Roller bearings

Abstract

To provide a roller bearing capable of preventing the falling of a fastening member which fastens a flange member to an inner ring.SOLUTION: To the other axial end of the inner ring, the brim member separate from the inner ring is fastened by a fastening member extending in the axial direction. The fastening member has a head part, and a shaft part extending from the head part to one axial end, and the brim member has a base part abutting on the inner ring in the axial direction. In the base part, a plurality of recesses extending from the inner peripheral face of the base part to the radial outside are formed at peripheral spaces. The outer peripheral face of each recess includes a first protruded portion arranged on one axial end side and protruded to the radial inside, a groove portion arranged on the other axial end side of the first protruded portion and recessed to the radial outside, and a second protruded portion arranged on the other axial end side of the groove portion and protruded to the radial inside. On the first protruded portion, a shaft part of the fastening member is arranged, and in the groove portion, the head part of the fastening member is arranged. The radial inside end of the second protruded portion is located on the radial inside further than the radial outside end of the head part of the fastening member.SELECTED DRAWING: Figure 2

Description

Technical Field

[0001] The present invention relates to a roller bearing.

Background Art

[0002] In recent years, in industrial machines, not only functions and prices but also life cycle costs have been emphasized. For this reason, there has been an increasing demand for roller bearings assembled in industrial machines to be repairable and reusable, and a bearing structure that can be disassembled for inspection is required.

[0003] The tapered roller bearing described in Patent Document 1 includes an inner ring having an inner ring raceway surface, an outer ring having an outer ring raceway surface, a plurality of tapered rollers that are rolling elements that roll between the inner ring raceway surface and the outer ring raceway surface, and a cage for holding the tapered rollers at equal intervals in the circumferential direction. A large flange is integrally formed at the large-diameter side end of the inner ring, and a separate small flange member for preventing the tapered rollers from falling off is provided at the small-diameter side end of the inner ring. The small flange member is locked to the inner ring by bolts. Therefore, when inspecting the inside of the tapered roller bearing or replacing the cage, it can be disassembled by removing the small flange member.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] However, in the tapered roller bearing of Patent Document 1, bolt loosening may occur when the bolts are not tightened with an appropriate tightening force, and the bolts may fall out of the bearing. If the bolts fall out, there is a possibility that the bolts may flow into the surrounding drive components (for example, a speed reducer), causing damage to the components.

[0006] This invention has been made in view of the above circumstances, and aims to provide a roller bearing that can prevent the fastening member that fastens the flange member to the inner ring from falling off. [Means for solving the problem]

[0007] The above objective of the present invention is achieved by the following configuration. (1) An inner ring having an inner ring raceway surface on its outer circumference, An outer ring having an outer ring raceway surface on its inner circumference, Multiple rollers are arranged to roll freely between the inner ring raceway surface and the outer ring raceway surface, A roller bearing comprising, A flange portion, which is integral with the inner ring, is formed at one axial end of the inner ring. A flange member, separate from the inner ring, is fastened to the other axial end of the inner ring by a fastening member extending in the axial direction. The fastening member has a head and a shaft portion extending from the head toward one axial end, The flange member has a base that abuts the inner ring in the axial direction, Multiple recesses are formed in the base portion, extending radially outward from the inner circumferential surface of the base portion, at intervals in the circumferential direction. The outer circumferential surface of the recess is A first projection is located at one end in the axial direction and protrudes radially inward, A groove is provided which is located on the other axial end side of the first protrusion and is recessed radially outward, A second projection is located on the other axial end side of the groove and protrudes radially inward, Includes, The shaft portion of the fastening member is positioned on the first protruding portion. The head of the fastening member is positioned in the groove. A roller bearing characterized in that the radially inner end of the second projection is located radially inward from the radially outer end of the head of the fastening member. (2) The head of the fastening member has a tool engagement hole recessed toward one end in the axial direction, into which a tool for rotating the fastening member can be engaged. When viewed from the axial direction, the tool engagement hole does not overlap with the second protrusion. (1) The roller bearing described above. (3) The recess has a short width portion located radially inward from the shaft portion of the fastening member, and having a circumferential width shorter than the outer diameter of the shaft portion. (1) or (2) the roller bearing described above. [Effects of the Invention]

[0008] According to the present invention, a roller bearing can be provided that can prevent the fastening member that fastens the flange member to the inner ring from falling off. [Brief explanation of the drawing]

[0009] [Figure 1] This is a cross-sectional view of a tapered roller bearing according to the first embodiment of the present invention. [Figure 2] Figure 1 is a cross-sectional view of the main part of the tapered roller bearing. [Figure 3] This is a view taken along line III-III in Figure 2. [Figure 4] This figure shows the cross-sectional shape of the flange member in the second embodiment, cut with a cross-section perpendicular to the axial direction, passing through the first projection on the outer circumferential surface of the recess. [Figure 5] This figure shows the cross-sectional shape of the flange member in a modified example of the second embodiment, cut with a cross-section perpendicular to the axial direction, passing through the first projection on the outer circumferential surface of the recess. [Figure 6] This figure shows the cross-sectional shape of the flange member in another modification of the second embodiment, cut with a cross-section perpendicular to the axial direction, passing through the first projection on the outer circumferential surface of the recess. [Modes for carrying out the invention]

[0010] (First Embodiment) Figure 1 is a cross-sectional view of a tapered roller bearing 1 according to a first embodiment of the present invention. Figure 2 is a cross-sectional view of the main part of the tapered roller bearing 1 of Figure 1.

[0011] The tapered roller bearing 1 includes an inner ring 10 having a tapered inner ring raceway surface 11 on its outer peripheral surface, an outer ring 20 having a tapered outer ring raceway surface 21 on its inner peripheral surface, and a plurality of tapered rollers 30 arranged to be rotatable between the inner ring raceway surface 11 and the outer ring raceway surface 21.

[0012] The tapered rollers 30 are held at regular intervals in the circumferential direction by an annular cage 40 incorporated between the inner ring raceway surface 11 and the outer ring raceway surface 21. The cage 40 is a pin-type cage and has a pair of annular portions 41, 42 and pins 43 for fastening the pair of annular portions 41, 42.

[0013] Note that the type of the cage 40 is not limited. For example, a press cage (basket-type cage) made of a steel plate, which has a large-diameter ring portion, a small-diameter ring portion, a plurality of column portions for axially connecting the large-diameter ring portion and the small-diameter ring portion, and pocket portions defined between the large-diameter ring portion, the small-diameter ring portion, and adjacent column portions, may be applied.

[0014] A flange portion 13 integral with the inner ring 10 is formed at one axial end portion (the left side in the figure, the large-diameter side end portion) of the inner ring 10. The flange portion 13 protrudes radially outward from the inner ring raceway surface 11 and prevents the tapered rollers 30 from falling off to one axial end side. The flange portion 13 constitutes a large flange of the inner ring 10.

[0015] An inner ring boss portion 15 that protrudes to the other axial end side of the inner ring raceway surface 11 is formed at the other axial end portion (the right side in the figure, the small-diameter side end portion) of the inner ring 10. In FIG. 2, a virtual plane A perpendicular to the inner ring raceway surface 11 extending from the other axial end portion 11a of the inner ring raceway surface 11 and a virtual plane B extending radially from the other axial end portion 11a are shown. The inner ring boss portion 15 protrudes to the other axial end side of these virtual planes A and B. The inner ring boss portion 15 is a convex portion that extends from a position radially inwardly spaced from the other axial end portion 11a of the inner ring raceway surface 11 toward the other axial end side. Therefore, a stepped portion is formed between the inner ring boss portion 15 and the other axial end portion 11a of the inner ring raceway surface 11.

[0016] A flange member 50, made of steel or resin material and separate from the inner ring 10, is fastened to the inner ring boss portion 15 by a bolt 60. In this example, the bolt 60 is a socket head cap bolt, but the type of bolt is not particularly limited, and it goes without saying that other types of fastening members such as screws may be used. The bolt 60 has a head 61 and a shaft portion 63 that extends from the head 61 to one axial end and has a male threaded portion formed on its outer circumference.

[0017] The head 61 has a hexagonal socket 65 (tool engagement hole) recessed from the other axial end to the one axial end, into which a tool such as a hex wrench for rotating the bolt 60 can be engaged. The illustrated bolt 60 is what is known as an ultra-low-profile bolt, in which the axial width of the head 61 is shorter than that of a normal bolt such as a JIS standard product, and the hexagonal socket 65 extends not only to the head 61 but also to the shaft portion 63. In addition, the diameter of the hexagonal socket 65 is also smaller than that of a normal bolt such as a JIS standard product. However, the bolt 60 is not limited to the ultra-low-profile bolt shown in the illustration, and a normal bolt may also be used.

[0018] The fastening members, such as the bolts 60, extend axially and fasten the inner ring boss portion 15 and the flange member 50 in the axial direction, making it easy to fasten the bolts 60 regardless of the cage configuration. Furthermore, the flange member 50 can be easily attached and detached, which simplifies the assembly of the tapered roller bearing 1, as well as facilitates inspection of the inside of the tapered roller bearing 1 and replacement of the tapered rollers 30 or the cage 40. The method for attaching and detaching the flange member 50 to the inner boss portion 15 will be described later.

[0019] A screw hole 15a is formed in the inner ring boss portion 15, oriented in the axial direction. Preferably, the female thread portion of the screw hole 15a is formed so as not to overlap with the virtual plane A in the axial direction, and more specifically, it is preferable that the female thread portion of the screw hole 15a is positioned on the other end in the axial direction relative to the virtual plane A. In this case, the bolt 60 that is screwed into the female thread portion of the screw hole 15a is also positioned so as not to overlap with the virtual plane A in the axial direction, and more specifically, it is positioned on the other end in the axial direction relative to the virtual plane A.

[0020] Furthermore, more preferably, the female thread portion of the screw hole 15a of the inner ring boss portion 15 is formed so as not to overlap with the other axial end 11a (virtual plane B) of the inner ring raceway surface 11 in the axial direction, and more specifically, is positioned on the other axial end side of the other axial end 11a (virtual plane B) of the inner ring raceway surface 11. In this case, the bolt 60 that is screwed into the female thread portion of the screw hole 15a is also positioned so as not to overlap with the other axial end 11a (virtual plane B) of the inner ring raceway surface 11 in the axial direction, and more specifically, is positioned on the other axial end side of the other axial end 11a (virtual plane B) of the inner ring raceway surface 11.

[0021] In this way, by arranging the bolts 60 so that they do not overlap the inner ring raceway surface 11 in the axial direction, the bolt fastening portion is avoided from being located directly below the inner ring raceway surface 11 in the radial direction. Therefore, even if a large load is generated on the raceway surface when the bearing is in use, it is possible to suppress the generation of high stress at the bolt fastening portion.

[0022] However, the above description does not exclude configurations in which the bolted fastening portion coincides with virtual planes A and B in the axial direction.

[0023] The flange member 50 may be composed of an annular member, or it may be composed of a plurality of annular pieces that form part of an annular ring and are arranged at intervals in the circumferential direction. The flange member 50 has an annular base 51 that extends radially outward from the inner ring boss portion 15, and a protrusion 53 that protrudes from the radially outer end of the base 51 toward one axial direction (the direction of arrow E in Figure 2, which is the direction toward the inner ring 10 and the tapered roller 30). The base 51 abuts with the inner ring boss portion 15 in the axial direction. The protrusion 53 fits into the stepped portion 17 of the inner ring 10.

[0024] Figure 3 is a view taken along line III-III in Figure 2. Note that in Figure 3, the hexagonal socket 65 of the bolt 60 is not shown, and the general shape of the shaft portion 63 is indicated. As shown in Figures 2 and 3, the base portion 51 has multiple recesses 55 that extend radially inward from the inner circumferential surface 51a of the base portion 51, spaced apart in the circumferential direction. The recesses 55 penetrate the base portion 51 in the axial direction and open radially inward.

[0025] As shown in Figure 2, the outer circumferential surface 55a (bottom surface) of the recess 55 includes a first projection 56 located at one axial end and projecting radially inward, a groove 57 located at the other axial end of the first projection 56 and recessed radially outward, and a second projection 58 located at the other axial end of the groove 57 and projecting radially inward.

[0026] The shaft portion 63 of the bolt 60 is positioned on the first projection 56 of the outer peripheral surface 55a of the recess 55, and the head portion 61 of the bolt 60 is positioned in the groove 57.

[0027] Figure 3 shows the cross-sectional shape of the flange member 50, cut in a section perpendicular to the axial direction, passing through the first projection 56 on the outer peripheral surface 55a of the recess 55. As shown in Figure 3, the recess 55 includes a partially cylindrical outer portion 55b that includes the first projection 56 on the outer peripheral surface 55a and opens radially inward, an inner portion 55c that is positioned radially inward from the outer portion 55b and opens radially inward, and a short-width portion 55d that connects the outer portion 55b and the inner portion 55c radially and has the shortest circumferential width of the recess 55.

[0028] The outer portion 55b of the recess 55 is the part that accommodates the shaft portion 63 of the bolt 60, and its outer diameter is set to be slightly larger than the outer diameter of the shaft portion 63. Therefore, the shaft portion 63 is allowed to move slightly within the outer portion 55b.

[0029] The short portion 55d of the recess 55 is positioned radially inward from the shaft portion 63 (central axis of the bolt 60) of the bolt 60. The circumferential width L of the short portion 55d is shorter than the outer diameter of the shaft portion 63 of the bolt 60. Therefore, the short portion 55d prevents the bolt 60 from falling out radially inward. In the illustrated example, the short portion 55d has a shape in which a pair of radially extending planes face each other in the circumferential direction, but the shape of the short portion 55d is not particularly limited.

[0030] The inner portion 55c of the recess 55 has a shape (throttle shape) in which the circumferential width decreases from the radially inward to the radially outward direction. Therefore, insertion of the bolt 60 into the recess 55 from the radially inward direction is facilitated.

[0031] The recess 55 does not necessarily have to have a short width portion 55d. For example, the outer portion 55b and the inner portion 55c may be smoothly continuous, and the circumferential width may decrease from the radially inward to the radially outward (throttle shape). In this case, since the recess 55 does not have a portion whose circumferential width is shorter than the outer diameter of the shaft portion 63 of the bolt 60, it is necessary to support the bolt 60, which is inserted into the flange member 50 and not screwed into the inner ring boss portion 15, with a jig or the like to prevent it from falling out radially. However, after fastening the flange member 50 and the inner ring boss portion 15, as long as at least one of the multiple bolts 60 is assembled with the inner ring boss portion 15, the head 61 of the bolt 60 will catch on the second projection 58, as will be described later, thus preventing the bolt 60 from falling out.

[0032] As shown in Figure 2, the bolt 60 inserted into the recess 55 has its radially outer head 61 seated on the axial end face 57a of the groove 57. The head 61 of the bolt 60 has a radial gap with the outer circumferential surface 57b of the groove 57 and an axial gap with the second projection 58. Preferably, the axial length of the groove 57 is such that the bolt 60 maintains its screw engagement with the inner ring 10 even when the head 61 of the bolt 60 is in contact with the second projection 58.

[0033] Here, as shown in Figure 2, the radially inner end of the second projection 58 is located radially inward from the radially outer end of the bolt head 61 of the bolt 60. That is, when viewed from the axial direction, the second projection 58 and the bolt head 61 of the bolt 60 overlap in at least a portion. As a result, even if the bolt 60 loosens and moves in the axial direction, the bolt head 61 of the bolt 60 will catch on the second projection 58, preventing the bolt 60 from falling out in the axial direction.

[0034] A method for inserting a bolt 60 into the recess 55 of the flange member 50 having the structure described above will now be explained. Since the flange member 50 in this example has a second projection 58, it is difficult to insert the bolt 60 in the axial direction, so it is inserted from the radially inner side to the radially outer side.

[0035] As described above with reference to Figure 3, the inner portion 55c of the recess 55 is shaped such that it is wider on the radially inner side and narrows towards the radially outer side, so that the shaft portion 63 of the bolt 60 is easily guided into the short width portion 55d and insertion is easy. Subsequently, the shaft portion 63 of the bolt 60 overcomes the short width portion 55d which has a fastening allowance (snap allowance) and is housed in the outer portion 55b.

[0036] The bolt 60, inserted into the flange member 50 and not screwed into the inner ring boss portion 15, is not firmly restrained, but its axial detachment is prevented by the second projection 58, and its radial detachment is prevented by the short width portion 55d. In this way, even when the inner ring boss portion 15 and the flange member 50 are not fastened together, the bolt 60 will not detach from the flange member 50, making it easy to handle.

[0037] Then, the flange member 50 is fastened to the inner ring boss 15 by screwing the shaft portion 63 of the bolt 60 into the threaded hole 15a of the inner ring boss 15. The protrusion 53 of the flange member 50 fastened to the inner ring boss 15 is located radially outward from the other axial end 11a of the inner ring raceway surface 11 and faces the tapered roller 30 in the axial direction, preventing the tapered roller 30 from falling off towards the other axial end. In this way, the flange member 50 constitutes a small flange of the inner ring 10.

[0038] Here, when screwing the bolt 60 into the threaded hole 15a, it is necessary to insert a tool such as a hex wrench into the hexagonal hole 65 of the bolt 60 from the axial direction. Therefore, in order to secure space for inserting the tool, the second projection 58 is located radially outward from the hexagonal hole 65. That is, when viewed from the axial direction, the hexagonal hole 65 does not overlap with the second projection 58. In other words, as shown in Figure 2, the second projection 58 is located radially outward from the radial region S in which the hexagonal hole 65 is formed, and does not overlap with the region S when viewed from the axial direction.

[0039] (Second Embodiment) Figure 4 shows the cross-sectional shape of the flange member 50 in the second embodiment, cut with a cross-section perpendicular to the axial direction, passing through the first projection 56 on the outer peripheral surface 55a of the recess 55. As shown in Figure 4, the cross-sectional shape of the flange member 50 in the second embodiment is different from that of the first embodiment (see Figure 3). The other configurations are the same as in the first embodiment, so their explanation is omitted.

[0040] The recess 55 of this embodiment includes a partially cylindrical outer portion 55b that includes a first projection 56 on the outer peripheral surface 55a and opens to one side in the circumferential direction (left side in Figure 4), an inner portion 55c that is positioned radially inward from the outer portion 55b and opens radially inward, and a short-width portion 55d that connects the outer portion 55b and the inner portion 55c in the circumferential direction and has the shortest radial width of the recess 55.

[0041] The outer portion 55b of the recess 55 is the part that accommodates the shaft portion 63 of the bolt 60, and its outer diameter is set to be slightly larger than the outer diameter of the shaft portion 63. Therefore, the shaft portion 63 is allowed to move slightly within the outer portion 55b.

[0042] The short portion 55d of the recess 55 is positioned on one side in the circumferential direction (left side in Figure 4) of the shaft portion 63 (central axis of the bolt 60) of the bolt 60. The radial width M of the short portion 55d is shorter than the outer diameter of the shaft portion 63 of the bolt 60. Therefore, the bolt 60 housed in the outer portion 55b is restricted from moving to one side in the circumferential direction (left side in Figure 4) by the short portion 55d, preventing it from falling out radially inward through the inner portion 55c. In the illustrated example, the short portion 55d has a shape in which a pair of circumferentially extending planes face each other radially, but the shape of the short portion 55d is not particularly limited.

[0043] The inner portion 55c of the recess 55 has an opening 55ca at its radially inner end. This opening 55ca is positioned offset to one side in the circumferential direction (left side in Figure 4) from the short width portion 55d and the outer portion 55b. The inner portion 55c curves to the other side in the circumferential direction (right side in Figure 4) as it extends radially outward from the opening 55ca at the radially inner end, approaching the short width portion 55d. The other end of the inner portion 55c in the circumferential direction (right side in Figure 4) connects to the short width portion 55d.

[0044] The end of the inner portion 55c on the other circumferential side (right side in Figure 4) has a shape (throttle shape) where the radial width decreases as it approaches the short width portion 55d. Therefore, the shaft portion 63 of the bolt 60 inserted radially outward from the opening 55ca of the inner portion 55c is guided circumferentially to the other side (right side in Figure 4) along the curved shape of the inner portion 55c as it moves radially outward. Then, the shaft portion 63 of the bolt 60 is further guided to the short width portion 55d by the throttle shape of the inner portion 55c, and subsequently overcomes the short width portion 55d which has a fastening allowance (snap allowance), and is housed in the outer portion 55b.

[0045] In this embodiment as well, the bolt 60, which is inserted into the flange member 50 and not screwed into the inner ring boss portion 15 (see Figures 1 and 2), is not firmly restrained, but is prevented from falling out in the axial direction by the second projection portion 58 (see Figures 1 and 2). Furthermore, the bolt 60's movement in the circumferential direction is restricted by the short width portion 55d, thus preventing it from falling out radially through the inner portion 55c. In addition, unlike the first embodiment in which the outer portion 55b that houses the bolt 60 is open radially inward, the outer portion 55b in which the bolt 60 is housed has a structure in which the radially inward side is closed, thus preventing the bolt 60 from coming out radially inward from the outer portion 55b due to its own weight. Thus, even when the inner ring boss portion 15 and the flange member 50 are not fastened together, the bolt 60 will not fall out of the flange member 50 even when the flange member 50 is alone with the bolt 60 inserted, making it easy to handle.

[0046] In addition, the inner portion 55c of the recess 55 shown in Figure 4 curves circumferentially toward the other side (right side in Figure 4) as it moves radially outward from the opening 55ca at the radial inner end, approaching the short width portion 55d. However, the shape of the inner portion 55c can be appropriately changed as long as it connects the opening 55ca and the short width portion 55d, and for example, a shape like that shown in Figure 5 can be adopted.

[0047] Figure 5 shows the cross-sectional shape of the flange member 50 according to a modified example of the second embodiment, cut in a cross section perpendicular to the axial direction, passing through the first projection 56 on the outer peripheral surface 55a of the recess 55. In the example shown in Figure 5, the inner portion 55c has an L-shaped cross-section and includes a radial extension portion 55cb extending radially outward from the opening 55ca, and a circumferential extension portion 55cc extending from the radially outer end of the radial extension portion 55cb toward the other side in the circumferential direction (right side in Figure 5) and connecting to the short width portion 55d.

[0048] The other end of the circumferential extension portion 55cc (right side in Figure 5) has a shape (throttle shape) in which the radial width decreases as it approaches the short width portion 55d. The shaft portion 63 of the bolt 60, inserted radially outward from the opening 55ca of the inner portion 55c, is guided along the radial extension portion 55cb and the circumferential extension portion 55cc. The shaft portion 63 of the bolt 60 is then guided to the short width portion 55d by the throttle shape of the circumferential extension portion 55cc, and subsequently overcomes the short width portion 55d, which has a fastening allowance (snap allowance), and is housed in the outer portion 55b.

[0049] Thus, the modified version of the second embodiment shown in Figure 5 can achieve the same effects as the second embodiment shown in Figure 4.

[0050] Figure 6 shows the cross-sectional shape of the flange member 50 according to another modification of the second embodiment, cut in a cross section perpendicular to the axial direction, passing through the first projection 56 on the outer peripheral surface 55a of the recess 55. In the modification of the second embodiment shown in Figure 5, the end on the other circumferential side (right side in Figure 5) of the circumferential extension 55cc had a shape (throttle shape) in which the radial width decreased as it approached the short width portion 55d. However, the shape of the end on the other circumferential side of the circumferential extension 55cc is not limited to the shape shown in Figure 5, and may be a shape that extends linearly to the other circumferential side, as shown in Figure 6. In this case, the circumferential extension 55cc and the short width portion 55d are connected by a wall portion 55e that extends radially perpendicular to the circumferential extension 55cc.

[0051] It should be noted that the present invention is not limited to the embodiments described above and can be modified in various ways. For example, the present invention can be applied to any roller bearing, such as cylindrical roller bearings, in addition to tapered roller bearings.

[0052] For example, in the above example, an inner ring boss portion 15 was formed at the other axial end of the inner ring 10, protruding axially from the inner ring raceway surface 11. However, this inner ring boss portion 15 is not necessarily required. If the inner ring boss portion 15 is not formed, a flange member 50 is placed at the other axial end of the inner ring 10 (a position adjacent to the other axial end 11a of the inner ring raceway surface 11), similar to the above-mentioned Patent Document 1 (Japanese Patent Application Publication No. 2014-190352). In this case, since the inner ring boss portion 15 is not formed, the inner ring 10 does not have a stepped portion 17, and the flange member 50 does not have a protrusion 53. Also, the screw hole 15a is formed so as to extend from the other axial end surface of the inner ring 10 toward the one axial end. [Explanation of Symbols]

[0053] 1 Tapered roller bearing (roller bearing) 10 Inner Ring 11 Inner ring raceway surface 11a Other axial end 13. Tsuba (guard) 15 Internal Boss Section 15a Screw hole 17 Step section 20 Outer ring 21 Outer ring raceway surface 30 yen water roller 40 Retainer 41,42 Annular section 43 pins 50 Flange member 51 Base 51a Inner surface 53 Convex part 55 recess 55a Outer surface 55b outer part 55c inner part 55ca aperture 55cb Radial extension 55cc circumferential extension part 55d Short width part 55e wall 56 1st protrusion 57 Groove 57a One end surface in the axial direction 57b Outer surface 58 Second protrusion 60 bolts (fastening members) 61 Head 63 Shaft 65 Hexagonal hole (tool engagement hole) A,B virtual plane L Circumferential width M Radial width

Claims

1. An inner ring having an inner ring raceway surface on its outer circumference, An outer ring having an outer ring raceway surface on its inner circumference, Multiple rollers are arranged to roll freely between the inner ring raceway surface and the outer ring raceway surface, A roller bearing comprising, A flange portion, which is integral with the inner ring, is formed at one axial end of the inner ring. A flange member, separate from the inner ring, is fastened to the other axial end of the inner ring by a fastening member extending in the axial direction. The fastening member has a head and a shaft portion extending from the head toward one axial end, The flange member has a base that abuts the inner ring in the axial direction, Multiple recesses are formed in the base portion, extending radially outward from the inner circumferential surface of the base portion, at intervals in the circumferential direction. The outer circumferential surface of the recess is A first projection is located at one end in the axial direction and protrudes radially inward, A groove is provided which is located on the other axial end side of the first protrusion and is recessed radially outward, A second projection is positioned on the other axial end side of the groove and protrudes radially inward, Includes, The shaft portion of the fastening member is positioned on the first protruding portion. The head of the fastening member is positioned in the groove. A roller bearing characterized in that the radially inner end of the second projection is located radially inward from the radially outer end of the head of the fastening member.

2. The head of the fastening member has a tool engagement hole recessed toward one end in the axial direction, into which a tool for rotating the fastening member can be engaged. When viewed from the axial direction, the tool engagement hole does not overlap with the second projection. The roller bearing according to claim 1.

3. The roller bearing according to claim 1 or 2, wherein the recess has a short width portion that is radially inward from the shaft portion of the fastening member and has a circumferential width shorter than the outer diameter of the shaft portion.

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