JP2023072404A - roller bearing - Google Patents

Abstract

To provide a roller bearing which can prevent occurrence of high stress at a fastening part fastening an inner ring boss part to a flange member.SOLUTION: A roller bearing includes: an inner ring having an inner ring raceway surface on an outer peripheral surface; an outer ring having an outer ring raceway surface on an inner peripheral surface; multiple rollers disposed between the inner ring raceway surface and the outer ring raceway surface in a rollable manner. One axial end of the inner ring is provided with a flange part integrated with the inner ring. The other axial end of the inner ring is provided with an inner ring boss part protruding to the other axial end side farther than the inner ring raceway surface. A flange member formed separately from the inner ring is fastened to the inner ring boss part by a fastening member extending in an axial direction. The fastening member does not overlap with the inner ring raceway surface in the axial direction.SELECTED DRAWING: Figure 1

Description

The present invention relates to roller bearings.

In recent years, in industrial machinery, not only functions and prices but also life cycle costs have been emphasized. For this reason, there is an increasing demand for repair and reuse of roller bearings assembled in industrial machinery, and there is a demand for a bearing structure that can be disassembled for inspection.

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 which are rolling elements that roll between the inner ring raceway surface and the outer ring raceway surface, and a tapered roller bearing. and a retainer for retaining the rollers at regular 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 is provided at the small diameter side end of the inner ring to prevent the tapered rollers from coming off. The small flange member is locked to the inner ring with a bolt. Therefore, when inspecting the inside of the tapered roller bearing or replacing the retainer, the bearing can be disassembled by removing the small flange member.

In roller bearings, cage cages manufactured by press working are sometimes used. When a tapered roller bearing has a small rib on the inner ring and the inner ring roller and cage are assembled to form an assembly, the rollers are first accommodated in each pocket of the cage to form a temporary assembly, and then the temporary assembly is assembled. Since the diameter of the inscribed circle of the roller assembled in each pocket is smaller than the outer diameter of the small rib, the inner ring cannot be assembled. Therefore, a process called bottom pressing of the cage is added, and the pillars of the holding portion are radially expanded by a mold or the like so as to increase the diameter of the inscribed circle of the roller. After that, the rollers, cage, and inner ring are assembled, and in order to reduce the diameter of the inscribed circle of the expanded rollers, the pillars are narrowed in the radial direction using a mold. This process is called a crimping process, and by going through this process, the aforementioned assembly is prevented from being disassembled (called roller cracking).

As described above, in a tapered roller bearing, in order to incorporate the tapered rollers and the cage into the inner ring, after the cage is molded to a predetermined size, the pillars of the cage are pushed (bottom widened) and caulked to achieve the following: Since it is necessary to plastically deform the retainer twice, the adjustment requires a lot of man-hours and may adversely affect the accuracy of the retainer.

In particular, large tapered roller bearings require large dies for bottom pressing (bottom widening) and crimping, and a large press machine is required for processing, resulting in increased manufacturing costs.

JP 2014-190352 A

However, in the tapered roller bearing of Patent Document 1, when the small flange member is assembled to the inner ring with a bolt, the bolt overlaps with the inner ring raceway surface in the axial direction, and the bolt fastening portion is arranged directly below the inner ring raceway surface in the radial direction. be done. Therefore, when a large load is applied to the bearing raceway surface during use, high stress is generated in the bolted portion, which may cause cracks in the inner ring.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a roller bearing that can prevent the occurrence of high stress in the fastening portion between the inner ring boss portion and the flange member.

The above objects of the present invention are achieved by the following configurations.
(1) an inner ring having an inner ring raceway surface on its outer peripheral surface;
an outer ring having an outer ring raceway surface on its inner peripheral surface;
a plurality of rollers rollably disposed between the inner ring raceway surface and the outer ring raceway surface;
A roller bearing comprising
A flange integral with the inner ring is formed at one axial end of the inner ring,
An inner ring boss portion projecting from the inner ring raceway surface to the other axial end side is formed at the other axial end portion of the inner ring,
A flange member separate from the inner ring is fastened to the inner ring boss portion by a fastening member extending in the axial direction,
A roller bearing, wherein the fastening member does not overlap the inner ring raceway surface in the axial direction.
(2) The roller bearing according to (1), wherein the fastening member axially fastens the inner ring boss portion and the flange member.
(3) the roller bearing is a tapered roller bearing;
The flange portion constitutes a large flange of the inner ring,
The roller bearing according to (1) or (2), wherein the flange member constitutes a small flange of the inner ring.

ADVANTAGE OF THE INVENTION According to this invention, the roller bearing which can prevent generation|occurrence|production of high stress to the fastening part of an inner ring|wheel boss part and a collar member can be provided.

FIG. 1 is a cross-sectional view of a tapered roller bearing according to a first embodiment of the invention. 2 is a cross-sectional view of the tapered roller bearing of FIG. 1. FIG. FIG. 3 is a cross-sectional view of a tapered roller bearing according to a second embodiment of the invention. FIG. 4 is a cross-sectional view of a tapered roller bearing according to a third embodiment of the invention. FIG. 5 is a cross-sectional view of a tapered roller bearing according to a fourth embodiment of the invention.

(First embodiment)
FIG. 1 is a cross-sectional view of a tapered roller bearing 1 according to a first embodiment of the invention. FIG. 2 is a cross-sectional view of the tapered roller bearing 1 of FIG.

A tapered roller bearing 1 comprises an inner ring 10 having a conical inner ring raceway surface 11 on its outer peripheral surface, an outer ring 20 having a conical outer ring raceway surface 21 on its inner peripheral surface, and an inner ring raceway surface 11 and an outer ring raceway surface 21 . and a plurality of tapered rollers 30 arranged rollably therebetween.

The tapered rollers 30 are held at regular intervals in the circumferential direction by an annular retainer 40 incorporated between the inner ring raceway surface 11 and the outer ring raceway surface 21 . The retainer 40 is, for example, a press retainer (cage-shaped retainer) made of steel, and includes a large-diameter ring portion, a small-diameter ring portion, and a plurality of columns that axially connect 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 the adjacent post.

A collar portion 13 that is integral with the inner ring 10 is formed at one axial end of the inner ring 10 (on the left side in the drawing; large diameter side end). The flange portion 13 protrudes radially outward from the inner ring raceway surface 11 and prevents the tapered rollers 30 from coming off toward one end in the axial direction. The flange portion 13 constitutes a large flange of the inner ring 10 .

An inner ring boss portion 15 that protrudes from the inner ring raceway surface 11 toward the other axial end is formed at the other axial end of the inner ring 10 (on the right side in the drawing; the smaller diameter side end). In addition, FIG. 2 shows a virtual plane A that passes through the other axial end portion 11a of the inner ring raceway surface 11 and extends in the radial direction. The inner ring boss portion 15 protrudes from the imaginary plane A toward the other end in the axial direction. The inner ring boss portion 15 is a convex portion extending toward the other axial end side from a position spaced radially inward from the other axial end portion 11 a of the inner ring raceway surface 11 . A step portion 17 is formed between it and the other axial end portion 11a.

A flange member 50 made of steel or a resin material, which is separate from the inner ring 10 , is fastened to the inner ring boss portion 15 with bolts 60 . Needless to say, other than the bolt 60, a fastening member such as a screw may be used.

The inner ring boss portion 15 is formed with a threaded hole 15a extending in the axial direction. The female threaded portion of the screw hole 15a is formed so as not to overlap the other axial end portion 11a of the inner ring raceway surface 11 in the axial direction. More specifically, the female threaded portion of the threaded hole 15 a is arranged closer to the other axial end than the other axial end 11 a of the inner ring raceway surface 11 . That is, the female threaded portion of the screw hole 15a is arranged on the other end side of the virtual plane A in the axial direction.

The collar member 50 may be configured by an annular member, or may be configured by arranging a plurality of annular pieces forming a part of the annular ring at intervals in the circumferential direction. The collar member 50 has a base portion 51 that extends radially outward from the inner ring boss portion 15 and a convex portion 53 that protrudes from the radially outer end portion of the base portion 51 toward one side in the axial direction. The base portion 51 abuts the inner ring boss portion 15 in the axial direction. The convex portion 53 enters the stepped portion 17 of the inner ring 10 .

The base portion 51 has a recessed portion 51b recessed from the other end surface in the axial direction toward one side in the axial direction. The recess 51b functions as a seat on which the head of the bolt 60 is seated. The recess 51b in the illustrated example opens radially inward, but the presence or absence of the opening is not particularly limited. Further, the base portion 51 is formed with a threaded hole 51a penetrating in the axial direction at a position axially facing the threaded hole 15a of the inner ring boss portion 15 .

The bolt 60 is screwed into the threaded hole 15a of the inner ring boss portion 15 and the threaded hole 51a of the base portion 51, extends axially, and fastens the inner ring boss portion 15 and the flange member 50 in the axial direction. At this time, the head of the bolt 60 is seated in the recess 51 b of the base 51 . The convex portion 53 of the flange member 50 is located radially outside the other axial end portion 11 a of the inner ring raceway surface 11 , faces the tapered rollers 30 in the axial direction, and extends toward the other axial end side of the tapered rollers 30 . prevent it from falling off. Thus, the flange member 50 constitutes a small flange of the inner ring 10 .

Here, as described above, the internal thread portion of the threaded hole 15a of the inner ring boss portion 15 extends from the other axial end portion 11a of the inner ring raceway surface 11 in the axial direction and is perpendicular to the inner ring raceway surface 11 (virtual plane A). More specifically, it is arranged on the other end side of the virtual plane A in the axial direction. Therefore, the bolt 60 screwed into the female threaded portion of the screw hole 15a is also arranged so as not to overlap the imaginary plane A in the axial direction, and more specifically, is arranged on the other end side of the imaginary plane A in the axial direction. .

More preferably, the internal thread portion of the threaded hole 15a of the inner ring boss portion 15 is axially aligned with the other axial end portion 11a of the inner ring raceway surface 11 (an imaginary plane B radially extending from the other axial end portion 11a). It is formed so as not to overlap, and more specifically, it is arranged on the other axial end side of the other axial end portion 11 a (virtual plane B) of the inner ring raceway surface 11 . Therefore, the bolt 60 screwed into the female threaded portion of the screw hole 15a is also arranged so as not to overlap the other axial end portion 11a (virtual plane B) of the inner ring raceway surface 11 in the axial direction. It is arranged on the other axial end side of the other axial end portion 11 a (virtual plane B) of the raceway surface 11 .

As described above, the bolt 60 does not overlap the inner ring raceway surface 11 in the axial direction, so that the bolt fastening portion is prevented from being arranged radially directly below the inner ring raceway surface 11 . Therefore, even if a large load is applied to the raceway surface during use of the bearing, it is possible to suppress the occurrence of high stress in the bolted portion.

In addition, since the flange member 50 can be easily attached and detached, the assembly work of the tapered roller bearing 1 is facilitated, and inspection of the inside of the tapered roller bearing 1 and replacement of the tapered rollers 30 or the cage 40 are facilitated. Become.

In addition, since the bolt 60 extends in the axial direction and fastens the inner ring boss portion 15 and the flange member 50 in the axial direction, there is an effect that the bolt can be easily fastened regardless of the shape of the retainer.

(Second embodiment)
FIG. 3 is a cross-sectional view of a tapered roller bearing 1 according to a second embodiment of the invention.

In the tapered roller bearing 1 (see FIGS. 1 and 2) of the first embodiment, the base 51 of the flange member 50 is provided with the recess 51b in which the head of the bolt 60 is seated. Unlike the bearing 1, the concave portion 51b may not be provided. In this case, the other end surface in the axial direction of the base portion 51 is a flat surface, and the head of the bolt 60 is seated on the flat surface. Since other configurations are the same as those of the first embodiment, the same reference numerals are given to the drawings, and the description thereof is omitted.

(Third embodiment)

FIG. 4 is a cross-sectional view of a tapered roller bearing 1 according to a third embodiment of the invention.

In the present embodiment, retainer 40 is a pin-type retainer and has a pair of annular portions 41 and 42 and a pin 43 that fastens the pair of annular portions 41 and 42 . Since other configurations are the same as those of the first embodiment (see FIGS. 1 and 2), the same reference numerals are given to the drawings, and the description thereof will be omitted.

(Fourth embodiment)
FIG. 5 is a cross-sectional view of a tapered roller bearing 1 according to a fourth embodiment of the invention.

In the tapered roller bearing 1 (see FIG. 4) of the third embodiment, the base 51 of the flange member 50 is provided with the recess 51b in which the head of the bolt 60 is seated. As in the embodiment (see FIG. 3), the concave portion 51b may not be provided. Since other configurations are the same as those of the third embodiment, the same reference numerals are given to the drawings, and the description thereof is omitted.

It should be noted that the present invention is not limited to the above-described embodiments, and various modifications are possible. For example, the present invention is applicable to roller bearings such as cylindrical roller bearings in addition to tapered roller bearings.

1 Tapered roller bearing (roller bearing)
10 inner ring 11 inner ring raceway surface 11a other axial end 13 flange (large flange)
15 Inner ring boss portion 15a Screw hole 17 Stepped portion 20 Outer ring 21 Outer ring raceway surface 30 Tapered roller
40 retainer 41, 42 annular portion 43 pin 50 flange member (small flange)
51 base 51a screw hole 51b recess 53 projection 60 bolt (fastening member)
A virtual plane B virtual plane

Claims (3)

an inner ring having an inner ring raceway surface on its outer peripheral surface;
an outer ring having an outer ring raceway surface on its inner peripheral surface;
a plurality of rollers rollably disposed between the inner ring raceway surface and the outer ring raceway surface;
A roller bearing comprising
A flange integral with the inner ring is formed at one axial end of the inner ring,
An inner ring boss portion projecting from the inner ring raceway surface to the other axial end side is formed at the other axial end portion of the inner ring,
A flange member separate from the inner ring is fastened to the inner ring boss portion by a fastening member extending in the axial direction,
A roller bearing, wherein the fastening member does not overlap the inner ring raceway surface in the axial direction. The roller bearing according to claim 1, wherein the fastening member axially fastens the inner ring boss portion and the flange member. The roller bearing is a tapered roller bearing,
The flange portion constitutes a large flange of the inner ring,
3. The roller bearing according to claim 1, wherein said flange member constitutes a small flange of said inner ring.

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