JP3121942B2 - Rolling mill thickness control device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates relates to a plate thickness control system for a single stand rolling mill, more particularly, single to achieve a plate thickness control with high response in the rolling mill of the hydraulic pressure system
The present invention relates to a thickness control device for a stand rolling mill.

[0002]

2. Description of the Related Art As an example of a conventional hydraulic rolling mill, FIG. 6 shows reels 20 and 2 on an entrance side and an exit side (in / out side).
7 shows a single-stand cold reversible rolling mill in which No. 7 is arranged. In this figure, a rolled material 30 is a reel 20 for rewinding.
After passing through the work rolls 3 and 4 from the deflector roll 21 and a predetermined rolling is performed between them,
It is wound on a winding reel 27 through a deflector roll 26. The unwinding and winding reels 20 and 27 are driven by motors 19 and 28, respectively.
There are provided reel motor tension controllers 18 and 29 for keeping the tension acting on the rolled material 30 at the entrance and exit sides of the reel motor constant.
The tension controllers 18 and 29 generally control the motor current to be proportional to the tension. The rolling speed of the line is controlled to a predetermined value by controlling the speed of the work roll driving motor 23 of the rolling mill 32 by the speed control device 24.

In FIG. 6, 1 is a load cell for detecting a rolling load, 2 is an upper backup roll, 3 and 4 are upper and lower work rolls, 5 is a lower backup roll, and 6 is a roll gap between the work rolls 3 and 4. A hydraulic cylinder, 7 is a pipe between the hydraulic cylinder 6 and the servo valve 8, and 9 is a displacement meter for detecting a displacement of a hydraulic ram 6 'mounted in the hydraulic cylinder. 10 a servo amplifier sends the opening command to the servo valve 8 (current signals), 11 denotes a coefficient multiplier which gives a control gain K _G to amplify an output signal of the subtracter 12, a 'pressing position S' of pressure ram 6 Control.

[0004] The conventional hydraulic rolling mill is provided with a hydraulic rolling device 66 as a basic position control loop. The control loop compares calculating an output signal S of the displacement gauge 9 and the command signal R, multiplied by the gain K _G in the coefficient multiplier 11 to the deviation signal e, the servo valve via a servo amplifier 10 by the signal 8 The position S 'of the ram 6' is controlled by controlling the opening of the ram 6 'by controlling the amount of pressure oil supplied from the pipe 7 to the hydraulic cylinder 6. As a result, the lower backup roll 5 and the lower work roll 4 move, and the opening degree (roll gap) between the upper and lower work rolls 3 and 4 can be adjusted to a predetermined value.

[0005] Further, the conventional rolling mill of the hydraulic pressure reduction type is provided with a mill constant control device 54 for correcting the elongation of the mill which receives the rolling load. That is, simply controlling the position S 'of the pressing ram 6' by the above-described hydraulic pressing device 66 causes an error corresponding to the elongation of the mill receiving the rolling load in the roll gap between the upper and lower work rolls 3, 4. Therefore, the reference rolling load _Pref is normally stored at a certain timing after the start of rolling, and the difference ΔP from the signal P indicating the rolling load during rolling detected by the load cell 1 is added to the adder / subtractor 1.
7, it is divided by the mill constant K _m (corresponding to the spring constant of the rolling mill, which is obtained in advance) in the coefficient unit 16 of the mill constant control device 54 to obtain the elongation of the mill, and a correction is made by a factor. or a by multiplying the correction gain c which determines, obtains a correction signal C _P to correct 'position S' of pressure ram 6, applied to the adder 13 this as an instruction of the previous basic position control loop, pressure ram 6 ' Is corrected.

In addition, a conventional hydraulic rolling mill has a monitor AGC (Automatic Gauge Control) which controls the thickness by monitoring the actual thickness after rolling.
l) A device is provided. This monitor AGC device is provided with a thickness gauge 25 provided on the exit side of the rolling mill 32 in order to match the absolute plate thickness of the rolled material 30 on the exit side of the rolling mill 32 with the target value _href.
(The signal h detected by the thickness gauge 22 when traveling in the reverse direction is used) and a target value _href is compared and calculated by an adder / subtractor 31 to obtain a deviation Δh. The coefficient unit 14 multiplies the actual reduction position by a correction gain 1+ (M / K _e ) to correct the position S ′ of the reduction ram 6 ′.
Obtains a correction signal C _h modifying the adder 1 as the instruction of the aforementioned basic position control loop (hydraulic screw down device 66)
3 to correct the position S 'of the reduction ram 6'. Here, M is obtained in advance as a constant representing the hardness of the rolled material 30. Also, K _e is a mill constant, controlled K _e = K _m /
There is a relationship of (1-c).

[0007]

In order to control the thickness of the rolled material 30 in the above-mentioned conventional hydraulic rolling mill (FIG. 6), the position of the rolling ram 6 'is changed and the roll gap is changed. Then, the tension on the entrance and exit sides acting on the rolled material 30 changes. For example, if the roll gap between the work rolls 3 and 4 is narrowed in order to reduce the plate thickness, the rolled material 30 extends, and the tension on the entrance and exit sides decreases. However, the motors 19, 2 of the rewind and take-up reels 20, 27 on the inlet / outlet side,
The response of the reel motor tension controllers 18 and 29 for controlling the motor 8 is generally one order of magnitude slower than the hydraulic pressure reduction. Therefore, even if the roll gap is changed and the tension changes, the tension is set at the same speed as the hydraulic pressure reduction. I can't return to For this reason, the tension on the entrance and exit sides is reduced, and as a result, an effect occurs as if the deformation resistance of the rolled material 30 has apparently increased, and the roll gap tends to increase (the sheet thickness does not decrease). That is, even if the plate thickness is reduced under a high-speed hydraulic pressure, the reel motor tension control device 1 for the inlet / outlet motors 19 and 28 is required.
At a speed higher than the response speeds of 8, 29, there was a problem that the plate thickness could not be reduced. For this reason, there has been a problem that, especially for a fast incoming-side sheet thickness disturbance of 2 to 3 Hz or more, even if an attempt is made to make the mill hard by the above-described mill constant control, the sheet thickness control does not respond, and the mill cannot be removed. It is often heard at rolling mills that no matter how fast the position S 'of the reduction ram 6' is controlled using hydraulic reduction, the accuracy of the thickness control is not improved as expected. It turned out that.

FIG. 7 shows an example of a computer simulation by the present inventor, which clarifies the above-mentioned problem. The object of the simulation is a single-stand cold reversible rolling mill shown in FIG. 4 with a set tension of 1.36 tons on the incoming side, a set tension of 2.35 tons on the outgoing side, a thickness of 0.52 mm on the input side, and a thickness of 1800 mm. Material rolling speed 18
This is an example in which the roll gap is reduced stepwise by 10 μm under the condition that the target plate thickness is 0.3 mm at 00 m / min. The response under hydraulic pressure is assumed to be a 90-degree phase delay of 20 Hz in a frequency response, and a high-speed response of a step response to reach a target value in 0.04 seconds or less. Looking at the simulation results, when the roll gap is changed by 10 μm, the change in the exit side plate thickness Δh reaches a steady value approximately one second later. Although the actual hydraulic pressure reduction reaches the target value in 0.04 seconds, the plate thickness changes only 25 times slower in time, as described above. Response is slow. That is, the tension of the reels 20 and 27 is generally controlled by keeping the motor current constant.
This is because the inertia of the reels 20 and 27 including the above is considerably large, so that it takes about one second until the peripheral speed of the reels 20 and 27 suppresses the tension fluctuation and reaches the next steady value by the current control.

To solve the above problem, one of the inventors of the present invention disclosed in Japanese Unexamined Patent Publication No. Hei 3-155406, "Apparatus for controlling thickness of rolling mill".
Has proposed a thickness control device for a rolling mill as shown in FIG. 8 , which is provided with a tension control device for adjusting the tension applied to the rolling material on both the entrance side and the entrance side of the rolling mill. Note that, in FIG. 8, portions denoted by the same reference numerals as those in FIG. 6 indicate the same components. According to the apparatus shown in FIG. 8, the fluctuation of the tension generated as a result of operating the roll gap can be suppressed promptly, so that the result of moving the roll gap is immediately reflected in the sheet thickness, and the conventional mill is used. Constant control also works well. Specifically, as the tension control devices 33 and 34 in FIG. 8, one as shown in FIG. 9 can be considered as an example. That is, in FIG. 9, reference numeral 35 denotes a press roll for holding the rolled material 30, which is rotatably supported by the arm 36. Reference numeral 37 denotes a load detector (load cell) attached to the bearing of the presser roll 35.
The reaction force from zero is detected. The arm 36 is connected to a lever 38 and rotates about a rotating main shaft 39 so that the presser roll 35 is moved up and down. The lever 38 is connected to a piston rod 41 mounted on a hydraulic cylinder 40, and rotates around a rotating main shaft 39 by adjusting a flow rate to the hydraulic cylinder 40 by a servo valve 42. As a result, the integrated arm 36 rotates and moves the presser roll 35 up and down. The opening of the servo valve 42 is adjusted by the load detector 3
7, the tension T of the rolled material 30 is calculated from the reaction force of the rolled material 30 detected.
Is calculated by a tension calculator 46, and is calculated by an adder / subtractor 45.
In a deviation ΔT in comparison operation with tension set value T _ref, the coefficient multiplier 44 to the deviation ΔT is multiplied by a coefficient K _T, by controlling the servo valve 42 through a servo amplifier 43, zero deviation ΔT Is controlled as follows.

According to the tension control devices 33 and 34 shown in FIG. 9, when the roll gap changes, the resulting tension change is detected by the load detector 37 of the bearing portion of the presser roll 35.
And the flow rate of the fluid flowing into and out of the hydraulic cylinder 40 is adjusted by the high-speed servo valve 42 so as to match the target value _Tref . As a result, the presser roll 35 moves up and down, The tension changes immediately. For this reason, the result of changing the roll gap under hydraulic pressure is immediately reflected in the exit plate thickness,
Compared to a case where a tension control device using a conventional motor current is used, a plate thickness control with a higher response can be performed.
In the apparatus shown in FIG. 8, the reel motor tension controllers 18 and 29 suppress the slow tension fluctuation, and the tension controller 3
Numerals 3 and 34 act to absorb fast fluctuations in tension, so that the above-described delay in thickness control can be solved as a whole, and high-response thickness control can be performed.

However, even in a rolling mill provided with such a tension control device, if the mill is hardened to eliminate the input side thickness disturbance by controlling the mill constant, disturbance such as roll eccentricity of the mill machine main body affects the thickness. This has the problem that the thickness of the sheet is easily affected and the thickness accuracy is deteriorated. On the other hand, conventionally, a so-called roll eccentricity removal control device that extracts a roll eccentricity from a rolling load signal or the like and corrects the roll gap by moving the roll gap in a direction opposite to the eccentric motion has been put to practical use. Was. However, this method also has a problem that when the rolling speed is increased, the fluctuation cycle of the roll eccentricity is increased, and the response under hydraulic pressure cannot be made in time, so that the influence of the eccentricity cannot be sufficiently removed.

FIGS. 10 to 13 show the results of computer simulation performed by the present inventor to study such problems. The objects for which the simulations were performed are shown in FIGS.
In the single-stand cold rolling mill shown in (1), a material having an input side set tension of 1.42 tons, an output side set tension of 3.04 tons, an input side sheet thickness of 0.28 mm, and a sheet width of 1800 mm was rolled at a rolling speed of 1
Under the condition that the target plate thickness is set to 0.2 mm at 800 m / min, the amplitude of the input-side plate thickness disturbance is ± 4 μm and the fluctuation frequency is 5H.
z, amplitude ± 3 μm as roll eccentricity, fluctuation frequency 6.5
This is an example in which the calculation is performed assuming 3 Hz. FIGS. 10 and 11 show only the influence of the variation in the thickness of the inlet side plate.
Is an example in which the mill constant is made ten times harder by mill constant control in the conventional rolling mill shown in FIG. 6 without a tension controller. As is apparent from FIG.
^The variation of the exit side plate thickness is 5.4 μm ^{PP, which} is larger than ^PP . FIG. 11 shows the case of the apparatus shown in FIG. 6 in which the tension control device 33 is provided on the inlet side of the rolling mill 32. As can be seen from FIG. 11, the thickness variation has been reduced to 3.4 μm ^PP . This is because the entry side tension variation can be suppressed by the tension control device 33, so that the mill can be hardened by mill constant control to sufficiently reduce the entry side thickness variation.

On the other hand, FIG. 12 and FIG. 13 show the case where only the effect of the roll eccentricity is examined. FIG. 12 shows a conventional rolling mill 32 shown in FIG. Roll eccentricity of 6μm with 10 times harder
^PP caused almost no variation in outlet thickness. That is, as can be seen from the change in the entrance side tension, the tension varies by as much as 0.88 ton ^PP , so that the eccentricity of the roll hardly affects the sheet thickness. In contrast, when the rolling mill 32 entry side add tension control device 33, as the entry side tension fluctuation as shown in FIG. 11 is greatly reduced with 0.2 tons ^PP, exit side thickness fluctuation is 3. 2μm ^PP
To increase. That is, since the change in the entrance tension is suppressed, the change in the roll gap caused by the eccentricity of the roll affects the thickness of the rolled material.

Therefore, even in a rolling mill provided with the above-described tension control device, it is difficult to control the thickness with high responsiveness and high accuracy in the case where both the input side thickness disturbance and the roll eccentricity are present. There was a problem. Therefore, rolling mill 3
When the tension control devices 33 and 34 for adjusting the tension applied to the rolled material 30 are provided on both the entry side and the entry and exit sides of the roll 2, causes such as disturbance on the entry side thickness due to the material itself and roll eccentricity It has been found that it is important to consider countermeasures that take into account both the causes attributable to machines such as. The present invention has been made in view of the above points, and enhances the responsiveness of sheet thickness control to both the input side sheet thickness disturbance and the like and the roll eccentricity and the like, and can obtain a highly accurate product sheet thickness. It is intended to provide a machine thickness control device.

[0015]

SUMMARY OF THE INVENTION The present invention relates to a rolling mill thickness control apparatus provided with a hydraulic pressure reduction device for setting a roll gap between upper and lower work rolls and a load cell for detecting a rolling load. Tension control device for adjusting the tension of the rolled material on the entry side of the rolling mill, thickness gauge for detecting the thickness of the rolled material on the entry side of the rolling mill, and speedometer for detecting the traveling speed of the rolled material on the entry side of the rolling mill Further, a roll gap change amount calculator that calculates the timing of changing the roll gap from the signal of the speedometer and outputs the change amount of the roll gap to the hydraulic pressure reduction device, the change amount of the roll gap
Multiply the mill constant of the rolling mill and the correction amount to obtain a signal corresponding to the rolling load.
The load and the rolling load measured from the load cell
The rolling load constant control that calculates the load and makes the difference zero
Perform .

[0016]

According to the structure of the present invention, since the tension control device is provided on the entrance side of the single stand rolling mill, the fluctuation of the tension due to the fluctuation of the roll gap can be suppressed quickly. Also, the thickness variation on the entry side is measured by the thickness gauge on the entry side of the rolling mill, the feed speed of the rolled material is measured by the speedometer, and the roll gap change amount based on the signals from the thickness meter and the speedometer, The timing at which the fluctuation passes between the upper and lower work rolls of the rolling mill is calculated, and a roll gap change amount signal _CF is output to a hydraulic pressure reduction device or a tension control device, and the roll gap between the upper and lower work rolls of the rolling mill is adjusted. And the thickness variation on the entry side is removed,
Based on the signal of the load cell, the rolling mill is operated with a constant rolling load control (mill constant = 0) in order to eliminate the influence of disturbance components caused by the rolling mill itself, such as roll eccentricity, on the exit side plate thickness. This makes it possible to maximize the high-speed controllability under the hydraulic pressure, enhance the response of the plate thickness control, and obtain an accurate product plate thickness.

[0017]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a single-stand rolling mill according to the present invention; FIG. 1 shows an embodiment of a thickness control apparatus for a single-stand rolling mill according to the present invention. In the drawing, the portions denoted by the same reference numerals as those in FIG. 6 indicate the same components. As shown in FIG. 1, the apparatus according to the present invention is a rolling mill including a hydraulic pressure reduction device 66 for setting a roll gap between upper and lower work rolls 3 and 4 and a load cell 1 for detecting a rolling load P. A tension control device 33 for adjusting the tension of the rolling material on the entry side of the rolling mill, a thickness gauge 22 for detecting the thickness t of the rolling material on the entry side of the rolling mill, and a traveling speed V of the rolling material on the entry side of the rolling mill. A speedometer 50 for detection. Further, the plate thickness control device of the rolling mill according to the present invention controls the rolling load P to be constant by the hydraulic pressure reduction device 66 based on the signal of the load cell 1 and, based on the signal of the thickness gauge 22, the sheet thickness variation on the delivery side of the rolling mill. A roll gap change amount calculator 51 is provided for calculating the amount and calculating the timing for changing the roll gap from the signal of the speedometer 50 and outputting the change amount of the roll gap to the hydraulic pressure reduction device 66. With such a configuration, the roll gap change amount for canceling the entrance thickness disturbance is obtained from the signal t of the entrance thickness gauge 22 and the roll gap is changed from the signal V _{S1 of the} speedometer 50, that is, the entrance thickness disturbance is reduced by rolling. it can be added by calculating the timing of passing between the upper and lower work rolls 3 and 4 of the machine 32 to the adder 13 a roll gap change quantity signal C _F as a command value to the rolling load constant control loop. The operation of the above-described control system will be described below. The tension control device 33 controls the rolling material 3
FIG. 7 shows how to measure the tension fluctuation of zero and reduce it.
In order to move the presser roll 35 as shown in (1), the fluctuation of the tension due to the fluctuation of the roll gap is quickly suppressed, and the fluctuation of the roll gap is reflected on the exit side plate thickness. Further, the thickness variation ΔH on the entry side is measured by the thickness gauge 22 provided on the entry side of the rolling mill 32, and the feed speed V of the rolled material 30 is measured by the speedometer 50. The roll gap change amount calculator 51 calculates the roll gap change amount based on the signals t and V _S1 ,
The inlet-side sheet thickness variation ΔH is equal to the upper and lower work rolls 3 of the rolling mill 32,
4 is calculated, and the roll gap change amount signal _CF is added to the adder 1 of the rolling load constant control loop.
3 and the roll gap between the upper and lower work rolls 3 and 4 of the rolling mill 32 is adjusted to remove the entry-side thickness fluctuation ΔH. That is, from FIG. 1, e = (C _F + _Ch ) × α ·
K _m -P. The meaning of this expression is
The sum of the signal C _h a roll gap change amount C _F to fix S '
Over mill constant K _m of the rolling mill, directly on the load corresponding signal
And compare it with the rolling load P measured by the load cell 1.
Then, the difference e is multiplied by the control gain K _G ′, and the servo amplifier 1
0 to drive the servo valve to reduce the ram
The position S ′ of 6 ′ is corrected, and the rolling load P is changed to the command value (C _F +
To implement the C _h) × equal to alpha · K _m rolling load constant control
You. Here, α is the mill constant K _{m of} the rolling mill measured in advance.
Is a coefficient for correcting the measurement error of In addition, the conventional embodiment
11 of Figure 2 Figure 1 and described below with respect to 11 of the K _G 8
From being distinguished from the K _G ', the present invention is the rolling load constant control
Fig. 8 shows the position of the reduction ram.
This is because the fixed control is performed.

FIG. 2 shows another embodiment of the present invention. According to the present invention, a speedometer 50b for detecting the running speed v of the rolled material is provided on the output side of the single stand rolling mill, and the thickness variation ΔH on the input side is provided.
The thickness variation Δh on the delivery side of the rolling mill caused by the
T and the signals of the speedometers at the entrance and exit of the rolling mill and V _S1 and V _S2
Can be obtained from With this configuration, the thickness gauge 22
T and the signals of the speedometers at the entrance and exit of the rolling mill and V _S1 and V _S2
The roll gap change amount for canceling the entry side sheet thickness disturbance, and the timing of changing the roll gap from the signal V _{S1 of the} speedometer 50, that is, the entry side sheet thickness disturbance passes between the upper and lower work rolls 3 and 4 of the rolling mill 32. roll gap change amount signal C _F and calculates the timing of capable of adding to the adder 13 as a command value to the rolling load constant control loop. That is, since the volume flow rate before and after the roll gap is constant, there is a relationship of Δh = (V _S1 / V _S2 ) × ΔH, and the thickness variation Δh can be obtained from this relationship. By doing so, compared to the embodiment of FIG.
Since the exit side plate thickness variation Δh caused by the entrance side thickness variation ΔH can be obtained more accurately, the control accuracy can be further improved. Operation of the present control system is the same as that described in FIG. 1, different from rather than seek roll gap change amount C _F directly from entry side thickness fluctuation [Delta] H, the speed of the inlet and outlet V _S1, V _{S 2} In this way, the outlet thickness variation Δh immediately after the roll gap caused by the entrance thickness variation ΔH is obtained, and the roll gap change amount _CF is calculated from the variation.

Here, as shown in FIGS. 12 and 13, in order to eliminate the influence of the roll eccentricity, in the embodiment shown in FIGS. 1 and 2, the hydraulic pressure reduction device controls the rolling load to be constant. Is carried out, the mill constant, which is the spring constant of the rolling mill, becomes zero, and the reduction in the exit side plate thickness variation due to the roll eccentricity is suppressed. On the other hand, when the control for keeping the rolling load constant is performed, the influence of the disturbance of the incoming thickness on the variation of the outgoing thickness is increased. In the embodiment of the present invention shown in FIG. 1, the thickness variation on the entry side is measured by the thickness gauge 22 provided on the entry side of the rolling mill 32, and the speed of the rolled material 30 is measured by the speedometer 50. The input side thickness disturbance ΔH is removed by determining the timing at which the input side thickness variation passes between the upper and lower work rolls 3 and 4 of the rolling mill 32 and changing the roll gap from time to time accordingly. As a result, the variation in the exit side plate thickness can be reduced.

FIGS. 3 and 4 show another embodiment of the present invention, in which a roll gap change signal is output to the tension controller 33. FIG. At the fluctuating frequency of the input thickness disturbance,
Since the response of the tension control by the entry-side reel motor cannot be made in time, the plate thickness can be changed by operating the tension control device 33 directly and changing the tension. The pressure reduction control device 60 and the tension control device 66 can be switched and used by the mode selection control device 65 in response to the disturbance (problem of the input side plate thickness, roll eccentricity, etc.) that poses a problem. 3 and 4, reference numeral 61 denotes a hydraulic cylinder, 62 denotes a servo valve, 63 denotes a load cell, and 64 denotes a displacement meter. FIG. 3 corresponds to the configuration of FIG. 1 and directly changes the tension change amount T from the input side plate thickness disturbance ΔH.
_Ref (see FIG. 9) is obtained. FIG. 4 is a diagram showing the sheet thickness fluctuation Δh once obtained from the speeds V _S1 and V _S2 of the rolled material on the inlet and outlet sides, and the tension change amount T _ref is obtained therefrom. It is an example. FIG. 5 shows the result of a computer simulation performed to show the effect of the embodiment of the present invention, and is an example in the case where the fluctuation in the input side plate thickness and the roll eccentricity are simultaneously added as disturbances. The conditions are the same as those in FIGS. 8 to 11 described above. As is clear from this figure, after activating the tension control device 33 of the present invention, the rolling mill is controlled to keep the rolling load constant, and the control for suppressing the inlet thickness fluctuation ΔH described in FIG. 1 is performed. As a result, the variation in the thickness of the outlet side is reduced to about ± 1.3 μm, which indicates the excellent effect of the present invention on the variation in the thickness of the entrance side and the eccentricity of the roll.

In the above embodiment, only the case where the present invention is applied to a single-stand cold reversible rolling mill has been described. The present invention can be applied to all rolling mills in which the above problem occurs, and the tension is detected by a reaction force from a rolled material on rolls and other members arranged in the running path of the rolled material other than the presser roll and the deflector roll. It goes without saying that various changes can be made without departing from the gist of the present invention, such as the fact that the present invention can be detected.

[0022]

As described above, according to the apparatus for controlling the thickness of a rolling mill according to the present invention, a tension control device is provided on the entrance side of the rolling mill. The tension fluctuation at the entry side of the rolling mill resulting from the change of the position can be suppressed promptly, and furthermore, the thickness disturbance at the entry side is measured and removed by the thickness gauge at the entry side of the rolling mill, and the influence of the roll eccentricity is reduced. Since the rolling mill is controlled by the constant rolling load control, the response of the thickness control can be accelerated, and an excellent effect that a product thickness with high accuracy can be obtained can be obtained.

[Brief description of the drawings]

FIG. 1 is a block diagram illustrating a system configuration according to an embodiment of the present invention.

FIG. 2 is a block diagram showing a system configuration according to another embodiment of the present invention.

FIG. 3 is a block diagram showing a system configuration of still another embodiment of the present invention.

FIG. 4 is a block diagram showing a system configuration of still another embodiment of the present invention.

FIG. 5 is an example of a computer simulation in the embodiment of FIG. 1;

FIG. 6 is a block diagram showing a system configuration of a conventional example.

FIG. 7 is a diagram showing a computer simulation result in the apparatus of FIG. 6;

FIG. 8 is a block diagram showing a system configuration of a rolling mill provided with a tension controller currently proposed.

9 is a block diagram showing a specific example of a tension control device of the device shown in FIG.

FIG. 10 is a diagram showing a computer simulation result of a change in the thickness of the outlet side and a change in the tension on the inlet side with respect to the change in the thickness of the inlet side in the apparatus of FIG. 6;

FIG. 11 is a diagram showing a computer simulation result of a change in the thickness of the outlet side and a change in the tension in the inlet side with respect to the change in the thickness of the inlet side in the apparatus of FIG.

12 is a diagram showing a computer simulation result of a variation in the thickness of the delivery side and a variation in the tension on the entry side with respect to the roll eccentricity in the apparatus of FIG. 6;

FIG. 13 is a diagram showing a computer simulation result of a change in the outlet side plate thickness and a change in the inlet side tension with respect to the roll eccentricity in the apparatus of FIG. 8;

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Load cell 2 Upper backup roll 3 Upper work roll 4 Lower work roll 5 Lower backup roll 6 Hydraulic cylinder 7 Piping 8, 42 Servo valve 9 Displacement gauge 10, 43 Servo amplifier 11, 44 Coefficient unit 12, 17, 31, 45 Adder / subtractor Reference Signs List 13 adder 14 coefficient unit 15 integration controller 18, 29 reel motor tension control device 19, 28 motor 20 rewinding reel 21, 26 deflector roll 22, 25 thickness gauge 23 work roll driving motor 24 speed control device 27 winding Reel for roll 30 Rolled material 32 Rolling machine 33, 34 Tension control device 35 Pressing roll 36 Arm 37 Load detector 38 Lever 39 Rotating spindle 40 Hydraulic cylinder 41 Piston rod 46 Tension calculator 50, 50b Speedometer 51 Roll gap change amount calculation Vessel 52 Mil Constant Performance Calculator 53 Correction gain setting unit 54 Mill constant control unit 60 Pressure reduction control device 61 Hydraulic cylinder 62 Servo valve 63 Load cell 64 Displacement gauge 65 Mode selection control device 66 Hydraulic pressure reduction device 67 Tension control calculation device P _ref Reference rolling load P signal (rolling load) R command signal t signal (thickness at entrance side) V _s signals (feedrate) C _F roll gap change amount signal h signal (delivery side thickness) K _B mill constant signal c correction gain signal e deviation signal S 'position C _h control gain 'signal K _m mill constant K _G modifies the' position S

──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Isao Imai 1 Shin-Nakahara-cho, Isogo-ku, Yokohama-shi, Kanagawa Pref. Ishikawajima-Harima Heavy Industries Co., Ltd. Address Kobe Steel Co., Ltd. Moka Works (72) Inventor Osamu Uchida 15 Kinuigaoka, Moka City, Tochigi Prefecture Kobe Steel Co., Ltd. Moka Works (56) References JP-A-3-155406 (JP, A) JP-A-59-21423 (JP, A) JP-B-62-26844 (JP, B2) (58) Field surveyed (Int. Cl. ⁷ , DB name) B21B 37/16-37/20

Claims (4)

(57) [Claims] 1. A thickness control device for a rolling mill, comprising: a hydraulic pressure reduction device for setting a roll gap between upper and lower work rolls; and a load cell for detecting a rolling load. A tension gauge for detecting the thickness of the rolled material on the entry side of the rolling mill, a speedometer for detecting the running speed of the rolled material on the entry side of the rolling mill, and a speedometer. A roll gap change amount calculator that calculates the timing of changing the roll gap from the signal of the signal and outputs the change amount of the roll gap to the hydraulic pressure reduction device,
The mill constant of the rolling mill and the correction amount
To change the signal to a rolling load equivalent signal.
The rolling load measured from the load cell is compared and the difference is calculated.
Performing rolling load constant control to zero, and wherein the sheet
Thickness control device for single stand rolling mill. And a speedometer for detecting a running speed of the rolled material on an output side of the rolling mill, wherein a variation in thickness of the output side of the rolling mill is determined by a signal from the thickness gauge and an input / output side of the rolling mill. The signal of claim 1, wherein the signal is obtained from a signal of a speedometer.
Thickness control device for single stand rolling mill. Wherein the tension controller is composed of a load detector and the hydraulic cylinder and Bridle roll, Thing according to claim 1 which is controlled by the servo valve, it is characterized by
Thickness control device for rolling stand rolling mill. 4. A sheet according to claim 1 and 2 and outputs the roll gap change amount to tension controller
Thickness control device for single stand rolling mill.