JPH09236119A - Thrust cylinder roller bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To facilitate machining without reducing bearing precision of a thrust cylinder bearing and to reduce a manufacturing cost. SOLUTION: In a cylinder roller bearing formed such that a plurality of cylinder rollers 3 held at a holder 4 between track wheels 1 and 2 are arranged, an outside diameter D1 of at least one track wheel 1 or 2 is reduced to a value lower than an outside diameter d1 of a holder 4 with a range not attaining a contact region B with a cylinder roller 3 or an inside diameter D2 of at least one track wheel 1 or 2 is increased to a value higher than an inside diameter d2 of the holder 4 within a range not attaining a contact region B with the cylinder roller 3. Further, an outside diameter D1 of at least one track wheel 1 or 2 is decreased to a value lower than an outside diameter d1 of the holder 4 in a range not attaining a contact region B with the cylinder roller 3 and an inside diameter D2 of at least one track wheel 1 or 2 is increased to a value higher than the inside diameter d2 of the holder 4 in a range not attaining the contact region B with the cylinder roller 3.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a thrust cylindrical roller bearing used for supporting an axial load such as a crushing table in a speed reducer for a vertical mill.

[0002]

2. Description of the Related Art For example, as a bearing for supporting an axial load from a grinding table in a speed reducer for a vertical mill, FIG.
Thrust cylindrical roller bearings such as those shown in are generally used. This thrust cylindrical roller bearing has two bearing rings (1
1, 12), a plurality of cylindrical rollers (13) and a cage (1
4) composed of a plurality of cylindrical rollers (13)
The bearing ring (1) is accommodated in a double row in pockets (15) provided in the cage (14) at equal intervals in the circumferential direction.
1) and 12). And each bearing ring (1
1, 12) are ground on both side surfaces, one surface being raceway surfaces (11a, 12a) in contact with the cylindrical roller (13) and the other surface being width surfaces (11b, 12b).

Conventionally, in this type of thrust cylindrical roller bearing, the outer diameter D1 of the bearing rings (11, 12) is set to the cage (1
Formed to have a larger diameter than the outer diameter d1 of 4), and the races (11, 12)
The inner diameter D2 of the cage is smaller than the inner diameter d2 of the cage (14).

[0004]

By the way, the bearing rings (11, 12) in this type of thrust cylindrical roller bearing are
The load is applied only to the contact area with the cylindrical roller (13), that is, the radial area indicated by reference symbol B in FIG. 3 (b). It is not necessary that the diameter D1 is larger than the outer diameter d1 of the cage (14) and the inner diameter D2 is smaller than the inner diameter d2 of the cage (14).

Thus, the outer diameter D1 of the bearing ring (11, 12)
Although the outer diameter d1 of the cage (14) is larger than the inner diameter D2 of the bearing ring (11, 12), the inner diameter D2 of the bearing ring (11, 12) is smaller than the inner diameter d2 of the cage (14). No
As described above, the outer diameter D1 of the bearing rings (11, 12) is formed to be larger than the outer diameter d1 of the cage (14), and the bearing rings (11, 12) are
If the inner diameter D2 of 12) is formed to be smaller than the inner diameter d2 of the cage (14), the width (A) of the bearing rings (11, 12) is correspondingly widened and the grinding area is increased. It takes a long time to grind the wheels (11, 12) and increases the amount of wear of the grinding wheel, which causes an increase in manufacturing cost.

Moreover, if the width (A) of the bearing ring is large, the width warp tends to increase, which is a problem in terms of bearing accuracy.

The present invention has been proposed in view of the above problems of the prior art, and an object thereof is to make it possible to facilitate the machining without lowering the bearing accuracy and to contribute to the reduction of the manufacturing cost. It is intended to provide a cylindrical roller bearing.

[0008]

In order to achieve the above-mentioned object, the present invention is characterized by adopting the following structure.

That is, according to the present invention, in a thrust cylindrical roller bearing in which a plurality of cylindrical rollers held by a cage are arranged between the bearing rings, the outer diameter of at least one bearing ring is set to the contact area with the cylindrical rollers. Is smaller than the outer diameter of the cage (Claim 1), or the inner diameter of at least one bearing ring is larger than the inner diameter of the cage in the range that does not reach the contact area with the cylindrical roller. It is formed to have a diameter (claim 2).

Further, according to the present invention, the outer diameter of at least one bearing ring is formed to be smaller than the outer diameter of the cage within the range where it does not reach the contact area with the cylindrical roller, and the inner diameter of at least one bearing ring is The inner diameter of the cage is larger than the inner diameter of the cage so as not to reach the contact area with the cylindrical rollers (claim 3).

By adopting such a configuration,
Compared with the conventional structure, the amount of material forming the bearing ring is smaller, and the area of the bearing ring that needs to be ground is smaller, which reduces the bearing ring grinding time and wear amount of the grinding wheel. I'm done. Therefore, the manufacturing cost can be reduced.

Further, according to another aspect of the present invention, a relief is formed in a portion other than the contact area with the cylindrical roller on either or both of the side surfaces of the bearing ring. As a result, the area that requires grinding is reduced, so the grinding time is shortened.
It is possible to reduce the amount of wear of the grinding wheel and eventually reduce the manufacturing cost. The surface forming the clearance is the raceway surface (claim 4) or the width surface (claim 5) or both the raceway surface and the width surface (claim 6) of one or both of the pair of races.

[0013]

Embodiments of the present invention will be described below with reference to the drawings.

A thrust cylindrical roller bearing, the main part of which is shown in FIG. 1 (a), has two bearing rings (1, 2) and a plurality of bearing rings, similar to the basic structure of the conventional thrust cylindrical roller bearing shown in FIG. Of the cylindrical rollers (3) and the cage (4), and the plurality of cylindrical rollers (3) are arranged in a double row in a pocket (5) provided in the cage (4) at equal intervals in the circumferential direction. It is held between the bearing rings (1, 2) in the state of being housed in, but the outer diameter D1 of the bearing rings (1, 2) does not reach the contact area (B) with the cylindrical roller (3). The difference is that the outer diameter d1 of the cage (4) is smaller (D1 <d1).

The outer diameter D1 of the bearing rings (1, 2) is the cage (4)
Since the outer diameter d1 of the bearing ring is smaller than that of the conventional configuration, the width (A) of the bearing ring (1, 2) is narrower and the grinding area is reduced, and the bearing ring (1, 2) is reduced accordingly. The grinding time is shortened and the amount of wear of the grinding wheel is small. Therefore,
A reduction in manufacturing cost is realized.

The thrust cylindrical roller bearing, the main part of which is shown in FIG. 1 (b), is a cage in which the inner diameter D2 of the bearing rings (1, 2) does not reach the contact area (B) with the cylindrical roller (3). Except for the point (D2> d2) formed larger than the inner diameter d2 in (4), the basic structure is the same as that of the conventional thrust cylindrical roller bearing shown in FIG. That is, two bearing rings (1,
2) is composed of a plurality of cylindrical rollers (3) and a cage (4), and the plurality of cylindrical rollers (3) is a cage (4).
Are held between the races (1, 2) in a state where they are accommodated side by side in a double row in pockets (5) provided at even intervals in the circumferential direction.

The inner diameter D2 of the bearing rings (1, 2) is the cage (4)
Since the inner diameter d2 is larger than the inner diameter d2, the width (A) of the bearing rings (1, 2) is narrower and the grinding area is smaller than in the conventional structure, as in the case of FIG. 1 (a). It is possible,
As a result, the grinding time of the bearing rings (1, 2) is shortened and the amount of wear of the grinding wheel is small, which reduces the manufacturing cost.

As shown in FIG. 1 (a), the outer diameter D1 of the bearing rings (1, 2) is made smaller than the outer diameter d1 of the cage (4), and as shown in FIG. 1 (b), the bearing rings ( Although making the inner diameter D2 of 1 and 2) larger than the inner diameter d2 of the cage (4) can be carried out separately as described above, both of them can be combined in one thrust cylindrical roller bearing. It can also be implemented in combination.

Since the thrust cylindrical roller bearing illustrated in FIG. 1 is of a type in which the cage (4) is not guided by the bearing rings (1 or 2), D1 for both bearing rings (1, 2) is used. It is possible to adopt a configuration such as <d1 and / or D2> d2, but in the case of the type in which the cage (4) is guided by the bearing ring (1 or 2), the bearing ring ( As for 1 or 2), it is necessary to secure a part for contacting and guiding the cage (4), so D1 <d1 only for the bearing ring (2 or 1) that does not guide the cage (4).
And / or a configuration such as D2> d2 will be adopted.

Next, another embodiment of the present invention shown in FIG. 2 will be described.

Out of both side surfaces (race surfaces 1a, 2a and width surfaces 1b, 2b) extending in the radial direction of the bearing rings (1, 2) except the contact area (B) with the cylindrical roller (3). By forming the relief (6), the area to be ground is reduced.

In FIG. 2 (a), a relief (6) is provided in a portion of the raceway surface (1a, 2a) of each bearing ring (1, 2) other than the contact area (B) with the cylindrical roller (3). It is provided. FIG.
In (b), the reliefs (6) are provided in portions of the width surfaces (1b, 2b) of the bearing rings (1, 2) other than the contact area (B) with the cylindrical rollers (3). In FIG. 2 (c), reliefs (6) are provided on both side surfaces of each race ring (1, 2), that is, both raceway surfaces (1a, 2a) and width surfaces (1b, 2b). Any of them can be implemented in combination with the above-described one shown in FIG.

The cage (4) with pockets (5) is
It may be either a comb-shaped cage having a ring attached to the outer circumference thereof or a cage having a square hole pocket. Further, the cylindrical roller (3) is not limited to the double row as shown and may be a single row.

[0024]

As described above, according to the present invention,
The outer diameter of at least one of the bearing rings is formed to be smaller than the outer diameter of the cage within a range that does not reach the contact region with the cylindrical rollers, or at least one of the bearing rings has an inner diameter of the contact region with the cylindrical rollers. Since it is formed to be larger than the inner diameter of the cage in the range that does not reach, the outer diameter of at least one of the bearing rings is formed to be smaller than the outer diameter of the cage in the range that does not reach the contact area with the cylindrical roller. At the same time, since the inner diameter of at least one of the bearing rings is formed to be larger than the inner diameter of the cage within the range where it does not reach the contact area with the cylindrical roller, compared with the conventional configuration,
The raceway area of the bearing ring can be narrowed to reduce the grinding area, and accordingly, the grinding time of the bearing ring can be shortened and the abrasion amount of the grinding wheel can be reduced, which can contribute to the reduction of manufacturing cost.

Further, by forming a clearance on the raceway surface and the width surface of the race ring in a portion other than the contact area with the cylindrical roller, the area to be ground can be reduced and the grinding time can be shortened. Not only that, the width warp is suppressed, and the bearing accuracy can be expected to improve.

[0026]

[Brief description of drawings]

[0027]

FIG. 1 is an enlarged sectional view of an essential part of a thrust cylindrical roller bearing showing an embodiment of the present invention.

[0028]

FIG. 2 is an enlarged sectional view of a main part of a thrust cylindrical roller bearing showing an embodiment of the present invention.

[0029]

FIG. 3A is a sectional view of a conventional thrust cylindrical roller bearing, and FIG. 3B is an enlarged sectional view of essential parts.

[0030]

[Explanation of symbols]

 1 Raceway 1a Raceway surface 1b Width surface 2 Raceway ring 2a Raceway surface 2b Width surface 3 Cylindrical roller 4 Cage 5 Pocket 6 Escape A Raceway ring width B Contact area with cylindrical roller D1 Raceway ring outer diameter D2 Raceway ring inner diameter d1 Cage outer diameter d2 Cage inner diameter

Claims (6)

[Claims] 1. A cylindrical roller bearing having a plurality of cylindrical rollers held by a cage between the bearing rings, wherein the outer diameter of at least one bearing ring does not reach the contact area with the cylindrical rollers. A thrust cylindrical roller bearing having a smaller diameter than the outer diameter of the cage. 2. A cylindrical roller bearing having a plurality of cylindrical rollers held by a cage between bearing rings, wherein at least one bearing ring has an inner diameter within a range that does not reach a contact area with the cylindrical rollers. Thrust cylindrical roller bearing characterized by having a larger diameter than the inner diameter of the container. 3. A thrust cylindrical roller bearing having a plurality of cylindrical rollers held by a cage between the bearing rings, wherein the outer diameter of at least one bearing ring does not reach the contact area with the cylindrical rollers. The thrust cylinder is characterized in that it is formed to have a smaller diameter than the outer diameter of the cage, and at least one inner ring has an inner diameter larger than the inner diameter of the cage within a range not reaching the contact area with the cylindrical roller. Roller bearing. 4. A cylindrical roller bearing having a plurality of cylindrical rollers held by a cage between the bearing rings, wherein at least one portion of the bearing surface of the bearing ring other than the contact area with the cylindrical rollers. A thrust cylindrical roller bearing characterized in that a relief is formed. 5. A cylindrical roller bearing having a plurality of cylindrical rollers held by a cage between the bearing rings, wherein at least one of the width faces of the bearing ring escapes to a portion other than the contact region with the cylindrical rollers. A thrust cylindrical roller bearing characterized in that 6. A cylindrical roller bearing having a plurality of cylindrical rollers held by a cage between the bearing rings, wherein at least one of the bearing rings has a surface extending in the radial direction and is in contact with the cylindrical roller. A thrust cylindrical roller bearing characterized in that a relief is formed in a portion other than the region.