JP2012026502A - Retainer for ball bearing and ball bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent two annular bodies from being separated even if a large centrifugal force is loaded by high rotation to secure the enclosed capacity of a lubricant.SOLUTION: In a retainer in which hemispherical pockets 12 for storing balls in an opposing face 11 of the two annular bodies 10 are formed at a plurality of places in a circumferential direction and the two annular bodies is combined with the opposing face abutting, the circumferential end outer diameter side of the pocket on one annular body is extended in an axial direction to form an outer diameter side projection 13 and the inner diameter side is dented to form an inner diameter side recess 14, also the circumferential end inner diameter side of the pocket on another annular body is extended in an axial direction to form an inner diameter side projection 15 and the outer diameter side is dented to form an outer diameter side recess 16, the outer diameter side projection is inserted into the outer diameter side recess and the inner diameter side projection is inserted into the inner diameter recess thereby engaging the outer diameter side projection with the inner diameter side projection in an axial direction, and the engaged surfaces 13a and 15a between the outer diameter side projection and the inner diameter side projection are inclined in an axial direction such that the tip side is thicker than the base end side of the outer diameter side projection and the inner diameter side projection.

Description

  The present invention relates to a ball bearing cage made of synthetic resin that holds a ball so as to roll freely, and a ball bearing in which the cage is incorporated between an outer ring and an inner ring.

  For example, various sealed ball bearings such as deep groove ball bearings and angular ball bearings are widely used for gear support shafts of transmissions of vehicles having motors.

  This type of ball bearing includes an inner ring having an inner race surface formed on the outer diameter surface, an outer ring disposed on the outer side of the inner ring and having an outer race surface formed on the inner diameter surface, and an inner race surface of the inner ring. A plurality of balls interposed between the outer ring and the outer raceway surface of the outer ring, a cage disposed between the inner ring and the outer ring, and holding the balls at equal intervals in the circumferential direction, and the inner ring The main part is constituted by a seal part arranged in an annular space formed between the outer rings. Either the outer ring or the inner ring is attached to a fixed part such as a housing, and the other is attached to a rotating part such as a rotating shaft.

  In particular, in an electric vehicle or a hybrid vehicle, since high-speed motor rotation is input, a rotating portion such as a rotating shaft tends to be high. As a result, insufficient lubrication, torque (heat generation), deformation of the cage due to centrifugal force, and the like become problems. The cage deformation due to insufficient lubrication or torque (heat generation) can be solved by devising the shape of the cage, and by using a lightweight synthetic resin cage, It is possible to suppress deformation of the cage. On the other hand, in the case of a ball bearing used as an electrical accessory part of an automobile (for example, a motor, an alternator, etc.), since it is used in a sealed state with both side seals, it is essential to use a lubricant such as grease.

  Various lightweight synthetic resin cages have been proposed for the purpose of suppressing deformation of the cage due to centrifugal force (see, for example, Patent Document 1). The cage disclosed in Patent Document 1 includes an annular main portion and a pair of elastic members integrally projected in a circumferentially spaced manner on one axial surface of the main portion with a space between each other. And a pocket that is recessed between the pair of elastic pieces and that opens on the outer diameter side and the inner diameter side, and has a crown shape that holds the ball in a freely rolling manner. In such a crown-shaped cage, the ball is held from only one side, and when a large centrifugal force is applied, the ball can drop out of the pocket due to uneven deformation, or it can interfere with other parts such as inner and outer rings There is sex.

  In order to eliminate such a concern, various cages have been proposed in which the cage shape is symmetrical in the axial direction (see, for example, Patent Document 2). The cage disclosed in Patent Document 2 has a structure in which a pair of annular bodies are coupled to each other in the axial direction, and an annular base portion and a column portion standing upright from the base portion are integrally formed. The ring-shaped bodies are opposed to each other so that one pillar portion is located at an intermediate point between the other pillar portions, and are joined so as to form a pocket for holding a ball between adjacent pillar portions. Is.

Japanese Patent Laid-Open No. 9-151943 JP 2009-115128 A

  By the way, in the crown-shaped cage disclosed in Patent Document 1, as described above, the ball is held only from one side, and when a large centrifugal force is applied, the ball falls out of the pocket due to uneven deformation, There is a possibility of interference with other parts such as inner and outer rings. Further, in the cage of Patent Document 2 proposed to eliminate such a concern, the annular bodies are opposed to each other so that one column portion is located at the midpoint between the other column portions, and adjacent columns are arranged. Since the structure combined so as to form a pocket for holding the rolling elements between the parts is adopted, it can be applied to an even number of balls, but cannot be applied to an odd number of balls.

  In addition, when incorporated in a sealed ball bearing using a lubricant such as grease, the symmetrically shaped cage disclosed in Patent Document 2 has a structure in which a pair of annular bodies are coupled by a column portion. Compared to the crown-shaped cage disclosed in Document 1, the space volume between the inner and outer rings of the ball bearing is reduced, and in particular, the ball bearing of a type with a small axial dimension ensures a sufficient amount of lubricant. May be difficult to do.

  Therefore, the present invention has been proposed in view of the above-described problems, and the object of the present invention is not limited by the number of balls, and a large centrifugal force is generated by high rotation while ensuring sufficient strength. An object of the present invention is to provide a ball bearing retainer and a ball bearing that can reliably prevent separation of two annular bodies even when loaded, and can ensure a sufficient amount of lubricant.

  As a technical means for achieving the above-mentioned object, the present invention forms hemispherical pockets for accommodating balls on a plurality of facing surfaces of two annular members facing each other in the axial direction at a plurality of locations in the circumferential direction. This is a ball bearing retainer in which two annular bodies are joined by abutting the surfaces, and the outer diameter side convex portion of the outer circumferential side of the pocket of one annular body is extended in the axial direction. The inner peripheral surface of the annular portion is formed so that the inner peripheral surface can come into contact with the ball and the inner diameter side is recessed to form the inner diameter side concave portion, and the inner peripheral side of the circumferential end of the pocket of the other annular body is set in the axial direction. Extending to form an inner diameter-side convex portion so that its inner peripheral surface can come into contact with the ball, and denting the outer diameter side to form an outer-diameter-side concave portion, and forming the outer-diameter-side convex portion as an outer-diameter-side concave portion The outer diameter side convex portion and the inner diameter side convex portion are engaged with each other in the axial direction by inserting the inner diameter side convex portion into the inner diameter side concave portion. The engagement surface of the convex portion, characterized in that is inclined relative to the axial direction so that the outer diameter side protruding portion and distal than the proximal end side of the inner diameter side protruding portion becomes thick. In addition, it is effective that the annular body in the present invention is made of a synthetic resin in that the weight of the cage can be reduced.

  In the present invention, by engaging the outer diameter side convex portion and the inner diameter side convex portion in the axial direction, a frictional force is generated along the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion. Further, the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion is inclined with respect to the axial direction so that the distal end side is thicker than the proximal end side of the outer diameter side convex portion and the inner diameter side convex portion. As a result, the axial component of the reaction force generated in the normal direction of the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion appears. High rotation speed is achieved by a synergistic effect of the frictional force generated along the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion and the axial component of the reaction force generated in the normal direction of the engagement surface. Even when a larger centrifugal force is applied, it is possible to reliably prevent the two annular bodies from separating in the axial direction. Further, in the present invention, by providing a coupling portion of two annular bodies at the circumferential end of the annular pocket, the present invention can be applied not only to an even number of balls but also to an odd number of balls. There are no restrictions. Furthermore, since the pillar portion located between the pockets is not a joint portion between the two annular bodies, it is easy to obtain a structure that can sufficiently secure the amount of the lubricant enclosed.

  In the present invention, it is desirable that the angle of inclination of the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion is 5 ° or more. By setting the inclination angle in this way, it becomes easy to suppress deformation of the engagement surface when a large centrifugal force is applied due to high rotation, and the axial component of the reaction force is reliably applied to the engagement surface. This makes it easy to secure the coupling force between the two annular bodies. When the inclination angle of the engagement surface is smaller than 5 °, it becomes difficult to suppress deformation of the engagement surface when a large centrifugal force is applied due to high rotation, and the axial direction of the reaction force is applied to the engagement surface. It becomes difficult to ensure that the components act.

  In the present invention, a structure in which the inner diameter side convex portion is thicker than the outer diameter side convex portion is desirable. In this way, when a large centrifugal force is applied due to high rotation, the inner diameter side convex portion made thicker than the outer diameter side convex portion is larger in mass than the outer diameter side convex portion. A convex part deform | transforms larger than an outer diameter side convex part. Here, the engagement surface of the outer diameter side convex portion and the inner diameter side convex portion is inclined with respect to the axial direction so that the distal end side is thicker than the proximal end side of the outer diameter side convex portion and the inner diameter side convex portion. Therefore, the deformation of the inner diameter side convex portion acts to increase the coupling force on the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion.

  In the present invention, it is desirable to form the outer diameter side convex portion and the inner diameter side convex portion at both circumferential ends of three or more pockets. In this way, it is easy to secure the coupling force at the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion, and the two annular bodies are prevented from separating in the axial direction. can do. In addition, the coupling force on the engagement surface between the outer diameter side convex part and the inner diameter side convex part only by forming the outer diameter side convex part and the inner diameter side convex part at both circumferential ends of one or two pockets. It becomes difficult to ensure.

  In the present invention, a structure in which an outer diameter side convex portion and an inner diameter side concave portion are formed at one circumferential end portion of the pocket and an inner diameter side convex portion and an outer diameter side concave portion are formed at the other circumferential end portion is desirable. With such a structure, it is possible to make one annular body and the other annular body by using a kind of annular body manufactured by one mold, and the product cost can be reduced.

  In the present invention, a structure in which the axial dimension of the column portion located between the pockets is smaller than the axial dimension at the pocket position of the two annular bodies is desirable. With this structure, when this cage is applied to a sealed ball bearing, the space volume between the inner and outer rings of the ball bearing can be made larger than before, and a sufficient amount of lubricant is ensured. Easy to do.

  A ball bearing can be configured by adding an outer ring and an inner ring that rotate relative to each other and a ball interposed between the outer ring and the inner ring to the cage having the above-described configuration. In particular, the present invention is effective for a sealed ball bearing provided with a seal portion having a seal lip made of an elastic member and disposed in an annular space formed between an inner ring and an outer ring.

  According to the present invention, by engaging the outer diameter side convex portion and the inner diameter side convex portion in the axial direction, the frictional force generated along the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion, The engagement surface of the outer diameter side convex portion and the inner diameter side convex portion is inclined with respect to the axial direction so that the distal end side is thicker than the proximal end side of the outer diameter side convex portion and the inner diameter side convex portion. This is the case when a large centrifugal force is applied due to high rotation due to the synergistic action with the axial component of the reaction force generated in the normal direction of the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion. However, it is possible to reliably prevent the two annular bodies from separating in the axial direction.

  As a result, without being restricted by the number of balls, while ensuring sufficient strength, even when a large centrifugal force is applied due to high rotation, the two annular bodies are reliably prevented from separating. In addition, it is possible to provide a ball bearing retainer that can secure a sufficient amount of lubricant, and to provide a ball bearing for automobiles suitable for a high-speed bearing used in an electric vehicle or a hybrid vehicle.

In embodiment of this invention, it is an assembly exploded perspective view which shows the two annular bodies which comprise a holder | retainer. It is a partial expanded view which shows the two annular bodies before a coupling | bonding. It is sectional drawing which follows the AA line of FIG. It is sectional drawing which follows the BB line of FIG. It is a partial expanded view which shows the two annular bodies after a coupling | bonding. It is sectional drawing which follows the CC line of FIG. It is sectional drawing which follows the DD line | wire of FIG. FIG. 2 is a cross-sectional view showing a sealed ball bearing incorporating the retainer of FIG. 1 in the embodiment of the present invention.

  Embodiments of a ball bearing retainer and a ball bearing according to the present invention will be described in detail below. In addition, although the following embodiment demonstrates the case where a cage | basket is applied to a sealed ball bearing, it is applicable also to the ball bearing which is not sealed.

  As shown in FIG. 8, the ball bearing 1 of this embodiment is arranged on the outer side of the inner ring 2 having the inner race surface 2 a formed on the outer diameter surface and on the outer side of the inner ring 2, and on the outer race surface 3 a on the inner diameter surface. Between the inner ring 2 and the outer ring 3, between the inner ring 2 and the outer ring 3, between the inner ring 2 and the outer ring 3, the inner ring 2 and the outer ring 3. A cage 5 that holds the balls 4 at equal intervals in the circumferential direction, and a seal portion 7 that is arranged in an annular space 6 formed between the inner ring 2 and the outer ring 3 and has a sealing lip made of an elastic member, The main part is composed of.

  In this embodiment, the outer ring 3 is mounted on a fixed part such as a housing, and the inner ring 2 is mounted on a rotating part such as a rotating shaft. The seal portion 7 includes a cored bar 8a attached to the inner diameter end of the outer ring 3 on the fixed side, and a seal member 8b integrally vulcanized and bonded to the cored bar 8a. The seal member 8b is a rubber member. It has a sealing lip 8c that is in contact with the outer diameter end of the inner ring 2 at its tip. Although the inner ring rotation type is illustrated in this embodiment, the present invention can also be applied to an outer ring rotation type in which the inner ring 2 is mounted on a fixed part such as a housing and the outer ring 3 is mounted on a rotating part such as a rotation shaft. .

  This ball bearing 1 is suitable as a high rotation bearing used in an electric vehicle or a hybrid vehicle, and is a lightweight synthetic for the purpose of suppressing deformation of the cage 5 due to insufficient lubrication, torque (heat generation), and centrifugal force. A resin cage 5 is provided. As shown in FIG. 1, this type of cage 5 includes a plurality of hemispherical pockets 12 for accommodating balls 4 (see FIG. 8) on the opposing surfaces 11 of two annular bodies 10 facing in the axial direction. It is formed in a place, and has a symmetrical shape in which the opposing surfaces 11 of the annular body 10 are abutted to join the two annular bodies 10 together. The cage 5 of this embodiment includes the following coupling structure as means for coupling the two annular bodies 10.

  2 shows two annular bodies 10 before being joined, FIG. 3 is a cross section taken along the line AA in FIG. 2, and FIG. 4 is a cross section taken along the line BB in FIG. As shown in the figure, each of the two annular bodies 10 has an outer diameter side convex portion 13 formed by extending the outer diameter side of one circumferential end portion of the pocket 12 in the axial direction and the inner diameter side. Is formed by extending the inner diameter side of the other circumferential end of the pocket 12 in the axial direction to form the inner diameter side convex portion 15 and the outer diameter side is recessed. An outer diameter side recess 16 is formed.

  As described above, the two annular bodies 10 each form the outer diameter side convex portion 13 and the inner diameter side concave portion 14 at one circumferential end portion of the pocket 12, and the inner circumferential side convex portion at the other circumferential end portion. By adopting the structure in which the portion 15 and the outer diameter side concave portion 16 are formed, one annular body 10 and the other annular body 10 can be formed by using a kind of annular body 10 manufactured by one mold. The product cost can be reduced.

  In this structure, the outer diameter side convex portion 13 of one annular body 10 is inserted into the outer diameter side concave portion 16 of the other annular body 10, and the inner diameter side convex portion 15 of one annular body 10 is inserted into the other annular body 10. By inserting into the inner diameter side concave portion 14, the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are engaged in the axial direction. Further, the engagement surfaces 13a, 15a of the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are thicker at the distal end side than the proximal end sides of the outer diameter side convex portion 13 and the inner diameter side convex portion 15. It is inclined with respect to the axial direction (see FIGS. 3 and 4).

  5 shows the two annular bodies 10 after being combined, FIG. 6 is a cross section taken along the line CC of FIG. 5, and FIG. 7 is a cross section taken along the line DD of FIG. As shown in the figure, the opposing surfaces 11 of the two annular bodies 10 are brought into contact with each other, and the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are engaged in the axial direction with a predetermined tightening margin. Thus, a frictional force is generated along the engagement surfaces 13a, 15a between the outer diameter side convex portion 13 and the inner diameter side convex portion 15. Further, the engagement surfaces 13a, 15a of the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are thicker at the distal end side than the proximal end sides of the outer diameter side convex portion 13 and the inner diameter side convex portion 15. By tilting with respect to the axial direction, an axial component of the reaction force generated in the normal direction of the engagement surfaces 13a, 15a of the outer diameter side convex portion 13 and the inner diameter side convex portion 15 appears.

  Axial component of the frictional force generated along the engagement surfaces 13a and 15a between the outer diameter side convex portion 13 and the inner diameter side convex portion 15 and the reaction force generated in the normal direction of the engagement surfaces 13a and 15a. As a result, the two annular bodies 10 can be reliably prevented from separating in the axial direction even when a large centrifugal force is applied due to high rotation.

  Thus, by providing the joint part which consists of the outer diameter side convex part 13, the inner diameter side recessed part 14, the inner diameter side convex part 15, and the outer diameter side recessed part 16 at the circumferential direction both ends of the pocket 12 of the annular body 10, When a large centrifugal force is applied due to high rotation, even if one annular body 10 and the other annular body 10 are separated from each other in the axial direction and the pocket 12 is opened, the ball 4 is pocketed by the above-described coupling portion. It becomes easy to maintain the state accommodated in 12 (refer FIG. 5).

  Further, by providing a joint portion of the two annular bodies 10 at the circumferential end of the pocket 12 of the annular body 10, it is applicable not only to an even number of balls but also to an odd number of balls. There are no restrictions. Furthermore, since the column part 17 located between the pockets 12 is not a joint part of the two annular bodies 10, it becomes easy to make a structure that can secure a sufficient amount of lubricant.

That is, as shown in FIG. 5, the axial dimension W ₂ of the column portion 17 located between the pockets is smaller than the axial dimension W ₁ at the pocket position of the two annular bodies 10 ( _{W 1>} W 2). By adopting such a structure, when this cage 5 is applied to a sealed ball bearing, the space volume between the inner and outer rings of the ball bearing can be made larger than before, and a sufficient amount of lubricant can be enclosed. It is easy to ensure.

  In this embodiment, the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are illustrated as being formed at both circumferential ends of all the pockets 12, but the outer diameter side convex portion 13 and the inner diameter side convex portion are illustrated. 15 may be formed at both circumferential ends of three or more pockets 12. Thus, if the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are formed at both circumferential ends of the three or more pockets 12, the engagement surface between the outer diameter side convex portion 13 and the inner diameter side convex portion 15 is formed. It becomes easy to secure the coupling force at 13a and 15a, and the two annular bodies 10 can be prevented from separating in the axial direction. In addition, the engagement between the outer-diameter side convex portion 13 and the inner-diameter side convex portion 15 is achieved only by forming the outer-diameter-side convex portion 13 and the inner-diameter-side convex portion 15 at both circumferential ends of one or two pockets 12. It becomes difficult to secure the coupling force at the surfaces 13a and 15a.

  In the coupling structure of this embodiment, the inclination angle θ (see FIGS. 3 and 4) of the engagement surfaces 13a and 15a between the outer diameter side convex portion 13 and the inner diameter side convex portion 15 needs to be 5 ° or more. By setting the inclination angle θ in this way, it becomes easy to suppress deformation of the engagement surfaces 13a and 15a when a large centrifugal force is applied due to high rotation, and a reaction force is applied to the engagement surfaces 13a and 15a. An axial component can be made to act reliably, and it becomes easy to ensure the coupling force of the two annular bodies 10. If the inclination angle θ of the engagement surfaces 13a and 15a is smaller than 5 °, it becomes difficult to suppress deformation of the engagement surfaces 13a and 15a when a large centrifugal force is applied due to high rotation. It becomes difficult to reliably apply the axial component of the reaction force to the surfaces 13a and 15a.

Moreover, in this coupling structure, as shown in FIGS. 6 and 7, the inner diameter side convex portion 15 is thicker than the outer diameter side convex portion 13 (t _IN > t _OUT ). By making the inner diameter side convex portion 15 thicker than the outer diameter side convex portion 13 in this way, the inner diameter side made thicker than the outer diameter side convex portion 13 when a large centrifugal force is applied due to high rotation. Since the mass of the convex portion 15 is larger than that of the outer diameter side convex portion 13, the inner diameter side convex portion 15 is deformed larger than the outer diameter side convex portion 13.

  Here, the engagement surfaces 13a and 15a of the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are thicker on the distal end side than the proximal end sides of the outer diameter side convex portion 13 and the inner diameter side convex portion 15. Therefore, the deformation of the inner diameter side convex portion 15 increases the coupling force between the outer diameter side convex portion 13 and the inner diameter side convex portion 15 at the engagement surfaces 13a, 15a. Works.

  The two annular bodies 10 described above are made of synthetic resin in that the weight of the cage 5 can be reduced. Here, in view of cost and oil resistance, it is effective to mold with any one synthetic resin selected from PPS (polyphenylene sulfide), PA66 (polyamide 66) or PA46 (polyamide 46). . For example, when a lot of resin-aggressive components (phosphorus, sulfur) are contained in the oil used, it is preferable to use PPS because the superiority and inferiority of oil resistance is PPS> PA46> PA66. Further, considering the price of the resin material, since PA66> PA46> PPS, it is desirable to select the material in consideration of the resin aggressiveness of the oil used. In addition, as other resin materials, it is possible to use PA9T (polyamide 9T), PEEK (polyether ether ketone), and phenol resin.

  The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the gist of the present invention. It includes the equivalent meanings recited in the claims and the equivalents recited in the claims, and all modifications within the scope.

DESCRIPTION OF SYMBOLS 1 Ball bearing 2 Inner ring 3 Outer ring 4 Ball 5 Cage 6 Annular space 7 Seal part 8c Seal lip 10 Annular body 11 Opposing surface 12 Pocket 13 Outer diameter side convex part 13a Engagement surface 14 Inner diameter side concave part 15 Inner diameter side convex part 15a Engagement Joint surface 16 Outer diameter side concave portion 17 Column portion θ Inclination angle

Claims (9)

A ball bearing in which hemispherical pockets for accommodating balls are formed at a plurality of locations in the circumferential direction on opposing surfaces of two annular members facing in the axial direction, and the two annular members are joined by abutting the opposing surfaces. A cage for
The outer diameter side of the circumferential end of one annular body is extended in the axial direction to form a convex on the outer diameter side so that the inner peripheral surface can come into contact with the ball and the inner diameter side is recessed. The inner diameter side concave portion is formed, and the inner circumferential surface of the other annular body pocket is extended in the axial direction to form the inner diameter side convex portion, and the inner circumferential surface thereof can be brought into contact with the ball. The outer diameter side is recessed to form an outer diameter side concave portion, and the outer diameter side convex portion is inserted into the outer diameter side concave portion and the inner diameter side convex portion is inserted into the inner diameter side concave portion. The side convex portion and the inner diameter side convex portion are engaged in the axial direction, and the engagement surface of the outer diameter side convex portion and the inner diameter side convex portion is set to be closer to the base end side of the outer diameter side convex portion and the inner diameter side convex portion. A ball bearing retainer that is inclined with respect to the axial direction so that the tip side is thick.   The ball bearing retainer according to claim 1, wherein an inclination angle of an engagement surface between the outer diameter side convex portion and the inner diameter side convex portion is 5 ° or more.   The cage for ball bearings according to claim 1 or 2 which made said inner diameter side convex part thicker than said outer diameter side convex part.   The cage for ball bearings according to any one of claims 1 to 3 which formed said outer diameter side convex part and said inner diameter side convex part in the peripheral direction both ends of three or more pockets.   The outer diameter side convex portion and the inner diameter side concave portion are formed at one circumferential end portion of the pocket, and the inner diameter side convex portion and the outer diameter side concave portion are formed at the other circumferential end portion. A ball bearing retainer according to claim 1.   The ball bearing retainer according to any one of claims 1 to 5, wherein an axial dimension of the column portion positioned between the pockets is smaller than an axial dimension at the pocket position of the two annular bodies. .   The ball bearing retainer according to any one of claims 1 to 6, wherein the annular body is made of a synthetic resin.   A ball bearing comprising the cage according to claim 1, an outer ring and an inner ring that rotate relative to each other, and a ball interposed between the outer ring and the inner ring.   The ball bearing according to claim 8, further comprising a seal portion having a seal lip made of an elastic member and disposed in an annular space formed between the inner ring and the outer ring.

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