JPS5848246B2 - Itazaiatsu Enkiniokel Keijiyouseigiyosouchi - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a shape control device for rolling a metal sheet material, particularly a rolling load width control by adjusting the axial movement of a roll;
The present invention relates to a shape control device that controls the shape of a rolled material by controlling roll pending force.

For example, in the rolling of metal sheets such as steel strips, a roll crown is attached in advance to reduce the thickness deviation in the width direction of the rolled material, that is, to control the shape. There are various ways to apply paint to the rolls, but among them, for example, in a six-high rolling mill, the intermediate roll is displaced in the axial direction to control the width of the rolling load applied to the rolled material. Recently, a method of controlling the shape of a rolled material, or a method of combining the above method with a method of imparting pendingness to the rolls, has been proposed and disclosed.

However, these excellent shape control devices still have the following technical problems to be solved.

In other words, the correlation between the shape of the material to be rolled and the rolling load width, and the correlation between the rolling load and the roll bending force can be grasped independently, and the correlation between the rolling load width and the roll bending force can be unified and integrated. These elements were not understood as control elements, and each was determined independently, creating a bottleneck in achieving highly accurate and accurate shape control.

This invention was made in order to solve the above-mentioned problems in the conventional shape control device for rolling plate material.

The feature of this rolling mill is that it has rolls that are configured to move in the axial direction of the rolls according to the width of the metal material to be rolled, and that is configured to apply a roll bending force. In this step, a shape influence coefficient is calculated from the actually measured rolling load and the roll axial movement amount, and the optimum roll axial movement amount and/or is calculated from the shape influence coefficient and the necessary shape correction amount obtained from the plate shape detection device. Alternatively, a shape control device in a plate rolling mill comprising a calculation device that outputs an optimum roll pending force, and a roll pending pressure setting device and a roll axial movement amount setting device that operate based on the output from the calculation device. be.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The shape control device for a plate rolling mill according to the present invention will be described in detail below based on an embodiment thereof with reference to the drawings.

FIG. 1 shows an example of a rolling mill to which the shape control device for a plate rolling mill according to the present invention is applied. In the figure, 1 is a material to be rolled, 2, 2' are work rolls, 3,
Reference numeral 3' denotes an intermediate roll, which is disposed between the work rolls 2, 2' and the reinforcing rolls 4, 4'. be moved in the direction.

5, 5' C. A roll venting device, the rolling mill shown in FIG.
By controlling the width of the rolling load applied to the material to be rolled 1 through the axial movement of the material, the shape of the material to be rolled is controlled, that is, the thickness deviation in the width direction of the material is controlled.

The present invention aims to provide a control device to be applied to a plate rolling mill configured in this manner, thereby making it possible to perform excellent shape control.

Figure 2 shows the amount of necessary shape correction, for example, the elongation rate in the rolling direction of the point lost in the strip width, and the elongation rate of 80 mm from the side edge of the strip toward the center point.
The horizontal axis is the amount of elongation correction necessary to eliminate the difference with the elongation rate at the mm point, the vertical axis is the amount of roll pending correction, and the relationship is shown in correspondence to the shape influence coefficient described later. It is.

The required shape correction amount is determined by shape detection that detects the shape of the rolled material 1 after passing through the rolling mill.

The shape influence coefficient α shown in FIG.
It is a dimensionless number that changes in response to changes in the rolling load width applied to the rolled material and changes in the rolling load caused by the axial movement of .

This is shown in Figure 3.

In the rolling mill shown in Fig. 1, the time when the body edge of the intermediate roll overlaps the edge of the material to be rolled 1 is defined as the transition roll, in this example, intermediate rolls 3 and 3', position O (zero), and the material to be rolled. The transition roll position (minus) is when the edge of intermediate row/1/3.3' is closer to the center in the width direction of the rolled material 1 than the edge of 1, and corresponding to the rolling load at that time,
The shape influence coefficient α is determined.

The rolling load is detected by a detection end such as a load cell.

The shape influence coefficient α is determined from the relationship between the rolling load thus determined and the width of the rolling load applied to the material 1 to be rolled.

From the shape influence coefficient α thus determined and the required shape correction amount, the optimum roll pending force is determined using the relationship shown in FIG.

On the other hand, it is of course possible to control the shape only by controlling the amount of axial movement of the intermediate rolls 3, 3'.

Figure 4 shows the relationship.

By moving the intermediate rolls 3 and 3' in the axial direction, the width of the rolled material 1 and
By changing the relationship with the load width applied to the rolled material 1, the amount of correction of the surface difference in elongation rate in the width direction of the rolled material 1 changes in accordance with the rolling load.

As mentioned above, when controlling the shape of the rolled material 1, the shape influence coefficient is determined from the rolling load and the load width applied to the rolled material, and the shape influence coefficient α is used as a parameter to determine the optimal roll pending. The amount of force correction can be obtained.

In addition, it is of course possible to control the shape by using the shape influence coefficient α as a parameter, fixing the roll bending force, and displacing the intermediate rolls 3, 3 in the axial direction.

That is, in the case of shape modification, roll bending force is used. Although it is possible to change either 10,000 yen or both of the roll axial movement amounts, in practice either 10,000 yen is fixed, and for example, first, the roll pending force is changed based on the degree of influence on operation and shape. It is more common to perform the adjustment, and if this is insufficient, to correct the roll axial movement amount at the next step.

If both are performed at the same time, the degree of shape correction and roll pending capacity under the rolling conditions at that time. Selection and adaptation are made depending on the size of the shape influence coefficient of each roll axial movement amount.

An example is shown in FIG.

In this figure, reference numeral 11 denotes a rolling load detector, for example a load cell is used, and a signal from the load cell is input to an arithmetic unit 12.

13 is a transition roll, in this embodiment intermediate rolls 3, 3;
The axial position detection device shown in FIG. 6, for example, is used.

In FIG. 6, 3 is an intermediate roll, which in this embodiment is a transition roll.

13-1 is a fluid pressure cylinder that displaces the intermediate roll 3 in the axial direction.

13-1a and 13-1b are fluid pressure cylinder chambers, and when fluid pressure is applied to the cylinder chambers 13-1a, the intermediate roll 3 is displaced to the left in FIG. 6.

Moreover, when fluid pressure is applied to the cylinder chamber 13-1b,
The intermediate opening -/[/3 is displaced to the right as viewed in FIG.

13-2 is a rack and pinion assembly,
The rack is displaced by the same amount as the axial displacement of the intermediate row/1/3.

Since the rack meshes with the pinion, the number of revolutions of the pinion corresponds to the amount of displacement of the rack.

Reference numeral 13-3 denotes a synchro transmitter, which is connected to the pinion by a shaft and transmits a number of signals corresponding to the rotation angle of the pinion.

13-4 is a synchro receiver that outputs a signal synchronized with the synchro oscillator.

The amount of axial displacement of the intermediate roll 3 is grasped by this synchro receiver 13-4.

The arithmetic unit 12 calculates and outputs the shape influence coefficient α based on the input signals from the rolling load detector 11 and the transition roll axial position detecting device 13 described above.

14 is an arithmetic device which receives the shape influence coefficient α output from the arithmetic device 12 and stores it.

When the magnitude of the rolling load changes during rolling, the calculation device 1
In step 2, a new shape influence coefficient is calculated, and the shape influence coefficient α of the arithmetic unit 14 is updated.

A shape control device 15 controls fluid pressure in the roll pending device 18 via a roll pending pressure setting device 17 in response to changes in the output from the shape detection device 16.

As the shape detector 16, for example, a device as shown in FIG. 7 is used.

In Fig. 7, S stands for step I-IJ, and 16-3 stands for
A drive signal generator, for example a square wave oscillator.

16-3a is an amplifier.

Reference numeral 16-4 denotes a detection head, which is provided along the width direction of the strip S at appropriate intervals on the surface of the strip S by appropriate engagement means.

This detection head 16-4 is composed of an external force applying device 16-4a and a displacement detector 16-4b.

The external force applying device 16-4a is composed of an electromagnet with an excitation coil B provided on a magnetic pole A having a U-shaped cross section along the width direction of the strip S, and the displacement detector 16-4b is arranged along the width direction of the strip S. A plurality of displacement measuring electrodes D are provided on the base portion C along the ridge so as to face the surface of the st-IJ sp S, and are provided integrally with the external force applying device 16-4a.

16-4C is a displacement conversion circuit such as a capacitance-to-voltage converter.

16-9 (1, signal processing circuit, polarity switch 16-5,
It consists of an integrating circuit 16-6, a sample and hold circuit 16-7, and a timing generating circuit 16-8 connected to each of the devices 16-5.1, 6-6.1, and 6-7. 8 is also a square wave oscillator 16
-3 is also connected.

The signal processing circuit 16-9 controls a display device 16- such as a CRT monitor via a display control device 16-10.
1 Connected to 1.

The operation of the shape detector 16 configured as described above will be explained. The rectangular wave oscillator 16-3 generates a rectangular wave with a predetermined period as a drive signal.

This drive signal is amplified in the amplifier 16-3a, and this amplified drive signal is applied as an external force to the surface of the strip S through the external force application device 16-4a, thereby causing displacement in the strip S. .

The displacement generated on the surface of the S I-IJ S is detected as a capacitance by the displacement detection electrode D provided in the displacement detector 16-4b, and converted into a displacement conversion circuit, that is, a capacitance-voltage Convert it to a voltage signal using a converter.

The plurality of displacement detection electrodes D provided along the width direction of the strip S similarly detect the displacement of each part of the corresponding strip S in the width direction, and after converting it into a voltage signal, the signal processing circuit 16-9 is input.

After switching the polarity of the displacement detection signal with a polarity switch 16-5, the signal is input to an integrating circuit 16-6, and the integrating circuit performs integration for each rectangular wave period to remove noise other than the tension signal.
Only the portions related to the tension in each portion of the IJ tube S in the width direction are calculated and input to the sample and hold circuit 16-1, where they are sampled and held.

The timing generation circuit 16-8 includes a square wave oscillator 16-3.
The polarity switching timing of the polarity switch 16-5, the sample hold timing of the sample hold circuit 16-7, and other timings are controlled based on the reference signal from the polarity switch 16-5.

The output of the sample and hold circuit 16-7 is displayed on a display device 16-11, such as a CRT monitor, via a display device control circuit 16-10.

In this way, with tension applied to the strip, the strip is vibrated and the amount of deflection at each part in the width direction of the strip S is detected to calculate the tension at each part in the width direction of the strip S. From this tension value, the strip It is used to know the shape of.

The shape control device in the plate rolling mill configured as described above controls the shape of the rolled material 1.

When controlling the shape of the rolled material by displacing the intermediate rows/1/3 and 3' in the axial direction, the shape is controlled based on the shape influence coefficient α obtained as described above and stored in the calculation device 14. In response to the output from the detection device 16, the intermediate roll 3,
The axial position correction amount of the intermediate rolls 3, 3' is calculated by the shape control device and output to the axial position setting device 19 of the intermediate rolls 3, 3', thereby setting the axial positions of the intermediate rolls 3, 3'.

At that time, the roll pending power takes a constant value.

In the embodiment described above, the rolling mill in which the intermediate rolls 3 and 3' are displaced in the axial direction in a six-high rolling mill is used, but the present invention is applicable to a rolling mill in which the work rolls or reinforcing rolls are displaced in the axial direction. It is clear from the description in the present specification that the invention is also applicable.

However, when applied to work rolls, it is limited to cases where the load width is larger than the width of the rolling mill.

The shape control device for a plate rolling mill according to the present invention is as follows:
Since the structure and operation are as described above, it is possible to control the shape with higher precision and accuracy.

[Brief explanation of the drawing]

FIG. 1 is a diagram showing an example of a rolling apparatus to which the present invention is applied, FIG. 2 is a diagram showing the relationship between the required shape correction amount and the roll pending roller, and FIG. 3 is a diagram showing the load on the material to be rolled. FIG. 4 is a diagram showing the relationship between the width and the shape influence coefficient; FIG. 4 is a diagram showing the relationship between the load width on the rolled material and the amount of shape modification; FIG. 5 is a diagram showing an embodiment of the present invention. , FIG. 6 is a side view showing an example of an axial position detecting device, and FIG. 7 is a perspective view showing an example of a shape detecting device. 1... Rolled material, 2. 2'...Work roll 3,3'...Intermediate roll, 4,4'
...Reinforcement roll, 5,5'...Roll pendink device, 6,6'...Roll axial direction moving device, 11...Rolling load detection Vessel, 12...
... Arithmetic device, 13 ... Axial position detector, 13-1 ... Cylinder for intermediate roll transfer, 1
3-1a, 13-1b...Hydraulic chamber, 13-2.
...Rack, 13-3...Synchronized oscillator, 13-4...Selsin, 14...
Arithmetic device, 15...Shape control device, 16...
...shape detector, 16-3...drive signal generator, 16-3a...amplifier, 16-4...
...Detection head, 16-4a... External force application device, 16-4b... Displacement detector, 16-4c...
...Displacement conversion circuit, 16-5...Polarity switch, 16-6...Integrator circuit, 16-7...
... Sample hold circuit, 16-8 ... Timing generation circuit, 16-9 ... Signal processing circuit,
1 6-1 0...Display control device, 16-11
... Display device, 17 ... Roll pending force adjuster, 18 ... Roll pending device, 19 ... Axial direction position setting device.

Claims (1)

[Claims] 1 Measured rolling in a rolling mill that has rolls configured to move in the axial direction of the rolls according to the width of the metal material to be rolled, and that is configured to apply a roll pending force. The shape influence coefficient is calculated in advance from the load and the roll axial movement amount, and the optimum roll axial movement amount and /or a calculation device that outputs an optimal roll venting force;
A shape control device for a plate rolling mill, comprising a roll pending pressure setting device and a roll axial movement amount setting device that operate based on an output from the arithmetic device.