SU1409361A1 - Rolling mill roll support - Google Patents

Abstract

The invention relates to rolling production, in particular, combi-screw supports for the rolls of high-speed sheet rolling mills. The purpose of the invention is to increase the bearing life by uniformly distributing the load across the axial bearing rolling elements. The support consists of a roller neck 1, a multi-radial bearing 2 and an axial bearing

Description

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with

with

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Inca 3 double-sided, installed in the pillow A, seals 5 and fixing unit 6, Pillow 4 is fixed in the pillow of the support roll or in the bed 7 by the latch 8c On both sides of the outer ring of the axial bearing there are annular gaskets 9 made of elastomeric material - polyurethane, ensuring uniform distribution load on the rolling elements of the axial bearing. The initial thickness of each gasket is determined from the following equation; a (p, 8-l, 6) DE; T (l, oG, + t / j) (D - - d) / 2BC, where D is the outer diameter of the axial bearing; E is the modulus of elasticity of the gasket material; d - vnut1

This invention relates to rolling production and can be used as a combination support for high speed sheet mill rolls.

The purpose of the invention is to increase the bearing life by uniformly distributing the load over the rolling elements of an axial bearing,

The drawing shows the support of the rolling roller, general view. The bearing consists of a neck 1, a multi-radial bearing 2 and an axial bearing 3 mounted on its neck, pillow 4, sealing units 5 and fixing unit 6 Pillow 4 is fixed in the pillow of the support roll or frame 7 by means of a latch 8 "Radial inner ring bearing 2 can be mounted on the neck of the roll 1 with both tension and clearance. When landing with a gap, since its size in the roll supports is significant, it must be taken into account when calculating the maximum possible skew. The outer ring of the radial bearing is seated in the cushion 4 along the landing with a gap. The axial bearing 3 on the neck of the roll 1 is set to fit the slide, Toe, with a small gap for ease of mounting and dismounting the assembled cushion on the roll, but it is rigidly fixed to the roll in the axial tension of the gasket; f is the average radial clearance in the radial bearing; (f is the average radial clearance between the roll neck and the inner ring of the radial bearing;

o 2 is the average radial clearance between the cushion and the outer ring of the radial bearing; B - width of the radial bearing; C is the dynamic bearing capacity of the bearing. Increasing the durability of axial bearings leads to an increase in the life of the entire bearing. This is especially important for high-speed mills, as it allows the use of axial ball thrust radial bearings, 1 sludge as axial ball bearings.

When the nut of the fixation unit is fixed to 6, it is planted in the air cushion with a radial clearance of 0.25–0.5 mm per side, which excludes the perception of the radial load. Its outer ring is mounted in a cushion 4 between two annular spacers 9, which are clamped by a pre-tightening cushion lining. The gaskets 9 are made of an elastomeric material, for example polyurethane, the initial thickness of each gasket before tightening is determined by the following equation:

a (0.8. ,, ,,, 6) -2Ml., l ilDL-d:

where D is the outer diameter of the axial bearing;

E is the modulus of elasticity of the gasket material;

d is the inner diameter of the ring gasket;

o is the average radial clearance in the radial bearing;

i is the average radial clearance between the roll neck and the inner ring of the radial bearing, when the ring is loaded with tension 0;

Oj is the average radial clearance between the cushion and the outer ring of the radial bearing;

B - width of the radial bearing;

C is the dynamic bearing capacity of the bearing.

The calculated thickness of the gasket in combination with its area and the mechanical properties of the material ensures in each case its elastic deformation under actual loads and the elastic restoration of its thickness when changing the direction of the axial load.

The design of an assembly to be chosen is that the thickness of the elastomer gasket should not be less than the calculated value, since, with a smaller thickness, its elastic deformation under load and elastic recoil during unloading will not fully ensure the self-installation of the outer ring of the support under the load. It should not exceed the design thickness, as this will lead to an excessive increase in its width, (diametrical dimensions) under load, worsening the conditions of its work, as well as increase the size of the site and cost.

When the axial force appears, roll I, together with the pillows 4, begins to move in the axial direction within the gap in the axial fixation unit. Depending on the direction of movement, the projections of the pillow 4 abut against the end surface of the support pillow or the base 7 or the latches 8, which move them restrict. At that, more or less skew of pillow A relative to roll 1 takes place almost always: for new unworn parts, as a result of manufacturing inaccuracies, for worn out during operation, as a result of frequent changing of worn and differently worn sets of working pillows that come in contact with less frequently replaced ones support cushions or bed.

The action of the axial force in combination with the skew of the cushion 4 relative to the neck of the roller 1 unevenly compresses the loaded elastic gasket 9 and causes a response to the elastic recoil of the pre-tightened unloaded loading gasket 9. Due to this, the outer ring of the axial bearing 3 self-aligning the working surface of the axial bearing 3 by means of the pre-tightening of the axial bearing 3, by means of the self-tightening unloaded loading 9, the outer ring of the axial bearing 3 automatically aligns the spring-loaded spring 9. load on rolling bodies.

to

15

20

25

45

thirty

35

40

0

five

In comparison with the known technical solution, the proposed support of the mill roll, by equalizing the load over the rolling bodies, allows increasing the realizable capacity of the axial bearings and, accordingly, to a power of 3 (for ball bearings) or 3.33 (for roller bearings) to increase durability „

The increased resistance of axial bearings also leads to an increase in the resistance of the proposed supports. This is especially important for high-speed mills, as it allows wide use in their supports as axial ball thrust radial bearings, which have high speed capabilities, but insufficient capacity in conventional supports without gaskets. .

Claims (1)

Invention Formula A roll roll support containing a cushion with a multi-radial rolling bearing and a self-aligning double-acting axial bearing placed on the roll neck, characterized in that, in order to increase the bearing life by uniformly distributing the load on the axial bearing rolling bodies, the support is equipped with two annular gaskets made of elastomeric material installed on each side of the outer ring of the axial bearing, and the initial thickness of each gasket is equal to , - (08 6) a-vi, o, “oh, OJ2BC where D is the outer diameter of the axial bearing; E is the modulus of elasticity of the gasket material; d is the inner diameter of the gasket; f - radial clearance in the radial bearing; “/, Is the radial clearance between the neck and the inner rings of the radial bearing; e / j is the radial clearance between the cushion and the outer ring of the radial bearing; B - width of the radial bearing; C is the dynamic load capacity of the axial bearing.