CN112207139B - Method for calculating rolling force of six-roller temper mill - Google Patents
Method for calculating rolling force of six-roller temper mill Download PDFInfo
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- CN112207139B CN112207139B CN202011217088.4A CN202011217088A CN112207139B CN 112207139 B CN112207139 B CN 112207139B CN 202011217088 A CN202011217088 A CN 202011217088A CN 112207139 B CN112207139 B CN 112207139B
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B38/00—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product
- B21B38/08—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product for measuring roll-force
Abstract
The invention belongs to the technical field of rolling mill operation, and particularly relates to a six-roller temper mill rolling forceAnd (4) a calculation method. The invention firstly improves the gravity G of the roll surface of the upper supporting roll BURRF Upper middle roller surface gravity G IRRF And upper work roll surface gravity G WRRF The computational model of (2); then, according to the positive and negative bending roller cylinder force characteristics, the value of the negative bending roller cylinder force is processed, the positive bending roller cylinder force is positive, and the negative bending roller cylinder force is negative to calculate. Therefore, the calculated value of the improved rolling force mathematical model is consistent with the actual rolling force value.
Description
Technical Field
The invention belongs to the technical field of rolling mill operation, and particularly relates to a method for calculating the rolling force of a six-roller temper mill.
Background
The single-frame six-roller CVC planisher comprises a main hydraulic cylinder, a supporting roller balance cylinder, a roller system, a middle roller bending cylinder, a working roller bending cylinder, a crease-resist roller, a protective roller, a rolling line adjusting mechanism, a planisher housing and the like. Wherein, the roll system comprises an upper supporting roll, an upper middle roll and an upper working roll.
In actual production, a rolling line adjusting mechanism of a single-stand six-roller CVC planisher firstly vertically pushes a lower supporting roller, a middle roller and a working roller to move upwards to the position of a strip steel rolling line, so that the roller surface of the working roller is 5-10 mm away from strip steel. Then, the main hydraulic cylinder vertically pushes the upper supporting roller, the middle roller and the working roller to move downwards, so that the upper working roller and the lower working roller generate a certain pressing rate (0.5-4%) to the strip steel, and the three purposes are achieved: firstly, the roughness of the surface of the working roll is printed on the surface of the strip steel, so that the surface roughness of the strip steel is uniform, and a reflective and beautiful surface is obtained, thereby creating conditions for coating treatment; secondly, rolling the strip steel at a certain reduction, and eliminating a yield platform and yield lines of the strip steel, thereby improving the mechanical property of the strip steel; and thirdly, driving the upper and lower intermediate roll bending cylinders and the working roll bending cylinder to act under the action of rolling force to generate certain roll bending cylinder force, so that the working roll realizes micro-deformation in the axis direction, and the middle waves or edge waves of the strip steel are eliminated through the deformed roll surface of the working roll, thereby achieving the purpose of flattening the strip steel plate. Therefore, in the process of flattening the strip steel, the rolling force of the single-stand six-roller CVC flattening machine must meet the production requirement at any time, otherwise, the product quality is influenced. Therefore, it is necessary to comprehensively consider the main factors influencing the rolling force in the flattening process, and deeply research the mathematical model of the rolling force, so as to calculate the rolling force more accurately and meet the requirements of actual production.
To date, the research on the mathematical model of the rolling force of the cold rolling continuous annealing temper mill mainly focuses on two aspects: firstly, researching a rolling force forecasting model; and secondly, researching a rolling force control model. In the research of the rolling force forecasting model, in consideration of the requirements of different preset rolling forces for different strip steel products and the comprehensive influence of various factors on the rolling force in the production process, a plurality of scholars deeply research and correspondingly improve the mathematical model of the rolling force so as to obtain the accurate rolling force preset value which is consistent with the actual rolling force. These studies do not deal with the mathematical modeling problem of the rolling force of the temper mill itself. In practice, the rolling force preset value is of fixed importance, and the rolling force generated by the temper mill itself also affects the quality of the product. Therefore, many researchers have studied a control model of rolling force. They consider the temper mill to be a highly nonlinear system, so the rolling process of the temper mill is controlled by adopting a system identification theory and an intelligent control theory so as to improve the control precision of the rolling force of the temper mill. However, the complicated control theory for controlling the rolling force may not only increase the control cost, but also may not achieve the required control effect, which may lead to questioning the practicability of the rolling force control model.
In view of the above, the present invention provides a mathematical model for calculating the rolling force of the leveler itself under the condition that the preset rolling force is correct and correct on the basis of various devices for definitely generating the rolling force. Through on-site actual operation, the problems of gravity change caused by roll surface abrasion and the value taking of negative roll bending cylinder force are found, so that the deviation between the calculated value of a mathematical model of the rolling force of the original single-frame six-roll CVC planisher and the actual value of the rolling force is large, and the production requirement cannot be well met particularly when the required rolling force is small.
Disclosure of Invention
The technical problem to be solved by the invention is as follows: the method for calculating the rolling force of the six-roller temper mill is provided, so that the calculated rolling force is more consistent with the actual rolling force.
In order to solve the technical problems, the invention adopts the technical scheme that: the method for calculating the rolling force of the six-roller temper mill comprises the following steps of:
F N ＝F MAIN +(G BUR +G IR +G WR )-(F IRB +F WRB +F BURB ) (1)，
in equation (1): f N The unit is the temper mill rolling force kN; f MAIN Is main hydraulic pressureCylinder force in kN; g BUR The unit is kN for the gravity of the upper supporting roller; g IR Is the gravity of the upper middle roller, and the unit is kN; g WR The gravity of the upper working roll is expressed in kN; f IRB The bending cylinder force of the upper intermediate roll is expressed in kN; f WRB The roll bending cylinder force of the upper working roll is expressed in kN; f BURB Balancing cylinder force of an upper supporting roller, wherein the unit is kN;
wherein the main hydraulic cylinder force F MAIN Calculated according to the following formula:
F MAIN ＝(P MAINROD ×S MAINROD -P MAINROD-LESS ×S MAINROD-LESS )×K 1 ÷100 (2)，
in equation (2): p MAINROD The pressure of a rod cavity of the main hydraulic cylinder is in bar; s. the MAINROD The main hydraulic cylinder has a rod area with the unit of cm 2 ；P MAINROD-LESS The pressure of a rodless cavity of the main hydraulic cylinder is in bar; s MAINROD-LESS Is the rodless area of the main hydraulic cylinder and has the unit of cm 2 ；K 1 The number of main hydraulic cylinders;
upper support roller gravity G BUR Calculated according to the following formula:
G BUR ＝G BURRF +G BURSH +G BURBH (3)，
in equation (3): g BURRF The gravity of the roll surface of the upper supporting roll is expressed in kN; g BURSH The unit is kN for the gravity of the upper supporting roller shaft head; g BURBH The unit is kN for the gravity of the bearing seat of the upper supporting roller;
upper intermediate roll gravity G IR Calculated according to the following formula:
G IR ＝G IRRF +G IRSH +G IRBH (4)，
in equation (4): g IRRF The gravity of the roll surface of the upper intermediate roll is expressed in kN; g IRSH The gravity of the upper middle roller shaft head is expressed in kN; g IRBH The unit is kN for the gravity of the bearing seat of the upper middle roller;
upper work roll gravity G WR Calculated according to the following formulaCalculating:
G WR ＝G WRRF +G WRSH +G WRBH (5)，
in equation (5): g WRRF The gravity of the roll surface of the upper working roll is expressed in kN; g WRSH The unit is kN for the gravity of the upper working roll shaft head; g WRBH The gravity of a bearing seat of the upper working roll is expressed in kN;
upper intermediate roll bending cylinder force F IRB Calculated according to the following formula:
in equation (6): p IRBROD The pressure of a rod cavity of a bending cylinder of an upper middle roller is in bar; s IRBROD The area of a rod of a bending cylinder of an upper middle roll is in cm 2 ；P IRBROD-LESS The pressure of a rodless cavity of a bending cylinder of the upper and middle rollers is in bar; s IRBROD-LESS The area of the upper middle roller bending cylinder without a rod is in cm 2 (ii) a A is an upper middle roller bending cylinder force amplitude limiting compensation coefficient; k is 2 The number of the upper middle roller bending cylinders is the number of the upper middle roller bending cylinders;
upper working roll bending cylinder force F WRB Calculated according to the following formula:
in equation (7): p is WRBROD The pressure of a rod cavity of a bending cylinder of the upper working roll is in bar; s WRBROD The upper working roll bending cylinder has a rod area in cm 2 ；P WRBROD-LESS The pressure of a rodless cavity of a bending cylinder of the upper working roll is in bar; s WRBROD-LESS The rodless area of the upper working roll bending cylinder is expressed in cm 2 (ii) a B is an upper working roll bending cylinder force amplitude limiting compensation coefficient; k 3 The number of the upper working roll bending cylinders is the number of the upper working roll bending cylinders;
upper support roll balance cylinder force F BURB Calculated according to the following formula:
in equation (8): p BURBROD The pressure of a rod cavity of the upper support roller balance cylinder is in bar; s. the BURBROD The area of the rod of the balance cylinder of the upper supporting roller is cm 2 ；P BURBROD-LESS The pressure of a rodless cavity of an upper support roller balance cylinder is in bar; s BURBROD-LESS The area of the upper supporting roller balance cylinder without a rod is in cm 2 ；K 4 The number of the upper supporting roller balancing cylinders is equal to that of the upper supporting roller balancing cylinders;
upper backup roll surface gravity G in equation (3) BURRF Calculated according to the following formula:
in equation (9): d BURRF The roll surface of the upper supporting roll has the diameter of m; l is BURRF The length of the roll surface of the upper supporting roll is m; rho Fe1 For the upper support roll density, in kN/m 3 ；
Upper intermediate roll surface gravity G in equation (4) IRRF Calculated according to the following formula:
in equation (10): d IRRF The roll surface of the upper intermediate roll has the diameter of m; l is a radical of an alcohol IRRF The length of the roll surface of the upper middle roll is m; rho Fe2 Is the upper intermediate roll density, and has a unit of kN/m 3 ；
Upper work roll surface gravity G in equation (5) WRRF Calculated according to the following formula:
in equation (11): d WRRF The roll surface of the upper working roll has the diameter of m; l is WRRF The length of the roll surface of the upper working roll is m; rho Fe3 The density of the upper working roll is expressed in kN/m 3 ；
Bending cylinder force F of upper intermediate roll IRB And upper work roll bending cylinder force F WRB In other words, the positive roll bending cylinder force is a positive number, the negative roll bending cylinder force is a negative number, and then the positive roll bending cylinder force and the negative roll bending cylinder force are substituted into the formula (1) to be calculated.
Further, the method comprises the following steps: according to the main hydraulic cylinder force F MAIN The values of the two are different, the maximum amplitude limiting compensation coefficient is set for the bending roller cylinder force,
control was performed according to the parameters of the table above.
The invention has the beneficial effects that: firstly, the gravity G of the roll surface of the upper supporting roll is improved BURRF Upper middle roller surface gravity G IRRF And upper work roll surface gravity G WRRF The computational model of (2); then, according to the positive and negative bending roller cylinder force characteristics, the value of the negative bending roller cylinder force is processed, the positive bending roller cylinder force is positive, and the negative bending roller cylinder force is negative to calculate. Therefore, the calculated value of the improved rolling force mathematical model is consistent with the actual rolling force value.
Detailed Description
The present invention will be further described with reference to the following examples.
The rolling force in the invention is calculated according to the following formula:
F N ＝F MAIN +(G BUR +G IR +G WR )-(F IRB +F WRB +F BURB ) (1),
in equation (1): f N The rolling force of the temper mill is kN; f MAIN Is the main hydraulic cylinder force with the unit of kN; g BUR The unit is kN for the gravity of the upper supporting roller; g IR Is the gravity of the upper middle roller, and the unit is kN; g WR The gravity of the upper working roll is expressed in kN; f IRB The bending cylinder force of the upper intermediate roll is expressed in kN; f WRB The roll bending cylinder force of the upper working roll is expressed in kN; f BURB Balancing cylinder force of an upper supporting roller in kN;
wherein the main hydraulic cylinder force F MAIN Calculated according to the following formula:
F MAIN ＝(P MAINROD ×S MAINROD -P MAINROD-LESS ×S MAINROD-LESS )×K 1 ÷100 (2),
in equation (2): p MAINROD The pressure of a rod cavity of the main hydraulic cylinder is in bar; s MAINROD The main hydraulic cylinder has a rod area in cm 2 ；P MAINROD-LESS The pressure of a rodless cavity of the main hydraulic cylinder is in bar; s MAINROD-LESS Is the rodless area of the main hydraulic cylinder and has the unit of cm 2 ；K 1 The number of main hydraulic cylinders;
upper support roller gravity G BUR Calculated according to the following formula:
G BUR ＝G BURRF +G BURSH +G BURBH (3),
in equation (3): g BURRF The gravity of the roll surface of the upper supporting roll is expressed in kN; g BURSH The unit is kN for the gravity of the upper supporting roller shaft head; g BURBH The unit is kN for the gravity of the bearing seat of the upper supporting roller;
upper intermediate roll gravity G IR Calculated according to the following formula:
G IR ＝G IRRF +G IRSH +G IRBH (4),
in equation (4): g IRRF The gravity of the roll surface of the upper intermediate roll is expressed in kN; g IRSH The gravity of the upper middle roller shaft head is expressed in kN; g IRBH The unit is kN for the gravity of the bearing seat of the upper middle roller;
upper work roll gravity G WR Calculated according to the following formula:
G WR ＝G WRRF +G WRSH +G WRBH (5),
in equation (5): g WRRF The gravity of the roll surface of the upper working roll is expressed in kN; g WRSH The unit is kN for the gravity of the upper working roll shaft head; g WRBH The unit is kN for the gravity of a bearing seat of the upper working roll;
upper intermediate roll bending cylinder force F IRB Calculated according to the following formula:
in equation (6): p IRBROD The pressure of a rod cavity of a bending cylinder of an upper middle roller is in bar; s IRBROD The bending cylinder of the upper intermediate roll has a rod area with the unit of cm 2 ；P IRBROD-LESS The pressure of a rodless cavity of a bending cylinder of an upper intermediate roll is expressed by b ar ；S IRBROD-LESS The area of the upper middle roller bending cylinder without a rod is in cm 2 (ii) a A is an upper intermediate roll bending cylinder force amplitude limiting compensation coefficient; k 2 The number of the upper middle roller bending cylinders is the number of the upper middle roller bending cylinders;
upper working roll bending cylinder force F WRB Calculated according to the following formula:
in equation (7): p WRBROD The pressure of a rod cavity of a bending cylinder of the upper working roll is in bar; s WRBROD The upper working roll bending cylinder has a rod area in cm 2 ；P WRBROD-LESS The pressure of a rodless cavity of a bending cylinder of the upper working roll is in bar; s WRBROD-LESS The rodless area of the upper working roll bending cylinder is expressed in cm 2 (ii) a B is an upper working roll bending cylinder force amplitude limiting compensation coefficient; k is 3 The number of the upper working roll bending cylinders is equal to that of the upper working roll bending cylinders;
upper support roller balance cylinder force F BURB Calculated according to the following formula:
in equation (8):P BURBROD the pressure of a rod cavity of the upper support roller balance cylinder is in bar; s BURBROD The area of a rod of a balance cylinder of the upper supporting roller is in cm 2 ；P BURBROD-LESS The pressure of a rodless cavity of an upper support roller balance cylinder is in bar; s BURBROD-LESS The area of the upper supporting roller balance cylinder without a rod is in cm 2 ；K 4 The number of cylinders is balanced for the upper support roll.
Calculating the top roll gravity G using equation (3) BUR In the meantime, the maximum gravity G of the upper support roller is assembled by inquiring detailed design drawings BURmax 344.93kN; wherein, the upper supporting roller shaft head gravity G BURSH 66.07kN and upper support roll bearing block gravity G BURBH 117.10kN are two fixed values, only the gravity G of the roller surface of the upper supporting roller BURRF Is variable with roll diameter. The length of the roll surface of the upper supporting roll is 1.98m, and the diameter of the roll surface is between 1.15m and 1.00 m. After the upper supporting roller is used for a period of time, the roller surface is ground and then the upper supporting roller is put on a machine for use again, so that the gravity G of the roller surface of the upper supporting roller is caused BURRF Will decrease as the roll surface diameter decreases, for which reason the upper support roll gravity G BUR In the original calculation model of (1), G BURRF Will no longer be carried in with a fixed value, but will be calculated with the following equation (9):
in equation (9): d BURRF The roll surface of the upper supporting roll has the diameter of m; l is BURRF The length of the roll surface of the upper supporting roll is m; rho Fe1 For the upper support roll density, in kN/m 3 。
Calculate the upper intermediate roll gravity G using equation (4) IR In the meantime, by inquiring a detailed design drawing, the upper intermediate roll is assembled with the maximum gravity G IRmax Is 117.96kN; wherein, the upper middle roller head gravity G IRSH 23.04kN and upper intermediate roll chock weight G IRBH 28.84kN are two fixed values, and only the gravity G of the roll surface of the upper intermediate roll IRRF Is changed along with the roller diameter, and is mounted on the intermediate rollerThe surface length is 2.18m, the roll surface use diameter is 0.7 m-0.62 m, the upper intermediate roll is used for a period of time, and is ground and then is used again on a machine, so that the gravity G of the roll surface of the upper intermediate roll is caused IRRF Decreasing as the roll face diameter decreases. For this purpose, the upper intermediate roll weight G IR In the original calculation model of (1), G IRRF Will no longer be taken in with a fixed value, but will be calculated using the following equation (10):
in equation (10): d IRRF The roll surface of the upper middle roll has the diameter of m; l is IRRF The length of the roll surface of the upper middle roll is m; rho Fe2 Is the upper intermediate roll density, and has a unit of kN/m 3 。
Calculate the work roll gravity G using equation (5) WR In the meantime, the upper working roll is assembled with the maximum gravity G by inquiring the detailed design drawing WRmax 42.49kN; wherein, the upper working roll shaft head gravity G WRSH 9.05kN and the weight G of the upper working roll bearing block WRBH 13.89kN are two fixed values, only the gravity G of the roll surface of the upper working roll WRRF Is a function of the roll diameter. The length of the roll surface of the upper working roll is 1.98m, the using diameter of the roll surface is 0.40-0.35 m, the upper working roll is used for a period of time, and the roll surface is ground and then put on a machine for use again, so that the gravity G of the roll surface of the upper working roll is caused WRRF Decreasing as the roll face diameter decreases. For this purpose, the upper work roll weight G WR In the original calculation model of (1), G WRRF Will no longer be taken in with a fixed value, but will be calculated using equation (11) below:
in equation (11): d WRRF The roll surface of the upper working roll is the using diameter, and the unit is m; l is a radical of an alcohol WRRF The length of the roll surface of the upper working roll is m; rho Fe3 To the upper work roll densityIn the unit kN/m 3 。
In addition, the invention processes the value of the negative bending roller cylinder force according to the characteristics of the positive and negative bending roller cylinder forces, and processes the bending roller cylinder force F of the upper intermediate roller IRB And upper work roll bending cylinder force F WRB In other words, the positive bending cylinder force and the negative bending cylinder force are respectively a positive number and a negative number, and then are substituted into the formula (1) to be calculated, so that the purpose of calculating the rolling force to be consistent with the actual rolling force is achieved.
Master cylinder force F to prevent reverse impact of roll bending cylinder force MAIN Is influenced to cause a rolling force F N The invention sets the maximum amplitude limiting compensation coefficient for the bending roller cylinder force when the oscillation is too large, and the concrete mode is as follows: according to the main hydraulic cylinder force F MAIN The maximum amplitude limiting compensation coefficient is set for the bending roll cylinder force, and the amplitude limiting compensation coefficient is controlled according to the parameters in the table 1.
TABLE 1 amplitude limiting compensation coefficient of bending roll cylinder force of working roll and intermediate roll under different main hydraulic cylinder forces
In the actual production process, the rolling force calculated by the original mathematical model shows that the deviation with the actual rolling force is large, the rolling function cannot be realized when the rolling force is small, the beautification of the plate shape and the appearance cannot be realized, and even the strip steel can be broken down. The inventor of the present application finds the cause of these situations through field operation analysis, and specifically includes two aspects:
1. upper support roller gravity G BUR Upper middle roll gravity G IR And upper work roll gravity G WR The calculation problem of (2):
in the original mathematical model formula (1), the gravity G of the upper supporting roller BUR Upper middle roll gravity G IR And upper work roll gravity G WR The calculated value is always a fixed value. That is, regardless of the actual situation of operation, the model always calculates the roll surface gravity G contained in each of the three gravities by using the maximum roll diameter BURRF 、G IRRF And G WRRF Then substituting the formula into the formulas (3), (4) and (5) respectively to obtain G BUR 、G IR And G WR . However, this is not in line with actual production. Because the upper supporting roll, the upper middle roll and the upper working roll have thickness abrasion in the using process, the roll diameter is reduced, the gravity of the roll surface is reduced, and G is enabled to be further formed BUR 、G IR And G WR The smaller the rolling force, the larger the rolling force calculated by the original mathematical model than the actual rolling force. When the required rolling force is large, the deviation value is small, and the influence is not obvious. When the required rolling force is very small, the deviation value is large, so that the rolling force fluctuation is caused, the yield platform and the yield lines of the strip steel are not eliminated, and the product quality is influenced.
2. The value problem of the negative roll bending cylinder force is as follows:
upper intermediate roll bending cylinder force F IRB And upper work roll bending cylinder force F WRB Has a component of positive and negative bending cylinder force. The force direction of the positive bending roller cylinder is vertical and upward, the positive bending roller cylinder is opposite to the direction of the rolling force, and the positive bending roller cylinder and the rolling force are in a subtraction relation; at this time, F IRB And F WRB The calculation should be done taking positive numbers and substituting them into equation (1). The direction of the negative bending roller cylinder force is vertical downward, is the same as the direction of the rolling force, and is in addition relation with the rolling force; at this time, F IRB And F WRB The calculation should be done taking a negative number into equation (1). And only F is taken from the original mathematical model IRB And F WRB The positive value of the rolling force is taken into the formula (4) to participate in calculation, so that the deviation exists between the rolling force calculated by the original mathematical model and the actual rolling force. When the rolling force is large, such deviation is small. When the rolling force is smaller, the negative bending cylinder force F of the upper intermediate roll IRB And the negative roll bending cylinder force F of the upper working roll WRB The calculated value of the rolling force of the original mathematical model is sharply reduced, so that the calculated rolling force is far smaller than the actual rolling force, and at the moment, in order to meet the preset rolling force, the force F of the main hydraulic cylinder MAIN It is increased, which causes an actually generated rolling force higher than a preset rolling force, thereby rolling the strip steel to be overcorrected, resulting in an unrealistic false impression of a small rolling force.
Examples
Introduction of actual data on site and related calculation:
in actual production field, the single-stand six-roller CVC planisher is preset with rolling force F N A main hydraulic cylinder force F ranging from 800kN to 12000kN MAIN The range is 0-12000 kN, and the practical balance cylinder force F of the upper supporting roller BURB Is 400kN.
According to the change condition of the roll diameters of the upper supporting roll, the upper middle roll and the upper working roll in actual production, the G corresponding to the maximum roll diameter and the minimum roll diameter can be calculated by adopting the formulas (3), (4) and (5) and the formulas (9), (10) and (11) after the improvement of the invention BUR ，G IR And G WR As shown in table 2. The G calculated by the original mathematical model is also shown in Table 2 BUR ，G IR And G WR 。
TABLE 2 maximum and minimum roll diameters G BUR ，G IR And G WR Is calculated data of
As can be seen from Table 2, G BUR ，G IR And G WR Since the difference between the maximum roll diameter and the minimum roll diameter is large, it is necessary to take into account the influence of the roll diameter change on the rolling force when calculating the actual rolling force.
In actual production, the cylinder force ranges of a positive bending roller and a negative bending roller of a middle roller of a temper mill are 2400 kN-1800 kN, and the cylinder force ranges of a positive bending roller and a negative bending roller of a working roller of the temper mill are 1000 kN-700 kN; from the data in equations (6) and (7), and table 1, the correspondence F can thus be calculated MAIN Modified F IRB And F WRB As shown in table 4.
TABLE 3 different F MAIN Corresponding F IRB And F WRB Is calculated data of
| F MAIN /kN | F IRB /kN | F WRB /kN |
| 0～800 | 1200～-900 | 500～-350 |
| 8000～12000 | 240～-180 | 100～-70 |
In Table 3, F IRB And F WRB A positive value in (b) indicates a maximum positive roll bending cylinder force and a negative value indicates a maximum negative roll bending cylinder force. Therefore, when the rolling force is calculated, the negative bending roller cylinder force is not reasonably processed, and a large error is brought to the calculation of the rolling force.
And analyzing the original mathematical model and the practical application condition of the invention according to the data. Two points need to be explained here: first, the present invention is limited to space, and only discusses several field applications; secondly, in an actual production field, the rolling requirement can be met when the fluctuation of the rolling force deviation value is within 1%.
Analysis of application conditions in consideration of roll diameter change and maximum positive roll bending cylinder force: when the roll diameters of the upper supporting roll, the upper intermediate roll and the upper working roll are at the maximum roll diameter or the minimum roll diameter, the roll bending cylinder force F of the upper intermediate roll is considered IRB And upper work roll bending cylinder force F WRB The maximum positive roll bending cylinder force is obtained, and the rolling forces obtained by the prior model and the present invention are shown in tables 4 and 5. The actual rolling force at the production site and the preset rolling force for the production demand are given in table 4 and table 5.
TABLE 4 comparison of roll force model before and after improvement considering maximum roll diameter and maximum positive roll bending cylinder force
TABLE 5 comparison of roll force model before and after improvement considering minimum roll diameter and maximum positive roll bending cylinder force
From Table 4, it can be found that when the upper backup roll, the upper intermediate roll and the upper work roll are at the maximum roll diameter, regardless of the master cylinder force F MAIN And in the minimum condition or the maximum condition, the rolling force calculated by the two mathematical models respectively accords with the actual rolling force, but is smaller than the preset rolling force. Thus, for F MAIN When the pressure is 0, the preset rolling force can be achieved by lifting the main hydraulic cylinder force; for F MAIN In the case of 12000kN, the actual rolling force can be reduced to the preset rolling force by reducing the positive roll bending cylinder force.
As can be seen from table 5:
(1) When the upper supporting roller, the upper middle roller and the upper working roller are the minimum roller diameter, the force F of the main hydraulic cylinder MAIN In the minimum condition, the rolling force calculated by the original mathematical model is larger than the actual rolling force by 59.3kN, and the deviation from the actual rolling force is 3.6%. At this time, even if the force of the main hydraulic cylinder is increased to make the rolling force calculated by the original mathematical model reach the preset rolling force of 800kN, the deviation between the actually achieved rolling force of the model and the preset rolling force is 7.4% (59.3/800), and the rolling requirement that the rolling force deviation value fluctuation is within 1% cannot be met. The rolling force obtained by the invention has no deviation with the actual rolling force, and can completely reach the preset rolling force after the force of the main hydraulic cylinder is lifted, thereby meeting the rolling requirement.
(2) When the upper supporting roll, the upper intermediate roll and the upper working roll are in the minimum roll diameter, the force F of the main hydraulic cylinder MAIN In the maximum case, the original mathematical modelThe calculated rolling force is greater than the actual rolling force by 59.3kN, and the deviation from the actual rolling force is about 0.5%. At this time, since the rolling force calculated by the original mathematical model is less than the preset rolling force of 12000kN, the preset rolling force is achieved by reducing the positive roll bending cylinder force, and the deviation between the finally actually achieved rolling force and the preset rolling force is 0.5% (59.3/12000), but the rolling requirement that the deviation value fluctuation of the rolling force is within 1% is met. Therefore, in this case, when the rolling force is large, the deviation of the rolling force obtained by the original mathematical model is small and can be ignored. Meanwhile, the rolling force calculated by the method is consistent with the actual rolling force, but is smaller than the preset rolling force, and the deviation between the rolling force and the preset rolling force can be avoided by reducing the positive roll bending cylinder force, so that the rolling requirement is met.
And (3) analyzing the application condition when the roll diameter change and the maximum negative roll bending cylinder force are considered: when the roll diameters of the upper supporting roll, the upper middle roll and the upper working roll are in the maximum roll diameter or the minimum roll diameter, the roll bending cylinder force F of the upper middle roll is considered IRB And upper work roll bending cylinder force F WRB The maximum negative roll bending cylinder force is obtained, and the rolling forces obtained by the original model and the present invention are shown in tables 6 and 7. The actual rolling force at the production site and the preset rolling force for the production demand are given in tables 6 and 7.
TABLE 6 comparison of roll force model before and after improvement considering maximum roll diameter and maximum negative roll bending cylinder force
TABLE 7 comparison of roll force model before and after improvement considering minimum roll diameter and maximum negative roll bending cylinder force
From table 6 it can be found that:
(1) When the main hydraulic cylinder force F MAIN In the minimum condition, the rolling force calculated by the original mathematical model is 2500kN less than the actual rolling force, and the actual rolling force is compared with the actual rolling forceThe rolling force deviation is 184.4%. At this time, since the rolling force calculated by the model is much lower than the preset rolling force, the rolling force is increased in two ways: firstly, by increasing the main hydraulic cylinder force 1944.6kN (1144.6 + 800), but at the moment, the actual field rolling force is 1355.4kN which is much larger than the preset rolling force 800kN, if the actual field rolling force is increased 1944.6kN again to reach the preset rolling force, the final result is that the actual field rolling force is 3300kN (1355.4 + 1944.6), and the deviation from the preset rolling force is 312.5% (2500/800), so that the situation of rolling and rotting the strip steel can occur; secondly, because the model takes a positive number of the negative roll bending cylinder force, the preset rolling force can be tried to be reached by reducing the negative roll bending cylinder force, but the practical situation is that the adjustment range 1250kN (900 + 350) of the negative roll bending cylinder force is smaller than 1944.6kN, which means that the preset rolling force cannot be reached even if the roll bending cylinder force is reduced to zero, and in order to meet the processing requirement of strip steel edge waves, the negative roll bending cylinder force must be ensured to be a certain value and is not allowed to be reduced to zero. Therefore, the original model shows the false impression that the production with small rolling force cannot be realized in the actual production on site. The rolling force calculated by the method conforms to the actual rolling force, but is larger than the preset rolling force, so that the preset rolling force can be achieved by reducing the negative bending roller cylinder force 555.4kN (1355.4-800), and the rolling requirement is met.
(2) When the master cylinder force F MAIN Under the maximum condition, the rolling force calculated by the original mathematical model is less than the actual rolling force by 500kN, and the deviation from the actual rolling force is 4%. At this time, since the rolling force calculated by the original model is lower than the preset rolling force, the preset rolling force is attempted to be achieved by lowering the negative roll bending cylinder force by 144.6kN (12000-11855.4). However, since the actual rolling force is 12355.4kN, even if the negative roll bending cylinder force is reduced by 144.6kN, the finally obtained rolling force is 12210.8kN (12355.4-144.6), and the deviation from the preset rolling force is 1.8% (210.8/12000), so that the rolling requirement that the rolling force deviation value fluctuation is within 1% cannot be met. The calculated rolling force has no deviation from the actual rolling force, but is larger than the preset rolling force, and the preset rolling force can be achieved by reducing the force of the main hydraulic cylinder, so that the rolling requirement is met.
From table 7 it can be found that:
(1) When the main hydraulic cylinder force F MAIN Under the minimum condition, the rolling force calculated by the original mathematical model is less than the actual rolling force 2440.7kN and has 188.3 percent deviation with the actual rolling force. At this moment, because the rolling force that original model calculated is less than predetermineeing the rolling force far away, so can increase the rolling force through two kinds of modes: firstly, through increasing the main hydraulic cylinder force 1944.6kN (1144.6 + 800), but the actual rolling force on site is 1296.1kN which is much larger than the preset rolling force 800kN, 1944.6kN is increased again to reach the preset rolling force, the final result is that the actual rolling force becomes 3240.7kN (1296.1 + 1944.6), and the deviation from the preset rolling force is 305% (2440.7/800), so that the condition of rolling the strip steel can occur; the negative roll bending cylinder force is reduced to try to reach the preset rolling force, but in the practical situation, the adjustment range 1250kN (900 + 350) of the negative roll bending cylinder force is smaller than 1944.6kN, which means that the required rolling force cannot be reached even if the roll bending cylinder force is reduced to zero, and in order to meet the processing requirement of strip edge waves, the negative roll bending cylinder force must be ensured to be a certain value and not allowed to be reduced to zero. Therefore, the original model shows the false impression that the production with small rolling force cannot be realized in the actual production on site. The rolling force calculated by the invention is consistent with the actual rolling force, but is larger than the preset rolling force, and the preset rolling force can be achieved by reducing the negative roll bending cylinder force by 496.1kN (1.1-800), so that the rolling requirement is met.
(2) When the main hydraulic cylinder force F MAIN Under the maximum condition, the rolling force calculated by the original mathematical model is less than the actual rolling force 440.7kN and has a deviation of 3.6 percent with the actual rolling force. At this time, since the rolling force calculated by the original model is lower than the preset rolling force, the preset rolling force is attempted to be achieved by reducing the negative roll bending cylinder force by 144.6kN (12000-11855.4), but the actual rolling force is 12296.1kN, so even if the negative roll bending cylinder force is reduced by 144.6kN, the finally actually obtained rolling force is 12151.5kN (12296.1-144.6), and the deviation from the preset rolling force is 1.3% (151.5/12 000), the rolling requirement that the rolling force deviation value fluctuates within 1% cannot be met. The rolling force calculated by the invention has no deviation with the actual rolling force, but is larger than the preset rolling force, so that the rolling force can be calculatedThe preset rolling force is achieved by reducing the force of the main hydraulic cylinder, and the rolling requirement is met.
Through the above analysis of the original rolling force mathematical model and the application condition of the invention, the following conclusion can be obtained:
(1) The deviation between the rolling force calculated by the original rolling force mathematical model and the actual rolling force and the preset rolling force is large, the rolling requirement is not met, and the condition that the small rolling force cannot be produced due to the fact that the strip steel is rolled up and broken can be caused.
(2) The rolling force calculated by the method is consistent with the actual rolling force, no deviation can be caused between the actual rolling force and the preset rolling force, and all the rolling forces can be realized.
(3) The invention is applied to the actual production of a certain steel mill, and proves that the calculation method can meet the actual requirements of the production of all series of high-strength steel from soft materials, thin materials to thick materials, accurately control the rolling force and improve the mechanical property, the plate shape and the surface quality of the strip steel. Therefore, the calculation method can be popularized and applied to similar planishers and has wide practicability.
Claims (2)
1. The method for calculating the rolling force of the six-roller temper mill comprises the following steps of:
F N ＝F MAIN +(G BUR +G IR +G WR )-(F IRB +F WRB +F BURB ) (1)，
in equation (1): f N The rolling force of the temper mill is kN; f MAIN Is the main hydraulic cylinder force with the unit of kN; g BUR The unit is kN for the gravity of the upper supporting roller; g IR Is the gravity of the upper middle roller, and the unit is kN; g WR The gravity of the upper working roll is expressed in kN; f IRB The bending cylinder force of the upper intermediate roll is expressed in kN; f WRB The roll bending cylinder force of the upper working roll is expressed in kN; f BURB Balancing cylinder force of an upper supporting roller, wherein the unit is kN;
wherein the main hydraulic cylinder force F MAIN Calculated according to the following formula:
F MAIN ＝(P MAINROD ×S MAINROD -P MAINROD-LESS ×S MAINROD-LESS )×K 1 ÷100 (2)，
in equation (2): p MAINROD The pressure of a rod cavity of the main hydraulic cylinder is in bar; s. the MAINROD The main hydraulic cylinder has a rod area with the unit of cm 2 ；P MAINROD-LESS The pressure of a rodless cavity of the main hydraulic cylinder is in bar; s MAINROD-LESS Is the rodless area of the main hydraulic cylinder and has the unit of cm 2 ；K 1 The number of main hydraulic cylinders;
upper support roller gravity G BUR Calculated according to the following formula:
G BUR ＝G BURRF +G BURSH +G BURBH (3)，
in formula (3): g BURRF The gravity of the roll surface of the upper supporting roll is expressed in kN; g BURSH The unit is kN for the gravity of the upper supporting roller shaft head; g BURBH The unit is kN for the gravity of the bearing seat of the upper supporting roller;
upper intermediate roll gravity G IR Calculated according to the following formula:
G IR ＝G IRRF +G IRSH +G IRBH (4)，
in equation (4): g IRRF The gravity of the roll surface of the upper intermediate roll is expressed in kN; g IRSH The gravity of the upper middle roller shaft head is expressed in kN; g IRBH The gravity of a bearing seat of the upper middle roller is expressed in kN;
upper work roll gravity G WR Calculated according to the following formula:
G WR ＝G WRRF +G WRSH +G WRBH (5)，
in equation (5): g WRRF The gravity of the roll surface of the upper working roll is expressed in kN; g WRSH The unit is kN for the gravity of the upper working roll shaft head; g WRBH The gravity of a bearing seat of the upper working roll is expressed in kN;
upper intermediate roll bending cylinder force F IRB Calculated according to the following formula:
in equation (6): p is IRBROD The pressure of a rod cavity of a bending cylinder of an upper middle roller is in bar; s IRBROD The bending cylinder of the upper intermediate roll has a rod area with the unit of cm 2 ；P IRBROD-LESS The pressure of a rodless cavity of a bending cylinder of the upper and middle rollers is in bar; s. the IRBROD-LESS The area of the upper middle roller bending cylinder without a rod is in cm 2 (ii) a A is an upper intermediate roll bending cylinder force amplitude limiting compensation coefficient; k 2 The number of the upper middle roller bending cylinders is the number of the upper middle roller bending cylinders;
upper working roll bending cylinder force F WRB Calculated according to the following formula:
in equation (7): p WRBROD The pressure of a rod cavity of a bending cylinder of the upper working roll is in bar; s. the WRBROD The upper working roll bending cylinder has a rod area in cm 2 ；P WRBROD-LESS The pressure of a rodless cavity of a bending cylinder of the upper working roll is in bar; s WRBROD-LESS The rodless area of the upper working roll bending cylinder is expressed in cm 2 (ii) a B is an upper working roll bending cylinder force amplitude limiting compensation coefficient; k 3 The number of the upper working roll bending cylinders is the number of the upper working roll bending cylinders;
upper support roller balance cylinder force F BURB Calculated according to the following formula:
in equation (8): p BURBROD The pressure of a rod cavity of the upper support roller balance cylinder is in bar; s BURBROD The area of a rod of a balance cylinder of the upper supporting roller is in cm 2 ；P BURBROD-LESS The pressure of a rodless cavity of an upper support roller balance cylinder is in bar; s BURBROD-LESS The area of the upper supporting roller balance cylinder without a rod is in cm 2 ；K 4 Is to be arranged atThe number of the balance cylinders of the supporting roller;
the method is characterized in that:
upper backup roll surface gravity G in equation (3) BURRF Calculated according to the following formula:
in equation (9): d BURRF The roll surface of the upper supporting roll has a diameter of m; l is BURRF The length of the roll surface of the upper supporting roll is m; rho Fe1 For the upper support roll density, in kN/m 3 ；
Upper intermediate roll surface gravity G in equation (4) IRRF Calculated according to the following formula:
in equation (10): d IRRF The roll surface of the upper intermediate roll has the diameter of m; l is IRRF The length of the roll surface of the upper middle roll is m; rho Fe2 Is the upper intermediate roll density, and has a unit of kN/m 3 ；
Upper work roll surface gravity G in equation (5) WRRF Calculated according to the following formula:
in equation (11): d WRRF The roll surface of the upper working roll is the using diameter, and the unit is m; l is WRRF The length of the roll surface of the upper working roll is m; ρ is a unit of a gradient Fe3 Is the upper work roll density, and has a unit of kN/m 3 ；
Bending cylinder force F of upper intermediate roll IRB And upper work roll bending cylinder force F WRB In other words, the positive roll bending cylinder force is set to be a positive number, the negative roll bending cylinder force is set to be a negative number, and then the positive roll bending cylinder force and the negative roll bending cylinder force are substituted into the formula (1) to be calculated.
2. The method of calculating a rolling force of a six-roll temper mill according to claim 1, wherein: according to the force F of the master cylinder MAIN The values of the two are different, the maximum amplitude limiting compensation coefficient is set for the bending roller cylinder force,
control was performed according to the parameters of the table above.
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