WO2018016533A1 - Calculation device and calculation method - Google Patents
Calculation device and calculation method Download PDFInfo
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- WO2018016533A1 WO2018016533A1 PCT/JP2017/026128 JP2017026128W WO2018016533A1 WO 2018016533 A1 WO2018016533 A1 WO 2018016533A1 JP 2017026128 W JP2017026128 W JP 2017026128W WO 2018016533 A1 WO2018016533 A1 WO 2018016533A1
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- elongation
- width
- influence coefficient
- rolled material
- influence
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
- B21B37/28—Control of flatness or profile during rolling of strip, sheets or plates
- B21B37/38—Control of flatness or profile during rolling of strip, sheets or plates using roll bending
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
- B21B37/58—Roll-force control; Roll-gap control
Definitions
- the present invention relates to a calculation device and a calculation method for calculating a correction value for correcting a control amount of a shape control mechanism used for shape control of a rolled material in cold rolling.
- the rolling shape of the rolled material during rolling is measured using a shape detector arranged on the delivery side of the rolling mill, and the roll is determined based on the control result from the measurement result.
- a method of correcting the control amount of the shape control mechanism such as the bender, the roll shift mechanism, and the saddle pressing of the backup roll is generally employed (see Non-Patent Document 1).
- the rolling shape is the plate shape of the rolled material, and typical shape defects include ear elongation (the elongation of the plate edge is longer than the center of the thin plate in the rolling direction) and medium elongation (in the rolling direction). The center elongation is longer than the edge of the plate).
- the rolling shape is predicted based on a control expression expressed by a control amount function such as a shape control mechanism, and the shape
- a control amount function such as a shape control mechanism
- an influence coefficient indicating the degree of influence of the shape control mechanism on the elongation difference is used in the control equation.
- This influence coefficient is set in a table for each section such as a plate width, a plate thickness, or a material.
- the influence coefficient is expressed as a function as a function of a plate width, a plate thickness, a material, and the like (see Patent Document 1).
- the present invention has been made in view of the above-described conventional problems, and an object thereof is to provide a calculation device and a calculation method capable of setting an influence coefficient so as to obtain a good rolling shape.
- An arithmetic device is an arithmetic device that calculates a correction value for correcting a control amount of a shape control mechanism included in a cold rolling mill, which controls a rolling shape of a rolled material, the rolling material And a calculation unit that calculates the correction value using a mathematical expression that includes the correction value as a variable.
- the mathematical expression affects the elongation difference.
- An influence coefficient indicating the influence degree of the shape control mechanism is included, and the influence coefficient is represented by a function including a load applied to a unit width of the rolled material and the width of the rolled material as variables.
- the calculation method is a calculation method for calculating a correction value for correcting a control amount of a shape control mechanism provided in a cold rolling mill for controlling a rolling shape of a rolled material
- the calculation method Is a method of using a mathematical expression that includes the correction value as a variable, showing the amount of change in the elongation difference due to the correction between a plurality of locations in the rolled material, and the influence on the elongation difference included in the mathematical expression
- On influence coefficient A2 of the difference load S L it is a graph showing the effect of a unit width load p and plate width W. It is a block diagram which shows the schematic structure of the process computer which the said 6-high rolling mill contains. It is a flowchart which shows an example of the flow of the process which the said process computer performs. It is a graph showing the distribution of the difference between the target value and the actual value of the difference Y S between the elongation at elongation and sheet width center of the plate end portion of the rolled steel strip in an embodiment of the present invention.
- On influence coefficient A2 of the difference load S L in the first modification is a graph showing the effect of unit width load p and plate width W. It is a graph which shows the influence of the unit width load p and the board width W on the influence coefficient A1 of the intermediate roll bender force Fi in the modification 2 of Embodiment 1 of this invention.
- On influence coefficient A2 of the difference load S L in the above modified example 2 is a graph showing the effect of unit width load p and plate width W.
- (A) to (c) are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Ae of the intermediate roll bender force Fi in each of the conditions A to C in Embodiment 2 of the present invention. is there.
- (A) to (c) are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Be of the intermediate roll shift position ⁇ in each of the above conditions A to C.
- (A) to (c) are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Aq of the intermediate roll bender force Fi in each of the above conditions A to C.
- (A) to (c) are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Bq of the intermediate roll shift position ⁇ in each of the above conditions A to C.
- Embodiment 1 One embodiment of the present invention will be described below with reference to FIGS. The following description is for better understanding of the gist of the invention and does not limit the present invention unless otherwise specified. Further, in this specification, “A to B” indicates that A is B or more and B or less.
- FIG. 1 is a schematic diagram illustrating a configuration of a six-high rolling mill 1 as an example of a multi-high rolling mill provided with a calculation device according to the present embodiment.
- the six-high rolling mill 1 is a cold rolling mill that cold-rolls the rolled material 8.
- the six-high rolling mill 1 may be a final-pass rolling mill in a rolling system in which a plurality of rolling mills are continuously arranged, or a single rolling mill that executes a plurality of passes including the final pass. May be.
- the rolled material 8 is a metal strip such as a steel strip, for example.
- the rolled material 8 may be a resin material.
- the six-high rolling mill 1 includes a pair of work rolls 9 that sandwich the rolled material 8 in the thickness direction, a pair of backup rolls 11 that respectively press the pair of work rolls 9 in the opposing direction, and And a pair of intermediate rolls 10 that are arranged between the work roll 9 and the backup roll 11 and support the work roll 9.
- these rolls have a longitudinal direction perpendicular to the paper surface, and the rolled material 8 flows and rolls on the paper surface from the right to the left.
- the six-high rolling mill 1 includes an intermediate roll shift mechanism 2, an intermediate roll bender 3, a differential load generator 4, a shape detector 7, and a process computer 6.
- the intermediate roll shift mechanism 2 and the intermediate roll bender 3 are shape control mechanisms that control symmetrical components of the rolled shape of the thin sheet after rolling.
- the differential load generator 4 is a shape control mechanism that controls an asymmetric component of the rolling shape of the thin sheet after rolling.
- the intermediate roll shift mechanism 2 moves the taper portion by moving the intermediate roll 10 having one or more taper portions at one end in the axial direction thereof.
- the contact load distribution with the roll 9 and the backup roll 11 is changed to control the rolling shape of the thin sheet after rolling.
- the intermediate roll 10 may not be provided with a tapered portion.
- the intermediate roll bender 3 gives the intermediate roll 10 a force by which the intermediate roll 10 bends in the thickness direction of the rolled material 8.
- the differential load generator 4 is a device that generates a differential load for controlling the load asymmetry in the longitudinal direction of the backup roll 11.
- a load may be applied to the backup roll 11 by hydraulic pressure via bearing portions (chock) at both ends thereof.
- the load is applied at two places, a drive side chock and a work side chock.
- the drive side is a side where a motor (not shown) for rotating the work roll 9 is provided in the 6-high rolling mill 1, and the work side is a drive with the 6-high rolling mill 1 interposed therebetween. It is the opposite side.
- the differential load generating device 4 is a device that generates a difference between the loads applied to the drive side chock and the load applied to the work side chock, and the difference between the loads is the differential load.
- the shape detector 7 is a device that detects the shape of the rolled material 8 after rolling, and outputs a signal indicating the detection result to the process computer 6.
- the process computer 6 controls the intermediate roll shift mechanism 2, the intermediate roll bender 3, and the differential load generator 4 based on the output signal of the shape detector 7.
- the six-high rolling mill 1 includes a host computer 5 that controls the process computer 6.
- the host computer 5 includes a display unit 5a (for example, a display device such as a liquid crystal display) that displays control parameters and the like, and an input unit 5b (for example, a mouse and a keyboard) that receives input for changing the control parameters. .
- the arithmetic device can be realized as a device included in the process computer 6.
- the shape control mechanism is controlled using the correction value calculated by the arithmetic unit.
- the technical idea of the arithmetic device according to one aspect of the present invention will be described using the six-high rolling mill 1 as an example.
- the 6-high rolling mill 1 is taken as an example here, the present invention is similarly applied to multi-high rolling mills other than the 6-high rolling mill, such as a 4-high rolling mill, a 12-high rolling mill, and a 20-high rolling mill. Of course, is applied.
- the present invention can be applied to a work roll bender and a differential load generator as control targets.
- the fluctuation factors that affect the rolling shape include disturbances such as plate thickness, material, lubrication state, rolling load, and control amount of shape control mechanisms such as intermediate roll bender, work roll bender, intermediate roll shift, and differential load generator.
- the plate thickness is an important quality item, and is usually controlled to be a substantially constant value by automatic plate thickness control.
- the material and the lubrication state influence the rolling shape, but most of the influence is caused by the roll deflection changing according to the fluctuation of the rolling load. Therefore, the main factors that cause the shape change during rolling are the rolling load and the control amount of the shape control mechanism.
- control amount of the shape control mechanism is set based on a control expression for predicting the rolling shape.
- an influence coefficient indicating the degree of influence of the shape control mechanism on the elongation difference is used.
- the setting of the influence coefficient has the above-described problems.
- the present inventors have an influence coefficient so that a good rolling shape can be obtained when the rolling shape is controlled using a mathematical model representing the difference in elongation with respect to the center of the plate width at both ends in the plate width direction of the rolled material.
- Various methods for approximating the above were investigated. As a result, it was found that the influence coefficient can be approximated with high accuracy when the influence coefficient is expressed by a function of unit width load (load applied to the unit width of the rolled material) and sheet width.
- the inventors decided to control the rolling shape of the rolled material in the 6-high rolling mill 1 as follows. That is, in a state where the control amount (shift position) of the intermediate roll shift mechanism 2 is fixed, the intermediate roll bender 3 and the differential load generator 4 are controlled based on the output signal of the shape detector 7 to roll the rolled material. The shape was controlled.
- the control amount (shift position) of the intermediate roll shift mechanism 2 of the six-high rolling mill 1 is fixed for convenience of explaining the knowledge of the present invention, but the six-high rolling mill 1 is actually operated. In this case, the control amount of the intermediate roll shift mechanism 2 may not be fixed.
- the main controlled objects in the six-high rolling mill 1 of the present embodiment are the intermediate roll bender 3 and the differential load generator 4. On the other hand, it should be understood that it is not excluded that the intermediate roll shift mechanism 2 is controlled in the actual operation of the six-high rolling mill 1.
- the rolling shape was evaluated by breaking it down into a symmetric component and an asymmetric component. Specifically, the symmetrical component of the rolling shape was approximated by a quadratic equation, and the asymmetric component of the rolled shape was approximated by a linear equation as follows.
- y Symmetric component of rolled shape
- y ′ Asymmetric component of rolled shape
- W Plate width x: Plate width direction position (work side plate end: ⁇ W / 2, plate width center: 0, drive side plate end: W / 2) a, b: coefficients.
- control formulas (1) and (2) are used (control formula for predicting the rolling shape change).
- ⁇ Y S A1 ⁇ ⁇ Fi (1)
- ⁇ Y N A2 ⁇ ⁇ S L (2)
- Y S difference between the elongation at the edge of the plate and the elongation at the center of the plate width (average of work side and drive side)
- Y N Difference between work side elongation and drive side elongation (elongation difference)
- Fi Intermediate roll bender force S L : Differential load
- ⁇ Y S Amount of change in the difference between the elongation at the plate edge and the elongation at the center of the plate width (average of work side and drive side)
- ⁇ Y N Change amount of difference between work side elongation rate and drive side elongation rate (elongation rate difference)
- ⁇ Fi Change amount of intermediate roll bender force
- ⁇ S L Change amount of differential load
- A1 Influence of intermediate roll bender force Coefficient
- A2 Influence coefficient of differential load.
- FIG. 2 shows the difference (elongation rate difference) Y S (first elongation) between the elongation at the plate end (the end in the width direction of the rolled material) and the elongation at the center of the plate width (the center in the width direction of the rolled material).
- Y S first elongation
- middle roll bender force Fi which acts on a rate difference.
- the elongation difference is 10-5 as a unit, the unit was labeled iunit (also in the following description, the iunit a unit representing a 10 -5).
- the change in the intermediate roll bender force Fi appears as a change in the bending of the work roll 9, the intermediate roll 10, and the backup roll 11, and changes the shape of the rolled material.
- the relationship between the intermediate roll bender force Fi and the amount of deflection of the roll is substantially linear because it is intended for deformation in the elastic region. Therefore, as shown in FIG. 2, the elongation difference Y S is also linearly related to the intermediate roll bender force Fi.
- the slope in the linear relationship of FIG. 2 is the influence coefficient A1 of the intermediate roll bender force Fi, which is expressed by the above equation (1).
- Figure 3 is a graph showing the effect of the difference load S L on the difference (elongation difference) Y N (second elongation difference) between the elongation of the work side and drive side elongation. That is, it shows the influence of the differential load S L on the elongation difference Y N between both ends in the width direction of the rolled material.
- Change in the difference load S L is the work rolls 9, it appears as a deflection change of the intermediate roll 10 and backup roll 11, to change the shape of the rolled material. Relationship between the difference load S L and the amount of deflection of the roll is approximately linear relationship because it is intended for deformation in the elastic region. Therefore, as shown in FIG.
- Non-Patent Document 2 describes an example of an existing shape analysis method related to calculation of the sheet crown and flatness of a rolled material. The convergence calculation as described in the flowchart can be performed to calculate the sheet crown and flatness of the rolled material.
- shape analysis can be performed for plate shapes (plate profiles) other than plate crown and flatness.
- plate shapes plate profiles
- those skilled in the art apply a conventional shape analysis technique according to a plate profile to be analyzed, obtain a plate profile corresponding to the operation conditions by calculation, and adjust the rolling conditions.
- the present inventors use an analysis program that applies an existing shape analysis technique. Using this analysis program, it is possible to evaluate the elongation rate difference Y S and the elongation rate difference Y N by calculating the elongation rates of the plate width center portion and the plate end portion of the plate profile.
- the influence coefficients A1 and A2 under certain rolling conditions can be obtained by calculating the plots of FIGS. 2 and 3 using the shape prediction analysis program.
- the number of plots used for calculating the influence coefficient is preferably 4 or more. This is for more accurately obtaining the value of the influence coefficient as the slope of a straight line drawn so as to pass through each plot (or approximated by least squares for each plot).
- the above calculation is performed under predetermined (set) rolling conditions that are the premise of the calculation. For example, if the rolling load (unit width load) changes, the influence coefficients A1 and A2 also change accordingly.
- a plurality of rolling lines each including a rolling mill can be provided at a site such as a factory that performs rolling. Then, various kinds of rolled materials (sheet width, sheet thickness, deformation resistance) can be flowed through each rolling line in accordance with a desired product lot.
- the range of types of rolled material (sheet width, sheet thickness, deformation resistance) that can be handled in a certain rolling line is set in advance.
- the rolling conditions in the rolling mill change accordingly.
- the unit width load applied to the rolled material can be appropriately changed according to the pass schedule. It is not realistic to calculate the respective plots of FIG. 2 and FIG. 3 each time according to various rolling conditions and obtain the influence coefficients A1 and A2 under a certain rolling condition. In such a case, in such a case, (i) it takes time to calculate the influence coefficient every time the type of rolled material is changed, and (ii) the influence coefficient cannot be adjusted in accordance with the change in the unit width load. Because.
- FIG. 4 shows the result obtained by the above.
- FIG. 4 is a graph showing the influence of the unit width load p and the plate width W on the influence coefficient A1 of the intermediate roll bender force Fi.
- the numerical analysis of the shape prediction can be performed using an existing analysis program as described above.
- the plot shown in FIG. 4 is obtained as follows.
- the rolling load is obtained using a known rolling load equation based on certain conditions within the above ranges of the plate thickness, the plate width, and the deformation resistance of the material.
- the rolling load is determined according to fluctuations in sheet thickness before and after rolling, tension applied to the rolled material, deformation resistance (steel type) of the material, and the like.
- Table 1 shows an example of calculating the rolling load when performing a 6-pass rolling on a steel plate of steel type NCH780 using a known rolling load equation.
- a plurality of types of rolling load formulas are known. As to which rolling load formula is used, the user or the like may select and use an appropriate formula. Since the rolling load formula is a known technique, description thereof is omitted.
- the rolling load under the conditions of a predetermined plate thickness, plate width, and material deformation resistance can be calculated using a known rolling load equation.
- a unit width load is calculated by dividing the calculated rolling load by a sheet width (for example, 1050 mm).
- a plot as shown in FIG. 2 can be calculated using a numerical analysis of shape prediction under certain plate width and unit width load conditions.
- the influence coefficient A1 can be obtained.
- the plot shown in FIG. 4 can be calculated by performing these procedures for the types of rolled material (sheet width, sheet thickness, deformation resistance) in a range that can be handled by a rolling mill of a certain rolling line.
- the influence coefficient A1 intermediate roll bender force Fi is changed under each condition.
- the slope of the linear relationship between the control amount of the intermediate roll bender force Fi and the elongation difference Ys) is calculated.
- the influence coefficient A1 obtained under the condition that the plate width is 1050 mm and the unit width load is about 6300 N / mm is about ⁇ 0.3 Iunit / kN. This corresponds to a square plot at the lower right end of the 18 plots shown in FIG.
- the plate thickness, the plate width, and the deformation resistance of the material influence the shape of the rolled material, but most of the influence is caused by the change in roll deflection through the rolling load distribution.
- region to the work roll 9 of a rolling load changes depending on a board width.
- the present inventors thought that the influence coefficient A1 of the intermediate roll bender force Fi could be arranged by the unit width load p and the plate width W.
- the absolute value of the influence coefficient A1 of the intermediate roll bender force Fi decreases as the unit width load p increases, and the unit width load increases when the unit width load p is large. It was found that the influence of p on the influence coefficient A1 is small. As the plate width W increases, the influence coefficient A1 of the intermediate roll bender force Fi decreases. From this, the new knowledge that the unit width load p influences the influence degree of the plate width W was also obtained.
- the present inventors can search for an expression that approximates the influence coefficient A1 of the intermediate roll bender force Fi with high accuracy, and approximate the influence coefficient A1 with high accuracy by using the following expression (3). I found out that I can do it.
- A1 a1 1 ⁇ (1 / p) + a1 2 ⁇ (W / p) + a1 3 (3)
- A1 Influence coefficient of intermediate roll bender force Fi p: Unit width load
- W Plate width
- a1 1 , a1 2 , a1 3 A coefficient in an approximate expression of influence coefficient A1 of intermediate roll bender force Fi.
- FIG. 5 shows the result obtained by the above.
- the numerical analysis of the shape prediction can also be performed using a shape prediction analysis program.
- the plate thickness, the plate width, and the deformation resistance of the material influence the shape of the rolled material, but most of the influence is caused by changes in roll deflection through the rolling load distribution.
- region to the work roll 9 of a rolling load changes depending on a board width.
- the present inventors also the influence coefficient A2 of the difference load S L, was considered to be organized in a unit width load p and the plate width W. Further, as shown in FIG. 5, for the same plate width, with increasing unit width load p, the difference load S absolute value of the influence coefficient A2 of L decreases, the unit width load p is at large unit width load p Has a small influence on the influence coefficient A2. Then, the influence coefficient A2 of the difference load S L as the plate width W is increased to decrease, the unit width load p affects the impact of the plate width W.
- A2 a2 1 ⁇ (1 / p) + a2 2 ⁇ (W / p) + a2 3 (4)
- A a 1 ⁇ (1 / p) + a 2 ⁇ (W / p) + a 3 (5)
- the coefficient (a1 1 , a1 2 , a1 3 ), the coefficient (a2 1 , a2 2 , a2 3 ), and the coefficient (a 1 , Hereinafter, a 2 and a 3 ) may be referred to as approximate expression coefficients.
- This approximate expression coefficient can be obtained in advance corresponding to the range of types of rolled material (sheet width, sheet thickness, deformation resistance) that can be handled in a certain rolling line.
- This range (operating condition) can be set according to various conditions. For example, even if the operating condition is divided and set in such a range that a high correlation coefficient is obtained as a result of the multiple regression analysis. Good.
- the correlation coefficient value may be 0.9 or more, and preferably 0.95 or more. If the correlation coefficient is 0.9 or more, the approximate expression of the influence coefficient including such an approximate expression coefficient can be sufficiently put into practical use.
- the influence coefficient A1 for a certain unit width load p and plate width W can be calculated.
- the influence coefficient A2 can be calculated using an approximate expression represented by Expression (4).
- the influence coefficient A1 and the influence coefficient A2 under the conditions of the unit width load p and the plate width W between a plurality of plots as shown in FIGS. 4 and 5 can be obtained by approximating with high accuracy.
- the control amount of the intermediate roll bender force Fi and the differential load SL is controlled based on the equations (1) and (2), thereby improving the shape control. It can be performed with accuracy and a good rolling shape can be obtained.
- the arithmetic device can be realized as one function of the process computer 6 included in the six-high rolling mill 1, for example.
- the arithmetic device may be realized using a computer (for example, the host computer 5) different from the process computer 6, and hardware is not particularly limited.
- the process computer 6 includes a control unit 20 and a storage unit 30.
- the control unit 20 is connected to a host computer 5, a shape detector 7, and a shape control mechanism 40 provided outside the process computer 6.
- the host computer 5 includes a load calculation unit 5c.
- the shape control mechanism 40 in the present embodiment is the intermediate roll shift mechanism 2, the intermediate roll bender 3, and the differential load generator 4 (see FIG. 1).
- the control amount (shift position) of the intermediate roll shift mechanism 2 is used. ) Is fixed to a predetermined value.
- the control unit 20 includes an influence coefficient calculation unit 21, a correction target value calculation unit 22, a change amount calculation unit 23 (calculation unit), and a mechanism control unit 24.
- the storage unit 30 stores predetermined coefficient data 31 and control parameters 32.
- the control unit 20 is, for example, a CPU (Central Processing Unit) that controls the operation of the entire process computer 6.
- CPU Central Processing Unit
- Each part with which control part 20 is provided may be realized as software which operates by CPU, for example.
- the detailed description of the influence coefficient calculation unit 21, the correction target value calculation unit 22, the change amount calculation unit 23, and the mechanism control unit 24 in the control unit 20 corrects the control amount of the shape control mechanism executed by the process computer 6. This will be described later together with an example of the flow of processing for calculating a correction value to be performed.
- the storage unit 30 is a non-volatile storage device (for example, hard disk, flash memory, etc.) that stores various data used in the control unit 20.
- the predetermined coefficient data 31 is data indicating each approximate expression coefficient included in the expressions (3) and (4), and is data of the approximate expression coefficient obtained in advance as described above.
- the predetermined coefficient data 31 may be prepared in advance so that the influence coefficient calculation unit 21 can select an approximate expression coefficient corresponding to the rolling condition input to the host computer 5. Alternatively, the approximate equation coefficient may be calculated shortly before the rolling by the six-high rolling mill 1 is started.
- the approximate equation coefficient is obtained in advance using the host computer 5, for example.
- the host computer 5 has a function as an approximate expression coefficient calculation unit.
- the approximate expression coefficient may be obtained in advance using a device other than the host computer 5.
- the process computer 6 may calculate the approximate expression coefficient.
- the control parameter 32 includes various rolling conditions (the rotation speed of the work roll 9, the diameter of the work roll 9, the friction coefficient, the plate width, the input / output side plate thickness, the average input / output side tension, the deformation resistance of the rolled material 8, etc.). Further, the control parameter 32 includes a rolling shape target value that defines a rolling shape of the rolled material 8 targeted after rolling by the six-high rolling mill 1. For example, if the rolling shape after rolling the goal of which is flat (elongation difference 0 at each location in the plate width direction), it Ys and Y N is 0 both is rolled shape target value .
- the control parameter 32 is input by the user via the input unit 5b of the host computer 5, and is also used for calculating the rolling load by the load calculation unit 5c.
- FIG. 7 is a flowchart showing an example of the flow of processing executed by the process computer 6 of this embodiment.
- the host computer 5 obtains the approximate expression coefficient stored in the predetermined coefficient data 31 in advance.
- the method of obtaining the approximate expression coefficient is as described above, but briefly described as follows.
- the types of rolled material (sheet width, sheet thickness, deformation resistance) targeted by the six-high rolling mill 1 are as follows: sheet thickness 0.8 mm to 4.0 mm, sheet width 850 mm to 1050 mm, material deformation resistance 700 N / Mm 2 to 1200 N / mm 2 .
- the input method of the control parameter 32 is not particularly limited.
- the control parameter 32 includes at least the type of rolled material targeted by the above-described six-high rolling mill 1 (condition range setting step). Other rolling conditions may be input in this step, or may be input in advance.
- the unit width load is calculated as follows. That is, rolling conditions (work roll rotation speed, work roll diameter, friction coefficient, plate width, input / output side thickness, average input / output side tension, deformation resistance of the rolled material, etc.) are input to the host computer 5 as control parameters 32. Yes.
- the load calculation unit 5c calculates the rolling load P according to the rolling load formula, and calculates the unit width load p by substituting the sheet width W into the formula (6).
- the rolling load P is a load predicted by using a known rolling load equation based on previously input rolling conditions, and is the sum of the load on the dry side and the load on the work side.
- Some of the rolling conditions inputted in advance may fluctuate during rolling, and the rolling load P may fluctuate accordingly. It is not considered because it is small.
- the host computer 5 that calculates the unit width load p may also be regarded as the arithmetic device of the present invention. Further, the process computer 6 may calculate the unit width load p instead of the host computer 5.
- the host computer 5 calculates the influence coefficient A1 and the influence coefficient A2 under the conditions of a certain plate width and unit width load by using the shape prediction analysis program. This calculation method has been described above with reference to FIGS.
- Each plot of the graphs as shown in FIGS. 4 and 5 is calculated by calculating the influence coefficient A1 and the influence coefficient A2 with respect to several rolling conditions within the range of the above-mentioned rolled material varieties (plots). Calculation step).
- the plate width condition is changed by three levels, and the influence coefficient is calculated for six unit width load conditions in each plate width condition.
- 18 plots are calculated for each of the influence coefficient A1 and the influence coefficient A2, and a total of 36 plots are calculated (see FIGS. 4 and 5).
- the approximate equation coefficient can be obtained by performing multiple regression analysis on the calculated plot using the above equation (5).
- the approximate expression coefficients described in Table 1 and Table 2 are obtained.
- the obtained approximate expression coefficient is stored in the predetermined coefficient data 31.
- the storage unit 30 of the process computer 6 stores the approximate expression coefficients a1 1 , a1 2 , a1 3 and approximate expression coefficients a2 1 , a2 2 shown in, for example, Tables 1 and 2 in advance.
- A2 3 are stored as the predetermined coefficient data 31.
- an approximate expression of the influence coefficient can be set (approximation expression setting step).
- the process computer 6 executes processing as follows to calculate a correction value for correcting the control amount of the shape control mechanism.
- the influence coefficient calculation unit 21 substitutes the plate width W, the calculated unit width load p, and the predetermined coefficient data 31 using Expressions (3) and (4),
- the influence coefficient A1 and the influence coefficient A2 are calculated (step 11; hereinafter abbreviated as S11) (influence coefficient calculation step, influence coefficient setting step).
- the shape detector 7 detects the shape of the rolled material 8 and transmits a detection signal indicating the shape to the correction target value calculation unit 22.
- the correction target value calculation unit 22 calculates a difference (correction target value) between the shape of the rolled material 8 after rolling and the rolling shape target value included in the control parameter 32 based on the output signal from the shape detector 7. (S12). For example, if the target value of the elongation difference Y S is Y S 0 and the elongation difference measured by the shape detector 7 is Y S 1 , the amount of change ⁇ Y S in the elongation difference as the corrected target value is Y S 0.
- This change amount ⁇ Y S corresponds to the difference between the elongation difference before correction of the control amount of the shape control mechanism 40 and the elongation difference after correction, and the target value Y should be reduced by how much the actual elongation difference is reduced. It is a value indicating whether or not S 0 is matched.
- the change amount calculation unit 23 uses the equation (1) to calculate the intermediate roll bender force.
- a change amount ⁇ Fi of Fi is calculated (S13) (correction value calculation step). This change amount ⁇ Fi corresponds to a difference in bending force before and after the correction of the intermediate roll bender 3.
- the change amount calculation unit 23 uses the equation (2) based on the calculated influence coefficient A2 and the change amount ⁇ Y N of the elongation difference Y N as the correction target value to calculate the difference load SL . calculates the amount of change [Delta] S L (S14) (correction value calculating step).
- the change amount calculation unit 23 calculates a correction value for correcting the control amount of the shape control mechanism, using the mathematical expression indicating the change amount of the elongation difference between the plurality of locations in the rolled material 8. To do.
- the rolled material 8 after rolling by the 6-high rolling mill 1 can be made into a good rolling shape.
- the arithmetic device in the six-high rolling mill 1 in the present embodiment controls the intermediate roll bender 3 and the differential load generator 4 to perform rolling.
- a calculation unit (change amount calculation unit 23) that calculates control values (change amount ⁇ Fi, change amount ⁇ S L ) for controlling the shape is provided.
- the influence coefficient calculation unit 21 calculates the influence coefficients A1 and A2 in the expressions (1) and (2) used for calculating the control value using the approximate expression (3) and the approximate expression (4), respectively.
- the approximate expression coefficients in the approximate expression (3) and the approximate expression (4) are obtained as follows.
- the difference Y S between the elongation at the plate end of the rolled material 8 and the elongation at the center of the plate width is defined as a first elongation difference.
- the difference Y N between the elongation rate of the rolled material 8 on the work side of the six-high rolling mill 1 and the elongation rate on the drive side of the six-high rolling mill 1 is defined as a second elongation difference.
- a load applied to the unit width of the rolled material 8 is defined as a unit width load.
- the high-order computer 5 serving as the arithmetic device of the present embodiment is configured such that the plate thickness, the plate width, and the material are deformed within a predetermined range based on a plurality of types of rolled material 8 to be rolled by the six-high rolling mill 1. While changing the resistance, (A) calculating the unit width load of the rolled material 8 under each of the set plurality of rolling conditions, and (B) (i) the intermediate roll bender force Fi and the first in each rolling condition. The relationship between the elongation difference and (ii) the relationship between the differential load SL and the second elongation difference is calculated using a numerical analysis program for shape prediction.
- the upper computer 5 obtains the influence coefficients A1 and A2 in each of the plurality of rolling conditions based on the obtained relation, thereby obtaining a relation (for example, the influence width A1 or A2).
- the plots shown in FIG. 4 and FIG. 5 are obtained, and multiple regression analysis is performed on the relationship using the approximate expression (3) and the approximate expression (4).
- the approximate expression coefficients of approximate expression (3) and approximate expression (4) used in a predetermined range of the rolled material 8 are calculated for each of the influence coefficients A1 and A2.
- This approximate expression coefficient may be stored as the predetermined coefficient data 31 in the storage unit 30.
- the influence coefficient calculation unit 21 uses the approximate expression (3) and the approximate expression (4) into which the approximate expression coefficient calculated as described above is substituted, and the influence coefficient A1 according to the type of the rolled material. And A2 are respectively calculated.
- the influence coefficients A1 and A2 of the shape control mechanism 40 are approximated as a function of the unit width load and the plate width, as shown in FIG. the absolute value of the difference between the target value and the actual value of the difference Y S of the growth rate (the one absolute value in the work side and drive side is large) in was not fit within 25Iunit.
- the difference Y between the elongation at the plate end and the elongation at the center of the plate width is 35 Units or more.
- the range of the plate width of the target rolled material is in the range of 1050 mm to 1250 mm. It is assumed that the range of plate thickness and material deformation resistance remains the same.
- FIG. 10 is a graph showing the influence of the unit width load p and the plate width W on the influence coefficient A1 of the intermediate roll bender force Fi in the present modification.
- FIG. 11 on the influence coefficient A2 of the difference load S L in this modification is a graph showing the effect of a unit width load p and plate width W.
- analysis is performed by changing the plate thickness, the plate width, and the deformation resistance of the material within the above ranges using the shape prediction analysis program.
- the influence coefficient A1 was calculated. The results are shown in FIG.
- analysis is performed by changing the plate thickness, the plate width, and the deformation resistance of the material in the above ranges using the analysis program for shape prediction.
- the influence coefficient A2 was calculated under the conditions. The results are shown in FIG.
- the shape control It can be performed with high accuracy and a good rolling shape can be obtained.
- the range of the plate width of the target rolled material is in the range of a plate width of 600 mm to 850 mm. It is assumed that the range of plate thickness and material deformation resistance remains the same.
- FIG. 12 is a graph showing the influence of the unit width load p and the plate width W on the influence coefficient A1 of the intermediate roll bender force Fi in the present modification.
- 13, on the influence coefficient A2 of the difference load S L in this modification is a graph showing the effect of a unit width load p and plate width W.
- analysis is performed by changing the plate thickness, the plate width, and the deformation resistance of the material within the above ranges using the shape prediction analysis program.
- the influence coefficient A1 was calculated. The results are shown in FIG.
- each approximate equation coefficient in the approximate equation is as shown in Table 6, and a high correlation was obtained.
- analysis is performed by changing the plate thickness, the plate width, and the deformation resistance of the material in the above ranges using the analysis program for shape prediction.
- the influence coefficient A2 was calculated under the conditions. The results are shown in FIG.
- the shape control It can be performed with high accuracy and a good rolling shape can be obtained.
- the control amount (shift position) of the intermediate roll shift mechanism 2 is fixed to a predetermined value, and the intermediate roll bender 3 and the differential load generator 4 are controlled. Further, as equations (1) and (2), the change amount ⁇ Y S of the difference in elongation, which is the difference between the elongation at the plate edge and the elongation at the center of the plate width (average of the work side and drive side), and It was evaluated rolled shape using a variation [Delta] Y N of elongation being the difference between the elongation of the work side and drive side elongation.
- the intermediate roll shift mechanism 2 and the intermediate roll bender 3 are used as the shape control mechanism used during rolling, and not only the plate end portion but also the quarter portion are used for evaluating the rolling shape. (Intermediate part) is also different.
- the differential load generator 4 may be controlled.
- the rolling shape is evaluated in consideration of the quota part, and the amount of change in the control values of the intermediate roll shift mechanism 2 and the intermediate roll bender 3 is calculated.
- the quarter portion is a portion located between the plate width center portion and the plate end portion in the plate width direction of the rolled material 8.
- the position of the quarter portion is not particularly limited between the center portion of the plate width and the end portion of the plate, but can be, for example, 70% of the distance from the center portion of the plate width to the end portion of the plate.
- the quota section includes a work side quota section and a drive side quota section.
- control formulas (7) and (8) can be used as formulas for controlling the rolling shape of the rolled material.
- Equation (7) may be referred to as a control equation relating to the plate end portion
- Equation (8) may be referred to as a control equation relating to the quota portion.
- influence coefficients Ae, Aq, Be, and Bq can be expressed by expressions (9) and (10) that are essentially the same as the above-described expression (5).
- A a 1 ⁇ (1 / p) + a 2 ⁇ (W / p) + a 3 (9)
- B b 1 ⁇ (1 / p) + b 2 ⁇ (W / p) + b 3 (10)
- p Unit width load
- W Plate width a 1 , a 2 , a 3 : Approximate expression coefficient in the approximate expression of the influence coefficient b 1 , b 2 , b 3 : Approximate expression coefficient in the approximate expression of the influence coefficient
- Coefficient A and influence coefficient B are calculated. Specifically, it is as follows.
- the approximate expression coefficients (aq 1 , aq 2 , aq 3 ) in the approximate expression of the influence coefficient Aq, and the approximate expression coefficient ( bq 1 , bq 2 , bq 3 ) can be obtained.
- Condition A is a range of plate widths from 1050 mm to 1250 mm
- Condition B is a range of plate widths from 850 mm to 1050 mm
- Condition C is a range of plate widths from 600 mm to 850 mm.
- Conditions A to C are assumed to have the same thickness range and the same range of material deformation resistance.
- (About the control formula for the plate edge) 14A to 14C are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Ae of the intermediate roll bender force Fi under the conditions A to C, respectively.
- 15A to 15C are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Be of the intermediate roll shift position ⁇ under the conditions A to C, respectively.
- FIGS. 16A to 16C are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Aq of the intermediate roll bender force Fi under the conditions A to C, respectively.
- FIGS. 17A to 17C are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Bq of the intermediate roll shift position ⁇ under the conditions A to C, respectively.
- the approximate expression coefficient can be obtained in advance according to the operating conditions of the rolling mill.
- the influence coefficient calculation unit 21 substitutes the approximate expression coefficient obtained as described above into Expression (9) or Expression (10), and affects the influence coefficients Ae, Aq, Be for a certain unit width load p and plate width W. , Bq is calculated (influence coefficient calculation step).
- the shape detector 7 detects the shape of the rolled material 8 and transmits a detection signal indicating the shape to the corrected target value calculation unit 22. Based on the output signal from the shape detector 7, the correction target value calculation unit 22 is the difference between the value indicating the shape of the rolled material 8 after rolling and the rolling shape target value included in the control parameter 32 (correction target value). Is calculated. As a result, the change amounts ⁇ e and ⁇ q of the elongation difference as correction target values are obtained.
- the change amount calculation unit 23 substitutes the influence coefficients Ae, Aq, Be, Bq and the change amounts ⁇ e and ⁇ q of the difference in elongation rate into the equations (7) and (8), By solving the simultaneous equations for the intermediate roll bender force Fi and the intermediate roll shift position ⁇ , the change amount ⁇ Fi of the intermediate roll bender force Fi and the change amount ⁇ of the intermediate roll shift position ⁇ are calculated (correction value calculation step).
- the mechanism control unit 24 (see FIG. 6) corrects the intermediate roll bender force Fi by changing ⁇ Fi and the intermediate roll shift position ⁇ by ⁇ .
- the rolled material 8 after rolling by the 6-high rolling mill 1 can be made into a good rolling shape.
- the arithmetic unit (process computer 6, or host computer 5 and process computer 6) in the six-high rolling mill 1 in the present embodiment controls the intermediate roll shift mechanism 2 and the intermediate roll bender 3 to perform rolling.
- a calculation unit (change amount calculation unit 23) that calculates control values (change amount ⁇ e, change amount ⁇ q) for controlling the shape is provided.
- the influence coefficient calculation unit 21 calculates the influence coefficients Ae, Be, Aq, and Bq in the equations (7) and (8) used for calculating the control value using approximate equations (11) to (14), respectively. To do.
- the approximate equation coefficients in the approximate equations (11) to (14) are obtained as follows.
- the difference ⁇ e between the elongation at the plate end of the rolled material 8 and the elongation at the center of the plate width is defined as a first elongation difference.
- the difference ⁇ q between the elongation at the quarter portion of the rolled material 8 and the elongation at the center of the sheet width is defined as a third elongation difference.
- a load applied to the unit width of the rolled material 8 is defined as a unit width load.
- the high-order computer 5 serving as the arithmetic device of the present embodiment is configured such that the plate thickness, the plate width, and the material are deformed within a predetermined range based on a plurality of types of rolled material 8 to be rolled by the six-high rolling mill 1. While changing the resistance, (A) calculating the unit width load of the rolled material 8 under each of the set plurality of rolling conditions, and (B) (i) the intermediate roll bender force Fi and the first in each rolling condition.
- the upper computer 5 obtains the influence coefficients Ae, Be, Aq, and Bq in each of the plurality of rolling conditions based on the obtained relationship, whereby the unit width load and the influence coefficients Ae, Be. , Aq, or Bq (for example, the plots shown in FIGS. 14 to 17) are obtained, and multiple regression analysis is performed on the relationships using approximate equations (11) to (14). Thereby, the approximate expression coefficients of the approximate expressions (11) to (14) used in the predetermined range of the rolled material 8 are calculated for each of the influence coefficients Ae, Be, Aq, and Bq.
- This approximate expression coefficient may be stored as the predetermined coefficient data 31 in the storage unit 30.
- the influence coefficient calculation unit 21 uses the approximate expressions (11) to (14) into which the approximate expression coefficient calculated as described above is substituted, and the influence coefficients Ae, Be according to the type of the rolled material. , Aq, and Bq are calculated respectively.
- control blocks of the host computer 5 and the process computer 6 are integrated circuits (IC chips). ) Or the like, or may be realized by software using a CPU (Central Processing Unit).
- the host computer 5 and the process computer 6 include a CPU that executes instructions of an information processing program that is software for realizing each function, and a ROM in which the program and various data are recorded so as to be readable by the computer (or CPU).
- a CPU that executes instructions of an information processing program that is software for realizing each function
- a ROM in which the program and various data are recorded so as to be readable by the computer (or CPU).
- Recording media or a storage device (these are referred to as “recording media”)
- RAM Random Access Memory
- the computer or CPU reads the program from the recording medium and executes it to achieve the object of the present invention.
- the recording medium a “non-temporary tangible medium” such as a tape, a disk, a card, a semiconductor memory, a programmable logic circuit, or the like can be used.
- the program may be supplied to the computer via an arbitrary transmission medium (such as a communication network or a broadcast wave) that can transmit the program.
- a transmission medium such as a communication network or a broadcast wave
- the present invention can also be realized in the form of a data signal embedded in a carrier wave, in which the program is embodied by electronic transmission.
- the arithmetic device in the aspect 1 of the present invention controls the shape of the cold rolling mill (six-high rolling mill 1) that controls the rolling shape of the rolled material 8.
- An arithmetic device for calculating a correction value for correcting a control amount of a mechanism (intermediate roll bender 3 and differential load generator 4 or intermediate roll bender 3 and intermediate roll shift mechanism 2), in the rolled material 8
- a calculation unit (change amount calculation unit 23) that calculates the correction value using a mathematical expression that includes the correction value as a variable and indicates the amount of change in elongation difference due to correction between a plurality of locations, Including an influence coefficient indicating an influence degree of the shape control mechanism on the elongation difference, and the influence coefficient includes a load applied to a unit width of the rolled material, a width of the rolled material, and It is represented by a function including as a variable.
- the influence coefficient is approximated as a function of sheet width, sheet thickness, and material deformation resistance by the conventional method, the precision of the influence coefficient is not very high. Therefore, in the conventional method, a shape control mechanism is used to detect elongation difference between a plurality of locations in the sheet width direction of the rolled material 8, and using the detected result and the obtained influence coefficient, the shape control mechanism When a correction value for correcting the control amount is calculated, even if the control amount of the shape control mechanism is changed based on the correction value, the calculated change between the rolling shape and the actual change In some cases, the error of (see FIG. 9) becomes large.
- the influence coefficient is a function including the load (unit width load) applied to the unit width of the rolled material and the width of the rolled material as variables.
- the expression can be approximated with high accuracy. Therefore, the elongation difference between a plurality of locations in the sheet width direction of the rolled material 8 is detected using a shape detector, and the control amount of the shape control mechanism is determined using the detected result and the obtained influence coefficient.
- a correction value for correction can be calculated with high accuracy. As a result, correction can be performed by appropriately changing the control amount of the shape control mechanism based on the calculated correction value. Therefore, the rolling shape of the rolled material rolled by the cold rolling mill can be improved.
- A can be an influence coefficient
- p can be a unit width load
- W can be a width of the rolled material
- a 1 , a 2 and a 3 can be coefficients.
- the elongation at the end in the width direction of the rolled material and the elongation at the center in the width direction in the arithmetic device in aspect 1 or aspect 2, as the difference in elongation between a plurality of locations, the elongation at the end in the width direction of the rolled material and the elongation at the center in the width direction.
- the difference in elongation between both ends in the width direction of the rolled material, or the difference between the elongation at the intermediate portion closer to the center than the end and the elongation at the center is used.
- the rolling shape when the elongation difference between both end portions in the width direction of the rolled material is used, the rolling shape can be evaluated in consideration of the asymmetric component of the rolled material. Moreover, when the difference between the elongation rate at the intermediate portion closer to the center than the end portion and the elongation rate at the center is used, the rolling shape can be more accurately evaluated.
- the arithmetic device according to aspect 4 of the present invention is the arithmetic device according to any one of aspects 1 to 3, wherein the mathematical formulas each have an influence coefficient indicating the degree of influence of the plurality of types of shape control mechanisms on the difference in elongation. Multiple influence terms may be included.
- the arithmetic device when a plurality of types of shape control mechanisms are involved in the difference in elongation between certain locations, the arithmetic device first calculates the unit width load and the rolling material for each of the plurality of types of shape control mechanisms.
- the influence coefficient approximated with high accuracy can be obtained by an expression represented by a function including the width of
- the correction values of the plurality of types of shape control mechanisms can be calculated using mathematical expressions including a plurality of influence terms each having an influence coefficient of the plurality of types of shape control mechanisms.
- the calculation method according to aspect 5 of the present invention is a calculation method for calculating a correction value for correcting a control amount of a shape control mechanism provided in a cold rolling mill for controlling a rolling shape of a rolled material
- the calculation method Is a method of using a mathematical expression that includes the correction value as a variable, showing the amount of change in the elongation difference due to the correction between a plurality of locations in the rolled material, and the influence on the elongation difference included in the mathematical expression
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Abstract
The present invention provides a calculation device and a calculation method that are able to set an influence coefficient in order to obtain a fine rolling shape through cold rolling. This calculation device is provided with a variation calculation unit (23) which determines the level of change in elongation percentage difference caused by correction, between multiple locations of a rolled material (8), and which, at the same time, calculates a correction value using a mathematical expression that includes the correction value as a variable, wherein the mathematical expression includes an influence coefficient indicating a degree of influence exerted on the elongation percentage difference by a shape control mechanism, and the influence coefficient is represented by a function that includes, as variables, a load applied per unit width of the rolled material (8) and the width of the rolled material (8).
Description
本発明は、冷間圧延における圧延材の形状制御に用いられる形状制御機構の制御量を補正するための補正値を算出する演算装置および演算方法に関する。
The present invention relates to a calculation device and a calculation method for calculating a correction value for correcting a control amount of a shape control mechanism used for shape control of a rolled material in cold rolling.
冷間圧延では、圧延中(稼働中の圧延ライン)の圧延材の圧延形状を、圧延機出側に配置された形状検出器を用いて測定し、その測定結果から制御式に基づいて、ロールベンダー、ロールシフト機構、およびバックアップロールのサドル押込み、等の形状制御機構の制御量を補正する方法が一般的に採用されている(非特許文献1参照)。圧延形状とは、圧延材の板形状のことであり、代表的な形状不良としては、耳伸び(圧延方向において薄板の中央よりも板端部の伸びが長い)、および中伸び(圧延方向において板端部よりも中央の伸びが長い)がある。
In cold rolling, the rolling shape of the rolled material during rolling (the rolling line in operation) is measured using a shape detector arranged on the delivery side of the rolling mill, and the roll is determined based on the control result from the measurement result. A method of correcting the control amount of the shape control mechanism such as the bender, the roll shift mechanism, and the saddle pressing of the backup roll is generally employed (see Non-Patent Document 1). The rolling shape is the plate shape of the rolled material, and typical shape defects include ear elongation (the elongation of the plate edge is longer than the center of the thin plate in the rolling direction) and medium elongation (in the rolling direction). The center elongation is longer than the edge of the plate).
また、このような圧延機出側での形状検出に基づく形状制御に先立って、圧延開始前に、形状制御機構等の制御量の関数で表わした制御式に基づいて圧延形状を予測し、形状制御機構の制御量を初期設定するプリセット制御が一般に行われている。
In addition, prior to shape control based on shape detection on the rolling mill exit side, before rolling starts, the rolling shape is predicted based on a control expression expressed by a control amount function such as a shape control mechanism, and the shape In general, preset control for initially setting a control amount of a control mechanism is performed.
圧延中の形状制御およびプリセット制御のいずれの場合においても、制御式には、伸び率差に及ぼす形状制御機構の影響度を示す影響係数が用いられる。この影響係数は、板幅、板厚、または材質等の区分毎にテーブル設定される。或いは、影響係数は、板幅、板厚、および材質等の関数として数式化される(特許文献1参照)。
In both cases of shape control during rolling and preset control, an influence coefficient indicating the degree of influence of the shape control mechanism on the elongation difference is used in the control equation. This influence coefficient is set in a table for each section such as a plate width, a plate thickness, or a material. Alternatively, the influence coefficient is expressed as a function as a function of a plate width, a plate thickness, a material, and the like (see Patent Document 1).
しかし、影響係数を板幅、板厚、または材質等の区分毎にテーブル設定する場合、テーブルの区分が粗いと、同一区分内の影響係数の誤差が大きくなり、精度が悪くなる。そのため、影響係数を組み込んだ制御式に基づいて得られる圧延形状が悪化し得る。したがって、テーブルの区分を細かくして、多数のテーブルを用意することが必要となり、コンピュータの記憶領域に占める割合が大きくなるとともに、テーブル値の管理も複雑となるという問題がある。
However, when the influence coefficient is set for each section such as plate width, sheet thickness, or material, if the table section is rough, the error of the influence coefficient in the same section becomes large and the accuracy is deteriorated. Therefore, the rolling shape obtained based on the control formula incorporating the influence coefficient can be deteriorated. Accordingly, it is necessary to prepare a large number of tables by making the table sections finer, and there is a problem that the ratio of the storage area of the computer increases and the management of table values becomes complicated.
また、影響係数を数式化する場合、影響係数の高精度な近似式がなく、以下のような問題があった。すなわち、例えば、板幅、板厚、および材質(材料の変形抵抗)の関数として近似した場合、影響係数の誤差が大きくなり、影響係数を組み込んだ制御式に基づいて得られる圧延形状が悪化する場合があるという問題がある。
In addition, when formulating the influence coefficient, there is no high-precision approximate expression of the influence coefficient, and there are the following problems. That is, for example, when approximated as a function of sheet width, sheet thickness, and material (material deformation resistance), the error of the influence coefficient becomes large, and the rolling shape obtained based on the control formula incorporating the influence coefficient deteriorates. There is a problem that there are cases.
本発明は、上記従来の問題点に鑑みなされたものであって、その目的は、良好な圧延形状が得られるように影響係数を設定できる演算装置および演算方法を提供することにある。
The present invention has been made in view of the above-described conventional problems, and an object thereof is to provide a calculation device and a calculation method capable of setting an influence coefficient so as to obtain a good rolling shape.
本発明の一態様における演算装置は、圧延材の圧延形状を制御する、冷間圧延機が備える形状制御機構の制御量を補正するための補正値を算出する演算装置であって、前記圧延材における複数箇所間の、補正による伸び率差の変化量を示すと共に、前記補正値を変数として含む数式を用いて前記補正値を算出する算出部を備え、前記数式は、前記伸び率差に及ぼす前記形状制御機構の影響度を示す影響係数を含み、前記影響係数は、前記圧延材の単位幅に加えられる荷重と前記圧延材の幅とを変数として含む関数で表されている。
An arithmetic device according to an aspect of the present invention is an arithmetic device that calculates a correction value for correcting a control amount of a shape control mechanism included in a cold rolling mill, which controls a rolling shape of a rolled material, the rolling material And a calculation unit that calculates the correction value using a mathematical expression that includes the correction value as a variable. The mathematical expression affects the elongation difference. An influence coefficient indicating the influence degree of the shape control mechanism is included, and the influence coefficient is represented by a function including a load applied to a unit width of the rolled material and the width of the rolled material as variables.
本発明の一態様における演算方法は、圧延材の圧延形状を制御する、冷間圧延機が備える形状制御機構の制御量を補正するための補正値を算出する演算方法であって、前記演算方法は、前記圧延材における複数箇所間の、補正による伸び率差の変化量を示すと共に、前記補正値を変数として含む数式を用いる方法であり、前記数式に含まれる、前記伸び率差に及ぼす前記形状制御機構の影響度を示す影響係数を算出する影響係数算出工程と、算出された影響係数を含む前記数式を用いて前記補正値を算出する補正値算出工程とを含み、前記影響係数は、前記圧延材の単位幅に加えられる荷重と前記圧延材の幅とを変数として含む関数で表されている。
The calculation method according to an aspect of the present invention is a calculation method for calculating a correction value for correcting a control amount of a shape control mechanism provided in a cold rolling mill for controlling a rolling shape of a rolled material, the calculation method Is a method of using a mathematical expression that includes the correction value as a variable, showing the amount of change in the elongation difference due to the correction between a plurality of locations in the rolled material, and the influence on the elongation difference included in the mathematical expression An influence coefficient calculating step of calculating an influence coefficient indicating an influence degree of the shape control mechanism, and a correction value calculating step of calculating the correction value using the mathematical formula including the calculated influence coefficient, It is represented by a function including the load applied to the unit width of the rolled material and the width of the rolled material as variables.
本発明の一態様においては、良好な形状の圧延材が得られる影響係数を設定することができる。
In one aspect of the present invention, it is possible to set an influence coefficient for obtaining a rolled material having a good shape.
〔実施形態1〕
本発明の一実施形態について、図1~9に基づいて説明すれば、以下のとおりである。なお、以下の記載は発明の趣旨をより良く理解させるためのものであり、特に指定のない限り、本発明を限定するものではない。また、本明細書において、「A~B」とは、A以上B以下であることを示している。Embodiment 1
One embodiment of the present invention will be described below with reference to FIGS. The following description is for better understanding of the gist of the invention and does not limit the present invention unless otherwise specified. Further, in this specification, “A to B” indicates that A is B or more and B or less.
本発明の一実施形態について、図1~9に基づいて説明すれば、以下のとおりである。なお、以下の記載は発明の趣旨をより良く理解させるためのものであり、特に指定のない限り、本発明を限定するものではない。また、本明細書において、「A~B」とは、A以上B以下であることを示している。
One embodiment of the present invention will be described below with reference to FIGS. The following description is for better understanding of the gist of the invention and does not limit the present invention unless otherwise specified. Further, in this specification, “A to B” indicates that A is B or more and B or less.
以下の説明においては、本発明の一態様における演算装置についての理解を容易にするために、先ず、前記演算装置が算出する補正値を用いて形状制御機構の制御が行われる多段圧延機の一例としての6段圧延機の概要を、図1に基づいて説明する。その後、本発明の知見について概略的な説明を行い、本実施形態の演算装置の構成について詳細に説明する。
In the following description, in order to facilitate understanding of the arithmetic device according to one aspect of the present invention, first, an example of a multi-high rolling mill in which the shape control mechanism is controlled using a correction value calculated by the arithmetic device. An outline of the 6-high rolling mill will be described with reference to FIG. After that, the knowledge of the present invention will be outlined and the configuration of the arithmetic device of this embodiment will be described in detail.
(6段圧延機の概略的構成)
図1は、本実施の形態における演算装置を備える多段圧延機の一例としての6段圧延機1の構成を示す概略図である。6段圧延機1は、圧延材8を冷間圧延する冷間圧延機である。この6段圧延機1は、複数の圧延機が連続的に配置された圧延システムにおける最終パスの圧延機であってもよいし、最終パスを含む複数パスを実行する単一の圧延機であってもよい。圧延材8としては、例えば鋼帯等の金属帯である。圧延材8は樹脂材であってもよい。 (Schematic configuration of 6-high rolling mill)
FIG. 1 is a schematic diagram illustrating a configuration of a six-high rollingmill 1 as an example of a multi-high rolling mill provided with a calculation device according to the present embodiment. The six-high rolling mill 1 is a cold rolling mill that cold-rolls the rolled material 8. The six-high rolling mill 1 may be a final-pass rolling mill in a rolling system in which a plurality of rolling mills are continuously arranged, or a single rolling mill that executes a plurality of passes including the final pass. May be. The rolled material 8 is a metal strip such as a steel strip, for example. The rolled material 8 may be a resin material.
図1は、本実施の形態における演算装置を備える多段圧延機の一例としての6段圧延機1の構成を示す概略図である。6段圧延機1は、圧延材8を冷間圧延する冷間圧延機である。この6段圧延機1は、複数の圧延機が連続的に配置された圧延システムにおける最終パスの圧延機であってもよいし、最終パスを含む複数パスを実行する単一の圧延機であってもよい。圧延材8としては、例えば鋼帯等の金属帯である。圧延材8は樹脂材であってもよい。 (Schematic configuration of 6-high rolling mill)
FIG. 1 is a schematic diagram illustrating a configuration of a six-high rolling
図1に示すように、6段圧延機1は、圧延材8をその厚さ方向に挟み込む一対のワークロール9、一対のワークロール9をその対向方向に各々押圧する一対のバックアップロール11、および、ワークロール9とバックアップロール11との間に配され、ワークロール9を支持する一対の中間ロール10、を備えている。図1において、これらのロールは、紙面に対して垂直方向が長手方向となっており、圧延材8は紙面上を右方向から左方向へと流れて圧延されるようになっている。
As shown in FIG. 1, the six-high rolling mill 1 includes a pair of work rolls 9 that sandwich the rolled material 8 in the thickness direction, a pair of backup rolls 11 that respectively press the pair of work rolls 9 in the opposing direction, and And a pair of intermediate rolls 10 that are arranged between the work roll 9 and the backup roll 11 and support the work roll 9. In FIG. 1, these rolls have a longitudinal direction perpendicular to the paper surface, and the rolled material 8 flows and rolls on the paper surface from the right to the left.
また、6段圧延機1は、中間ロールシフト機構2、中間ロールベンダー3、差荷重発生装置4、形状検出器7、およびプロセスコンピュータ6を備えている。ここで、中間ロールシフト機構2および中間ロールベンダー3は、圧延後の薄板の圧延形状の対称成分を制御する形状制御機構である。また、差荷重発生装置4は、圧延後の薄板の圧延形状の非対称成分を制御する形状制御機構である。
The six-high rolling mill 1 includes an intermediate roll shift mechanism 2, an intermediate roll bender 3, a differential load generator 4, a shape detector 7, and a process computer 6. Here, the intermediate roll shift mechanism 2 and the intermediate roll bender 3 are shape control mechanisms that control symmetrical components of the rolled shape of the thin sheet after rolling. The differential load generator 4 is a shape control mechanism that controls an asymmetric component of the rolling shape of the thin sheet after rolling.
中間ロールシフト機構2は、片側端部に1段あるいは多段のテーパ部を設けた中間ロール10をその軸方向に移動させることにより、該テーパ部を移動させ、これにより、中間ロール10と、ワークロール9およびバックアップロール11との接触荷重分布を変化させ、圧延後の薄板の圧延形状を制御する。なお、中間ロール10はテーパ部が設けられていなくてもよい。
The intermediate roll shift mechanism 2 moves the taper portion by moving the intermediate roll 10 having one or more taper portions at one end in the axial direction thereof. The contact load distribution with the roll 9 and the backup roll 11 is changed to control the rolling shape of the thin sheet after rolling. Note that the intermediate roll 10 may not be provided with a tapered portion.
中間ロールベンダー3は、中間ロール10が圧延材8の厚さ方向に曲がる力を、中間ロール10に付与する。
The intermediate roll bender 3 gives the intermediate roll 10 a force by which the intermediate roll 10 bends in the thickness direction of the rolled material 8.
差荷重発生装置4は、バックアップロール11の長手方向における荷重の非対称性を制御するための差荷重を発生させる装置である。ここで、バックアップロール11には、その両端の軸受部(チョック)を介して、油圧により荷重がかかるようになっていてもよい。この場合、荷重がかかるのは、ドライブサイドのチョックと、ワークサイドのチョックとの2箇所である。ドライブサイドとは、6段圧延機1において、前記ワークロール9を回転させるためのモータ(図示せず)が設けられている側であり、ワークサイドとは、6段圧延機1を挟んでドライブサイドの反対側のことである。差荷重発生装置4は、ドライブサイドのチョックにかかる荷重と、ワークサイドのチョックにかかる荷重とについて、互いの荷重に差を発生させる装置であり、この荷重の差が差荷重である。
The differential load generator 4 is a device that generates a differential load for controlling the load asymmetry in the longitudinal direction of the backup roll 11. Here, a load may be applied to the backup roll 11 by hydraulic pressure via bearing portions (chock) at both ends thereof. In this case, the load is applied at two places, a drive side chock and a work side chock. The drive side is a side where a motor (not shown) for rotating the work roll 9 is provided in the 6-high rolling mill 1, and the work side is a drive with the 6-high rolling mill 1 interposed therebetween. It is the opposite side. The differential load generating device 4 is a device that generates a difference between the loads applied to the drive side chock and the load applied to the work side chock, and the difference between the loads is the differential load.
形状検出器7は、圧延後の圧延材8の形状を検出する装置であり、検出結果を示す信号をプロセスコンピュータ6に出力する。
The shape detector 7 is a device that detects the shape of the rolled material 8 after rolling, and outputs a signal indicating the detection result to the process computer 6.
プロセスコンピュータ6は、形状検出器7の出力信号に基づいて、中間ロールシフト機構2、中間ロールベンダー3、および差荷重発生装置4を制御する。
The process computer 6 controls the intermediate roll shift mechanism 2, the intermediate roll bender 3, and the differential load generator 4 based on the output signal of the shape detector 7.
さらに6段圧延機1は、プロセスコンピュータ6を制御する上位コンピュータ5を備えている。上位コンピュータ5は、制御パラメータ等を表示する表示部5a(例えば、液晶ディスプレイなどの表示装置)、および制御パラメータを変更するための入力を受け付ける入力部5b(例えば、マウス、キーボード)を備えている。
Further, the six-high rolling mill 1 includes a host computer 5 that controls the process computer 6. The host computer 5 includes a display unit 5a (for example, a display device such as a liquid crystal display) that displays control parameters and the like, and an input unit 5b (for example, a mouse and a keyboard) that receives input for changing the control parameters. .
詳しくは後述するが、本発明の一態様における演算装置は、前記プロセスコンピュータ6に含まれる装置として実現することができる。プロセスコンピュータ6では、該演算装置が算出する補正値を用いて形状制御機構の制御が行われる。
Although described in detail later, the arithmetic device according to an aspect of the present invention can be realized as a device included in the process computer 6. In the process computer 6, the shape control mechanism is controlled using the correction value calculated by the arithmetic unit.
(発明の知見の概略的な説明)
以下、前記6段圧延機1を例にして、本発明の一態様における演算装置の技術的思想について説明する。なお、ここでは6段圧延機1を例にするが、4段圧延機、12段圧延機、および20段圧延機等の、6段圧延機以外の多段圧延機に対しても同様に本発明が適用されることは勿論である。4段圧延機の場合には、ワークロールベンダーおよび差荷重発生装置を制御対象として、本発明を適用することができる。 (Schematic explanation of the findings of the invention)
Hereinafter, the technical idea of the arithmetic device according to one aspect of the present invention will be described using the six-high rolling mill 1 as an example. In addition, although the 6-high rolling mill 1 is taken as an example here, the present invention is similarly applied to multi-high rolling mills other than the 6-high rolling mill, such as a 4-high rolling mill, a 12-high rolling mill, and a 20-high rolling mill. Of course, is applied. In the case of a four-high rolling mill, the present invention can be applied to a work roll bender and a differential load generator as control targets.
以下、前記6段圧延機1を例にして、本発明の一態様における演算装置の技術的思想について説明する。なお、ここでは6段圧延機1を例にするが、4段圧延機、12段圧延機、および20段圧延機等の、6段圧延機以外の多段圧延機に対しても同様に本発明が適用されることは勿論である。4段圧延機の場合には、ワークロールベンダーおよび差荷重発生装置を制御対象として、本発明を適用することができる。 (Schematic explanation of the findings of the invention)
Hereinafter, the technical idea of the arithmetic device according to one aspect of the present invention will be described using the six-
圧延形状に影響する変動要因には、板厚、材質、潤滑状態、圧延荷重等の外乱、および、中間ロールベンダー、ワークロールベンダー、中間ロールシフト、差荷重発生装置等の形状制御機構の制御量がある。板厚は、重要な品質項目であり、通常は自動板厚制御によってほぼ一定値となるように制御されている。材質及び潤滑状態は圧延形状に影響するが、その影響の大半は圧延荷重の変動に応じてロール撓みが変化することにより生じる。したがって、圧延中に形状変化をもたらす主要因は、圧延荷重および形状制御機構の制御量である。
The fluctuation factors that affect the rolling shape include disturbances such as plate thickness, material, lubrication state, rolling load, and control amount of shape control mechanisms such as intermediate roll bender, work roll bender, intermediate roll shift, and differential load generator. There is. The plate thickness is an important quality item, and is usually controlled to be a substantially constant value by automatic plate thickness control. The material and the lubrication state influence the rolling shape, but most of the influence is caused by the roll deflection changing according to the fluctuation of the rolling load. Therefore, the main factors that cause the shape change during rolling are the rolling load and the control amount of the shape control mechanism.
一般に、形状制御機構の制御量は、圧延形状を予測する制御式に基づいて設定される。該制御式には、伸び率差に及ぼす形状制御機構の影響度を示す影響係数が用いられる。しかしながら、従来、この影響係数の設定には、前述のような課題があった。
Generally, the control amount of the shape control mechanism is set based on a control expression for predicting the rolling shape. In the control equation, an influence coefficient indicating the degree of influence of the shape control mechanism on the elongation difference is used. However, conventionally, the setting of the influence coefficient has the above-described problems.
本発明者らは、圧延材の板幅方向の両端部における、板幅中央に対する伸び率差を表す数式モデルを用いて圧延形状を制御する場合に、良好な圧延形状が得られるように影響係数を高精度に近似する方法を種々調査検討した。その結果、影響係数を単位幅荷重(圧延材の単位幅に加えられる荷重)および板幅の関数で表すと、高精度に影響係数を近似できることを見出した。この新たな知見について順に説明する。
The present inventors have an influence coefficient so that a good rolling shape can be obtained when the rolling shape is controlled using a mathematical model representing the difference in elongation with respect to the center of the plate width at both ends in the plate width direction of the rolled material. Various methods for approximating the above were investigated. As a result, it was found that the influence coefficient can be approximated with high accuracy when the influence coefficient is expressed by a function of unit width load (load applied to the unit width of the rolled material) and sheet width. These new findings will be described in order.
本発明者らは、6段圧延機1において、以下のようにして圧延材の圧延形状を制御することとした。すなわち、中間ロールシフト機構2の制御量(シフト位置)を固定した状態において、形状検出器7の出力信号に基づいて、中間ロールベンダー3および差荷重発生装置4を制御して、圧延材の圧延形状を制御することとした。なお、下記の説明では、本発明の知見を説明する便宜上、6段圧延機1の中間ロールシフト機構2の制御量(シフト位置)を固定しているが、6段圧延機1を実際に動作させる場合には、中間ロールシフト機構2の制御量は固定されていなくともよい。本実施形態の6段圧延機1における主たる制御対象は中間ロールベンダー3および差荷重発生装置4である。その一方で、6段圧延機1の実際の動作において中間ロールシフト機構2が制御されることは除外されないことを理解されたい。
The inventors decided to control the rolling shape of the rolled material in the 6-high rolling mill 1 as follows. That is, in a state where the control amount (shift position) of the intermediate roll shift mechanism 2 is fixed, the intermediate roll bender 3 and the differential load generator 4 are controlled based on the output signal of the shape detector 7 to roll the rolled material. The shape was controlled. In the following description, the control amount (shift position) of the intermediate roll shift mechanism 2 of the six-high rolling mill 1 is fixed for convenience of explaining the knowledge of the present invention, but the six-high rolling mill 1 is actually operated. In this case, the control amount of the intermediate roll shift mechanism 2 may not be fixed. The main controlled objects in the six-high rolling mill 1 of the present embodiment are the intermediate roll bender 3 and the differential load generator 4. On the other hand, it should be understood that it is not excluded that the intermediate roll shift mechanism 2 is controlled in the actual operation of the six-high rolling mill 1.
ここで、圧延形状を対称成分と非対称成分とに分解して評価した。具体的には、次のように、圧延形状の対称成分を2次式で近似し、圧延形状の非対称成分を1次式で近似した。
Here, the rolling shape was evaluated by breaking it down into a symmetric component and an asymmetric component. Specifically, the symmetrical component of the rolling shape was approximated by a quadratic equation, and the asymmetric component of the rolled shape was approximated by a linear equation as follows.
y=a・(2x/W)2
y’=b・(2x/W)
上記式において、
y:圧延形状の対称成分
y’:圧延形状の非対称成分
W:板幅
x:板幅方向位置(ワークサイドの板端:-W/2、板幅中央:0、ドライブサイドの板端:W/2)
a、b:係数
である。 y = a · (2x / W) 2
y ′ = b · (2x / W)
In the above formula,
y: Symmetric component of rolled shape y ′: Asymmetric component of rolled shape W: Plate width x: Plate width direction position (work side plate end: −W / 2, plate width center: 0, drive side plate end: W / 2)
a, b: coefficients.
y’=b・(2x/W)
上記式において、
y:圧延形状の対称成分
y’:圧延形状の非対称成分
W:板幅
x:板幅方向位置(ワークサイドの板端:-W/2、板幅中央:0、ドライブサイドの板端:W/2)
a、b:係数
である。 y = a · (2x / W) 2
y ′ = b · (2x / W)
In the above formula,
y: Symmetric component of rolled shape y ′: Asymmetric component of rolled shape W: Plate width x: Plate width direction position (work side plate end: −W / 2, plate width center: 0, drive side plate end: W / 2)
a, b: coefficients.
そして、圧延材の圧延形状を制御する式として、下記の式(1)、(2)に示す制御式(圧延形状変化の予測式)を用いた。
And as a formula for controlling the rolling shape of the rolled material, the following control formulas (1) and (2) are used (control formula for predicting the rolling shape change).
ΔYS=A1・ΔFi (1)
ΔYN=A2・ΔSL (2)
上記式において、
YS:板端部における伸び率と板幅中央における伸び率との差(ワークサイドおよびドライブサイドの平均)
YN:ワークサイドの伸び率とドライブサイドの伸び率との差(伸び率差)
Fi:中間ロールベンダー力
SL:差荷重
ΔYS:板端部における伸び率と板幅中央における伸び率との差の変化量(ワークサイドおよびドライブサイドの平均)
ΔYN:ワークサイドの伸び率とドライブサイドの伸び率との差(伸び率差)の変化量
ΔFi:中間ロールベンダー力の変化量
ΔSL:差荷重の変化量
A1:中間ロールベンダー力の影響係数
A2:差荷重の影響係数
である。 ΔY S = A1 · ΔFi (1)
ΔY N = A2 · ΔS L (2)
In the above formula,
Y S : difference between the elongation at the edge of the plate and the elongation at the center of the plate width (average of work side and drive side)
Y N : Difference between work side elongation and drive side elongation (elongation difference)
Fi: Intermediate roll bender force S L : Differential load ΔY S : Amount of change in the difference between the elongation at the plate edge and the elongation at the center of the plate width (average of work side and drive side)
ΔY N : Change amount of difference between work side elongation rate and drive side elongation rate (elongation rate difference) ΔFi: Change amount of intermediate roll bender force ΔS L : Change amount of differential load A1: Influence of intermediate roll bender force Coefficient A2: Influence coefficient of differential load.
ΔYN=A2・ΔSL (2)
上記式において、
YS:板端部における伸び率と板幅中央における伸び率との差(ワークサイドおよびドライブサイドの平均)
YN:ワークサイドの伸び率とドライブサイドの伸び率との差(伸び率差)
Fi:中間ロールベンダー力
SL:差荷重
ΔYS:板端部における伸び率と板幅中央における伸び率との差の変化量(ワークサイドおよびドライブサイドの平均)
ΔYN:ワークサイドの伸び率とドライブサイドの伸び率との差(伸び率差)の変化量
ΔFi:中間ロールベンダー力の変化量
ΔSL:差荷重の変化量
A1:中間ロールベンダー力の影響係数
A2:差荷重の影響係数
である。 ΔY S = A1 · ΔFi (1)
ΔY N = A2 · ΔS L (2)
In the above formula,
Y S : difference between the elongation at the edge of the plate and the elongation at the center of the plate width (average of work side and drive side)
Y N : Difference between work side elongation and drive side elongation (elongation difference)
Fi: Intermediate roll bender force S L : Differential load ΔY S : Amount of change in the difference between the elongation at the plate edge and the elongation at the center of the plate width (average of work side and drive side)
ΔY N : Change amount of difference between work side elongation rate and drive side elongation rate (elongation rate difference) ΔFi: Change amount of intermediate roll bender force ΔS L : Change amount of differential load A1: Influence of intermediate roll bender force Coefficient A2: Influence coefficient of differential load.
ここで、対称成分に関する上記制御式(1)、および非対称成分に関する上記制御式(2)において、板幅方向位置xが(W/2)であるとして、板端部に関する形状変化を予測する近似式としている。
Here, in the control equation (1) regarding the symmetric component and the control equation (2) regarding the asymmetric component, it is assumed that the plate width direction position x is (W / 2). It is an expression.
図2は、板端部(圧延材の幅方向の端部)における伸び率と板幅中央(圧延材の幅方向の中央)における伸び率との差(伸び率差)YS(第1伸び率差)に及ぼす中間ロールベンダー力Fiの影響を示すグラフである。なお、前記伸び率差は10-5を単位とし、この単位をIunitと表示した(以下の記載においても同様に、Iunitとは10-5を表す単位である)。
FIG. 2 shows the difference (elongation rate difference) Y S (first elongation) between the elongation at the plate end (the end in the width direction of the rolled material) and the elongation at the center of the plate width (the center in the width direction of the rolled material). It is a graph which shows the influence of the intermediate | middle roll bender force Fi which acts on a rate difference. Incidentally, the elongation difference is 10-5 as a unit, the unit was labeled iunit (also in the following description, the iunit a unit representing a 10 -5).
中間ロールベンダー力Fiの変化は、ワークロール9、中間ロール10およびバックアップロール11の撓みの変化となって現れ、圧延材の形状を変化させる。中間ロールベンダー力Fiとロールの撓み量との関係は、弾性領域における変形を対象としていることからほぼ線形な関係にある。したがって、図2に示すように、伸び率差YSも中間ロールベンダー力Fiと線形関係にある。そして、図2の線形関係における傾きが中間ロールベンダー力Fiの影響係数A1であり、このことは前記式(1)にて表される。
The change in the intermediate roll bender force Fi appears as a change in the bending of the work roll 9, the intermediate roll 10, and the backup roll 11, and changes the shape of the rolled material. The relationship between the intermediate roll bender force Fi and the amount of deflection of the roll is substantially linear because it is intended for deformation in the elastic region. Therefore, as shown in FIG. 2, the elongation difference Y S is also linearly related to the intermediate roll bender force Fi. The slope in the linear relationship of FIG. 2 is the influence coefficient A1 of the intermediate roll bender force Fi, which is expressed by the above equation (1).
図3は、ワークサイドの伸び率とドライブサイドの伸び率との差(伸び率差)YN(第2伸び率差)に及ぼす差荷重SLの影響を示すグラフである。つまり、圧延材の幅方向の両端部間の伸び率差YNに及ぼす差荷重SLの影響を示したものである。差荷重SLの変化は、ワークロール9、中間ロール10およびバックアップロール11の撓みの変化となって現れ、圧延材の形状を変化させる。差荷重SLとロールの撓み量との関係は、弾性領域における変形を対象としていることからほぼ線形な関係にある。したがって、図3に示すように、ワークサイドの伸び率とドライブサイドの伸び率との差YNも差荷重SLと線形関係にある。そして、図3の線形関係における傾きが差荷重SLの影響係数A2であり、このことは前記式(2)にて表される。
Figure 3 is a graph showing the effect of the difference load S L on the difference (elongation difference) Y N (second elongation difference) between the elongation of the work side and drive side elongation. That is, it shows the influence of the differential load S L on the elongation difference Y N between both ends in the width direction of the rolled material. Change in the difference load S L is the work rolls 9, it appears as a deflection change of the intermediate roll 10 and backup roll 11, to change the shape of the rolled material. Relationship between the difference load S L and the amount of deflection of the roll is approximately linear relationship because it is intended for deformation in the elastic region. Therefore, as shown in FIG. 3, the difference Y N between the work side elongation rate and the drive side elongation rate is also in a linear relationship with the differential load S L. Then, an influence coefficient of the slope difference load S L A2 in the linear relationship of FIG. 3, this is represented by the formula (2).
ここで、図2および図3に示す各プロットは、形状予測の解析プログラムを用いて算出される。一般に、形状予測の解析プログラムは、圧延材の形状を予測するために用いられている。例えば、非特許文献2には、圧延材の板クラウン・平坦度の計算に関する既存の形状解析方法の例が記載されている。フローチャートにて説明されているような収束計算を行い、圧延材の板クラウン・平坦度を計算することができる。
Here, each plot shown in FIGS. 2 and 3 is calculated using an analysis program for shape prediction. Generally, the shape prediction analysis program is used to predict the shape of a rolled material. For example, Non-Patent Document 2 describes an example of an existing shape analysis method related to calculation of the sheet crown and flatness of a rolled material. The convergence calculation as described in the flowchart can be performed to calculate the sheet crown and flatness of the rolled material.
同様の考え方(手法)にて、板クラウン・平坦度以外の板形状(板プロファイル)についても形状解析を行うことができる。通常、当業者は、解析の対象とする板プロファイルに応じて、既存の形状解析技術を応用して、操業条件に対応した板プロファイルを計算により求め、圧延条件の調整を行っている。
Using the same concept (method), shape analysis can be performed for plate shapes (plate profiles) other than plate crown and flatness. Usually, those skilled in the art apply a conventional shape analysis technique according to a plate profile to be analyzed, obtain a plate profile corresponding to the operation conditions by calculation, and adjust the rolling conditions.
本発明者らは、既存の形状解析技術を応用した解析プログラムを用いている。この解析プログラムを用いて、板プロファイルのうち板幅中央部および板端部の点の伸び率を計算により求め、伸び率差YSおよび伸び率差YNを評価することができる。
The present inventors use an analysis program that applies an existing shape analysis technique. Using this analysis program, it is possible to evaluate the elongation rate difference Y S and the elongation rate difference Y N by calculating the elongation rates of the plate width center portion and the plate end portion of the plate profile.
形状予測の解析プログラムを用いて、図2および図3の各プロットを算出することにより、或る圧延条件下での影響係数A1、A2を求めることができる。なお、影響係数の算出に用いられるプロットの数は4個以上とすることが好ましい。これは、各プロットを通過するように描いた(或いは、各プロットについて最小二乗近似した)直線の傾きとしての影響係数の値をより正確に求めるためである。
The influence coefficients A1 and A2 under certain rolling conditions can be obtained by calculating the plots of FIGS. 2 and 3 using the shape prediction analysis program. The number of plots used for calculating the influence coefficient is preferably 4 or more. This is for more accurately obtaining the value of the influence coefficient as the slope of a straight line drawn so as to pass through each plot (or approximated by least squares for each plot).
ここで、上記の演算は、演算の前提となる所定の(設定した)圧延条件の下で行うことになる。例えば、圧延荷重(単位幅荷重)が変化すれば、それに応じて影響係数A1、A2も変化することになる。
Here, the above calculation is performed under predetermined (set) rolling conditions that are the premise of the calculation. For example, if the rolling load (unit width load) changes, the influence coefficients A1 and A2 also change accordingly.
一般に、圧延を行う工場等の現場においては、圧延機をそれぞれ含む複数の圧延ラインが設けられ得る。そして、それぞれの圧延ラインには、所望の製品のロットに応じて、様々な品種(板幅、板厚、変形抵抗)の圧延材が流され得る。或る圧延ラインにおいて対応可能な圧延材の品種(板幅、板厚、変形抵抗)の範囲が、予め設定される。
Generally, at a site such as a factory that performs rolling, a plurality of rolling lines each including a rolling mill can be provided. Then, various kinds of rolled materials (sheet width, sheet thickness, deformation resistance) can be flowed through each rolling line in accordance with a desired product lot. The range of types of rolled material (sheet width, sheet thickness, deformation resistance) that can be handled in a certain rolling line is set in advance.
圧延ラインに流される圧延材の品種が変化すれば、それに対応して圧延機における圧延条件も変化する。また、圧延材に与えられる単位幅荷重は、パススケジュールに応じて適宜変動し得る。各種の圧延条件に応じて、図2および図3の各プロットをその都度算出し、或る圧延条件における影響係数A1、A2を求めることは現実的ではない。これは、そのような場合、(i)圧延材の品種を変更する度に影響係数を算出する時間を要する、および、(ii)単位幅荷重の変化に応じて影響係数を調整することができない、ためである。
If the type of rolled material that flows in the rolling line changes, the rolling conditions in the rolling mill change accordingly. Further, the unit width load applied to the rolled material can be appropriately changed according to the pass schedule. It is not realistic to calculate the respective plots of FIG. 2 and FIG. 3 each time according to various rolling conditions and obtain the influence coefficients A1 and A2 under a certain rolling condition. In such a case, in such a case, (i) it takes time to calculate the influence coefficient every time the type of rolled material is changed, and (ii) the influence coefficient cannot be adjusted in accordance with the change in the unit width load. Because.
従来、前記式(1)および(2)の数式モデルに用いられる、中間ロールベンダー力Fiの影響係数A1、および差荷重SLの影響係数A2を高精度に近似する方法は知られていなかった。そこで、本発明者らは、影響係数A1およびA2を高精度に近似する方法を種々調査検討した結果、以下のような知見を得た。
Conventionally, used for mathematical model of the formula (1) and (2) a method for approximating the influence coefficient of the intermediate roll bender force Fi A1, and the influence coefficient A2 of the difference load S L with high accuracy has not been known . Therefore, as a result of various investigations and studies on methods for approximating the influence coefficients A1 and A2 with high accuracy, the present inventors have obtained the following knowledge.
例えば、板厚0.8mm~4.0mm、板幅850mm~1050mm、材料の変形抵抗700N/mm2~1200N/mm2の範囲において、中間ロールベンダー力Fiの影響係数A1を形状予測の数値解析により求めた結果を図4に示す。図4は、中間ロールベンダー力Fiの影響係数A1に及ぼす、単位幅荷重pおよび板幅Wの影響を示すグラフである。この形状予測の数値解析は、上述のように、既存の解析プログラムを用いて行うことができる。
For example, plate thickness 0.8 mm ~ 4.0 mm, the plate width 850 mm ~ 1050 mm, in the range of deformation resistance 700N / mm 2 ~ 1200N / mm 2 of the material, the numerical analysis of the influence coefficients A1 of the intermediate roll bender force Fi shape prediction FIG. 4 shows the result obtained by the above. FIG. 4 is a graph showing the influence of the unit width load p and the plate width W on the influence coefficient A1 of the intermediate roll bender force Fi. The numerical analysis of the shape prediction can be performed using an existing analysis program as described above.
具体的には、図4に示すプロットは、以下のようにして求める。先ず、板厚、板幅、および材料の変形抵抗の上記範囲内における或る条件に基づいて、公知の圧延荷重式を用いて、圧延荷重を求める。圧延荷重は、圧延前後における板厚の変動、圧延材に与えられる張力、および材料の変形抵抗(鋼種)等に応じて定まる。例えば、鋼種NCH780の鋼板について、公知の圧延荷重式を用いて、6パスの圧延を行う場合の圧延荷重を算出した一例を表1に示す。なお、圧延荷重式については複数種類の式が知られている。どの圧延荷重式を用いるかについては、ユーザ等が適切な式を選択して、使用すればよい。圧延荷重式については、公知の技術であるので、説明を省略する。
Specifically, the plot shown in FIG. 4 is obtained as follows. First, the rolling load is obtained using a known rolling load equation based on certain conditions within the above ranges of the plate thickness, the plate width, and the deformation resistance of the material. The rolling load is determined according to fluctuations in sheet thickness before and after rolling, tension applied to the rolled material, deformation resistance (steel type) of the material, and the like. For example, Table 1 shows an example of calculating the rolling load when performing a 6-pass rolling on a steel plate of steel type NCH780 using a known rolling load equation. A plurality of types of rolling load formulas are known. As to which rolling load formula is used, the user or the like may select and use an appropriate formula. Since the rolling load formula is a known technique, description thereof is omitted.
このように、公知の圧延荷重式を用いて、所定の板厚、板幅、および材料の変形抵抗の条件における圧延荷重を算出することができる。算出した圧延荷重を板幅(例えば1050mm)で除算することにより、単位幅荷重を算出する。
Thus, the rolling load under the conditions of a predetermined plate thickness, plate width, and material deformation resistance can be calculated using a known rolling load equation. A unit width load is calculated by dividing the calculated rolling load by a sheet width (for example, 1050 mm).
そして、或る板幅および単位幅荷重の条件において、形状予測の数値解析を用いて、図2に示したようなプロットを算出することができる。その結果、影響係数A1を求めることができる。これらの手順を、或る圧延ラインの圧延機が対応可能な範囲の圧延材の品種(板幅、板厚、変形抵抗)について行うことにより、図4に示すプロットを算出することができる。
Then, a plot as shown in FIG. 2 can be calculated using a numerical analysis of shape prediction under certain plate width and unit width load conditions. As a result, the influence coefficient A1 can be obtained. The plot shown in FIG. 4 can be calculated by performing these procedures for the types of rolled material (sheet width, sheet thickness, deformation resistance) in a range that can be handled by a rolling mill of a certain rolling line.
すなわち、形状予測の解析プログラムを用いて、板厚、板幅、および材料の変形抵抗を上記の範囲で変化させて解析を行い、それぞれの条件で影響係数A1(中間ロールベンダー力Fiを変化させて解析したときの、中間ロールベンダー力Fiの制御量と伸び率差Ysとの線形関係における傾き)を算出する。これにより、図4に示すように、板幅Wおよび単位幅荷重pが、影響係数A1に及ぼす影響について整理できる。例えば、所定の前提条件のもとで、板幅が1050mm、単位幅荷重が約6300N/mmの条件にて求めた影響係数A1は約-0.3Iunit/kNであった。これは図4に示す18個のプロットのうち、右端下段の四角形のプロットに対応する。
That is, using the shape prediction analysis program, analysis is performed by changing the thickness, width, and deformation resistance of the material within the above ranges, and the influence coefficient A1 (intermediate roll bender force Fi is changed under each condition. The slope of the linear relationship between the control amount of the intermediate roll bender force Fi and the elongation difference Ys) is calculated. Thereby, as shown in FIG. 4, the influence which the board width W and the unit width load p exert on the influence coefficient A1 can be arranged. For example, under a predetermined precondition, the influence coefficient A1 obtained under the condition that the plate width is 1050 mm and the unit width load is about 6300 N / mm is about −0.3 Iunit / kN. This corresponds to a square plot at the lower right end of the 18 plots shown in FIG.
ここで、板厚、板幅、および材料の変形抵抗は圧延材の形状に影響するが、その影響のほとんどは圧延荷重分布を介したロール撓みの変化によって生じる。また、圧延荷重のワークロール9への作用領域は、板幅に依存して変化する。
Here, the plate thickness, the plate width, and the deformation resistance of the material influence the shape of the rolled material, but most of the influence is caused by the change in roll deflection through the rolling load distribution. Moreover, the action area | region to the work roll 9 of a rolling load changes depending on a board width.
したがって、本発明者らは、中間ロールベンダー力Fiの影響係数A1は、単位幅荷重pと板幅Wで整理できるのではないかと考えた。また、図4に示すように、同じ板幅の場合、単位幅荷重pの増加とともに、中間ロールベンダー力Fiの影響係数A1の絶対値は減少し、単位幅荷重pの大きいところでは単位幅荷重pが影響係数A1に及ぼす影響が小さいことがわかった。そして、板幅Wが増加するにつれて中間ロールベンダー力Fiの影響係数A1は減少する。このことから、板幅Wの影響度に単位幅荷重pが影響するという新たな知見も得た。
Therefore, the present inventors thought that the influence coefficient A1 of the intermediate roll bender force Fi could be arranged by the unit width load p and the plate width W. As shown in FIG. 4, in the case of the same plate width, the absolute value of the influence coefficient A1 of the intermediate roll bender force Fi decreases as the unit width load p increases, and the unit width load increases when the unit width load p is large. It was found that the influence of p on the influence coefficient A1 is small. As the plate width W increases, the influence coefficient A1 of the intermediate roll bender force Fi decreases. From this, the new knowledge that the unit width load p influences the influence degree of the plate width W was also obtained.
そこで、本発明者らは、中間ロールベンダー力Fiの影響係数A1を高精度に近似する式を探索し、下記の式(3)を用いることによって、影響係数A1を高精度に近似することができることを見出した。
Accordingly, the present inventors can search for an expression that approximates the influence coefficient A1 of the intermediate roll bender force Fi with high accuracy, and approximate the influence coefficient A1 with high accuracy by using the following expression (3). I found out that I can do it.
A1=a11・(1/p)+a12・(W/p)+a13 (3)
上記式において、
A1:中間ロールベンダー力Fiの影響係数
p:単位幅荷重
W:板幅
a11、a12、a13:中間ロールベンダー力Fiの影響係数A1の近似式における係数
である。 A1 = a1 1 · (1 / p) + a1 2 · (W / p) + a1 3 (3)
In the above formula,
A1: Influence coefficient of intermediate roll bender force Fi p: Unit width load W: Plate width a1 1 , a1 2 , a1 3 : A coefficient in an approximate expression of influence coefficient A1 of intermediate roll bender force Fi.
上記式において、
A1:中間ロールベンダー力Fiの影響係数
p:単位幅荷重
W:板幅
a11、a12、a13:中間ロールベンダー力Fiの影響係数A1の近似式における係数
である。 A1 = a1 1 · (1 / p) + a1 2 · (W / p) + a1 3 (3)
In the above formula,
A1: Influence coefficient of intermediate roll bender force Fi p: Unit width load W: Plate width a1 1 , a1 2 , a1 3 : A coefficient in an approximate expression of influence coefficient A1 of intermediate roll bender force Fi.
図4に示すデータについて、前記式(3)を用いて重回帰分析を行った結果、近似式における各係数は表2に示すようになり、高い相関関係が得られた。この重回帰分析については、数値解析における一般的な手法であるので、ここでは説明を省略する。
As a result of performing multiple regression analysis on the data shown in FIG. 4 using the above equation (3), the coefficients in the approximate equation are as shown in Table 2, and a high correlation was obtained. Since this multiple regression analysis is a general technique in numerical analysis, description thereof is omitted here.
同様に、板厚0.8mm~4.0mm、板幅850mm~1050mm、材料の変形抵抗700N/mm2~1200N/mm2の範囲において、差荷重SLの影響係数A2を形状予測の数値解析により求めた結果を図5に示す。この形状予測の数値解析も、形状予測の解析プログラムを用いて行うことができる。ここで、板厚、板幅、および材料の変形抵抗は圧延材の形状に影響するが、その影響のほとんどは圧延荷重分布を介したロール撓みの変化によって生じる。また、圧延荷重のワークロール9への作用領域は、板幅に依存して変化する。
Similarly, thickness 0.8 mm ~ 4.0 mm, the plate width 850 mm ~ 1050 mm, in the range of deformation resistance 700N / mm 2 ~ 1200N / mm 2 of the material, the numerical analysis of the influence coefficient A2 of the difference load S L shape prediction FIG. 5 shows the result obtained by the above. The numerical analysis of the shape prediction can also be performed using a shape prediction analysis program. Here, the plate thickness, the plate width, and the deformation resistance of the material influence the shape of the rolled material, but most of the influence is caused by changes in roll deflection through the rolling load distribution. Moreover, the action area | region to the work roll 9 of a rolling load changes depending on a board width.
したがって、本発明者らは、差荷重SLの影響係数A2についても同様に、単位幅荷重pと板幅Wで整理できると考えた。また、図5に示すように、同じ板幅の場合、単位幅荷重pの増加とともに、差荷重SLの影響係数A2の絶対値は減少し、単位幅荷重pの大きいところでは単位幅荷重pが影響係数A2に及ぼす影響が小さいことがわかった。そして、板幅Wが増加するにつれて差荷重SLの影響係数A2は減少し、板幅Wの影響度に単位幅荷重pが影響する。
Accordingly, the present inventors, also the influence coefficient A2 of the difference load S L, was considered to be organized in a unit width load p and the plate width W. Further, as shown in FIG. 5, for the same plate width, with increasing unit width load p, the difference load S absolute value of the influence coefficient A2 of L decreases, the unit width load p is at large unit width load p Has a small influence on the influence coefficient A2. Then, the influence coefficient A2 of the difference load S L as the plate width W is increased to decrease, the unit width load p affects the impact of the plate width W.
このことから、上記した中間ロールベンダー力Fiの影響係数A1と同様に、差荷重SLの影響係数A2についても、下記の式(4)を用いることによって高精度に近似することができることを見出した。
Therefore, similarly to the influence coefficient A1 of the intermediate roll bender force Fi as described above, the influence coefficient A2 of the difference load S L, it found that can be approximated with high accuracy by using equation (4) below It was.
A2=a21・(1/p)+a22・(W/p)+a23 (4)
上記式において、
A2:差荷重の影響係数
p:単位幅荷重
W:板幅
a21、a22、a23:差荷重SLの影響係数A2の近似式における係数
である。 A2 = a2 1 · (1 / p) + a2 2 · (W / p) + a2 3 (4)
In the above formula,
A2: influence coefficient of the difference load p: unit width load W: strip width a2 1, a2 2, a2 3 : is a coefficient in the approximation formula of the influence coefficient A2 of the difference load S L.
上記式において、
A2:差荷重の影響係数
p:単位幅荷重
W:板幅
a21、a22、a23:差荷重SLの影響係数A2の近似式における係数
である。 A2 = a2 1 · (1 / p) + a2 2 · (W / p) + a2 3 (4)
In the above formula,
A2: influence coefficient of the difference load p: unit width load W: strip width a2 1, a2 2, a2 3 : is a coefficient in the approximation formula of the influence coefficient A2 of the difference load S L.
図5に示すデータについて、前記式(4)を用いて重回帰分析を行った結果、近似式における各係数は表3に示すようになり、高い相関関係が得られた。
As a result of performing multiple regression analysis on the data shown in FIG. 5 using the formula (4), the coefficients in the approximate formula are as shown in Table 3, and a high correlation was obtained.
これらの前記式(3)および(4)をまとめると、以下のように表すことができる。すなわち、中間ロールベンダー力Fiおよび差荷重SLといった形状制御機構の影響係数Aは、単位幅荷重pと板幅Wとで整理でき、式(5)で近似できる。
These formulas (3) and (4) can be summarized as follows. That is, the influence coefficient A of the intermediate roll bender forces Fi and difference load S L, such shape control mechanism, can organize in a unit width load p and the plate width W, can be approximated by equation (5).
A=a1・(1/p)+a2・(W/p)+a3 (5)
上記式において、
A:影響係数
p:単位幅荷重
W:板幅
a1、a2、a3:影響係数の近似式における係数
である。 A = a 1 · (1 / p) + a 2 · (W / p) + a 3 (5)
In the above formula,
A: influence coefficient p: unit width load W: plate width a 1 , a 2 , a 3 : coefficients in an approximate expression of the influence coefficient.
上記式において、
A:影響係数
p:単位幅荷重
W:板幅
a1、a2、a3:影響係数の近似式における係数
である。 A = a 1 · (1 / p) + a 2 · (W / p) + a 3 (5)
In the above formula,
A: influence coefficient p: unit width load W: plate width a 1 , a 2 , a 3 : coefficients in an approximate expression of the influence coefficient.
なお、本明細書において、影響係数Aとの区別が明確となるように、係数(a11、a12、a13)、係数(a21、a22、a23)、および係数(a1、a2、a3)を、以下では、近似式係数と称することがある。
In the present specification, the coefficient (a1 1 , a1 2 , a1 3 ), the coefficient (a2 1 , a2 2 , a2 3 ), and the coefficient (a 1 , Hereinafter, a 2 and a 3 ) may be referred to as approximate expression coefficients.
以上のように、式(3)および(4)を用いて、高精度に影響係数を近似することができ、近似した影響係数を用いて高精度な形状制御を行うことができる。具体的には、形状解析モデルを用いて、板厚、板幅、および材料の変形抵抗を広範囲に変化させて解析を行い、それぞれの条件で影響係数A(形状制御機構を変化させて解析したときの、形状制御機構の制御量と伸び率差との線形関係における傾き)を算出する。これにより、図4および図5に示すように、板幅Wと単位幅荷重pが、影響係数Aに及ぼす影響について整理できる。そして、影響係数Aを式(3)または式(4)で表したときの近似式係数(a11、a12、a13)または近似式係数(a21、a22、a23)を、それぞれ重回帰分析により予め求める。
As described above, it is possible to approximate the influence coefficient with high accuracy using the equations (3) and (4), and it is possible to perform highly accurate shape control using the approximate influence coefficient. Specifically, using the shape analysis model, analysis was performed by changing the thickness, width, and deformation resistance of the material over a wide range, and the influence coefficient A (the shape control mechanism was changed under each condition). The slope of the linear relationship between the control amount of the shape control mechanism and the elongation difference is calculated. Thereby, as shown in FIGS. 4 and 5, the influence of the plate width W and the unit width load p on the influence coefficient A can be arranged. Then, when the influence coefficient A is expressed by the expression (3) or the expression (4), the approximate expression coefficient (a1 1 , a1 2 , a1 3 ) or the approximate expression coefficient (a2 1 , a2 2 , a2 3 ), respectively, Obtained beforehand by multiple regression analysis.
この近似式係数は、或る圧延ラインにおける、対応可能な圧延材の品種(板幅、板厚、変形抵抗)の範囲に対応して、予め求めることができる。この範囲(操業条件)は、様々な条件に応じて設定され得るが、例えば、重回帰分析を行った結果として高い相関係数が得られるような範囲に操業条件を区分して設定されてもよい。この相関係数の値としては、0.9以上であればよく、好ましくは0.95以上である。相関係数が0.9以上であれば、そのような近似式係数を含む影響係数の近似式は、実用に供することが充分に可能である。
This approximate expression coefficient can be obtained in advance corresponding to the range of types of rolled material (sheet width, sheet thickness, deformation resistance) that can be handled in a certain rolling line. This range (operating condition) can be set according to various conditions. For example, even if the operating condition is divided and set in such a range that a high correlation coefficient is obtained as a result of the multiple regression analysis. Good. The correlation coefficient value may be 0.9 or more, and preferably 0.95 or more. If the correlation coefficient is 0.9 or more, the approximate expression of the influence coefficient including such an approximate expression coefficient can be sufficiently put into practical use.
予め求めた近似式係数を代入して、式(3)で表される近似式を用いることにより、或る単位幅荷重pおよび板幅Wにおける影響係数A1を算出することができる。また、その単位幅荷重pおよび板幅Wにおいて、式(4)で表される近似式を用いて、影響係数A2を算出することができる。
By substituting the approximate expression coefficient obtained in advance and using the approximate expression represented by Expression (3), the influence coefficient A1 for a certain unit width load p and plate width W can be calculated. In addition, in the unit width load p and the plate width W, the influence coefficient A2 can be calculated using an approximate expression represented by Expression (4).
これにより、例えば、図4および図5に示すような複数のプロットの間の単位幅荷重pおよび板幅Wの条件における影響係数A1および影響係数A2を高精度に近似して求めることができる。
Thereby, for example, the influence coefficient A1 and the influence coefficient A2 under the conditions of the unit width load p and the plate width W between a plurality of plots as shown in FIGS. 4 and 5 can be obtained by approximating with high accuracy.
そして、求めた影響係数A1および影響係数A2を用いて、式(1)および(2)に基づいて、中間ロールベンダー力Fiおよび差荷重SLの制御量を制御することにより、形状制御を高精度に行うことができ、良好な圧延形状が得られる。
Then, using the obtained influence coefficient A1 and influence coefficient A2, the control amount of the intermediate roll bender force Fi and the differential load SL is controlled based on the equations (1) and (2), thereby improving the shape control. It can be performed with accuracy and a good rolling shape can be obtained.
(本発明の一態様における演算装置の構成)
以上の検討に用いた圧延機と同一の6段圧延機1において、中間ロールシフト機構2の制御量(シフト位置)を所定値に固定し、中間ロールベンダー3および差荷重発生装置4を制御して、形状検出器7の出力信号に基づいて形状制御を行う際に本発明を適用した例を、図6に基づいて以下に説明する。その中で、本発明の一態様における演算装置の構成について説明する。 (Configuration of arithmetic device in one embodiment of the present invention)
In the same 6-high rolling mill 1 as the rolling mill used for the above examination, the control amount (shift position) of the intermediate roll shift mechanism 2 is fixed to a predetermined value, and the intermediate roll bender 3 and the differential load generator 4 are controlled. An example in which the present invention is applied when performing shape control based on the output signal of the shape detector 7 will be described below with reference to FIG. Among them, the structure of the arithmetic device in one embodiment of the present invention is described.
以上の検討に用いた圧延機と同一の6段圧延機1において、中間ロールシフト機構2の制御量(シフト位置)を所定値に固定し、中間ロールベンダー3および差荷重発生装置4を制御して、形状検出器7の出力信号に基づいて形状制御を行う際に本発明を適用した例を、図6に基づいて以下に説明する。その中で、本発明の一態様における演算装置の構成について説明する。 (Configuration of arithmetic device in one embodiment of the present invention)
In the same 6-
本発明の一態様における演算装置は、例えば前記6段圧延機1が含むプロセスコンピュータ6の一機能として実現することができる。なお、本発明の一態様における演算装置は、プロセスコンピュータ6とは異なるコンピュータ(例えば、上位コンピュータ5)を用いて実現されてよく、ハードウェアは特に限定されない。
The arithmetic device according to one aspect of the present invention can be realized as one function of the process computer 6 included in the six-high rolling mill 1, for example. Note that the arithmetic device according to one embodiment of the present invention may be realized using a computer (for example, the host computer 5) different from the process computer 6, and hardware is not particularly limited.
図6に示すように、プロセスコンピュータ6は、制御部20および記憶部30を備えている。この制御部20には、プロセスコンピュータ6の外部に設けられた上位コンピュータ5、形状検出器7、および形状制御機構40が接続されている。
As shown in FIG. 6, the process computer 6 includes a control unit 20 and a storage unit 30. The control unit 20 is connected to a host computer 5, a shape detector 7, and a shape control mechanism 40 provided outside the process computer 6.
上位コンピュータ5は荷重算出部5cを備えている。本実施の形態における形状制御機構40は、中間ロールシフト機構2、中間ロールベンダー3、および差荷重発生装置4(図1参照)であるが、ここでは中間ロールシフト機構2の制御量(シフト位置)は所定値に固定することとする。
The host computer 5 includes a load calculation unit 5c. The shape control mechanism 40 in the present embodiment is the intermediate roll shift mechanism 2, the intermediate roll bender 3, and the differential load generator 4 (see FIG. 1). Here, the control amount (shift position) of the intermediate roll shift mechanism 2 is used. ) Is fixed to a predetermined value.
制御部20は、影響係数算出部21、補正目標値算出部22、変化量算出部23(算出部)、および機構制御部24を備えている。記憶部30は、所定係数データ31および制御パラメータ32を格納している。
The control unit 20 includes an influence coefficient calculation unit 21, a correction target value calculation unit 22, a change amount calculation unit 23 (calculation unit), and a mechanism control unit 24. The storage unit 30 stores predetermined coefficient data 31 and control parameters 32.
制御部20は、プロセスコンピュータ6全体の動作を制御する、例えばCPU(CentralProcessing Unit)である。制御部20が備える各部は、例えばCPUによって動作するソフトウェアとして実現されてよい。
The control unit 20 is, for example, a CPU (Central Processing Unit) that controls the operation of the entire process computer 6. Each part with which control part 20 is provided may be realized as software which operates by CPU, for example.
制御部20における、影響係数算出部21、補正目標値算出部22、変化量算出部23、および機構制御部24の詳細な説明は、プロセスコンピュータ6が実行する、形状制御機構の制御量を補正するための補正値を算出する処理の流れの一例の説明と合わせて後述する。
The detailed description of the influence coefficient calculation unit 21, the correction target value calculation unit 22, the change amount calculation unit 23, and the mechanism control unit 24 in the control unit 20 corrects the control amount of the shape control mechanism executed by the process computer 6. This will be described later together with an example of the flow of processing for calculating a correction value to be performed.
記憶部30は、制御部20において用いられる各種データを記憶する不揮発性の記憶装置(例えばハードディスク、フラッシュメモリ等)である。
The storage unit 30 is a non-volatile storage device (for example, hard disk, flash memory, etc.) that stores various data used in the control unit 20.
所定係数データ31は、前記式(3)および(4)が含む各近似式係数を示すデータであり、上述したようにして予め求めた近似式係数のデータである。所定係数データ31は、上位コンピュータ5に入力された圧延条件に対応した近似式係数を影響係数算出部21が選択することができるように予め用意されていればよい。或いは、近似式係数は、6段圧延機1による圧延を開始する少し前に算出されてもよい。
The predetermined coefficient data 31 is data indicating each approximate expression coefficient included in the expressions (3) and (4), and is data of the approximate expression coefficient obtained in advance as described above. The predetermined coefficient data 31 may be prepared in advance so that the influence coefficient calculation unit 21 can select an approximate expression coefficient corresponding to the rolling condition input to the host computer 5. Alternatively, the approximate equation coefficient may be calculated shortly before the rolling by the six-high rolling mill 1 is started.
近似式係数は、例えば、上位コンピュータ5を用いて予め求められる。この場合、上位コンピュータ5は、近似式係数算出部としての機能を有する。なお、近似式係数は、上位コンピュータ5以外の装置を用いて予め求められてもよい。プロセスコンピュータ6が近似式係数を算出してもよい。
The approximate equation coefficient is obtained in advance using the host computer 5, for example. In this case, the host computer 5 has a function as an approximate expression coefficient calculation unit. The approximate expression coefficient may be obtained in advance using a device other than the host computer 5. The process computer 6 may calculate the approximate expression coefficient.
制御パラメータ32は、各種の圧延条件(ワークロール9の回転速度、ワークロール9の径、摩擦係数、板幅、入出側板厚、平均入出側張力、圧延材8の変形抵抗等)を含む。また、制御パラメータ32は、6段圧延機1による圧延後に目標とする圧延材8の圧延形状を規定する圧延形状目標値を含む。例えば、圧延後の圧延形状が平坦(板幅方向の各場所で伸び率差が0)であることを目標とすれば、YsおよびYNがいずれも0であることが圧延形状目標値となる。
The control parameter 32 includes various rolling conditions (the rotation speed of the work roll 9, the diameter of the work roll 9, the friction coefficient, the plate width, the input / output side plate thickness, the average input / output side tension, the deformation resistance of the rolled material 8, etc.). Further, the control parameter 32 includes a rolling shape target value that defines a rolling shape of the rolled material 8 targeted after rolling by the six-high rolling mill 1. For example, if the rolling shape after rolling the goal of which is flat (elongation difference 0 at each location in the plate width direction), it Ys and Y N is 0 both is rolled shape target value .
この制御パラメータ32は、上位コンピュータ5の入力部5bを介してユーザによって入力され、荷重算出部5cによる圧延荷重の算出にも用いられる。
The control parameter 32 is input by the user via the input unit 5b of the host computer 5, and is also used for calculating the rolling load by the load calculation unit 5c.
(処理の流れ)
上記のような本発明の一態様における演算装置としてのプロセスコンピュータ6が実行する処理の流れの一例を、図7を用いて説明する。図7は、本実施の形態のプロセスコンピュータ6が実行する処理の流れの一例を示すフローチャートである。 (Process flow)
An example of the flow of processing executed by theprocess computer 6 as the arithmetic device according to one embodiment of the present invention as described above will be described with reference to FIG. FIG. 7 is a flowchart showing an example of the flow of processing executed by the process computer 6 of this embodiment.
上記のような本発明の一態様における演算装置としてのプロセスコンピュータ6が実行する処理の流れの一例を、図7を用いて説明する。図7は、本実施の形態のプロセスコンピュータ6が実行する処理の流れの一例を示すフローチャートである。 (Process flow)
An example of the flow of processing executed by the
ここで、図7に示す処理を行う前に、上位コンピュータ5は、所定係数データ31に格納される近似式係数を予め求める。この近似式係数を求める方法については、前述したとおりであるが、簡単に説明すれば、以下のとおりである。なお、6段圧延機1が対象とする圧延材の品種(板幅、板厚、変形抵抗)の範囲は、板厚0.8mm~4.0mm、板幅850mm~1050mm、材料の変形抵抗700N/mm2~1200N/mm2の範囲であるとする。
Here, before performing the processing shown in FIG. 7, the host computer 5 obtains the approximate expression coefficient stored in the predetermined coefficient data 31 in advance. The method of obtaining the approximate expression coefficient is as described above, but briefly described as follows. Note that the types of rolled material (sheet width, sheet thickness, deformation resistance) targeted by the six-high rolling mill 1 are as follows: sheet thickness 0.8 mm to 4.0 mm, sheet width 850 mm to 1050 mm, material deformation resistance 700 N / Mm 2 to 1200 N / mm 2 .
先ず、ユーザは、入力部5bを介して制御パラメータ32を入力する。この制御パラメータ32の入力方法は特に限定されるものではない。制御パラメータ32には、少なくとも、上記した6段圧延機1が対象とする圧延材の品種が含まれる(条件範囲設定ステップ)。その他の圧延条件は、本ステップにて入力されてよく、または、予め入力されていてもよい。
First, the user inputs the control parameter 32 via the input unit 5b. The input method of the control parameter 32 is not particularly limited. The control parameter 32 includes at least the type of rolled material targeted by the above-described six-high rolling mill 1 (condition range setting step). Other rolling conditions may be input in this step, or may be input in advance.
次に、以下のようにして、単位幅荷重が算出される。すなわち、上位コンピュータ5には制御パラメータ32として圧延条件(ワークロールの回転速度、ワークロール径、摩擦係数、板幅、入出側板厚、平均入出側張力、圧延材の変形抵抗等)が入力されている。荷重算出部5cは、圧延荷重式に従って圧延荷重Pを算出し、式(6)に板幅Wを代入して単位幅荷重pを算出する。
Next, the unit width load is calculated as follows. That is, rolling conditions (work roll rotation speed, work roll diameter, friction coefficient, plate width, input / output side thickness, average input / output side tension, deformation resistance of the rolled material, etc.) are input to the host computer 5 as control parameters 32. Yes. The load calculation unit 5c calculates the rolling load P according to the rolling load formula, and calculates the unit width load p by substituting the sheet width W into the formula (6).
p=P/W (6)。
P = P / W (6).
なお、圧延荷重Pは、予め入力された圧延条件から、公知の圧延荷重式を用いて予測される荷重であり、ドライプサイドの荷重とワークサイドとの荷重の和である。
Note that the rolling load P is a load predicted by using a known rolling load equation based on previously input rolling conditions, and is the sum of the load on the dry side and the load on the work side.
予め入力された圧延条件の一部(ワークロールの回転速度、平均入出側張力など)は、圧延中に変動することがあり、それに伴って圧延荷重Pも変動し得るが、その変動の影響は小さいため考慮しないこととしている。
Some of the rolling conditions inputted in advance (work roll rotation speed, average entry / exit side tension, etc.) may fluctuate during rolling, and the rolling load P may fluctuate accordingly. It is not considered because it is small.
なお、単位幅荷重pを算出する上位コンピュータ5も本発明の演算装置であると見なしてもよい。また、上位コンピュータ5の代わりにプロセスコンピュータ6が単位幅荷重pを算出してもよい。
Note that the host computer 5 that calculates the unit width load p may also be regarded as the arithmetic device of the present invention. Further, the process computer 6 may calculate the unit width load p instead of the host computer 5.
そして、上位コンピュータ5は、形状予測の解析プログラムを用いて、或る板幅および単位幅荷重の条件において、影響係数A1および影響係数A2を算出する。この算出方法については、図2、3を用いて前述した。
The host computer 5 calculates the influence coefficient A1 and the influence coefficient A2 under the conditions of a certain plate width and unit width load by using the shape prediction analysis program. This calculation method has been described above with reference to FIGS.
上記の圧延材の品種の範囲内における、いくつかの圧延条件について、影響係数A1および影響係数A2を算出することにより、図4および図5に示したようなグラフの各プロットを算出する(プロット算出ステップ)。
Each plot of the graphs as shown in FIGS. 4 and 5 is calculated by calculating the influence coefficient A1 and the influence coefficient A2 with respect to several rolling conditions within the range of the above-mentioned rolled material varieties (plots). Calculation step).
上記いくつかの条件としては、限定されるものではないが、例えば、板幅条件を3水準変更するとともに、それぞれの板幅条件において、6つの単位幅荷重条件について影響係数を算出する。この場合、影響係数A1および影響係数A2のそれぞれについて、18個のプロットが算出され、合計36個のプロットを算出することになる(図4および図5を参照)。
Although the above-mentioned several conditions are not limited, for example, the plate width condition is changed by three levels, and the influence coefficient is calculated for six unit width load conditions in each plate width condition. In this case, 18 plots are calculated for each of the influence coefficient A1 and the influence coefficient A2, and a total of 36 plots are calculated (see FIGS. 4 and 5).
そして、算出したプロットについて、上記した式(5)も用いて重回帰分析を行うことにより、近似式係数を求めることができる。例えば、上記した表1および表2に記載の近似式係数が得られる。得られた近似式係数は、所定係数データ31に格納される。
Then, the approximate equation coefficient can be obtained by performing multiple regression analysis on the calculated plot using the above equation (5). For example, the approximate expression coefficients described in Table 1 and Table 2 are obtained. The obtained approximate expression coefficient is stored in the predetermined coefficient data 31.
以上のようにして、プロセスコンピュータ6の記憶部30には、予め求められた、例えば表1および表2に示した近似式係数a11、a12、a13および近似式係数a21、a22、a23が所定係数データ31として格納されている。この近似式係数を式(3)および式(4)に代入することにより、影響係数の近似式を設定することができる(近似式設定ステップ)。そして、プロセスコンピュータ6は、以下のように処理を実行し、形状制御機構の制御量を補正するための補正値を算出する。
As described above, the storage unit 30 of the process computer 6 stores the approximate expression coefficients a1 1 , a1 2 , a1 3 and approximate expression coefficients a2 1 , a2 2 shown in, for example, Tables 1 and 2 in advance. , A2 3 are stored as the predetermined coefficient data 31. By substituting this approximate expression coefficient into expressions (3) and (4), an approximate expression of the influence coefficient can be set (approximation expression setting step). Then, the process computer 6 executes processing as follows to calculate a correction value for correcting the control amount of the shape control mechanism.
図7に示すように、影響係数算出部21が、式(3)および式(4)を用いて、板幅W、前記算出された単位幅荷重p、および所定係数データ31を代入して、影響係数A1および影響係数A2を算出する(ステップ11;以下S11のように略記する)(影響係数算出工程、影響係数設定ステップ)。
As shown in FIG. 7, the influence coefficient calculation unit 21 substitutes the plate width W, the calculated unit width load p, and the predetermined coefficient data 31 using Expressions (3) and (4), The influence coefficient A1 and the influence coefficient A2 are calculated (step 11; hereinafter abbreviated as S11) (influence coefficient calculation step, influence coefficient setting step).
圧延中において、形状検出器7は、圧延材8の形状を検出して、当該形状を示す検出信号を補正目標値算出部22に送信する。補正目標値算出部22は、形状検出器7からの出力信号に基づいて、圧延後の圧延材8の形状と、制御パラメータ32が含む圧延形状目標値との差(補正目標値)を算出する(S12)。例えば、伸び率差YSの目標値をYS
0、形状検出器7で測定した伸び率差をYS
1とすると、補正目標値としての伸び率差の変化量ΔYSは、YS
0-YS
1となる。この変化量ΔYSは、形状制御機構40の制御量を補正する前の伸び率差と補正後の伸び率差との差に相当し、実際の伸び率差をどれだけ縮めれば目標値YS
0に一致するかを示す値である。
During rolling, the shape detector 7 detects the shape of the rolled material 8 and transmits a detection signal indicating the shape to the correction target value calculation unit 22. The correction target value calculation unit 22 calculates a difference (correction target value) between the shape of the rolled material 8 after rolling and the rolling shape target value included in the control parameter 32 based on the output signal from the shape detector 7. (S12). For example, if the target value of the elongation difference Y S is Y S 0 and the elongation difference measured by the shape detector 7 is Y S 1 , the amount of change ΔY S in the elongation difference as the corrected target value is Y S 0. -Y S 1 This change amount ΔY S corresponds to the difference between the elongation difference before correction of the control amount of the shape control mechanism 40 and the elongation difference after correction, and the target value Y should be reduced by how much the actual elongation difference is reduced. It is a value indicating whether or not S 0 is matched.
次に、変化量算出部23は、前記算出した影響係数A1と、前記補正目標値としての伸び率差YSの変化量ΔYSとに基づき、式(1)を用いて、中間ロールベンダー力Fiの変化量ΔFiを算出する(S13)(補正値算出工程)。この変化量ΔFiは、中間ロールベンダー3の補正前後のベンディング力の差に相当する。
Next, based on the calculated influence coefficient A1 and the change amount ΔY S of the elongation difference Y S as the correction target value, the change amount calculation unit 23 uses the equation (1) to calculate the intermediate roll bender force. A change amount ΔFi of Fi is calculated (S13) (correction value calculation step). This change amount ΔFi corresponds to a difference in bending force before and after the correction of the intermediate roll bender 3.
そして、変化量算出部23は、前記算出した影響係数A2と、前記補正目標値としての伸び率差YNの変化量ΔYNとに基づき、式(2)を用いて、差荷重SLの変化量ΔSLを算出する(S14)(補正値算出工程)。
Then, the change amount calculation unit 23 uses the equation (2) based on the calculated influence coefficient A2 and the change amount ΔY N of the elongation difference Y N as the correction target value to calculate the difference load SL . calculates the amount of change [Delta] S L (S14) (correction value calculating step).
このように、変化量算出部23は、圧延材8における複数箇所間の、補正による伸び率差の変化量を示す数式を用いて、形状制御機構の制御量を補正するための補正値を算出する。
In this way, the change amount calculation unit 23 calculates a correction value for correcting the control amount of the shape control mechanism, using the mathematical expression indicating the change amount of the elongation difference between the plurality of locations in the rolled material 8. To do.
その後、機構制御部24が、中間ロールベンダー力FiをΔFi、および差荷重SLをΔSL変化させて補正する。
Thereafter, the mechanism control unit 24, the intermediate roll bender force Fi .DELTA.Fi, and the difference load S L is corrected by [Delta] S L changes.
これにより、6段圧延機1による圧延後の圧延材8を、良好な圧延形状とすることができる。
Thereby, the rolled material 8 after rolling by the 6-high rolling mill 1 can be made into a good rolling shape.
以上のように、本実施形態における6段圧延機1における演算装置(プロセスコンピュータ6、または、上位コンピュータ5およびプロセスコンピュータ6)は、中間ロールベンダー3および差荷重発生装置4を制御して、圧延形状を制御するための制御値(変化量ΔFi、変化量ΔSL)を算出する算出部(変化量算出部23)を備えている。
As described above, the arithmetic device (process computer 6, or host computer 5 and process computer 6) in the six-high rolling mill 1 in the present embodiment controls the intermediate roll bender 3 and the differential load generator 4 to perform rolling. A calculation unit (change amount calculation unit 23) that calculates control values (change amount ΔFi, change amount ΔS L ) for controlling the shape is provided.
影響係数算出部21は、この制御値の算出に用いる式(1)および式(2)における影響係数A1およびA2をそれぞれ、近似式(3)および近似式(4)を用いて算出する。近似式(3)および近似式(4)における近似式係数は、以下のように求められる。
The influence coefficient calculation unit 21 calculates the influence coefficients A1 and A2 in the expressions (1) and (2) used for calculating the control value using the approximate expression (3) and the approximate expression (4), respectively. The approximate expression coefficients in the approximate expression (3) and the approximate expression (4) are obtained as follows.
ここで、圧延材8の板端部における伸び率と板幅中央における伸び率との差YSを第1伸び率差とする。また、圧延材8の、6段圧延機1のワークサイドにおける伸び率と6段圧延機1のドライブサイドにおける伸び率との差YNを第2伸び率差とする。圧延材8の単位幅に加えられる荷重を単位幅荷重とする。
Here, the difference Y S between the elongation at the plate end of the rolled material 8 and the elongation at the center of the plate width is defined as a first elongation difference. Further, the difference Y N between the elongation rate of the rolled material 8 on the work side of the six-high rolling mill 1 and the elongation rate on the drive side of the six-high rolling mill 1 is defined as a second elongation difference. A load applied to the unit width of the rolled material 8 is defined as a unit width load.
本実施形態の演算装置としての、例えば上位コンピュータ5は、6段圧延機1が圧延対象とする圧延材8の複数の品種に基づく所定の範囲内にて板厚、板幅、および材料の変形抵抗を変化させて、(A)設定した複数の圧延条件のそれぞれにおける圧延材8の単位幅荷重を算出するとともに、(B)各圧延条件における、(i)中間ロールベンダー力Fiと前記第1伸び率差との関係、および(ii)差荷重SLと前記第2伸び率差との関係を、形状予測の数値解析プログラムを用いて算出する。
For example, the high-order computer 5 serving as the arithmetic device of the present embodiment is configured such that the plate thickness, the plate width, and the material are deformed within a predetermined range based on a plurality of types of rolled material 8 to be rolled by the six-high rolling mill 1. While changing the resistance, (A) calculating the unit width load of the rolled material 8 under each of the set plurality of rolling conditions, and (B) (i) the intermediate roll bender force Fi and the first in each rolling condition. The relationship between the elongation difference and (ii) the relationship between the differential load SL and the second elongation difference is calculated using a numerical analysis program for shape prediction.
そして、上位コンピュータ5は、得られた前記関係に基づいて、前記複数の圧延条件のそれぞれにおける影響係数A1およびA2を求めることにより、前記単位幅荷重と前記影響係数A1またはA2との関係(例えば、図4および図5に示したプロット)を求め、該関係について近似式(3)および近似式(4)を用いて重回帰分析を行う。これにより、前記影響係数A1およびA2のそれぞれについて、圧延材8の所定の範囲において用いられる近似式(3)および近似式(4)の近似式係数を算出する。この近似式係数は、記憶部30に所定係数データ31として格納されてよい。
Then, the upper computer 5 obtains the influence coefficients A1 and A2 in each of the plurality of rolling conditions based on the obtained relation, thereby obtaining a relation (for example, the influence width A1 or A2). The plots shown in FIG. 4 and FIG. 5 are obtained, and multiple regression analysis is performed on the relationship using the approximate expression (3) and the approximate expression (4). Thereby, the approximate expression coefficients of approximate expression (3) and approximate expression (4) used in a predetermined range of the rolled material 8 are calculated for each of the influence coefficients A1 and A2. This approximate expression coefficient may be stored as the predetermined coefficient data 31 in the storage unit 30.
そして、影響係数算出部21は、上述のように算出した前記近似式係数を代入した近似式(3)および近似式(4)を用いて、前記圧延材の品種に応じて、前記影響係数A1およびA2をそれぞれ算出する。
Then, the influence coefficient calculation unit 21 uses the approximate expression (3) and the approximate expression (4) into which the approximate expression coefficient calculated as described above is substituted, and the influence coefficient A1 according to the type of the rolled material. And A2 are respectively calculated.
(実施例)
本実施の形態の6段圧延機1を用いて、板厚0.8mm~4.0mm、板幅850mm~1050mm、材料の変形抵抗700N/mm2~1200N/mm2の範囲で条件を変えて、50個の条件にて圧延を行った。このとき、形状制御機構40(中間ロールベンダー3および差荷重発生装置4)の影響係数A1および影響係数A2を、板幅および単位幅荷重の関数として近似して求めた。 (Example)
With 6-high mill 1 of the present embodiment, sheet thickness 0.8 mm ~ 4.0 mm, by changing the plate width 850 mm ~ 1050 mm, the condition in the range of deformation resistance 700N / mm 2 ~ 1200N / mm 2 of the material , Rolling was performed under 50 conditions. At this time, the influence coefficient A1 and the influence coefficient A2 of the shape control mechanism 40 (the intermediate roll bender 3 and the differential load generator 4) were obtained by approximation as functions of the plate width and unit width load.
本実施の形態の6段圧延機1を用いて、板厚0.8mm~4.0mm、板幅850mm~1050mm、材料の変形抵抗700N/mm2~1200N/mm2の範囲で条件を変えて、50個の条件にて圧延を行った。このとき、形状制御機構40(中間ロールベンダー3および差荷重発生装置4)の影響係数A1および影響係数A2を、板幅および単位幅荷重の関数として近似して求めた。 (Example)
With 6-
また、比較のため、形状制御機構の影響係数を板幅、板厚、材料の変形抵抗の関数として、従来の方法に基づいて近似した場合について、上記と同様の範囲で条件を変えて、50個の条件にて圧延を行った。
For comparison, when the influence coefficient of the shape control mechanism is approximated based on the conventional method as a function of the plate width, the plate thickness, and the deformation resistance of the material, the conditions are changed in the same range as above, and 50 Rolling was performed under individual conditions.
本発明の一態様により、形状制御機構40の影響係数A1およびA2を単位幅荷重と板幅との関数として近似した場合は、図8に示すように、板端部における伸び率と板幅中央における伸び率との差YSの目標値と実績値との差(ワークサイドとドライブサイドで絶対値が大きい方)の絶対値は25Iunit以内に収まっていた。
According to one aspect of the present invention, when the influence coefficients A1 and A2 of the shape control mechanism 40 are approximated as a function of the unit width load and the plate width, as shown in FIG. the absolute value of the difference between the target value and the actual value of the difference Y S of the growth rate (the one absolute value in the work side and drive side is large) in was not fit within 25Iunit.
これに対して、従来法により板幅、板厚、材料の変形抵抗の関数として近似した場合は、図9に示すように、板端部における伸び率と板幅中央における伸び率との差YSの目標値と実績値の差(ワークサイドとドライブサイドで絶対値が大きい方)の絶対値が35Iunit以上になるものもあった。
On the other hand, when approximated as a function of plate width, plate thickness, and material deformation resistance by the conventional method, as shown in FIG. 9, the difference Y between the elongation at the plate end and the elongation at the center of the plate width. In some cases, the absolute value of the difference between the target value of S and the actual value (the larger absolute value on the work side and the drive side) is 35 Units or more.
(変形例1)
前記実施形態1の6段圧延機1とは異なり、本変形例の6段圧延機は、対象とする圧延材の板幅の範囲が、板幅1050mm~1250mmの範囲である。板厚および材料の変形抵抗の範囲はそのままであるとする。 (Modification 1)
Unlike the six-high rolling mill 1 of the first embodiment, in the six-high rolling mill of this modification, the range of the plate width of the target rolled material is in the range of 1050 mm to 1250 mm. It is assumed that the range of plate thickness and material deformation resistance remains the same.
前記実施形態1の6段圧延機1とは異なり、本変形例の6段圧延機は、対象とする圧延材の板幅の範囲が、板幅1050mm~1250mmの範囲である。板厚および材料の変形抵抗の範囲はそのままであるとする。 (Modification 1)
Unlike the six-
本変形例における近似式係数の算出について、図10および図11に基づいて説明すれば、以下のとおりである。図10は、本変形例における中間ロールベンダー力Fiの影響係数A1に及ぼす、単位幅荷重pおよび板幅Wの影響を示すグラフである。図11は、本変形例における差荷重SLの影響係数A2に及ぼす、単位幅荷重pおよび板幅Wの影響を示すグラフである。
The calculation of the approximate expression coefficient in this modification will be described below with reference to FIGS. 10 and 11. FIG. 10 is a graph showing the influence of the unit width load p and the plate width W on the influence coefficient A1 of the intermediate roll bender force Fi in the present modification. 11, on the influence coefficient A2 of the difference load S L in this modification is a graph showing the effect of a unit width load p and plate width W.
前記実施形態1にて説明したことと同様にして、形状予測の解析プログラムを用いて、板厚、板幅、および材料の変形抵抗を上記の範囲で変化させて解析を行い、それぞれの条件で影響係数A1を算出した。結果を図10に示す。
In the same manner as described in the first embodiment, analysis is performed by changing the plate thickness, the plate width, and the deformation resistance of the material within the above ranges using the shape prediction analysis program. The influence coefficient A1 was calculated. The results are shown in FIG.
図10に示すデータについて、前記式(3)を用いて重回帰分析を行った結果、近似式における各近似式係数は表4に示すようになり、高い相関関係が得られた。
As a result of performing multiple regression analysis on the data shown in FIG. 10 using the formula (3), the approximate formula coefficients in the approximate formula are as shown in Table 4, and a high correlation was obtained.
また、前記実施形態1にて説明したことと同様にして、形状予測の解析プログラムを用いて、板厚、板幅、および材料の変形抵抗を上記の範囲で変化させて解析を行い、それぞれの条件で影響係数A2を算出した。結果を図11に示す。
Further, in the same manner as described in the first embodiment, analysis is performed by changing the plate thickness, the plate width, and the deformation resistance of the material in the above ranges using the analysis program for shape prediction. The influence coefficient A2 was calculated under the conditions. The results are shown in FIG.
図11に示すデータについて、前記式(4)を用いて重回帰分析を行った結果、近似式における各近似式係数は表5に示すようになり、高い相関関係が得られた。
As a result of performing multiple regression analysis on the data shown in FIG. 11 using the equation (4), the approximate equation coefficients in the approximate equation are as shown in Table 5, and a high correlation was obtained.
このように、本変形例の6段圧延機の操業条件において、表4および表5に示す近似式係数を代入して、前記式(3)および式(4)で表される近似式を用いることにより、或る単位幅荷重pおよび板幅Wにおける影響係数A1および影響係数A2を高精度に近似して求めることができる。
Thus, in the operating conditions of the six-high rolling mill of the present modification, the approximate formula coefficients shown in Tables 4 and 5 are substituted, and the approximate formulas expressed by the formulas (3) and (4) are used. Thus, the influence coefficient A1 and the influence coefficient A2 in a certain unit width load p and the plate width W can be obtained by approximating with high accuracy.
そして、求めた影響係数A1および影響係数A2を用いて、前記式(1)および(2)に基づいて、中間ロールベンダー力Fiおよび差荷重SLの制御量を制御することにより、形状制御を高精度に行うことができ、良好な圧延形状を得ることができる。
Then, using the influence coefficients A1 and influence coefficient A2 obtained, on the basis of the equation (1) and (2), by controlling the control amount of the intermediate roll bender forces Fi and difference load S L, the shape control It can be performed with high accuracy and a good rolling shape can be obtained.
(変形例2)
前記変形例1の6段圧延機とは異なり、本変形例の6段圧延機は、対象とする圧延材の板幅の範囲が、板幅600mm~850mmの範囲である。板厚および材料の変形抵抗の範囲はそのままであるとする。 (Modification 2)
Unlike the six-high rolling mill of the first modification, in the six-high rolling mill of this modification, the range of the plate width of the target rolled material is in the range of a plate width of 600 mm to 850 mm. It is assumed that the range of plate thickness and material deformation resistance remains the same.
前記変形例1の6段圧延機とは異なり、本変形例の6段圧延機は、対象とする圧延材の板幅の範囲が、板幅600mm~850mmの範囲である。板厚および材料の変形抵抗の範囲はそのままであるとする。 (Modification 2)
Unlike the six-high rolling mill of the first modification, in the six-high rolling mill of this modification, the range of the plate width of the target rolled material is in the range of a plate width of 600 mm to 850 mm. It is assumed that the range of plate thickness and material deformation resistance remains the same.
本変形例における近似式係数の算出について、図12および図13に基づいて説明すれば、以下のとおりである。図12は、本変形例における中間ロールベンダー力Fiの影響係数A1に及ぼす、単位幅荷重pおよび板幅Wの影響を示すグラフである。図13は、本変形例における差荷重SLの影響係数A2に及ぼす、単位幅荷重pおよび板幅Wの影響を示すグラフである。
The calculation of the approximate expression coefficient in this modification will be described as follows based on FIGS. 12 and 13. FIG. 12 is a graph showing the influence of the unit width load p and the plate width W on the influence coefficient A1 of the intermediate roll bender force Fi in the present modification. 13, on the influence coefficient A2 of the difference load S L in this modification is a graph showing the effect of a unit width load p and plate width W.
前記実施形態1にて説明したことと同様にして、形状予測の解析プログラムを用いて、板厚、板幅、および材料の変形抵抗を上記の範囲で変化させて解析を行い、それぞれの条件で影響係数A1を算出した。結果を図12に示す。
In the same manner as described in the first embodiment, analysis is performed by changing the plate thickness, the plate width, and the deformation resistance of the material within the above ranges using the shape prediction analysis program. The influence coefficient A1 was calculated. The results are shown in FIG.
図12に示すデータについて、前記式(3)を用いて重回帰分析を行った結果、近似式における各近似式係数は表6に示すようになり、高い相関関係が得られた。
As a result of performing multiple regression analysis on the data shown in FIG. 12 using the above equation (3), each approximate equation coefficient in the approximate equation is as shown in Table 6, and a high correlation was obtained.
また、前記実施形態1にて説明したことと同様にして、形状予測の解析プログラムを用いて、板厚、板幅、および材料の変形抵抗を上記の範囲で変化させて解析を行い、それぞれの条件で影響係数A2を算出した。結果を図13に示す。
Further, in the same manner as described in the first embodiment, analysis is performed by changing the plate thickness, the plate width, and the deformation resistance of the material in the above ranges using the analysis program for shape prediction. The influence coefficient A2 was calculated under the conditions. The results are shown in FIG.
図13に示すデータについて、前記式(4)を用いて重回帰分析を行った結果、近似式における各近似式係数は表7に示すようになり、高い相関関係が得られた。
As a result of performing multiple regression analysis on the data shown in FIG. 13 using the equation (4), the approximate equation coefficients in the approximate equation are as shown in Table 7, and a high correlation was obtained.
このように、本変形例の6段圧延機の操業条件において、表6および表7に示す近似式係数を代入して、前記式(3)および式(4)で表される近似式を用いることにより、或る単位幅荷重pおよび板幅Wにおける影響係数A1および影響係数A2を高精度に近似して求めることができる。
Thus, in the operating conditions of the six-high rolling mill of this modification, the approximate formula coefficients shown in Table 6 and Table 7 are substituted, and the approximate formulas expressed by the formulas (3) and (4) are used. Thus, the influence coefficient A1 and the influence coefficient A2 in a certain unit width load p and the plate width W can be obtained by approximating with high accuracy.
そして、求めた影響係数A1および影響係数A2を用いて、前記式(1)および(2)に基づいて、中間ロールベンダー力Fiおよび差荷重SLの制御量を制御することにより、形状制御を高精度に行うことができ、良好な圧延形状を得ることができる。
Then, using the influence coefficients A1 and influence coefficient A2 obtained, on the basis of the equation (1) and (2), by controlling the control amount of the intermediate roll bender forces Fi and difference load S L, the shape control It can be performed with high accuracy and a good rolling shape can be obtained.
〔実施形態2〕
以下、本発明の他の実施形態について説明する。なお、本実施の形態において説明すること以外の構成は、前記実施形態1と同じである。また、説明の便宜上、前記実施形態1の図面に示した部材と同一の機能を有する部材については、同一の符号を付し、その説明を省略する。 [Embodiment 2]
Hereinafter, other embodiments of the present invention will be described. Configurations other than those described in the present embodiment are the same as those in the first embodiment. For convenience of explanation, members having the same functions as those shown in the drawings ofEmbodiment 1 are given the same reference numerals, and descriptions thereof are omitted.
以下、本発明の他の実施形態について説明する。なお、本実施の形態において説明すること以外の構成は、前記実施形態1と同じである。また、説明の便宜上、前記実施形態1の図面に示した部材と同一の機能を有する部材については、同一の符号を付し、その説明を省略する。 [Embodiment 2]
Hereinafter, other embodiments of the present invention will be described. Configurations other than those described in the present embodiment are the same as those in the first embodiment. For convenience of explanation, members having the same functions as those shown in the drawings of
前記実施の形態1の6段圧延機1では、中間ロールシフト機構2の制御量(シフト位置)を所定値に固定し、中間ロールベンダー3および差荷重発生装置4を制御対象としていた。また、式(1)および(2)として、板端部における伸び率と板幅中央における伸び率との差(ワークサイドおよびドライブサイドの平均)である伸び率差の変化量ΔYS、および、ワークサイドの伸び率とドライブサイドの伸び率との差である伸び率差の変化量ΔYNを用いて圧延形状を評価していた。これに対して、本実施の形態の演算装置では、圧延中に用いる形状制御機構として、中間ロールシフト機構2および中間ロールベンダー3を用いると共に、圧延形状の評価に板端部だけでなくクオータ部(中間部)も考慮する点が異なっている。以下の説明においては、形状制御機構としての差荷重発生装置4については、稼働させない、または制御量(発生させる差荷重)が所定の値に固定されている。なお、6段圧延機1を実際に動作させる場合には、差荷重発生装置4が制御されてもよい。
In the six-high rolling mill 1 of the first embodiment, the control amount (shift position) of the intermediate roll shift mechanism 2 is fixed to a predetermined value, and the intermediate roll bender 3 and the differential load generator 4 are controlled. Further, as equations (1) and (2), the change amount ΔY S of the difference in elongation, which is the difference between the elongation at the plate edge and the elongation at the center of the plate width (average of the work side and drive side), and It was evaluated rolled shape using a variation [Delta] Y N of elongation being the difference between the elongation of the work side and drive side elongation. On the other hand, in the arithmetic unit according to the present embodiment, the intermediate roll shift mechanism 2 and the intermediate roll bender 3 are used as the shape control mechanism used during rolling, and not only the plate end portion but also the quarter portion are used for evaluating the rolling shape. (Intermediate part) is also different. In the following description, the differential load generator 4 as the shape control mechanism is not operated or the control amount (differential load to be generated) is fixed to a predetermined value. In addition, when actually operating the 6-high rolling mill 1, the differential load generator 4 may be controlled.
本実施の形態の演算装置では、圧延形状の評価にクオータ部を考慮して演算を行い、中間ロールシフト機構2および中間ロールベンダー3の制御値の変化量を算出する。ここで、前記クオータ部とは、圧延材8の板幅方向において、板幅中央部と板端部との間に位置する部分である。クオータ部の位置は、板幅中央部と板端部との間において特に限定されないが、例えば、板幅中央部から板端部までの距離の70%の位置とすることができる。クオータ部としては、ワークサイドのクオータ部と、ドライブサイドのクオータ部とがある。
In the arithmetic device of the present embodiment, the rolling shape is evaluated in consideration of the quota part, and the amount of change in the control values of the intermediate roll shift mechanism 2 and the intermediate roll bender 3 is calculated. Here, the quarter portion is a portion located between the plate width center portion and the plate end portion in the plate width direction of the rolled material 8. The position of the quarter portion is not particularly limited between the center portion of the plate width and the end portion of the plate, but can be, for example, 70% of the distance from the center portion of the plate width to the end portion of the plate. The quota section includes a work side quota section and a drive side quota section.
クオータ部を考慮する場合には、2点の板端部(ワークサイドおよびドライブサイド)並びに2点のクオータ部(ワークサイドおよびドライブサイド)のそれぞれの伸び率と、板幅中央の伸び率との差で圧延形状を評価すればよい。
When considering the quota part, the elongation of each of the two plate end parts (work side and drive side) and the two quarter parts (work side and drive side) and the elongation percentage at the center of the plate width What is necessary is just to evaluate a rolling shape by a difference.
具体的には、本実施の形態では、圧延材の圧延形状を制御する式として、下記の式(7)、(8)に示す制御式を用いることができる。
Specifically, in this embodiment, the following control formulas (7) and (8) can be used as formulas for controlling the rolling shape of the rolled material.
Δεe=Ae・ΔFi + Be・Δδ (7)
Δεq=Aq・ΔFi + Bq・Δδ (8)
上記式において、
εe:板端部における伸び率と板幅中央における伸び率との差(ワークサイドおよびドライブサイドの平均)
εq:クオータ部における伸び率と板幅中央における伸び率との差(ワークサイドおよびドライブサイドの平均)
Fi:中間ロールベンダー力
δ:中間ロールシフト位置
Δεe:板端部における伸び率と板幅中央における伸び率との差の変化量(ワークサイドおよびドライブサイドの平均)
Δεq:クオータ部における伸び率と板幅中央における伸び率との差の変化量(ワークサイドおよびドライブサイドの平均)
ΔFi:中間ロールベンダー力Fiの変化量
Δδ:中間ロールシフト位置δの変化量
Ae:板端部における伸び率と板幅中央における伸び率との差に及ぼす中間ロールベンダー力Fiの影響係数
Be:板端部における伸び率と板幅中央における伸び率との差に及ぼす中間ロールシフト位置δの影響係数
Aq:クオータ部における伸び率と板幅中央における伸び率との差に及ぼす中間ロールベンダー力Fiの影響係数
Bq:クオータ部における伸び率と板幅中央における伸び率との差に及ぼす中間ロールシフト位置δの影響係数
である。 Δεe = Ae · ΔFi + Be · Δδ (7)
Δεq = Aq · ΔFi + Bq · Δδ (8)
In the above formula,
εe: difference between the elongation at the edge of the plate and the elongation at the center of the plate width (average of work side and drive side)
εq: difference between the elongation at the quarter and the elongation at the center of the sheet width (average of work side and drive side)
Fi: Intermediate roll bender power
δ: Intermediate roll shift position Δεe: Amount of change in the difference between the elongation at the end of the plate and the elongation at the center of the plate width (average of work side and drive side)
Δεq: Change in the difference between the elongation at the quarter and the elongation at the center of the plate width (average of work side and drive side)
ΔFi: Change amount of the intermediate roll bender force Fi Δδ: Change amount of the intermediate roll shift position δ Ae: Influence coefficient of the intermediate roll bender force Fi on the difference between the elongation rate at the plate end and the elongation rate at the center of the plate width Be: Influence coefficient of the intermediate roll shift position δ on the difference between the elongation at the plate end and the elongation at the center of the sheet width Aq: Intermediate roll bender force Fi affecting the difference between the elongation at the quarter and the elongation at the center of the sheet width Bq: Influence coefficient of the intermediate roll shift position δ on the difference between the elongation at the quarter and the elongation at the center of the plate width.
Δεq=Aq・ΔFi + Bq・Δδ (8)
上記式において、
εe:板端部における伸び率と板幅中央における伸び率との差(ワークサイドおよびドライブサイドの平均)
εq:クオータ部における伸び率と板幅中央における伸び率との差(ワークサイドおよびドライブサイドの平均)
Fi:中間ロールベンダー力
δ:中間ロールシフト位置
Δεe:板端部における伸び率と板幅中央における伸び率との差の変化量(ワークサイドおよびドライブサイドの平均)
Δεq:クオータ部における伸び率と板幅中央における伸び率との差の変化量(ワークサイドおよびドライブサイドの平均)
ΔFi:中間ロールベンダー力Fiの変化量
Δδ:中間ロールシフト位置δの変化量
Ae:板端部における伸び率と板幅中央における伸び率との差に及ぼす中間ロールベンダー力Fiの影響係数
Be:板端部における伸び率と板幅中央における伸び率との差に及ぼす中間ロールシフト位置δの影響係数
Aq:クオータ部における伸び率と板幅中央における伸び率との差に及ぼす中間ロールベンダー力Fiの影響係数
Bq:クオータ部における伸び率と板幅中央における伸び率との差に及ぼす中間ロールシフト位置δの影響係数
である。 Δεe = Ae · ΔFi + Be · Δδ (7)
Δεq = Aq · ΔFi + Bq · Δδ (8)
In the above formula,
εe: difference between the elongation at the edge of the plate and the elongation at the center of the plate width (average of work side and drive side)
εq: difference between the elongation at the quarter and the elongation at the center of the sheet width (average of work side and drive side)
Fi: Intermediate roll bender power
δ: Intermediate roll shift position Δεe: Amount of change in the difference between the elongation at the end of the plate and the elongation at the center of the plate width (average of work side and drive side)
Δεq: Change in the difference between the elongation at the quarter and the elongation at the center of the plate width (average of work side and drive side)
ΔFi: Change amount of the intermediate roll bender force Fi Δδ: Change amount of the intermediate roll shift position δ Ae: Influence coefficient of the intermediate roll bender force Fi on the difference between the elongation rate at the plate end and the elongation rate at the center of the plate width Be: Influence coefficient of the intermediate roll shift position δ on the difference between the elongation at the plate end and the elongation at the center of the sheet width Aq: Intermediate roll bender force Fi affecting the difference between the elongation at the quarter and the elongation at the center of the sheet width Bq: Influence coefficient of the intermediate roll shift position δ on the difference between the elongation at the quarter and the elongation at the center of the plate width.
以下では、式(7)を板端部に関する制御式、式(8)をクオータ部に関する制御式と称することがある。
Hereinafter, Equation (7) may be referred to as a control equation relating to the plate end portion, and Equation (8) may be referred to as a control equation relating to the quota portion.
影響係数Ae、Aq、Be、Bqは、上述した式(5)と本質的に同じ式(9)、(10)によって表現することができる。
The influence coefficients Ae, Aq, Be, and Bq can be expressed by expressions (9) and (10) that are essentially the same as the above-described expression (5).
A=a1・(1/p)+a2・(W/p)+a3 (9)
B=b1・(1/p)+b2・(W/p)+b3 (10)
p:単位幅荷重
W:板幅
a1、a2、a3:影響係数の近似式における近似式係数
b1、b2、b3:影響係数の近似式における近似式係数
以下に、前記式(7)、(8)に基づく、本実施の形態の演算装置が実行する処理および圧延形状の制御について概略的に説明する。 A = a 1 · (1 / p) + a 2 · (W / p) + a 3 (9)
B = b 1 · (1 / p) + b 2 · (W / p) + b 3 (10)
p: Unit width load W: Plate width a 1 , a 2 , a 3 : Approximate expression coefficient in the approximate expression of the influence coefficient b 1 , b 2 , b 3 : Approximate expression coefficient in the approximate expression of the influence coefficient The processing executed by the arithmetic device according to the present embodiment and the control of the rolling shape based on (7) and (8) will be schematically described.
B=b1・(1/p)+b2・(W/p)+b3 (10)
p:単位幅荷重
W:板幅
a1、a2、a3:影響係数の近似式における近似式係数
b1、b2、b3:影響係数の近似式における近似式係数
以下に、前記式(7)、(8)に基づく、本実施の形態の演算装置が実行する処理および圧延形状の制御について概略的に説明する。 A = a 1 · (1 / p) + a 2 · (W / p) + a 3 (9)
B = b 1 · (1 / p) + b 2 · (W / p) + b 3 (10)
p: Unit width load W: Plate width a 1 , a 2 , a 3 : Approximate expression coefficient in the approximate expression of the influence coefficient b 1 , b 2 , b 3 : Approximate expression coefficient in the approximate expression of the influence coefficient The processing executed by the arithmetic device according to the present embodiment and the control of the rolling shape based on (7) and (8) will be schematically described.
前記実施の形態1と同様にして、形状予測の解析プログラム(形状解析モデル)を用いて、板厚、板幅、および材料の変形抵抗を広範囲に変化させて解析を行い、それぞれの条件で影響係数Aおよび影響係数B(形状制御機構を変化させて解析したときの、形状制御機構の制御量と伸び率差との線形関係における傾き)を算出する。具体的には、以下のとおりである。
In the same manner as in the first embodiment, using a shape prediction analysis program (shape analysis model), analysis is performed by changing the thickness, width, and deformation resistance of the material over a wide range. Coefficient A and influence coefficient B (inclination in the linear relationship between the control amount of the shape control mechanism and the difference in elongation when the shape control mechanism is changed) are calculated. Specifically, it is as follows.
伸び率差εeについて、それぞれの条件で中間ロールベンダー力Fiを変化させたときに、図示しないが、前述した図2に類似する線形関係を示すグラフが得られ、傾きとしてそれぞれの条件に対応した影響係数Aeが求まる。これにより、具体的には後述するが(図14参照)、前述した図4に類似するグラフが得られ、板幅Wと単位幅荷重pとが、影響係数Aeに及ぼす影響について整理できる。
Regarding the elongation difference εe, when the intermediate roll bender force Fi is changed under each condition, a graph showing a linear relationship similar to FIG. 2 described above is obtained, and the slope corresponds to each condition as shown in FIG. The influence coefficient Ae is obtained. Thereby, although specifically described later (see FIG. 14), a graph similar to FIG. 4 described above is obtained, and the influence of the plate width W and the unit width load p on the influence coefficient Ae can be organized.
その結果、前記実施の形態1と同様にして、影響係数Aeの近似式における近似式係数(ae1、ae2、ae3)を得ることができる。
As a result, similar to the first embodiment, approximate expression coefficients (ae 1 , ae 2 , ae 3 ) in the approximate expression of the influence coefficient Ae can be obtained.
また、伸び率差εeについて、それぞれの条件で中間ロールシフト位置δを変化させたときに、図示しないが、図3に類似する線形関係を示すグラフが得られ、傾きとして影響係数Beが求まる。そして、上記のことと同様に、影響係数Beの近似式における近似式係数(be1、be2、be3)を得ることができる。
Further, regarding the elongation difference εe, when the intermediate roll shift position δ is changed under each condition, a graph showing a linear relationship similar to FIG. 3 is obtained although not shown, and the influence coefficient Be is obtained as the slope. Then, similar to the above, approximate expression coefficients (be 1 , be 2 , be 3 ) in the approximate expression of the influence coefficient Be can be obtained.
伸び率差εq(第3伸び率差)についても同様にして、影響係数Aqの近似式における近似式係数(aq1、aq2、aq3)、および影響係数Bqの近似式における近似式係数(bq1、bq2、bq3)を得ることができる。
Similarly for the elongation difference εq (third elongation difference), the approximate expression coefficients (aq 1 , aq 2 , aq 3 ) in the approximate expression of the influence coefficient Aq, and the approximate expression coefficient ( bq 1 , bq 2 , bq 3 ) can be obtained.
所定の操業条件における一例について、以下に説明する。ここでは、次の3条件(条件A~C)の圧延材の板幅の範囲をそれぞれ対象とする3種類の6段圧延機について考えることとする。条件Aは板幅1050mm~1250mmの範囲、条件Bは板幅850mm~1050mmの範囲、条件Cは板幅600mm~850mmの範囲である。条件A~Cはそれぞれ、板厚および材料の変形抵抗の範囲は同じであるとする。
An example of the predetermined operating conditions will be described below. Here, three types of six-high rolling mills each considering the range of the sheet width of the rolled material under the following three conditions (conditions A to C) are considered. Condition A is a range of plate widths from 1050 mm to 1250 mm, Condition B is a range of plate widths from 850 mm to 1050 mm, and Condition C is a range of plate widths from 600 mm to 850 mm. Conditions A to C are assumed to have the same thickness range and the same range of material deformation resistance.
(板端部に関する制御式について)
図14の(a)~(c)はそれぞれ、条件A~Cにおける、中間ロールベンダー力Fiの影響係数Aeに及ぼす単位幅荷重pおよび板幅Wの影響を示すグラフである。 (About the control formula for the plate edge)
14A to 14C are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Ae of the intermediate roll bender force Fi under the conditions A to C, respectively.
図14の(a)~(c)はそれぞれ、条件A~Cにおける、中間ロールベンダー力Fiの影響係数Aeに及ぼす単位幅荷重pおよび板幅Wの影響を示すグラフである。 (About the control formula for the plate edge)
14A to 14C are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Ae of the intermediate roll bender force Fi under the conditions A to C, respectively.
図14の(a)~(c)に示すデータについて、下記式(11)を用いて重回帰分析を行った結果、近似式における各近似式係数は表8に示すようになり、高い相関関係が得られた。
As a result of performing multiple regression analysis on the data shown in (a) to (c) of FIG. 14 using the following formula (11), the approximate formula coefficients in the approximate formula are as shown in Table 8, and high correlation was gotten.
Ae=ae1・(1/p)+ae2・(W/p)+ae3 (11)
Ae = ae 1 · (1 / p) + ae 2 · (W / p) + ae 3 (11)
また、図15の(a)~(c)はそれぞれ、条件A~Cにおける、中間ロールシフト位置δの影響係数Beに及ぼす単位幅荷重pおよび板幅Wの影響を示すグラフである。
15A to 15C are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Be of the intermediate roll shift position δ under the conditions A to C, respectively.
図15の(a)~(c)に示すデータについて、下記式(12)を用いて重回帰分析を行った結果、近似式における各近似式係数は表9に示すようになり、高い相関関係が得られた。
As a result of performing multiple regression analysis on the data shown in (a) to (c) of FIG. 15 using the following equation (12), the approximate equation coefficients in the approximate equation are as shown in Table 9, and the correlation is high. was gotten.
Be=be1・(1/p)+be2・(W/p)+be3 (12)
Be = be 1 · (1 / p) + be 2 · (W / p) + be 3 (12)
(クオータ部に関する制御式について)
そして、図16の(a)~(c)はそれぞれ、条件A~Cにおける、中間ロールベンダー力Fiの影響係数Aqに及ぼす単位幅荷重pおよび板幅Wの影響を示すグラフである。 (About the control formula for the quota section)
FIGS. 16A to 16C are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Aq of the intermediate roll bender force Fi under the conditions A to C, respectively.
そして、図16の(a)~(c)はそれぞれ、条件A~Cにおける、中間ロールベンダー力Fiの影響係数Aqに及ぼす単位幅荷重pおよび板幅Wの影響を示すグラフである。 (About the control formula for the quota section)
FIGS. 16A to 16C are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Aq of the intermediate roll bender force Fi under the conditions A to C, respectively.
図16の(a)~(c)に示すデータについて、下記式(13)を用いて重回帰分析を行った結果、近似式における各近似式係数は表10に示すようになり、高い相関関係が得られた。
As a result of performing multiple regression analysis on the data shown in (a) to (c) of FIG. 16 using the following formula (13), the approximate formula coefficients in the approximate formula are as shown in Table 10, and the correlation is high. was gotten.
Aq=aq1・(1/p)+aq2・(W/p)+aq3 (13)
Aq = aq 1 · (1 / p) + aq 2 · (W / p) + aq 3 (13)
また、図17の(a)~(c)はそれぞれ、条件A~Cにおける、中間ロールシフト位置δの影響係数Bqに及ぼす単位幅荷重pおよび板幅Wの影響を示すグラフである。
FIGS. 17A to 17C are graphs showing the influence of the unit width load p and the plate width W on the influence coefficient Bq of the intermediate roll shift position δ under the conditions A to C, respectively.
図17の(a)~(c)に示すデータについて、下記式(14)を用いて重回帰分析を行った結果、近似式における各近似式係数は表11に示すようになり、高い相関関係が得られた。
As a result of performing multiple regression analysis on the data shown in (a) to (c) of FIG. 17 using the following equation (14), the approximate equation coefficients in the approximate equation are as shown in Table 11 and have a high correlation. was gotten.
Bq=bq1・(1/p)+bq2・(W/p)+bq3 (14)
Bq = bq 1 · (1 / p) + bq 2 · (W / p) + bq 3 (14)
以上のように、或る圧延ラインにおいて、圧延機の操業条件に応じて、近似式係数を予め求めることができる。
As described above, in a certain rolling line, the approximate expression coefficient can be obtained in advance according to the operating conditions of the rolling mill.
(処理の流れ)
影響係数算出部21は、上述のようにして得られた近似式係数を式(9)または式(10)に代入し、或る単位幅荷重pおよび板幅Wにおける影響係数Ae、Aq、Be、Bqを算出する(影響係数算出工程)。 (Process flow)
The influencecoefficient calculation unit 21 substitutes the approximate expression coefficient obtained as described above into Expression (9) or Expression (10), and affects the influence coefficients Ae, Aq, Be for a certain unit width load p and plate width W. , Bq is calculated (influence coefficient calculation step).
影響係数算出部21は、上述のようにして得られた近似式係数を式(9)または式(10)に代入し、或る単位幅荷重pおよび板幅Wにおける影響係数Ae、Aq、Be、Bqを算出する(影響係数算出工程)。 (Process flow)
The influence
また、圧延中において、形状検出器7が、圧延材8の形状を検出して、当該形状を示す検出信号を補正目標値算出部22に送信する。補正目標値算出部22は、形状検出器7からの出力信号に基づいて、圧延後の圧延材8の形状を示す値と、制御パラメータ32が含む圧延形状目標値との差(補正目標値)を算出する。これにより補正目標値としての伸び率差の変化量ΔεeおよびΔεqが得られる。
Further, during rolling, the shape detector 7 detects the shape of the rolled material 8 and transmits a detection signal indicating the shape to the corrected target value calculation unit 22. Based on the output signal from the shape detector 7, the correction target value calculation unit 22 is the difference between the value indicating the shape of the rolled material 8 after rolling and the rolling shape target value included in the control parameter 32 (correction target value). Is calculated. As a result, the change amounts Δεe and Δεq of the elongation difference as correction target values are obtained.
そして、変化量算出部23(図6参照)が、前記式(7)、(8)に影響係数Ae、Aq、Be、Bq、並びに、伸び率差の変化量ΔεeおよびΔεqを代入して、中間ロールベンダー力Fiおよび中間ロールシフト位置δについて連立方程式を解くことにより、中間ロールベンダー力Fiの変化量ΔFiおよび中間ロールシフト位置δの変化量Δδを算出する(補正値算出工程)。
Then, the change amount calculation unit 23 (see FIG. 6) substitutes the influence coefficients Ae, Aq, Be, Bq and the change amounts Δεe and Δεq of the difference in elongation rate into the equations (7) and (8), By solving the simultaneous equations for the intermediate roll bender force Fi and the intermediate roll shift position δ, the change amount ΔFi of the intermediate roll bender force Fi and the change amount Δδ of the intermediate roll shift position δ are calculated (correction value calculation step).
その後、機構制御部24(図6参照)が、中間ロールベンダー力FiをΔFi、および中間ロールシフト位置δをΔδ変化させて補正する。
Thereafter, the mechanism control unit 24 (see FIG. 6) corrects the intermediate roll bender force Fi by changing ΔFi and the intermediate roll shift position δ by Δδ.
これにより、6段圧延機1による圧延後の圧延材8を、良好な圧延形状とすることができる。
Thereby, the rolled material 8 after rolling by the 6-high rolling mill 1 can be made into a good rolling shape.
以上のように、本実施形態における6段圧延機1における演算装置(プロセスコンピュータ6、または、上位コンピュータ5およびプロセスコンピュータ6)は、中間ロールシフト機構2および中間ロールベンダー3を制御して、圧延形状を制御するための制御値(変化量Δεe、変化量Δεq)を算出する算出部(変化量算出部23)を備えている。
As described above, the arithmetic unit (process computer 6, or host computer 5 and process computer 6) in the six-high rolling mill 1 in the present embodiment controls the intermediate roll shift mechanism 2 and the intermediate roll bender 3 to perform rolling. A calculation unit (change amount calculation unit 23) that calculates control values (change amount Δεe, change amount Δεq) for controlling the shape is provided.
影響係数算出部21は、この制御値の算出に用いる式(7)および式(8)における影響係数Ae、Be、Aq、およびBqをそれぞれ、近似式(11)~(14)を用いて算出する。近似式(11)~(14)における近似式係数は、以下のように求められる。
The influence coefficient calculation unit 21 calculates the influence coefficients Ae, Be, Aq, and Bq in the equations (7) and (8) used for calculating the control value using approximate equations (11) to (14), respectively. To do. The approximate equation coefficients in the approximate equations (11) to (14) are obtained as follows.
ここで、圧延材8の板端部における伸び率と板幅中央における伸び率との差εeを第1伸び率差とする。また、圧延材8のクオータ部における伸び率と板幅中央における伸び率との差εqを第3伸び率差とする。圧延材8の単位幅に加えられる荷重を単位幅荷重とする。
Here, the difference εe between the elongation at the plate end of the rolled material 8 and the elongation at the center of the plate width is defined as a first elongation difference. Further, the difference εq between the elongation at the quarter portion of the rolled material 8 and the elongation at the center of the sheet width is defined as a third elongation difference. A load applied to the unit width of the rolled material 8 is defined as a unit width load.
本実施形態の演算装置としての、例えば上位コンピュータ5は、6段圧延機1が圧延対象とする圧延材8の複数の品種に基づく所定の範囲内にて板厚、板幅、および材料の変形抵抗を変化させて、(A)設定した複数の圧延条件のそれぞれにおける圧延材8の単位幅荷重を算出するとともに、(B)各圧延条件における、(i)中間ロールベンダー力Fiと前記第1伸び率差との関係、(ii)中間ロールシフト位置δと前記第1伸び率差との関係、(iii)中間ロールベンダー力Fiと前記第3伸び率差との関係、および(iv)中間ロールシフト位置δと前記第3伸び率差との関係を、形状予測の数値解析プログラムを用いて算出する。
For example, the high-order computer 5 serving as the arithmetic device of the present embodiment is configured such that the plate thickness, the plate width, and the material are deformed within a predetermined range based on a plurality of types of rolled material 8 to be rolled by the six-high rolling mill 1. While changing the resistance, (A) calculating the unit width load of the rolled material 8 under each of the set plurality of rolling conditions, and (B) (i) the intermediate roll bender force Fi and the first in each rolling condition. Relationship between elongation difference, (ii) Relationship between intermediate roll shift position δ and first elongation difference, (iii) Relationship between intermediate roll bender force Fi and third elongation difference, and (iv) Intermediate The relationship between the roll shift position δ and the third elongation difference is calculated using a numerical analysis program for shape prediction.
そして、上位コンピュータ5は、得られた前記関係に基づいて、前記複数の圧延条件のそれぞれにおける影響係数Ae、Be、Aq、およびBqを求めることにより、前記単位幅荷重と前記影響係数Ae、Be、Aq、またはBqとの関係(例えば、図14~図17に示したプロット)をそれぞれ求め、該関係について近似式(11)~(14)を用いて重回帰分析を行う。これにより、前記影響係数Ae、Be、Aq、およびBqのそれぞれについて、圧延材8の所定の範囲において用いられる近似式(11)~(14)の近似式係数を算出する。この近似式係数は、記憶部30に所定係数データ31として格納されてよい。
Then, the upper computer 5 obtains the influence coefficients Ae, Be, Aq, and Bq in each of the plurality of rolling conditions based on the obtained relationship, whereby the unit width load and the influence coefficients Ae, Be. , Aq, or Bq (for example, the plots shown in FIGS. 14 to 17) are obtained, and multiple regression analysis is performed on the relationships using approximate equations (11) to (14). Thereby, the approximate expression coefficients of the approximate expressions (11) to (14) used in the predetermined range of the rolled material 8 are calculated for each of the influence coefficients Ae, Be, Aq, and Bq. This approximate expression coefficient may be stored as the predetermined coefficient data 31 in the storage unit 30.
そして、影響係数算出部21は、上述のように算出した前記近似式係数を代入した近似式(11)~(14)を用いて、前記圧延材の品種に応じて、前記影響係数Ae、Be、Aq、およびBqをそれぞれ算出する。
Then, the influence coefficient calculation unit 21 uses the approximate expressions (11) to (14) into which the approximate expression coefficient calculated as described above is substituted, and the influence coefficients Ae, Be according to the type of the rolled material. , Aq, and Bq are calculated respectively.
〔ソフトウェアによる実現例〕
上位コンピュータ5およびプロセスコンピュータ6の制御ブロック(特に、荷重算出部5c、影響係数算出部21、補正目標値算出部22、変化量算出部23、および機構制御部24)は、集積回路(ICチップ)等に形成された論理回路(ハードウェア)によって実現してもよいし、CPU(Central Processing Unit)を用いてソフトウェアによって実現してもよい。 [Example of software implementation]
The control blocks of thehost computer 5 and the process computer 6 (in particular, the load calculation unit 5c, the influence coefficient calculation unit 21, the correction target value calculation unit 22, the change amount calculation unit 23, and the mechanism control unit 24) are integrated circuits (IC chips). ) Or the like, or may be realized by software using a CPU (Central Processing Unit).
上位コンピュータ5およびプロセスコンピュータ6の制御ブロック(特に、荷重算出部5c、影響係数算出部21、補正目標値算出部22、変化量算出部23、および機構制御部24)は、集積回路(ICチップ)等に形成された論理回路(ハードウェア)によって実現してもよいし、CPU(Central Processing Unit)を用いてソフトウェアによって実現してもよい。 [Example of software implementation]
The control blocks of the
後者の場合、上位コンピュータ5およびプロセスコンピュータ6は、各機能を実現するソフトウェアである情報処理プログラムの命令を実行するCPU、前記プログラムおよび各種データがコンピュータ(またはCPU)で読み取り可能に記録されたROM(Read Only Memory)または記憶装置(これらを「記録媒体」と称する)、前記プログラムを展開するRAM(Random Access Memory)などを備えている。そして、コンピュータ(またはCPU)が前記プログラムを前記記録媒体から読み取って実行することにより、本発明の目的が達成される。前記記録媒体としては、「一時的でない有形の媒体」、例えば、テープ、ディスク、カード、半導体メモリ、プログラマブルな論理回路などを用いることができる。また、前記プログラムは、該プログラムを伝送可能な任意の伝送媒体(通信ネットワークや放送波等)を介して前記コンピュータに供給されてもよい。なお、本発明は、前記プログラムが電子的な伝送によって具現化された、搬送波に埋め込まれたデータ信号の形態でも実現され得る。
In the latter case, the host computer 5 and the process computer 6 include a CPU that executes instructions of an information processing program that is software for realizing each function, and a ROM in which the program and various data are recorded so as to be readable by the computer (or CPU). (Read Only Memory) or a storage device (these are referred to as “recording media”), a RAM (Random Access Memory) for expanding the program, and the like. Then, the computer (or CPU) reads the program from the recording medium and executes it to achieve the object of the present invention. As the recording medium, a “non-temporary tangible medium” such as a tape, a disk, a card, a semiconductor memory, a programmable logic circuit, or the like can be used. The program may be supplied to the computer via an arbitrary transmission medium (such as a communication network or a broadcast wave) that can transmit the program. The present invention can also be realized in the form of a data signal embedded in a carrier wave, in which the program is embodied by electronic transmission.
本発明は上述した各実施形態に限定されるものではなく、請求項に示した範囲で種々の変更が可能であり、異なる実施形態にそれぞれ開示された技術的手段を適宜組み合わせて得られる実施形態についても本発明の技術的範囲に含まれる。
The present invention is not limited to the above-described embodiments, and various modifications are possible within the scope shown in the claims, and embodiments obtained by appropriately combining technical means disclosed in different embodiments. Is also included in the technical scope of the present invention.
〔まとめ〕
本発明の態様1における演算装置(プロセスコンピュータ6、または、上位コンピュータ5およびプロセスコンピュータ6)は、圧延材8の圧延形状を制御する、冷間圧延機(6段圧延機1)が備える形状制御機構(中間ロールベンダー3および差荷重発生装置4、または、中間ロールベンダー3および中間ロールシフト機構2)の制御量を補正するための補正値を算出する演算装置であって、前記圧延材8における複数箇所間の、補正による伸び率差の変化量を示すと共に、前記補正値を変数として含む数式を用いて前記補正値を算出する算出部(変化量算出部23)を備え、前記数式は、前記伸び率差に及ぼす前記形状制御機構の影響度を示す影響係数を含み、前記影響係数は、前記圧延材の単位幅に加えられる荷重と前記圧延材の幅とを変数として含む関数で表されている。 [Summary]
The arithmetic device (process computer 6, or host computer 5 and process computer 6) in the aspect 1 of the present invention controls the shape of the cold rolling mill (six-high rolling mill 1) that controls the rolling shape of the rolled material 8. An arithmetic device for calculating a correction value for correcting a control amount of a mechanism (intermediate roll bender 3 and differential load generator 4 or intermediate roll bender 3 and intermediate roll shift mechanism 2), in the rolled material 8 A calculation unit (change amount calculation unit 23) that calculates the correction value using a mathematical expression that includes the correction value as a variable and indicates the amount of change in elongation difference due to correction between a plurality of locations, Including an influence coefficient indicating an influence degree of the shape control mechanism on the elongation difference, and the influence coefficient includes a load applied to a unit width of the rolled material, a width of the rolled material, and It is represented by a function including as a variable.
本発明の態様1における演算装置(プロセスコンピュータ6、または、上位コンピュータ5およびプロセスコンピュータ6)は、圧延材8の圧延形状を制御する、冷間圧延機(6段圧延機1)が備える形状制御機構(中間ロールベンダー3および差荷重発生装置4、または、中間ロールベンダー3および中間ロールシフト機構2)の制御量を補正するための補正値を算出する演算装置であって、前記圧延材8における複数箇所間の、補正による伸び率差の変化量を示すと共に、前記補正値を変数として含む数式を用いて前記補正値を算出する算出部(変化量算出部23)を備え、前記数式は、前記伸び率差に及ぼす前記形状制御機構の影響度を示す影響係数を含み、前記影響係数は、前記圧延材の単位幅に加えられる荷重と前記圧延材の幅とを変数として含む関数で表されている。 [Summary]
The arithmetic device (
従来の方法により、影響係数を、板幅、板厚、および材料の変形抵抗の関数として近似した場合、影響係数の精度はあまり高いものではなかった。そのため、従来法において、形状検出器を用いて圧延材8の板幅方向の複数箇所間の伸び率差を検出し、その検出した結果と上記得られた影響係数とを用いて、形状制御機構の制御量を補正するための補正値を算出した場合、その補正値に基づいて形状制御機構の制御量を変化させたとしても、圧延形状の計算上の変化と、実際上の変化との間の誤差が大きくなることがあった(図9参照)。
When the influence coefficient is approximated as a function of sheet width, sheet thickness, and material deformation resistance by the conventional method, the precision of the influence coefficient is not very high. Therefore, in the conventional method, a shape control mechanism is used to detect elongation difference between a plurality of locations in the sheet width direction of the rolled material 8, and using the detected result and the obtained influence coefficient, the shape control mechanism When a correction value for correcting the control amount is calculated, even if the control amount of the shape control mechanism is changed based on the correction value, the calculated change between the rolling shape and the actual change In some cases, the error of (see FIG. 9) becomes large.
これに対して、本発明の一態様における、上記の構成によれば、影響係数を、圧延材の単位幅に加えられる荷重(単位幅荷重)と前記圧延材の幅とを変数として含む関数で表される式によって、高精度に近似することができる。そのため、形状検出器を用いて圧延材8の板幅方向の複数箇所間の伸び率差を検出し、その検出した結果と上記得られた影響係数とを用いて、形状制御機構の制御量を補正するための補正値を精度良く算出することができる。その結果、この算出した補正値に基づいて、形状制御機構の制御量を適切に変化させて補正することができる。したがって、冷間圧延機が圧延した圧延材の圧延形状を良好なものとすることができる。
On the other hand, according to the above-described configuration in one aspect of the present invention, the influence coefficient is a function including the load (unit width load) applied to the unit width of the rolled material and the width of the rolled material as variables. The expression can be approximated with high accuracy. Therefore, the elongation difference between a plurality of locations in the sheet width direction of the rolled material 8 is detected using a shape detector, and the control amount of the shape control mechanism is determined using the detected result and the obtained influence coefficient. A correction value for correction can be calculated with high accuracy. As a result, correction can be performed by appropriately changing the control amount of the shape control mechanism based on the calculated correction value. Therefore, the rolling shape of the rolled material rolled by the cold rolling mill can be improved.
本発明の態様2における演算装置は、態様1における演算装置において、前記影響係数は、下記式で近似され、
A=a1・(1/p)+a2・(W/p)+a3
上記式において、Aは影響係数、pは単位幅荷重、Wは前記圧延材の幅、a1、a2およびa3は係数であるとすることができる。 In the arithmetic device according toaspect 2 of the present invention, in the arithmetic device according to aspect 1, the influence coefficient is approximated by the following equation:
A = a 1 · (1 / p) + a 2 · (W / p) + a 3
In the above formula, A can be an influence coefficient, p can be a unit width load, W can be a width of the rolled material, and a 1 , a 2 and a 3 can be coefficients.
A=a1・(1/p)+a2・(W/p)+a3
上記式において、Aは影響係数、pは単位幅荷重、Wは前記圧延材の幅、a1、a2およびa3は係数であるとすることができる。 In the arithmetic device according to
A = a 1 · (1 / p) + a 2 · (W / p) + a 3
In the above formula, A can be an influence coefficient, p can be a unit width load, W can be a width of the rolled material, and a 1 , a 2 and a 3 can be coefficients.
上記の構成によれば、予め求めておいたa1、a2およびa3の係数を用いて、上記式に基づいて、単位幅荷重pと前記圧延材の幅Wとを変数として含む関数で表される式によって、高精度に近似された影響係数を得ることができる。そのため、冷間圧延機が圧延する圧延材を変更して(圧延条件を変更して)、板幅、仕上げ板厚、材料の変形抵抗が変わった場合に、上記式に基づいて、高精度に近似された影響係数を得ることができる。つまり、良好な圧延形状が得られるように影響係数を設定することができ、圧延材の圧延形状を良好なものとすることができる。
According to the above configuration, by using the coefficients of a 1, a 2 and a 3 obtained in advance, based on the above equation, a function including the width W of the unit width load p the rolled material as a variable An influence coefficient approximated with high accuracy can be obtained by the expression expressed. Therefore, when the rolling material rolled by the cold rolling mill is changed (changing rolling conditions), and the plate width, finished plate thickness, and deformation resistance of the material change, based on the above formula, An approximate influence coefficient can be obtained. That is, the influence coefficient can be set so that a good rolled shape can be obtained, and the rolled shape of the rolled material can be made good.
本発明の態様3における演算装置は、態様1または態様2における演算装置において、複数箇所間の伸び率差として、前記圧延材の幅方向の端部における伸び率と幅方向の中央における伸び率との差、前記圧延材の幅方向の両端部間の伸び率差、または、前記端部よりも前記中央に寄った中間部における伸び率と前記中央における伸び率との差が用いられている。
In the arithmetic device in aspect 3 of the present invention, in the arithmetic device in aspect 1 or aspect 2, as the difference in elongation between a plurality of locations, the elongation at the end in the width direction of the rolled material and the elongation at the center in the width direction The difference in elongation between both ends in the width direction of the rolled material, or the difference between the elongation at the intermediate portion closer to the center than the end and the elongation at the center is used.
上記の構成によれば、圧延材の幅方向の両端部間の伸び率差を用いた場合、圧延材の非対称成分を考慮して、圧延形状の評価をすることができる。また、端部よりも前記中央に寄った中間部における伸び率と前記中央における伸び率との差を用いた場合、圧延形状をより正確に評価することができる。
According to the above configuration, when the elongation difference between both end portions in the width direction of the rolled material is used, the rolling shape can be evaluated in consideration of the asymmetric component of the rolled material. Moreover, when the difference between the elongation rate at the intermediate portion closer to the center than the end portion and the elongation rate at the center is used, the rolling shape can be more accurately evaluated.
本発明の態様4における演算装置は、態様1~3のいずれか1における演算装置において、前記数式は、前記伸び率差に及ぼす複数種類の前記形状制御機構の影響度を示す影響係数をそれぞれ有する複数の影響項を含んでよい。
The arithmetic device according to aspect 4 of the present invention is the arithmetic device according to any one of aspects 1 to 3, wherein the mathematical formulas each have an influence coefficient indicating the degree of influence of the plurality of types of shape control mechanisms on the difference in elongation. Multiple influence terms may be included.
上記の構成によれば、演算装置は、或る箇所間の伸び率差に複数種類の形状制御機構が関わる場合に、先ず、その複数種類の形状制御機構のそれぞれについて、単位幅荷重と圧延材の幅とを変数として含む関数で表される式によって、高精度に近似された影響係数を得ることができる。そして、その複数種類の形状制御機構の影響係数をそれぞれ有する複数の影響項を含む数式を用いて、その複数種類の形状制御機構の補正値を算出することができる。これにより、或る箇所間の伸び率差に複数種類の形状制御機構が関わる場合であっても、冷間圧延機が圧延した圧延材の圧延形状を良好なものとすることができる。
According to the above configuration, when a plurality of types of shape control mechanisms are involved in the difference in elongation between certain locations, the arithmetic device first calculates the unit width load and the rolling material for each of the plurality of types of shape control mechanisms. The influence coefficient approximated with high accuracy can be obtained by an expression represented by a function including the width of Then, the correction values of the plurality of types of shape control mechanisms can be calculated using mathematical expressions including a plurality of influence terms each having an influence coefficient of the plurality of types of shape control mechanisms. Thereby, even if it is a case where multiple types of shape control mechanisms relate to the elongation difference between certain locations, the rolled shape of the rolled material rolled by the cold rolling mill can be made favorable.
本発明の態様5における演算方法は、圧延材の圧延形状を制御する、冷間圧延機が備える形状制御機構の制御量を補正するための補正値を算出する演算方法であって、前記演算方法は、前記圧延材における複数箇所間の、補正による伸び率差の変化量を示すと共に、前記補正値を変数として含む数式を用いる方法であり、前記数式に含まれる、前記伸び率差に及ぼす前記形状制御機構の影響度を示す影響係数を算出する影響係数算出工程と、算出された影響係数を含む前記数式を用いて前記補正値を算出する補正値算出工程とを含み、前記影響係数は、前記圧延材の単位幅に加えられる荷重と前記圧延材の幅とを変数として含む関数で表されている。
The calculation method according to aspect 5 of the present invention is a calculation method for calculating a correction value for correcting a control amount of a shape control mechanism provided in a cold rolling mill for controlling a rolling shape of a rolled material, the calculation method Is a method of using a mathematical expression that includes the correction value as a variable, showing the amount of change in the elongation difference due to the correction between a plurality of locations in the rolled material, and the influence on the elongation difference included in the mathematical expression An influence coefficient calculating step of calculating an influence coefficient indicating an influence degree of the shape control mechanism, and a correction value calculating step of calculating the correction value using the mathematical formula including the calculated influence coefficient, It is represented by a function including the load applied to the unit width of the rolled material and the width of the rolled material as variables.
上記の構成によれば、上記態様1と同様の効果を奏する。
According to said structure, there exists an effect similar to the said aspect 1.
1:6段圧延機
2:中間ロールシフト機構
3:中間ロールベンダー
4:差荷重発生装置
5:上位コンピュータ
6:プロセスコンピュータ
7:形状検出器
8:圧延材
9:ワークロール
10:中間ロール
11:バックアップロール
23:変化量算出部(算出部) 1: Six-high rolling mill 2: Intermediate roll shift mechanism 3: Intermediate roll bender 4: Differential load generator 5: High-order computer 6: Process computer 7: Shape detector 8: Rolled material 9: Work roll 10: Intermediate roll 11: Backup roll 23: change amount calculation unit (calculation unit)
2:中間ロールシフト機構
3:中間ロールベンダー
4:差荷重発生装置
5:上位コンピュータ
6:プロセスコンピュータ
7:形状検出器
8:圧延材
9:ワークロール
10:中間ロール
11:バックアップロール
23:変化量算出部(算出部) 1: Six-high rolling mill 2: Intermediate roll shift mechanism 3: Intermediate roll bender 4: Differential load generator 5: High-order computer 6: Process computer 7: Shape detector 8: Rolled material 9: Work roll 10: Intermediate roll 11: Backup roll 23: change amount calculation unit (calculation unit)
Claims (7)
- 圧延材の圧延形状を制御する、冷間圧延機が備える形状制御機構の制御量を補正するための補正値を算出する演算装置であって、
前記圧延材における複数箇所間の、補正による伸び率差の変化量を示すと共に、前記補正値を変数として含む数式を用いて前記補正値を算出する算出部を備え、
前記数式は、前記伸び率差に及ぼす前記形状制御機構の影響度を示す影響係数を含み、前記影響係数は、前記圧延材の単位幅に加えられる荷重と前記圧延材の幅とを変数として含む関数で表されている演算装置。 An arithmetic device for calculating a correction value for correcting a control amount of a shape control mechanism included in a cold rolling mill, which controls a rolling shape of a rolled material,
A calculation unit that calculates the correction value using a mathematical expression that includes the correction value as a variable, as well as indicating the amount of change in the elongation difference due to the correction between a plurality of locations in the rolled material,
The mathematical expression includes an influence coefficient indicating the degree of influence of the shape control mechanism on the elongation difference, and the influence coefficient includes a load applied to a unit width of the rolled material and a width of the rolled material as variables. Arithmetic unit represented by a function. - 前記影響係数は、下記式で近似され、
A=a1・(1/p)+a2・(W/p)+a3
前記式において、
Aは、影響係数
pは、単位幅荷重
Wは、前記圧延材の幅
a1、a2およびa3は係数
である請求項1に記載の演算装置。 The influence coefficient is approximated by the following equation:
A = a 1 · (1 / p) + a 2 · (W / p) + a 3
In the above formula,
The arithmetic unit according to claim 1, wherein A is an influence coefficient p, unit width load W is a width a 1 , a 2, and a 3 of the rolled material. - 複数箇所間の伸び率差として、前記圧延材の幅方向の端部における伸び率と幅方向の中央における伸び率との差、前記圧延材の幅方向の両端部間の伸び率差、または、前記端部よりも前記中央に寄った中間部における伸び率と前記中央における伸び率との差が用いられている請求項1または2に記載の演算装置。 As the difference in elongation between a plurality of locations, the difference between the elongation at the end in the width direction of the rolled material and the elongation at the center in the width direction, the difference in elongation between both ends in the width direction of the rolled material, or The arithmetic unit according to claim 1, wherein a difference between an elongation rate at an intermediate portion closer to the center than the end portion and an elongation rate at the center is used.
- 前記数式は、前記伸び率差に及ぼす複数種類の前記形状制御機構の影響度を示す影響係数をそれぞれ有する複数の影響項を含む請求項1~3のいずれか1項に記載の演算装置。 The arithmetic unit according to any one of claims 1 to 3, wherein the mathematical expression includes a plurality of influence terms each having an influence coefficient indicating the degree of influence of the plurality of types of the shape control mechanisms on the elongation difference.
- 圧延材の圧延形状を制御する、冷間圧延機が備える形状制御機構の制御量を補正するための補正値を算出する演算方法であって、
前記演算方法は、前記圧延材における複数箇所間の、補正による伸び率差の変化量を示すと共に、前記補正値を変数として含む数式を用いる方法であり、
前記数式に含まれる、前記伸び率差に及ぼす前記形状制御機構の影響度を示す影響係数を算出する影響係数算出工程と、
算出された影響係数を含む前記数式を用いて前記補正値を算出する補正値算出工程とを含み、
前記影響係数は、前記圧延材の単位幅に加えられる荷重と前記圧延材の幅とを変数として含む関数で表されている演算方法。 A calculation method for calculating a correction value for correcting a control amount of a shape control mechanism provided in a cold rolling mill for controlling a rolling shape of a rolled material,
The calculation method is a method of using a mathematical expression including the correction value as a variable while showing the change amount of the elongation difference due to the correction between a plurality of locations in the rolled material,
An influence coefficient calculating step for calculating an influence coefficient indicating the degree of influence of the shape control mechanism on the elongation difference included in the mathematical expression;
A correction value calculating step of calculating the correction value using the mathematical formula including the calculated influence coefficient,
The influence coefficient is a calculation method represented by a function including a load applied to a unit width of the rolled material and a width of the rolled material as variables. - 請求項1~4のいずれか1項に記載の演算装置としてコンピュータを機能させるための情報処理プログラムであって、前記算出部としてコンピュータを機能させるための情報処理プログラム。 An information processing program for causing a computer to function as the arithmetic device according to any one of claims 1 to 4, wherein the information processing program causes the computer to function as the calculation unit.
- 請求項6に記載の情報処理プログラムを記録したコンピュータ読み取り可能な記録媒体。 A computer-readable recording medium on which the information processing program according to claim 6 is recorded.
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JP2001137925A (en) * | 1999-11-08 | 2001-05-22 | Nisshin Steel Co Ltd | Method for controlling shape in multi roll mill |
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