JP2003307222A - Thrust conical roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a thrust conical roller bearing being easily built in a shaft and easy in handling and maintenance. <P>SOLUTION: This thrust conical roller bearing 10 has an inner ring 11 externally fitted to the shaft, an outer ring 13 fitted in a housing, and a plurality of conical rollers 15 arranged between the inner and outer rings. The inner ring 11 is provided with a displacement preventive means 12 for engaging with the conical rollers 15 so as to restrain the radial directional displacement of the inner ring. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a thrust tapered roller bearing mainly used as a roll neck bearing for steel equipment, rolling mills and the like.

[0002]

2. Description of the Related Art A roll neck bearing for a work roll for a rolling mill has a structure in which a radial load (bending load) and a thrust load are supported by a set of four-row tapered roller bearings, and a dedicated radial load and thrust load are provided. There is a structure to support by (radial bearing and thrust bearing). The latter structure is often used when the thrust load is large, depending on the structure and characteristics of the rolling mill. In this structure, a bending load is applied to the radial tapered roller bearing via the housing. As a result, the roll neck is displaced, and the work roll performs rolling while controlling the shape of the plate. The thrust load generated by the friction between the work roll and the plate making during the rolling is supported only by the thrust tapered roller bearing. The thrust tapered roller bearing does not apply a radial load due to the bearing structure.

FIG. 3 shows a conventional example of a thrust tapered roller bearing. The thrust tapered roller bearing 80 has a roll neck 90.
Annular inner ring (intermediate ring) 81 that is externally fitted to the outer peripheral surface of the fitting portion 91, a pair of collared outer rings 83 and 83 arranged on both axial sides of the inner ring 81, the inner ring 81 and each outer ring 83. A plurality of tapered rollers 85 are provided between the rollers and a cage 86 that holds the tapered rollers 85. On the outer peripheral side of the inner ring 81,
An outer ring spacer 87 is interposed between the pair of outer rings 83.

The thrust tapered roller bearing 80 and the radial tapered roller bearing (not shown) are sequentially assembled in a housing (not shown) arranged so that the axial direction is the vertical direction.
Outer rings 83, 83 of the thrust tapered roller bearing 80 are fitted in the housing. Then, the bearings and the housing are mounted on the roll neck 90 with the axial direction oriented horizontally (in a horizontal state). Inner ring 8 of thrust tapered roller bearing 80
When 1 is externally fitted to the fitting portion 91 of the roll neck 90, there is a gap h between the outer peripheral surface of the inner ring 81 and the inner peripheral surface of the outer ring spacer 87.

[0005]

When the thrust tapered roller bearing 80 is in a horizontal state, the inner ring 81 may shift downward due to its own weight. That is, the inner ring 81 is displaced in the radial direction until the outer peripheral surface of the lower portion of the inner ring 81 contacts the inner peripheral surface of the lower portion of the outer ring spacer 87. An enlarged view of part A in FIG. 3 is shown in FIG. In this state where the inner ring 81 is displaced downward (displacement amount δ), the inner peripheral surface of the inner ring 81 is
Since the step portion of the stepped cylindrical roll neck 90 abuts, the assembling work is complicated. In recent years, assembling work is often performed using an automatic device, but since the inner peripheral surface of the inner ring 81 and the step portion of the roll neck 90 contact as shown in FIG. 4, the assembling operation is automated in this assembling work. Problems such as difficulty in fine adjustment of equipment are likely to occur. The present invention is
The present invention has been made in view of the above circumstances, and an object thereof is to provide a thrust tapered roller bearing which can be easily incorporated into a shaft and which can be easily handled and maintained.

[0006]

The object of the present invention is achieved by the following constitution. (1) In a thrust tapered roller bearing including an inner ring externally fitted to a shaft, an outer ring internally fitted to a housing, and a plurality of tapered rollers arranged between the inner and outer rings, the inner ring has a diameter of the inner ring. A thrust tapered roller bearing, characterized in that displacement preventing means for engaging with the tapered roller is provided so as to suppress the displacement in the direction. (2) The thrust tapered roller bearing according to (1), wherein the displacement prevention means is an inner ring collar provided on the inner ring so as to come into contact with the end surface of the tapered roller. (3) The thrust tapered roller bearing according to (2), wherein the inner ring flange comes into contact with the small-diameter end surface of the tapered roller. (4) The thrust tapered roller bearing according to (2), wherein the inner ring flange comes into contact with a large-diameter end surface of the tapered roller.

According to the thrust tapered roller bearing having the above structure, the radial displacement of the inner ring is suppressed or prevented by the displacement preventing means even when the thrust tapered roller bearing is in a horizontal state, so that it can be incorporated into the shaft such as a roll neck. It will be easier. Not only at the time of manufacturing the bearing, but also at the time of maintenance, the work of removing and assembling the bearing becomes easy, and the work time can be shortened.
Further, it is possible to reduce the thickness of the outer ring spacer and increase the outer diameter of the inner ring, thereby increasing the capacity of the bearing. In order to obtain even greater capacity, it is possible to design without the outer ring spacer.

[0008]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1A shows a main part of a thrust tapered roller bearing 10 according to the first embodiment of the present invention. The thrust tapered roller bearing 10 has an annular inner ring (intermediate ring) 11 which is fitted onto the outer peripheral surface of a roll neck fitting portion (not shown).
And a pair of collared outer rings 1 arranged on both axial sides of the inner ring 11.
3, 13 and a plurality of tapered rollers 15 arranged between the inner ring 11 and each outer ring 13, and a cage 16 for holding the tapered rollers 15.
It has and. An outer ring spacer 17 is interposed between the pair of outer rings 13 and 13 on the outer peripheral side of the inner ring 11.

An outer ring collar 13a is provided on the outer peripheral side of the surface of the outer ring 13 facing the inner ring 11. Outer ring collar 13
“A” supports the large-diameter end surface of the tapered roller 15. On the other hand, an inner ring collar 12 is provided at a position on the inner peripheral side of the surface of the inner ring 11 facing the outer ring 13. In this embodiment, the inner ring collar 12
Are continuously and integrally provided on the entire circumference of the inner ring 11. The flange surface of the inner ring flange 12 is formed in an inclined plane shape following the shape of the small diameter end surface of the tapered roller 15.

When the thrust tapered roller bearing 10 is brought into a horizontal state when assembled on a shaft such as a roll neck, the outer ring 1
3,13 do not displace in the housing (not shown),
The inner ring 11 tends to be displaced downward due to its own weight. At that time, the inner ring flange 12 provided on the inner ring 11 contacts the small-diameter end surface of the tapered roller 15. Tapered roller 1 under the bearing
Since the large-diameter end surface of 5 is supported by the outer ring collar 13a of the outer ring 13, it does not move downward. Therefore, the tapered roller 15 supports the inner ring 11 via the inner ring flange 12, and the radial displacement of the inner ring 11 is suppressed.

FIG. 1B is an enlarged view of portion B in FIG. When the shaft is fitted in the inner ring 11, a gap having a predetermined dimension Δc is formed between the inner ring flange 12 and the small diameter end surface of the tapered roller 15 located below the bearing. The size of this gap Δc
Is larger than the size Δa of the clearance between the fitting surfaces of the inner ring 11 and the shaft as shown in FIG. 1 (A), and the distance between the outer peripheral surface of the inner ring 11 and the inner peripheral surface of the outer ring spacer 17 is larger than It is set smaller than the dimension Δb of the gap. That is, Δa
<Δc <Δb is set.

According to the thrust tapered roller bearing 10 as described above, the radial displacement of the inner ring 11 is suppressed or prevented by the inner ring collar 12 even in the horizontal state.
It is easy to install on a shaft such as a roll neck. Bearing 1
Bearing 10 not only at the time of manufacturing
The work of removing and assembling is also facilitated, and the work time can be shortened. Further, since there is no concern that the inner ring 11 comes into contact with the outer ring spacer 17 and the outer ring spacer 17 is displaced, the outer ring spacer 17
It is also possible to reduce the wall thickness of the inner ring 11 and increase the outer diameter of the inner ring 11, so that the capacity of the bearing can be increased. In order to obtain a larger capacity, the design without the spacer 17 is possible.

FIG. 2A shows a main part of a thrust tapered roller bearing 20 according to the second embodiment of the present invention. It should be noted that the members having the same configurations and operations as those already described are given the same or corresponding reference numerals in the drawings to simplify or omit the description. Thrust tapered roller bearing 20
Is an inner ring (intermediate ring) 21, a pair of flanged outer rings 13, 13 arranged on both axial sides of the inner ring 21, a plurality of tapered rollers 15 arranged between the inner ring 21 and each outer ring 13, and a conical Around 1
And a retainer 16 for holding 5. On the outer peripheral side of the inner ring 21, the outer ring spacer 17 is provided between the pair of outer rings 13, 13.
Is installed.

In the present embodiment, an inner ring collar 22 is provided at a position on the outer peripheral side of the surface of the inner ring 21 facing the outer ring 13. Also in this embodiment, the inner ring collar 22 is continuously and integrally provided on the entire circumference of the inner ring 21. The flange surface of the inner ring flange 22 is formed in an inclined flat surface shape or an inclined curved surface shape following the shape of the large diameter end surface of the tapered roller 15.

The thrust tapered roller bearing 20 is made horizontal when it is installed on a shaft such as a roll neck, and when the inner ring 21 tends to be displaced downward due to its own weight, the inner ring 21
The inner ring brim 22 provided on the abutment portion abuts on the large-diameter end surface of the tapered roller 15. The tapered roller 15 at the upper part of the bearing is supported by the raceway surface 13b of the outer ring 13 having a conical inner surface, and therefore does not move downward. Therefore, by the tapered roller 15,
The inner ring 21 is supported via the inner ring collar 22, and displacement of the inner ring 21 in the radial direction is suppressed.

FIG. 2B is an enlarged view of portion C in FIG. When the shaft is fitted into the inner ring 21, a gap having a predetermined dimension Δc is formed between the inner ring flange 22 and the large diameter end surface of the tapered roller 15 located above the bearing. The size of this gap Δc
2A, the size of the clearance between the fitting surface of the inner ring 21 and the shaft as shown in FIG. 2A is made larger than the size Δa of the clearance between the outer peripheral surface of the inner ring 21 and the inner peripheral surface of the outer ring spacer 17 Set small (Δa <Δc <Δb).

The present invention is not limited to the above-described embodiments, but can be appropriately modified and improved.
For example, the inner ring collar may be molded separately from the inner ring and then attached to the inner ring. Further, the outer ring may be provided with a collar that supports the small-diameter end surface of the tapered roller. Further, the present invention can be applied to a thrust tapered roller bearing having only one outer ring.

[0018]

As described above, according to the present invention,
It is possible to provide a thrust tapered roller bearing that is easy to incorporate in a shaft and is easy to handle and maintain.

[Brief description of drawings]

FIG. 1 is a diagram showing a first embodiment of the present invention.

FIG. 2 is a diagram showing a second embodiment of the present invention.

FIG. 3 is a diagram showing a conventional thrust tapered roller bearing.

FIG. 4 is an enlarged view of part A in FIG.

[Explanation of symbols]

10, 20 thrust tapered roller bearing 11,21 inner ring 12,22 Inner ring collar (displacement prevention means) 13 outer ring 13a outer ring tsuba 15 tapered rollers

Claims (4)

[Claims] 1. A thrust tapered roller bearing comprising an inner ring externally fitted to a shaft, an outer ring internally fitted to a housing, and a plurality of tapered rollers arranged between the inner and outer rings, wherein the inner ring is the inner ring. A thrust tapered roller bearing, wherein a displacement preventing means for engaging with the tapered roller is provided so as to suppress radial displacement of the roller. 2. The thrust tapered roller bearing according to claim 1, wherein the displacement prevention means is an inner ring collar provided on the inner ring so as to contact the end surface of the tapered roller. 3. The thrust tapered roller bearing according to claim 2, wherein the inner ring collar is in contact with a small-diameter end surface of the tapered roller. 4. The thrust tapered roller bearing according to claim 2, wherein the inner ring flange abuts a large-diameter end surface of the tapered roller.