JPH0133202Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a bearing device for rolling rolls in a rolling mill.

As is well known, some conventional bearing devices for rolling rolls in rolling mills rotatably support a roll neck via a rolling bearing in a bearing box provided in a rolling stand. As an example of a conventional device of this kind, as shown in Fig. 1 is a four-row tapered roller bearing system, and Fig. 2 is a combination system of a four-row cylindrical roller bearing and a thrust ball bearing. , the inner ring b of the rolling bearing a is fixed immovably in the axial direction by an inner ring holder e provided at the outer end of the neck portion d of the roll c, and the outer ring f is an outer ring holder h provided at both ends of the bearing box g; h, and the bearing box g is fixed to the stand i so that it cannot move in the axial direction.

Therefore, when changing rolls, the outer ring holder h
The relative positioning of the bearing housing g and the bearing a in the axial direction had to be performed by adjusting the thickness of the shim j interposed between the bearing housing g and the outer ring f, or between the outer ring retainer h and the end face of the bearing housing g.

However, this shim adjustment work
Bearing a is tightened with uniform force on both sides by outer ring holders h, h at both ends, and bearing a, at both ends of roll c is tightened.
It was necessary to tighten with so-called zero touch so that no thrust force was applied to a, which required an extremely high level of skill and relied heavily on intuition. Therefore, there were problems in that the work required a skilled person, took a long time, and caused damage to the bearing device due to poor adjustment.

Furthermore, since the bearing box g, bearing a, roll c, etc. are incorporated into stand i so that they cannot move in the axial direction, if thermal expansion of roll c or thermal expansion of bearing a occurs due to rolling operations, or If an abnormal thrust force is generated in the axial direction on roll c during rolling work, it will not be able to absorb these deformations and impact forces, resulting in overload on bearing a, causing seizure and damage. Ta.

On the other hand, there are methods which attempt to prevent play in the axial direction by using a hydraulic cylinder without using shims, for example, Japanese Utility Model Application Publication No. 165501/1983, Japanese Patent Publication No. 8785/1987, or Japanese Patent Application Publication No. 25465/1989. Disclosed in the official gazette.

However, in the device disclosed in Japanese Utility Model Application Publication No. 56-165501, only one hydraulic cylinder is provided in the bearings at both ends of the roll, and the hydraulic cylinders on both sides press the bearings in opposite directions. , if an abnormal thrust force occurs in the axial direction of the roll,
One cylinder had to absorb this thrust force, and the cylinder had to be made strong.

In addition, what is described in Special Publication No. 52-8785 is
A hydraulic cylinder is provided at only one location in the bearing section at one end, and the bearing is held between this cylinder and the fixed member, so the thrust force is I couldn't absorb it.

Furthermore, since the bearing described in JP-A No. 50-25465 uses a double-acting cylinder to hold the bearing immovably in the axial direction, it is necessary to absorb the impact thrust force with the double-acting cylinder. , cylinders and hydraulic piping had to be made stronger.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a rolling roll bearing device with a simple structure that can reliably absorb the impactive thrust force generated during rolling.

Therefore, the feature of the present invention is that the neck portions 6 at both ends of the rolling roll 5 are supported by the bearing box 3 via the rolling bearings 4, and the bearing box 3 is supported by the stand 1. The inner ring 7 of the rolling bearing 4 is fitted onto the neck portion 6 so as not to be movable in the axial direction, and the outer ring 11 of the bearing 4 is fitted onto the neck portion 6 so as not to be movable in the axial direction.
An outer ring holder 15 is removably fixed to one end of the bearing box 3, and a hydraulic piston 18 for pressing the outer ring 11 in the axial direction is built into the holder 15. A disc spring 24 that resists the pressing force of the hydraulic piston 18 is provided so as to come into contact with the other end of the outer ring 11.

Hereinafter, embodiments of the present invention will be described in detail based on the drawings.

What is shown in Figures 3 and 4 is the first example of the present invention.
This is an embodiment in which the present invention is applied to a four-row tapered roller bearing system. In Figure 3, 1
A pair of left and right roll stands are provided on the rolling mill.
A bearing box 3 having a rectangular outer shape and having a bearing hole 2 penetrating through the center is fitted into the stand 1 so as to be movable and fixed in the vertical direction and immovable in the left and right direction (in the axial direction). A four-row tapered roller bearing 4 is fitted into the bearing hole 2 of the bearing box 3 as an example of a rolling bearing. Neck portions 6 at both ends of the rolling roll 5 are attached to the bearing 4.
is rotatably supported.

The inner ring 7 of the bearing 4 cannot be moved in the axial direction by a fillet ring 8 fitted onto the base of the neck part 6 and an inner ring holder 10 which is detachably fixed to the tip of the neck part 6 with a bolt 9. It is clamped by and fitted onto the neck part 6.

In FIG. 4, the outer ring 11 of the bearing 4 has rolling elements 12.
The outer ring 11 is integrally constructed with the inner ring 7 via the
It is fitted into the bearing hole 2 of the bearing box 3 so that it can move in the axial direction and cannot rotate relative to the bearing box 3. Both left and right end surfaces of the outer ring 11 are in contact with end surfaces of a thrust ring 13 fitted into the bearing hole 2 so as to be movable in the axial direction. A plurality of press holes 14 are opened at predetermined intervals in the circumferential direction on the end surface (outer end surface) of the thrust ring 13 that is not in contact with the outer ring 11. An outer ring retainer 15 having an inner end face facing the outer end face of the thrust ring 13 with a predetermined gap is detachably fixed to both left and right end faces of the bearing box 3 by bolts 16. Cylinder holes 17 facing the press holes 14 of the thrust ring 13 are opened on the inner end surface of the outer ring holder 15 located at the outer end of the outer ring holder 15 at a predetermined interval in the circumferential direction.

A hydraulic piston 18 is fitted into the cylinder hole 17 so as to be slidable in the axial direction, and a projecting end of the piston 18 is fitted into the press hole 14 . An oil passage 19 communicating between the outside and the cylinder hole 17 is provided in the outer ring retainer 15. The oil passage 19 is connected to a hydraulic pressure generator 20 provided externally. Hydraulic oil supplied from the hydraulic pressure generating device 20 passes through an oil passage 19 and is supplied to the cylinder hole 17 so as to press the piston 18 toward the outer ring 11 side. Reference numeral 21 denotes an O-ring that is fitted onto the inner periphery of the cylinder hole 17 to prevent oil leakage between the piston 18 and the cylinder hole 17.

A disc spring 24 is interposed between the outer ring holder 15 located inside the outer ring holder 15 and the end face of the outer ring 11.

The outer ring 11 is restrained from moving in the axial direction by left and right outer ring retainers 15, 15 via a hydraulic piston 18 and a disc spring 24.

In addition, 22 is a sealing member, which is interposed between the fillet ring 8 and the outer ring retainer 15, and 23 is a bearing box cover, which covers the bearing hole 2 of the bearing box 3.

Note that although the above configuration describes the configuration of one bearing device at both ends of the roll, it is substantially the same for the other bearing device. As is clear from Fig. 1 used in the explanation of the conventional example, the tip of the other roll neck is a drive part that protrudes from the bearing box, so the inner ring fixing structure of the bearing is slightly different, but the outer ring fixing structure is slightly different. The structure is almost the same.

According to the first embodiment of the present invention having the above configuration, the rolling bearings 4 are fixed to both ends of the rolling roll 5 so as not to be able to move in the axial direction, and the bearing box is provided in the roll stand 1 so as not to be able to move in the axial direction. 3 through the hydraulic piston 18 and disc spring 24, zero touch installation of the roll 5 becomes extremely easy.

In other words, if the outer ring is directly clamped by the outer ring holder via a shim as in the past, for example, the shim between the outer outer ring holder and the outer ring is thicker than a predetermined size, and therefore the bearings at both ends of the roll are If the bearing is assembled so that the distance between the outer end surfaces is narrower than a predetermined dimension, there is no place to absorb this dimensional difference because the bearing is fixed to the roll so that it cannot move in the axial direction.
This dimensional difference will be absorbed by the distortion of each member such as the stand, bearing, roll, etc. Therefore, an excessive inward thrust force acts on the bearing, causing strain on the bearing and causing seizure and damage.

However, in the first embodiment, there is a gap between the outer ring 11 and the outer ring holder 15, and the hydraulic piston 18 and disc spring 24 are provided, so for example, when the rolls are rearranged, the old roll Even if the dimension between the outer end surfaces of the bearings at both ends of the hydraulic piston 1 and the same dimension of the new roll 5 are slightly different, this dimensional difference is
8 and the disk spring 24, and excessive force that would cause distortion in the bearing 4, stand 1, etc. is absorbed.

Furthermore, since the bearing 4 is fixed via the hydraulic piston 18 and the disc spring 24, even if thermal expansion occurs in the roll 5 or the bearing 4 in the axial direction, the piston 1
The deformation is absorbed by the bearing 4 and the disc spring 24, and the hydraulic characteristics and the elasticity of the disc spring 24 provide a buffering effect against the instantaneous thrust load applied to the roll 5. No thrust force is applied.

What is shown in FIG. 5 is a second embodiment of the present invention, in which the present invention is applied to a combination system of a cylindrical roller bearing 4a and a thrust ball bearing 4b, and the thrust ball bearing 4b is connected to a hydraulic piston. 18 and a coned disc spring 24 in the axial direction. In this case, since the outer ring 11 of the bearing 4b is thin, the piston 18 and the disc spring 24
Since it is difficult to provide a thrust ring 13, a thrust ring 13 is fitted onto the outer ring 11 and held therebetween. The other configurations are substantially the same as each of the above embodiments. Note that the same number of disk springs 24 are provided corresponding to the pistons 18.

Note that the present invention is not limited to the above-mentioned embodiments; for example, a plurality of hydraulic pistons 18 are provided at predetermined intervals in the circumferential direction, but an annular cylinder hole is provided in the end surface of the outer ring retainer 15. However, an annular piston may be fitted into the cylinder hole. Furthermore, it is not essential to provide the thrust ring 13.

According to the present invention, the outer ring is fixed to the bearing box via a hydraulic piston that presses the outer ring in the axial direction and a disc spring, so there is no need to perform shim adjustment work that requires skill and a long time as in the past. Roll rearrangement work can be performed, and the time required for rearrangement can be shortened. In addition, it stabilizes the clamping force of the bearing, buffers the thrust force, and absorbs thermal expansion, so it has many practical effects, such as preventing seizure and damage to the bearing and extending its life. .

[Brief explanation of drawings]

Figures 1 and 2 are cross-sectional views showing conventional examples;
The figure is a cross-sectional view showing a first embodiment of the present invention, FIG. 4 is an enlarged cross-sectional view of the same essential part, and FIG. 5 is a cross-sectional view showing a second embodiment of the present invention. 1...stand, 3...bearing box, 4...bearing,
5...Roll, 6...Network department, 7...Inner circle, 1
1... Outer ring, 15... Outer ring holder, 18... Hydraulic piston.

Claims (1)

[Scope of utility model registration request] The neck portions 6 at both ends of the rolling roll 5 are connected to the bearing box 3.
is supported via a rolling bearing 4, and the bearing box 3
is supported by the stand 1, the inner ring 7 of the rolling bearing 4 is fitted onto the neck portion 6 so as not to be able to move in the axial direction, and the outer ring 11 of the bearing 4 is fitted onto the bearing box 3 in the axial direction. An outer ring presser 15 is movably fitted into the bearing box 3 and detachably fixed to one end of the bearing box 3, and a hydraulic piston 18 for pressing the outer ring 11 in the axial direction is built into the presser 15.
A rolling roll bearing device characterized in that a disc spring 24 that resists the pressing force of the hydraulic piston 18 is provided so as to come into contact with the other end of the outer ring 11.