JP5623312B2 - Ball bearing cage and ball bearing - Google Patents

Description

  The present invention relates to a ball bearing retainer that holds a ball in a freely rolling manner, and a ball bearing in which the retainer 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.

  In general, as shown in FIG. 27, the ball bearing includes an inner ring 51, an outer ring 52, a ball 53 interposed between the inner ring 51 and the outer ring 52, and a cage 54 that holds the ball 53. Prepare. Either the outer ring 52 or the inner ring 51 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. The resin crown type cage 54 is made of a resin excellent in wear resistance, lubricity and the like, and has a predetermined pitch along the circumferential direction on one end surface 56 in the axial direction of the annular cage body 55 as shown in FIG. And a pair of claw portions 58 and 58 projecting from the opening ends facing the circumferential direction of the recess 57 are provided, and the concave portion 67 and the pair of claw portions 58 and 58 provide a ball. A pocket 59 for storing 53 is formed.

  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 cage as shown in FIG. 27 has a shape that holds 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

  However, in grease lubrication, when grease is interposed between the ball and the raceway surface, torque increases due to shear resistance. For this reason, the torque (heat generation) countermeasure is insufficient only with the structure in which the annular body shape is symmetrical in the axial direction as in Patent Documents 1 to 5.

Incidentally, in the resin crown type retainer 54 shown in FIG. 12, the PCD (P _PCD ) of the pocket 7 and the PCD (B _PCD ) of the ball 53 stored in the pocket 59 are set to be the same as shown in FIG. Is done. Further, the ball diameter (D _B ) is smaller than the pocket diameter (D _P ).

  For this reason, the pocket 59 and the ball 53 have the relationship shown in FIG. That is, a gap is formed between the pocket edge portion 65 on the inner diameter side and the pocket edge portion 66 on the outer diameter side and the ball 53, and it is difficult to scrape off the grease adhering to the ball at the pocket edge portions 65 and 66. Grease is likely to be interposed between the running surface and between the ball and the rolling surface of the outer ring, which may increase the torque.

  Therefore, in view of such circumstances, the present invention intends to provide a ball bearing retainer and a ball bearing that are effective for high-speed rotation even with grease lubrication.

A first ball bearing retainer according to the present invention has hemispherical pockets for accommodating balls on a plurality of circumferential surfaces of two annular bodies facing each other in the axial direction, and the opposed surfaces are abutted against each other. A ball bearing retainer in which two annular bodies are joined, and the outer diameter side between adjacent pockets of one annular body is extended in the axial direction to form an outer diameter-side convex portion. The inner diameter side corresponding to 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 to form the inner diameter side convex portion. In addition, the outer diameter side concave portion is formed by denting the outer diameter side facing 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 changed to the inner diameter side concave portion. engaged in the axial direction and the radial direction of the outer diameter side protruding portion and the inner diameter side protruding portion by inserting the outer diameter side protruding portion and the inner diameter-side convex The engagement surface 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 part and the inner diameter side convex part, and the pocket PCD is stored in the pocket. It is set smaller than the PCD.

  According to the first ball bearing retainer of the present invention, by engaging the outer diameter side convex portion and the inner diameter side convex portion in the axial direction, the outer diameter side convex portion and the inner diameter side convex portion are engaged. A frictional force is generated along the surface. 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.

  According to the first ball bearing retainer of the present invention, the pocket can be positioned on the inner diameter side with respect to the ball by setting the PCD of the pocket to be smaller than the PCD of the ball stored in the pocket. . As a result, the pocket edge portion on the outer diameter side comes close to the ball (the state in which the ball is held on the outer diameter side of the pocket), and the grease attached to the ball can be scraped off.

  When the PCD of the pocket is 0.9 to 0.99 of the PCD of the ball, the pocket diameter is preferably 1.06 times or less of the ball diameter. If it exceeds 1.06 times, the pocket diameter may become too large and play may occur.

  When the PCD of the pocket is 0.9 to 0.99 of the PCD of the ball, the pocket diameter is preferably 1.03 times or more of the ball diameter. If it is less than 1.03 times, the pocket diameter becomes too small, the gap between the ball and the pocket becomes small, and abnormal wear and stress may increase.

  It is preferable to provide a scraping structure portion for scraping the grease by contact or proximity with the ball on the outer diameter surface side of the cage. Thus, by providing the scraping structure portion, it is possible to scrape the grease adhering to the ball from the ball. For this reason, it is preferably used under grease lubrication.

The second ball bearing retainer of the present invention is formed by forming hemispherical pockets for accommodating balls in a plurality of locations in the circumferential direction on opposing surfaces of two annular members facing each other in the axial direction. A ball bearing retainer in which two annular bodies are joined, and the outer diameter side between adjacent pockets of one annular body is extended in the axial direction to form an outer diameter-side convex portion. The inner diameter side corresponding to 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 to form the inner diameter side convex portion. In addition, the outer diameter side concave portion is formed by denting the outer diameter side facing 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 changed to the inner diameter side concave portion. engaged in the axial direction and the radial direction of the outer diameter side protruding portion and the inner diameter side protruding portion by inserting the outer diameter side protruding portion and the inner diameter-side convex The PCD of the pocket and the ball stored in the pocket are inclined with respect to the axial direction so that the front end side is thicker than the base end side of the outer diameter side convex part and the inner diameter side convex part. And the inner surface of the pocket has an elliptical spherical shape in which a gap is formed between the ball outer diameter and the pocket inner surface .

  According to the second ball bearing cage of the present invention, as in the first ball bearing cage, the frictional force generated along the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion, Due to the synergistic action with the axial component of the reaction force generated in the normal direction of the engagement surface, the two annular bodies are separated in the axial direction even when a large centrifugal force is applied due to high rotation. This can be surely prevented.

  Further, when the pocket PCD and the ball PCD stored in the pocket are made the same, and the pocket diameter and the ball diameter are made the same, there is no gap between the pocket and the ball. However, by forming an elliptical spherical shape without making the pocket inner surface spherical, a gap can be secured between the pocket and the ball, and the grease can be scraped off by the pocket edge portion.

  A grease reservoir can be provided in the inner diameter portion and / or outer diameter portion on the opposite surface side of the annular body, or a grease reservoir can be provided in the inner diameter portion and / or outer diameter portion on the opposite surface side of the annular body. Thus, by providing the grease reservoir, the grease is accumulated in the grease reservoir, and the flow of grease to the rolling surface of the rolling element (ball) can be reduced. Thereby, the stirring resistance of grease can be reduced.

  A circumferential groove on the outer diameter surface may be provided. Even in this case, grease can accumulate in the circumferential groove and the grease flow to the rolling surface of the rolling element (ball) can be reduced.

  Even if it is shape | molded by cutting, it may be shape | molded by injection processing.

  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.

  The first and second ball bearing cages according to the present invention engage the outer diameter side convex portion with the inner diameter side convex portion by engaging the outer diameter side convex portion and the inner diameter side convex portion in the axial direction. The front end side of the frictional force generated along the mating surface and the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion is thicker than the proximal end side of the outer diameter side convex portion and the inner diameter side convex portion. By tilting with respect to the axial direction as described above, due to the synergistic action with the axial component of the reaction force generated in the normal direction of the engagement surface of the outer diameter side convex portion and the inner diameter side convex portion, Even when a large centrifugal force is applied, 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 particular, in the first cage for ball bearings, the pocket edge portion on the outer diameter side is close to the ball (the ball is held on the outer diameter side of the pocket), and the grease adhering to the ball is scraped off. Therefore, it is possible to obtain a torque reduction effect by grease lubrication.

  When the PCD of the pocket is 0.9 to 0.99 of the PCD of the ball, the pocket diameter is preferably 1.06 times or less of the ball diameter, and the PCD of the pocket is PCD of the ball Of 0.9 to 0.99, the pocket diameter is preferably 1.03 times or more of the ball diameter. If the ball diameter is 1.06 or less, backlash can be reduced and high-precision rotation can be obtained. If it is 1.03 times or more, there is no possibility that abnormal wear or stress will increase, and stable rotation can be obtained over a long period of time.

  In the second ball bearing cage, a clearance can be secured between the pocket and the ball, the ball rolling is stable, and grease can be scraped off at the pocket edge. Can be obtained.

  By providing the grease reservoir, the agitation resistance of the grease can be reduced and the torque can be further reduced.

  The ball bearing of the present invention can stably prevent separation of the two annular bodies while ensuring sufficient strength without increasing the number of parts and the number of assembling steps, and it can reduce the torque by grease lubrication. Can be obtained. For this reason, it is most suitable for the ball bearing for motor vehicles suitable for the high rotation bearing used in an electric vehicle or a hybrid vehicle.

The decomposition | disassembly state of the holder | retainer which shows embodiment of this invention is shown, (a) is the simplified front view of the expand | deployed state, (b) is a simplified sectional drawing. An annular body is shown, (a) is a plan view, and (b) is a front view. It is a perspective view of a pair of annular body before an assembly. It is an expanded view of a pair of annular body before an assembly. It is the sectional view on the AA line of the said FIG. It is the BB sectional view taken on the line of the said FIG. It is an expanded view of a pair of annular body after an assembly. 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 sectional drawing of the ball bearing using the said holder | retainer. It is a principal part top view which shows the relationship between a ball | bowl and a pocket. It is a simplified diagram showing the relationship between the ball PCD and the pocket PCD. It is an enlarged view which shows the relationship between a ball | bowl and a pocket. It is an enlarged view which shows the relationship between a ball | bowl and a pocket. It is a principal part enlarged view of the said FIG. It is an expanded view which shows the holder | retainer which provided the grease reservoir in the opposing surface side of the annular body. It is a principal part simplification top view of the holder | retainer which provided the grease reservoir in the internal diameter side of the opposing surface side of an annular body. It is a principal part simplification top view of the holder | retainer which provided the grease reservoir in the outer-diameter side of the opposing surface side of an annular body. It is an expanded view which shows the holder | retainer which provided the grease reservoir in the opposite surface side of the annular body. It is a principal part simplification top view of the holder | retainer by which the grease reservoir was provided in the inner diameter side in the opposite surface side of the annular body. It is a principal part simplified plan view of the holder | retainer in which the grease reservoir was provided in the outer-diameter side at the opposite surface side of the annular body. The annular body in which the circumferential direction groove | channel was provided in the outer-diameter surface is shown, (a) is an expanded view, (b) is sectional drawing. It is a principal part top view which shows the holder | retainer with the same pocket PCD and ball | bowl PCD. It is a principal part enlarged plan view which shows the holder | retainer with the same ball diameter and the curvature diameter of a pocket inner surface. It is a principal part enlarged plan view which shows the holder | retainer with the same ball diameter and the curvature diameter of a pocket inner surface. It is a principal part enlarged view of the said FIG. It is sectional drawing of the conventional ball bearing. It is a perspective view of the holder | retainer used for the conventional ball bearing. It is a principal part top view which shows the holder | retainer with the same pocket PCD and ball | bowl PCD. It is a simplified principal part enlarged view of the said 29 retainer.

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

  As shown in FIG. 10, the ball bearing 1 of this embodiment is arranged on the outer side of the inner ring 2 having the inner race surface 2a formed on the outer diameter surface, and on the outer side of the inner ring 2, and on the inner race surface 3a. 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 FIGS. 1 to 9, this type of retainer 5 has hemispherical pockets 12 that accommodate the 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. It forms and has the symmetrical shape which joined each two opposing bodies 11 by making each opposing surface 11 of the annular body 10 collide. The cage 5 of this embodiment includes the following coupling structure as means for coupling the two annular bodies 10.

  1, 3, and 4 show the two annular bodies 10 before joining, FIG. 5 is a cross section taken along line AA in FIG. 4, and FIG. 6 is a cross section taken along line BB in FIG. 4. is there. An outer diameter side between adjacent pockets 12 of one annular body 10 (see the left side in FIGS. 4 and 5) is extended in the axial direction to form an outer diameter side convex portion 13 and an inner diameter side is recessed to form an inner diameter. A side recess 14 is formed, and an inner diameter side convex portion 15 is formed by extending the inner diameter side between adjacent pockets 12 of the other annular body 10 (see the right side in FIGS. 2 and 3) in the axial direction. The outer diameter side recess 16 is formed by recessing the outer diameter side.

  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. 4 and 6) 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. 4 and 6) 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.

  FIG. 7 shows the two annular bodies 10 after joining, FIG. 8 is a cross section taken along the line CC in FIG. 7, and FIG. 9 is a cross section taken along the line DD in 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. 5 and 6) 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.

  In this coupling structure, as shown in FIGS. 8 and 9, 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 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. Thus, 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, a recess is formed as shown in FIGS.

  In this embodiment, the circumferential end of the pocket 12 of one annular body 10 (see the left side in FIG. 4) extends in the axial direction to form the tongue piece 19 and the other annular body 10 (FIG. 4). 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, The tongue piece 19 makes it easy to maintain the state in which the ball 4 is accommodated in the pocket 12 (see FIG. 7).

  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 are made of this kind of commonly used resins having excellent wear resistance and lubricity, such as polyethylene, polyamide, polyacetal, polyethylene terephthalate, polybutylene terephthalate, polycarbonate, polyphenylene sulfide, and polyether. It can be formed of synthetic resins such as sulfone, polyetherimide, polyamideimide, polyetheretherketone, thermoplastic polyimide, thermosetting polyimide, epoxy resin, and 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.

In the cage 5, the PCD of the pocket 12 is set smaller than the PCD of the ball 4 stored in the pocket 12. That is, as shown in FIGS. 11 and 12, when the pocket PCD is P _PCD and the ball PCD is B _PCD , P _PCD <B _PCD . In this case, PCD of the pocket 12, when a 0.9 to 0.99 of the ball PCD _(if a _{P PCD = 0.9B PCD ~0.99B PCD)} , the pocket diameter _{D P} to the ball diameter _{D B} and 1.06 times or less of, the pocket diameter _{D P} and above 1.03 times the ball diameter _{D B.}

  Here, as shown in FIG. 12, the pocket PCD is a length (diameter) that is twice the length (radius) from the R center (Rp) of the cage pocket to the center of the bearing. The ball PCD is a length (diameter) that is twice the length (radius) from the R center (RB) of the ball to the center of the bearing. By configuring the relationship between the ball 4 and the pocket 12 as described above, the pocket 12 can be positioned on the inner diameter side with respect to the ball 4 as shown in FIG. As a result, the pocket edge portion 41 on the outer diameter side comes close to the ball 4 (the state in which the ball 4 is held on the outer diameter side of the pocket), and the grease attached to the ball 4 can be scraped off. The pocket edge portion 42 on the inner diameter side is in a state of being separated from the ball 4, so that it is difficult to scrape off the grease adhering to the ball 4. Note that the arrows in FIG. 12 indicate the rotation direction of the ball 4.

By the way, as shown in FIG. 13, when the curvature diameter of the pocket inner surface is set larger than the ball diameter, a gap S is formed between the pocket edge portion 41 on the outer diameter side and the ball 4 as shown in FIGS. Can do. For this reason, it becomes difficult to scrape off the grease. That is, the radius of curvature of the pocket inner surface and R1, the radius of the ball 4 is taken as _{R B,} the R B <R1. Tsumashi, the diameter of curvature of the pocket inner surface and D1, the diameter of the ball 4 is taken as _{D B,} the D B <D1.

  Therefore, in the present invention, the PCD of the pocket 12 is set to be smaller than the PCD of the ball 4 stored in the pocket 12, and the pocket edge portion 41 on the outer diameter side is close to the ball 4 (the ball 4 is placed in the pocket). In this state, the grease adhering to the ball 4 can be scraped off.

  Thus, since it is preferable to scrape off the grease adhering to the ball 4, it is preferable to provide a scraping structure portion 50 for scraping off the grease by contact or proximity to the ball 4 as shown in FIG. . The scraping structure portion 50 in this case causes the outer diameter edge portion of the tongue piece portion 19 on the outer diameter side to slightly protrude from the outer diameter surface 11a of the annular body 11 to the outer diameter side. Accordingly, a scraping structure portion that scrapes off the grease attached to the ball 4 at the inner peripheral edge of the tongue piece portion 19 on the outer diameter side can be configured.

  In the present invention, by engaging the outer diameter side convex portion 13 and the inner diameter side convex portion 15 in the axial direction, along the engagement surfaces 13 a and 15 a of the outer diameter side convex portion 13 and the inner diameter side convex portion 15. The generated frictional force and 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 tip side than the proximal end sides of the outer diameter side convex portion 13 and the inner diameter side convex portion 15. With respect to the axial direction 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, Due to the synergistic action, even when a large centrifugal force is applied due to high rotation, it is possible to reliably prevent the two annular bodies 10 and 10 from separating in the axial direction.

As a result, it is possible to provide a ball bearing retainer that can reliably prevent the two annular bodies 10 and 10 from separating while ensuring sufficient strength without increasing the number of parts and the number of assembly steps. In addition, it is possible to provide a ball bearing for automobiles suitable for a high rotation bearing used in an electric vehicle or a hybrid vehicle.

  Further, since the pocket PCD is set smaller than the ball PCD stored in the pocket 12, the pocket 12 can be positioned on the inner diameter side with respect to the ball 4. As a result, the pocket edge portion 41 on the outer diameter side comes close to the ball 4 (the state in which the ball 4 is held on the outer diameter side of the pocket 12), and the grease adhering to the ball 4 can be scraped off. A torque reduction effect can be obtained by lubrication. In particular, by providing the scraping structure portion 50 as shown in FIG. 2, it is possible to stably scrape off the grease. In addition, since the pocket edge portion 42 on the outer diameter side is separated from the ball 4 and is difficult to be scraped off, it is difficult to leak grease.

When the pocket PCD is 0.9 to 0.99 of the ball PCD, the pocket diameter is preferably 1.06 times or less of the ball diameter, and the pocket PCD is 0.9 or less of the ball PCD. in case of a to 0.99, preferably pocket diameter _{D P} is greater than or equal to 1.03 times the ball diameter _{D B.} If 1.06 or less of the ball diameter D _B, can be made small backlash, obtaining the rotation precision. If it is 1.03 times or more, there is no possibility that abnormal wear or stress will increase, and stable rotation can be obtained over a long period of time.

  As described above, in the present invention, it is possible to provide a ball bearing provided with a cage that can obtain a torque reduction effect by grease lubrication and is effective for high-speed rotation.

  Incidentally, as shown in FIG. 16, the cage 5 is preferably provided with a grease reservoir 45 for collecting grease scraped off at the pocket edge portion 41 (see FIG. 12). The grease reservoir 45 is formed of a recess, and is provided between the pockets 12 adjacent in the circumferential direction on the opposite surface side in the figure. In this case, it may be provided on the inner diameter side as shown in FIG. 17 or on the outer diameter side as shown in FIG.

  Further, as shown in FIG. 19, a grease reservoir 45 may be provided on the opposite surface side. Also in this case, it may be provided on the inner diameter side as shown in FIG. 20, or may be provided on the outer diameter side as shown in FIG.

  Thus, by providing the grease reservoir 45, the grease is accumulated in the grease reservoir 45, and the flow of grease to the rolling surfaces 2a and 3a of the rolling element (ball) 4 can be reduced. Thereby, the stirring resistance of the grease can be reduced, and the torque can be further reduced.

  In FIG. 22, a circumferential groove 46 is provided on the outer diameter surface 10 a of the annular body 10. In this case, the circumferential groove 46 has a triangular cross section and is disposed at a position corresponding to the pocket 12. By providing such a circumferential groove 46, grease is accumulated in the circumferential groove 46, and the flow of grease to the rolling surfaces 2a and 3a of the rolling element (ball) 4 can be reduced. Thereby, the stirring resistance of the grease can be reduced, and the torque can be further reduced.

  By the way, the size of the grease reservoir 45 and the circumferential groove 46 can be variously changed according to the size of the cage itself, the material used, and the like. In this case, if it is too large, it will be inferior in strength, and if it is too small, the amount of grease will be small and the grease flow to the rolling surfaces 2a, 3a cannot be reduced. For this reason, it can change variously in the range which is not inferior in strength and can reduce grease flow.

By the way, in the cage shown in FIG. 23, the pocket PCD and the ball PCD stored in the pocket are made the same, and the curvature diameter and the ball diameter of the pocket inner surface are made the same as shown in FIGS. It is said. That is, when the pocket PCD is P _PCD and the ball PCD is B _PCD , P _PCD = B _PCD . Moreover, the radius of curvature of the pocket inner surface and R1, the radius of the balls and _{R B,} R = a _{R B} (the curvature diameter D1 of the pocket inner surface, the diameter _{D B} of the ball, and D1 = _{D B).}

However, if P _PCD = B _PCD and D1 = D _B as described above, no gap is formed between the ball outer diameter and the pocket inner surface as shown in FIG. If no gap is formed in this way, the rolling property of the ball 4 is inferior. Therefore, in this case, the inner surface of the pocket has an elliptical spherical shape.

  Thus, by making the pocket inner surface into an elliptical spherical shape instead of a spherical surface, a gap can be secured between the pocket 12 and the ball 4, and the ball rolling is stabilized. Moreover, grease can be scraped off by the pocket edge portion, and a torque reduction effect can be obtained by grease lubrication.

  The cage 5 may be made of metal such as carbon steel, spring steel, and stainless steel. The metal cage 5 is formed by cutting or the like. As in the embodiment, the resin cage 5 is molded by injection molding or the like. Thus, the cage 5 of the present invention can be made of various materials, and various molding methods can be adopted depending on the material used.

  The ball bearing of the present invention can stably prevent separation of the two annular bodies while ensuring sufficient strength without increasing the number of parts and the number of assembling steps, and it can reduce the torque by grease lubrication. Can be obtained. For this reason, it is most suitable for the ball bearing for motor vehicles suitable for the high rotation bearing used in an electric vehicle or a hybrid vehicle.

  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. For example, the number of pockets 12 for holding the ball 4 Can be increased or decreased arbitrarily. In addition, when the grease reservoir 45 is provided, it is provided between the pockets 12 adjacent to each other in the circumferential direction regardless of whether it is provided on the inner diameter side or the outer diameter side of the cage. Alternatively, it may be provided between any pockets 12.

2 Inner ring 4 Ball 5 Cage 10 Ring body 11 Opposing surface 12 Pocket 13 Outer diameter side convex portion 14 Inner diameter side concave portion 15 Inner diameter side convex portion 15a Engagement surface 16 Outer diameter side concave portion 45 Grease pool 50 Scraping structure

Claims (11)

A ball bearing in which hemispherical pockets for accommodating balls are formed at a plurality of circumferential locations on opposite surfaces of two annular members facing each other in the axial direction, and the two annular members are joined by abutting the opposed 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 portion, and the inner diameter side corresponding to the outer diameter side convex portion is recessed to form an inner diameter side concave portion. In addition, 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 opposed to the inner diameter side convex portion is recessed to the outer diameter side. A concave portion is formed, and the outer diameter side convex portion is inserted into the outer diameter side concave portion and the inner diameter side convex portion is inserted into the inner diameter side concave portion so that the outer diameter side convex portion and the inner diameter side convex portion are axially and radially engaged in direction, the outer engagement surfaces between the radially protruding portion and the inner diameter side protruding portion, the axial direction so that the tip side than the base end side of the outer diameter side protruding portion and the inner diameter side protruding portion becomes thick The ball bearing is characterized in that the PCD of the pocket is set smaller than the PCD of the ball stored in the pocket. The cage.   The ball bearing holder according to claim 1, wherein when the PCD of the pocket is 0.9 to 0.99 of the PCD of the ball, the pocket diameter is 1.06 times or less of the ball diameter. vessel.   The ball bearing retainer according to claim 1, wherein when the pocket PCD is 0.9 to 0.99 of the ball PCD, the pocket diameter is 1.03 times or more of the ball diameter. vessel.   The ball bearing holding according to any one of claims 1 to 3, wherein a scraping structure portion for scraping grease by contact or proximity to a ball is provided on the outer diameter surface side of the cage. vessel. A ball bearing in which hemispherical pockets for accommodating balls are formed at a plurality of circumferential locations on opposite surfaces of two annular members facing each other in the axial direction, and the two annular members are joined by abutting the opposed 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 portion, and the inner diameter side corresponding to the outer diameter side convex portion is recessed to form an inner diameter side concave portion. In addition, 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 opposed to the inner diameter side convex portion is recessed to the outer diameter side. A concave portion is formed, and the outer diameter side convex portion is inserted into the outer diameter side concave portion and the inner diameter side convex portion is inserted into the inner diameter side concave portion so that the outer diameter side convex portion and the inner diameter side convex portion are axially and radially engaged in direction, the outer engagement surfaces between the radially protruding portion and the inner diameter side protruding portion, the axial direction so that the tip side than the base end side of the outer diameter side protruding portion and the inner diameter side protruding portion becomes thick It is inclined with respect, and PCD pocket, with the same the PCD of the balls to be accommodated in the pocket, the pocket inner surface, Bo Le outer diameter and a cage for a ball bearing, characterized in that it has an elliptical spherical shape which gap is formed and the pocket inner surface.   The ball bearing retainer according to any one of claims 1 to 5, wherein a grease reservoir is provided in an inner diameter part and / or an outer diameter part on the opposite surface side of the annular body.   The ball bearing retainer according to any one of claims 1 to 5, wherein a grease reservoir is provided in an inner diameter portion and / or an outer diameter portion on the opposite surface side of the annular body.   The ball bearing retainer according to any one of claims 1 to 7, wherein a circumferential groove on the outer diameter surface is provided.   The ball bearing retainer according to any one of claims 1 to 8, wherein the ball bearing retainer is formed by cutting.   The ball bearing cage according to any one of claims 1 to 8, wherein the ball bearing cage is formed by injection processing.   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 10 is provided in the cage. A ball bearing using the ball bearing cage according to claim 1.

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