JP2023182960A - rolling bearing - Google Patents

Abstract

To provide a rolling bearing capable of being used for a long period by assembling a sliding member sliding on inner and outer rings into a holder.SOLUTION: A holder is a cage-type holder comprising a first annular body, a second annular body, and a plurality of columns, and rotates around a central axis m as a rolling element revolves. Either an outer periphery of an inner ring or an inner periphery of an outer ring has a first guide surface and a second guide surface on which a sliding member slides. The first annular body and the second annular body each comprise at least three sliding members, and any two sliding members that are directly adjacent to each other in a circumferential direction are arranged with a central angle of less than 180° around the central axis m.SELECTED DRAWING: Figure 1

Description

The present invention relates to large rolling bearings, and particularly to rolling bearings in which a cage is guided by an inner ring or an outer ring.

A rolling bearing includes an inner ring, an outer ring, rolling elements, and a cage. In outer ring rotating type rolling bearings, the inner ring is stationary and the outer ring rotates relative to the inner ring. When the outer ring rotates relative to the stationary inner ring, the rolling elements revolve around the inner ring. At this time, the cage holding the rolling elements rotates together with the rolling elements around the central axis of the inner ring.
A cage-shaped cage rotates while making sliding contact with the outer periphery of the inner ring and the inner periphery of the outer ring, so that the weight of the cage is supported by the inner ring and the outer ring, and the cage is rotated around the central axis of the inner ring and/or outer ring. There is a type that rotates. However, when this type of cage is used in large rolling bearings, the sliding speed between the inner or outer ring and the cage increases, resulting in increased wear on the cage, inner ring and/or outer ring, and sliding contact surfaces. There is a risk that problems such as image sticking may occur.
In order to deal with such problems, it is conceivable that the cage is manufactured from a material such as brass, which is a different metal from the bearing ring. However, in large rolling bearings, if the entire cage is made of expensive material such as brass, the cost of the cage increases. The cage disclosed in Patent Document 1 is a holding type in which an annular cage is divided into a plurality of segments in the circumferential direction, and a sliding member such as brass is welded to each segment and then assembled together. It is a vessel.

JP2020-094626A

In the cage of Patent Document 1, even if each segment is strained due to the heat during welding when sliding members are welded together, the cage as a whole can be prevented from being affected by the strain by bending at the joints of the segments. Can be made smaller.
However, if the cage body is made of an annular integral piece, there is a risk that the cage will be distorted by the heat effect during welding, making it impossible to fit it to the outer periphery of the inner ring or the inner periphery of the outer ring. . Therefore, it was considered that the sliding member could be fastened to the cage body with bolts, but the bolts would loosen after long-term use, and rolling bearings would become stuck with the bolts that fell off and become unable to rotate. There are concerns.

In view of the above circumstances, the present invention has been developed to prevent distortion caused by heat effects such as welding when assembling a sliding member to the cage body of a rolling bearing, and to prevent parts from falling off due to loosening of screws. The purpose of the present invention is to provide a rolling bearing that has excellent properties and can maintain good rotation over a long period of time.

The present invention provides an annular outer ring having an outer ring raceway surface on the inner periphery, an annular inner ring having an inner ring raceway surface on the outer periphery, and a plurality of rings arranged rollably between the inner ring raceway surface and the outer ring raceway surface. It includes a rolling element and an annular cage, and the cage includes a first annular body, a second annular body, and a plurality of columns that connect the first annular body and the second annular body in a substantially axial direction. , comprising at least three first sliding members and at least three second sliding members, the plurality of pillars being defined by the first annular body, the second annular body, and the two pillars adjacent to each other. A rolling bearing in which pockets are formed, the rolling elements are incorporated in each pocket, and the retainer rotates about a central axis m as the rolling elements revolve, wherein the outer periphery of the inner ring and the outer ring Either one of the inner peripheries has a first guide surface on a first side in the axial direction of the outer ring raceway surface or the inner ring raceway surface, and a second guide surface on the second side in the axial direction. ,
The at least three first sliding members are fixed to the inner periphery or outer periphery of the first annular body and slide on the first guide surface, and the at least three first sliding members are fixed to the inner periphery or outer periphery of the first annular body and slide on the first guide surface, and The moving members are arranged with a central angle smaller than 180° around the central axis m, and the at least three second sliding members are fixed to the outer periphery or inner periphery of the second annular body and Any two of the second sliding members that slide on the second guide surface and are directly adjacent to each other in the circumferential direction are characterized in that the central angle around the central axis m is smaller than 180°.

According to the present invention, when assembling a sliding member into a retainer of a rolling bearing, it is possible to prevent distortion due to heat effects such as welding, and prevent parts from falling off due to loosening of screws, resulting in excellent assembly performance and long-lasting performance. It is possible to provide a rolling bearing that can maintain rotation.

FIG. 1 is an axial cross-sectional view of a rolling bearing that is an embodiment of the present invention. FIG. 2(a) is a perspective view of the cage seen from the second annular body side, and FIG. 2(b) is a partially enlarged view of FIG. 2(a). FIG. 3 is an enlarged axial cross-sectional view of a region including a first annular body. 4(a) is a partial side view of the cage alone, and FIG. 4(b) is a plan view of the cage shown in FIG. 4(a) as viewed in the direction of the outlined arrow B. FIG. 3 is an enlarged axial cross-sectional view of a region including a second annular body. 6(a) is a partial side view of the cage alone, and FIG. 6(b) is a plan view of the cage shown in FIG. 4(a) as viewed in the direction of the outlined arrow D. FIG. 7 is an enlarged axial cross-sectional view of a region including a second annular body in another embodiment.

Embodiments of the present invention will be described in detail using figures.
FIG. 1 is an axial cross-sectional view of a rolling bearing 10 that is one embodiment (hereinafter referred to as "first embodiment") of the present invention. The rolling bearing 10 has an annular shape centered on the central axis m, and FIG. 1 shows one radial cross section.
The rolling bearing 10 is incorporated into a nacelle of wind power generation equipment and is used to rotationally support a main shaft on which a blade is mounted. In the rolling bearing 10 of the first embodiment, the outer diameter of the outer ring 11 is approximately 2500 mm, and the inner diameter of the inner ring 12 is approximately 2000 mm. Note that the size of the rolling bearing 10 is an example, and the present invention can be similarly applied to a rolling bearing having a diameter smaller or larger than the above dimensions. The present invention is particularly preferably applied to large bearings and extra large bearings.
In the following description, the direction parallel to the central axis m is the axial direction, the direction perpendicular to the central axis m is the radial direction, and the direction of rotation around the central axis m is the circumferential direction. Further, the left side of the figure is the first side in the axial direction, and the right side is the second side in the axial direction.

The rolling bearing 10 is a tapered roller bearing and includes an outer ring 11, an inner ring 12, a plurality of tapered rollers 13 (rolling elements), and a cage 14.

The outer ring 11 has an annular shape as a whole centered on the central axis m. The outer ring 11 is manufactured from a steel material such as chromium molybdenum steel (JIS G4053-2016 alloy steel for machine structures, for example, SCM430, SCM432, SCM435, SCM440, SCM445, etc.). Note that the steel types are examples, and are not limited to the steel types described here.

The outer ring 11 includes a bearing outer diameter surface 15, an outer ring back surface 16, an outer ring front surface 17, and an outer ring raceway surface 18.
The bearing outer diameter surface 15 is a cylindrical surface centered on the central axis m. The outer ring back surface 16 is connected to the first axial side of the bearing outer diameter surface 15 and extends radially inward in a direction perpendicular to the central axis m. The outer ring front surface 17 is connected to the second axial side of the bearing outer diameter surface 15 and extends radially inward in a direction perpendicular to the central axis m. The outer ring raceway surface 18 is a surface on which the tapered rollers 13 roll. The outer ring raceway surface 18 is a tapered surface whose diameter increases from the first axial side to the second axial side, and is part of a conical surface centered on the central axis m.

The inner ring 12 has an annular shape as a whole centered on the central axis m. The inner ring 12 is manufactured from a steel material such as chromium molybdenum steel (JIS G4053-2016 alloy steel for machine structures, for example, SCM430, SCM432, SCM435, SCM440, SCM445, etc.). Note that the steel types are examples and are not limited to the steel types described here.

The inner ring 12 includes a bearing inner diameter surface 21, an inner ring front surface 22, and an inner ring back surface 23, and has a small rib 24, an inner ring raceway surface 25, and a large rib 26 on the outer circumferential side.
The bearing inner diameter surface 21 is a cylindrical surface centered on the central axis m. The inner ring front face 22 is connected to the first axial end of the bearing inner diameter surface 21 and extends radially outward in a direction perpendicular to the central axis m, and extends from the axial first side of the small rib outer peripheral surface 24a. connected to the side edge. The inner ring back surface 23 is connected to the second axial end of the bearing inner diameter surface 21 and extends radially outward in a direction perpendicular to the central axis m, and is connected to the second axial end of the large rib outer peripheral surface 26a. connected to the side edge.

The inner ring raceway surface 25 faces the outer ring raceway surface 18 in the radial direction, and is a surface on which the tapered rollers 13 roll. The inner ring raceway surface 25 is a tapered surface whose diameter increases toward the second axial side, and is part of a conical surface centered on the central axis m.

The small flange 24 is formed on the first axial side of the inner ring raceway surface 25 and holds the tapered rollers 13. The small brim 24 includes a small brim outer circumferential surface 24 a (first guide surface) and a holding surface 27 . The small brim outer circumferential surface 24a is a cylindrical surface that is connected to the outer circumferential end of the inner ring front surface 22 and extends parallel to the central axis m toward the second axial side. The outer diameter of the small brim outer peripheral surface 24a is larger than the minimum diameter of the inner ring raceway surface 25. The roller holding surface 27 connects the second axial end of the small collar outer circumferential surface 24a and the first axial end of the inner ring raceway surface 25, and extends substantially in the radial direction.

The large rib 26 is formed on the second axial side of the inner ring raceway surface 25 to guide the tapered rollers 13 and to support mainly the thrust of the large end surface 31 of the tapered rollers 13 in the axial direction. The large brim 26 includes a large brim outer peripheral surface 26a (second guide surface) and a guide surface 32. The large brim outer circumferential surface 26a is a cylindrical surface that is connected to the outer circumferential end of the inner ring back surface 23 and extends parallel to the central axis m toward the first axial side. The outer diameter of the large brim outer peripheral surface 26a is larger than the maximum diameter of the inner ring raceway surface 25. The roller guide surface 32 connects the end of the large brim outer circumferential surface 26a on the first axial side and the end of the inner ring raceway surface 25 on the second axial side, and extends substantially in the radial direction.

The tapered rollers 13 are manufactured from bearing steel such as SUJ2. The tapered roller 13 has a substantially truncated cone shape and includes a small end surface 30, a large end surface 31, and a rolling surface 33. The rolling surface 33 is a tapered surface whose diameter increases from the small end surface 30 toward the large end surface 31, and is formed of a part of a conical surface centered on the central axis p. The small end surface 30 and the large end surface 31 are both side surfaces extending in a direction substantially perpendicular to the central axis p. The small end surface 30 is the small bottom surface of a truncated cone. The large end surface is the large base surface of the truncated cone.

The form of the retainer 14 will be explained with reference to FIG. FIG. 2(a) is a perspective view of the retainer 14 seen from the second annular body 37 side. FIG. 2(b) is a partially enlarged view of FIG. 2(a). The retainer 14 includes a first annular body 36 , a second annular body 37 , a plurality of columns 38 , a plurality of first sliding members 39 , and a plurality of second sliding members 40 . The cage main body 35 includes a first annular body 36, a second annular body 37, and a plurality of columns 38.
The cage body 35 is manufactured as a single piece by cutting a carbon steel material such as S25C. The plurality of first sliding members 39 are fixed to the inner periphery of the first annular body 36. The plurality of second sliding members 40 are fixed to the inner periphery of the second annular body 37.
The first annular body 36 and the second annular body 37 each have an annular shape centered on the central axis m, and the diameter of the first annular body 36 is smaller than the diameter of the second annular body 37. The first annular body 36 and the second annular body 37 are connected by a plurality of columns 38 extending substantially in the axial direction. Each pillar 38 extends along a plane including the central axis m, and is arranged at equal intervals in the circumferential direction.

The pocket 41 is a space sandwiched between the first annular body 36 and the second annular body 37 in the axial direction and between two adjacent columns 38 in the circumferential direction. The tapered rollers 13 are assembled into each pocket 41 one by one with the small end surfaces 30 facing the first annular body 36 side. The retainer 14 of the first embodiment has 80 pockets 41. Note that the number of pockets 41 is just an example, and can be increased or decreased as appropriate.
The distance L1 between the first annular body 36 and the second annular body 37 (see FIG. 2(b)) is the total length of the tapered roller 13 (the distance between the small end surface 30 and the large end surface 31 in the direction of the central axis p of the tapered roller 13). distance). Further, the tangential distance L2 between the columns 38 that define the pockets 41 (see FIG. 2(b)) is slightly larger than the distance of the tapered rollers that overlap this tangential distance L2. Therefore, the tapered rollers 13 can freely rotate around the central axis p inside the pocket 41.

Each column 38 has roller retainers 42 that protrude substantially in the radial direction at two locations in the axial direction. The roller retainer 42 is inclined toward the inside of the pocket 41 as it goes outward in the radial direction. The distance between the tips of the two roller retainers 42, 42 facing each other in the circumferential direction with the pocket 41 in between is smaller than the diameter of the tapered roller 13 at the axial position of the roller retainer 42. Therefore, the tapered rollers 13 can be assembled into the cage 14 from the radially inner side of the cage 14 (the side of the central axis m). The assembled tapered rollers 13 come into contact with the roller retainers 42 on the outside in the radial direction, so that they are prevented from passing through the pockets 41 and falling off in the outside in the radial direction.
Note that when the cage 14 and the tapered rollers 13 are assembled into the rolling bearing 10 (see FIG. 1), the tapered rollers 13 are separated from the retainers 42 in the radial direction. Therefore, when the rolling bearing 10 rotates, the tapered rollers 13 are not inhibited from rotating by the retainer 14. Further, when assembling the cage subassembly in which the tapered rollers 13 are assembled in each pocket 41 to the inner ring 12, the tapered rollers 13 are dislocated from the inner ring raceway surface 25 radially outward at the roller stopper 42. Since the tapered rollers 13 are held in contact with the small ribs 24, the tapered rollers 13 do not interfere with the small ribs 24. Further, after assembly, the tapered roller 13 does not get over the small rib 24 by making the distance between the tips of the two opposing retainers 42, 42 smaller by caulking the roller retainer 42 or the like.

Next, the first annular body 36 and the first sliding member 39 will be described in detail with reference to FIGS. 3 and 4.
FIG. 3 shows an axial cross section taken along a cross section including the first rivet 45 and the central axis m. In order to show the assembled state of the first rivet 45, the cross section of the first annular body 36 is cut along a plane parallel to the central axis m at the position XX in FIG. A cross section viewed in the direction is shown. The tapered roller 13 shows an axial cross section taken along a cross section including the first rivet 45 and the central axis m. FIG. 4(a) is a partial side view of the retainer 14 as viewed in the direction indicated by the outline arrow A in FIG. 3 at the circumferential position where the first sliding member 39 is assembled. FIG. 4(b) is a plan view of the retainer 14 of FIG. 4(a) viewed from the inside in the radial direction in the direction of the outlined arrow B. FIG.

The first sliding member 39 has a first main body 59 and two first rivets 45 (first rod-shaped parts), and the first main body 59 is firmly connected to the first annular body 36 by the first rivets 45. is fixed. As the first rivet 45, a round rivet with a spherical head defined in JIS B1213 (1995) is used, but other types of rivets such as a thin flat rivet or a pan rivet may be used. Further, the material of the first rivet 45 can be selected from various materials depending on usage conditions, such as carbon steel, stainless steel, copper, brass, and aluminum.
Note that in FIG. 4A, the first rivet 45 on the left side is shown in a state before being assembled to the first main body 59, and the first rivet 45 is inserted in the direction of arrow R.

See FIG. 3. The first annular body 36 has a first outer circumferential surface 48 , a first inner circumferential surface 49 , a second inner circumferential surface 50 , a first side surface 51 , and a second side surface 52 . The first annular body 36 is connected to a column 38. Therefore, the first outer circumferential surface 48 is continuous with the outer circumferential surface of the column 38, and the first inner circumferential surface 49 is continuous with the inner circumferential surface of the column 38. Further, at the position where the pocket 41 is formed in the circumferential direction, the end of the first outer circumferential surface 48 on the second axial side and the end of the first inner circumferential surface 49 on the second axial direction are connected to the pocket. They are connected on the inner side of 41. The first outer circumferential surface 48 and the first inner circumferential surface 49 are part of a conical surface centered on the central axis m, and each generatrix extends substantially parallel to the central axis p of the tapered roller 13. .
The second inner circumferential surface 50 is a cylindrical surface centered on the central axis m. The inner diameter of the second inner peripheral surface 50 is larger than the outer diameter of the small collar outer peripheral surface 24a, and a radial gap s1 is provided between the first annular body 36 and the small collar 24 of the inner ring 12. The first side surface 51 is a surface that extends in the radial direction, and connects the end of the first outer circumferential surface 48 on the first axial side and the end of the second inner circumferential surface 50 on the first axial direction. There is. The second side surface 52 is a surface that extends approximately in the radial direction, and includes an end on the first axial side of the first inner circumferential surface 49 and an end on the second axial side of the second inner circumferential surface 50. Connected.

As shown in FIG. 4(a), the first annular body 36 has a plurality of first grooves 54 for accommodating the first main body 59 on its inner periphery. The first groove portion 54 is a groove recessed radially outward from the second inner circumferential surface 50 and extends in the axial direction along the second inner circumferential surface 50 with a uniform cross-sectional shape. The first groove portions 54 are formed at six locations on the inner periphery of the first annular body 36 at equal intervals in the circumferential direction (see FIG. 2).
The first groove portion 54 is defined by a first groove bottom surface 54a, a first groove side surface 54b, and a second groove side surface 54c. The first groove bottom surface 54a is a plane parallel to the central axis m and perpendicular to a plane q that includes the central axis m and extends in the radial direction. The first groove side surface 54b and the second groove side surface 54c are parallel to the plane q and face each other in the circumferential direction with the plane q in between. The distance between the first groove side surface 54b and the plane q is equal to the distance between the second groove side surface 54c and the plane q.
The first groove bottom surfaces 54a of the first groove portions 54 formed at six locations are disposed at equal distances from each other from the central axis m.

The first annular body 36 is provided with two first through holes 56, 56 extending parallel to each other at the positions of the first grooves 54. The inner diameter of each first through hole 56 is slightly larger than the diameter of the shaft portion of the first rivet 45, so that the first rivet 45 can be easily inserted while suppressing its inclination. Each of the first through holes 56 extends in a direction perpendicular to the first groove bottom surface 54a, and penetrates the first annular body 36 in a substantially radial direction. The two first through holes 56, 56 are arranged at symmetrical positions with respect to the center position of the first groove bottom surface 54a.
The first through hole 56 is used for accommodating the first rivet 45 and fixing the first main body 59 to the first annular body 36 . In the first embodiment, two first through holes 56, 56 are provided, but the number of first through holes 56 may be one, or three or more. Even in this case, the one or more first through holes 56 are located at symmetrical positions with respect to the center position of the first groove bottom surface 54a so that the first main body 59 can be evenly pressed against the first groove bottom surface 54a. It is preferable that the

A first counterbore portion 57 is provided at the opening of the first through hole 56 on the first outer circumferential surface 48 side, recessed from the first outer circumferential surface 48 by a predetermined depth. The first counterbore portion 57 has a cylindrical shape with a bottom centered on the central axis n1 of the first through hole 56. The first bottom surface 57a of the first counterbore portion 57 is formed in a direction perpendicular to the central axis n1. The diameter of the cylindrical portion of the first counterbore portion 57 is larger than that of the first through hole 56, and the first through hole 56 opens into the first bottom surface 57a of the first counterbore portion 57.

Similarly, the first main body 59 will be explained with reference to FIG. The first main bodies 59 are fixed one by one to the first grooves 54 of the first annular body 36 with first rivets 45 . In the rolling bearing 10 of the first embodiment, the number of first bodies 59 is six, and each first body 59 has the same shape.
The first main body 59 has a substantially rectangular parallelepiped shape, and includes a first upper plane 60, a first sliding surface 61, a pair of circumferential side surfaces 62, 62, which are side surfaces on both sides in the circumferential direction, and a pair of axial side surfaces 63. It is equipped with 63.
The first upper plane 60 has a rectangular shape in plan view and is a plane that comes into contact with the first groove bottom surface 54a. The first sliding surface 61 is formed on the opposite side of the first upper plane 60 in the thickness direction. The first sliding surface 61 is a part of a cylindrical surface centered on the central axis m, and as shown in FIG. It has a slightly convex arc shape on the plane 60 side. The radius of curvature of the first sliding surface 61 is equivalent to the radius of curvature of the small rib outer peripheral surface 24a of the inner ring 12.

A pair of circumferential side surfaces 62, 62 are mutually parallel surfaces and are orthogonal to the first upper plane 60. The distance between the pair of circumferential side surfaces 62, 62 is equivalent to the distance between the first groove side surface 54b and the second groove side surface 54c of the first groove portion 54. In the first embodiment, the distance between the pair of circumferential side surfaces 62, 62 is set to about 2 to 5% of the inner circumference of the first annular body 36; , but is not limited to this. Since the contact surface pressure can be lowered by increasing the area of the first sliding surface 61, the distance between the pair of circumferential side surfaces 62, 62 is determined by the contact surface when the first main body 59 and the inner ring 12 make sliding contact. It can be changed as appropriate depending on usage conditions such as pressure and sliding speed.

The pair of axial side surfaces 63, 63 are mutually parallel surfaces, and are orthogonal to the first upper plane 60 and the pair of circumferential side surfaces 62. The axial distance between the pair of axial side surfaces 63, 63 is set to be approximately equal to the axial distance between the first side surface 51 and the second side surface 52 of the first annular body 36.

The first main body 59 is required to have a small coefficient of sliding friction when sliding on the inner ring 12 and the outer ring 11, and to have little wear even when used for a long period of time. Therefore, the material of the first body 59 is a metal material such as bronze or brass that is different from the material of the sliding counterpart (in this embodiment, it is iron-based), or a sintered material impregnated with oil or resin. In addition, solid lubricants such as molybdenum disulfide, graphite, and PTFE (polytetrafluoroethylene) can be used. Note that the first main body 59 may be made entirely of the above-mentioned material, and has a predetermined thickness including the first sliding surface 61 that makes sliding contact with the small collar outer peripheral surface 24a of the inner ring 12. Only the range may be made of the above material, and the other parts may be made of inexpensive carbon steel or the like.

The first main body 59 includes two second through holes 64 that extend in a direction perpendicular to the first upper plane 60 and penetrate in the thickness direction. The inner diameter of the second through hole 64 is equivalent to the inner diameter of the first through hole 56. The two second through holes 64 are arranged at positions corresponding to the two first through holes 56 provided in the first annular body 36, and the first body 59 is assembled to the first annular body 36. At this time, the first through hole 56 and the second through hole 64 communicate with each other with their central axes n1 aligned.

Further, a second counterbore portion 65 (first recess) is provided in the opening of the second through hole 64 on the first sliding surface 61 side, recessed from the first sliding surface 61 by a predetermined depth. There is. The second counterbore portion 65 has a cylindrical shape with a bottom centered on the central axis n1 of the second through hole 64. The second bottom surface 65a of the second counterbore portion 65 is formed in a direction perpendicular to the central axis n1. The diameter of the cylindrical portion of the second counterbore portion 65 is larger than that of the second through hole 64, and the second through hole 64 opens into the second bottom surface 65a of the second counterbore portion 65.

When fixing the first main body 59 to the first annular body 36, the first main body 59 is assembled into the first groove portion 54 with the first upper plane 60 in contact with the first groove bottom surface 54a. With the first body 59 in contact with the first annular body 36 on the radially inward opening side of the first through hole 56, the two first rivets 45 are inserted into the first sliding surface of the first body 59. It is inserted into the second through hole 64 from the 61 side.
Since the first through hole 56 and the second through hole 64 share a central axis and communicate with each other, the first rivet 45 protrudes from the first main body 59 and is housed inside the first through hole 56 . The first head 45a of the first rivet 45 is accommodated in the second counterbore 65.

The second counterbore portion 65 has a size that can accommodate the first head 45a of the first rivet 45. That is, the diameter of the cylindrical portion of the second counterbore portion 65 is larger than the diameter of the first head portion 45a, and the distance along the central axis n1 from the first sliding surface 61 of the second bottom surface 65a is greater than the diameter of the first head portion 45a. greater than the height of The first head 45a accommodated in the second counterbore 65 is not exposed outward from the first sliding surface 61. Preferably, the first head 45a is installed a predetermined distance away from the first sliding surface 61 in the direction of the central axis n1. Thereby, even if the first main body 59 is worn out due to long-term use, it is possible to reliably prevent the first head 45a from being exposed from the first sliding surface 61. The first head 45a of the first rivet 45 is not exposed from the first sliding surface 61 unless the first sliding surface 16 is excessively worn. Do not touch 24a directly. Damage and abrasion of the small brim outer circumferential surface 24a are prevented, and seizing between the first rivet 45 and the small brim outer circumferential surface 24a is prevented.

When the first head 45a of the first rivet 45 comes into contact with the second bottom surface 65a of the second counterbore 65, the shaft of the first rivet 45 moves toward the radially outer opening side of the first through hole 56. be exposed. When the exposed shaft portion is crushed using a press or the like, the end portion of the first rivet 45 is plastically deformed and becomes a first enlarged portion 58 whose diameter is expanded around the central axis n1. The first counterbore portion 57 has a size that can accommodate the first enlarged portion 58.

The first enlarged portion 58 comes into contact with the first bottom surface 57a of the first counterbore portion 57, which is the outer surface of the first annular body, and prevents the first rivet 45 from coming off. It is securely fixed to the annular body 36. FIG. 2B shows a state in which the first main body 59 is fixed to the inner circumference of the first annular body 36. As shown in FIG.
Note that the first annular body 36 has one or more first through holes 56, the first main body 59 has one or more second through holes 64 communicating with each of the first through holes 56, and one or more A plurality of first rivets 45 may be accommodated in each through hole 56, 64, respectively.

As shown in FIG. 4(a), when the first main body 59 is assembled into the first groove portion 54, the first sliding surface 61 protrudes radially inward from the second inner circumferential surface 50 and It is arranged at a distance from the axis m equal to the radius of curvature of the outer peripheral surface 24a of the small brim. Thereby, the first sliding surfaces 61 of the six first bodies 59 as a whole constitute a single cylindrical surface having the same diameter as the small brim outer circumferential surface 24a.

The assembled state of the second annular body 37 and the second sliding member 40 will be described with reference to FIG. 5. FIG. 5 is an axial cross-sectional view similar to FIG. 3 in which a region including the second annular body 37 is enlarged. The tapered roller 13 shows an axial cross section taken along a cross section that includes the second rivet 45 and the central axis m.
The second sliding member 40 has a second main body 78 and two second rivets 46 (second rod-shaped parts), and the second main body 78 is firmly connected to the second annular body 37 by the second rivets 46. Fixed. Since the assembled state of the second sliding member 40 is similar to the assembled state of the first sliding member 39 in the first annular body 36, the common configuration will be briefly described. Note that the second rivet 46 has the same form as the first rivet 45.

The second annular body 37 includes a second outer circumferential surface 67 , a third outer circumferential surface 68 , a third inner circumferential surface 69 , a fourth inner circumferential surface 70 , a third side surface 71 , and a fourth side surface 72 .
The second annular body 37 is connected to the pillar 38. Therefore, the second outer circumferential surface 67 is continuous with the outer circumferential surface of the column 38, and the third inner circumferential surface 69 is continuous with the inner circumferential surface of the column 38. The second outer circumferential surface 67 and the third inner circumferential surface 69 are part of a conical surface centered on the central axis m, and each generatrix extends substantially parallel to the central axis p of the tapered roller 13. . Further, at the position where the pocket 41 is formed in the circumferential direction, the end of the second outer circumferential surface 67 on the first axial side and the end of the third inner circumferential surface 69 on the first axial direction are connected to the pocket. They are connected on the inner side of 41.
The third outer circumferential surface 68 is a cylindrical surface centered on the central axis m, and is connected to the end of the second outer circumferential surface 67 on the second axial side. The fourth inner circumferential surface 70 is a cylindrical surface centered on the central axis m. The inner diameter of the fourth inner circumferential surface 70 is larger than the outer diameter of the large rib outer circumferential surface 26a, and a radial gap s2 is provided between the second annular body 37 and the large rib 26 of the inner ring 12.
The third side surface 71 extends approximately in the radial direction and connects the second axial end of the third inner circumferential surface 69 and the first axial end of the fourth inner circumferential surface 70. I'm here. The fourth side surface 72 extends approximately in the radial direction and substantially connects the second axial end of the third outer circumferential surface 68 and the second axial end of the fourth inner circumferential surface 70 . Connected radially. Note that the third outer circumferential surface 68 and the fourth side surface 72 are connected by a slightly large chamfer.

FIG. 6(a) is a partial side view of the retainer 14 as viewed in the direction shown by the outline arrow C in FIG. 5 at the circumferential position where the second sliding member 40 is assembled. FIG. 6(b) is a plan view of the retainer 14 of FIG. 6(a) viewed from the inside in the radial direction in the direction of the outlined arrow D.
The second annular body 37 has a plurality of second grooves 74 for accommodating the second main body 78 on its inner periphery. The second groove portion 74 is a groove recessed radially outward from the second inner circumferential surface 50 and extends in the axial direction along the fourth inner circumferential surface 70 with a uniform cross-sectional shape. The second groove portion 74 is defined by a second groove bottom surface 74a, a third groove side surface 74b, and a fourth groove side surface 74c. The second groove portions 74 are formed at six locations on the inner periphery of the second annular body 37 at equal intervals in the circumferential direction (see FIG. 2). The second groove bottom surfaces 74a of the respective second groove portions 74 are disposed at equal distances from each other from the central axis m.

Like the first annular body 36, the second annular body 37 includes two third through holes 75 at the positions of each second groove portion 74. The inner diameter of the third through hole 75 is slightly larger than the diameter of the shaft portion of the second rivet 46, so that the second rivet 46 can be easily inserted while suppressing its inclination. The third through hole 75 extends in a direction perpendicular to the second groove bottom surface 74a and penetrates the second annular body 37 in a substantially radial direction. The third through hole 75 is used to accommodate the shaft portion of the second rivet 46 and to fix the second main body 78 to the second annular body 37 . Therefore, the number of third through holes 75 may be one, or may be three or more.

The third counterbore portion 76 is provided at the opening of the third through hole 75 on the third outer circumferential surface 68 side, recessed from the third outer circumferential surface 68 by a predetermined depth. The third counterbore portion 76 has a cylindrical shape with a bottom centered on the central axis n2 of the third through hole 75. The third bottom surface 76a of the third counterbore portion 76 is formed in a direction perpendicular to the central axis n2.

The second main body 78 will be explained. The second main body 78 has a substantially rectangular parallelepiped shape, and includes a second upper plane 79, a second sliding surface 80, a pair of circumferential side surfaces 81, 81, which are side surfaces on both sides in the circumferential direction, and a pair of axial side surfaces 83, It is equipped with 83.

The second sliding surface 80 is a part of a cylindrical surface centered on the central axis m, and as shown in FIG. It has a slightly convex arc shape toward the plane 79. The radius of curvature of the second sliding surface 80 is equivalent to the radius of curvature of the large brim outer peripheral surface 26a of the inner ring 12.
The pair of circumferential side surfaces 81, 81 are parallel to each other, and the distance between the pair of circumferential side surfaces 81, 81 is equivalent to the distance between the first groove side surface 54b and the second groove side surface 54c of the first groove portion 54. . Further, the distance between the pair of circumferential side surfaces 81, 81 is set to about 2 to 5% of the inner circumference of the second annular body 37, but the distance between the pair of circumferential side surfaces 81, 81 is limited to this. It is not something that will be done.
The pair of axial side surfaces 83, 83 are parallel surfaces to each other, and the axial distance thereof is set to be approximately equal to the axial distance between the third side surface 71 and the fourth side surface 72 of the second annular body 37. has been done.
Further, the material of the second body 78 is selected from the materials that can be selected from the materials of the first body 45. What is the form of each part? Since it is the same as the first main body 59, the explanation will be omitted.

The second main body 78 includes two fourth through holes 84 that extend in a direction perpendicular to the second upper plane 79 and penetrate in the direction of the plate thickness. The inner diameter of the fourth through hole 84 is equivalent to the inner diameter of the third through hole 75. When the second main body 78 is assembled to the second annular body 37, the third through hole 75 and the fourth through hole 84 communicate with each other with their central axes aligned.

Further, a fourth counterbore portion 85 (second recess) is provided in the opening of the fourth through hole 84 on the second sliding surface 80 side, recessed from the second sliding surface 80 by a predetermined depth. There is. The fourth counterbore portion 85 has a cylindrical shape with a bottom centered on the central axis n2 of the fourth through hole 84. The fourth bottom surface 85a of the fourth counterbore portion 85 is formed in a direction perpendicular to the central axis n2.

When fixing the second main body 78 to the second annular body 37, the second main body 78 is assembled into the second groove portion 74 in such a direction that the second upper plane 79 and the second groove bottom surface 74a are in contact with each other. With the second body 78 in contact with the second annular body 37 on the radially inward opening side of the third through hole 75, the two second rivets 46 are inserted into the second sliding surface of the second body 78. It is inserted into the fourth through hole 84 from the 80 side.
Since the third through hole 75 and the fourth through hole 84 share a common central axis and communicate with each other, the second rivet 46 protrudes from the second main body 78 and is accommodated inside the third through hole 75 . The second head 46a of the second rivet 46 is accommodated in the fourth counterbore 85.

The fourth counterbore portion 85, like the second counterbore portion 65, is sized to accommodate the second head 46a of the second rivet 46. Therefore, unless the second sliding surface 80 is excessively worn, the second head 46a accommodated in the fourth counterbore 85 is not exposed to the outside of the second sliding surface 80. Preferably, the second head 46a is installed a predetermined distance away from the second sliding surface 80 in the direction of the central axis n2. In this way, the second head 46a of the second rivet 46 does not directly contact the outer peripheral surface 26a of the large brim of the inner ring 12. Damage and abrasion of the large brim outer circumferential surface 26a are prevented, and seizing between the second rivet 46 and the large brim outer circumferential surface 26a is prevented.

When the second head 46a of the second rivet 46 comes into contact with the fourth bottom surface 85a of the fourth counterbore portion 85, the shaft portion of the second rivet 46 is exposed to the radially outer opening side of the third through hole 75. do. When the exposed shaft portion is crushed by a press or the like, the end portion of the second rivet 46 is plastically deformed and becomes a second enlarged portion 77 whose diameter is expanded around the central axis n2. The third counterbore portion 76 has a size that can accommodate the second enlarged portion 77.

The second enlarged portion 77 comes into contact with the third bottom surface 76a of the third counterbore portion 76, which is the outer surface of the second annular body 37, and prevents the second rivet 46 from coming off. It is securely fixed to the two-ring body 37. FIG. 2(b) shows a state in which the second main body 78 is fixed to the inner periphery of the second annular body 37.
Note that the second annular body 37 has one or more third through holes 75, the second main body 78 has one or more fourth through holes 84 communicating with each of the third through holes 75, and one or more A plurality of second rivets 46 may be accommodated in each communication hole 75, 84, respectively.

As shown in FIG. 6(a), when each second main body 78 is assembled into the second groove portion 74, the second sliding surface 80 protrudes radially inward from the fourth inner circumferential surface 70, and It is arranged at a position equal to the radius of curvature of the outer peripheral surface 26a of the large brim from the central axis m. Thereby, the six second sliding surfaces 80 as a whole constitute a single cylindrical surface having the same diameter as the large brim outer circumferential surface 26a.

Moreover, each sliding member 39, 40 has a distance between a pair of circumferential side surfaces 62, 62, 81, 81, and a distance between groove side surfaces 54b, 54c, 74b, 74c on both circumferential sides defining each groove portion 54, 74. It may be made slightly larger and assembled into the respective grooves 54, 74 with an interference fit in the circumferential direction. By assembling the slide members 39 and 40 in a tightly fitted state, the circumferential movement of each sliding member 39 and 40 is suppressed relative to each annular body 36 and 37, so loosening of the rivets 45 and 46 can be more reliably prevented. It is from.

The assembly procedure of the rolling bearing 10 will be explained.
In the retainer 14 of the first embodiment, six sliding members 39 and 40 are fixed to the inner periphery of the first annular body 36 and the second annular body 37, respectively. Thereafter, the retainer 14 to which the respective sliding members 39 and 40 are attached is placed with the second annular body 37 facing upward and its central axis directed in the vertical direction. In this state, the plurality of tapered rollers 13 are assembled into each pocket 41 one by one. A cage 13 in which a plurality of tapered rollers 13 are assembled is a cage subassembly. At this time, each tapered roller 13 is assembled at a position closer to the outside in the radial direction so as to come into contact with the roller retainer 42. Thereafter, the inner ring 12 is axially assembled with its central axis aligned with the central axis of the retainer subassembly. The tapered rollers 13 are arranged on the inner ring raceway surface 25 beyond the small ribs 24. Further, after assembly, the tapered roller 13 does not get over the small rib 24 by making the distance between the tips of the two opposing retainers 42, 42 smaller by caulking the roller retainer 42 or the like.

In the retainer 14 of the first embodiment, the first main body 59 and the second main body 78 are fixed to the first annular body 36 and the second annular body 37 using rivets 45 and 46, respectively. Therefore, compared to the conventional method of manufacturing a cage in which the cage is fixed by welding, the process of attaching the sliding members 39 and 40 to the cage 14 body does not have any thermal effect on the cage 14 body, so the cage 14 is significantly reduced, and the strains of the first annular body 36 and the second annular body 37 are suppressed. Therefore, the sliding surfaces 61 and 80 of each sliding member 39 and 40 can maintain a state in which they constitute a single cylindrical surface more than in a conventional retainer.
Therefore, when the retainer subassembly and the inner ring 12 are assembled, the inner circumference of the first annular body 36 can be easily fitted to the outer circumference of the small collar 24, and the inner circumference of the second annular body 37 can be easily fitted to the outer circumference of the small collar 24. It is fitted onto the outer periphery of the large collar 26. The combination of cage subassembly and inner ring 12 is a cone assembly.

The outer ring 11 is then axially assembled to the cone assembly. In this way, the rolling bearing 10 shown in FIG. 1 is completed. In the rolling bearing 10, a plurality of tapered rollers 13 are arranged so as to be able to roll between an inner ring raceway surface 25 and an outer ring raceway surface 18. In the retainer 14, the first annular body 36 is disposed radially outward of the small rib 24 along the small end surface 30 of the plurality of tapered rollers 13, and the second annular body 37 is disposed along the small end surface 30 of the plurality of tapered rollers 13. The tapered rollers 13 are disposed radially outward along the large end surfaces 31 of the plurality of tapered rollers 13 .

When the inner ring 12 and the outer ring 11 rotate relative to each other, the tapered rollers 13 roll on the respective raceway surfaces 18 and 25 and revolve around the central axis m. Since the tapered rollers 13 are housed in the pockets 41 of the cage 14, the cage 14 rotates together with the tapered rollers 13 about the central axis m. At this time, the cage 14 and the inner ring 12 rotate relative to each other, so the first sliding member 39 slides on the small rib outer circumferential surface 24a, and the second sliding member 40 slides on the large rib outer circumferential surface 26a. do.
The sliding surfaces 61 and 80 of each sliding member 39 and 40 are made of a material with a low coefficient of sliding friction and little wear, thus preventing wear and seizure of the sliding contact surface between the cage 14 and the inner ring 12. Thus, the rolling bearing 10 can maintain good rotation over a long period of time.

In the first embodiment, the first sliding member 39 and the second sliding member 40 are arranged at six locations on the inner periphery of the first annular body 36 and the second annular body 37, respectively. However, the present invention is not limited to this, and the number of each sliding member 39, 40 is three or more, and the number of sliding members 39, 40 is 3 or more, and It is sufficient if the central angle is smaller than 180°. Here, "directly adjacent in the circumferential direction" means that in the first annular body 36, there is no other first sliding member 39 between any two selected first sliding members 39, 39; In the second annular body 37, there is no other second sliding member 40 between any two selected second sliding members 40, 40. "The central angle around the central axis m of two sliding members directly adjacent in the circumferential direction" is the side on which no other sliding member 39, 40 exists for any two selected sliding members 39, 40. is the central angle at . As a result, the central axis m is arranged inside the polygon connecting each first sliding member 39 in a plane orthogonal to the central axis m, and the central axis m is arranged in a plane orthogonal to the central axis m. It is arranged inside the polygon connecting each second sliding member 40. Therefore, the first annular body 36 and the small brim 24 are arranged to share a central axis, and the second annular body 37 is arranged to share a central axis m with the large brim 26. The container 14 can rotate with the outer ring 11 and the inner ring 12 sharing a central axis.

In addition, in the first embodiment, each sliding member 39, 40 and each annular body 36, 37 are connected with rivets 45, 46, so as in the case of screw fastening, the structure of bolts, nuts, etc. does not have. Therefore, the rolling bearing 10 can maintain good rotation over a long period of time by preventing problems such as parts falling off due to loosening of screws and falling parts getting caught.

Furthermore, the embodiments described above are merely examples, and the present invention can be modified in various ways.
A second embodiment of the present invention will be described. Each sliding member 39, 40 of the rolling bearing 10 of the first embodiment has a main body 59, 78 of the sliding member assembled to each annular body 36, 37, and a rivet 45, 46 is inserted from the inside in the radial direction. On the other hand, the rolling bearing 10 of the second embodiment is characterized in that the main body of the sliding member (hereinafter referred to as the third main body 87) and the rod-shaped portion (hereinafter referred to as the third rod-shaped portion 88) are integrally combined. It's different.

FIG. 7 shows an axial cross-sectional view of the second annular body 37, similar to FIG. 5, for the retainer 14 of the second embodiment. Components that are common to the first embodiment are given the same numbers. Note that the aspect of the first annular body 36 is similar to that of the second annular body 37, so a description of the first annular body 36 will be omitted.

The third body 87 has a similar form to the second body 78. One end of the third rod-shaped portion 88 protrudes from the third main body 87, and the one end has a cylindrical shape similar to the shaft of the second rivet 46. The other end of the third rod-shaped portion 88 is integrally formed with the third main body 87 by insert molding or casting. The other end of the third rod-shaped portion 88 has a shape that is larger than the one end, such as a cylindrical shape or a rectangular parallelepiped shape. Thereby, the third rod-shaped portion 88 is firmly held so that it does not easily tilt relative to the third main body 87. Note that the other end of the third rod-shaped portion 88 may have the same form as the second head 46a of the second rivet 46.

When fixing the third main body 87 to the second annular body 37, the third rod-shaped portion 88 is inserted into the third through hole 75. When the third main body 87 abuts the second annular body 37 on the radially inner opening side of the third through hole 75, one end of the third rod-shaped portion 88 radially outside the third through hole 75. exposed on the open side. When the exposed one end is crushed with a press or the like, the tip of the third rod-shaped portion 88 is plastically deformed and becomes a third enlarged portion 89 whose diameter is expanded around the central axis n2. In FIG. 7, the third rod-shaped portion 88 before being plastically deformed is shown with a broken line, and the third enlarged portion 89 is shown with a solid line. The third enlarged portion 89 comes into contact with the third bottom surface 76a of the third counterbore portion 76, which is the outer surface of the second annular body 37, and prevents the third rod-shaped portion 88 from coming off. It is securely fixed to the second annular body 37. Note that the third main body 87 and the third rod-shaped portion 88 may be integrally formed of a single material.

As can be understood from the above description, the rolling bearing 10 of each embodiment prevents distortion due to heat effects such as welding when assembling the sliding member to the cage 14 that makes sliding contact with the inner ring 12 or outer ring 11. Since components are prevented from falling off due to loosening of screws, the retainer 14 can be easily assembled and can maintain good rotation over a long period of time.

While the rolling bearing 10 of each embodiment was a rolling bearing 10 incorporated in a wind power generator, the rolling bearing of the present invention can be used in applications not limited to this use. The rolling bearing of the present invention may be applied, for example, to a swivel seat bearing used in iron and steel casting equipment, a rolling bearing that supports the main shaft of a tunnel excavator, and the like.
Further, in the rolling bearing 10 of this embodiment, the present invention is applied to a tapered roller bearing, and the sliding member assembled to the cage is in sliding contact with the outer periphery of the inner ring. However, the rolling bearing of the present invention is not limited to this configuration, and may be used in a cylindrical roller bearing or a self-aligning roller bearing. When used in these bearings, rolling bearings are not limited to configurations in which the sliding member makes sliding contact with the outer periphery of the inner ring. The member may be configured to make sliding contact with the inner circumferential surface of the outer ring.

10: Rolling bearing, 11: Outer ring, 12: Inner ring, 13: Tapered rollers, 14: Cage, 15: Bearing outer diameter surface, 16: Outer ring back surface, 17: Outer ring front surface, 18: Outer ring raceway surface, 21: Bearing inner diameter Surface, 22: Inner ring front, 23: Inner ring back, 24: Small rib, 24a: Small rib outer circumferential surface, 25: Inner ring raceway surface, 26: Large rib, 26a: Large rib outer circumferential surface, 27: Holding surface, 30: Small End face, 31: Large end face, 32: Roller guide surface, 33: Rolling surface, 36: First annular body, 37: Second annular body, 38: Pillar, 39: First sliding member, 40: Second sliding Moving member, 41: pocket, 42: roller retainer, 45: first rivet, 45a: first head, 46: second rivet, 46a: second head, 48: first outer peripheral surface, 49: first Inner peripheral surface, 50: Second inner peripheral surface, 51: First side surface, 52: Second side surface, 54: First groove portion, 54a: First groove bottom surface, 54b: First groove side surface, 54c: Second groove side surface , 56: first through hole, 57: first counterbore, 57a: first bottom surface, 58: first enlarged section, 59: first main body, 60: first upper plane, 61: first sliding surface, 62 : Circumferential side surface, 63: Axial side surface, 64: Second through hole, 65: Second counterbore, 65a: Second bottom surface, 67: Second outer circumferential surface, 68: Third outer circumferential surface, 69: Third inner surface Peripheral surface, 70: Fourth inner peripheral surface, 71: Third side surface, 72: Fourth side surface, 74: Second groove portion, 74a: Second groove bottom surface, 74b: Third groove side surface, 74c: Fourth groove side surface, 75: third through hole, 76: third counterbore, 76a: third bottom surface, 77: second enlarged portion, 78: second main body, 79: second upper plane, 80: second sliding surface, 81: Circumferential side surface, 82: Axial side surface, 84: Fourth through hole, 85: Fourth counterbore, 85a: Fourth bottom surface, 87: Third main body, 88: Rod-shaped portion, 89: Third enlarged portion

Claims (7)

an annular outer ring having an outer ring raceway surface on the inner periphery; an annular inner ring having an inner ring raceway surface on the outer periphery; and a plurality of rolling elements rollably disposed between the inner ring raceway surface and the outer ring raceway surface; Equipped with an annular retainer,
The retainer includes a first annular body, a second annular body, a plurality of columns that connect the first annular body and the second annular body in a substantially axial direction, and at least three first sliding members; at least three second sliding members, a plurality of pockets are defined by the first annular body, the two pillars adjacent to the second annular body, and each pocket is provided with a plurality of pockets, each of which is provided with a plurality of pockets. A rolling bearing in which a moving body is incorporated and the cage rotates around a central axis m as the rolling body revolves,
Either one of the outer periphery of the inner ring and the inner periphery of the outer ring has a first guide surface on a first axial side of the outer ring raceway surface or the inner ring raceway surface, and a first guide surface on a second axial side of the outer ring raceway surface or the inner ring raceway surface. having a second guide surface;
The at least three first sliding members are fixed to the inner periphery or outer periphery of the first annular body and slide on the first guide surface, and the at least three first sliding members are fixed to the inner periphery or outer periphery of the first annular body and slide on the first guide surface, and The moving member is arranged with a central angle of less than 180° around the central axis m,
The at least three second sliding members are fixed to the outer periphery or inner periphery of the second annular body and slide on the second guide surface, and the at least three second sliding members are fixed to the outer periphery or the inner periphery of the second annular body and slide on the second guide surface, and A rolling bearing characterized in that the moving member is arranged with a central angle smaller than 180° around the central axis m. The first annular body has one or more first through holes at at least three locations in the circumferential direction,
The first sliding member includes a first main body including a first sliding surface that slides on the first guide surface, one or more first rod-shaped parts protruding from the first main body, and the first sliding member. a first enlarged portion provided at the tip of the rod-shaped portion;
the first rod-shaped portion is housed inside the first through hole, and the first body abuts the first annular body on one opening side of the first through hole;
The rolling bearing according to claim 1, wherein the first enlarged portion is exposed on the other opening side of the first through hole and comes into contact with the first annular body. The first body has one or more first recesses recessed from the first sliding surface, and one or more second through holes opening into the first recesses,
The first rod-shaped portion is accommodated within the first through hole and communicated with the second through hole, and has a first head at an end opposite to the first enlarged portion. has,
The rolling bearing according to claim 2, wherein the first head abuts the first recess and does not protrude from the first sliding surface. The second annular body has one or more third through holes at at least three locations in the circumferential direction,
The second sliding member includes a second main body including a second sliding surface that slides on the second guide surface, one or more second rod-shaped parts protruding from the second main body, and the second sliding member. a second enlarged part provided at the tip of the rod-shaped part;
the second rod-shaped portion is housed inside the third through hole, and the second body abuts the second annular body on one opening side of the third through hole;
The rolling bearing according to claim 1, wherein the second enlarged portion is exposed on the other opening side of the third through hole and comes into contact with the second annular body. The second body has one or more second recesses recessed from the second sliding surface, and one or more fourth through holes opening into the second recesses,
The second rod-shaped portion is accommodated inside the third through hole and communicated with the fourth through hole, and has a second head at an end opposite to the second enlarged portion. has,
The rolling bearing according to claim 4, wherein the second head abuts the second recess and does not protrude from the second sliding surface. 4. The rolling bearing according to claim 1, wherein at least a first sliding surface of the first sliding member that makes sliding contact with the first guide surface is made of a solid lubricant. The second sliding member according to any one of claims 1, 4, and 5, wherein at least a second sliding surface in sliding contact with the second guide surface is made of a solid lubricant. A rolling bearing according to the claims.

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