JPS61269920A - Meandering control device for multi-passes rolling mill - Google Patents

Abstract

PURPOSE:To prevent the meandering of a rolling material and to stabilize an operation by providing a detector for the transverse end position of a rolling material and a detector for the meandering rate of the rolling material to a multi-passes rolling mill having >=3 pieces of work rolls rotating at different peripheral speeds in one stand and changing independently the roll gaps of the rolling passes. CONSTITUTION:The rolling material S is rolled by work rolls 8 and 9, 9 and 10, 10 and 11 in the stage of rolling the material S with the multi-passes rolling stand having the work rolls 8-11 and backup rolls 7, 12. The transverse end position of the material S is detected by the optical detector 21 for the transverse end just before the material enters the space between the rolls 8 and 9. The resultant detection signal is fed to a meandering rate calculator 22 which inputs the calculated value to a relational calculator 23. Said calculator calculates relationally the meandering rate and a target signal 24 from a setter. The deviation signal for the meandering rate by such calculation is processed by a meandering controlling 25 and is applied to bending controllers 26a, 26b which drive liquid pressure cylinders 18a, 18b for the respective work rolls, thereby adjusting the work roll gaps and preventing the meandering of the rolling material.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a meandering control device for a rolling mill that is capable of performing multi-pass rolling in one stand.

[Prior Art] In rolling operations, the rolled material cannot remain in the center of the roll due to the conditions during rolling, and moves toward the end of the roll as the rolling progresses, as shown by the dashed line in FIG. The phenomenon in which this happens is well known and is called meandering.

Here, to briefly explain the meandering of rolled material in a normal rolling mill, when rolling a rolled material in a rolling mill, factors required for the rolled material itself, such as hardness difference in the width direction of the material, taper in the width direction, etc. , due to operational factors such as the center of the rolled material shifting from the center of the roll (off-center), an imbalance occurs in the rolling loads applied to the working side and drive side of the rolling mill, resulting in There will be a difference in the roll gap between the two sides. Therefore, the drawing speed of the material on the entry side of the rolling mill is faster on the side where the gap is enlarged. As a result, the rolled material moves toward the wide gap side with respect to the advancing direction (direction of arrow C) as shown in FIG.
As shown in the figure, the rolled material a tilts as if shaking its butt, and the inclined rolled material a advances perpendicularly to the axis of the rolling roll b, so the rolled material a expands the roll gap as shown by the dashed line. A lateral shift occurs in the direction of the current, and the gap widens further. The state of the roll gap at this time is as shown in FIG. 11, with the arrow f indicating the meandering direction. As described above, once the rolled material meanderes, it is no longer possible to restore it to a stable state.

As mentioned above, if there is a difference in the roll gap between the work side and drive side (hereinafter referred to as left and right) of the rolling mill, the rolled material will start meandering, so in order to prevent meandering, it is necessary to It can be seen that it is sufficient to carry out control to narrow the roll gap.

On the other hand, recently, RD (Rolling Drawing
ng) rolling methods have been developed to reduce the size of rolling mills, reduce roll wear, roll hard materials such as high-strength steel, and reduce edge drop. In addition, as an improvement to this RD rolling method, three work rolls with different circumferential speeds are installed in one stand.
One-stand multi-pass rolling method in which the rolled material is wound around the work roll and rolled in each pass between the work rolls, or the rolled material is not wound around the work roll and rolled between each pass. A one-stand multi-pass rolling method has been proposed that performs rolling, and compared to the one-stand one-pass rolling method, this one-stand multi-pass rolling method enables high reduction rolling with a lower rolling load and is superior in productivity. Moreover, it has the advantage of being suitable for downsizing of rolling lines.

[Problems to be Solved by the Invention] However, even in the above-mentioned single-stand multi-pass rolling method, as in the case of single-stand rolling, if there is a difference in the roll gap between the work side and the drive side of the rolling mill, the rolled material begins to meander, and once meandering occurs, it is difficult to restore it to a stable state. In addition, in order to prevent meandering in a single-stand multi-pass rolling mill, it is possible to apply tension to the rolled material at the entrance of the rolling mill, but since the plate is thick in the pre-process of cold rolling, if tension is applied. It requires a very large amount of power, and according to a trial calculation, for example, if the degree of unparallelism between the rolled material and the roll is 30 am in the first rolling pass, a rear tension of about 3 k (1/mm2) is required, and the plate thickness is 4 mm and the plate width is 1000 mm. , plate speed 500 mm/min.

If so, 1000KW of power would be required.

In view of these circumstances, the present invention has been developed to easily and reliably prevent the meandering of rolled material without using large amounts of power, thereby eliminating problems such as rolling stoppage, damage to the edges of the rolled material, and even plate breakage. This was done to achieve stability, increase production efficiency, and improve product yield.

[Means for Solving the Problems] In the present invention, in a rolling technique in which three or more work rolls are provided in one stand and a rolled material is simultaneously rolled at two or more points using at least one of the work rolls, each rolling A plate width edge position detector disposed below or above the passing surface of the rolled material on either the entry side or the exit side of at least one of the passes, and a signal from the plate width edge position detector. There is provided a device that determines the meandering amount of the rolled material based on the meandering amount, and a control device that can independently change the roll gap of the rolling pass according to the meandering amount.

[Function] Therefore, in the present invention, the amount of meandering in a predetermined rolling pass is determined based on the signal detected by the plate width end position detector, and the working side and drive side of the rolling pass are determined based on the amount of meandering. The roll gaps of each roll are adjusted separately, thereby preventing meandering of the rolled material.

[Example] Hereinafter, an example of the present invention will be described with reference to the accompanying drawings.

1 to 3 show a first embodiment of the present invention, in which roll chocks 1a, 1b,
2a, 2b, 3a, 3b, 4a, 4b,
5a, 5b, 6a, and 6b are slidably attached in this order from below in the vertical direction and along the edge wall extending in the vertical direction of the window, and the roll chocks 2a, 2b
, 3a, 3b, 4a.

4b, 5a, 5b have work rolls 8, 9, 10 .
11 is also roll chock la, 1b, 6a, 6b
A backup roll 7.12 is rotatably supported on.

Also, roll chock Ia is installed on the lower cross member of the housing post.
Hydraulic cylinder 1 so that the reduction blade acts on 1b
3a and 13b are disposed, and lowering screws 14a and 14b driven by an electric motor (not shown) which act on rolling chocks 6a and 6b with lowering blades are disposed on the upper cross member of the housing post. There is.

The rolled material S is formed between the work rolls 8 and 9.
It is inserted through the 0-th gear gap 15 and wound around the work roll 9, and then passed through the 20-th gear gap 16 formed between the work rolls 9 and 10, and further wrapped around the work roll 1.
0 and is inserted into the 30th loop gap 17 formed between the work rolls 10 and 11.

Also, between the roll chocks 2a, 3a, 2b, 3b, between the roll chocks 3a, 4a, 3t), 4t), and the roll chock 4a.

Hydraulic cylinders 18a, 1 are provided between 5a, 4b, and 5b, respectively.
8b.

19a, 19b, 20a and 20b are arranged so that each work roll 8, 9, 10.11 can be subjected to the required roll bending.

An optical strip width end position detector 21 is disposed at a required position on the inlet side or outlet 1 of the rolling mill. It is preferable to install the cough plate width end position detector 21 as close as possible to the rolling mill.
It is also better to install it on the entrance side. This is because there will be a difference in characteristics in the amount of deviation of the rolled material to be detected between when it is installed on the entry side and when it is installed on the exit side. As shown in FIG. 3, the meandering in the roll gap results in camber on the exit side of the rolling mill, and this camber changes rapidly because it becomes a curved line expressed by a hyperbolic function. Therefore, unless the plate width end position detector is placed sufficiently close to the roll gap on the exit side, the amount of deviation of the rolled material S cannot be detected with good response. Furthermore, the detection delay from the roll gap to the detector results in wasted time.

On the other hand, on the entry side, if there is nothing that strongly restrains the rolled material S, such as a strong guide or strong dipping tension,
The rolled material S easily oscillates from one direction to the other due to the difference in elongation between the left and right sides, which causes meandering. Meandering occurs as mentioned above because it is drawn into the roll and spreads to the exit side in this state, but if a detector is installed on the entry side, in addition to the amount of deviation of the rolled material S due to meandering, the rolled material It is also possible to detect deviations due to the inclination of S.

To further explain with reference to FIG. 3, if the rolled material S is tilted by .theta. with respect to the rolling material traveling direction due to swinging, a deviation .delta. due to the inclination immediately appears on the entry side. On the exit side, the slope is integrated over time and spreads laterally. Therefore, as there is a time delay, the amount of deviation appears to be significantly smaller. In other words, the amount of deviation due to wobbling cannot be detected, and only the meandering caused by the wobbling of the rolled material S on the entry side can be detected.

On the other hand, the amount of deviation due to oscillation on the entry side tends to increase as the distance from the roll gap increases, so if a board width end position detector is installed on the entry side, it will be easier to detect the oscillation state that is the pre-meandering stage. In addition, it can be detected immediately and meandering control can be performed with good response. δ' is the initial meandering amount of the rolled material S.

The width end position signal of the board detected by the board width end position detector 21 can be sent to the meandering amount calculator 22, and the meandering amount calculator 22
The meandering amount signal calculated by the comparator 23 is sent to the comparator 23 so that the meandering amount signal can be compared with the target value signal 24 from the setting device. The deviation signal ΔX is processed by the meander regulator 25 so that it can be applied as a bending pressure correction signal lJp to the bending controller 26a, 261), and in response to the bending pressure correction signal @Ap, the bending controller 26a.

A command is given from 26b to the servo valves 27a and 27b, and the left and right hydraulic cylinders 18 are activated by the servo valves 27a and 27b.
a.

The amount of pressure fluid flowing into and out of the servo valves 27a and 27b can be controlled, and the hydraulic cylinder iaa
, a pressure detector 28a in a pipe line that sends pressure liquid to IAB.

28b is provided so that the pressure of the hydraulic fluid sent from the servo valves 28a, 28b to the hydraulic cylinders 18a, 18b can be detected, and the pressure signals detected by the pressure detectors 18a, 18b are transmitted to the bending controllers 26a, 26b. Make it possible to back up your feedback.

In the figure, 29 is a 20th gap balance control system, and 30 is a 30th gap balance control system. The work roll 10 can be held at a predetermined position by supplying pressure fluid at a predetermined pressure to the hydraulic cylinders 19a and 19b. and the hydraulic cylinder 20a.

Work roll 11 is supplied with pressure liquid at a predetermined pressure to 20b.
is pressed against the backup roll 12. Further, 32 is a working side of the rolling mill, 33 is a driving side thereof, and A is a rolling control system.

At the beginning of rolling, as the target value for the position of the rolled material, for example, the value of the initial passing position of the rolled material S detected by the plate width end position detector 21 after turning off a relay (not shown) is given to the memory circuit. The output is sent to the comparator 23 as a target value signal @24 for meandering control.

The width end position signal of the rolled material S continuously detected by the plate width end position detector 21 is sent to the meandering calculator 22, where the meandering amount of the rolled material S is calculated, and the meandering amount signal and the target value signal 24 are output. are compared and calculated by the comparison calculator 23, and the obtained meandering amount deviation signal A
x is applied to the meander adjuster 25, where the roll bending pressure correction signal Ap is, for example, Td is the differential gain and TI is the integral gain.

The roll bending pressure correction signal Ap obtained by the meandering controller 25 is sent to the bending controllers 26a and 26b. For example, when the rolled material S meanders toward the working side 32, the bending controller 26a adjusts the bending pressure on the working side. Initial setting value 1) 711ip is subtracted from w,
In the bending controller 26b, Ap is added to the drive-side bending pressure initial setting value pW, and from the bending controllers 26a and 26b, the cape N-Ap, I)w+l is added.
Command signal corresponding to Up 1. tb is the servo valve 27a,
27b. For this reason, the servo valves 27a, 27b
The amount of pressure fluid supplied to the hydraulic cylinders 8a, 18b and the amount of pressure fluid discharged from the hydraulic cylinders 8a, 18b are controlled, and the pressure on the hydraulic cylinder 8a side decreases by Ap, and the pressure of the hydraulic cylinders &b On the side, the pressure increases by Ap. In the work rolls 8 and 9, the roll bending pressure on the work side decreases and the roll bending pressure on the drive side increases, so that the roll gap on the work side is pinched and the roll gap on the drive side opens. Meandering of the rolled material S can be prevented by narrowing the roll gap on the closer side.
By controlling as described above, the rolled material S is moved to the working side 32.
This meandering is prevented and the value is returned to the target value.

The pressure detectors 28a and 28b continuously detect the roll bending pressure, and when the roll bending pressure reaches I)w-lUp on the work side and pv+4p on the drive side, a command signal is output from the bending controllers 26a and 26b. First, the servo valves 27a and 27b stop.

The inlet tension stress of the 10th gap 15, the 20th gap 16, and the 30th gap 17 is tl and t2, respectively.
．． If t3 is the tensile stress tl.

t2. t3 varies depending on the rolling conditions, but in particular, the tensile stress on the entry side of the 10th gap I-pipe 15 becomes low, and meandering is likely to occur in this gap, so as mentioned above, the 10th
Even if only the meandering of the 10th wheel gap 15 is prevented by controlling the 10th wheel gap 15, the rolling operation can be sufficiently stabilized.

FIG. 4 shows a second embodiment of the present invention with a 10th gear gap 15.
This is an example in which meandering control is performed in the same manner as in the case of FIG. 1, and the parallelism of the work rolls is controlled at the 30th roll gap 17.

The roll chocks 4a and 4b have displacement gauges 34a and 34.
b is .

It is installed so that the detection signals of the displacement meters 34a and 34b can be sent to the comparator 35, and the signal from the comparator 35 is connected to the output of the target value setting circuit 38 composed of a relay 36 and a memory circuit 37. The parallelism deviation signal obtained by the comparison is processed by the parallelism control adjuster 40 and installed as a left and right parallelism correction signal, and the parallelism correction signal is applied to the bending controller. 41a
, 41b, and the bending controller 4
From 1a and 41b, hydraulic cylinders 20a and 20b
a servo valve 42a that controls the amount of pressure fluid flowing into and out of the
42b so that a command signal can be sent to the pressure detector 43
The hydraulic pressure in the hydraulic pressure cylinders 20a, 20b detected by a, 43b can be fed back to the bending controllers 41a, 41b.

Now, at the time of initial setting to start rolling, the rolling screws 14a and 14b are lowered by driving an electric motor (not shown) without passing the rolling material S, and a load is applied, and each roll is brought into contact with the left and right rolls. Adjust the hydraulic pressure reduction system A on the working side and the driving side so that a load difference does not occur (this operation is generally called leveling).

When the leveling is completed, the relay 36 of the target value setting circuit 38 is turned on and the memory circuit 37 stores the current value in the comparator 3.
Store the output of step 5. This is the 30th leg gap 17
This is the target value for parallelism control.

Thereafter, the rolled material S is passed through the rolling screws 14a, 14b and the hydraulic cylinder 13 for rolling down as shown in FIG.
A load is applied at points a and 13b, and the first, second, and 30th wheel gaps 15, 16, and 17 are set, and rolling is started.

During rolling, the meandering control described in the first embodiment is performed, and the displacement meters 34a and 34b continuously detect the vertical displacement of the work roll 10, and the signals are compared by the comparator 35. The difference between the signal from the displacement meter 34a and the signal from the displacement meter 34b is determined.
In other words, the parallelism of the 30th loop gap 17 is obtained. This parallelism signal is compared and calculated with the target value from the storage circuit 37 in the comparator 39, and the difference is input to the parallelism control adjuster 40. The amount of pressure correction of the bending pressure control system between the two is calculated. For example, the 30th-le gap 17
If the work roll 10 is tilted such that the working side 32 is wide and the driving side 33 is narrow, the roll bending pressure on the driving side will be increased and the roll pending force on the working side will be reduced by the same amount. When the work roll 10 becomes parallel to the work roll 11, that is, when the difference between the left and right sides of the 30th wheel gap 17 disappears, the parallelism deviation of the work roll 10 becomes zero.

In single-stand multi-pass rolling, especially when rolling thin materials, slight deviations in the parallelism of the 30th wheel gap 17 can cause defects in the shape of the material, causing plate breakage, etc., and hindering rolling. There was a risk. However, these problems can be solved by performing parallelism control. In addition,
In the part of the roll gap 17, parallelism control is not performed,
Meandering control similar to that in the tenth loop gap 15 may be performed.

FIG. 5 shows the third embodiment of the present invention, and in this embodiment, the 10th-
Meandering control is performed in the double gap 15, and the second and third
This is an example in which parallelism control is performed with an 0-rail gap of 16.17.

Roll chocks 3a and 3b have displacement gauges 44a and 44b.
A fourth
The detection signal of the displacement meter 34b described in the figure is sent to the comparison calculators 35 and 45a, and the detection signal of 34b is sent to the comparison calculators 35 and 45a.
5b, respectively, and the comparison calculators 45a,
The signal obtained in step 45b is made to be able to be subjected to a comparison calculation in a comparison calculation unit 46, and the signal from the comparison calculation unit 46 is connected to the output of a target value setting circuit 49 constituted by a relay 47 and a memory circuit 48 and a comparison calculation unit 50. The deviation signal obtained by the comparison is processed by the parallelism control adjuster 51 to be taken out as a left and right parallelism correction signal, and the parallelism correction signal is applied to the lowering controllers 52a and 52b. From the pressure reduction controllers 52a and 52b, the hydraulic cylinder 13a
, 13b A displacement meter 54a that can send command signals to the servo valves 52a and 52b that control the amount of pressure fluid flowing out, and detects the ram positions of the hydraulic cylinders 13a and 13b.

The detection signal of 54b can be fed back to the pressure reduction controllers 52a and 52b.

At the initial setting before rolling starts, load is applied in the same way as in the case described above, and adjustments are made to the hydraulic reduction systems on the work side and drive side so that each roll is in contact and there is no load difference between the left and right sides. Perform leveling and 30th - after leveling
The target value for parallel control of the loop gap 17 is stored in the storage circuit 37 by the above-described operating procedure. This becomes the target value for the parallelism control of the 20th leg gap 16 and the 30th leg gap 17. Thereafter, the rolled material S is passed through as shown in FIG. 1, a load is applied to each roll, the 1st to 30th roll gaps are set, and rolling is started.

Meandering control in the 10th gear gap 15 and the 30th gear
Parallelism control in the double gap 17 is performed as described above. Further, the detection signals of the displacement meters 44a, 44b are sent to the comparators 45a, 45b, and the detection signals of the displacement meters 34a, 34
The detection signal b is sent to a comparison calculator 45a outside the comparison calculator 35.
, 45b, and is also sent to the comparator 45a.

45t), since the work rolls 9 and 10 can each freely move up and down, the difference in the amount of vertical movement is determined on the work side 32 and the drive side 33, and this difference in amount of movement is calculated by the comparator 4.
6, the left and right parallelism of the 20th loop gap 16 is determined. This parallelism signal is sent to the comparator 50
It is compared with the target value from the memory circuit 48 and calculated, and the difference is inputted to the parallelism control regulator 51.The parallelism control regulator 51 sends it to the reduction control system to adjust the parallelism of the 20th gear gap 16. The amount of position correction is calculated. For example, the 20th
- When the work roll 9 is inclined such that the working side 32 of the wheel gap 16 is narrow and the driving side 33 is wide, the ram of the hydraulic cylinder 13a is lowered and the ram of the hydraulic cylinder 13b is raised by the same amount. The target value to be stored in the storage circuit 48 is provided by turning on the relay 47 to output the output of the comparator 46 after leveling, as in the case of parallelism control of the 30th-level gap 17 described in FIG.

Note that while the 20th roll cap 16 is being controlled, the 10th roll gap 15 and the 30th roll gap 17 may also be affected by it, causing the left and right roll gaps to go out of order. system and parallelism control system, and ultimately all of the 1st to 30th loop gaps are stabilized. Further, the 20th wheel gap 16 may also perform meandering control in the same manner as the 10th wheel gap 15 instead of the parallelism control.

FIGS. 6 and 7 show a fourth embodiment of the present invention, in which the rolled material S is not wound around the work rolls, but pull-out rolls 55 and 56 are provided before and after the work rolls 9 and 10, and the rolled material S is pulled out from the pull-out rolls 55 and 56. This is an example in which guidance is provided at .56 and meandering control is performed at the full-time loop gap. In this embodiment, the meandering control in the 10th gear gap 15 is performed by the hydraulic pressure cylinders 13a and 13b for pressure reduction via the lower pressure reduction control system, and the 20th
- Meandering control at the double gap 16 is performed by bending control system B.
cylinders 19a, 19 for roll bending via
The meandering control at the 30th gear gap 17 is performed by a hydraulic cylinder 57 provided in place of the reduction screw 14.
a and 57b, the upper pressure reduction control system C is used. The configurations of the reduction control systems A and C are essentially the same as those shown in the third embodiment. In the figure, 58, 66 and 74 are board width end position detectors, 59°67 and 75 are meandering amount calculators, and 60
．． 68.76 is a comparison calculator, 61.69.77 is a target value for the position of the rolled material, 62, 70.78 is a meandering adjuster, 63a
, 63b, 79a, 79b are pressure reduction controllers, 71a
, 71b is a bending controller, 64a, 64b,
72a.

72b, 80a, 80b are servo valves, 65a, 6
5b, 73a, 73b.

81a and 81b are displacement gauges for detecting the amount of displacement of the hydraulic piston ram, and 83 is a tenth gear gap balance control system.

With such a configuration, the meandering in the 20th loop gap 16 is independently controlled by the bending control system, and the bending control system
The meandering control at the first and second wheel gaps 15 and 20th wheel gap 17 is independently controlled by the reduction control systems A and C, respectively. The specific control method is substantially the same as in the first and third embodiments, but the bending control system B of the 20th loop performs position control rather than pressure control.

In this embodiment, since the position of the 20th wheel gap 16 is controlled independently, the mutual interference between the roll gap controls is weak, and the 10th wheel gap 15 and the 30th wheel gap 17 are also controlled independently. The range over which control is effective is wide. Note that the configuration of the actuator of this embodiment may be maintained as is, and the parallelism control of an arbitrary roll gap may be performed by determining the difference between the left and right roll gaps as described in the second and third embodiments.

FIG. 8 shows an example of a plate width end position detector used in the meandering control device described above, in which a light source 87 is installed below the rolled material S, and a light source 87 is installed below the rolled material S.
The light from 7 is transferred to a board width end position detector 88 as shown in FIG.
It is designed to receive light. In this way, the rolled material S
When board width end position detectors 88 are installed on both sides of the board, a comparator 89 compares and calculates the difference between left and right signals, and the B difference signal is taken out as the meandering amount.

FIG. 9 shows the details of the above-mentioned sheet width edge position detector, in which the light emitted by the light source 870 below the rolled material S is emitted by the lens 8 provided in the intake part 84.
5, and the width end position of the rolled material S is detected by focusing the light onto an element group 86 having a large number of elements at equal intervals.

Now, let us assume that the total number of elements is N and the field of view length is such that the length of the end of the rolled material X hides the light source 87 and does not receive light. By measuring , the board width end position can be determined.

The same reference numerals are given to the middle parts of each of the above embodiments.

It should be noted that the control circuit used in the present invention can be configured not with hardware but with software using a computer, that the light source and detector can be installed on either the entry side or the exit side of the rolling mill, and that the light source and detector can be installed on the upper or lower side. The opposite may also be true, for example the meander regulator may be a simple amplifier circuit, i.e. a circuit using proportional gain, or a proportional and differential circuit;
It goes without saying that proportional, differential, and integral circuits can be used appropriately depending on the type of rolling disturbance, and that various other changes can be made without departing from the gist of the present invention.

[Effects of the Invention] According to the meandering control device for a multi-pass rolling mill of the present invention, rolling can be stabilized by preventing meandering of the rolled material, and as a result, accidents due to meandering of the rolled material can be prevented and operation can be improved. rate has improved,
Furthermore, unlike the case where high tension is applied to prevent meandering, a large amount of power is not required, so various excellent effects such as contributing to energy saving can be achieved.

[Brief explanation of the drawing]

1 to 3 are explanatory diagrams of the first embodiment of the present invention, and
The figure is a side view, Figure 2 is a front view, Figure 3 is an explanatory diagram of the installation position of the board width end position detector, Figure 4 is a front view of the second embodiment of the present invention, and Figure 5 is the present invention. Figures 6 and 7 are explanatory diagrams of the fourth embodiment of the present invention. Figure 6 is a side view, Figure 7 is a front view, and Figure 8 is a diagram used in the present invention. FIG. 9 is a detailed explanatory diagram of the detecting section, and FIGS. 10 and 11 are explanatory diagrams of the principle when meandering occurs in a rolled material. In the figure, 8.9 and 10.11 are work rolls, 13a, 1
3b. 18a, 18b, 19a, 19b, 20a,
20b is a hydraulic cylinder, 15 is a 10th lever gap, 1
6 is the 20th leg gap, 17 is the 30th leg gap,
21.5B, 66, 74 are board width end position detectors; 22.
59.67, 75 are meandering amount calculators, 23.35.39.
45a, 45b, 46a, 46b, 50.60
．． 68.76 is a comparison calculator, 25, 62, 70.78 is a meandering adjuster, and 26a. 26b, 41a, 41b, 71a, 71b are bending controllers, 27a, 27b, 42a, 42b,
53a, 53b, 64a, 64b, 72a, 72
b is a servo valve, 38.49 is a target position setting circuit, 40.
51 is a parallelism control adjuster, A and C are a lowering control system, and 8 is a bending control system. Figure 1 Figure 3 Figure 6

Claims (1)

[Claims] 1) In a rolling mill that has three or more work rolls in one stand and simultaneously rolls a rolled material at two or more points using at least one of the work rolls, at least one of each rolling pass is A plate width edge position detector is installed below or above the passing surface of the rolled material on either the entry side or the exit side of one pass, and rolling is performed based on the signal from the plate width edge position detector. A device for determining the amount of meandering of the material and a control device that can independently change the roll gap on the working side and drive side of the rolling pass according to the amount of meandering are provided to prevent meandering of the rolled material. A meandering control device for a multi-pass rolling mill featuring: 2) In a rolling mill that has three or more work rolls in one stand and simultaneously rolls a rolled material at two or more points using at least one of the work rolls, the entry side of at least one of each rolling pass. Alternatively, the meandering amount of the rolled material is determined based on a strip width end position detector disposed below or above the passing surface of the rolled material on either the exit side and the signal from the strip width end position detector. a control device that can independently change the roll gap on the working side and drive side of the rolling pass according to the amount of meandering; and a control device that directly or indirectly detects the roll gap in the rolling pass where meandering control is not performed. Detectors provided on the left and right sides of the work roll, a device that calculates the difference between the left and right detectors to determine the difference between the roll gaps on the working side and the driving side, and a device that calculates the difference between the roll gaps on the working side and the driving side according to the roll gap difference.
1. A meandering control device for a multi-pass rolling mill, comprising a bending control device that can independently change the roll gap on the driving side to prevent meandering of a rolled material. 3) In a rolling mill that has three or more work rolls in one stand and simultaneously rolls a rolled material at two or more points using at least one of the work rolls, the entry side of at least one of each rolling pass. Alternatively, the meandering amount of the rolled material is determined based on a strip width end position detector disposed below or above the passing surface of the rolled material on either the exit side and the signal from the strip width end position detector. a control device that can independently change the roll gap on the working side and drive side of the rolling pass according to the amount of meandering; and a control device that directly or indirectly detects the roll gap in the rolling pass where meandering control is not performed. Detectors provided on the left and right sides of the work roll, a device that calculates the difference between the left and right detectors to determine the difference between the roll gaps on the working side and the driving side, and a device that calculates the difference between the roll gaps on the working side and the driving side according to the roll gap difference.
1. A meandering control device for a multi-pass rolling mill, comprising a rolling reduction control device that can independently change the roll gap on the drive side, and configured to prevent meandering of a rolled material.