JP5697367B2 - Ball bearing cage and ball bearing - Google Patents

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 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, and a cage that is arranged between the inner ring and the outer ring and holds the balls at equal intervals in the circumferential direction. Is configured. 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.

  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 may drop from the pocket due to uneven deformation.

  In order to eliminate such concerns, various cages have been proposed in which the cage shape is symmetrical in the axial direction (see, for example, Patent Documents 2 to 4). The cages disclosed in these Patent Documents 2 to 4 form hemispherical pockets for accommodating balls on the opposing surfaces of two annular bodies facing each other in the axial direction at a plurality of locations in the circumferential direction, It has a symmetrical shape in which two annular bodies are joined by abutting the opposing surfaces.

  As a means for joining these two annular bodies, in the cage of Patent Document 2, an engaging claw protruding in the axial direction is provided between adjacent pockets of the annular body, and the engaging claw is engaged. It has a structure in which a hole is formed between adjacent pockets of the annular body. The cage of Patent Document 3 has a structure in which two annular bodies are fastened by a through fastening member that penetrates between adjacent pockets of the two annular bodies in the axial direction. Furthermore, in the cage of Patent Document 4, a protruding portion protruding in the axial direction is provided between adjacent pockets of the annular body, and a through hole into which the protruding portion is inserted is formed between adjacent pockets of the annular body, It has a structure in which a fixing piece for filling a gap between the protrusion and the through hole is inserted.

JP-A-11-264418 JP 2006-226430 A JP 2008-64221 A JP 2009-281399 A

  By the way, in the crown-shaped cage disclosed in Patent Document 1, the ball is held from only one side as described above, and the ball may drop from the pocket due to uneven deformation when a large centrifugal force is applied. There is. In addition, the cages of Patent Documents 2 to 4 proposed in order to eliminate such concerns have the following problems.

  First, in the cage of Patent Document 2, a structure is employed in which the engaging claws are engaged with the engaging holes in order to join the two annular bodies. Since the force to split the body increases, in order to cope with high rotation, the engagement claw must be sufficiently enlarged to ensure strength, and accordingly the engagement hole is enlarged, It becomes difficult to ensure the strength of the portion that becomes the pillar portion between the pockets. In addition, in order to make it difficult for the engaging claw to come out of the engaging hole, the engaging claw is sharpened at the tip, and in that case, the engaging claw may be broken or wear powder may be generated. become.

  In addition, the cages of Patent Documents 3 and 4 require separate members for the through fastening member and the fixing piece to join the two annular bodies, and the number of parts increases and the through fastening member and the fixing piece are inserted. This requires work to be performed and increases the number of assembly steps.

  Therefore, the present invention has been proposed in view of the above-mentioned problems, and the object of the present invention is to increase the centrifugal force by high rotation while ensuring sufficient strength without increasing the number of parts and the number of assembly steps. It is an object of the present invention to provide a ball bearing retainer and a ball bearing that can reliably prevent separation of two annular bodies even when a load is applied.

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. A ball bearing retainer in which two annular bodies are joined by abutting surfaces, and the outer diameter side convex portion is formed by extending the outer diameter side between adjacent pockets of one annular body in the axial direction. The inner diameter side of the outer diameter side convex portion is recessed to form an inner diameter side concave portion, and the inner diameter side between adjacent pockets of the other annular body is extended in the axial direction so that the inner diameter side convex portion is formed. The outer diameter side convex portion is recessed to form the outer diameter side concave portion, 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. Thus, the outer diameter side convex portion and the inner diameter side convex portion are engaged in the axial direction, and the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion is And than the base end side of the inner diameter side protruding portion is inclined with respect to the axial direction such that the distal end side becomes thick, characterized in that the inner diameter side protruding portion is thicker than the outer diameter side protruding portion.

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.
Also, in the present invention, the inner diameter side convex portion is thicker than the outer diameter side convex portion, so that when a large centrifugal force is applied due to high rotation, the inner diameter side is thicker than the outer diameter side convex portion. Since the mass of the convex portion is larger than that of the outer diameter side convex portion, the inner diameter side convex portion is deformed larger than the outer diameter side convex portion. 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 that the inclination angle 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, it is desirable to form the outer diameter side convex portions and the inner diameter side convex portions at three or more locations in the circumferential direction. 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, only by forming the outer diameter side convex part and the inner diameter side convex part at one place or two places in the circumferential direction, the coupling force on the engagement surface between the outer diameter side convex part and the inner diameter side convex part is ensured. It becomes difficult.

  In the present invention, it is desirable to provide an index for identifying the relative position between the outer diameter side convex portion and the inner diameter side convex portion on the opposite surfaces of the two annular bodies facing each other in the axial direction. In this way, when assembling the cage from the outside in the axial direction when assembling the ball bearing, that is, with the ball interposed between the outer ring and the inner ring, the opposite of the two annular members facing in the axial direction. Based on the index provided on the facing surface, it becomes easy to match the relative positions of the outer-diameter side convex portion and the inner-diameter side convex portion, which are difficult to see with the outer ring and the inner ring, and the assembling property of the cage can be improved.

  In the present invention, the outer diameter side convex portion and the inner diameter side convex portion of one annular body are formed adjacent to the outer diameter side convex portion and the inner diameter side concave portion in the circumferential direction, and the inner diameter side convex portion and the outer diameter of the other annular body are formed. A structure in which an inner diameter side recess and an outer diameter side protrusion are formed adjacent to the side recess in the circumferential direction 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, the circumferential end of the pocket of one annular body is extended in the axial direction to form a tongue piece, and the tongue piece is accommodated in the circumferential end of the pocket of the other annular body. A structure in which a notch is formed is desirable. With such a structure, when a large centrifugal force is applied due to high rotation, even if one annular body and the other annular body are separated from each other in the axial direction to open the pocket, It becomes easy to maintain the state in which the ball is accommodated in the pocket.

  In the present invention, a structure in which a tongue piece portion is formed at one circumferential end portion of the pocket and a notch portion is 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.

  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 view of cost and oil resistance, this annular body is preferably molded from any one synthetic resin selected from PPS, PA66, and PA46.

  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.

  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, it is possible to provide a ball bearing retainer that can reliably prevent separation of the two annular bodies while ensuring sufficient strength without increasing the number of parts and the number of assembly steps. It is possible to provide a ball bearing for automobiles suitable for a high rotation bearing used in a 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. It is sectional drawing which shows the ball bearing which integrated the holder | retainer of FIG. 1 in embodiment of this invention.

  Embodiments of a ball bearing retainer and a ball bearing according to the present invention will be described in detail below.

  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. The main part is comprised with the holder | retainer 5 which is distribute | arranged and hold | maintains each ball | bowl 4 at the circumferential direction equal intervals. Either the outer ring 3 or the inner ring 2 is attached to a fixed part such as a housing, and the other is attached to a rotating part such as a rotating 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 is formed with hemispherical pockets 12 for accommodating balls 4 on opposing surfaces 11 of two annular bodies 10 facing in the axial direction at a plurality of locations in the circumferential direction. Each of the annular bodies 10 has a symmetrical shape in which the opposing surfaces 11 are brought into contact with each other 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, the outer diameter side convex portion 13 is formed by extending the outer diameter side between adjacent pockets 12 of one annular body 10 (see the left side in FIGS. 2 and 3) in the axial direction. The inner diameter side concave portion 14 is formed by denting the inner diameter side of the outer diameter side convex portion 13 , and the inner diameter side between adjacent pockets 12 of the other annular body 10 (see the right side in FIGS. 2 and 3) is an axis. The inner diameter side convex portion 15 is formed by extending in the direction, and the outer diameter side concave portion 16 is formed by denting the outer diameter side of the inner diameter side convex portion 15 .

  In this structure, by inserting the outer diameter side convex portion 13 into the outer diameter side concave portion 16 and inserting the inner diameter side convex portion 15 into the inner diameter side concave portion 14, the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are pivoted. Engage in 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.

  Further, an outer diameter side concave portion 16 and an inner diameter side convex portion 15 are formed adjacent to the outer diameter side convex portion 13 and the inner diameter side concave portion 14 of one annular body 10 (see the left side in FIGS. 2 and 4) in the circumferential direction. A structure in which the inner diameter side concave portion 14 and the outer diameter side convex portion 13 are formed adjacent to the inner diameter side convex portion 15 and the outer diameter side concave portion 16 of the other annular body 10 (see the right side in FIGS. 2 and 4) in the circumferential direction. It is said. By adopting such a structure, it is possible to make one annular body 10 and the other annular body 10 by using a kind of annular body 10 manufactured by one mold, and the product cost can be reduced.

  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.

  In this embodiment, the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are formed at three or more locations in the circumferential direction. Thus, by forming the outer diameter side convex portion 13 and the inner diameter side convex portion 15 at three or more locations, the coupling force at the engagement surfaces 13a and 15a of the outer diameter side convex portion 13 and the inner diameter side convex portion 15 is achieved. It is easy to ensure the above, and it is possible to prevent the two annular bodies 10 from separating in the axial direction.

  Note that the engagement surfaces 13a and 15a of the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are formed only by forming the outer diameter side convex portion 13 and the inner diameter side convex portion 15 at one place or two places in the circumferential direction. It is difficult to ensure the bonding strength at

  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.

Further, 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.

  In assembling the ball bearing 1, two annular bodies 10 are assembled from the outside in the axial direction with the balls 4 interposed between the outer ring 3 and the inner ring 2 at equal intervals in the circumferential direction. In that case, it is difficult to visually recognize the outer diameter side convex portion 13 and the inner diameter side convex portion 15 of the annular body 10 by the outer ring 3 and the inner ring 2, and the outer diameter side convex portion 13 and the inner diameter side convex portion 15 can be engaged. It can be difficult.

  Therefore, an index 17 for identifying the relative position between the outer diameter side convex portion 13 and the inner diameter side convex portion 15 is provided on the opposite surfaces 18 of the two annular bodies 10 facing in the axial direction. Thereby, when the ball bearing 1 is assembled, when the annular body 10 is assembled from the outside in the axial direction with the ball 4 interposed between the outer ring 3 and the inner ring 2, the two annular bodies 10 facing in the axial direction Based on the index 17 provided on the opposite surface 18, it becomes easy to align the relative positions of the outer diameter side convex portion 13 and the inner diameter side convex portion 15 that are difficult to see with the outer ring 3 and the inner ring 2. Can improve the performance.

  The index 17 can be realized by forming protrusions, dents, or the like on the opposite surfaces 18 of the two annular bodies 10 or adding marks by coloring or the like. In this embodiment, as shown in FIG. 1, FIG. 2, and FIG.

  In this embodiment, the circumferential end of the pocket 12 of one annular body 10 (see the left side in FIG. 2) is extended in the axial direction to form the tongue piece 19 and the other annular body 10 (FIG. 2). A notch 20 for accommodating the tongue piece 19 is formed at the circumferential end of the pocket 12. By adopting such a structure, when a large centrifugal force is applied due to high rotation, even if one annular body 10 and the other annular body 10 are spaced apart from each other in the axial direction, It becomes easy to maintain the state in which the ball 4 is accommodated in the pocket 12 by the tongue piece 19 (see FIG. 5).

  A tongue piece 19 is formed at one circumferential end of the pocket 12 and a notch 20 is formed at the other circumferential end. Thereby, it can be set as one annular body 10 and the other annular body 10 using the kind of annular body 10 manufactured with one metal mold | die, and reduction of product cost can be aimed at.

  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.

  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 10 Ring body 11 Opposite 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 surface 16 Outer diameter side concave part 17 Index 18 Anti-opposing surface 19 Tongue piece 20 Notch θ Inclination angle

Claims (10)

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 between adjacent pockets of one annular body is extended in the axial direction to form an outer diameter side convex part and the inner diameter side of the outer diameter side convex part is recessed to form an inner diameter side concave part, Further, the inner diameter side between adjacent pockets of the other annular body is extended in the axial direction to form an inner diameter side convex portion, and the outer diameter side concave portion is formed by denting the outer diameter side of the inner diameter side convex portion. 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 to engage the outer diameter side convex portion and the inner diameter side convex portion in the axial direction, 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 , A ball bearing retainer characterized in that the inner diameter side convex portion is thicker than the outer diameter side convex portion .   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 ball bearing retainer according to claim 1 or 2 , wherein the outer diameter side convex portion and the inner diameter side convex portion are formed at three or more locations in the circumferential direction. Said outer an index for identifying the relative position between the diameter convex portion and the inner diameter side protruding portion, any one of claims 1 to 3 provided respectively on the non-opposing face of the two annular members facing in the axial direction The ball bearing retainer according to item. An outer diameter side convex portion and an inner diameter side convex portion are formed adjacent to the outer diameter side convex portion and the inner diameter side concave portion of the one annular body in the circumferential direction, and the inner diameter side convex portion and the outer diameter side concave portion of the other annular body are formed. When the cage for the ball bearing according to any one of claims 1 to 4 formed the inner diameter side recesses and the outer diameter side protruding portion adjacent to the circumferential direction. A notch that extends in the axial direction of the circumferential end of the pocket of the one annular body to form a tongue piece and accommodates the tongue piece at the circumferential end of the pocket of the other annular body The ball bearing retainer according to any one of claims 1 to 5 , wherein the ball bearing is formed. The ball bearing retainer according to claim 6 , wherein a tongue piece is formed at one circumferential end of the pocket and a notch is formed at the other circumferential end. The ball bearing retainer according to any one of claims 1 to 7 , wherein the annular body is made of a synthetic resin. The ball bearing retainer according to any one of claims 1 to 8 , wherein the annular body is formed of any one synthetic resin selected from PPS, PA66, and PA46. A cage according to any one of claims 1 to 9 ball bearing having an outer ring and the inner ring rotate relative to each other and a ball interposed between the outer ring and the inner ring.

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