SU1340847A1 - Rolling mill roll support - Google Patents

Abstract

The invention relates to rolling production, namely to the structures of the bearing assemblies of rolling stands, and can also be used in heavy loaded bearing bearings of machines and mechanisms. The purpose of the invention is to increase the durability of multi-bearing bearings and to improve the conditions of their assembly and disassembly. The support contains a cushion 4, in the upper part of which a boring is made: with a radius greater than the radius of the outer ring of the multi-bearing bearing 2, tightly G2;

Description

planted on the neck 1 roll. In a cushion 4, in a horizontal plate-flatness, rectangular grooves are inserted in which the ends of the membrane are inserted and hermetically fastened with pillows through seals. The cavity between the membrane and the cushion 4 is connected by vertical and horizontal channels 11 and 12, respectively, with the plug 13 and the shut-off hydraulic equipment, including a valve 14, a plate 15 with a pressure gauge 16 and a valve 17 with fast: 1

The invention relates to the design of bearing assemblies of rolling stands and can also be used in tons of loaded bearing bearings of machines and mechanisms.

The purpose of the invention is to increase the durability of multi-bearing bearings and to improve the conditions of their assembly and disassembly.

FIG. 1 shows the support, general view, longitudinal section; in fig. 2 — node I in FIG. one; in fig. 3 shows section A-A in FIG. 1 in the initial state of support; FIG. 4 is the same in the working condition of the support.

Example. The mill roll support consists of a roller neck 1, a four-sided cylindrical roller bearing, a bearing 2, a thrust assembly with a two-row tapered roller bearing 3 and a pillow 4 with two end covers 5 and 6. The pillow 4 is made with radius R, from the center O (FIG. 2). Along the axis of the four-sided cylindrical roller bearing 2 in the pillow 4 there are two rectangular grooves a into which the ends 7 of the membrane 8 are inserted, through the seal 9 with screws 10 rigidly connected to the pillow 4. In the pillow 4 there are 11 and 12 drilled from different sides which are closed by a stopper 13 and a valve 14. A plate 15 with a pressure gauge 16 is connected to a valve 14. A valve 17 with a fitting 18 is connected to a plate 15.

For normal operation of the reference node, an assembly of the reference node is necessary.

0847

by a snap connection 18. An end cap with an anchor assembly 3 and a pole 6 with seals are attached to the pillow. When assembling and disassembling the support between the diaphragm and the outer ring of the bearing 2, a gap is provided, which facilitates the installation of the headboard into and out of the cushion. Before operation of the support, fluid is pressurized into the cavity and the membrane tightly encloses the outer ring of the multi-bearing. 1 hp f-ly, 4 ill.

0

perform the following way. On the neck 1 of the roll, the inner ring of the roller bearing 2 is installed in a tight fit. Separately, a membrane 8 is fixed to a pillow 4, and the ends 7 of the membrane 8 are attached to the pillow 4 with screws 7 through a seal 9. A plug is screwed into the horizontal drilling thread 11 of the pillow 4 13, and in the horizontal drilling thread 12 - a fitting of a valve 14, with which a plate 15 is connected with a pressure gauge 16 and a valve 17 with

5 by fitting 18. Then, by means of known methods, the tightness of the attachment of the membrane to the pad is checked. If necessary, the seal is tightened or additional sealing means are used. Then, a working fluid supply device is connected to the detachable connection 15 and through the open valve 14, horizontal and vertical drilling 12 without excess pressure is supplied to the cavity between the cushion 4 and the membrane 8. Open the plug 13 to remove air. the meme-i brane must be in the original

Q position, providing a clearance F,. The rear face bolt 6 is attached to the pillow 4 and the outer ring is inserted with the bearing rollers 2 and a stop assembly 3 with an end cap 5 is attached to the 1 roll, which is fixed to

 cushion 4. The assembly of the support assembly is completed.

With valves 14 and 17 open, device 18 is connected to fitting 18.

0

fluid supply, for example, an oil-jet installation of the hydraulic system of the mill bending and a portable hydraulic press, and pumping fluid into the cavity between the membrane 8 and the cushion 4. Pressure gauge in the system is monitored by a pressure gauge 16. As the calculations show, the pressure of 0.5-1.0 Mlla is sufficient for the membrane to choose the gap S, and tightly pressed against the outer ring of the bearing 2. Then close the valve 17 and turn off the pump. By reading the pressure gauge 16 for, for example, an hour, you can additionally check the tightness of the container in the pad. If during the selected time the pressure of the pressure gauge is constant, then there is no leakage of fluid, and the seals are tight. With a significant change in pressure, it is necessary to disassemble the cushion and tighten the seal 9, tightening the ends 7 of the membrane 8 with screws. Ensuring the tightness of the seals, close the valve 14. This is necessary to disconnect the pressure gauge 16 from the hydraulic system of the cushion 4, as and reach large values, which can deactivate the pressure gauge 16. The pad is ready for operation.

The load P generated on the roll during the rolling process is transmitted through the neck 1 of the roll to the bearing 2 and, therefore, to the membrane 8. The membrane 8, compressing the liquid, evenly distributes the load between the rows of bearings, since the pressure of the fluid at any point along the horizontal axis the membrane is the same. For this reason, the load and ruler distribution between the rollers of the upper half of each row of the bearing 2 is also uniform. In the case of the roll bending system, a possible tilt of the neck 1 of the roll relative to the cushion 4 does not redistribute the load between the rows of the bearing 2. the membrane maintains uniform load.

In order to facilitate the assembly of the bearing and the dismounting of the bearing, it is necessary to eliminate the tight contact of the diaphragm and the outer ring of the bearing in the absence of pressure in the hydraulic system. For this, the gap 8 should be more than half of the effective landing nat hectare N:

H

n, r - (yn,

yn)

H - average landing nat.

wed

H,

+ N,

maize

1 “in, respectively, the largest and smallest values of tensions, calculated from the landing tables; YN, is a decrease in tension due to a reduction in the height of irregularities on the mounting surfaces of the shaft and housing when the bearing is installed; LN - reduction of seating tension when heating elements of the bearing assembly. For a bearing with a maximum real inner diameter of 900 mm with an acceptable fit of g 6, the tension value is equal to: H + 266 microns, H,

  MIN

210 microns Therefore, H 238 microns. According to tabular data take LN, 12 μm-m, and uHj according to preliminary calculations is chosen equal to 5 microns. Get H 221 microns.

Thus, the size of the gap S, 30

equals

5 0.11

mm Exodus from

five

0

five

0

design considerations take the minimum gap size S, 0.5 mm. The maximum gap is taken S, 1 mm. Further; an increase in S is impractical due to the difficulty of manufacturing a membrane with a large free stroke. Depending on the size of the bearings used in sheet mills (the outer diameter of the j is R 200-500 mm (size 5, equal to

  The value of S is determined from the condition that the elastic deformation from the fluid in the closed cavity between the membrane and the internal bore of the bearing must not exceed the value of:

with -; where du volume change

lr;

five

liquids under pressure F - membrane area.

iV is determined by the formula uV. V (j fi lR, where VQ is the initial volume of the liquid; | E is the coefficient of the relative volume compression of the liquid;

R B.

Vp can be defined as follows:

V, 1 (R + S) -R2 B- | C2 R f + 8 OB,

where B is the length of the cavity with liquid.

Rp is determined depending on the effective force P and membrane area

  rTRg Hence c equals H (2RS + 82) (2RS + SM 3-P

27-R-B-M-R-B

2 irR2 B

Taking with

mm

0.95 - („.5

6 S, 0.2

-ten

ten

mm )

/ dl sire.

lycon fluid, R 400 mm; 20,000 kN, 500 mm, & 65 mm. When with bo, 5mm. Depending on the size of the bearings, this gap is

eight

fe - 5 °) The angle of inclination of the longitudinal straight grooves is chosen on the basis of design considerations (axis 45- -60). As the angle increases to more than 60, the longitudinal section of the pad weakens and the relative bending angle of the membrane increases. Reducing the angle below leads to a decrease in the length of the longitudinal groove, which is impractical because it makes it difficult to mount the ends of the membrane.

The use of the proposed roller support allows evenly distributing the load between rows of a multi-sided, for example, four-row, cylindrical bearing, including when the cushion is tilted relative to the roll neck. The operating experience of the known roller supports showed that during the rolling process or the operation of the anti-bend device, the load is redistributed between the rows of bearings and only 2 rows of bearings are loaded from the side of the roll barrel. This leads to accelerated wear and tear. The use of the proposed roll support by

40847

elimination of the uneven distribution of the load on the podishchnik allows to increase its durability by 2 times.

In addition, the presence of an adjustable gap between the membrane and the outer ring of the bearing (by draining a part of the liquid from the cavity between the membrane) and the cushion) makes it easier to mount and dismount the bearing from the cushion.

Claims (2)

1. The support of the mill roll, containing a roll neck, mounted on it a multi-sided cylindrical roller bearing, an axial assembly with a two-row a tapered roller bearing covering the outer ring of the multi-end of the bearing base cushion and two face collars with seals, characterized in that, in order to increase the durability of many-sided bearings and improve their mounting and dismounting conditions, the upper half of the cushion is made with a radius greater than the outer radius Multiplex rings a bearing, the cavity being formed between the upper half of the pillow and the outer surface of the outer ring of the multi-bearing bearing; the support is provided with a membrane dividing the said cavity in height into two hermetically isolated compartments, one of which between the upper half of the pillow and the membrane is filled with liquid and connected by cushion channels in the cushion with pressure valves and pressure gauge. 45 50 2. A support according to claim 1, characterized in that the radius of the upper half of the bore of the cushion is 1/4 to 1/5 of the radius of the outboard ring of the multibearing bearing, and silicone oil is used as a liquid, while on both sides on the vertical the axes of the cushion in its lower half are symmetrically relative to each other with longitudinal grooves in which the end parts of the membrane are rigidly fixed. / Fzg.2 but Fi.Z Editor A. Ogar Compiled by 10. L mov Tehred L. Serdyukova Proofreader I. Muska Order 4380/13 Circulation 480 Subscription. VNIIL of the USSR State Committee for inventions and discoveries 113035, Moscow, Zh-35, 4/5 Raushska nab. Production and printing company, Uzhgorod, st. Project, 4 FIG.