JP5855411B2 - 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 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.

JP 2007-32821 A

  By the way, in the crown-shaped cage disclosed in Patent Document 1, since the ball is held from only one side as described above, the ball falls off the pocket due to uneven deformation when a large centrifugal force is applied. Or may interfere with other parts such as inner and outer rings. In order to eliminate such concerns, various cages have been proposed in which the cage shape is symmetrical in the axial direction. This cage has a structure in which a pair of annular bodies are joined in the axial direction, and hemispherical pockets for receiving balls are formed at a plurality of locations in the circumferential direction on opposite surfaces of the two annular bodies facing in the axial direction. In addition, two annular bodies are joined by abutting the opposing surfaces.

  However, in this type of cage, like the cage disclosed in Patent Document 1, the lubricant attached to the balls is scraped off on the inner diameter side and outer diameter side of the inner surface of the pocket by the rotation, There has been a problem that the lubricant leaks to the outside of the bearing by the breathing action of the seal portion because it adheres to and accumulates on the seal groove formed on the outer diameter surface of the inner ring of the bearing or the inner diameter surface of the outer ring.

  Therefore, the present invention has been proposed in view of the above-mentioned problems, and the object of the present invention is for a ball bearing that can prevent the lubricant scraped off from the pocket inner surface from leaking out of the bearing. The object is to provide a cage and a ball bearing.

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 a coupling portion for joining two annular bodies is provided at both circumferential ends of the pocket, and two annular bodies A recess is provided in at least one of the inner diameter side periphery and the outer diameter side periphery of the pocket, and the coupling portion extends the outer diameter side of the circumferential end of the pocket of one annular body in the axial direction to project the outer diameter side. The inner peripheral surface of the inner ring surface can be brought into contact with the ball, the inner diameter side is recessed to form an inner diameter side recess, and the inner diameter side of the circumferential end of the pocket of the other annular body is extended in the axial direction. The inner diameter convex part is formed to allow the inner peripheral surface to come into contact with the ball and the outer diameter side The outer diameter side concave portion is formed by recessing, and the outer diameter side convex portion and the inner diameter side convex portion are tightened by inserting the outer diameter side convex portion into the outer diameter side concave portion and inserting the inner diameter side convex portion into the inner diameter side concave portion. Instead, the engagement surface of the outer diameter side convex portion and the inner diameter side convex portion is made thicker at the tip side than the base end side of the outer diameter side convex portion and the inner diameter side convex portion. And having a structure in which the inner diameter side convex portion is thicker than the outer diameter side convex portion . Here, “at least one of the inner diameter side edge and the outer diameter side edge of the pocket” means a case where a recess is provided on the inner diameter side edge of the pocket, a case where a recess is provided on the outer diameter side edge of the pocket, and an inner diameter side edge of the pocket It means that a dent may be provided in both the outer peripheral side and the outer peripheral side.

  In addition, this hollow should just be provided in the rotation direction front side of the ball at least of the pocket. The lubricant is scraped off when the balls come into contact with the outer diameter side end face / inner diameter side end face of the pocket. The pocket, especially the front side of the ball in the direction of rotation, is easily scraped off. This is because the balls are mainly scraped off when the balls enter the pocket end faces.

  In the present invention, a coupling portion for joining two annular bodies is provided at both ends in the circumferential direction of the pocket, and a recess is provided in at least one of the inner peripheral edge and the outer peripheral edge of the pocket. The scraping of the lubricant at the peripheral edge or the outer peripheral edge can be reduced. Thereby, it is possible to prevent the lubricant from adhering and accumulating in the seal groove, to reduce a large amount of lubricant leakage, and to always interpose the lubricant between the inner and outer rings and the balls.

  In the present invention, a structure in which a flange extending in the radial direction is provided on at least one of the inner diameter side and the outer diameter side of the axial end portion of the annular body is desirable. Here, “at least one of the inner diameter side and the outer diameter side” means that when the flange portion is provided only on the inner diameter side, when the flange portion is provided only on the outer diameter side, the flange portion is provided on both the inner diameter side and the outer diameter side. It means to include all the cases where it is provided. In this case, if the groove is provided in the portion corresponding to the flange portion of the bearing inner and outer rings, the labyrinth formed by the flange portion and the groove can surely prevent the lubricant from leaking outside the bearing. .

  In this invention, the structure which provided the hollow in the site | part between pockets of the outer-diameter surface of an annular body is desirable. If it does in this way, a lubricant will accumulate in the hollow formed in the outside diameter surface of an annular body, and it can control that the lubricant leaks out of the bearing.

  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.

  In the coupling part in the present invention, it is desirable that the inclination angle of the engagement surface between the outer diameter side convex part and the inner diameter side convex part 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 , the inner diameter side convex portion is thicker than the outer diameter side convex portion when a large centrifugal force is applied due to high rotation by making the inner diameter side convex portion thicker than the outer diameter side convex portion. Therefore, the inner diameter side convex portion is deformed more greatly 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.

  The coupling portion in the present invention has 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 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. As the synthetic resin constituting the cyclic body, any one selected from a polyamide resin, a polyether ether ketone resin, a polyphenylene sulfide resin, a polyphthalamide resin, or a polyamideimide resin is preferable.

  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, joint portions for joining two annular bodies are provided at both ends in the circumferential direction of the pocket, and at least one of the inner diameter side periphery and the outer diameter side periphery of the pocket is provided with a recess. It is possible to reduce scraping of the lubricant at the inner peripheral edge or the outer peripheral edge. Thereby, it is possible to prevent the lubricant from adhering and accumulating in the seal groove, to reduce a large amount of lubricant leakage, and to always interpose the lubricant between the inner and outer rings and the balls. As a result, a long-life and highly reliable ball bearing can be provided.

In the embodiment of the present invention, it is an assembly exploded perspective view showing two annular bodies provided with depressions on the outer diameter side periphery of the pocket. FIG. 2 is an assembled perspective view showing two annular bodies of FIG. 1. In another embodiment of the present invention, it is an exploded perspective view showing two annular bodies provided with depressions on the inner periphery of the pocket. FIG. 4 is an assembled perspective view showing two annular bodies of FIG. 3. In other embodiment of this invention, it is an assembly exploded perspective view which shows the two annular bodies which provided the hollow in both the outer peripheral side periphery and the internal diameter side periphery of a pocket. FIG. 6 is an assembled perspective view showing the two annular bodies of FIG. 5. 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 a sealed ball bearing in embodiment of this invention. In another embodiment of the present invention, it is an exploded perspective view showing two annular bodies provided with flanges at axial ends. FIG. 15 is an assembled perspective view showing two annular bodies of FIG. 14. In other embodiment of this invention, it is a partial expanded sectional view which shows the ball bearing incorporating the cage | basket consisting of the annular body which provided the collar part. In another embodiment of the present invention, it is an exploded perspective view showing two annular bodies provided with a recess in the outer diameter surface. FIG. 18 is an assembled perspective view showing two annular bodies of FIG. 17.

  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. 13, the ball bearing 1 of this embodiment is disposed 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 is composed of a seal member 8b made of an elastic member such as rubber that is integrally vulcanized and bonded to the core metal 8a. The seal member 8b is an inner diameter end portion of the outer ring 3 whose base end portion is a fixed side. And has a seal lip 8c in contact with the outer diameter end of the inner ring 2 at the 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 FIGS. 1 and 2, the retainer 5 has a hemispherical pocket 12 that accommodates the balls 4 (see FIG. 13) on the opposing surfaces 11 of the two annular bodies 10 facing in the axial direction in the circumferential direction. It is formed in a plurality of locations, 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. 1 and FIG. 2 exemplifies a case where a recess 18 is provided on the outer peripheral side periphery of the pocket 12, and the embodiment shown in FIG. 3 and FIG. 12 illustrates the case where the recess 19 is provided on the inner periphery of the inner diameter 12, and the embodiment shown in FIGS. 5 and 6 further includes recesses 18 and 19 provided on both the outer periphery and the inner periphery of the pocket 12. The case is illustrated. In each embodiment, although the case where the two dents 18 and 19 were formed in the concave curved surface shape along the periphery of the pocket 12 was illustrated, the number and shape are arbitrary.

  In the cage 5 in each embodiment, the recesses 18 and 19 are provided in the inner periphery or outer periphery of the pocket 12 that accommodates the balls 4, so that lubrication is performed on the inner periphery or outer periphery of the pocket 12. The scraping of the material can be reduced. As a result, it is possible to prevent the lubricant from adhering to and accumulating in the seal groove 2b (see FIG. 13) formed on the outer diameter surface of the inner ring 2 and to reduce a large amount of lubricant leakage. A lubricant can always be interposed between the running surface 2a and the outer rolling surface 3a of the outer ring 3 and the balls 4.

  Since the lubricant is scraped off mainly when the ball 4 enters the end face of the pocket 12, the depressions 18 and 19 may be provided at least on the rotation direction side of the ball 4. For example, in the example in which the recess 18 is provided in the outer periphery of the pocket 12 as shown in FIG. 2, when the rotation direction of the ball 4 (see FIG. 10) is the arrow direction in FIG. It is sufficient if there is a recess 18 located at least on the front side in the rotation direction of the pocket 12. Further, in the example in which the recess 19 is provided on the inner periphery of the pocket 12 as shown in FIG. 4, when the rotation direction of the ball 4 (see FIG. 10) becomes the arrow direction in FIG. It is sufficient if there is a recess 19 located at least on the front side in the direction of rotation of 12.

  The cage 5 of each of the embodiments described above includes the following structure as the coupling portion 17 that couples the two annular bodies 10. 7 shows the two annular bodies 10 before joining, FIG. 8 is a cross section taken along the line AA in FIG. 7, and FIG. 9 is a cross section taken along the line BB in FIG. FIG. 10 shows the two annular bodies 10 after joining, FIG. 11 is a cross section taken along the line CC in FIG. 10, and FIG. 12 is a cross section taken along the line DD in FIG. The illustration shows an embodiment in which a recess 18 is provided on the outer periphery of the pocket 12, but an embodiment in which a recess 19 is provided on the inner periphery of the pocket 12, and an outer periphery and an inner periphery of the pocket 12. The same applies to the embodiment in which the depressions 18 and 19 are provided in both.

  As shown in FIGS. 7 to 9, each of the two annular bodies 10 forms an outer diameter side convex portion 13 by extending the outer diameter side of one circumferential end of the pocket 12 in the axial direction. In addition, the inner diameter side is recessed to form the inner diameter side concave portion 14, and the inner diameter side of the other circumferential end of the pocket 12 is extended in the axial direction to form the inner diameter side convex portion 15 and the outer diameter side is The outer diameter side recess 16 is formed by being recessed.

  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. 8 and 9).

  As shown in FIGS. 10 to 12, 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. By combining, 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 coupling | bond part 17 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 in 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 to be opened, the balls 4 are formed by the coupling portion 17 described above. Is easily maintained in the pocket 12 (see FIG. 10).

  In the coupling portion 17 of this embodiment, the inclination angle θ (see FIGS. 8 and 9) of the engagement surfaces 13a, 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 | bond part 17, as shown in FIG.11 and FIG.12, the inner diameter side convex part 15 is made thicker than the outer diameter side convex part 13 ( _tIN > _tOUT ). 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.

  14 and 15 show an embodiment in which a flange portion 21 extending in the radial direction is provided on the inner diameter side and the outer diameter side of the axial end portion of the annular body 10. In this case, as shown in FIG. 16, concave grooves 23 and 24 in which the labyrinth 22 is formed by the flange portion 21 are formed at portions corresponding to the flange portion 21 of the inner ring 2 and the outer ring 3 of the ball bearing 1. Accordingly, the labyrinth 22 formed by the flange portion 21 of the cage 5 and the concave grooves 23 and 24 of the inner and outer rings 2 and 3 can surely suppress leakage of the lubricant to the outside of the bearing. 14 and 15 show an embodiment in which a recess 18 is provided on the outer periphery of the pocket 12, an embodiment in which a recess 19 is provided on the inner periphery of the pocket 12, or an outer diameter side of the pocket 12. The same applies to the embodiment in which the depressions 18 and 19 are provided on both the peripheral edge and the inner peripheral edge.

  Further, as in the above-described embodiment, when the recess 18 is provided on the outer periphery of the pocket 12, the recess 19 is provided on the inner periphery of the pocket 12, or the outer periphery and the inner periphery of the pocket 12. In addition to the case where the depressions 18 and 19 are provided in both of them, as shown in FIGS. 17 and 18, a structure in which the depression 20 is provided in the portion between the pockets 12 of the outer diameter surface 25 of the annular body 10 is also possible. By providing the recess 20 in the outer diameter surface 25 of the annular body 10 in this way, the lubricant is deposited in the recess 20, and leakage of the lubricant to the outside of the bearing can be suppressed. The illustrated embodiment is an embodiment in which a recess 18 is provided on the outer periphery of the pocket 12, but an embodiment in which a recess 19 is provided on the inner periphery of the pocket 12, and the outer periphery and inner diameter of the pocket 12. The same applies to the embodiment in which the depressions 18 and 19 are provided on both peripheral edges.

  The annular body 10 described above is made of a synthetic resin in order to reduce the weight of the cage 5. Synthetic resins constituting the annular body 10 include polyamide resins (PA46, PA66, PA9T, PA11, PA6, etc.), polyetheretherketone resins (PEEK), polyphenylene sulfide in consideration of cost and oil resistance. Any one selected from resin (PPS), polyphthalamide resin (PPA), and polyamideimide resin (PAI) is preferable.

  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 10 Annular 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 Coupling part 18-20 Indentation 21 Gutter part θ Inclination angle

Claims (8)

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 retainer for coupling the two annular bodies is provided at both ends in the circumferential direction of the pocket, and at least one of the inner peripheral edge and the outer peripheral edge of the pocket in the two annular bodies. A recess is formed in the pocket, and an outer diameter side convex portion is formed by extending an outer diameter side of a circumferential end of the pocket of one annular body in an axial direction, and an inner circumferential surface thereof is abutted against the ball. The inner diameter side is recessed to form an inner diameter side concave portion, and the inner circumferential side end portion of the other annular body is extended in the axial direction to form an inner diameter side convex portion. The inner peripheral surface can be brought into contact with the ball and the outer diameter side is recessed to form an outer diameter side recess, By inserting the outer diameter side convex portion into the outer diameter side concave portion and inserting the inner diameter side convex portion into the inner diameter side concave portion, the outer diameter side convex portion and the inner diameter side convex portion are engaged in the axial direction with a tightening margin. 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. And a ball bearing retainer having a structure in which the inner diameter side convex portion is thicker than the outer diameter side convex portion .   The ball bearing retainer according to claim 1, wherein a flange portion extending in a radial direction is provided on at least one of an inner diameter side or an outer diameter side of an axial end portion of the annular body.   The ball bearing retainer according to claim 1 or 2, wherein a depression is provided in a portion between the pockets on the outer diameter surface of the annular body. The coupling portion is cage for the ball bearing according to any one of claims 1 to 3 in which said outer diameter side protruding portion and the inclination angle of the engaging surfaces between the inner diameter side protruding portion 5 ° or more. The coupling portion has an outer diameter side convex portion and an inner diameter side concave portion formed at one circumferential end portion of the pocket, and an inner diameter side convex portion and an outer diameter side concave portion formed at the other circumferential end portion. The ball bearing retainer according to any one of 1 to 4 . The ball bearing retainer according to any one of claims 1 to 5 , wherein the annular body is made of a synthetic resin. The ball bearing retainer according to claim 6 , wherein the synthetic resin is any one selected from a polyamide resin, a polyether ether ketone resin, a polyphenylene sulfide resin, a polyphthalamide resin, or a polyamideimide resin. A cage according to any one of claims 1 to 7 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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