guide surface 21, a flow path for guiding the grease to the raceway groove 13 is formed by the spiral groove 24, so that a sufficient amount of grease movement to the raceway groove 13 is ensured. Can do.

  The spiral groove 24 can be formed on the grease guide surface 21 even when the grease guide surface 21 is formed on at least one of the grease storage grooves 19 and 20 of the inner diameter portion of the outer ring 11.

A third embodiment of the present invention is shown in FIGS.
The angular ball bearing according to the third embodiment is different from that of the first embodiment in that the grease guide surface 21 of the grease storage groove 19 includes a lightened portion 25. For other configurations, the same reference numerals are given to the configurations that are considered to be the same as those of the first embodiment, and the description thereof is omitted.

  More specifically, the thinning portion 25 is formed on the outer side in the axial direction of the grease guide surface 21, and is formed outward in the axial direction and outward in the radial direction. When the loose portion 25 is formed, the amount of grease that can be stored in the grease storage groove 19 can be increased while ensuring the fluidity of the grease by the grease guide surface 21.

  As shown in FIG. 5, the thinning portion 25 is located radially inward from the maximum diameter portion Q of the inner surface of the raceway groove 13 of the outer ring 11 and is axially more than the axial center C of the shoulder portion 22 of the inner diameter portion of the outer ring 11. It is formed so as to be located on the inner side in the direction. The position and depth of the thinning portion 25 are appropriately set according to the specifications of the bearing in consideration of the workability with respect to the outer ring 11 and the strength of the outer ring 11.

  In this embodiment, in the grease storage groove 19, a thinning portion 25 is formed on the grease guide surface 21. However, as shown in FIG. 6, a spiral groove 24 connected to the raceway groove 13 is further formed on the grease guide surface 21. May be. The spiral groove 24 forms a flow path for guiding the grease to the track groove 13, and the increased amount of grease can be effectively guided to the track groove 13.

  Further, when the grease guide surface is formed on at least one of the bottom walls of the grease storage grooves 19 and 20 on the inner diameter portion of the outer ring 11, the thinning portion 25 can be formed on the grease guide surface.

A fourth embodiment of the present invention is shown in FIGS.
The angular ball bearing according to the fourth embodiment is different from that of the first embodiment in that the groove wall on the axially outer end side of the grease storage groove 19 has a tapered surface 26 continuous with the grease guide surface 21. For other configurations, the same reference numerals are given to the configurations that are considered to be the same as those in the first embodiment, and the description thereof is omitted.

  The taper surface 26 of the grease storage groove 19 is formed as a conical surface having the bearing central axis as an axis, and the conical surface is formed at a predetermined angle β (for example, 60 degrees) with respect to the bearing central axis. ing.

  The tapered surface 26 is set to an angle larger than the angle α with respect to the bearing central axis of the conical surface which is the grease guide surface 21 shown in FIG. For this reason, the grease adhering to the taper surface 26 moves to the grease guide surface 21 by the wind pressure generated by the rotation of the cage 15 accompanying the rolling of the balls 14. Therefore, the grease adhering to the entire inner surface of the grease storage groove 19 can be moved to the raceway groove 13 of the outer ring 11 without staying.

  In this embodiment, the grease storage groove 19 has a tapered surface 26, but a spiral groove 24 connected to the raceway groove 13 may be further formed on the grease guide surface 21 as shown in FIG. 8. The spiral groove 24 forms a flow path for guiding grease to the track groove 13, and the increased amount of grease can be effectively guided to the track groove 13.

  Further, the taper surface 26 can be formed on the grease guide surface 21 when the grease guide surface 21 is formed on at least one bottom wall of the grease storage grooves 19 and 20 in the inner diameter portion of the outer ring 11.

A fifth embodiment of the present invention is shown in FIG.
In the angular ball bearing according to the fifth embodiment, as shown in FIG. 9, the grease storage groove 19 has a grease guide surface 21 formed on the groove wall at the outer end in the axial direction. This is different from the first embodiment described above in that a cylindrical surface 29 having a bearing central axis as a cylinder axis is formed in the inner groove wall. For the other configurations, the same reference numerals are given to the configurations that are considered to be the same as those in the first embodiment, and the description thereof is omitted.

  The grease guide surface 21 is formed on a conical surface having the bearing central axis as an axis. This conical surface is formed at a predetermined angle γ (for example, 60 degrees) with respect to the bearing center axis.

  Thus, when the grease guide surface 21 is formed on the groove wall on the outer end side in the axial direction of the grease storage groove 19, the wind pressure generated by the rotation of the cage 15 accompanying the rolling of the balls 14 causes the grease guide surface 21. The pressed grease moves to the cylindrical surface 29. The grease adhered to the cylindrical surface 29 is moved to the raceway groove 13 of the outer ring 11. This grease movement ensures the lubricity of the bearing.

DESCRIPTION OF SYMBOLS 10 Inner ring 11 Outer ring 12 Track groove 13 Track groove 14 Ball 15 Cage 16 Seal 17 Counter bore 18 Step portion 19, 20 Grease storage groove 21 Grease guide surface 22 Shoulder portion 23 Cage guide surface 24 Spiral groove 25 Slack portion 26 Tapered surface 28 Seal groove 29 Cylindrical surface 30 Inner ring 31 Outer ring 33 Outer ring raceway groove 34 Ball 35 Cage 36 Grease storage groove 37 Bottom surface

Claims (13)

In the angular ball bearing in which a plurality of balls interposed between the inner ring and the outer ring are held by a cage,
The retainer is guided by the outer ring, and a grease storage groove connected to the raceway groove of the outer ring is formed on an inner side of the outer ring on the outer side in the axial direction of the raceway groove, and axially inward in the groove wall of the grease storage groove Further, an angular ball bearing characterized in that a grease guide surface inclined radially outward is formed.   The angular ball bearing according to claim 1, wherein the grease guide surface is formed so as to be continuous with an inner surface of the raceway groove.   The angular ball bearing according to claim 2, wherein the grease guide surface includes a relief portion formed outward in the axial direction and outward in the radial direction.   More than the axially central portion of the shoulder portion formed on the radially inner side of the inner diameter portion of the raceway groove, and the shoulder portion formed on the outer side in the axial direction of the grease storage groove of the inner diameter portion of the outer ring. The angular ball bearing according to claim 3, wherein the angular ball bearing is located on an inner side in the axial direction.   5. The angular ball bearing according to claim 2, wherein a spiral groove connected to the raceway groove of the outer ring is formed on the grease guide surface.   6. The angular contact ball according to claim 2, wherein a groove wall on an outer end side in the axial direction of the grease storage groove has a tapered surface that extends outward in the axial direction and continues to the grease guide surface. bearing.   The angular contact ball according to claim 2 or 6, wherein the grease storage groove is formed on both sides of the raceway groove, and the grease guide surface is formed on at least one of the two grease storage grooves. bearing.   The angular storage as set forth in claim 7, wherein the grease storage groove on the front surface side of the inner diameter portion of the outer ring is disposed radially inward from a radial position of a contact point with a ball in the raceway groove of the outer ring. Ball bearing.   An inner diameter portion of the outer ring includes a cage guide surface that guides the cage outside the grease storage groove in the axial direction, and the cage guide surface is 13% or more with respect to half of the axial width of the cage. The angular ball bearing according to claim 1, having an axial width.   The grease guide surface is formed in a groove wall on the outer end side in the axial direction of the grease storage groove, and the grease storage groove is a cylinder whose axial center is a groove wall on the inner side in the axial direction of the grease guide surface. The angular ball bearing according to claim 1, wherein a surface is formed so as to be continuous with an inner surface of the raceway groove.   The angular contact ball bearing according to any one of claims 1 to 10, wherein the grease guide surface is formed on a conical surface having a bearing central axis as an axis.   The angular contact ball bearing according to any one of claims 1 to 10, wherein the grease guide surface is formed in a circularly curved surface that is recessed radially outward.   In an outer ring for an angular contact ball bearing provided with a raceway groove in which a ball rolls on the inner diameter part, grease storage grooves connected to the raceway groove are formed on both sides in the axial direction of the raceway groove, and axially on the groove wall of the grease storage groove An outer ring for an angular contact ball bearing formed with a grease guide surface inclined inward and radially outward.

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