JP2015232400A - Holder for ball bearing, and ball bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a holder for a ball bearing capable of attaining reduction in torque and preventing a foreign matter from accumulating thereinside, and a ball bearing.SOLUTION: A holder for a ball bearing is made of resin, and has in a circumferential direction a plurality of hemispherical pockets 12 housing a ball 4 on opposite surfaces 11 of a pair of annular bodies 10 facing each other in an axial direction. The pair of annular bodies 10, 10 is integrated so as to be symmetrical in a circumferential overlapped manner at a connection part. On the inner peripheral surfaces of the pockets 12 of the annular bodies 10, 10 and mating surfaces 11a between the pockets 12 of the annular bodies 10, 10, respectively provided are recess grooves 19, 20 opened to a holder inner diameter surface and a holder outer diameter surface.

Description

The present invention relates to a ball bearing cage that holds a ball in a freely rolling manner, and a ball bearing in which the cage is incorporated between an outer ring and an inner ring, and particularly requires high-speed rotation and low torque under oil lubrication. The present invention relates to a bearing used in an application.

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.

  In general, a ball bearing includes an inner ring, an outer ring, a ball interposed between the inner ring and the outer ring, and a cage that holds the ball. One of the outer ring and 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.

  A resin crown type cage may be used for the cage. This resin crown type cage is made of a resin excellent in wear resistance, seizure resistance, and the like, and has a concave portion disposed at a predetermined pitch along the circumferential direction on one axial end surface of the annular cage body. In addition, a pair of claw portions projecting from the opening ends facing the circumferential direction of the concave portion are provided, and a pocket for storing a ball is formed by the concave portion and the pair of claw portions.

  By the way, in an electric vehicle and a hybrid vehicle, since high-speed motor rotation is input, rotation parts, such as a rotating shaft, tend to become high rotation. As a result, insufficient lubrication, torque (heat generation), deformation of the cage due to centrifugal force, and the like become problems.

  However, the resin crown type cage is configured to hold the ball only from one side (one axial end side). For this reason, when a large centrifugal force is applied, the ball may fall off due to uneven deformation. Therefore, conventionally, 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 formed by abutting the opposing surfaces. There is a combined cage.

  Moreover, in order to eliminate the torque (heat generation) countermeasure and the front and back of the bearing, it is preferable that the cage shape is symmetrical in the axial direction. For this reason, a structure in which the divided cages are joined together is indispensable. For this reason, conventionally, various cage structures for coupling two annular bodies to each other have been proposed (Patent Documents 1 to 5).

JP 2006-226430 A JP 2006-226447 A JP 2006-226448 A JP 2008-64221 A JP 2009-281399 A

  By the way, in the conventional bearing retainer described above, the ball-facing surface of the pocket for holding the hard sphere (ball) is constituted by a single curved surface that follows the ball. Causes shear resistance of oil (grease and other lubricants). This shear resistance is generated when an oil film formed between the inside of the pocket and a steel ball (ball) held in the pocket is sheared. In addition, resistance is generated when the lubricant passes through a minute gap between the inside of the cage pocket that covers the ball. For this reason, it has been difficult to reduce the torque in the conventional cage.

  As a means for reducing the shear resistance as described above, it can be proposed to provide a concave portion on the inner peripheral surface of the pocket. However, if such a concave portion is provided, there is a possibility that foreign matter may accumulate in the concave portion. In addition, foreign matter may be deposited on a mating portion or the like of the cage structure that couples the two annular bodies to each other. Foreign materials include water, dust, metal powder, bearing wear powder, and the like. If foreign matter stays, the load bearing performance will be significantly reduced, resulting in a shortened life. In addition, the acoustic performance is greatly affected. Note that the sound generated in the bearing includes case sound, beat sound, cage sound, scratch sound, dust sound, and the like.

  Therefore, in view of such circumstances, the present invention is intended to provide a ball bearing retainer and a bearing capable of realizing a reduction in torque and preventing foreign matter from being accumulated inside.

  The cage for ball bearings of the present invention has hemispherical pockets that accommodate balls on a plurality of circumferential surfaces on opposite surfaces of a pair of annular bodies facing in the axial direction, and the pair of annular bodies overlap in the circumferential direction. It is a resin ball bearing cage that is made symmetrical and integrated, and is provided with a concave groove on the inner peripheral surface of the pocket of the annular body from the inner diameter surface of the cage to the outer diameter surface of the cage. In the mating surface between the pockets on the opposing surface of the body, a concave groove is provided that extends radially from the center of the annular body toward the outer periphery and reaches the outer diameter surface of the cage from the inner diameter surface of the cage.

  According to the ball bearing cage of the present invention, the relief portion of the lubricant can be formed on the inside of the pocket by the recessed groove reaching from the cage inner diameter surface to the cage outer diameter surface. For this reason, in this ball bearing cage, the resistance when the lubricant passes through the pocket can be reduced, and the amount of oil film formed between the ball and the pocket can be reduced. In addition, by providing the groove on the inner peripheral surface of the pocket or the groove on the mating surface, foreign matter can be discharged to the outside.

  In this case, it is preferable to provide two concave grooves provided on the inner peripheral surface of the pocket. Thus, in the case where two concave grooves provided on the inner diameter surface of the cage are provided, the lubricant can be efficiently released.

  It is preferable that the end surface on the opposite side of the annular body is flat. By adopting such a flat shape, the stirring resistance of the lubricant can be reduced.

  As the cage material, any of polyamide resin, polyether ether ketone resin (PEEK), and polyphenylene sulfide resin (PPS) can be used. The polyamide resin may be PA66 (polyamide 66), PA46 (polyamide 46), PA9T (polyamide 9T), PA11 (polyamide 11), or PA6 (polyamide 6). . Polyamide resins such as PA66 are excellent in tensile elongation, tensile strength, impact resistance, wear resistance, lubricity and the like. PPS (polyphenylene sulfide resin) is an engineering plastic having high heat resistance, chemical resistance, and precision moldability. PEEK (polyether-ether-ketone resin) has very high heat resistance as a thermoplastic resin, is excellent in fatigue resistance, and is excellent in wear resistance, dimensional stability, and chemical resistance.

  A ball bearing according to the present invention includes an inner ring, an outer ring, a ball interposed between the inner ring and the outer ring, and a cage that holds the ball. The ball bearing includes the ball bearing. A cage is used.

  An outer flange portion extending to the outer diameter side is provided on the outer diameter portion on the counter mating side of the annular body, and an inner flange portion extending to the inner diameter side is provided on the inner diameter portion on the counter mating side, and between the outer flange portion and the inner diameter surface of the outer ring B ≧ A, where B is the clearance and A is the clearance between the inner flange and the outer diameter surface of the inner ring.

  An outer flange portion extending toward the outer diameter side is provided at the outer diameter portion on the counter mating side of the annular body, and an inner flange portion extending toward the inner diameter side is provided at the inner diameter portion on the counter mating side. And an outer ring tapered surface that expands from the inner side in the axial direction toward the outer side in the axial direction, and an outer diameter end of the outer flange portion is a tapered surface that increases in diameter from the inner side in the axial direction toward the outer side in the axial direction. If the clearance between the tapered surface and the outer ring tapered surface is B, and the clearance between the inner flange portion and the outer diameter surface of the inner ring is A, B ≧ A may be satisfied.

  By providing the outer flange portion and the inner flange portion, it is possible to restrict the inflow of the lubricant into the inside (inside the bearing) and prevent the lubricant from flowing out from the inside (inside the bearing). In particular, by setting B ≧ A, it is possible to discharge the foreign matter that tends to stay inside while preventing the lubricant from flowing out to the outside. Further, by using the outer diameter end of the outer ring on the inner diameter surface of the outer ring in the bearing axial direction and the outer diameter end of the outer collar portion as tapered surfaces, it is possible to improve the action of discharging foreign matters to the outside.

  The ball bearing is preferably applied to a transmission. The transmission is a main transmission that shifts the driving force from the engine and transmits it to the drive shaft, etc., and is roughly divided into a manual type and an automatic type, and a front axle drive (FWD) transaxle, rear There are wheel drive (RWD) transmissions and four-wheel drive (4WD) transfers (sub-transmissions). The rolling bearing is attached, for example, so as to be interposed between the main shaft and the main drive gear.

The cage for ball bearings of the present invention can reduce the resistance when the lubricant passes through the pocket, and can reduce the amount of oil film sheared when the ball moves. ) Torque can be reduced. In addition, excess lubricant between the pocket inner peripheral surface and the ball (hard sphere) can be discharged from this space, and the influence of the excess lubricant on the torque can be eliminated. Furthermore, the foreign matter can be discharged to the outside, and the foreign matter is difficult to accumulate, so that the occurrence of the problems due to the foreign matter accumulation can be prevented. In addition, since two annular bodies are used, deformation due to centrifugal force and dropout of the ball can be effectively prevented. Moreover, since this cage is made of resin, there is an advantage that it is inexpensive and light.

  By making the end face on the opposite side flat, the stirring resistance of the lubricant can be reduced, and torque can be further reduced.

  As the cage material, polyamide resin or the like excellent in tensile elongation, tensile strength, impact resistance, wear resistance, lubricity and the like can be used, and a high-quality cage can be provided.

  With a flange, it is possible to limit the inflow of lubricant into the interior (inside the bearing) and prevent the lubricant from flowing out from the inside (inside the bearing), and maintain a stable lubricant. Torque reduction can be achieved effectively. In particular, by satisfying B ≧ A, foreign matter can be discharged to the outside, the load bearing performance can be prevented from being lowered, and the life can be extended. Furthermore, noise generation can be effectively prevented.

  The ball bearing according to the present invention can reduce the deformation of the cage due to the high-speed rotation, reduce the inflow amount of the lubricating oil, and reduce the agitation resistance, thereby reducing the torque. For this reason, if a bearing is used for a motor vehicle, the environment-friendly driving | operation with a fuel-efficient improvement is attained. That is, this bearing is optimal for automobile transmissions.

It is sectional drawing of the ball bearing using the holder | retainer which shows embodiment of this invention. It is a principal part top view of the annular body of the holder | retainer shown in the said FIG. FIG. 2 is a simplified development view of a main part of an annular body of the cage shown in FIG. 1. FIG. 2 is a perspective view before assembly of the cage shown in FIG. 1. It is a perspective view of the state which assembled the holder shown in the above-mentioned FIG. FIG. 2 is a development view before assembly of the cage shown in FIG. 1. It is an expanded view of the state which assembled the holder | retainer shown in the said FIG. It is the sectional view on the AA line of the said FIG. It is the BB sectional view taken on the line of FIG. It is CC sectional view taken on the line of the said FIG. It is the DD sectional view taken on the line of the said FIG. It is a principal part top view of the cyclic | annular body of the holder | retainer which shows a reference example. FIG. 13 is a simplified development view of a main part of an annular body of the cage shown in FIG. 12. It is sectional drawing of the other ball bearing which shows embodiment of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 shows a ball bearing using a cage 5 showing an embodiment of the present invention. The ball bearing 1 includes an inner ring 2 having an inner raceway surface 2a formed on an outer diameter surface, and an outer side of the inner ring 2. The outer ring 3 having the outer raceway surface 3a formed on the inner diameter surface, and a plurality of rolls interposed between the inner raceway surface 2a of the inner race 2 and the outer raceway surface 3a of the outer race 3 so as to be freely rollable. The main part is comprised by the ball | bowl 4 and the said holder | retainer 5 which is distribute | arranged between the inner ring | wheel 2 and the outer ring | wheel 3, and hold | maintains each ball | bowl 4 at the circumferential direction equal intervals.

  As shown in FIGS. 4 to 7, the cage 5 has hemispherical pockets 12 that accommodate the balls 4 on the opposing surfaces 11 of the two annular bodies 10 facing each other in the axial direction so as to roll freely. The two annular bodies 10 are coupled to each other by joining portions 18 provided at both ends in the circumferential direction of the pocket 12 by abutting the respective opposing surfaces 11 of the annular body 10. The inner peripheral surface of the pocket 12 in the annular body 10 has a concave spherical shape with a single radius of curvature.

  In this case, as shown in FIGS. 2 and 3, etc., a groove for lubricating oil removal 19 having an arc-shaped cross section is provided on the inner peripheral surface of the pocket 12 of the annular body 10. The groove 19 is formed in a groove shape extending in the radial direction at two locations on the inner peripheral surface of the pocket 12 of each annular body 10. That is, each concave groove 19 reaches the cage outer diameter surface 10a from the cage inner diameter surface 10b, and opens to the cage inner diameter surface 10b and the cage outer diameter surface 10a, respectively.

  Further, in each of the mating surfaces 11a between the pockets adjacent to each other in the circumferential direction, a concave groove reaching the cage outer diameter surface 10a from the cage inner diameter surface 10b and opening to the cage inner diameter surface 10b and the cage outer diameter surface 10a, respectively. 20 is formed. Each of the concave grooves 19 and 20 is a semicircular groove in cross section, but may be a semi-elliptical or rectangular cross section, or a V-shaped cross section. Good.

  The flange portions 24 a and 24 b are provided on the outer diameter portion and the inner diameter portion on the opposite side of the annular body 10. That is, as shown in FIG. 1, the outer flange portion 24a on the bearing outer diameter side extends to the bearing outer diameter side, and the inner flange portion 24b on the bearing inner diameter side extends to the bearing inner diameter side. In this case, the end surface 21 on the counter mating side is formed into a flat shape (flat surface) parallel to the end surface in the bearing axial direction, and the inner diameter portion on the counter mating surface side of the inner flange portion 24b is aligned from the outer diameter side toward the inner diameter side. The tapered surface is inclined to the surface side.

  By the way, in order to escape such flanges 24a and 24b, a circumferential notch 22 is provided at the axial end of the inner diameter surface of the outer ring 3, and a circumferential direction is provided at the axial end of the outer diameter surface of the inner ring 2. A notch 23 is provided.

  The circumferential notch 23 of the inner ring 2 has a rectangular cross section, but the circumferential notch 22 of the outer ring 3 has an outer ring taper surface whose notch surface expands from the axially inner side toward the axially outer side. 22a. The taper angle α is, for example, about 20 ° to 45 °. Corresponding to the taper surface 22a, the outer diameter end of the outer flange portion 24a is a flange taper surface 25 that increases in diameter from the inner side in the axial direction toward the outer side in the axial direction. The taper angle β of the taper surface 25 is set to be substantially the same as the taper angle α of the outer ring taper surface 22a. A predetermined clearance is provided between the outer ring tapered surface 22 a and the tapered surface 25.

  In this case, a predetermined clearance is also provided between the notch surface 23d of the circumferential notch 23 of the inner ring 2 and the inner flange 24b, and this clearance is defined as A, between the taper surface 22a and the taper surface 25. Is provided with a predetermined clearance. When this clearance is B, B ≧ A. The clearance B is a radial dimension from the outer diameter end of the outer flange portion 24a to the tapered surface 22a. For example, when A is about 0.5 mm to 1.2 mm, B is preferably about 0.7 mm to 2.0 mm.

  The two annular bodies 10 are made of this kind of commonly used resin having excellent wear resistance and seizure resistance, such as polyethylene, polyamide, polyacetal, polyethylene terephthalate, polybutylene terephthalate, polycarbonate, polyphenylene sulfide, poly It can be formed of a synthetic resin such as ether sulfone, polyether imide, polyamide imide, polyether ether ketone, thermoplastic polyimide, thermosetting polyimide, epoxy resin, or phenol resin. Furthermore, based on a thermoplastic resin such as polyamide, polyphenylene sulfide, or polyether ether ketone, a glass fiber added to improve strength and dimensional stability can be used.

  However, in the present invention, it is preferable to use a polyamide resin excellent in tensile elongation, tensile strength, impact resistance, wear resistance, lubricity and the like as the cage material of the cage 5. The polyamide resin may be PA66 (polyamide 66), PA46 (polyamide 46), PA9T (polyamide 9T), PA11 (polyamide 11), or PA6 (polyamide 6). . Thus, in the present invention, a polyamide resin excellent in tensile elongation, tensile strength, impact resistance, wear resistance, lubricity, etc. can be used as the cage material, and a high-quality cage can be provided. . The outer ring 3, the inner ring 2, and the ball 4 are made of a metal such as bearing steel or carburized steel.

  The grease filled in this ball bearing is a semi-solid lubricant comprising a base oil, a thickener and an additive. Examples of the base oil constituting the lubricating grease include mineral oils such as paraffinic mineral oil and naphthenic mineral oil, hydrocarbon synthetic oils such as polybutene, poly-α-olefin, alkylbenzene, alkylnaphthalene, and alicyclic compounds, or Natural oils and fats, polyol ester oils, phosphate esters, diester oils, polyglycol oils, silicone oils, polyphenyl ether oils, alkyl diphenyl ether oils, non-hydrocarbon synthetic oils such as fluorinated oils, etc. Any oil that is used can be used without particular limitation.

  Examples of the thickener include metal soap-based thickeners such as aluminum soap, lithium soap, sodium soap, composite lithium soap, composite calcium soap, and composite aluminum soap, and urea compounds such as diurea compounds and polyurea compounds. These thickeners may be used alone or in combination of two or more.

  Known additives for lubricating greases include, for example, extreme pressure agents, amine-based and phenol-based antioxidants, metal deactivators such as benzotriazole, viscosity index improvers such as polymethacrylate and polystyrene, and molybdenum disulfide. And solid lubricants such as graphite. These can be added alone or in combination of two or more.

  The cage 5 of the above embodiment includes the following coupling structure as means for coupling the two annular bodies 10. 4 to 7 for explaining the engagement structure, the illustration of the flange portions 24a and 24b is omitted for simplification of the drawing. For this reason, in the cage 5 shown in FIGS. 4 to 7, the flange portions 24 a and 24 b are actually formed.

  As shown in FIGS. 4 to 7, 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 portion 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. 4 and 6, 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 axially engaged 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 joint part 18 which consists of the outer diameter side convex part 13, the inner diameter side concave part 14, the inner diameter side convex part 15, and the outer diameter side concave part 16 at both ends in the circumferential direction 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 spaced apart from each other in the axial direction and the pocket 12 is opened, the above-described coupling portion 18 causes the ball 4 to be opened. Can be easily maintained in the pocket 12.

  In the coupling structure 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.

  Further, in this connection structure, as shown in FIGS. 10 and 11, the inner diameter side convex portion 15 is thicker than the outer diameter side convex portion 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.

  In the present invention, it is possible to form a relief portion of the lubricant on the inner side of the pocket by the concave grooves 19 and 20 reaching the cage outer diameter surface 10b from the cage inner diameter surface 10a. For this reason, in this ball bearing cage, the resistance when the lubricant passes through the pocket can be reduced, and the amount of oil film formed between the ball 4 and the pocket 12 can be reduced. The concave grooves 19 and 20 can reduce the torque of the bearing (ball bearing) using the cage 5. In addition, excess lubricant between the ball facing surface and the ball (hard sphere) 4 can be discharged from this area, and the influence of the excess lubricant on the torque can be eliminated. Furthermore, the provision of the concave grooves 19 and 20 makes it possible to discharge the foreign matter to the outside, making it difficult for the foreign matter to accumulate, and preventing the above-described problems caused by the foreign matter accumulation. In addition, since two annular bodies are used, deformation due to centrifugal force and dropout of the ball can be effectively prevented.

  By making the end surface 21 on the counter mating side of the annular body 10 into a flat shape, it is possible to reduce the stirring resistance of the lubricant and to further reduce the torque.

  By providing the outer flange portion 24a and the inner flange portion 24b, it is possible to restrict the inflow of the lubricant into the inside (inside the bearing) and prevent the lubricant from flowing out from the inside (inside the bearing). In particular, by setting B ≧ A, it is possible to discharge the foreign matter that tends to stay inside while preventing the lubricant from flowing out to the outside. Further, by using the outer diameter end of the outer ring 3 in the bearing axial direction and the outer diameter end of the outer flange portion as the tapered surface 22a, it is possible to improve the discharging action to the outside of the foreign matter. The taper angle α and the taper angle β are set to about 20 ° to 45 °, but “a foreign matter that stays inside while preventing the lubricant from flowing out to the outside can be discharged to the outside. Can be set within a range of 20 ° to 45 ° or even beyond this range.

  As the cage material, polyamide resin or the like excellent in tensile elongation, tensile strength, impact resistance, wear resistance, lubricity and the like can be used, and a high-quality cage can be provided.

  Next, the cage shown in FIGS. 12 and 13 is a reference example, and in this cage, a U-shaped concave groove 26 is provided on the inner peripheral surface of the pocket 12. That is, the U-shaped concave groove 26 includes a central body groove 26a extending along the circumferential direction of the pocket, and a secondary groove 26b that is connected to the end of the central body groove 26a and opens to the outer diameter surface 10a of the cage. It is what has.

  Even with such a U-shaped concave groove 26, a lubricant escape portion can be formed on the inside of the pocket. For this reason, there exists an effect similar to the holder | retainer shown to FIG. 2, FIG. The groove 26 may be a groove having a semicircular cross section, a semi-elliptical or rectangular cross section, or a V-shaped groove having a V-shaped cross section.

  Moreover, as a bearing, the notch surface of the circumferential notch 22 of the outer ring 3 may not be a tapered surface. That is, as shown in FIG. 14, the circumferential notch 22 of the outer ring 3 is also rectangular in cross section. For this reason, the outer diameter end of the outer flange portion 24 a is an end surface parallel to the axial direction corresponding to the notch surface 28 of the circumferential notch portion 22. Further, the clearance between the outer flange portion 24a and the inner diameter surface of the outer ring 3 (in this case, the notch surface 28 of the circumferential notch 22) is B, and the outer diameter surface of the inner flange portion 24b and the inner ring 2 (in this case, When the clearance between the circumferential cutout 23 and the cutout surface 23a) is A, B ≧ A. Also in this case, for example, when A is about 0.5 mm to 1.2 mm, B is preferably about 0.7 mm to 2.0 mm.

  For this reason, even in such a bearing, by providing the outer flange portion 24a and the inner flange portion 24b, the inflow of the lubricant into the inside (inside the bearing) is restricted, and the outside from the inside (inside the bearing) to the outside. This prevents the lubricant from flowing out. In particular, by setting B ≧ A, it is possible to discharge the foreign matter that tends to stay inside while preventing the lubricant from flowing out to the outside.

  The other configuration of the cage 5 shown in FIG. 14 is the same configuration as the cage 5 shown in FIG. 2, and the ball bearing shown in FIG. 1 has the same configuration as the ball bearing shown in FIG. The same parts (same members) as the cage 5 shown in FIG. 14 and the ball bearing shown in FIG. 1 are denoted by the same reference numerals as those in FIG. 1 and FIG.

  Thus, the cage according to the present invention can achieve both a resistance when the lubricant passes and a reduction in the amount of oil film to be sheared, and can reduce the torque. This cage for ball bearings If a bearing using is used in an automobile, it is possible to improve the fuel efficiency and to drive friendly to the environment. That is, this bearing is optimal for automobile transmissions.

  As described above, the embodiment of the present invention has been described. However, the present invention is not limited to the above-described embodiment, and various modifications are possible. The size, depth, and the like of the concave grooves 19, 20, 26 are used. Depending on the lubricant to be used, various changes can be made within a range in which both resistance when the lubricant passes and reduction in the amount of oil film to be sheared can be achieved. For this reason, the number of the concave grooves 19 provided on the inner peripheral surface of the pocket 12 is not limited to two, and may be one or three or more. Further, the groove 20 provided on each mating surface 11a of the annular body 10 is not limited to one, and may be two or more. Furthermore, the groove 20 may be provided on an arbitrary mating surface 11a without being provided on the entire mating surface 11a.

  In order to exert the functions of “the restriction of the inflow of the lubricant into the inside (inside the bearing) and the outflow of the lubricant from the inside (inside the bearing) can be prevented” as in the above embodiment, Although it is preferable to provide the flange portions 24a and 24b, either the outer flange portion 24a or the inner flange portion 24b may be omitted, or the both flange portions 24a and 24b may be omitted. In the case where the flange portions 24a and 24b are provided, the thickness, radial length, etc. of the flange portions 24a and 24b are set in consideration of the balance, strength, weight, clearances A and B, etc. during rotation. Conversely, the size, shape, and the like of the circumferential notches 22 and 23 are set in consideration of the thickness and radial length of the flanges 24a and 24b. The number of pockets 12 that hold the ball 3 can be arbitrarily increased or decreased.

  By the way, as described above, the cage of the present invention is optimal for a bearing cage for a transmission, but of course, the bearing is not limited to a transmission and can be used for various machines and mechanisms.

2 Inner ring 3 Outer ring 4 Ball 5 Cage 10 Annular body 11 Opposing surface 11a mating surface 12 Pockets 19, 20 Concave groove 22a Outer ring taper surface 24a Outer flange part 24b Inner flange part 25 鍔 Tapered surface 26 Concave groove 26a Central body groove 26b groove

Claims (8)

Resin which has hemispherical pockets that accommodate balls on a plurality of circumferentially facing surfaces on opposite surfaces of a pair of annular bodies facing in the axial direction, and the paired annular bodies are symmetrical and integrated in the circumferential direction A ball bearing cage made of
A concave groove is provided on the inner peripheral surface of the pocket of the annular body from the inner diameter surface of the cage to the outer diameter surface of the cage. A ball bearing cage characterized by having a concave groove extending from the inner diameter surface of the cage to the outer diameter surface of the cage.   The ball bearing retainer according to claim 1, wherein there are two concave grooves provided on the inner peripheral surface of the pocket.   The ball bearing retainer according to claim 1 or 2, wherein an end face of the annular body on the opposite side is flat.   The ball bearing cage according to any one of claims 1 to 3, wherein the cage material is any one of a polyamide resin, a polyether ether ketone resin, and a polyphenylene sulfide resin.   In a ball bearing comprising an inner ring, an outer ring, a ball interposed between the inner ring and the outer ring, and a cage that holds the ball, any one of claims 1 to 4 is provided in the cage. A ball bearing using the ball bearing cage according to claim 1.   An outer flange portion extending to the outer diameter side is provided on the outer diameter portion on the counter mating side of the annular body, and an inner flange portion extending to the inner diameter side is provided on the inner diameter portion on the counter mating side, and between the outer flange portion and the inner diameter surface of the outer ring. The ball bearing according to claim 5, wherein B ≧ A, where B is a clearance and A is a clearance between the inner collar portion and the outer diameter surface of the inner ring.   An outer flange portion extending toward the outer diameter side is provided at the outer diameter portion on the counter mating side of the annular body, and an inner flange portion extending toward the inner diameter side is provided at the inner diameter portion on the counter mating side. And an outer ring tapered surface that expands from the inner side in the axial direction toward the outer side in the axial direction, and an outer diameter end of the outer flange portion is a tapered surface that increases in diameter from the inner side in the axial direction toward the outer side in the axial direction. 6. B ≧ A, where B is a clearance between the tapered surface and the outer ring tapered surface, and A is a clearance between the inner collar portion and the outer diameter surface of the inner ring. The ball bearing described.   It is applied to a transmission, The ball bearing of any one of Claims 5-7 characterized by the above-mentioned.

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