Method for preventing axial movement and loosening of oil film bearing

Abstract

The present application belongs to the field of rolling mill liquid power lubrication bearing, and particularly relates to an oil film bearing anti-axial movement and anti-loose method; a damping structure is added between an oil film bearing cone sleeve and a cone sleeve ring, the damping structure is composed of compression springs which are evenly distributed around the axis of the cone sleeve on the bonded end face of the cone sleeve and the cone sleeve ring; the spring damping structure is added between the oil film bearing cone sleeve and the cone sleeve ring, the number of the springs required for damping connection between the oil film bearing cone sleeve and the cone sleeve ring, the free height, and the number and depth of the damping holes are determined according to the actual operation condition of the bearing and the specification and model of the bearing. When the bearing is axially positioned, it can be determined whether sufficient pre-tightening force is generated, so that the anti-loose effect of the locking structure is achieved.

Description

Technical Field

[0001] This invention belongs to the field of hydraulically lubricated bearings for rolling mills, and specifically relates to a method for preventing axial movement and loosening of oil film bearings. Background Technology

[0002] Modern large-scale rolling mills, especially large continuous plate and strip rolling mills with automatic control over plate shape and thickness, mostly use oil film bearings. Those used as work roll bearings or support roll bearings in rolling mills are called rolling mill oil film bearings. Rolling mill oil film bearings are typically low-speed heavy-load, medium-speed medium-load, or heavy-load bearings. Generally, the axial positioning of oil film bearings is achieved through hydraulic devices, such as… Figure 1 As shown, the locking structure (composed of a screw ring and a nut) is used to achieve axial positioning of the oil film bearing. The locking force is achieved through the pressure value of the hydraulic device. Since the pressure value of the oil film bearing pressing device is related to many factors, insufficient preload during locking can lead to loosening of the threads during bearing operation. Furthermore, during the operation of the oil film bearing, the locking structure and the support roller rely on the contact of petals for positioning. Vibration during the rolling process of the support roller can cause axial movement of the support roller. Summary of the Invention

[0003] This invention aims to solve the problem of axial movement of the support roll during the rolling process.

[0004] The present invention provides the following technical solution: a method for preventing axial movement and loosening of an oil film bearing, wherein a damping structure is added between the tapered sleeve and the tapered sleeve ring of the oil film bearing, and the damping structure consists of compression springs evenly distributed around the axis of the tapered sleeve on the contact end face of the tapered sleeve and the tapered sleeve ring.

[0005] Furthermore, the axial load of the oil film bearing is calculated, and the parameters of the compression spring, wire diameter, distribution circle, compression amount, and number are determined based on the axial load of the oil film bearing.

[0006] The axial load of the oil film bearing is calculated using the following algebraic formula:

[0007]

[0008] Where f is the coefficient of friction between the rollers;

[0009] P - Rolling force, in tons;

[0010] K-coefficient,

[0011] L - Length of the contact area between the work roll and the support roll, in mm;

[0012] M - The limit displacement at half the width of the contact area between the work roll and the support roll;

[0013] υ - Roll morphology coefficient;

[0014] θ - the crossing angle between the work roll and the support roll, in radians (rad).

[0015] The total damping load generated by the compression spring is F 总 =0.45F b ~0.55F b .

[0016] Furthermore, the total damping load generated by the compression spring is 0.5%-1% of the total rolling force.

[0017] Furthermore, the compression spring is confined within the countersunk hole on the end face of the tapered sleeve, and the surface of the tapered sleeve ring that contacts the compression spring is a plane.

[0018] Compared with the prior art, the advantages of the present invention are:

[0019] This invention provides a method for preventing axial movement and loosening of oil film bearings. A spring damping structure is added between the tapered sleeve and the tapered ring of the oil film bearing. Based on the actual operating conditions of the bearing and its specifications, the required number of springs, free height, and the number and depth of damping holes for the damping connection between the tapered sleeve and the tapered ring are determined. When the bearing is axially positioned, it can be determined whether sufficient preload is generated (by checking the distance between the end faces of the nut and the ring to determine if the damping connection is fully effective), thereby achieving the anti-loosening effect of the locking structure. Attached Figure Description

[0020] Figure 1 This is a schematic diagram illustrating the working principle of the oil film bearing locking structure.

[0021] Figure 2 Schematic diagram of machining damping holes on the end face of the tapered sleeve;

[0022] Figure 3 for Figure 2 Sectional view at CC;

[0023] Figure 4 An assembly diagram showing the damping structure formed by the tapered sleeve and tapered sleeve ring;

[0024] Figure 5 for Figure 4 Enlarged view of point P in the middle;

[0025] Figure 6 This is a schematic diagram of the spring parameters;

[0026] In the diagram: 1-conical sleeve; 2-conical sleeve ring; 3-nut; 4-threaded ring; 5-support roller; 6-compression spring; 7-damping hole. Detailed Implementation

[0027] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0028] like Figures 2-5 As shown: A method for preventing axial movement and loosening of an oil film bearing is to add a damping structure between the tapered sleeve and the tapered sleeve ring of the oil film bearing. The damping structure consists of compression springs evenly distributed around the axis of the tapered sleeve on the contact end face of the tapered sleeve and the tapered sleeve ring.

[0029] Calculate the axial load of the oil film bearing, and determine the parameters of the compression spring, wire diameter, distribution circle, compression amount, and number of springs based on the axial load of the oil film bearing.

[0030] The axial load of the oil film bearing is calculated using the following algebraic formula:

[0031]

[0032] Where f is the coefficient of friction between the rollers;

[0033] P - Rolling force, in tons;

[0034] K-coefficient,

[0035] L - Length of the contact area between the work roll and the support roll, in mm;

[0036] M - The limit displacement at half the width of the contact area between the work roll and the support roll;

[0037] υ - Roll morphology coefficient;

[0038] θ - the crossing angle between the work roll and the support roll, in radians (rad).

[0039] The total damping load generated by the compression spring is F 总 =0.45F b ~0.55F b .

[0040] The formula for calculating compression springs is as follows:

[0041]

[0042] in:

[0043] G—Spring shear modulus in MPa, spring material is 60Si2Mn, shear modulus is 80000MPa;

[0044] d — spring wire diameter, in mm;

[0045] n—the effective number of spring coils;

[0046] D1—Spring center diameter, in mm;

[0047] k – spring constant, in N / mm.

[0048] Damping load generated by the compression spring:

[0049] F=N×δ×k

[0050] in:

[0051] N – Spring configuration;

[0052] δ — spring compression;

[0053] D1 = Dd

[0054] in:

[0055] D—Outer diameter of the spring (mm);

[0056] d——Spring wire diameter (mm);

[0057] For an 875 specification oil film bearing, the axial force generated by the rolling pressure is approximately 159.8 kN, and the total damping generated by the compression spring is 75.48 kN, accounting for 50% of the axial force.

[0058] For a 955 specification oil film bearing, the axial force generated by the rolling pressure is approximately 190.4 kN, and the total damping generated by the compression spring is 96.58 kN, with damping accounting for 50% of the axial force.

[0059] For a 1030 specification oil film bearing, the axial force generated by the rolling pressure is approximately 221.5 kN, and the total damping generated by the compression spring is 113.2 kN, accounting for 51% of the axial force.

[0060] For a 1090 specification oil film bearing, the axial force generated by the rolling pressure is approximately 248 kN, and the total damping generated by the compression spring is 126 kN, with damping accounting for 51% of the axial force.

[0061] For a 1130 specification oil film bearing, the axial force generated by the rolling pressure is approximately 365.6 kN, and the total damping generated by the compression spring is 182 kN, with damping accounting for 49.7% of the axial force.

[0062] For a 1520 specification oil film bearing, the axial force generated by the rolling pressure is approximately 964.6 kN, and the total damping generated by the compression spring is 533.3 kN, with damping accounting for 55% of the axial force.

[0063] For a 1670 specification oil film bearing, the axial force generated by the rolling pressure is approximately 1164.4 kN, and the total damping generated by the compression spring is 600 kN, accounting for 51.5% of the axial force.

[0064] The total damping load generated by the compression spring is 0.5%-1% of the total rolling force.

[0065] The compression spring is confined within the countersunk hole on the end face of the tapered sleeve, and the surface of the tapered sleeve ring that contacts the compression spring is a plane.

[0066] Example 1

[0067] When the outer diameter of the tapered sleeve is D3 = 875 mm, damping holes are made on the mating end faces of the tapered sleeve and the tapered sleeve ring. The diameter of the damping holes is 25 + 0.5 mm, and the depth of the damping holes is 30 - 0.5 mm. There are 12 damping holes, centered on the tapered sleeve keyway, with a distribution angle S = 15° and a distribution circle diameter A = 740 ± 1 mm.

[0068] A compression spring is placed at the damping hole. The spring parameters are as follows: spring height H = 38.5 mm, spring outer diameter D = 24 mm, spring wire diameter d = 6 mm, effective number of spring coils n = 3, and total number of spring coils n = 5.

[0069] The outer diameter of the tapered sleeve ring that mates with the tapered sleeve is E = 770 ± 1 mm, ensuring that the tapered sleeve ring can compress the spring.

[0070] Example 2

[0071] When the outer diameter of the tapered sleeve is D3 = 955 mm, damping holes are made on the mating end faces of the tapered sleeve and the tapered sleeve ring. The diameter of the damping holes is 25 + 0.5 mm, and the depth of the damping holes is 30 - 0.5 mm. There are 12 damping holes, centered on the tapered sleeve keyway, with a distribution angle S = 15° and a distribution circle diameter A = 820 ± 1 mm.

[0072] A compression spring is placed at the damping hole. The spring parameters are as follows: spring height H = 38.5 mm, spring outer diameter D = 24 mm, spring wire diameter d = 6.3 mm, effective number of spring coils n = 3, and total number of spring coils n = 5.

[0073] The outer diameter of the tapered sleeve ring that mates with the tapered sleeve is E = 870 ± 1 mm, ensuring that the tapered sleeve ring can compress the compression spring.

[0074] Example 3

[0075] When the outer diameter of the tapered sleeve is D3 = 1030 mm, damping holes are made on the mating end faces of the tapered sleeve and the tapered sleeve ring. The diameter of the damping holes is 25 + 0.5 mm, and the depth of the damping holes is 30 - 0.5 mm. There are 12 damping holes, centered on the keyway of the tapered sleeve, with a distribution angle S = 15° and a distribution circle diameter A = 880 ± 1 mm.

[0076] A compression spring is placed at the damping hole. The spring parameters are as follows: spring height H = 38.5 mm, spring outer diameter D = 24 mm, spring wire diameter d = 6.5 mm, effective number of spring coils n = 3, and total number of spring coils n = 5.

[0077] The outer diameter of the tapered sleeve ring that mates with the tapered sleeve is E = 920 ± 1 mm, ensuring that the tapered sleeve ring can compress the spring.

[0078] Example 4

[0079] When the outer diameter of the tapered sleeve is D3 = 1090 mm, damping holes are made on the mating end faces of the tapered sleeve and the tapered sleeve ring. The diameter of the damping holes is 27 + 0.5 mm, and the depth of the damping holes is 30 - 0.5 mm. There are 12 damping holes, centered on the keyway of the tapered sleeve, with a distribution angle S = 15° and a distribution circle diameter A = 950 ± 1 mm.

[0080] A compression spring is placed at the damping hole. The spring parameters are as follows: spring height H = 39 mm, spring outer diameter D = 26 mm, spring wire diameter d = 7 mm, effective number of spring coils n = 3, and total number of spring coils n = 5.

[0081] The outer diameter of the tapered sleeve ring that mates with the tapered sleeve is E = 980 ± 1 mm, ensuring that the tapered sleeve ring can compress the compression spring.

[0082] Example 5

[0083] When the outer diameter of the tapered sleeve is D3 = 1130 mm, damping holes are made on the mating end faces of the tapered sleeve and the tapered sleeve ring. The diameter of the damping holes is 27 + 0.5 mm, and the depth of the damping holes is 30 - 0.5 mm. There are 16 damping holes, centered on the keyway of the tapered sleeve, with a distribution angle S = 11.25° and a distribution circle diameter A = 980 ± 1 mm.

[0084] A compression spring is placed at the damping hole. The spring parameters are as follows: spring height H = 37 mm, spring outer diameter D = 24 mm, spring wire diameter d = 7 mm, effective number of spring coils n = 3, and total number of spring coils n = 5.

[0085] The outer diameter of the tapered sleeve ring that mates with the tapered sleeve is E = 1028 ± 1 mm, ensuring that the tapered sleeve ring can compress the compression spring.

[0086] Example 6

[0087] When the outer diameter of the tapered sleeve is D3 = 1520 mm, damping holes are made on the mating end faces of the tapered sleeve and the tapered sleeve ring. The diameter of the damping holes is 29 + 0.5 mm, and the depth of the damping holes is 30 - 0.5 mm. There are 16 damping holes, centered on the keyway of the tapered sleeve, with a distribution angle S = 11.25° and a distribution circle diameter A = 1280 ± 1 mm.

[0088] A compression spring is placed at the damping hole. The spring parameters are as follows: spring height H = 40 mm, spring outer diameter D = 24 mm, spring wire diameter d = 8 mm, effective number of spring coils n = 3, and total number of spring coils n = 5.

[0089] The outer diameter of the tapered sleeve ring that mates with the tapered sleeve is E = 1320 ± 1 mm, ensuring that the tapered sleeve ring can compress the compression spring.

[0090] Example 7

[0091] When the outer diameter of the tapered sleeve is D3 = 1670 mm, damping holes are made on the mating end faces of the tapered sleeve and the tapered sleeve ring. The diameter of the damping holes is 29 + 0.5 mm, and the depth of the damping holes is 30 - 0.5 mm. There are 18 damping holes, centered on the keyway of the tapered sleeve, with a distribution angle S = 10° and a distribution circle diameter A = 1460 ± 1 mm.

[0092] A compression spring is placed at the damping hole. The spring parameters are as follows: spring height H = 40 mm, spring outer diameter D = 24 mm, spring wire diameter d = 8 mm, effective number of spring coils n = 3, and total number of spring coils n = 5.

[0093] The outer diameter of the tapered sleeve ring that mates with the tapered sleeve is E = 1520 ± 1 mm, ensuring that the tapered sleeve ring can compress the compression spring.

[0094] The above description of the disclosed embodiments enables those skilled in the art to make or use the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the invention. Therefore, the invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A method of preventing axial migration and loosening of an oil film bearing, characterized by: The damping structure is composed of compression springs which are evenly distributed around the axis of the cone sleeve on the end face of the cone sleeve and the cone sleeve ring; The axial load of the oil film bearing is calculated, and the parameters, wire diameter, distribution circle, compression amount and number of the compression springs are determined according to the axial load of the oil film bearing; The axial load of the oil film bearing is calculated by the following algebraic expression: wherein, - inter-roller friction coefficient; - rolling force in tons; - coefficients, ; - length of the contact area between the work roll and the backup roll, in mm; - limit displacement at half-width of contact zone between work roll and backup roll; - roll contour coefficient; - intersection angle between work roll and backup roll in radians, rad; The total damping load generated by the compression spring is F 总 = 0.45 F b ~ 0.55 F b .

2. The method of claim 1, wherein: The total damping load generated by the compression springs is 0.5%-1% of the rolling force.

3. The method of claim 1, wherein: The compression springs are limited in the counterbore of the end face of the cone sleeve, and the surface of the cone sleeve ring in contact with the compression springs is a plane.

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