JP3075107B2 - Rolling equipment - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling machine having a device for controlling or supporting a work roll of upper and lower small diameters at a position which is deviated in a horizontal direction or slightly vertically from a horizontal direction.

[0002]

2. Description of the Related Art In recent years, it has been required to finely and accurately correct the shape of a rolling device in the width direction of a rolling mill, and to perform rolling of a material having a higher deformation resistance than a conventional material at a rolling reduction substantially equal to that of the conventional material. For the purpose, the work rolls 3, 4 supported by the upper and lower rolls 5, 6, 7, 8 as a 6Hi rolling mill or the work rolls 5, 4 as a 4Hi rolling mill have a small diameter of 400 mm or less within a range allowable in strength, A rolling machine has been developed that has a work roll horizontal support device that supports the upper and lower work rolls 3 and 4 to which a rolling load is applied at a position that is shifted in the horizontal direction or slightly vertically from the horizontal direction, at least in the same rolling direction. Have been. FIG.
4 (a) and 4 (b) (FIG. 4 (b) shows B-
As shown in the figure, the work rolls 3 and 4 which are vertically arranged opposite to the rolling device 1 and press down the rolled material 2 from above and below are respectively substantially horizontal. By supporting the work rolls from the direction, in addition to the function of rolling while preventing the shape of the work rolls 3 and 4 from being distorted due to the horizontal deflection, a positive pressing force is applied to the work rolls 3 and 4 from a substantially horizontal direction. Thus, the horizontal restraining rolls 11 and 12 that generate the bending force of the work roll chocks that support the work rolls 3 and 4 in the horizontal direction are divided into n and divided i.
The second roll 11-i and 11-i + 1 and 12-i and 12-i + 1
The horizontal pressing force is arbitrarily distributed by the hydraulic cylinders 13-i, 14-i buried in the housing to the shaft portion between and / or the roll end shaft, and the work rolls 3, 4 have a high degree of freedom. A horizontal bending is generated, and the high degree of freedom horizontal bending is converted into a high degree of freedom bending in the thickness direction along the vertical stay rolls 7 and 8, thereby controlling the shape of the rolled material 2 to control the rolled material. 2 also has a function of controlling the shape. In the example of the rolling device 1, if the work rolls 3 and 4 are bent to the horizontal exit side, the center of the roll gap between the upper and lower work rolls 3 and 4 becomes narrower with respect to the end of the roll, and the shape of the rolled material 2 becomes medium. If the work rolls 3 and 4 are bent inward in the horizontal direction, the roll gap between the upper and lower work rolls 3 and 4 becomes narrower at the roll end with respect to the center, and the shape of the rolled material 2 can be changed. Can be changed in the direction of the ear wave.

In such a rolling apparatus 1, work roll chocks 31 (upper side, not shown), 41 for horizontally supporting the work rolls 3, 4 and the work rolls 3, 4 are provided.
For example, the allowable limit load of horizontal bending is limited by the radial bearing strength of the work, and the work rolls 3 and 4 have small diameters. Therefore, the allowable limit load is much lower than that of a normal large-diameter rolling mill. About 10 tons). Therefore, if the horizontal bending force applied to the upper and lower work roll chocks 31 and 41 is different, the horizontal bending allowable limit load is easily reached by the difference between the upper and lower bending forces, and the control range of the horizontal bending is narrowed. FIG. 5 shows a case where the bending force is applied to the upper and lower work rolls 3 and 4 equally from the state where the bending force is applied only to the center position of the upper work roll chock 31. When the work roll 3 reduces the bending force, the lower work roll 4 reaches the allowable limit load first, and the target bending force is applied to the other work roll that has not reached the allowable limit load. There is a disadvantage that the strength of the equipment becomes dangerous and the usable range of the bending force becomes narrower than the intended use range of the bending force. In addition, when the rolling apparatus 1 does not actively use the horizontal bending of the work rolls 3 and 4 for shape control, but simply supports the work rolls 3 and 4 from the horizontal direction, for example, initial setting failure, For example, even when the pass line changes due to the above, bending forces having different magnitudes may be generated on the upper and lower work rolls 3 and 4. When the horizontal bending force of the upper and lower work rolls 3 and 4 is different, the horizontal deflection of the upper and lower work rolls 3 and 4 is different, and the work rolls 3 and 4 are offset from each other in the rolling direction. Problems such as difficulty in shape control due to change in lateral stiffness and warpage of the rolled material 2 also occur. In order to eliminate such inconveniences, the horizontal pushing cylinders 13-0 to 13-0-1 are so adjusted that the horizontal bending force applied to the upper and lower work roll chocks 31, 41 is equal.
It is necessary to set 3-n, 14-0 to 14-n,
In the conventional rolling mill, (1) the amount of movement of the upper and lower horizontal support devices from the reference position setting such as zero adjustment is made equal. (2) Make the pushing force of the upper and lower horizontal support devices equal. The setting of such a horizontal support device is performed.

[0004]

The rolling hydraulic cylinder of a rolling mill is usually mounted on either the lower part or the upper part of the rolling equipment. Changes. For example, when the hydraulic cylinder is pushed up to increase the load when the hydraulic cylinder for lowering is at the lower part of the rolling mill, the pass line rises and the offset between the work rolls 3 and 4 is temporarily generated. Therefore, assuming that the upper work roll 3 bends on the outgoing side and the lower work roll 4 bends on the incoming side, the upper pressing force is increased by the amount required to generate the bending force required to bend the upper work roll 3. In the direction in which the pressure increases. That is, the upper pressing force is increased by the amount required to generate the bending force required to bend the upper work roll to the outgoing side, and the bending force required to bend the lower work roll to the incoming side is generated on the incoming side in the rolling direction. The lower pressing force becomes smaller by the amount of the movement. In addition, the horizontal force between the work rolls acts in a direction in which the offset between the work rolls 3 and 4 is enlarged (the upper work roll 3 is on the outgoing side and the lower work roll 4 is on the incoming side). Further, the reaction force from the holding rolls 5 and 6 also acts so that the upper side is smaller and the lower side is larger by the amount by which the offset of the upper work roll 3 is reduced. Due to these forces, a vertical difference is generated in the direction in which the upper pressing force is reduced and the lower pressing force is increased. There is a characteristic.

As a result, as shown in FIG. 6, the above-mentioned force acts in the direction of increasing the upward pushing force, but the above-mentioned force acts in the direction of decreasing the upward pushing force. Further, the vertical difference in the pressing force generated by the above does not depend on the value of the rolling load at that time, but the vertical difference in the pressing force due to the rolling load changes depending on the rolling load. Therefore, there is a singular point rolling load in which the effect of the pressing force is exactly balanced and the horizontal pressing force in the vertical direction does not change even if any offset between the work rolls 3 and 4 occurs. When an offset between the work rolls 3 and 4 occurs, if the load is lower than the singular point load, the upper pressing force increases, and if the load is higher, the lower pressing force increases. When the work rolls 3 and 4 have small diameters,
Since the work rolls 3 and 4 are easy to bend, the vertical difference in the horizontal bending force of the work roll and the vertical difference in the horizontal pressing force generated by the above-mentioned effect have a relatively small value. In the small-diameter work roll rolling device, the singular point load described above exists in the rollable load range of the rolling device in the small-diameter work roll rolling device because the value is relatively large in the small-diameter work roll rolling device because the value increases in inverse proportion to the roll diameter. I do. Therefore, the above-described method of setting a horizontal push cylinder has the following problems.・ If the upper and lower horizontal pressing forces are set equal, the direction in which the pressing force on the side with the increased pressing force is reduced, that is, the horizontal supporting device is pulled in the pulling direction, and the pressing force on the side with the reduced pressing force is increased. The horizontal support device acts in the direction of pressing the horizontal support device, that is, in the direction of pushing the horizontal support device. However, when the rolling load is equal to or more than the singular point (S point) load, the effect is larger, so that the work roll 3 is changed by the change of the pass line. , 4, the downward pushing force increases. for that reason,
Since the horizontal support device acts not in the direction of converging the offset between the work rolls 3 and 4, but in the direction of expanding it,
On the contrary, there is a problem that the offset between the work rolls 3 and 4 is increased.

FIG. 7 shows a rolling device 1 in which work rolls 3 and 4 are provided.
It shows a change due to the load of the vertical difference of the horizontal pushing force generated when an offset exists between them. When the horizontal support device is set so that the upper and lower horizontal pressing forces are equal to each other, the upper pressing force is larger than the lower pressing force at a load lower than the S point. The horizontal support device acts to displace the roll 4 to the output side, and the offset between the work rolls 3 and 4 can be eliminated.
Even if an inter-offset exists, it is a singular point where no vertical difference in the pressing force occurs, so that the offset between the work rolls 3 and 4 cannot be eliminated. Therefore, the upper and lower work rolls 3
It is impossible to set the value of the horizontal bending force of the same. In addition, even if the upper work roll 3 is on the exit side at a load higher than the point S, the upper work roll 3 has a large downward pressing force.
Work rolls 3 and 4 because the horizontal support device acts to displace the lower work roll 4 to the entry side.
The inter-offset increases, and eventually rolling becomes impossible.
Therefore, it is understood that it is impossible to prevent the offset between the work rolls 3 and 4 by the control for equalizing the vertical pressing force. If the moving amounts of the upper and lower horizontal support devices are set to be equal, the set positions of the upper and lower horizontal support devices are equal regardless of the movement of the pass line.
Is displaced to the outgoing side along the upper split roll 10-i, and the lower work roll 4 is displaced to the incoming side along the lower split roll 11-i. In other words, the upper work roll 3 bends toward the exit side in the rolling direction and the lower work roll 4 bends toward the entrance side in the rolling direction, so that an offset between the work rolls remains. The thick line in FIG. 7 is an example of measuring the vertical difference of the horizontal pressing force. As the load increases, the pass line rises, and the offset between the work rolls 3 and 4 increases. Therefore, as shown by the thick line, the vertical difference in the pressing force changes on a curve in which there is a different offset between the work rolls 3 and 4 for each rolling load, and thus shows a complicated behavior.

FIG. 8 shows a rolling device 1 in which the upper and lower work rolls 3 and 4 are brought into contact with a load of 200 ton, and at this time the positions of the upper and lower horizontal support devices are fixed. This is an example in which the horizontal deflection of the upper and lower work rolls 3 and 4 was measured when the number increased and decreased. The pass line changes upward as the load increases, and the upper work roll 3
Moves to the outgoing side, the lower work roll 4 is displaced to the incoming side, and the difference between the horizontal deflections of the upper and lower work rolls 3, 4 increases.
It can be seen that the horizontal deflection difference between the upper and lower work rolls 3 and 4 is proportional to the amount of change in the pass line. Further, in the setting of the conventional horizontal support device, when the pass line P changes, FIG.
As described above, the offset is different in the width direction of the work roll, and the shape becomes an ear wave more than the original lateral rigidity of the rolling device, and there is a problem that the shape control of the rolling device becomes difficult and the rolled material 2 is warped. As described above, when the horizontal bending of the work rolls 3 and 4 is used for shape control, there is a difference in the bending force applied to the upper and lower work roll chocks, so that there is a problem that the horizontal bending cannot be used effectively. is there. FIG. 9B is a horizontal deflection distribution diagram of the work rolls 3 and 4, and FIG. 9C is a vertical deflection distribution diagram of the same. The present invention has been made in order to solve the above problems, and is intended to prevent an offset between upper and lower work rolls from occurring.
Plate rolling that always keeps the pass line at the set position
It is intended to provide a device .

[0008]

According to the rolling apparatus of the present invention, the upper and lower small-diameter work rolls and the upper and lower small-diameter work rolls are flexed in the horizontal direction at positions slightly shifted from the horizontal direction or the horizontal direction. a device for supporting or Maseru, comprising upper and lower one or more stages of the backup roll, the upper
To each of the bottom of the backup roll, Pasura during rolling
Maintains the pass line in its original position when the in changes
A pressure reducing device for controlling the pressure reduction is provided . Further, the rolling device of the present invention can
An arithmetic unit that calculates the amount of change or the thickness or the upper and lower
Vertical relative position between small diameter work roll and housing
A computing device or a measuring device, comprising a measuring device for measuring
Controlling the upper and lower pressure reduction devices based on the output of
It is a feature.

[0009]

In the rolling apparatus of the present invention, the upper and lower
Since a roll- down device is provided for each roll, when the pass line changes up and down, the roll- down devices up and down are actuated by the amount of the change to offset the change in the pass line, and the pass line is always set at the original set position. To be maintained.

[0010]

[Embodiment 1] Hereinafter, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is an explanatory diagram showing a schematic configuration of a rolling apparatus according to one embodiment to which the present invention is applied. In the drawing, reference numeral 1 denotes a rolling device, which shows the entire configuration of this device. 2 is a rolled material. Reference numerals 3 and 4 denote work rolls for stretching the rolled material 2. Reference numerals 5 and 6 denote intermediate rolls which directly back up the work rolls 3 and 4. 7, 8 are backup rolls, and intermediate rolls 5, 6
The work rolls 3 and 4 are indirectly backed up via. In this case, the upper and lower work rolls 3 and 4 are formed to have a small diameter within an allowable range in strength. Further, the upper and lower work rolls 3, 4 are respectively provided with pressing rolls 9, 10, which are pressed from the entry side in the sheet passing direction, and further with the pressing rolls 9, 4,
The division rolls 11 and 12 for pressing the workpiece 10 in the direction of the work rolls 3 and 4 are arranged so as to be sequentially aligned. The divided rolls 11 and 12 have a plurality of roll portions 11-i and 12-i (i = 1 to n, n = 5 in this embodiment) on their axes.
Are distributed. The split rolls 11 and 12 have their ends and the axis between the rolls aligned with the horizontal cylinders 13-i and 14-i (i = 0) arranged in the housing.
To n, in this embodiment, n = 6 ), so that the rods are individually applied with a pressing force in the directions of the upper and lower work rolls 3 and 4 respectively. Each horizontal cylinder 13-i, 14-i
Are position detectors 15-i and 16-i for detecting the amount of movement.
(I = 0 to n, n = 6 in the present embodiment). The work roll horizontal support device includes the holding rolls 9 and 10, the split rolls 11-i and 12-i, and the horizontal cylinder 1
3-i, 14-i and position detectors 15-i, 16-i. Servo valves 17-i and 18-i for supplying pressure oil are attached to the horizontal cylinders 13-i and 14-i.

The upper backup roll 7 is supplied to the choke 31 via the load cell 21 via the hydraulic cylinder 19 for rolling down.
Are arranged. The lower backup roll 8 is provided with a hydraulic cylinder 20 for lowering the chocks 32 and is pressed vertically. Accordingly, a vertical rolling force can be generated between the work rolls 3 and 4 from above and below. This rolling force is detected by the load cell 21. The displacement hydraulic cylinders 19 and 20 each have a displacement meter 2 indicating the amount of vertical movement.
2, 23 are attached. The thickness of the rolled material 2 after stretching is measured by a thickness gauge 29. Also,
The hydraulic cylinders 19 and 20 for pressure reduction are connected to servo valves 25 and 26, and are controlled by a path line change amount calculating device 27 which operates based on data from the displacement meters 22 and 23. The change in the pass line is determined by the chocks of the work rolls 3 and 4 or the displacement meter 28 attached to the body.
In, it is also possible to measure the vertical relative position between the housing of the rolling device 1.

The rolling operation of this rolling device is as follows. The method based on the elongation of the rolling mill and the change in sheet thickness from the time of initial setting is caused by the change in the pass line. In the case of the present embodiment, when the lower backup roll 8 is raised and lowered by the hydraulic cylinder 20 for reduction, the plate is released. The following pass line changes occur on the upper and lower sides of the whirl rolling mill 1. -Rolling machine upper side: (a) Elongation of rolling machine by applying rolling load-Rolling machine lower side: (b) Elongation of rolling machine by applying rolling load, and (c) Change in sheet thickness from initial setting And (b) can be determined as follows. The sum of the elongations (a) and (b) of the rolling device is the elongation of the entire rolling device due to the application of a load. Assuming that the elongation increase δ of the entire rolling apparatus is a mill constant M and a load change ΔP from a reference rolling load (rolling load at the time of initial setting), δ = ΔP / M = (a) + (b) Therefore, if one of (a) and (b) is known, the other can be known. On the other hand, at the same time when the lower backup roll 8 is raised by the hydraulic cylinder 20 for lowering, the horizontal support device embedded in the housing is also raised. Since the upper and lower horizontal support devices are mounted at substantially vertically symmetrical positions of the housing, the elevation amounts of the upper and lower horizontal support devices are substantially the same. Since the elongation of the housing itself is as small as about 10% of the entire rolling device, the amount of rise of the horizontal support device is also small. From the above, for example, for (a), i) ignoring the amount of elevation of the horizontal support device, and assuming (a) = １ ／ × ΔP / M as half the elongation of the entire rolling device. ii) The amount of change in the upper side of the rolling machine and the amount of change in the horizontal support device with respect to the load change are measured in advance off-line, and the constant k is determined from this based on (a) = k × ΔP / M.

The above (c) can be obtained by the following. On the lower side of the rolling device, even if there is no change in the load, the rolling device moves by an amount corresponding to the change in the plate thickness (h), and the pass line changes. Therefore, it is necessary to consider the amount of change in plate thickness. As a method of obtaining the thickness variation Δh, a thickness gauge 29
Or from the change amount ΔS of the drafting device and the load change amount ΔP as Δh = ΔS−ΔP / M. Note that the present invention can be applied to a case where there is no offset between a work roll and a standby roll or an intermediate roll in contact with a work roll.

The rolling operation according to the above configuration is as follows. The calculation of the pass line is performed as follows. The factors of the pass line change are as follows: Upper roll side: Elongation of the upper side of the rolling mill + Movement amount of the upper rolling device (signal of the displacement gauge 22 ) Lower roll side: Elongation of the lower side of the rolling mill + Change in sheet thickness from the initial setting The elongation (upper side + lower side) of the entire housing of the rolling device 1 and the change in sheet thickness are obtained as described above.
Each signal of the rolling load detected by the load cell 21, the rolling position change detected by the displacement meters 22 and 23, and the sheet thickness detected by the sheet thickness gauge 29 is input to the pass line change amount calculating device 27. The lower pass line change amount is calculated. The calculation result is output to the servo valve 25, Pas
Maintain the line at the original setting . A method of actually measuring the change of the pass line The upper and lower work roll chocks (not shown) are provided by displacement gauges 28 attached very close to the holding rolls 9 and 10 forming the horizontal support device provided in the rolling mill 1.
Alternatively, by measuring the displacement of the work rolls 3 and 4, it is possible to measure the change of the pass line in a state where the rise of the horizontal support device due to the load change is offset. sand
That is, the relative displacement in the vertical direction between the work roll chock (not shown) or the body of the work rolls 3, 4 and the housing of the rolling device is measured by the displacement meter 28 . The output signal of the pass line change amount is input to the servo valves 25 and 26. Sa
-Bo valves 25 and 26 are in the position of hydraulic cylinders 19 and 20 for rolling down.
Hydraulic cylinders 19 and 20 so that the position is equal to the set value.
Control. When rolling without changing the pass line in such an operation, when the responsiveness of the rolling device on the upper side of the rolling mill is equivalent or dull compared to the lower side, the rolling device on the upper side of the rolling mill is connected to the upper pass line. Using the reduction amount corresponding to the change amount, the lower side reduction device operates by utilizing other control such as controlling the plate thickness.・ When the response of the rolling device on the upper side of the rolling mill is equivalent to that of the lower side,
In addition to eliminating the change in the pass line, the vertical pressing device is operated while using it for other controls such as controlling the plate thickness.
By performing this operation every short enough time to control the operation, it is possible to prevent a change in the pass line. It is possible to perform rolling. FIG. 2 shows that the upper and lower work rolls are brought into contact with a load of 200 ton, and the positions of the upper and lower horizontal cylinders are fixed at this time.
It is the measurement result of the vertical difference of the pressing force in the horizontal direction by increasing or decreasing the vertical rolling load while rotating the work roll. In the case of the related art, a complicated behavior appears as the vertical difference in the pressing force is indicated by a mark. On the other hand, according to the present invention, it can be seen that there is almost no change in the vertical difference of the pressing force as indicated by the circle. FIG. 3 shows the result of measuring the horizontal deflection of the upper and lower work rolls. It can be seen that according to the present invention, the horizontal deflection in the vertical direction hardly changes despite the rise of the pass line due to the load change. As described above, according to the present invention, it is apparent that an increase in the work roll offset due to a change in the pass line can be prevented.

[0015]

As described above, according to the present invention, in a rolling machine having a small-diameter work roll, the upper and lower
Since a rolling device is provided for each of the up rolls,
The pass line is always maintained at the set position by the upper and lower rolling devices.
Offset between the upper and lower work rolls
Not, therefore, to the shape of the rolled material is obtained based on the lateral stiffness of the original mill, it is possible to prevent occurrence of defects such as edge waving or warping of the rolled material. Further, when the horizontal bending is used for shape control, the horizontal bending can be used effectively because there is no restriction on the horizontal bending use range based on the deflection difference between the upper and lower work rolls.

[Brief description of the drawings]

FIG. 1 is an explanatory view showing a schematic configuration of an embodiment of a rolling device of the present invention.

FIG. 2 is an explanatory diagram showing a relationship between a vertical difference in a pressing force of a rolling device and a rolling load.

FIG. 3 is a graph showing a result of measuring a deflection of a work roll of a rolling device .

FIG. 4 is an explanatory diagram showing a schematic configuration of one embodiment of a conventional rolling device.

FIG. 5 is an explanatory diagram showing a range of use of a bending force with respect to an allowable bending force of a work roll of a conventional rolling device.

FIG. 6 is an explanatory diagram showing a change in an offset amount between work rolls in a conventional rolling device.

FIG. 7 is an explanatory diagram showing a relationship between a vertical difference in a pressing force of a conventional rolling device and a rolling load.

FIG. 8 is an explanatory diagram showing a relationship between a rolling load of a conventional rolling device and a horizontal deflection of a work roll.

FIG. 9 is an explanatory view schematically showing a state of deflection of a work roll with respect to a pass line of a conventional rolling device.

────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Naoki Ikeuchi 1-1-2 Marunouchi, Chiyoda-ku, Tokyo Inside Nippon Kokan Co., Ltd. (72) Inventor Hisaaki Kataoka 1-1-2 Marunouchi, Chiyoda-ku, Tokyo Nippon Kokan Inside (72) Inventor Shigefumi Hosoya 1-2-1, Marunouchi, Chiyoda-ku, Tokyo Nippon Kokan Co., Ltd. (72) Inventor Tatsuo Toyofuku 1-2-1, Marunouchi, Chiyoda-ku, Tokyo Nippon Kokan Co., Ltd. (56) References JP-A-63-286206 (JP, A) JP-A-8-117823 (JP, A) JP-A-2-284706 (JP, A) JP-A-5-169119 (JP, A) JP-A-3-114603 (JP, A) JP-A-57-106412 (JP, A) JP-A-59-10901 (JP, U) JP-A-59-157704 (JP, U) Int.Cl. ⁷ , DB name) B21B 3 1/20 B21B 13/14 B21B 29/00 B21B 37/00 BBH B21B 37/28

Claims (2)

(57) [Claims] An apparatus for bending or supporting a work roll in a horizontal direction at a position where each of the upper and lower small-diameter work rolls is displaced in a horizontal direction or slightly vertically from a horizontal direction, and one or more stages up and down Backup rolls , each of the upper and lower backup rolls during rolling .
When the path line changes, move the path line to its original position
A rolling reduction device provided with a reduction device for controlling the rolling device to maintain the rolling speed. 2. An arithmetic unit for calculating a change amount of a pass line.
Or plate thickness or the above and below small diameter work roll and housing
Equipped with a measuring device that measures the vertical relative position between
Based on the output of the computing device or measuring device
2. The reduction device according to claim 1, wherein the reduction device is controlled.
Rolling equipment.