JP2024039336A - Roller bearing and double row roller bearing - Google Patents

Abstract

To provide a roller bearing and a double row roller bearing capable of preventing falling of a fastening member for fastening a flange member to an inner ring boss portion.SOLUTION: A double row roller bearing includes a pair of roller bearings. Each of the roller bearings 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; and a plurality of rollers rollingly disposed between the inner ring raceway surface and the outer ring raceway surface. An axial one end portion of the inner ring is provided with a flange portion formed integrally with the inner ring, a flange member separated from the inner ring is fastened to the axial other end portion of the inner ring by a fastening member extending in an axial direction, the fastening member has a head portion and a shaft portion extending to an axial one end side from the head portion, and a spacer for preventing falling of the fastening member is positioned between the pair of roller bearings and disposed in opposition to the head portion of the fastening member in the axial direction.SELECTED DRAWING: Figure 1

Description

The present invention relates to a roller bearing and a double row roller bearing.

In recent years, importance has been placed on industrial machinery not only on functionality and price but also on life cycle cost. For this reason, there is an increasing demand for repair and reuse of roller bearings assembled into industrial machinery, and there is a need for bearing structures 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 that are rolling elements that roll between the inner ring raceway surface and the outer ring raceway surface, and a tapered roller bearing that is a rolling element that rolls between the inner ring raceway surface and the outer ring raceway surface. A cage for holding the rollers at equal intervals in the circumferential direction. A large flange is integrally formed at the large diameter end of the inner ring, and a separate small flange member is provided at the small diameter end of the inner ring to prevent the tapered rollers from falling off. The small collar member is locked to the inner ring with a bolt. Therefore, when inspecting the inside of the tapered roller bearing or replacing the cage, it can be disassembled by removing the small collar member.

Japanese Patent Application Publication No. 2014-190352

However, in the tapered roller bearing of Patent Document 1, if the bolt is not fastened with an appropriate tightening force, the bolt may become loose, and the bolt may fall off from the bearing. If a bolt falls off, it may flow into surrounding drive parts (such as a reduction gear), causing damage to the parts.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a roller bearing and a double row roller bearing that can prevent a fastening member that fastens a collar member to an inner ring from falling off.

The above object of the present invention is achieved by the following configuration.
[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 the inner peripheral surface;
a plurality of rollers rotatably disposed between the inner ring raceway surface and the outer ring raceway surface;
A double row roller bearing including a pair of roller bearings each having a
A flange portion that is integral with the inner ring is formed at one axial end of the inner ring,
A collar member that is separate from the inner ring is fastened to the other end of the inner ring in the axial direction by a fastening member that extends in the axial direction,
The fastening member has a head and a shaft extending from the head to one end in the axial direction,
A spacer that prevents the fastening member from falling off is located between the pair of roller bearings and is provided so as to face the head of the fastening member in the axial direction.
A double row roller bearing characterized by:
[2] An inner ring having an inner ring raceway surface on its outer peripheral surface;
an outer ring having an outer ring raceway surface on the inner peripheral surface;
a plurality of rollers rotatably disposed between the inner ring raceway surface and the outer ring raceway surface;
A roller bearing comprising:
A flange portion that is integral with the inner ring is formed at one axial end of the inner ring,
A collar member that is separate from the inner ring is fastened to the other axial end of the inner ring by a fastening member that extends in the axial direction,
The fastening member has a head and a shaft extending from the head to one end in the axial direction,
A spacer that prevents the fastening member from falling off is provided so as to face the head of the fastening member in the axial direction.
A roller bearing characterized by:

According to the present invention, it is possible to provide a roller bearing and a double row roller bearing that can prevent a fastening member that fastens a collar member to an inner ring from falling off.

FIG. 1 is a sectional view of a double-row tapered roller bearing according to a first embodiment of the present invention. FIG. 2 is an enlarged view of essential parts of the double-row tapered roller bearing 1 shown in FIG.

(First embodiment)
FIG. 1 is a sectional view of a double-row tapered roller bearing according to a first embodiment of the present invention. FIG. 2 is an enlarged view of essential parts of the double-row tapered roller bearing 1 shown in FIG.

As shown in FIG. 1, the double-row tapered roller bearing 1 includes a pair of tapered roller bearings 1A and 1B that are arranged opposite to each other in the axial direction (left-right direction in FIGS. 1 and 2) with a gap therebetween. Hereinafter, the tapered roller bearing 1A on the left side of FIG. 1 may be referred to as a first tapered roller bearing, and the tapered roller bearing 1B on the right side of FIG. 1 may be referred to as a second tapered roller bearing. The first and second tapered roller bearings 1A and 1B have an axially symmetrical structure.

The first and second tapered roller bearings 1A and 1B rotatably support an axially extending shaft member 3 with respect to a housing 5 disposed on the radially outer side of the shaft member 3 with a gap therebetween. A cylindrical spacer 7 fitted onto the shaft member 3 is disposed in the axial gap between the first and second tapered roller bearings 1A and 1B.

The first and second tapered roller bearings 1A and 1B include an inner ring 10 that fits around a shaft member 3 that extends in the axial direction, and an outer ring that fits inside a housing 5 that is disposed on the outside of the shaft member 3 in the radial direction with a gap therebetween. 20, and a plurality of tapered rollers 30 arranged between the inner ring 10 and the outer ring 20.

The inner ring 10 has a conical inner ring raceway surface 11 on its outer peripheral surface. The shaft member 3 has a convex portion 3a that protrudes radially outward on the axially outer side (the side away from the spacer 7 in FIG. 1, the left side) of the inner ring 10 of the first tapered roller bearing 1A. The inner ring 10 of the first tapered roller bearing 1A is fitted onto the outer circumferential surface of the shaft member 3, and is positioned by being in contact with the convex portion 3a of the shaft member 3 in the axial direction. The inner ring 10 of the second tapered roller bearing 1B fits into the outer circumferential surface of the shaft member 3, and connects in the axial direction with a separate flange member 4 fixed to the tip of the shaft member 3 (the right end in FIG. 1). is positioned in contact with the

The outer ring 20 has a conical outer ring raceway surface 21 on its inner circumferential surface. The housing 5 has a protrusion 5a that protrudes radially inward between the outer rings 20, 20 of the first and second tapered roller bearings 1A, 1B. The outer rings 20, 20 of the first and second tapered roller bearings 1A, 1B fit into the inner circumferential surface of the housing 5 and are positioned by abutting axially against the protrusion 5a of the housing 5.

The plurality of tapered rollers 30 are disposed between the inner ring raceway surface 11 and the outer ring raceway surface 21 so as to be freely rollable. The tapered rollers 30 are held at a constant interval in the circumferential direction by an annular retainer 40 installed between the inner ring raceway surface 11 and the outer ring raceway surface 21. The retainer 40 is a pin type retainer and includes a pair of annular portions 41 and 42 and a pin 43 that fastens the pair of annular portions 41 and 42.

The type of retainer 40 is not limited, and for example, it may be a pressed retainer (cage type retainer) made of steel plate, which has a large diameter ring part, a small diameter ring part, and a large diameter ring part and a small diameter ring part. A structure having a plurality of pillars connected in the axial direction and a pocket defined between the large-diameter ring part, the small-diameter ring part, and the adjacent pillars may be applied.

A flange portion 13 that is integral with the inner ring 10 is formed at the axially outer end of the inner ring 10 (the distal end with respect to the spacer 7; one axial end; the large diameter end). The collar portion 13 protrudes radially outward from the inner ring raceway surface 11 and prevents the tapered rollers 30 from falling off axially outward. The flange portion 13 constitutes a large flange of the inner ring 10.

The axially inner end of the inner ring 10 (the proximal end with respect to the spacer 7; the other axial end; the small diameter end) is provided with an axially inner end (the spacer 7 An inner ring boss portion 15 is formed that protrudes toward the inner ring (side).

The double-row tapered roller bearing 1 shown in FIG. 1 is assembled as follows. First, the left first tapered roller bearing 1A is inserted into the shaft member 3 from the right side until it hits the convex portion 3a. Next, the shaft member 3 is inserted into the housing 5 from the left side, and the first tapered roller 1A fitted onto the shaft member 3 is brought into contact with the convex portion 5a of the housing 5. Subsequently, the spacer 7 is inserted into the shaft member 3 from the right side. Note that the order of the step of bringing the first tapered roller bearing 1A into contact with the convex portion of the housing 5 and the step of inserting the spacer 7 into the shaft member 3 is not particularly limited. Next, the second tapered roller bearing 1B on the right side is inserted into the shaft member 3 from the right side until it hits the convex portion 5a of the housing 5. Then, a separate flange member 4 is fixed to the tip of the shaft member 3 (the right end in FIG. 1).

FIG. 2 shows an enlarged view of the area around the inner ring boss portion 15 of the inner ring 10 of the first tapered roller bearing 1A in FIG. Note that the structure around the inner ring boss portion 15 of the inner ring 10 of the first tapered roller bearing 1A and the structure around the inner ring boss portion 15 of the inner ring 10 of the second tapered roller bearing 1B are symmetrical and similar. A description of the latter structure will be omitted.

Note that FIG. 2 shows a virtual plane A extending perpendicularly to the inner ring raceway surface 11 from the axially inner end 11a of the inner ring raceway surface 11, and a virtual plane B extending radially from the axially inner end 11a of the inner ring raceway surface 11. has been done. The inner ring boss portion 15 protrudes inward in the axial direction from these virtual planes A and B. The inner ring boss portion 15 is a convex portion that extends toward the other end in the axial direction from a position spaced apart radially inward from the axially inner end 11a of the inner ring raceway surface 11. Therefore, the inner ring boss portion 15 and the inner ring raceway surface 11 are A stepped portion 17 is formed between the axially inner end portion 11a and the axially inner end portion 11a.

A collar member 50 made of steel or resin and separate from the inner ring 10 is fastened to the inner ring boss portion 15 with a plurality of bolts 60 . The plurality of bolts 60 are arranged at predetermined intervals from each other in the circumferential direction. Although the bolt 60 in this example is a hexagon socket head bolt, 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 includes a head 61 and a shaft portion 63 that extends from the head 61 toward one end in the axial direction and has a male threaded portion formed on its outer peripheral surface.

Since the fastening members such as the bolts 60 extend in the axial direction and fasten the inner ring boss portion 15 and the collar member 50 in the axial direction, it is easy to fasten the bolts regardless of the cage form. Furthermore, since the collar member 50 can be easily attached and detached, 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 also facilitated. Become.

The inner ring boss portion 15 has a female threaded portion on its inner peripheral surface, and a threaded hole 15a extending in the axial direction is formed. The female threaded portion of the screw hole 15a is preferably formed so as not to overlap with the virtual plane A in the axial direction, and more specifically, the female threaded portion of the screw hole 15a is arranged inside the virtual plane A in the axial direction. It is preferable that In this case, the male threaded part of the shaft part 63 of the bolt 60 that is screwed into the female threaded part of the screw hole 15a is also arranged so as not to overlap with the virtual plane A in the axial direction. placed on the inside.

More preferably, the female threaded portion of the screw hole 15a of the inner ring boss portion 15 is formed so as not to overlap with the axially inner end 11a (virtual plane B) of the inner ring raceway surface 11 in the axial direction. is arranged axially inward from the axially inner end 11a (virtual plane B) of the inner ring raceway surface 11. In this case, the male threaded portion of the shaft portion 63 of the bolt 60 that is threaded into the female threaded portion of the screw hole 15a is also arranged so as not to overlap with the axially inner end 11a (virtual plane B) of the inner ring raceway surface 11 in the axial direction. More specifically, it is arranged axially inward from the axially inner end 11a (virtual plane B) of the inner ring raceway surface 11.

In this way, if the male threaded portion of the shaft portion 63 of the bolt 60 is arranged so as not to overlap the inner ring raceway surface 11 in the axial direction, it is possible to avoid the bolt fastening portion from being arranged directly below the inner ring raceway surface 11 in the radial direction. Ru. Note that the bolt fastening portion refers to the threaded portion in the axial direction between the female threaded portion of the screw hole 15a and the male threaded portion of the shaft portion 63, and FIG. The combined length H is shown. In this way, by arranging the bolt fastening part (the part indicated by the threaded length H) so that it does not intersect with the virtual planes A and B, even if a large load is generated on the raceway surface when the bearing is used, Also, it is possible to suppress the occurrence of high stress in the bolted part.

However, the above description does not exclude an embodiment in which the bolt fastening portion overlaps the virtual planes A and B in the axial direction.

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

As shown in FIG. 2, the base 51 has a recess 51b that is recessed from the axially inner surface 51a toward the axially outer side. The recessed portion 51b functions as a seating portion on which the head 61 of the bolt 60 is seated. The recess 51b in this example is formed over the entire circumference of the base 51 and opens radially inward, but the shape of the recess 51b is not particularly limited.

Furthermore, a through hole 51e is formed in the base 51, passing through the base 51 in the axial direction. The through hole 51e penetrates from the bottom surface 51c of the recess 51b to the axially outer surface 51d of the base 51. The through hole 51e is provided at a position facing the screw hole 15a of the inner ring boss portion 15 in the axial direction. Therefore, the same number of through holes 51e as the screw holes 15a are provided.

The bolt 60 passes through the through hole 51e of the base 51 and is threaded into the screw hole 15a of the inner ring boss 15 to extend in the axial direction and fasten the inner ring boss 15 and the collar member 50 in the axial direction. At this time, the head 61 of the bolt 60 is located within the recess 51b of the base 51 and is seated on the bottom surface 51c of the recess 51b.

The convex portion 53 of the collar member 50 fastened to the inner ring boss portion 15 is located radially outward from the axially inner end 11a of the inner ring raceway surface 11 and faces the tapered roller 30 in the axial direction. Prevents it from falling inward in the axial direction. In this way, the collar member 50 constitutes a small collar of the inner ring 10.

The spacer 7 disposed between the first and second tapered roller bearings 1A, 1B prevents the bolts 60, 60 of the first and second tapered roller bearings 1A, 1B from falling off. It is provided so as to face the heads 61, 61 in the axial direction. Further, the material of the spacer 7 is not particularly limited, and examples thereof include iron-based materials, high-strength brass, and resin.

In order to enhance the effect of the spacer 7 on preventing the bolt 60 from falling off, the axial length S of the gap between the spacer 7 and the head 61 of the bolt 60 is preferably short. More specifically, the axial length S of the gap is set shorter than the axial screw engagement length H between the female threaded portion of the screw hole 15a and the male threaded portion of the shaft portion 63 (S<H ). In the illustrated example, the axial length S of the gap is the axial distance Lb between the heads 61, 61 of the bolts 60, 60 of the first and second tapered roller bearings 1A, 1B, and the axial length of the spacer 7. It is half of the difference between the dimension Ls and {S=(Lb-Ls)/2}.

By setting S<H in this way, even if the bolt 60 becomes loose and moves axially inward (towards the spacer 7), the female thread of the screw hole 15a Since the head 61 of the bolt 60 comes into contact with the spacer 7 before the threaded engagement between the bolt and the male threaded portion of the shaft portion 63 is released, the bolt 60 is prevented from falling off in the axial direction.

Furthermore, the outer diameter Dko of the spacer 7 is larger than the pitch circle diameter Dbp of the bolt 60 (Dko>Dbp). As a result, even if the bolt 60 becomes loose and moves axially inward (towards the spacer 7), the head 61 of the bolt 60 will surely abut against the spacer 7, so the bolt 60 is prevented from falling off in the axial direction. Furthermore, it is possible to suppress wear caused by contact between the spacer end face and the bolt head. If the outer diameter Dko of the spacer 7 is less than or equal to the pitch circle diameter Dbp of the bolt 60 (Dko≦Dbp), this is not preferable because the bolt 60 may ride over the spacer 7 radially outward and fall off. .

Further, although the spacer 7 is fitted to the outer circumferential surface of the shaft member 3, the relationship of the fitting is not limited, and may be a clearance fit, an interference fit, or an intermediate fit. . For example, if the inner diameter Dki of the spacer 7 is set smaller than the outer diameter Dso of the shaft member 3 (Dki<Dso), wear of the fitting surface due to external vibration and wear due to contact between the spacer end face and the bolt head can be suppressed. effective. Moreover, if the inner diameter Dki of the spacer 7 is set larger than the outer diameter Dso of the shaft member 3 (Dki>Dso), there is an effect that the spacer can be easily removed from the shaft.

Note that the present invention is not limited to the embodiments described above, and can be modified in various ways. For example, the present invention is applicable to any roller bearing other than a tapered roller bearing, such as a cylindrical roller bearing.

For example, in the above example, the inner ring boss 15 that protrudes further toward the other axial end side than the inner ring raceway surface 11 is formed at the other axial end of the inner ring 10, but the inner ring boss 15 does not necessarily have to be provided. If the inner ring boss 15 is not formed, the flange member 50 is disposed at the other axial end of the inner ring 10 (at a position adjacent to the axial inner end 11a of the inner ring raceway surface 11) as in the above Patent Document 1 (JP Patent Publication 2014-190352). In this case, since the inner ring boss 15 is not formed, the inner ring 10 does not have a step portion 17, and the flange member 50 does not have a protrusion 53. In addition, the screw hole 15a is formed from the axial inner surface of the inner ring 10 toward the axial outer side at a position opposite the through hole 51e of the flange member 50.

Further, in the above-described example, the collar member 50 had a recess 51b that was recessed toward one side in the axial direction from the axially inner surface 51a of the base 51, and on which the head 61 of the bolt 60 was seated. The concave portion 51b may not be formed in the collar member 50. In this case, the through hole 51e is formed to penetrate from the axially inner surface 51a of the base 51 to the axially outer surface 51d, and the head 61 of the bolt 60 is seated on the axially inner surface 51a of the base 51. Also in this case, the spacer 7 is provided so as to face the head 61 of the bolt 60 in the axial direction. As a result, even if the bolt 60 becomes loose and moves in the axial direction, the head 61 of the bolt 60 will catch on the spacer 7, preventing the bolt 60 from falling off in the axial direction. be done.

Further, in the above example, the first and second tapered roller bearings 1A and 1B had a symmetrical structure in the axial direction, but the sizes of the first and second tapered roller bearings 1A and 1B are different from each other. It doesn't matter if you stay there. In that case, the spacer 7 may have a tapered shape or a stepped shape, for example, depending on the size of the first and second tapered roller bearings 1A and 1B.

Further, in the above example, the double-row tapered roller bearing 1 including the pair of tapered roller bearings 1A, 1B and the spacer 7 disposed between them has been described, but the content of the present invention is limited to the double-row roller bearing. It can also be applied to ordinary roller bearings. That is, the spacer 7 does not need to be placed between the pair of roller bearings, but may be provided so as to face the head of the bolt (fastening member) of at least one roller bearing in the axial direction. By providing the spacer 7 in this manner, it is possible to prevent the bolt from falling off. Also in this case, by setting the various dimensional relationships (S<H, Dko>Dbp, etc.) as described above, it is possible to more reliably prevent the bolt from falling off.

1 Double row tapered roller bearing (double row roller bearing)
1A, 1B Tapered roller bearing (roller bearing)
3 Shaft member 3a Convex portion 5 Housing 5a Convex portion 7 Spacer 10 Inner ring 11 Inner ring raceway surface 11a Axial inner end 13 Flange portion 15 Inner ring boss portion 15a Threaded hole 17 Step portion 20 Outer ring 21 Outer ring raceway surface 30 Tapered roller (roller)
40 Retainer 41, 42 Annular part 43 Pin 50 Flange member 51 Base part 51a Axial inner surface 51b Recessed part (seating part)
51c Bottom surface 51d Axial outer surface 51e Through hole 53 Convex portion 60 Bolt (fastening member)
61 Head 63 Shaft

Claims (4)

an inner ring having an inner ring raceway surface on the outer peripheral surface;
an outer ring having an outer ring raceway surface on the inner peripheral surface;
a plurality of rollers rotatably disposed between the inner ring raceway surface and the outer ring raceway surface;
A double row roller bearing including a pair of roller bearings each having a
A flange portion that is integral with the inner ring is formed at one axial end of the inner ring,
A collar member that is separate from the inner ring is fastened to the other end of the inner ring in the axial direction by a fastening member that extends in the axial direction,
The fastening member has a head and a shaft extending from the head to one end in the axial direction,
A spacer that prevents the fastening member from falling off is located between the pair of roller bearings and is provided so as to face the head of the fastening member in the axial direction.
A double row roller bearing characterized by: The other end of the inner ring in the axial direction has a female threaded portion and is formed with a threaded hole extending in the axial direction,
A male threaded portion is formed on the outer circumferential surface of the shaft portion of the fastening member, and the male threaded portion is threadedly engaged with the female threaded portion of the threaded hole;
An axial length of a gap between the spacer and the head of the fastening member is shorter than an axial length of the threaded engagement between the female threaded portion of the screw hole and the male threaded portion of the shaft portion. Double row roller bearings described in . The outer diameter of the spacer is larger than the pitch circle diameter of the fastening member.
The double row roller bearing according to claim 1 or 2. an inner ring having an inner ring raceway surface on the outer peripheral surface;
an outer ring having an outer ring raceway surface on the inner peripheral surface;
a plurality of rollers rotatably disposed between the inner ring raceway surface and the outer ring raceway surface;
A roller bearing comprising:
A flange portion that is integral with the inner ring is formed at one axial end of the inner ring,
A collar member that is separate from the inner ring is fastened to the other end of the inner ring in the axial direction by a fastening member that extends in the axial direction,
The fastening member has a head and a shaft extending from the head to one end in the axial direction,
A spacer that prevents the fastening member from falling off is provided so as to face the head of the fastening member in the axial direction.
A roller bearing characterized by:

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