JPH04224005A - rolling mill - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention]

0001

[Industrial Application Field] The present invention relates to a rolling mill used in the steel industry and non-ferrous metal industry, for forming a plate material such as a steel plate into a desired thickness by passing it between rolls and plastically deforming it. In particular, it relates to a rolling mill equipped with shape correction and crown correction means.

0002

2. Description of the Related Art A conventional four-high rolling mill is shown in FIGS. 8 to 10. This type of rolling mill is equipped with a pair of work rolls 1 and 2 of relatively small diameter, and back-up rolls 3 and 4 of relatively large diameter arranged to sandwich them from the outside. The necks of each roll 1, 2, 3, and 4 are connected to a bearing 5.
, 6, 7, and 8, and these are attached to a housing 9. Further, a rolling down cylinder 10 is attached to the housing 9, and a rolling down force is applied between the work rolls 1 and 2 by rolling down between the bearings 5 to 8 arranged in tandem.

A material to be rolled 11 is passed between the work rolls 1 and 2 of such a rolling mill to obtain a strip material of a desired thickness. 2 is widened, and a so-called roll bending occurs in which the center of passage of the rolled material 11 bulges outward from the both end bearings 5 and 6 side. For this reason, the backup rolls 3 and 4 have a medium-thick crown shape to absorb the roll bending of the work rolls 1 and 2.

However, even if crowned backup rolls 3 and 4 are used, the amount of roll bending cannot be determined uniquely due to the properties of the material to be rolled 11 and the difference in rolling reduction, so in practice, as shown in FIG. , there is a difference (=H-h) between the end thickness h and the center thickness H of the rolled material 11.
This occurs, and the cross-sectional shape of the strip material after rolling becomes a drum-shaped cross-section with a middle and high height, with so-called selvage elongation occurring on both side edges. For this reason, various proposals have been made to obtain strip materials with a rectangular cross section.

A roll bending method is known as a conventional crown control method. In this method, a bending cylinder is attached to the roll neck, and the elastic deformation of the roll crown and work roll is canceled out to control the rolling surface of the work roll to become flat, thereby correcting the crown. That is, as shown in FIG. 9, a double rod type bending cylinder mechanism 12 is disposed between bearings 5 and 6 attached to the necks of work rolls 1 and 2, and by expanding and contracting this cylinder mechanism 12, The distance between the bearings 5 and 6 can be adjusted, and the crown that is about to occur in the rolled material 11 can be corrected depending on the amount of bending. This is a work roll bending method, but there is also a backup roll bending method.

[0006] Furthermore, there is a VC roll method in which an oil chamber is provided in the rolling roll and the oil pressure applied thereto is adjusted to change the crown of the work roll, and a heat crown method in which the work roll is partially heated and expanded to change the crown. Alternatively, a method is known in which the amount of expansion is determined in detail by partially adjusting the amount of roll coolant applied.

[0007]

However, although the roll bending method is highly responsive and flexible, as shown in FIGS. 11(a) and 11(b), the work rolls 1 and 2 Because the backup rolls 3 and 4 are restrained on the entire surface, it is difficult to give sufficient deflection to the work rolls, and not only do they lack absolute capacity, but also the backup rolls are limited due to the width, strength, shape, etc. of the material to be rolled. There are disadvantages such as the need to rearrange the crown and change the crown shape.

[0008] Furthermore, in the VC roll method, the work roll structure becomes complicated, which makes it expensive and requires troublesome maintenance. Furthermore, although the heat crown method and the roll coolant method have flexibility, there is a problem in that the responsiveness is extremely poor.

An object of the present invention is to focus on the above-mentioned conventional problems, and to provide a method that can respond quickly to constantly changing conditions, especially in high-speed rolling, and has a wide range of work roll crown control functions. In particular, it is an object of the present invention to provide a rolling mill that can significantly increase the amount of work roll deflection control and that can provide high operability with a small number of parts.

0010

[Means for Solving the Problems] In order to achieve the above object, a rolling mill according to the present invention includes a pair of work rolls that roll down a rolled material, a pair of backup rolls that contact each work roll, In a rolling mill, in which bearings at both ends of each roll are attached to a housing, and pressure means for controlling the crown by adjusting the bearing interval between the pair of work rolls is incorporated in the housing, each of the backup rolls is moved in the axial direction of the rolls. The structure is formed by a pair of support rolls with a short body length separated into two parts, and each separated support roll is rotatably and axially movably attached to a backup shaft, and each separated support roll has a guide member that engages and holds them. is attached to the guide member, and an elastic urging member that urges the support rolls toward or away from each other is linked to the guide member, and between the pair of elastically urged guide members or between the fixed member and the guide member. forms a wedge receiving portion, and the housing side is provided with a hydraulic cylinder means having a wedge that is fitted into the wedge receiving portion, and the hydraulic cylinder means extends and contracts the wedge to move the wedge into and out of the wedge receiving portion. By adjusting the amount, the spacing between the coaxial separation support rolls can be adjusted.

[0011]

[Operation] According to the above configuration, each backup roll that suppresses the deflection of the work roll that directly rolls down the rolled material is
It is composed of a pair of support rolls separated in the axial direction of the rolls, each partially rolling into contact with the work roll to support the rolling force. These separation support rolls are movable in the axial direction, and by moving their positions, the bending moment fulcrum changes, and the amount of roll bending by the pressure means of the work roll neck can be adjusted. Such positional movement of the separation support rolls is basically performed by inserting a wedge between guide members holding each separation support roll.

That is, the coaxial guide members are normally urged toward each other by elastic urging means such as coil springs. A wedge receiving portion is formed between the two guide members, and by inserting and removing the wedge into the wedge receiving portion, the distance between the two guide members is expanded or reduced, and the pair of supports with which the guide members are engaged and held are The rolls can be moved toward or away from each other arbitrarily and quickly. The wedge may be inserted or removed by operating a fluid pressure cylinder means linked thereto. Therefore, by controlling the amount of expansion and contraction of the hydraulic cylinder means, the roll bending fulcrum set by the pair of separated support rolls is changed, independently or in cooperation with the pressurizing force by the pressurizing means interposed between the bearings of the work rolls. The amount of roll bending can be quickly adjusted and crown control can be performed accurately during high-speed rolling. In particular, since the position of the separation roll is moved by the hydraulic cylinder means, it is possible to quickly and appropriately control the position, and it is also possible to provide a high crown control function with extremely simple structural members.

The above-mentioned effect can be achieved by disposing a resilient member such as a coil spring between a pair of guide members, forming a wedge receiving portion between the guide member and the housing, and inserting the wedge therein. The same applies even if

[0014]

DESCRIPTION OF THE PREFERRED EMBODIMENTS A specific embodiment of the rolling mill according to the present invention will be described in detail below with reference to the drawings, in which the rolling mill is applied to a four-high rolling mill.

FIGS. 1 and 2 show the overall configuration of a four-high rolling mill according to an embodiment. As shown in the figure, a pair of upper and lower work rolls 22, 2 parallel to the gate-shaped housing 20
4 are horizontally suspended so that they can be rolled into contact with each other, and the material to be rolled 2 is placed between them.
6 is made possible to pass through the plate. On the back side of each of the upper and lower work rolls 22 and 24, an upper backup roll unit 28 and a lower backup roll unit 30 are also horizontally suspended in parallel.

The upper backup roll unit 28 has a backup shaft 32 arranged parallel to the work roll 22, which includes a backup shaft 32 that is separated to the left and right in the roll axis direction.
A pair of support rolls 34R, 3 formed with a short body length
4L is rotatably attached. The pair of support rolls 34R and 34L are in rolling contact with the upper work roll 22 and serve as backup support for the work roll 22 during rolling. Similarly, the lower backup roll unit 30 also includes a backup shaft 36, a pair of left and right support rolls 38R attached to the backup shaft 36,
It has a length of 38L and is brought into rolling contact with the lower work roll 24 to serve as a backup support during rolling.

The neck portions of the upper and lower work rolls 22 and 24 and the upper and lower backup roll units 28 and 3
As shown in FIG. 2, bearings 46, 48, 50, and 52 are attached to the neck portions of the backup shafts 32 and 36 of No. 0, and these are attached to the housing 20 in a cascade arrangement. A rolling down cylinder 54 is provided at the lower part of the housing 20, and by driving this, a predetermined rolling pressure is generated between the work rolls 22 and 24.

In such a configuration, the separation support roll 34 of the above-mentioned upper backup roll unit 28
R, 34L, and lower backup roll unit 30
By moving each of the separation support rolls 38R and 38L in the roll axis direction, the contact position with respect to the outer peripheral surface of the work roll 22 (24) can be adjusted so as not to overlap with the rolled material 26. There is. For this position adjustment, support rolls 34R, 34L, 38R, 38L in each unit 28, 30 are engaged with roll guides 56R, 56L as guide members. 3 and 4 show examples of attachment to the upper backup roll unit 28. As shown in the figure, two guide shafts 58 are installed in parallel with the backup shaft 32, extending between the bearings 50 at both ends of the backup shaft 32. By attaching the backup shaft 32 and the guide shaft 58 to a common bearing 50, the parallelism of both shafts 32 and 58 is maintained. The roll guide 5
6R and 56L are attached to the slide casing 60R, which is formed so as to pass through the guide shaft 58 and not interfere with the support rolls 34R and 34L.
, 60L. And slide casing 6
Thrust bearing supports 62 and 64 are attached to 0R and 60L, which extend toward both end surfaces of the support rolls 34R and 34L and sandwich thrust bearings 42 and 44 that are attached to both end surfaces of the rolls 34R and 34L. . Thrust bearing support 62, 64
are the direct thrust bearings 4 as shown in FIG.
2 and 44, a donut-shaped presser plate 66
and a reinforcing plate 68 that reinforces and supports this from the outside. The presser plate 66 is passed through the backup shaft 32 so as not to interfere with it. Therefore, each of the support rolls 34R, 34L is slid in the axial direction of the backup shaft 32 as the roll guides 56R, 56L are moved in the axial direction along the guide shaft 58, respectively. Such a roll guide 56
R and 56L are similarly engaged and attached to other support rolls 38R and 38L.

Here, the support rolls 34R, 34
A drive mechanism is provided to move the positions of L, 38R, and 38L, which is driven by a pair of roll guides 56.
Coil springs 70R and 70L are interposed between the outer end surfaces of R and 56L and the backup shaft bearing 50,
A wedge means 72 adjusts the distance between the roll guides 56R and 56L by expanding the distance between the roll guides 56R and 56L by a wedge action. This will be explained regarding the upper backup roll unit 28.

First, the coil springs 70R and 70L are wound around both ends of the backup shaft 32, and are attached to the inner surfaces of the bearings 50 at both ends of the shaft and the presser plates 66 of the thrust bearing supports 62 and 64 as spring seats. It is being As a result, the pair of roll guides 56R, 56L are elastically biased toward each other, which in turn biases the support rolls 34R, 34L toward each other.

On the other hand, the roll guides 56R, 56L are urged in the proximal direction by the action of the coil springs 70R, 70L, but the opposing surfaces of the slide casings 60R, 60L that are about to come into contact with each other have inclined surfaces 74R, 74L
is formed, and a V-shaped wedge receiving portion 76 is formed by both inclined surfaces 74R and 74L. This wedge receiving portion 76 is expanded toward the cross beam member 78 of the upper housing 20, and by moving a wedge 80 in and out of this wedge receiving portion 76, the distance between the roll guides 56R and 56L can be adjusted. It is now possible to do so. The wedge means 72 for this drive is a hydraulic cylinder 82 fixed to the cross beam member 78.
, which has a telescopic rod 84 protruding in a direction perpendicular to the roll axis and toward the wedge receiver 76,
It has a structure in which a wedge 80 is attached to the tip. As shown in FIG. 4, the wedge 80 is formed in an inverted U-shape that straddles the guide shaft 58, and both side surfaces of both legs are formed so that they become gradually tapered toward the tip. Therefore, the pair of roll guides 56R, 56L can be pushed out equally to the left and right against the elastic biasing force depending on the amount of insertion into the wedge receiver 76, and the interval between the support rolls 34R, 34L can be adjusted.

[0022] The above-mentioned configuration is similarly configured in the lower backup roll unit 30, and in particular, the wedge means 72 is attached to the lower pedestal 86 and is formed symmetrically.

Further, a roll bending device 100 is incorporated in the housing 20, and as shown in FIG.
It is composed of an upper roll bending rod 102, a lower roll bending rod 104, a roll bending cylinder 106, and a piston 108.

The lower end of the upper roll bending rod 102 is fixed to the upper piston 108, and the upper end is arranged so as to be movable toward and away from the upper work roll bearing 46. Conversely, the lower roll bending rod 104 has an upper end fixed to the lower piston 108, and a lower end that can move toward and away from the lower work roll bearing 48. cylinder 1
06 is provided with a small diameter communication hole 110, and when pressure oil is introduced here from a pressure oil supply device (not shown), the roll bending rods 102, 104 are separated from each other, and the upper and lower work rolls 22, 24 The bearings 46 and 48 of the backup roll units 28 and 30 are respectively connected to the bearings 50 of the backup roll units 28 and 30,
52 side.

[0025] Also, the roll bending cylinder 10
6 and the sliding surfaces of the upper and lower work roll bearings 46 and 48,
Liners 112 and 114 are attached to each liner, and when pressure oil is supplied to the cylinder 106, the liners slide on this sliding surface, pushing open the work roll bearings 46 and 48, and pushing open the support rolls 34 and 3.
8 and the work rolls 22, 24 are used as fulcrums to facilitate bending moment. As a result, the work roll rolling surface profile during rolling by the work rolls 22 and 24 is corrected and adjusted to become a flat surface.

Note that the reduction cylinder 54 is connected to the housing 2
This is provided at the lower part of the rolling cylinder 54, and has a built-in head, and during rolling, the head is raised by introducing pressure oil into the reduction cylinder 54 from the pressure oil supply device. The operation of the head pushes up the backup shaft bearing 52 of the lower backup roll unit 30, and this downward force is applied to the lower support rolls 38R, 38L and the lower work roll 2.
4, bearing 48, roll bending device 100, bearing 4
6. Upper work roll 22, upper support roll 34R
, 34L, the upper backup shaft bearing 50, and the housing 20 to generate the desired rolling force.

The operation of the rolling mill constructed as described above is as follows.

Before rolling, the positions of the support rolls 34R, 34L and 38R, 38L are determined in advance according to the width of the material to be rolled 26. In this case, support rolls 34, 3
The rolling contact position of 8 to the work rolls 22 and 24 is the rolled material 2
6 to a position where no overlapping occurs, but this initial setting initially drives the reduction cylinder 54 to raise the lower backup roll unit 30 and keep the work rolls 22, 24 and support rolls 34, 38 in light contact. Thereafter, the fluid pressure cylinder 82 for adjusting the position of the support rolls 34, 38 is driven to project the wedge 80 at the tip and insert it into the wedge receiver 76 between the pair of spring-biased roll guides 56R, 56L. interrupt. As a result, the roll guides 56R and 56L are pushed apart to the left and right, and a pair of separated support rolls 34R and 34L (3
8R, 38L), and can be moved to a desired position away from the outer edge of the material to be rolled 26. Therefore, the distance between the pair of support rolls 34R, 34L and 38R, 38L is set to a desired distance. In this state, the contact position of each of the support rolls 34 and 38 is made to be out of the rolling area of the material to be rolled 26.

After this initial setting is completed, the material to be rolled 26 is passed between the work rolls 22 and 24. As a result, the material to be rolled 26 is rolled to a desired thickness and output as a strip material, and the shape is determined visually, by a contact method using a sensor roll, or by a non-contact method using light or magnetism. If edge elongation or mid-elongation occurs as a result of this determination, the fluid pressure cylinder 82 attached to the housing 20 is driven to adjust the amount of insertion of the wedge 80, so that the pair of support rolls 34R, 34L and 38
R and 38L are moved close to each other or away from each other, the amount of bending moment acting on the work rolls 22 and 24 is adjusted, and the occurrence of shape abnormalities is suppressed,
A rectangular strip of material can be obtained.

FIGS. 6 and 7 show upper and lower work rolls 22 and 24.
The experimental results show how the profile changes depending on the magnitude of the bending force caused by adjusting the positions of the support rolls 34 and 38.

FIG. 6 shows a roll diameter of 600 mm and a rolling force of 600 mm.
The figure shows changes in the profile of the upper work roll 22 when the distance between the support rolls is set to 1400 mm and the roll bending force is adjusted from 0 to 125 tons.

FIG. 7 shows a roll diameter of 600 mm and a rolling force of 600 mm.
ton, the distance between the support rolls is set to 1600 mm, and the change in the profile of the upper work roll 22 is shown when the roll bending force is adjusted from 0 to 125 tons.

As can be understood from these results, it is found that the amount of deflection of the work roll can be arbitrarily changed by changing the roll bending force and the position of the support roll, thereby making it possible to adjust the cross section of the strip material. Therefore, it is possible to provide a crown control ability that allows shape control over a wide range.

In the above embodiment, the wedge receiver 76 is formed at the center of the coaxial roll guides 56R, 56L to adjust the support roll spacing. It is also possible to interpose a spring so that the support rolls 34 and 38 are always biased toward the pillar side of the housing 20 so as to generate a wedge action between the pillar side and the roll guide. In such a case, it becomes possible to control the left and right support rolls independently, and effects such as being able to easily follow deviations in the passing position of the rolled material 26 are obtained, and a higher control function is achieved. You can get the effect that you want.

[0035]

[Effects of the Invention] As explained above, according to the present invention,
By arbitrarily changing the backup support portion of the work roll, crown control can be performed quickly and over a wide range, and the product shape can be modified extremely easily.

In particular, in the present invention, the distance between a pair of coaxially arranged separation rolls can be adjusted by a wedge action driven by a fluid pressure cylinder to move the position of the separation support rolls that serve as backup during rolling. Since the position can be moved accurately and the movement speed can be increased while the work continues, the shape correction function can be performed quickly and crown control can be performed by precise position control. Furthermore, since the moving mechanism is based on the wedge effect caused by the driving force of the fluid pressure cylinder, it has excellent responsiveness and does not require complicated mechanical members, so it is possible to provide a high control function with an extremely simple structure.

[Brief explanation of the drawing]

FIG. 1 is a front view of a rolling mill according to an embodiment.

FIG. 2 is a side view of the rolling mill.

FIG. 3 is an enlarged sectional view of a main part of the upper support roll portion.

FIG. 4 is a side cross-sectional view of the upper support roll portion.

FIG. 5 is a sectional view of the roll bending device.

FIG. 6 is a characteristic diagram of the amount of roll deflection accompanying the positional movement of the support roll.

FIG. 7 is a characteristic diagram of the amount of roll deflection accompanying the positional movement of the support roll.

FIG. 8 is a front view of a conventional four-high rolling mill.

FIG. 9 is the same side view of FIG. 8;

FIG. 10 is a schematic diagram showing roll deflection.

FIG. 11 is a schematic illustration of crown increase and decrease states.

[Explanation of symbols]

20
Housing 22, 24
Work roll 26
Rolled material 28, 30
Backup roll unit 32, 36
Backup shaft 34R, 34L, 38R, 38L Support roll 40
Rotating bearing 46, 4
8, 50, 52 Bearing 54

Pressure cylinder 56R, 56L
Roll guide 70
R, 70L
coil spring 72
Wedge means 74R, 74L
Slope 76

Wedge receiving part 80
Wedge 82

Fluid pressure cylinder 100
roll bending equipment

Claims (1)

[Claims] 1. A pair of work rolls for rolling down a rolled material, and a pair of backup rolls for rolling contact with each work roll, with bearings at both ends of each roll attached to a housing, and a bearing interval between the pair of work rolls. In a rolling mill in which a pressurizing means is incorporated in the housing to perform crown control by adjusting It is configured to be rotatably and axially movable attached to a backup shaft, and each separated support roll is equipped with a guide member that engages and holds them, and the guide member urges the support rolls toward or away from each other. A wedge receiving portion is formed between the pair of elastically biased guide members or between the fixed member and the guide member, and a wedge receiving portion is fitted into the wedge receiving portion on the housing side. a hydraulic cylinder means having a wedge;
A rolling mill characterized in that the spacing between the coaxial separation support rolls can be adjusted by expanding and contracting the wedge using the hydraulic cylinder means and adjusting the amount of movement in and out of the wedge receiver.