Rotary bearing

Abstract

DC60 (22 / 12 / 57) The provided bearing is a rotating bearing that includes an inner rail (12) and an outer rail (14). It can rotate relative to each other a certain number of rotating parts (15) that have been inserted. Insert the fastener (16) that is positioned between the inner rail (12) and the outer rail (14) into the space between the inner rails. The inner (12) and outer (14) rails are for securing a large number of rotating parts (15) at equal angles. The flange sections (20,21) are formed on the inner radially and on the outer radially. The radial line of the end of the fastener (16) to protrude radially and the groove received. The formation of an open recess (30,31) in one area of ​​the inner track (12) and the area One of the outer rails (14) aligns with each flange section (20,21) to form a meander (24, 25) together with the flange section (20,21), the surface of the inner surface (34,35) of the flange section (20, 21) and the surfaces at the axial ends (38,39) of the grooves that have been made into open recesses (30,31) which are located In contrast, the inner surface (34,35) of the flange section is tilted radially to create flow. of lubricants The bearings provided are rolling bearings, which include an inner rail (12) and an outer rail (14). Can rotate relative to each other, a certain number of rolling parts (15) have been inserted. Insert between the inner rail (12) and the outer rail (14). The fastener (16) is positioned between the inner rails. In (12) and the outer rail (14) for holding a large number of rolling parts (15) at equal angles. The flange sections (20,21) are formed on at least one side of the inner side along the line. The radius and the outside along the radius of the end of the fastener (16) to protrude as Along the radial and recessed grooves (30,31) that have been formed in one area. of the inner rail (12) and one area of ​​the outer rail (14) that corresponds to each flange section (20, 21) To form a winding shape (24,25) together with the flat front (20,21) surface of the inner surface (34, 35) of the flange sections (20,21) and the axial end surfaces (38,39) of the grooves that have been made. It is an open recess (30,31) opposite the inner surface (34,35) of the flange section, which is tilted accordingly. Radial direction to create lubricant flow;

Description

[0001] The present invention relates to a rolling bearing in which a cage made of synthetic resin that holds rolling elements so as to be able to roll is incorporated between an inner ring and an outer ring.

[0002] For example, various types of rolling bearings, such as deep groove ball bearings and angular contact ball bearings, are widely used for the gear support shafts of transmissions in vehicles equipped with engines.

[0003] This type of rolling bearing mainly consists of an inner ring with an inner rolling surface formed on its outer diameter surface, an outer ring positioned outside the inner ring with an outer rolling surface formed on its inner diameter surface, a plurality of rolling elements interposed between the inner rolling surface of the inner ring and the outer rolling surface of the outer ring so as to be able to roll, and a cage positioned between the inner ring and the outer ring to hold each rolling element at equal intervals in the circumferential direction. Either the inner ring or the outer ring is mounted on a fixed part such as a housing, and the other is mounted on a rotating part such as a rotating shaft.

[0004] When using this rolling bearing, various types of rolling bearings have been proposed, including one equipped with means to promote the inflow of lubricant into the bearing (see, for example, Patent Document 1) and another equipped with means to restrict the inflow of lubricant into the bearing (see, for example, Patent Document 2).

[0005] The rolling bearing disclosed in Patent Document 1 has a structure in which a raceway consisting of an outer ring and an inner ring is arranged concentrically, a plurality of rolling elements are interposed between them, an annular sealing member is arranged to seal the internal space formed by the outer ring, the inner ring and the rolling elements, and the sealing member is provided with an intake portion having a hole that connects the outside of the bearing and the inside of the bearing.

[0006] In this rolling bearing, the rotation of the sealing member accompanying the rotation of the inner and outer rings is used to draw lubricant from outside the bearing into the bearing through the intake holes of the sealing member. With this configuration, lubricant can be taken into the bearing without the need to provide a separate special lubrication device for pressurizing the lubricant or to install lubrication holes in the raceway surface, thereby ensuring good rotational performance at high speeds.

[0007] Furthermore, the rolling bearing disclosed in Patent Document 2 has a structure in which a small guide gap is provided between the inner and outer rings and the cage, the end face of the cage on the lubricant inlet side is an inclined surface, and the inner diameter surface of the cage is also an inclined surface.

[0008] In this rolling bearing, a slight guiding clearance is provided between the inner and outer rings and the cage, and by making the end face on the lubricant inflow side of the cage an inclined surface, it is possible to suppress the excessive drawing-in of the lubricant into the bearing. Further, by making the inner diameter surface of the cage an inclined surface, the lubricant that has flowed excessively into the bearing is actively discharged to the outside of the bearing.

[0009] Japanese Patent Application Laid-Open No. 2002-266876, WO2009 / 131139A1

[0010] By the way, in the rolling bearing disclosed in Patent Document 1, since a seal member is prepared as a separate part and it is necessary to form a hole that communicates the outside and inside of the bearing, the processing cost of the seal member increases and the assembly man-hours of the seal member increase. Further, the lubricant drawn into the bearing is agitated by the rolling elements and the cage inside the bearing, and as the rotational speed of the bearing increases, the lubricant drawn into the bearing tends to concentrate on the outer diameter side inside the bearing due to centrifugal force. The lubricant drawn in excessively in this way generates stirring resistance, and the inner diameter side becomes partially lubrication-deficient. In particular, there is a possibility that the torque (heat generation) of the bearing becomes significantly large under high-speed rotation.

[0011] Further, in the rolling bearing disclosed in Patent Document 2, even in a structure in which a slight guiding clearance is provided between the inner and outer rings and the cage and the end face on the lubricant inflow side of the cage is an inclined surface, since there is a linear path through which the lubricating oil flows in from the outside of the bearing, the suppressing effect on the inflow of the lubricant into the bearing is limited. Further, in the case of a structure in which the inner diameter surface of the cage is an inclined surface in order to actively discharge the lubricant, since the wall thickness varies greatly in the axial direction around the pocket portion that is not a continuous annular shape in the circumferential direction, the influence of non-uniform cage deformation due to centrifugal force cannot be ignored under high-speed rotation.

[0012] Therefore, the present invention has been proposed in view of the above problems, and an object thereof is to provide a rolling bearing that can supply an appropriate amount of lubricant from the outside of the bearing to the inside of the bearing and discharge the high-temperature lubricant from the inside of the bearing to the outside of the bearing with a simple structure.

[0013] As a technical means to achieve the above-mentioned objective, the present invention provides a rolling bearing comprising an inner ring and an outer ring that rotate relative to each other, a plurality of rolling elements interposed between the inner ring and the outer ring, and a cage disposed between the inner ring and the outer ring that holds the rolling elements at equal intervals in the circumferential direction, wherein a radially extending flange is provided on at least one of the inner diameter side or outer diameter side of the axial end of the cage, and a groove is provided in a portion of the inner ring or outer ring corresponding to the flange, forming a labyrinth with the flange, and at least one of the inner surface of the flange or the axial end surface of the groove facing the inner surface of the flange is inclined with respect to the radial direction to generate a flow of lubricating oil. In other words, the present invention focuses on the flow of lubricating oil and the labyrinth structure formed by the flange and the groove, and by appropriately combining the structures of both, it is possible to intentionally generate a flow of lubricating oil without separately providing a sealing member with an intake portion having a hole that connects the outside of the bearing and the inside of the bearing.

[0014] The phrase "at least one of the inner diameter side or the outer diameter side" includes all cases in which the flange is provided only on the inner diameter side, only on the outer diameter side, or on both the inner and outer diameter sides. The phrase "at least one of the inner surface of the flange or the axial end face of the groove facing the inner surface of the flange" includes all cases in which only the inner surface of the flange is inclined, only the axial end face of the groove facing the inner surface of the flange is inclined, or both the inner surface of the flange and the axial end face of the groove facing the inner surface of the flange are inclined.

[0015] In the present invention, a radially extending flange is provided on at least one of the inner diameter side or outer diameter side of the axial end of the cage, and a groove is provided in the part of the inner ring or outer ring corresponding to the flange, forming a labyrinth with the flange, and at least one of the inner surface of the flange or the axial end surface of the groove facing the inner surface of the flange is inclined with respect to the radial direction, so that the labyrinth formed by the flange and the groove restricts the flow of lubricant with the inclined surface which is the inner surface of the flange or the axial end surface of the groove. With such a simple structure, an appropriate amount of lubricant can be supplied from outside the bearing to inside the bearing, and high-temperature lubricant can be discharged from inside the bearing to outside the bearing. As a result, the inflow of foreign matter and excessive lubricant from outside the bearing to inside the bearing can be prevented, and foreign matter contained in high-temperature lubricant can be quickly discharged.

[0016] In the present invention, in order to supply an appropriate amount of lubricant from outside the bearing to inside the bearing and to discharge high-temperature lubricant from inside the bearing to outside the bearing, it is desirable that the flow of lubricant, which flows in from outside the bearing to inside the bearing and out from inside the bearing to outside the bearing, through the labyrinth formed by the flange and groove, be in the direction in which the lubricant flows in from the inner diameter side of the cage and out to the outer diameter side.

[0017] In the present invention, when the flow of the lubricant is such that the lubricant flows in from the inner diameter side of the retainer and flows out to the outer diameter side, it is desirable to have a structure in which the inner surface of the flange located on the inner diameter side at both axial ends of the retainer is inclined to expand radially inward, and the axial end faces of the grooves located at both axial ends of the outer ring are inclined to expand radially inward.

[0018] In the present invention, in order to supply an appropriate amount of lubricant from outside the bearing to inside the bearing and to discharge high-temperature lubricant from inside the bearing to outside the bearing, it is desirable that the flow of lubricant, which flows in from outside the bearing to inside the bearing and out from inside the bearing to outside the bearing, through the labyrinth formed by the flange and groove, be in a direction in which the lubricant flows in from one axial end of the cage and out to the other axial end.

[0019] In the present invention, when the flow of the lubricant is such that the lubricant flows in from one axial end of the retainer and flows out to the other axial end, it is desirable to have a structure in which the inner surface of the flange located on the inner diameter side of one axial end of the retainer is inclined to expand radially inward, the inner surface of the flange located on the outer diameter side of one axial end of the retainer is inclined to expand radially inward, the inner surface of the flange located on the outer diameter side of the other axial end of the retainer is inclined to expand radially outward, and the axial end surface of the groove located at the other axial end of the outer ring is formed in a direction perpendicular to the axial direction.

[0020] In the present invention, it is desirable that the axial thickness of the flange portion be 0.15 mm or more and 20% or less of the diameter of the rolling element. By restricting the axial thickness of the flange portion to the above range, the strength of the flange portion can be ensured, the molding of the flange portion becomes easier, and the axial dimensions of the bearing do not increase. If the axial thickness of the flange portion is less than 0.15 mm, insufficient strength of the flange portion and molding defects are likely to occur, and if it is greater than 20% of the diameter of the rolling element, the axial dimensions of the inner and outer rings increase along with the axial dimensions of the cage, resulting in a larger bearing.

[0021] In the present invention, it is preferable that the retainer has a structure in which hemispherical pockets for housing rolling elements are formed at multiple locations in the circumferential direction on the opposing surfaces of two annular bodies facing each other in the axial direction, and the two annular bodies are joined by bringing their opposing surfaces into contact. By adopting such a structure, when centrifugal force is applied under high-speed rotation, the two annular bodies constituting the retainer can suppress each other's deformation, thereby suppressing deformation of the entire retainer and preventing the rolling elements from falling out of the pockets or interfering with other parts such as inner and outer rings.

[0022] The holder in the present invention is effectively made of synthetic resin in terms of weight reduction. Furthermore, considering cost and oil resistance, it is desirable that the holder be molded from one of the synthetic resins selected from PPS, PA66, or PA46.

[0023] When the retainer in the present invention has a structure in which two asymmetrical annular bodies are joined together, it is desirable that the annular bodies be of different colors. This makes identification easier and ensures that the flow of lubricating oil is reliably directed in the intended direction.

[0024] According to the present invention, a radially extending flange is provided on at least one of the inner diameter side or outer diameter side of the axial end of the cage, and a groove is provided in the part of the inner ring or outer ring corresponding to the flange, forming a labyrinth with the flange, and at least one of the inner surface of the flange or the axial end surface of the groove facing the inner surface of the flange is inclined radially to generate lubricant flow, thereby reducing costs without increasing the number of parts or assembly steps. Furthermore, an appropriate amount of lubricant can be supplied from outside the bearing to inside the bearing, and high-temperature lubricant can be discharged from inside the bearing to outside the bearing, thereby preventing an increase in bearing torque (heat generation) under high-speed rotation. In addition, the inflow of foreign matter and excessive lubricant from outside the bearing to inside the bearing can be prevented, and foreign matter contained in high-temperature lubricant can be quickly discharged, thereby extending the lifespan of the rolling bearing. As a result, a rolling bearing suitable for automotive applications, such as high-speed bearings used in electric vehicles and hybrid vehicles, can be provided.

[0025] This is a partial cross-sectional view showing a rolling bearing in an embodiment of the present invention. This is a partial cross-sectional view showing a rolling bearing in another embodiment of the present invention. This is a cross-sectional view of the cage of Figure 1 showing two annular bodies before joining. This is a cross-sectional view of the cage of Figure 1 showing two annular bodies after joining. This is a cross-sectional view of the cage of Figure 2 showing two annular bodies before joining. This is a cross-sectional view of the cage of Figure 2 showing two annular bodies after joining. This is an enlarged cross-sectional view of a key part showing part A of Figure 1. This is an enlarged cross-sectional view of a key part showing part B of Figure 1. This is an enlarged cross-sectional view of a key part showing part C of Figure 2. This is an enlarged cross-sectional view of a key part showing part D of Figure 2. This is an enlarged cross-sectional view of a key part showing part E of Figure 2.

[0026] Embodiments of the rolling bearing according to the present invention will be described in detail below. The rolling bearing of this embodiment is particularly suitable for high-speed bearings in automotive applications used under oil bath lubrication in electric vehicles and hybrid vehicles. Figure 1 shows one embodiment of the present invention, and Figure 2 shows another embodiment of the present invention.

[0027] As shown in Figures 1 and 2, the rolling bearing of each embodiment mainly consists of an inner ring 12 having an inner rolling surface 11 formed on its outer diameter surface, an outer ring 14 positioned outside the inner ring 12 and having an outer rolling surface 13 formed on its inner diameter surface, a plurality of rolling elements 15 interposed between the inner rolling surface 11 of the inner ring 12 and the outer rolling surface 14 of the outer ring 13 so as to be rotatable, and a cage 16 positioned between the inner ring 12 and the outer ring 13 to hold each rolling element 15 at equal intervals in the circumferential direction. Either the inner ring 12 or the outer ring 13 is mounted on a fixed part such as a housing, and the other is mounted on a rotating part such as a rotating shaft.

[0028] This rolling bearing is equipped with a lightweight synthetic resin cage 16 in order to suppress deformation of the cage 16 due to centrifugal force at high speed rotation. Considering cost and oil resistance, it is effective to mold the cage 16 with one of the synthetic resins selected from PPS (polyphenylene sulfide), PA66 (polyamide 66), or PA46 (polyamide 46). In addition, other resin materials such as PA9T (polyamide 9T), PEEK (polyether ether ketone), and phenolic resin can also be used.

[0029] Figures 3A and 3B show the retainer 16 of Figure 1, and Figures 4A and 4B show the retainer 16 of Figure 2. These retainers 16 have a shape in which hemispherical pockets 19 for housing rolling elements 15 (see Figures 1 and 2) are formed at multiple locations in the circumferential direction on the opposing surfaces 18 of two annular bodies 17 that face each other in the axial direction, and the two annular bodies 17 are joined by a connecting part (not shown) by abutting the opposing surfaces 18 of the annular bodies 17. The two annular bodies 17 suppress each other's deformation, thereby suppressing deformation of the entire retainer 16 and preventing the rolling elements 15 from falling out of the pockets 19 or interfering with other parts such as the inner ring 12 and outer ring 13.

[0030] When using this rolling bearing under oil bath lubrication, it is equipped with a simple structure that supplies an appropriate amount of lubricant from outside the bearing to inside the bearing, and discharges high-temperature lubricant from inside the bearing to outside the bearing. In other words, as shown in Figures 1 and 2, flanges 20 to 23 extending in the radial direction are provided on both the inner diameter side and the outer diameter side of the axial end of the cage 16, and grooves 30 to 33 are provided in the inner ring 12 and outer ring 14 in the parts corresponding to the flanges 20 to 23, forming labyrinths 24 to 29 with the flanges 20 to 23, and the inner surfaces 34 to 37 of the flanges 20 to 23 or the inner and outer ring axial end faces 38 to 41 facing the inner surfaces 34 to 37 of the flanges of the grooves 30 to 33 are inclined with respect to the radial direction. In this way, by appropriately inclining the axial end faces 38-41 of the inner and outer rings and the inner surfaces 34-37 of the flange, it is possible to intentionally generate a flow of lubricating oil.

[0031] The grooves 30 and 32 on the inner ring side are formed by recessing the outer diameter axial end of the inner ring 12 in a stepped manner, and the grooves 31 and 33 on the outer ring side are formed by recessing the inner diameter axial end of the outer ring 14 in a stepped manner. Furthermore, since the labyrinths 24 to 29 are formed by the flanges 20 and 23 integrally provided on the annular body 17 and the grooves 30 to 33 integrally formed on the inner ring 12 and outer ring 14, only the shape of the retainer 16 and the inner ring 12 and outer ring 14 needs to be changed, thus reducing the number of parts and assembly man-hours and making cost reduction easier.

[0032] The embodiment shown in Figure 1 illustrates a structure that supplies an appropriate amount of lubricant from outside the bearing to inside the bearing and discharges high-temperature lubricant from inside the bearing to outside the bearing, in which the lubricant flows from outside the bearing to inside the bearing and out from inside the bearing to outside the bearing via labyrinths 24, 25 formed by flanges 20, 21 and grooves 30, 31, in a direction in which the lubricant flows in from the inner diameter side of the retainer 16 and out toward the outer diameter side (radial direction).

[0033] In this embodiment of the rolling bearing in which the lubricant flow is radial, the inner surface 34 of the flange portion 20 located on the inner diameter side at both axial ends of the cage 16 is inclined to expand radially inward, and the axial end faces 39 of the grooves 31 located at both axial ends of the outer ring 14 are inclined to expand radially inward. In this case, the inner surface 34 and 35 of the flange portions 20 and 21 located at both axial ends of the cage 16 are inclined to expand radially around their entire circumference. Because the cage 16 has a symmetrical shape, when centrifugal force is applied under high-speed rotation, the two annular bodies 17 constituting the cage 16 suppress each other's deformation, thereby suppressing deformation of the entire cage 16 and preventing the rolling elements 15 from falling out of the pockets 19 or interfering with other parts such as the inner ring 12 and outer ring 14.

[0034] In this embodiment, the axial end faces 39 of the grooves 31 located at both axial ends of the outer ring 14 that face the inner surfaces 35 of the flanges are inclined to widen radially inward (the axial end faces 39 of the grooves 31 are parallel to the inner surfaces 35 of the flanges 21), but the axial end faces 39 may be shaped to extend in a direction perpendicular to the axial direction. Similarly, the axial end faces 38 of the grooves 30 located at both axial ends of the inner ring 12 that face the inner surfaces 34 of the flanges are inclined to widen radially outward (the axial end faces 38 of the grooves 30 are parallel to the inner surfaces 34 of the flanges 20), but the axial end faces 38 may be shaped to extend in a direction perpendicular to the axial direction.

[0035] When centrifugal force is applied under high-speed rotation, the lubricant flows into the bearing through a labyrinth 24 formed by the flange 20 located on the inner diameter side of the cage 16 and the groove 30 of the inner ring 12, as shown by the arrows in Figure 1, due to the pumping action of centrifugal force, and flows out to the outside of the bearing through a labyrinth 25 formed by the flange 21 located on the outer diameter side of the cage 16 and the groove 31 of the outer ring 14.

[0036] In the labyrinth 24 (see Figure 1) formed by the flange portion 20 located on the inner diameter side of the retainer 16 and the groove 30 of the inner ring 12, as shown in Figure 5, the lubricant flows radially outward due to centrifugal force under high-speed rotation (see dashed arrow in the figure). At this time, since the inner surface 34 of the flange portion 20 is inclined to expand radially inward, the lubricant flows along the inner surface 34 of the flange portion 20, resulting in a lubricant flow as shown by the solid arrow in the figure.

[0037] In addition, in the labyrinth 25 (see Figure 1) formed by the flange 21 located on the outer diameter side of the retainer 16 and the groove 31 of the outer ring 14, as shown in Figure 6, the lubricant flows radially outward due to the centrifugal force under high-speed rotation (see dashed arrow in the figure). At this time, since the axial end face 39 of the groove 31 of the outer ring 14 is inclined to expand radially inward, the lubricant flows along the axial end face 39 of the groove 31, resulting in a lubricant flow as shown by the solid arrow in the figure.

[0038] The embodiment shown in Figure 2 is a structure that supplies an appropriate amount of lubricant from outside the bearing to inside the bearing and discharges high-temperature lubricant from inside the bearing to outside the bearing. It illustrates a case in which the flow of lubricant, which flows from outside the bearing to inside the bearing and out from inside the bearing to outside the bearing, is such that the lubricant flows in from one axial end of the cage 16 and out to the other axial end (axial direction). In this case, the lubricant flows from the right side to the left side in the figure, but if it is to flow from the left side to the right side in the figure, the flanges 20 to 23 of the cage 16 should be arranged in a reversed position.

[0039] In this embodiment of the rolling bearing with the lubricant flow axially directed, the inner surface 34 of the flange 20 located on the inner diameter side of one axial end of the cage 16 is inclined to expand radially inward, the inner surface 36 of the flange 22 located on the outer diameter side of one axial end of the cage 16 is inclined to expand radially inward, the inner surface 35 of the flange 21 located on the outer diameter side of the other axial end of the cage 16 is inclined to expand radially outward, and the axial end surface 41 of the groove 33 located on the outer diameter side of the other axial end of the outer ring 14 is formed in a direction perpendicular to the axial direction. In this case, the cage 16 has a structure in which two asymmetrical annular bodies 17 are joined together, but by making the colors of each annular body 17 different, identification becomes easy and the flow of lubricant can be reliably directed in the intended direction. Furthermore, this does not reduce the workability in the manufacture of the cage 16. Furthermore, the inner surface 37 of the flange portion 23 located on the inner diameter side of the other axial end of the retainer 16 is shaped to extend in a direction perpendicular to the axial direction.

[0040] In this embodiment, the axial end faces 40 facing the inner surfaces 34 and 37 of the flanges of the grooves 32 located at both axial ends of the inner ring 12 are shaped to extend in a direction perpendicular to the axial direction, but the axial end faces 40 may be inclined to widen radially outward. Similarly, the axial end faces 41 facing the inner surfaces 35 and 36 of the flanges of the grooves 33 located at both axial ends of the outer ring 14 are shaped to extend in a direction perpendicular to the axial direction, but the axial end faces 41 may be inclined to widen radially inward.

[0041] When centrifugal force is applied under high-speed rotation, the lubricant flows into the bearing interior by being drawn in by the centrifugal pump action from the labyrinth 26 formed by the flange 20 located on the inner diameter side of the cage 16 and the groove 32 of the inner ring 12, as shown by the arrows in Figure 2. It also flows into the bearing interior by being drawn in by the centrifugal pump action from the labyrinth 27 formed by the flange 22 located on the outer diameter side of the cage 16 and the groove 33 of the outer ring 14, and flows out to the outside of the bearing by being drawn in by the centrifugal pump action from the labyrinth 29 formed by the flange 21 located on the outer diameter side of the cage 16 and the groove 33 of the outer ring 14.

[0042] In the labyrinth 26 (see Figure 2) formed by the flange portion 20 located on the inner diameter side of the retainer 16 and the groove 32 of the inner ring 12, as shown in Figure 7, the lubricant flows radially outward due to centrifugal force under high-speed rotation (see dashed arrow in the figure). At this time, since the inner surface 34 of the flange portion 20 is inclined to expand radially inward, the lubricant flows along the inner surface 34 of the flange portion 20, resulting in a lubricant flow as shown by the solid arrow in the figure.

[0043] Furthermore, in the labyrinth 27 (see Figure 2) formed by the flange portion 22 located on the outer diameter side of the retainer 16 and the groove 33 of the outer ring 14, as shown in Figure 8, when the lubricant flows radially outward due to centrifugal force under high-speed rotation, the inner surface 36 of the flange portion 22 is inclined to expand radially inward, causing the lubricant to come into contact with the inner surface 36 (see dashed arrow in the figure). As a result, the lubricant flows axially inward, resulting in the lubricant flow shown by the solid arrow in the figure.

[0044] Furthermore, in the labyrinth 29 (see Figure 2) formed by the flange portion 21 located on the outer diameter side of the retainer 16 and the groove 33 of the outer ring 14, as shown in Figure 9, when the lubricant flows radially outward due to the centrifugal force under high-speed rotation, the inner surface 35 of the flange portion 21 is inclined to expand radially outward, and the axial end face 41 of the groove 33 of the outer ring 14 is formed in a direction perpendicular to the axial direction. As a result, the gap between the inner surface 35 of the flange portion 21 and the axial end face 41 of the groove 33 of the outer ring 14 widens radially outward, so the lubricant hits the inner surface 35 of the flange portion 21 and flows radially outward along that inner surface 35 (see dashed arrow in the figure), resulting in a lubricant flow as shown by the solid arrow in the figure.

[0045] As described above in the embodiments (see Figures 1 and 2), radially extending flanges 20 to 23 are provided on the inner and outer diameter sides of the axial end of the retainer 16, and grooves 30 to 33 are provided in the inner ring 12 and outer ring 14 at the corresponding locations to the flanges 20 to 23, forming labyrinths 24 to 29 with the flanges 20 to 23. The inner surfaces 34 to 37 of the flanges 20 to 23 or the axial end surfaces 38 to 41 of the grooves 30 to 33 that face the inner surfaces 34 to 37 of the flanges are inclined with respect to the radial direction.

[0046] As a result, the labyrinths 24-29, which are composed of flanges 20-23 and grooves 30-33, restrict the flow of lubricant with the inclined surfaces that are the inner surfaces 34-37 of the flanges 20-23 or the axial end surfaces 38-41 of the grooves 30-33. With this simple structure, the flow of lubricant inside the cage 16 is directed so that the lubricant flows in from the inner diameter side of the cage 16 and out to the outer diameter side (radial direction), or so that the lubricant flows in from one axial end side of the cage 16 and out to the other axial end side (axial direction), thereby supplying an appropriate amount of lubricant (cooled lubricant) from outside the bearing to inside the bearing, and discharging high-temperature lubricant from inside the bearing to outside the bearing along with any unwanted foreign matter that has entered inside the bearing. In this way, the inflow of foreign matter and excessive lubricant from outside the bearing to inside the bearing can be prevented, and foreign matter contained in the high-temperature lubricant can be quickly discharged.

[0047] In this embodiment, as shown in Figure 1, the axial thickness t of the flange portions 20 to 23 is set to 0.15 mm or more, and to 20% or less of the diameter D of the rolling element 15. By restricting the axial thickness t of the flange portions 20 to 23 to the above range, the strength of the flange portions 20 to 23 can be ensured, the molding of the flange portions 20 to 23 can be made easier, and the axial dimension of the bearing does not increase. If the axial thickness t of the flange portions 20 to 23 is less than 0.15 mm, insufficient strength of the flange portions 20 to 23 and molding defects are likely to occur. Furthermore, if the axial thickness t of the flange portions 20-23 is greater than 20% of the diameter D of the rolling element 15, the axial dimensions (groove width) of the grooves 30-33 of the inner ring 12 and outer ring 14 must be increased to avoid the flange portions 20-23 of the cage 16 protruding from the bearing end face. This increases the axial dimensions of the inner ring 12 and outer ring 14, resulting in a larger overall bearing size.

[0048] In addition, the embodiments described above have described a case in which flanges 20 to 23 are provided on both the inner diameter side and the outer diameter side of the axial end of the retainer 16. However, the present invention is not limited thereto, and although not shown, flanges 20 to 23 may be provided on only one of the inner diameter side or the outer diameter side of the axial end of the retainer 16.

[0049] The present invention is not limited in any way to the embodiments described above, and can be implemented in various other forms without departing from the spirit of the invention. The scope of the present invention is indicated by the claims, and further includes all modifications within the meaning and scope of equivalents set forth in the claims.

Claims

1. A rolling bearing consisting of an inner and outer track that are relatively rotatable with each other; a number of rolling elements are inserted between the inner and outer tracks; fasteners are arranged between the inner and outer tracks to hold the rolling elements at equal angles; flanges are formed radially on at least one side of the inner end and radially on the outer end of the fastener to protrude radially; and recessed grooves are formed in one area of ​​the inner track corresponding to the flange or in one area of ​​the outer track corresponding to the flange to form a convoluted shape with the flange, where at least one surface of the inner surface of the flange and the axial end surface of the recessed groove opposite the inner surface of the flange are radially inclined to create lubricant flow;