WO2020261444A1 - Temperature control device for hot rolling line - Google Patents

Temperature control device for hot rolling line Download PDF

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Publication number
WO2020261444A1
WO2020261444A1 PCT/JP2019/025458 JP2019025458W WO2020261444A1 WO 2020261444 A1 WO2020261444 A1 WO 2020261444A1 JP 2019025458 W JP2019025458 W JP 2019025458W WO 2020261444 A1 WO2020261444 A1 WO 2020261444A1
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WO
WIPO (PCT)
Prior art keywords
cooling device
rot
temperature
rolled material
value
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Application number
PCT/JP2019/025458
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French (fr)
Japanese (ja)
Inventor
鈴木　敦
Original Assignee
東芝三菱電機産業システム株式会社
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Application filed by 東芝三菱電機産業システム株式会社 filed Critical 東芝三菱電機産業システム株式会社
Priority to JP2020534629A priority Critical patent/JP6954476B2/en
Priority to CN201980006321.3A priority patent/CN112437702B/en
Priority to PCT/JP2019/025458 priority patent/WO2020261444A1/en
Publication of WO2020261444A1 publication Critical patent/WO2020261444A1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B1/00—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations
    • B21B1/22—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length
    • B21B1/24—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length in a continuous or semi-continuous process
    • B21B1/26—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length in a continuous or semi-continuous process by hot-rolling, e.g. Steckel hot mill
    • 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
    • B21B37/74—Temperature control, e.g. by cooling or heating the rolls or the product
    • B21B37/76—Cooling control on the run-out table
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B45/00—Devices for surface or other treatment of work, specially combined with or arranged in, or specially adapted for use in connection with, metal-rolling mills
    • B21B45/02—Devices for surface or other treatment of work, specially combined with or arranged in, or specially adapted for use in connection with, metal-rolling mills for lubricating, cooling, or cleaning

Definitions

  • the present invention relates to a temperature control device for a hot rolling line.
  • Patent Document 1 discloses a temperature control device for a hot rolling line. According to the temperature control device, the accuracy of the temperature model in the ROT cooling device of the hot rolling line can be improved.
  • the temperature control device described in Patent Document 1 does not control a hot rolling line in which a ROT cooling device and an acceleration cooling device are provided. Therefore, if a hot rolling line in which a ROT cooling device and an accelerated cooling device are provided is simply applied to the temperature control device, the accuracy of the temperature model cannot be improved.
  • An object of the present invention is to provide a temperature control device for a hot rolling line capable of improving the accuracy of a temperature model at a hot rolling line temperature in which a ROT cooling device and an accelerated cooling device are provided.
  • the temperature control device for the hot rolling line is a unit for water cooling in a temperature model that predicts the temperature of the rolled material with respect to the ROT cooling device that injects water into the rolled material in the downstream process of the hot rolling line.
  • the ROT side calculation unit that calculates the predicted value of the temperature of the rolled material using the ROT side water-cooled heat transfer coefficient that represents the amount of heat removed per area, and the upstream side of the ROT cooling device in the downstream process of the hot rolling line.
  • the amount of heat removed per unit area in water cooling is determined.
  • An acceleration side calculation unit that calculates a predicted value of the temperature of the rolled material using a value set separately from the ROT side water cooling heat transfer coefficient set by the ROT side calculation unit as the acceleration side water-cooled heat transfer coefficient. Equipped with.
  • the temperature control device sets the ROT side water-cooled heat transfer coefficient and the acceleration side water-cooled heat transfer coefficient separately. Therefore, the accuracy of the temperature model can be improved in the hot rolling line in which the ROT cooling device and the acceleration cooling device are installed side by side.
  • FIG. 5 is a block diagram of a main part of a hot rolling line to which a temperature control device for the hot rolling line according to the first embodiment is applied. It is a perspective view of the cut plate to which the temperature control device of the hot rolling line according to Embodiment 1 is applied. It is a figure which shows the predicted value and the actual value (re-predicted value) of the temperature change of each cut plate in the acceleration cooling device to which the temperature control device of the hot rolling line in Embodiment 1 is applied. It is a figure which shows the predicted value and the actual value (re-predicted value) of the temperature change of each cut plate in the ROT cooling device to which the temperature control device of the hot rolling line according to Embodiment 1 is applied.
  • FIG. 1 It is a figure which shows the flow of error learning of the temperature model in the acceleration cooling device to which the temperature control device of the hot rolling line in Embodiment 1 is applied. It is a figure which shows the flow of the error learning of the temperature model in the ROT cooling device to which the temperature control device of the hot rolling line in Embodiment 1 is applied. It is a hardware block diagram of the temperature control apparatus of the hot rolling line in Embodiment 1. FIG. It is a figure which shows the predicted value and the actual value (re-predicted value) of the temperature change of each cutting plate in the ROT cooling device to which the temperature control device of the hot rolling line in Embodiment 2 is applied.
  • FIG. 1 is a block diagram of a main part of a hot rolling line to which the temperature control device for the hot rolling line according to the first embodiment is applied.
  • the finishing rolling mill 1 is provided on the downstream side of a rough rolling mill (not shown).
  • the acceleration cooling device 2 is provided on the downstream side of the finish rolling mill 1.
  • the ROT cooling device 3 is provided on the downstream side of the acceleration cooling device 2.
  • the take-up coiler 4 is provided on the downstream side of the ROT cooling device 3.
  • the acceleration cooling device 2 is divided into a plurality of banks 2a by the cooling water supply system, and the plurality of banks 2a are arranged in the length direction of the hot rolling line.
  • Each of the plurality of banks 2a includes a plurality of water injection valves 2b.
  • the plurality of water injection valves 2b are arranged in the length direction of the hot rolling rolling line.
  • a plurality of nozzles 2c are provided for the plurality of water injection valves 2b.
  • the plurality of nozzles 2c are arranged in the width direction of the hot rolling line.
  • the ROT cooling device 3 is composed of a water injection device and a transfer table.
  • the water injection device is provided at a position higher than that of the acceleration cooling device 2.
  • the water injection device is divided into a plurality of banks 3a in the cooling water supply system.
  • the plurality of banks 3a are arranged in the length direction of the hot rolling line.
  • Each of the plurality of banks 3a includes a plurality of water injection valves 3b.
  • the plurality of water injection valves 3b are arranged in the length direction of the hot rolling line.
  • a plurality of nozzles 3c are provided for the plurality of water injection valves 3b.
  • the plurality of nozzles 3c are arranged in the width direction of the hot rolling line.
  • the finish rolling mill outlet side thermometer 5 is provided between the finish rolling mill 1 and the acceleration cooling device 2.
  • the intermediate thermometer 6 is provided between the acceleration cooling device 2 and the ROT cooling device 3.
  • the take-up thermometer 7 is provided between the ROT cooling device 3 and the take-up coiler 4.
  • the finish rolling mill 1 finish rolls the rolled material 8.
  • the finish rolling mill outlet side thermometer 5 measures the initial temperature of the total length of the rolled material 8 as the actual FDT value before cooling.
  • the acceleration cooling device 2 accelerates and cools the rolled material 8 by driving a pump (not shown) with an inverter (not shown) and injecting water at a high pressure. In accelerated cooling, the cooling rate of the rolled material 8 is faster than that of normal water cooling. As a result, the crystal structure of the rolled material 8 is adjusted, so that the mechanical properties of the rolled material 8 change.
  • the intermediate thermometer 6 measures the initial temperature of the entire length of the rolled material 8 as the actual MT value.
  • the ROT cooling device 3 cools the rolled material 8 by injecting water at a constant pressure.
  • the take-up thermometer 7 measures the initial temperature of the entire length of the rolled material 8 as a CT actual value.
  • the take-up coiler 4 winds up the rolled material 8.
  • the temperature control device 9 includes an acceleration side calculation unit 9a, a ROT side calculation unit 9b, and a control unit 9c.
  • the acceleration side calculation unit 9a predicts in advance the temperature of the rolled material 8 on the entrance / exit side of each bank 2a of the acceleration cooling device 2 using the temperature model.
  • the ROT side calculation unit 9b predicts in advance the temperature of the rolled material 8 on the inlet / outlet side of each bank 3a of the ROT cooling device 3 using the temperature model.
  • the control unit 9c controls the opening and closing of each water injection valve 2b of the acceleration cooling device 2 based on the prediction result by the acceleration side calculation unit 9a.
  • the control unit 9c controls the opening and closing of each water injection valve 3b of the ROT cooling device 3 based on the prediction result by the ROT side calculation unit 9b.
  • the acceleration side calculation unit 9a accelerates based on the FDT actual value from the finish rolling mill output side thermometer 5 and the MT actual value from the intermediate thermometer 6.
  • the ROT side calculation unit 9b learns the temperature model in the ROT cooling device 3 based on the MT actual value from the intermediate thermometer 6 and the CT actual value from the take-up thermometer 7.
  • the temperature control device 9 starts from the FDT actual value of each cutting plate, and each bank of the accelerated cooling device 2 of each cutting plate so that the final CT predicted value reaches the CT target value.
  • the temperature prediction calculation of the inlet / outlet side of each bank 3a of 2a and the ROT cooling device 3 is performed.
  • the temperature control device 9 has a reference value (V 1 acc , C 2 acc , ... C n acc ) of the amount of cooling water to each bank 2a of the accelerated cooling device 2 and the amount of cooling water to each bank 3a of the ROT cooling device 3. (V 1 rot , C 2 rot , ... C n rot ) is determined.
  • each bank 2a the number of water injection valves 2b to be opened is determined based on the reference value.
  • the number of water injection valves 3b to be opened is determined based on the reference value.
  • the temperature control device 9 learns the temperature model in the acceleration cooling device 2 so that the error due to the position of the intermediate thermometer 6 becomes zero.
  • the temperature control device 9 learns the temperature model in the ROT cooling device 3 so that the error due to the position of the take-up thermometer 7 becomes zero.
  • the MT actual value is used as the initial value for the initial temperature in the temperature prediction of each cutting plate.
  • FIG. 2 is a perspective view of a cutting plate to which the temperature control device for the hot rolling line according to the first embodiment is applied.
  • the heat inflow and outflow is calculated after the rolled material 8 is divided into cutting plates 8a having a constant length.
  • the constant length is set between 3 m and 5 m.
  • h w is a water-cooled heat transfer coefficient (W / mm 2 / ° C.). h w is different between the acceleration cooling device 2 and the ROT cooling device 3.
  • a w is the area (mm 2 ) of the upper and lower surfaces of the cutting plate 8a in contact with the cooling water.
  • a w changes with the number of water injection valves opened in each bank.
  • T w is the temperature (° C.) of the cooling water.
  • T surf is the surface temperature (° C.) of the cutting plate 8a.
  • T is the temperature (° C.) of the cutting plate 8a.
  • ⁇ is the density of the cutting plate 8a (kg / mm 3 ).
  • C P is the specific heat of Setsuban 8a (J / kg / °C) .
  • l is the length (mm) of the cutting plate 8a in the traveling direction.
  • B is the width (mm) of the cutting plate 8a.
  • H is the plate thickness (mm) of the cutting plate 8a.
  • t is the time (s). i is the number of the cutting plate 8a.
  • FIG. 3 is a diagram showing a predicted value and an actual value (re-predicted value) of a temperature change of each cutting plate inside the acceleration cooling device to which the temperature control device of the hot rolling line according to the first embodiment is applied.
  • FIG. 4 is a diagram showing predicted values and actual values (repredicted values) of temperature changes of each cutting plate inside the ROT cooling device to which the temperature control device for the hot rolling line according to the first embodiment is applied.
  • FIG. 5 is a diagram showing a flow of error learning of a temperature model in an accelerated cooling device to which the temperature control device for the hot rolling line according to the first embodiment is applied.
  • FIG. 6 is a diagram showing a flow of error learning of a temperature model in a ROT cooling device to which a temperature control device for a hot rolling line according to the first embodiment is applied.
  • Z 1 acc and Z 2 acc which are learning values of the water-cooled heat transfer coefficient h w acc of the acceleration cooling device 2, are automatically adjusted.
  • v a acc (m / s ) is the average speed of each Setsuban 8a inside the accelerated cooling device 2.
  • v 0 (m / s) is the reference speed of each cutting plate 8a inside the acceleration cooling device 2.
  • f w acc is a model prediction function.
  • Z 1 acc is a multiplication type learning value for the predicted value of the temperature model.
  • Z 2 acc is a power-type learning value for the velocity ratio.
  • the cooling phenomenon in the rolled material 8 differs between when the rolled material 8 moves at high speed and when the rolled material 8 is stationary. Therefore, as shown in Eq. (3), the influence of speed is adjusted by the learning term.
  • Z 2 acc is obtained so that the error of the MT predicted value becomes 0 by using the data of the specific cutting plate 8a of the Middle portion which is the portion of the rolled material 8 during or after acceleration. At this time, the value obtained in the Head portion is used for Z 1 acc .
  • Z 1 rot and Z 2 rot which are learning values of the water-cooled heat transfer coefficient h w rot of the ROT cooling device 3, are automatically adjusted.
  • v a rot (m / s ) is the average speed of each Setsuban 8a inside the ROT cooling device 3.
  • v 0 (m / s) is the reference speed of each cutting plate 8a inside the ROT cooling device 3.
  • f w rot is a model prediction function.
  • Z 1 rot is a learning value of a multiplication type with respect to the predicted value of the temperature model.
  • Z 2 rot is a power-type learning value for the velocity ratio.
  • the cooling phenomenon in the rolled material 8 differs between when the rolled material 8 moves at high speed and when the rolled material 8 is stationary. Therefore, as shown in Eq. (4), the influence of speed is adjusted by the learning term.
  • the Z 2 rotor is obtained so that the error of the CT predicted value becomes 0. At this time, the value obtained in the head section is used for Z 1 rot .
  • the temperature control device 9 sets the water-cooled heat transfer coefficient separately in the acceleration cooling device 2 and the ROT cooling device 3. Therefore, the accuracy of the temperature model can be improved.
  • the temperature control device 9 corrects the predicted value of the temperature of the rolled material 8 based on the difference between the predicted value of the cooled temperature of the rolled material 8 predicted by the temperature model and the measured value of the actual temperature. Calculate the learning value to do. Therefore, the accuracy of the temperature model can be further improved.
  • the temperature control device 9 calculates a learning value for correcting the predicted value of the temperature of the rolled material 8 based on the actual MT value. Therefore, the accuracy of the temperature model can be further improved.
  • the cooling water can be maintained in a state of covering the surface of the rolled material 8 directly under the intermediate thermometer 6. Therefore, the surface temperature of the rolled material 8 may not be accurately measured by the intermediate thermometer 6.
  • the water injection valve 2b closer to the intermediate thermometer 6 may be closed preferentially.
  • FIG. 7 is a hardware configuration diagram of the temperature control device for the hot rolling line according to the first embodiment.
  • Each function of the temperature control device 9 can be realized by a processing circuit.
  • the processing circuit includes at least one processor 100a and at least one memory 100b.
  • the processing circuit comprises at least one dedicated hardware 200.
  • each function of the temperature control device 9 is realized by software, firmware, or a combination of software and firmware. At least one of the software and firmware is written as a program. At least one of the software and firmware is stored in at least one memory 100b. At least one processor 100a realizes each function of the temperature control device 9 by reading and executing a program stored in at least one memory 100b. At least one processor 100a is also referred to as a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microcomputer, and a DSP.
  • at least one memory 100b is a non-volatile or volatile semiconductor memory such as RAM, ROM, flash memory, EPROM, EEPROM, magnetic disk, flexible disk, optical disk, compact disk, mini disk, DVD or the like.
  • the processing circuit comprises at least one dedicated hardware 200
  • the processing circuit may be implemented, for example, as a single circuit, a composite circuit, a programmed processor, a parallel programmed processor, an ASIC, an FPGA, or a combination thereof.
  • each function of the temperature control device 9 is realized by a processing circuit.
  • each function of the temperature control device 9 is collectively realized by a processing circuit.
  • a part may be realized by the dedicated hardware 200, and the other part may be realized by software or firmware.
  • the function of the control unit 9c is realized by a processing circuit as dedicated hardware 200, and for functions other than the function of the control unit 9c, at least one processor 100a reads a program stored in at least one memory 100b. It may be realized by executing.
  • the processing circuit realizes each function of the temperature control device 9 with the hardware 200, software, firmware, or a combination thereof.
  • FIG. 8 is a diagram showing predicted values and actual values (repredicted values) of temperature changes of each cutting plate inside the ROT cooling device to which the temperature control device for the hot rolling line according to the second embodiment is applied.
  • the same or corresponding parts as those of the first embodiment are designated by the same reference numerals. The explanation of the relevant part is omitted.
  • the MT predicted value and the MT actual result of the cutting plate 8a If there is a prediction error of the temperature model between the value and the value, the start point (MT) inside the ROT cooling device 3 is corrected to the actual MT value, and then the ROT cooling device 3 is used to reach the CT target value.
  • the predicted value of the temperature change of the rolled material 8 inside is recalculated.
  • the reference values (V 1 rot , V 2 rot , ... V M rot ) of the amount of cooling water to each bank 3a are corrected so that the recalculated predicted value is achieved.
  • the temperature control device 9 when the temperature control device 9 has a temperature model prediction error between the actual temperature value of the rolled material 8 and the predicted temperature value of the rolled material 8 by the intermediate thermometer 6.
  • the water injection valve 3b of the ROT cooling device 3 is controlled so as to compensate for the error. Therefore, the accuracy of the temperature model can be further improved.
  • the temperature control device 9 uses the intermediate thermometer 6 to measure the temperature of the rolled material 8 when there is an error in the temperature model between the actual temperature value of the rolled material 8 and the predicted temperature value.
  • the predicted value of the temperature change of the rolled material 8 inside the ROT cooling device 3 is recalculated with the actual value of the above as the initial value. Therefore, the accuracy of the temperature model can be further improved.
  • FIG. 9 is a diagram showing predicted values and actual values (repredicted values) of temperature changes of each cutting plate inside the accelerated cooling device to which the temperature control device for the hot rolling line according to the third embodiment is applied.
  • FIG. 10 is a diagram showing a predicted value and an actual value (repredicted value) of a temperature change of each cutting plate inside the ROT cooling device to which the temperature control device of the hot rolling line according to the first embodiment is applied.
  • the same or corresponding parts as those of the first embodiment are designated by the same reference numerals. The explanation of the relevant part is omitted.
  • an experiment for identifying the cooling efficiency using the acceleration cooling device 2 and the ROT cooling device 3 alone is performed in advance.
  • the acceleration cooling device 2 and the ROT cooling device 3 Based on the actual temperature drop value (° C), which is the value obtained by subtracting the CT actual value from the FDT actual value of each cutting plate 8a, and the actual number of open water injection valves, the acceleration cooling device 2 and the ROT cooling device 3 The cooling efficiency (° C / valve) per valve is calculated.
  • the speed pattern of the rolled material 8 at this time is the same as that of normal rolling.
  • the cooling efficiency of the acceleration cooling device 2 is a (k) (° C./valve).
  • k is the number of the cutting plate 8a.
  • the predicted temperature drop value of the accelerated cooling device 2 is a (k) ⁇ A (k) (° C.).
  • the predicted temperature drop value of the ROT cooling device 3 is b (k) ⁇ B (k) (° C.).
  • the actual temperature drop by the acceleration cooling device 2 for each cutting plate 8a is calculated by the following equation (5).
  • the actual temperature drop by the ROT cooling device 3 for each cutting plate 8a is calculated by the following equation (6).
  • the predicted value on the entry / exit side of each bank 2a is recalculated with the value obtained by subtracting the value shown in the equation (5) from the FDT actual value as the MT actual value.
  • the MT actual value is used as the initial value, and the value obtained by subtracting the value shown in Eq. (6) from the initial value is used as the CT actual value for prediction on the entry / exit side of each bank 3a. The value is recalculated.
  • the temperature control device 9 has the cooling efficiency obtained by the identification experiment using the accelerated cooling device 2 alone, and the cooling efficiency obtained from the upstream side of the accelerated cooling device 2 and the ROT cooling device 3.
  • the cooling efficiency per valve is calculated from the actual value of the temperature drop of the rolled material 8 to the downstream side and the number of sprays used in the accelerated cooling device 2.
  • the temperature control device 9 has the cooling efficiency obtained by the identification experiment using the ROT cooling device 3 alone and the temperature drop of the rolled material 8 from the upstream side to the downstream side of the accelerated cooling device 2 and the ROT cooling device 3.
  • the cooling efficiency per valve is calculated from the actual value and the number of sprays used in the ROT cooling device 3. Therefore, the accuracy of the temperature model can be further improved.
  • the temperature control device 9 may calculate the cooling efficiency of the accelerated cooling device 2 and the cooling efficiency of the ROT cooling device 3 and the cooling efficiency by using the ratio of the accelerated cooling device 2 and the ROT cooling device 3. In this case as well, the accuracy of the temperature model can be further improved.
  • FIG. 11 is a diagram showing a predicted value and an actual value (re-predicted value) of a temperature change of each cutting plate inside the acceleration cooling device to which the temperature control device of the hot rolling line according to the fourth embodiment is applied.
  • FIG. 12 is a diagram showing predicted values and actual values (re-predicted values) of temperature changes of each cutting plate inside the ROT cooling device to which the temperature control device for the hot rolling line according to the fourth embodiment is applied.
  • the same or corresponding parts as those of the first embodiment are designated by the same reference numerals. The explanation of the relevant part is omitted.
  • an experiment for identifying the cooling efficiency using the acceleration cooling device 2 and the ROT cooling device 3 alone is performed in advance. Based on the actual value of temperature drop (° C.) and the actual value of the spray flow rate of the opened valve (m 3 / h), the value obtained by subtracting the actual CT value from the actual FDT value of each cutting plate 8a is combined with the acceleration cooling device 2. cooling efficiency per one valve between the ROT cooling device 3 (°C / m 3 / h ) is calculated. The speed pattern of the rolled material 8 at this time is the same as that of normal rolling.
  • the cooling efficiency of the accelerated cooling device 2 and ⁇ (k) (°C / m 3 / h).
  • the cooling efficiency of the ROT cooling device 3 and ⁇ (k) (°C / m 3 / h).
  • the number of water injection valves 2b used in the acceleration cooling device 2 be A (k) (valve).
  • the number of water injection valves 3b used in the ROT cooling device 3 be B (k) (valve).
  • Pa (m 3 / h / valve) be the spray flow rate per water injection valve 2b in the acceleration cooling device 2.
  • P b (m 3 / h / valve) be the spray flow rate per water injection valve 3 b in the ROT cooling device 3.
  • the temperature drop predicted value of accelerated cooling device 2 is a ⁇ (k) ⁇ A (k ) ⁇ P a (°C).
  • the predicted temperature drop value of the ROT cooling device 3 is ⁇ (k) ⁇ B (k) ⁇ P b (° C.).
  • the actual temperature drop by the acceleration cooling device 2 for each cutting plate 8a is calculated by the following equation (7).
  • the actual temperature drop by the ROT cooling device 3 for each cutting plate 8a is calculated by the following equation (8).
  • the predicted value on the entry / exit side of each bank 2a is recalculated with the value obtained by subtracting the value shown in the equation (7) from the FDT actual value as the MT actual value.
  • the MT actual value is used as the initial value, and the value obtained by subtracting the value shown in Eq. (8) from the initial value is used as the CT actual value for prediction on the entry / exit side of each bank 3a. The value is recalculated.
  • the temperature control device 9 has the cooling efficiency obtained by the identification experiment using the accelerated cooling device 2 alone, and the cooling efficiency obtained from the upstream side of the accelerated cooling device 2 and the ROT cooling device 3.
  • the cooling efficiency per valve is calculated from the actual value of the temperature drop of the rolled material 8 to the downstream side and the volume of the spray flow rate used in the accelerated cooling device 2.
  • the temperature control device 9 has the cooling efficiency obtained by the identification experiment using the ROT cooling device 3 alone and the temperature drop of the rolled material 8 from the upstream side to the downstream side of the accelerated cooling device 2 and the ROT cooling device 3.
  • the cooling efficiency per valve is calculated from the actual value and the volume of the spray flow rate used in the ROT cooling device 3. Therefore, the accuracy of the temperature model can be further improved.
  • temperature control device 9 of any of the first to fourth embodiments may be applied to the hot rolling line provided with the acceleration cooling device 2 on the downstream side of the ROT cooling device 3. In this case as well, the accuracy of the temperature model can be improved.
  • the temperature control device for the hot rolling line according to the present invention can be used for the hot rolling system.

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  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)

Abstract

Provided is a temperature control device for a hot rolling line having a ROT cooling device and an accelerated cooling device, the temperature control device enabling an increase in the accuracy of a temperature model of a rolled material. The temperature control device for a hot rolling line is provided with: a ROT side calculation unit which, in a temperature model for predicting the temperature of a rolled material with respect to a ROT cooling device that injects water to the rolled material, calculates a predicted value of the temperature of the rolled material using a ROT side water-cooled heat transfer coefficient representing the amount of heat removed per unit area during cooling by water; and an acceleration side calculation unit that is provided on an upstream side or a downstream side of the ROT cooling device, and which, in a temperature model for predicting the temperature of the rolled material with respect to an accelerated cooling device that injects water to the rolled material under a different condition from the ROT cooling device, calculates a predicted value of the temperature of the rolled material using a value which is set, separately from the ROT side water cooling heat transfer coefficient set by the ROT side calculation unit, as an acceleration side water cooling heat transfer coefficient representing the amount of heat removed per unit area during cooling by water.

Description

熱間圧延ラインの温度制御装置Temperature control device for hot rolling line
　この発明は、熱間圧延ラインの温度制御装置に関する。 The present invention relates to a temperature control device for a hot rolling line.
　特許文献１は、熱間圧延ラインの温度制御装置を開示する。当該温度制御装置によれば、熱間圧延ラインのＲＯＴ冷却装置における温度モデルの精度を高め得る。 Patent Document 1 discloses a temperature control device for a hot rolling line. According to the temperature control device, the accuracy of the temperature model in the ROT cooling device of the hot rolling line can be improved.
日本特許第５８３５４８３号公報Japanese Patent No. 58354843
　しかしながら、特許文献１に記載の温度制御装置は、ＲＯＴ冷却装置と加速冷却装置とを併設した熱間圧延ラインを制御対象としない。このため、ＲＯＴ冷却装置と加速冷却装置とを併設した熱間圧延ラインを当該温度制御装置に単純に適用すると、温度モデルの精度を高めることができない。 However, the temperature control device described in Patent Document 1 does not control a hot rolling line in which a ROT cooling device and an acceleration cooling device are provided. Therefore, if a hot rolling line in which a ROT cooling device and an accelerated cooling device are provided is simply applied to the temperature control device, the accuracy of the temperature model cannot be improved.
　この発明は、上述の課題を解決するためになされた。この発明の目的は、ＲＯＴ冷却装置と加速冷却装置とを併設した熱間圧延ライン温度において、温度モデルの精度を高めることができる熱間圧延ラインの温度制御装置を提供することである。 This invention was made to solve the above-mentioned problems. An object of the present invention is to provide a temperature control device for a hot rolling line capable of improving the accuracy of a temperature model at a hot rolling line temperature in which a ROT cooling device and an accelerated cooling device are provided.
　この発明に係る熱間圧延ラインの温度制御装置は、熱間圧延ラインの下流工程において、圧延材に注水するＲＯＴ冷却装置に対し、当該圧延材の温度を予測する温度モデルにおいて、水冷冷却における単位面積あたりの抜熱量を表すＲＯＴ側水冷熱伝達係数を用いて当該圧延材の温度の予測値を計算するＲＯＴ側計算部と、前記熱間圧延ラインの下流工程において、前記ＲＯＴ冷却装置の上流側または下流側に設けられ、前記ＲＯＴ冷却装置とは異なる条件で当該圧延材に注水する加速冷却装置に対し、当該圧延材の温度を予測する温度モデルにおいて、水冷冷却における単位面積あたりの抜熱量を表す加速側水冷熱伝達係数として前記ＲＯＴ側計算部により設定されたＲＯＴ側水冷熱伝達係数とは別に設定された値を用いて当該圧延材の温度の予測値を計算する加速側計算部と、を備えた。 The temperature control device for the hot rolling line according to the present invention is a unit for water cooling in a temperature model that predicts the temperature of the rolled material with respect to the ROT cooling device that injects water into the rolled material in the downstream process of the hot rolling line. The ROT side calculation unit that calculates the predicted value of the temperature of the rolled material using the ROT side water-cooled heat transfer coefficient that represents the amount of heat removed per area, and the upstream side of the ROT cooling device in the downstream process of the hot rolling line. Alternatively, in a temperature model that predicts the temperature of the rolled material for an accelerated cooling device that is installed on the downstream side and injects water into the rolled material under conditions different from the ROT cooling device, the amount of heat removed per unit area in water cooling is determined. An acceleration side calculation unit that calculates a predicted value of the temperature of the rolled material using a value set separately from the ROT side water cooling heat transfer coefficient set by the ROT side calculation unit as the acceleration side water-cooled heat transfer coefficient. Equipped with.
　この発明によれば、温度制御装置は、ＲＯＴ側水冷熱伝達係数と加速側水冷熱伝達係数とを別々に設定する。このため、ＲＯＴ冷却装置と加速冷却装置とを併設した熱間圧延ラインにおいて、温度モデルの精度を高めることができる。 According to the present invention, the temperature control device sets the ROT side water-cooled heat transfer coefficient and the acceleration side water-cooled heat transfer coefficient separately. Therefore, the accuracy of the temperature model can be improved in the hot rolling line in which the ROT cooling device and the acceleration cooling device are installed side by side.
実施の形態１における熱間圧延ラインの温度制御装置が適用される熱間圧延ラインの要部の構成図である。FIG. 5 is a block diagram of a main part of a hot rolling line to which a temperature control device for the hot rolling line according to the first embodiment is applied. 実施の形態１における熱間圧延ラインの温度制御装置が適用される切板の斜視図である。It is a perspective view of the cut plate to which the temperature control device of the hot rolling line according to Embodiment 1 is applied. 実施の形態１における熱間圧延ラインの温度制御装置が適用される加速冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。It is a figure which shows the predicted value and the actual value (re-predicted value) of the temperature change of each cut plate in the acceleration cooling device to which the temperature control device of the hot rolling line in Embodiment 1 is applied. 実施の形態１における熱間圧延ラインの温度制御装置が適用されるＲＯＴ冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。It is a figure which shows the predicted value and the actual value (re-predicted value) of the temperature change of each cut plate in the ROT cooling device to which the temperature control device of the hot rolling line according to Embodiment 1 is applied. 実施の形態１における熱間圧延ラインの温度制御装置が適用される加速冷却装置での温度モデルの誤差学習の流れを示す図である。It is a figure which shows the flow of error learning of the temperature model in the acceleration cooling device to which the temperature control device of the hot rolling line in Embodiment 1 is applied. 実施の形態１における熱間圧延ラインの温度制御装置が適用されるＲＯＴ冷却装置での温度モデルの誤差学習の流れを示す図である。It is a figure which shows the flow of the error learning of the temperature model in the ROT cooling device to which the temperature control device of the hot rolling line in Embodiment 1 is applied. 実施の形態１における熱間圧延ラインの温度制御装置のハードウェア構成図である。It is a hardware block diagram of the temperature control apparatus of the hot rolling line in Embodiment 1. FIG. 実施の形態２における熱間圧延ラインの温度制御装置が適用されるＲＯＴ冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。It is a figure which shows the predicted value and the actual value (re-predicted value) of the temperature change of each cutting plate in the ROT cooling device to which the temperature control device of the hot rolling line in Embodiment 2 is applied. 実施の形態３における熱間圧延ラインの温度制御装置が適用される加速冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。It is a figure which shows the predicted value and the actual value (re-predicted value) of the temperature change of each cutting plate in the acceleration cooling device to which the temperature control device of the hot rolling line in Embodiment 3 is applied. 実施の形態１における熱間圧延ラインの温度制御装置が適用されるＲＯＴ冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。It is a figure which shows the predicted value and the actual value (re-predicted value) of the temperature change of each cut plate in the ROT cooling device to which the temperature control device of the hot rolling line in Embodiment 1 is applied. 実施の形態４における熱間圧延ラインの温度制御装置が適用される加速冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。It is a figure which shows the predicted value and the actual value (re-predicted value) of the temperature change of each cut plate in the acceleration cooling device to which the temperature control device of the hot rolling line in Embodiment 4 is applied. 実施の形態４における熱間圧延ラインの温度制御装置が適用されるＲＯＴ冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。It is a figure which shows the predicted value and the actual value (re-predicted value) of the temperature change of each cut plate in the ROT cooling device to which the temperature control device of the hot rolling line in Embodiment 4 is applied.
　この発明を実施するための形態について添付の図面に従って説明する。なお、各図中、同一または相当する部分には同一の符号が付される。当該部分の重複説明は適宜に簡略化ないし省略する。 The embodiment for carrying out the present invention will be described with reference to the attached drawings. In each figure, the same or corresponding parts are designated by the same reference numerals. The duplicate description of the relevant part will be simplified or omitted as appropriate.
実施の形態１．
　図１は実施の形態１における熱間圧延ラインの温度制御装置が適用される熱間圧延ラインの要部の構成図である。 Embodiment 1.
FIG. 1 is a block diagram of a main part of a hot rolling line to which the temperature control device for the hot rolling line according to the first embodiment is applied.
　図１の熱間圧延ラインにおいて、仕上圧延機１は、図示されない粗圧延機の下流側に設けられる。加速冷却装置２は、仕上圧延機１の下流側に設けられる。ＲＯＴ冷却装置３は、加速冷却装置２の下流側に設けられる。巻取コイラー４は、ＲＯＴ冷却装置３の下流側に設けられる。 In the hot rolling line of FIG. 1, the finishing rolling mill 1 is provided on the downstream side of a rough rolling mill (not shown). The acceleration cooling device 2 is provided on the downstream side of the finish rolling mill 1. The ROT cooling device 3 is provided on the downstream side of the acceleration cooling device 2. The take-up coiler 4 is provided on the downstream side of the ROT cooling device 3.
　加速冷却装置２は、冷却水の供給系統で複数のバンク２ａに区分される、複数のバンク２ａは、熱間圧延ラインの長さ方向に並ぶ。複数のバンク２ａの各々は、複数の注水バルブ２ｂを備える。複数の注水バルブ２ｂは、圧延熱間圧延ラインの長さ方向に並ぶ。複数の注水バルブ２ｂに対し、複数のノズル２ｃが設けられる。複数のノズル２ｃは、熱間圧延ラインの幅方向に並ぶ。 The acceleration cooling device 2 is divided into a plurality of banks 2a by the cooling water supply system, and the plurality of banks 2a are arranged in the length direction of the hot rolling line. Each of the plurality of banks 2a includes a plurality of water injection valves 2b. The plurality of water injection valves 2b are arranged in the length direction of the hot rolling rolling line. A plurality of nozzles 2c are provided for the plurality of water injection valves 2b. The plurality of nozzles 2c are arranged in the width direction of the hot rolling line.
　ＲＯＴ冷却装置３は、注水装置と搬送テーブルから構成される。ＲＯＴ冷却装置３において、注水装置は、加速冷却装置２よりも高い位置に設けられる。ＲＯＴ冷却装置３において、注水装置は、冷却水の供給系統で複数のバンク３ａに区分される。複数のバンク３ａは、熱間圧延ラインの長さ方向に並ぶ。複数のバンク３ａの各々は、複数の注水バルブ３ｂを備える。複数の注水バルブ３ｂは、熱間圧延ラインの長さ方向に並ぶ。複数の注水バルブ３ｂに対し、複数のノズル３ｃが設けられる。複数のノズル３ｃは、熱間圧延ラインの幅方向に並ぶ。 The ROT cooling device 3 is composed of a water injection device and a transfer table. In the ROT cooling device 3, the water injection device is provided at a position higher than that of the acceleration cooling device 2. In the ROT cooling device 3, the water injection device is divided into a plurality of banks 3a in the cooling water supply system. The plurality of banks 3a are arranged in the length direction of the hot rolling line. Each of the plurality of banks 3a includes a plurality of water injection valves 3b. The plurality of water injection valves 3b are arranged in the length direction of the hot rolling line. A plurality of nozzles 3c are provided for the plurality of water injection valves 3b. The plurality of nozzles 3c are arranged in the width direction of the hot rolling line.
　仕上圧延機出側温度計５は、仕上圧延機１と加速冷却装置２との間に設けられる。中間温度計６は、加速冷却装置２とＲＯＴ冷却装置３との間に設けられる。巻取温度計７は、ＲＯＴ冷却装置３と巻取コイラー４との間に設けられる。 The finish rolling mill outlet side thermometer 5 is provided between the finish rolling mill 1 and the acceleration cooling device 2. The intermediate thermometer 6 is provided between the acceleration cooling device 2 and the ROT cooling device 3. The take-up thermometer 7 is provided between the ROT cooling device 3 and the take-up coiler 4.
　仕上圧延機１は、圧延材８を仕上圧延する。その後、仕上圧延機出側温度計５は、冷却前に当該圧延材８の全長の初期温度をＦＤＴ実績値として計測する。その後、加速冷却装置２は、図示されないインバータで図示されないポンプを駆動して高圧で注水することで当該圧延材８を加速冷却する。加速冷却において、圧延材８の冷却速度は、通常の水冷よりも速くなる。その結果、圧延材８の結晶組織が調整されることで、圧延材８の機械的性質が変化する。 The finish rolling mill 1 finish rolls the rolled material 8. After that, the finish rolling mill outlet side thermometer 5 measures the initial temperature of the total length of the rolled material 8 as the actual FDT value before cooling. After that, the acceleration cooling device 2 accelerates and cools the rolled material 8 by driving a pump (not shown) with an inverter (not shown) and injecting water at a high pressure. In accelerated cooling, the cooling rate of the rolled material 8 is faster than that of normal water cooling. As a result, the crystal structure of the rolled material 8 is adjusted, so that the mechanical properties of the rolled material 8 change.
　その後、中間温度計６は、当該圧延材８の全長の初期温度をＭＴ実績値として計測する。その後、ＲＯＴ冷却装置３は、一定の圧力で注水することで当該圧延材８を冷却する。その後、巻取温度計７は、当該圧延材８の全長の初期温度をＣＴ実績値として計測する。その後、巻取コイラー４は、当該圧延材８を巻き取る。 After that, the intermediate thermometer 6 measures the initial temperature of the entire length of the rolled material 8 as the actual MT value. After that, the ROT cooling device 3 cools the rolled material 8 by injecting water at a constant pressure. After that, the take-up thermometer 7 measures the initial temperature of the entire length of the rolled material 8 as a CT actual value. After that, the take-up coiler 4 winds up the rolled material 8.
　温度制御装置９は、加速側計算部９ａとＲＯＴ側計算部９ｂと制御部９ｃとを備える。 The temperature control device 9 includes an acceleration side calculation unit 9a, a ROT side calculation unit 9b, and a control unit 9c.
　加速側計算部９ａは、温度モデルを用いて加速冷却装置２の各バンク２ａの出入側における圧延材８の温度を事前に予測する。ＲＯＴ側計算部９ｂは、温度モデルを用いてＲＯＴ冷却装置３の各バンク３ａの出入側における圧延材８の温度を事前に予測する。制御部９ｃは、加速側計算部９ａによる予測結果に基づいて加速冷却装置２の各注水バルブ２ｂの開閉を制御する。制御部９ｃは、ＲＯＴ側計算部９ｂによる予測結果に基づいてＲＯＴ冷却装置３の各注水バルブ３ｂの開閉を制御する。 The acceleration side calculation unit 9a predicts in advance the temperature of the rolled material 8 on the entrance / exit side of each bank 2a of the acceleration cooling device 2 using the temperature model. The ROT side calculation unit 9b predicts in advance the temperature of the rolled material 8 on the inlet / outlet side of each bank 3a of the ROT cooling device 3 using the temperature model. The control unit 9c controls the opening and closing of each water injection valve 2b of the acceleration cooling device 2 based on the prediction result by the acceleration side calculation unit 9a. The control unit 9c controls the opening and closing of each water injection valve 3b of the ROT cooling device 3 based on the prediction result by the ROT side calculation unit 9b.
　圧延材８が巻取コイラー４に巻き取られた後、加速側計算部９ａは、仕上圧延機出側温度計５からのＦＤＴ実績値と中間温度計６からのＭＴ実績値とに基づいて加速冷却装置２における温度モデルを学習する。ＲＯＴ側計算部９ｂは、中間温度計６からのＭＴ実績値と巻取温度計７からのＣＴ実績値とに基づいてＲＯＴ冷却装置３における温度モデルを学習する。 After the rolled material 8 is wound by the take-up coiler 4, the acceleration side calculation unit 9a accelerates based on the FDT actual value from the finish rolling mill output side thermometer 5 and the MT actual value from the intermediate thermometer 6. Learn the temperature model in the cooling device 2. The ROT side calculation unit 9b learns the temperature model in the ROT cooling device 3 based on the MT actual value from the intermediate thermometer 6 and the CT actual value from the take-up thermometer 7.
　具体的には、温度制御装置９は、各切板のＦＤＴ実績値を開始点として、最終的なＣＴ予測値がＣＴ目標値に到達するように、各切板の加速冷却装置２の各バンク２ａとＲＯＴ冷却装置３の各バンク３ａの入出側の温度予測計算を行う。温度制御装置９は、加速冷却装置２の各バンク２ａへの冷却水量の基準値（Ｖ１ ａｃｃ、Ｃ２ ａｃｃ、・・・Ｃｎ ａｃｃ）とＲＯＴ冷却装置３の各バンク３ａへの冷却水量の基準値（Ｖ１ ｒｏｔ、Ｃ２ ｒｏｔ、・・・Ｃｎ ｒｏｔ）とを決定する。 Specifically, the temperature control device 9 starts from the FDT actual value of each cutting plate, and each bank of the accelerated cooling device 2 of each cutting plate so that the final CT predicted value reaches the CT target value. The temperature prediction calculation of the inlet / outlet side of each bank 3a of 2a and the ROT cooling device 3 is performed. The temperature control device 9 has a reference value (V 1 acc , C 2 acc , ... C n acc ) of the amount of cooling water to each bank 2a of the accelerated cooling device 2 and the amount of cooling water to each bank 3a of the ROT cooling device 3. (V 1 rot , C 2 rot , ... C n rot ) is determined.
　各バンク２ａにおいては、当該基準値に基づいて開く注水バルブ２ｂの数を決定する。各バンク３ａにおいては、当該基準値に基づいて開く注水バルブ３ｂの数を決定する。 In each bank 2a, the number of water injection valves 2b to be opened is determined based on the reference value. In each bank 3a, the number of water injection valves 3b to be opened is determined based on the reference value.
　圧延材８の切板が中間温度計６の位置に達した際、温度制御装置９は、中間温度計６の位置による誤差が０になるように加速冷却装置２における温度モデルを学習する。圧延材８が巻取温度計７の位置に達した際、温度制御装置９は、巻取温度計７の位置による誤差が０になるようにＲＯＴ冷却装置３における温度モデルを学習する。この際、各切板の温度予測における初期温度はＭＴ実績値を初期値とする。 When the cut plate of the rolled material 8 reaches the position of the intermediate thermometer 6, the temperature control device 9 learns the temperature model in the acceleration cooling device 2 so that the error due to the position of the intermediate thermometer 6 becomes zero. When the rolled material 8 reaches the position of the take-up thermometer 7, the temperature control device 9 learns the temperature model in the ROT cooling device 3 so that the error due to the position of the take-up thermometer 7 becomes zero. At this time, the MT actual value is used as the initial value for the initial temperature in the temperature prediction of each cutting plate.
　次に、図２を用いて、温度モデルの考え方を説明する。
　図２は実施の形態１における熱間圧延ラインの温度制御装置が適用される切板の斜視図である。 Next, the concept of the temperature model will be described with reference to FIG.
FIG. 2 is a perspective view of a cutting plate to which the temperature control device for the hot rolling line according to the first embodiment is applied.
　図２に示されるように、圧延材８がＲＯＴ冷却装置３の直下においてローラーテーブル１０で搬送される際、熱の出入りは、圧延材８を一定長の切板８ａに分割した上で計算される。例えば、一定長は、３ｍから５ｍの間で設定される。 As shown in FIG. 2, when the rolled material 8 is conveyed by the roller table 10 directly under the ROT cooling device 3, the heat inflow and outflow is calculated after the rolled material 8 is divided into cutting plates 8a having a constant length. To. For example, the constant length is set between 3 m and 5 m.
　熱の出入りの要素としては、水冷熱伝達、放射、相変態よる発熱等が考えられる。例えば、水冷熱伝達のみが要素とされる場合、水冷による抜熱量（Ｗ）は、次の（１）式で表される。 As factors for heat in and out, water-cooled heat transfer, radiation, heat generation due to phase transformation, etc. can be considered. For example, when only water-cooled heat transfer is a factor, the amount of heat removed by water cooling (W) is expressed by the following equation (1).
Figure JPOXMLDOC01-appb-M000001
Figure JPOXMLDOC01-appb-M000001
　（１）式において、ｈｗは水冷熱伝達係数（Ｗ／ｍｍ２／℃）である。ｈｗは加速冷却装置２とＲＯＴ冷却装置３とで異なる。Ａｗは冷却水と接触する切板８ａの上下面の面積（ｍｍ２）である。Ａｗは各バンクにおいて開く注水バルブの数で変化する。Ｔｗは冷却水の温度（℃）である。Ｔｓｕｒｆは切板８ａの表面温度（℃）である。 In equation (1), h w is a water-cooled heat transfer coefficient (W / mm 2 / ° C.). h w is different between the acceleration cooling device 2 and the ROT cooling device 3. A w is the area (mm 2 ) of the upper and lower surfaces of the cutting plate 8a in contact with the cooling water. A w changes with the number of water injection valves opened in each bank. T w is the temperature (° C.) of the cooling water. T surf is the surface temperature (° C.) of the cutting plate 8a.
　この際、各切板８ａの温度変化は、次の（２）式で表される。 At this time, the temperature change of each cutting plate 8a is expressed by the following equation (2).
Figure JPOXMLDOC01-appb-M000002
Figure JPOXMLDOC01-appb-M000002
　（２）式において、Ｔは切板８ａの温度（℃）である。ρは切板８ａの密度（ｋｇ／ｍｍ３）である。ＣＰは切板８ａの比熱（Ｊ／ｋｇ／℃）である。ｌは切板８ａの進行方向長さ（ｍｍ）である。Ｂは切板８ａの幅（ｍｍ）である。Ｈは切板８ａの板厚（ｍｍ）である。ｔは時間（ｓ）である。ｉは切板８ａの番号である。 In equation (2), T is the temperature (° C.) of the cutting plate 8a. ρ is the density of the cutting plate 8a (kg / mm 3 ). C P is the specific heat of Setsuban 8a (J / kg / ℃) . l is the length (mm) of the cutting plate 8a in the traveling direction. B is the width (mm) of the cutting plate 8a. H is the plate thickness (mm) of the cutting plate 8a. t is the time (s). i is the number of the cutting plate 8a.
　次に、図３と図４とを用いて、温度モデルの学習を説明する。
　図３は実施の形態１における熱間圧延ラインの温度制御装置が適用される加速冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。図４は実施の形態１における熱間圧延ラインの温度制御装置が適用されるＲＯＴ冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。 Next, learning of the temperature model will be described with reference to FIGS. 3 and 4.
FIG. 3 is a diagram showing a predicted value and an actual value (re-predicted value) of a temperature change of each cutting plate inside the acceleration cooling device to which the temperature control device of the hot rolling line according to the first embodiment is applied. FIG. 4 is a diagram showing predicted values and actual values (repredicted values) of temperature changes of each cutting plate inside the ROT cooling device to which the temperature control device for the hot rolling line according to the first embodiment is applied.
　図３に示されるように、加速冷却装置２における冷却制御に関し、ＭＴ実績値に対して温度モデルの予測誤差があった場合、当該予測誤差の値を用いて各バンク２ａの入出側における予測値が再計算される。その結果、各バンク２ａの入出側における圧延材８の温度の実績値として確からしい値が求められる。 As shown in FIG. 3, regarding the cooling control in the accelerated cooling device 2, when there is a prediction error of the temperature model with respect to the actual MT value, the predicted value on the entry / exit side of each bank 2a is used using the value of the prediction error. Is recalculated. As a result, a probable value is obtained as the actual temperature value of the rolled material 8 on the inlet / outlet side of each bank 2a.
　図４に示されるように、ＲＯＴ冷却装置３における冷却制御に関し、ＣＴ実績値に対して温度モデルの予測誤差があった場合、当該予測誤差の値を用いて各バンク３ａの入出側における予測値が再計算される。その結果、各バンク３ａの入出側における圧延材８の温度の実績値として確からしい値が求められる。 As shown in FIG. 4, regarding the cooling control in the ROT cooling device 3, when there is a prediction error of the temperature model with respect to the actual CT value, the predicted value on the entry / exit side of each bank 3a is used using the value of the prediction error. Is recalculated. As a result, a probable value is obtained as the actual temperature value of the rolled material 8 on the inlet / outlet side of each bank 3a.
　次に、図５と図６とを用いて、圧延材８の巻き取り完了後の学習機能の概要を説明する。
　図５は実施の形態１における熱間圧延ラインの温度制御装置が適用される加速冷却装置での温度モデルの誤差学習の流れを示す図である。図６は実施の形態１における熱間圧延ラインの温度制御装置が適用されるＲＯＴ冷却装置での温度モデルの誤差学習の流れを示す図である。 Next, the outline of the learning function after the winding of the rolled material 8 is completed will be described with reference to FIGS. 5 and 6.
FIG. 5 is a diagram showing a flow of error learning of a temperature model in an accelerated cooling device to which the temperature control device for the hot rolling line according to the first embodiment is applied. FIG. 6 is a diagram showing a flow of error learning of a temperature model in a ROT cooling device to which a temperature control device for a hot rolling line according to the first embodiment is applied.
　図５において、次の（３）式に示されるように、加速冷却装置２の水冷熱伝達係数ｈｗ ａｃｃの学習値であるＺ１ ａｃｃとＺ２ ａｃｃとが自動調整される。 In FIG. 5, as shown in the following equation (3), Z 1 acc and Z 2 acc, which are learning values of the water-cooled heat transfer coefficient h w acc of the acceleration cooling device 2, are automatically adjusted.
Figure JPOXMLDOC01-appb-M000003
Figure JPOXMLDOC01-appb-M000003
　（３）式において、ｖａ ａｃｃ（ｍ／ｓ）は加速冷却装置２の内部での各切板８ａの平均速度である。ｖ０（ｍ／ｓ）は加速冷却装置２の内部での各切板８ａの基準速度である。ｆｗ ａｃｃはモデル予測関数である。Ｚ１ ａｃｃは温度モデルの予測値に対する乗算型の学習値である。Ｚ２ ａｃｃは速度比に対するべき乗型の学習値である。 (3) In the equation, v a acc (m / s ) is the average speed of each Setsuban 8a inside the accelerated cooling device 2. v 0 (m / s) is the reference speed of each cutting plate 8a inside the acceleration cooling device 2. f w acc is a model prediction function. Z 1 acc is a multiplication type learning value for the predicted value of the temperature model. Z 2 acc is a power-type learning value for the velocity ratio.
　圧延材８における冷却現象は、圧延材８が高速で移動するときと圧延材８が静止しているときとで異なる。このため、（３）式に示されるように、速度の影響は、学習項で調整される。 The cooling phenomenon in the rolled material 8 differs between when the rolled material 8 moves at high speed and when the rolled material 8 is stationary. Therefore, as shown in Eq. (3), the influence of speed is adjusted by the learning term.
　具体的には、圧延材８の全長の先端に近い部分であるＨｅａｄ部の特定の切板８ａのデータを用いて、当該切板８ａのＭＴ予測値の誤差が０になるようにＺ１ ａｃｃが求められる。この際、Ｚ２ ａｃｃは、０として扱われる。 Specifically, using the data of a specific cut plate 8a of the head portion which is a portion near the tip of the total length of the rolled material 8, Z 1 acc so that the error of the MT predicted value of the cut plate 8a becomes 0. Is required. At this time, Z 2 acc is treated as 0.
　圧延材８の加速中または加速後の部分であるＭｉｄｄｌｅ部の特定の切板８ａのデータを用いてＭＴ予測値の誤差が０になるようにＺ２ ａｃｃが求められる。この際、Ｚ１ ａｃｃは、Ｈｅａｄ部において求められた値が用いられる。 Z 2 acc is obtained so that the error of the MT predicted value becomes 0 by using the data of the specific cutting plate 8a of the Middle portion which is the portion of the rolled material 8 during or after acceleration. At this time, the value obtained in the Head portion is used for Z 1 acc .
　求められたＺ１ ａｃｃとＺ２ ａｃｃとが（３）式に代入されることで、全ての切板８ａの再予測値が計算される。Ｈｅａｄ部とＭｉｄｄｌｅ部との予測誤差を０にすることで、圧延材８の全長における精度が改善される。 By substituting the obtained Z 1 acc and Z 2 acc into the equation (3), the repredicted values of all the cutting plates 8a are calculated. By setting the prediction error between the head portion and the middle portion to 0, the accuracy of the total length of the rolled material 8 is improved.
　図６において、次の（４）式に示されるように、ＲＯＴ冷却装置３の水冷熱伝達係数ｈｗ ｒｏｔの学習値であるＺ１ ｒｏｔとＺ２ ｒｏｔとが自動調整される。 In FIG. 6, as shown in the following equation (4), Z 1 rot and Z 2 rot, which are learning values of the water-cooled heat transfer coefficient h w rot of the ROT cooling device 3, are automatically adjusted.
Figure JPOXMLDOC01-appb-M000004
Figure JPOXMLDOC01-appb-M000004
　（４）式において、ｖａ ｒｏｔ（ｍ／ｓ）はＲＯＴ冷却装置３の内部での各切板８ａの平均速度である。ｖ０（ｍ／ｓ）はＲＯＴ冷却装置３の内部での各切板８ａの基準速度である。ｆｗ ｒｏｔはモデル予測関数である。Ｚ１ ｒｏｔは温度モデルの予測値に対する乗算型の学習値である。Ｚ２ ｒｏｔは速度比に対するべき乗型の学習値である。 (4) In the formula, v a rot (m / s ) is the average speed of each Setsuban 8a inside the ROT cooling device 3. v 0 (m / s) is the reference speed of each cutting plate 8a inside the ROT cooling device 3. f w rot is a model prediction function. Z 1 rot is a learning value of a multiplication type with respect to the predicted value of the temperature model. Z 2 rot is a power-type learning value for the velocity ratio.
　圧延材８における冷却現象は、圧延材８が高速で移動するときと圧延材８が静止しているときとで異なる。このため、（４）式に示されるように、速度の影響は、学習項で調整される。 The cooling phenomenon in the rolled material 8 differs between when the rolled material 8 moves at high speed and when the rolled material 8 is stationary. Therefore, as shown in Eq. (4), the influence of speed is adjusted by the learning term.
　具体的には、圧延材８の全長の先端に近い部分であるＨｅａｄ部の特定の切板８ａのデータを用いて、当該切板８ａのＣＴ予測値の誤差が０になるようにＺ１ ｒｏｔが求められる。この際、Ｚ２ ｒｏｔは、０として扱われる。 Specifically, using the data of a specific cut plate 8a of the head portion which is a portion close to the tip of the total length of the rolled material 8, Z 1 rot so that the error of the CT prediction value of the cut plate 8a becomes 0. Is required. At this time, Z 2 lot is treated as 0.
　圧延材８の加速中または加速後の部分であるＭｉｄｄｌｅ部の特定の切板８ａのデータを用いてＣＴ予測値の誤差が０になるようにＺ２ ｒｏｔが求められる。この際、Ｚ１ ｒｏｔは、Ｈｅａｄ部において求められた値が用いられる。 Using the data of the specific cutting plate 8a of the Middle portion, which is the portion of the rolled material 8 during or after acceleration, the Z 2 rotor is obtained so that the error of the CT predicted value becomes 0. At this time, the value obtained in the head section is used for Z 1 rot .
　求められたＺ１ ｒｏｔとＺ２ ｒｏｔとが（４）式に代入されることで、全ての切板８ａの再予測値が計算される。Ｈｅａｄ部とＭｉｄｄｌｅ部との予測誤差を０にすることで、圧延材８の全長における精度が改善される。 By substituting the obtained Z 1 rot and Z 2 rot into the equation (4), the repredicted values of all the cutting plates 8a are calculated. By setting the prediction error between the head portion and the middle portion to 0, the accuracy of the total length of the rolled material 8 is improved.
　以上で説明した実施の形態１によれば、温度制御装置９は、加速冷却装置２とＲＯＴ冷却装置３とにおいて水冷熱伝達係数とを別々に設定する。このため、温度モデルの精度を高めることができる。 According to the first embodiment described above, the temperature control device 9 sets the water-cooled heat transfer coefficient separately in the acceleration cooling device 2 and the ROT cooling device 3. Therefore, the accuracy of the temperature model can be improved.
　また、温度制御装置９は、温度モデルによって予測した当該圧延材８の冷却後の温度の予測値と実際の温度の実測値との差に基づいて、当該圧延材８の温度の予測値を補正するための学習値を計算する。このため、温度モデルの精度をより高めることができる。 Further, the temperature control device 9 corrects the predicted value of the temperature of the rolled material 8 based on the difference between the predicted value of the cooled temperature of the rolled material 8 predicted by the temperature model and the measured value of the actual temperature. Calculate the learning value to do. Therefore, the accuracy of the temperature model can be further improved.
　また、温度制御装置９は、ＭＴ実績値に基づいて、当該圧延材８の温度の予測値を補正するための学習値を計算する。このため、温度モデルの精度をより高めることができる。 Further, the temperature control device 9 calculates a learning value for correcting the predicted value of the temperature of the rolled material 8 based on the actual MT value. Therefore, the accuracy of the temperature model can be further improved.
　なお、中間温度計６の周辺の注水バルブ２ｂを開くと、中間温度計６の直下において、冷却水が圧延材８の表面を覆った状態に維持され得る。このため、中間温度計６において、圧延材８の表面温度が正確に計測されない場合もある。この場合、中間温度計６に近いバンク２ａの全ての注水バルブ２ｂを全て閉じることで巻取温度計７の直下において、冷却水が圧延材８の表面を覆うことを抑制できる。その結果、中間温度計６において、圧延材８の表面温度を正確に計測することができる。中間温度計６に近いバンク２ａの全てのち注水バルブ２ｂの全てを閉じることが難しい場合は、中間温度計６により近い注水バルブ２ｂを優先的に閉じればよい。 When the water injection valve 2b around the intermediate thermometer 6 is opened, the cooling water can be maintained in a state of covering the surface of the rolled material 8 directly under the intermediate thermometer 6. Therefore, the surface temperature of the rolled material 8 may not be accurately measured by the intermediate thermometer 6. In this case, by closing all the water injection valves 2b of the bank 2a close to the intermediate thermometer 6, it is possible to prevent the cooling water from covering the surface of the rolled material 8 directly under the take-up thermometer 7. As a result, the surface temperature of the rolled material 8 can be accurately measured by the intermediate thermometer 6. If it is difficult to close all the water injection valves 2b of the bank 2a close to the intermediate thermometer 6, the water injection valve 2b closer to the intermediate thermometer 6 may be closed preferentially.
　次に、図７を用いて、温度制御装置９の例を説明する。
　図７は実施の形態１における熱間圧延ラインの温度制御装置のハードウェア構成図である。 Next, an example of the temperature control device 9 will be described with reference to FIG. 7.
FIG. 7 is a hardware configuration diagram of the temperature control device for the hot rolling line according to the first embodiment.
　温度制御装置９の各機能は、処理回路により実現し得る。例えば、処理回路は、少なくとも１つのプロセッサ１００ａと少なくとも１つのメモリ１００ｂとを備える。例えば、処理回路は、少なくとも１つの専用のハードウェア２００を備える。 Each function of the temperature control device 9 can be realized by a processing circuit. For example, the processing circuit includes at least one processor 100a and at least one memory 100b. For example, the processing circuit comprises at least one dedicated hardware 200.
　処理回路が少なくとも１つのプロセッサ１００ａと少なくとも１つのメモリ１００ｂとを備える場合、温度制御装置９の各機能は、ソフトウェア、ファームウェア、またはソフトウェアとファームウェアとの組み合わせで実現される。ソフトウェアおよびファームウェアの少なくとも一方は、プログラムとして記述される。ソフトウェアおよびファームウェアの少なくとも一方は、少なくとも１つのメモリ１００ｂに格納される。少なくとも１つのプロセッサ１００ａは、少なくとも１つのメモリ１００ｂに記憶されたプログラムを読み出して実行することにより、温度制御装置９の各機能を実現する。少なくとも１つのプロセッサ１００ａは、中央処理装置、処理装置、演算装置、マイクロプロセッサ、マイクロコンピュータ、ＤＳＰともいう。例えば、少なくとも１つのメモリ１００ｂは、ＲＡＭ、ＲＯＭ、フラッシュメモリ、ＥＰＲＯＭ、ＥＥＰＲＯＭ等の、不揮発性または揮発性の半導体メモリ、磁気ディスク、フレキシブルディスク、光ディスク、コンパクトディスク、ミニディスク、ＤＶＤ等である。 When the processing circuit includes at least one processor 100a and at least one memory 100b, each function of the temperature control device 9 is realized by software, firmware, or a combination of software and firmware. At least one of the software and firmware is written as a program. At least one of the software and firmware is stored in at least one memory 100b. At least one processor 100a realizes each function of the temperature control device 9 by reading and executing a program stored in at least one memory 100b. At least one processor 100a is also referred to as a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microcomputer, and a DSP. For example, at least one memory 100b is a non-volatile or volatile semiconductor memory such as RAM, ROM, flash memory, EPROM, EEPROM, magnetic disk, flexible disk, optical disk, compact disk, mini disk, DVD or the like.
　処理回路が少なくとも１つの専用のハードウェア２００を備える場合、処理回路は、例えば、単一回路、複合回路、プログラム化したプロセッサ、並列プログラム化したプロセッサ、ＡＳＩＣ、ＦＰＧＡ、またはこれらの組み合わせで実現される。例えば、温度制御装置９の各機能は、それぞれ処理回路で実現される。例えば、温度制御装置９の各機能は、まとめて処理回路で実現される。 If the processing circuit comprises at least one dedicated hardware 200, the processing circuit may be implemented, for example, as a single circuit, a composite circuit, a programmed processor, a parallel programmed processor, an ASIC, an FPGA, or a combination thereof. To. For example, each function of the temperature control device 9 is realized by a processing circuit. For example, each function of the temperature control device 9 is collectively realized by a processing circuit.
　温度制御装置９の各機能について、一部を専用のハードウェア２００で実現し、他部をソフトウェアまたはファームウェアで実現してもよい。例えば、制御部９ｃの機能については専用のハードウェア２００としての処理回路で実現し、制御部９ｃの機能以外の機能については少なくとも１つのプロセッサ１００ａが少なくとも１つのメモリ１００ｂに格納されたプログラムを読み出して実行することにより実現してもよい。 For each function of the temperature control device 9, a part may be realized by the dedicated hardware 200, and the other part may be realized by software or firmware. For example, the function of the control unit 9c is realized by a processing circuit as dedicated hardware 200, and for functions other than the function of the control unit 9c, at least one processor 100a reads a program stored in at least one memory 100b. It may be realized by executing.
　このように、処理回路は、ハードウェア２００、ソフトウェア、ファームウェア、またはこれらの組み合わせで温度制御装置９の各機能を実現する。 In this way, the processing circuit realizes each function of the temperature control device 9 with the hardware 200, software, firmware, or a combination thereof.
実施の形態２．
　図８は実施の形態２における熱間圧延ラインの温度制御装置が適用されるＲＯＴ冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。なお、実施の形態１の部分と同一又は相当部分には同一符号が付される。当該部分の説明は省略される。 Embodiment 2.
FIG. 8 is a diagram showing predicted values and actual values (repredicted values) of temperature changes of each cutting plate inside the ROT cooling device to which the temperature control device for the hot rolling line according to the second embodiment is applied. The same or corresponding parts as those of the first embodiment are designated by the same reference numerals. The explanation of the relevant part is omitted.
　図８に示されるように、実施の形態２においては、圧延材８の冷却中に、各切板８ａが中間温度計６の直下を通過した際、当該切板８ａのＭＴ予測値とＭＴ実績値との間において、温度モデルの予測誤差がある場合、ＲＯＴ冷却装置３の内部における開始点（ＭＴ）をＭＴ実績値に修正した上で、ＣＴ目標値に到達するようにＲＯＴ冷却装置３の内部における圧延材８の温度変化の予測値が再計算される。再計算された予測値が達成されるように、各バンク３ａへの冷却水量の基準値（Ｖ１ ｒｏｔ、Ｖ２ ｒｏｔ、・・・ＶＭ ｒｏｔ）が修正される。 As shown in FIG. 8, in the second embodiment, when each cutting plate 8a passes directly under the intermediate thermometer 6 during cooling of the rolled material 8, the MT predicted value and the MT actual result of the cutting plate 8a If there is a prediction error of the temperature model between the value and the value, the start point (MT) inside the ROT cooling device 3 is corrected to the actual MT value, and then the ROT cooling device 3 is used to reach the CT target value. The predicted value of the temperature change of the rolled material 8 inside is recalculated. The reference values (V 1 rot , V 2 rot , ... V M rot ) of the amount of cooling water to each bank 3a are corrected so that the recalculated predicted value is achieved.
　以上で説明した実施の形態２によれば、温度制御装置９は、中間温度計６による当該圧延材８の温度の実績値と温度の予測値との間に温度モデルの予測誤差があった場合に、当該誤差を補償するようにＲＯＴ冷却装置３の注水バルブ３ｂを制御する。このため、温度モデルの精度をより高めることができる。 According to the second embodiment described above, when the temperature control device 9 has a temperature model prediction error between the actual temperature value of the rolled material 8 and the predicted temperature value of the rolled material 8 by the intermediate thermometer 6. In addition, the water injection valve 3b of the ROT cooling device 3 is controlled so as to compensate for the error. Therefore, the accuracy of the temperature model can be further improved.
　また、温度制御装置９は、中間温度計６による当該圧延材８の温度実績値と温度予測値との間に温度モデルの誤差があった場合に、中間温度計６による当該圧延材８の温度の実績値を初期値としてＲＯＴ冷却装置３の内部における当該圧延材８の温度変化の予測値を再計算する。このため、温度モデルの精度をより高めることができる。 Further, the temperature control device 9 uses the intermediate thermometer 6 to measure the temperature of the rolled material 8 when there is an error in the temperature model between the actual temperature value of the rolled material 8 and the predicted temperature value. The predicted value of the temperature change of the rolled material 8 inside the ROT cooling device 3 is recalculated with the actual value of the above as the initial value. Therefore, the accuracy of the temperature model can be further improved.
実施の形態３．
　図９は実施の形態３における熱間圧延ラインの温度制御装置が適用される加速冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。図１０は実施の形態１における熱間圧延ラインの温度制御装置が適用されるＲＯＴ冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。なお、実施の形態１の部分と同一又は相当部分には同一符号が付される。当該部分の説明は省略される。 Embodiment 3.
FIG. 9 is a diagram showing predicted values and actual values (repredicted values) of temperature changes of each cutting plate inside the accelerated cooling device to which the temperature control device for the hot rolling line according to the third embodiment is applied. FIG. 10 is a diagram showing a predicted value and an actual value (repredicted value) of a temperature change of each cutting plate inside the ROT cooling device to which the temperature control device of the hot rolling line according to the first embodiment is applied. The same or corresponding parts as those of the first embodiment are designated by the same reference numerals. The explanation of the relevant part is omitted.
　実施の形態３においては、加速冷却装置２とＲＯＴ冷却装置３とを単体のみで用いる冷却効率の同定実験が事前に行われる。各切板８ａのＦＤＴ実績値からＣＴ実績値を引いた値である温度降下の実績値（℃）と開いた注水バルブの本数の実績とに基づいて、加速冷却装置２とＲＯＴ冷却装置３とのバルブ一本当たりの冷却効率（℃／ｖａｌｖｅ）が計算される。この際の圧延材８の速度パターンは、通常の圧延と同様である。 In the third embodiment, an experiment for identifying the cooling efficiency using the acceleration cooling device 2 and the ROT cooling device 3 alone is performed in advance. Based on the actual temperature drop value (° C), which is the value obtained by subtracting the CT actual value from the FDT actual value of each cutting plate 8a, and the actual number of open water injection valves, the acceleration cooling device 2 and the ROT cooling device 3 The cooling efficiency (° C / valve) per valve is calculated. The speed pattern of the rolled material 8 at this time is the same as that of normal rolling.
　ここで、加速冷却装置２の冷却効率をａ（ｋ）（℃／ｖａｌｖｅ）とする。ＲＯＴ冷却装置３の冷却効率をｂ（ｋ）（℃／ｖａｌｖｅ）とする。加速冷却装置２で使用した注水バルブ２ｂの数をＡ（ｋ）（ｖａｌｖｅ）とする。ＲＯＴ冷却装置３で使用した注水バルブ３ｂの数をＢ（ｋ）（ｖａｌｖｅ）とする。ｋは切板８ａの番号である。 Here, the cooling efficiency of the acceleration cooling device 2 is a (k) (° C./valve). Let the cooling efficiency of the ROT cooling device 3 be b (k) (° C./valve). Let the number of water injection valves 2b used in the acceleration cooling device 2 be A (k) (valve). Let the number of water injection valves 3b used in the ROT cooling device 3 be B (k) (valve). k is the number of the cutting plate 8a.
　この場合、加速冷却装置２の温度降下予測値は、ａ（ｋ）×Ａ（ｋ）（℃）である。ＲＯＴ冷却装置３の温度降下予測値は、ｂ（ｋ）×Ｂ（ｋ）（℃）である。 In this case, the predicted temperature drop value of the accelerated cooling device 2 is a (k) × A (k) (° C.). The predicted temperature drop value of the ROT cooling device 3 is b (k) × B (k) (° C.).
　各切板８ａに対する加速冷却装置２による温度降下実績は、次の（５）式により計算される。 The actual temperature drop by the acceleration cooling device 2 for each cutting plate 8a is calculated by the following equation (5).
Figure JPOXMLDOC01-appb-M000005
Figure JPOXMLDOC01-appb-M000005
　各切板８ａに対するＲＯＴ冷却装置３による温度降下実績は、次の（６）式により計算される。 The actual temperature drop by the ROT cooling device 3 for each cutting plate 8a is calculated by the following equation (6).
Figure JPOXMLDOC01-appb-M000006
Figure JPOXMLDOC01-appb-M000006
　加速冷却装置２に関しては、図９に示されるように、ＦＤＴ実績値から（５）式に示す値を引いた値をＭＴ実績値として各バンク２ａの入出側における予測値が再計算される。 Regarding the accelerated cooling device 2, as shown in FIG. 9, the predicted value on the entry / exit side of each bank 2a is recalculated with the value obtained by subtracting the value shown in the equation (5) from the FDT actual value as the MT actual value.
　ＲＯＴ冷却装置３に関しては、図１０に示されるように、ＭＴ実績値を初期値として、当該初期値から（６）式に示す値引いた値をＣＴ実績値として各バンク３ａの入出側における予測値が再計算される。 Regarding the ROT cooling device 3, as shown in FIG. 10, the MT actual value is used as the initial value, and the value obtained by subtracting the value shown in Eq. (6) from the initial value is used as the CT actual value for prediction on the entry / exit side of each bank 3a. The value is recalculated.
　以上で説明した実施の形態３によれば、温度制御装置９は、加速冷却装置２を単体で使用する同定実験により得られた冷却効率と加速冷却装置２とＲＯＴ冷却装置３との上流側から下流側への当該圧延材８の温度降下の実績値と加速冷却装置２において使用されたスプレーの本数から１バルブあたりの冷却効率を計算する。温度制御装置９は、ＲＯＴ冷却装置３を単体で使用する同定実験により得られた冷却効率と加速冷却装置２とＲＯＴ冷却装置３との上流側から下流側への当該圧延材８の温度降下の実績値とＲＯＴ冷却装置３において使用されたスプレーの本数から１バルブあたりの冷却効率を計算する。このため、温度モデルの精度をより高めることができる。 According to the third embodiment described above, the temperature control device 9 has the cooling efficiency obtained by the identification experiment using the accelerated cooling device 2 alone, and the cooling efficiency obtained from the upstream side of the accelerated cooling device 2 and the ROT cooling device 3. The cooling efficiency per valve is calculated from the actual value of the temperature drop of the rolled material 8 to the downstream side and the number of sprays used in the accelerated cooling device 2. The temperature control device 9 has the cooling efficiency obtained by the identification experiment using the ROT cooling device 3 alone and the temperature drop of the rolled material 8 from the upstream side to the downstream side of the accelerated cooling device 2 and the ROT cooling device 3. The cooling efficiency per valve is calculated from the actual value and the number of sprays used in the ROT cooling device 3. Therefore, the accuracy of the temperature model can be further improved.
　なお、温度制御装置９は、加速冷却装置２とＲＯＴ冷却装置３との比を用いて、加速冷却装置２の冷却効率とＲＯＴ冷却装置３と冷却効率とを計算してもよい。この場合も、温度モデルの精度をより高めることができる。 Note that the temperature control device 9 may calculate the cooling efficiency of the accelerated cooling device 2 and the cooling efficiency of the ROT cooling device 3 and the cooling efficiency by using the ratio of the accelerated cooling device 2 and the ROT cooling device 3. In this case as well, the accuracy of the temperature model can be further improved.
実施の形態４．
　図１１は実施の形態４における熱間圧延ラインの温度制御装置が適用される加速冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。図１２は実施の形態４における熱間圧延ラインの温度制御装置が適用されるＲＯＴ冷却装置の内部での各切板の温度変化の予測値と実績値（再予測値）を示す図である。なお、実施の形態１の部分と同一又は相当部分には同一符号が付される。当該部分の説明は省略される。 Embodiment 4.
FIG. 11 is a diagram showing a predicted value and an actual value (re-predicted value) of a temperature change of each cutting plate inside the acceleration cooling device to which the temperature control device of the hot rolling line according to the fourth embodiment is applied. FIG. 12 is a diagram showing predicted values and actual values (re-predicted values) of temperature changes of each cutting plate inside the ROT cooling device to which the temperature control device for the hot rolling line according to the fourth embodiment is applied. The same or corresponding parts as those of the first embodiment are designated by the same reference numerals. The explanation of the relevant part is omitted.
　実施の形態４においては、加速冷却装置２とＲＯＴ冷却装置３とを単体のみで用いる冷却効率の同定実験が事前に行われる。各切板８ａのＦＤＴ実績値からＣＴ実績値を引いた値を温度降下の実績値（℃）と開いたバルブのスプレー流量（ｍ３／ｈ）の実績とに基づいて、加速冷却装置２とＲＯＴ冷却装置３とのバルブ一本当たりの冷却効率（℃／ｍ３／ｈ）が計算される。この際の圧延材８の速度パターンは、通常の圧延と同様である。 In the fourth embodiment, an experiment for identifying the cooling efficiency using the acceleration cooling device 2 and the ROT cooling device 3 alone is performed in advance. Based on the actual value of temperature drop (° C.) and the actual value of the spray flow rate of the opened valve (m 3 / h), the value obtained by subtracting the actual CT value from the actual FDT value of each cutting plate 8a is combined with the acceleration cooling device 2. cooling efficiency per one valve between the ROT cooling device 3 (℃ / m 3 / h ) is calculated. The speed pattern of the rolled material 8 at this time is the same as that of normal rolling.
　ここで、加速冷却装置２の冷却効率をα（ｋ）（℃／ｍ３／ｈ）とする。ＲＯＴ冷却装置３の冷却効率をβ（ｋ）（℃／ｍ３／ｈ）とする。加速冷却装置２で使用した注水バルブ２ｂの数をＡ（ｋ）（ｖａｌｖｅ）とする。ＲＯＴ冷却装置３で使用した注水バルブ３ｂの数をＢ（ｋ）（ｖａｌｖｅ）とする。加速冷却装置２における１注水バルブ２ｂあたりのスプレー流量をＰａ（ｍ３／ｈ／ｖａｌｖｅ）とする。ＲＯＴ冷却装置３における１注水バルブ３ｂあたりのスプレー流量をＰｂ（ｍ３／ｈ／ｖａｌｖｅ）とする。 Here, the cooling efficiency of the accelerated cooling device 2 and α (k) (℃ / m 3 / h). The cooling efficiency of the ROT cooling device 3 and β (k) (℃ / m 3 / h). Let the number of water injection valves 2b used in the acceleration cooling device 2 be A (k) (valve). Let the number of water injection valves 3b used in the ROT cooling device 3 be B (k) (valve). Let Pa (m 3 / h / valve) be the spray flow rate per water injection valve 2b in the acceleration cooling device 2. Let P b (m 3 / h / valve) be the spray flow rate per water injection valve 3 b in the ROT cooling device 3.
　この場合、加速冷却装置２の温度降下予測値は、α（ｋ）×Ａ（ｋ）×Ｐａ（℃）である。ＲＯＴ冷却装置３の温度降下予測値は、β（ｋ）×Ｂ（ｋ）×Ｐｂ（℃）である。 In this case, the temperature drop predicted value of accelerated cooling device 2 is a α (k) × A (k ) × P a (℃). The predicted temperature drop value of the ROT cooling device 3 is β (k) × B (k) × P b (° C.).
　各切板８ａに対する加速冷却装置２による温度降下実績は、次の（７）式により計算される。 The actual temperature drop by the acceleration cooling device 2 for each cutting plate 8a is calculated by the following equation (7).
Figure JPOXMLDOC01-appb-M000007
Figure JPOXMLDOC01-appb-M000007
　各切板８ａに対するＲＯＴ冷却装置３による温度降下実績は、次の（８）式により計算される。 The actual temperature drop by the ROT cooling device 3 for each cutting plate 8a is calculated by the following equation (8).
Figure JPOXMLDOC01-appb-M000008
Figure JPOXMLDOC01-appb-M000008
　加速冷却装置２に関しては、図１１に示されるように、ＦＤＴ実績値から（７）式に示す値を引いた値をＭＴ実績値として各バンク２ａの入出側における予測値が再計算される。 Regarding the accelerated cooling device 2, as shown in FIG. 11, the predicted value on the entry / exit side of each bank 2a is recalculated with the value obtained by subtracting the value shown in the equation (7) from the FDT actual value as the MT actual value.
　ＲＯＴ冷却装置３に関しては、図１２に示されるように、ＭＴ実績値を初期値として、当該初期値から（８）式に示す値引いた値をＣＴ実績値として各バンク３ａの入出側における予測値が再計算される。 Regarding the ROT cooling device 3, as shown in FIG. 12, the MT actual value is used as the initial value, and the value obtained by subtracting the value shown in Eq. (8) from the initial value is used as the CT actual value for prediction on the entry / exit side of each bank 3a. The value is recalculated.
　以上で説明した実施の形態４によれば、温度制御装置９は、加速冷却装置２を単体で使用する同定実験により得られた冷却効率と加速冷却装置２とＲＯＴ冷却装置３との上流側から下流側への当該圧延材８の温度降下の実績値と加速冷却装置２において使用されたスプレー流量の体積から１バルブあたりの冷却効率を計算する。温度制御装置９は、ＲＯＴ冷却装置３を単体で使用する同定実験により得られた冷却効率と加速冷却装置２とＲＯＴ冷却装置３との上流側から下流側への当該圧延材８の温度降下の実績値とＲＯＴ冷却装置３において使用されたスプレー流量の体積から１バルブあたりの冷却効率を計算する。このため、温度モデルの精度をより高めることができる。 According to the fourth embodiment described above, the temperature control device 9 has the cooling efficiency obtained by the identification experiment using the accelerated cooling device 2 alone, and the cooling efficiency obtained from the upstream side of the accelerated cooling device 2 and the ROT cooling device 3. The cooling efficiency per valve is calculated from the actual value of the temperature drop of the rolled material 8 to the downstream side and the volume of the spray flow rate used in the accelerated cooling device 2. The temperature control device 9 has the cooling efficiency obtained by the identification experiment using the ROT cooling device 3 alone and the temperature drop of the rolled material 8 from the upstream side to the downstream side of the accelerated cooling device 2 and the ROT cooling device 3. The cooling efficiency per valve is calculated from the actual value and the volume of the spray flow rate used in the ROT cooling device 3. Therefore, the accuracy of the temperature model can be further improved.
　なお、ＲＯＴ冷却装置３の下流側に加速冷却装置２が設けられた熱間圧延ラインに対し、実施の形態１から実施の形態４のいずれかの温度制御装置９を適用してもよい。この場合も、温度モデルの精度を高めることができる。 Note that the temperature control device 9 of any of the first to fourth embodiments may be applied to the hot rolling line provided with the acceleration cooling device 2 on the downstream side of the ROT cooling device 3. In this case as well, the accuracy of the temperature model can be improved.
　以上のように、この発明に係る熱間圧延ラインの温度制御装置は、熱間圧延システムに利用できる。 As described above, the temperature control device for the hot rolling line according to the present invention can be used for the hot rolling system.
　１　仕上圧延機、　２　加速冷却装置、　２ａ　バンク、　２ｂ　注水バルブ、　２ｃ　ノズル、　３　ＲＯＴ冷却装置、　３ａ　バンク、　３ｂ　注水バルブ、　３ｃ　ノズル、　４　巻取コイラー、　５　仕上圧延機出側温度計、　６　中間温度計、　７　巻取温度計、　８　圧延材、８ａ　切板、　９　温度制御装置、　９ａ　加速側計算部、　９ｂ　ＲＯＴ側計算部、　９ｃ　制御部、　１０　ローラーテーブル、　１００ａ　プロセッサ、　１００ｂ　メモリ、　２００　ハードウェア 1 Finishing rolling mill, 2 Acceleration cooling device, 2a bank, 2b water injection valve, 2c nozzle, 3 ROT cooling device, 3a bank, 3b water injection valve, 3c nozzle, 4 winding coiler, 5 Finishing rolling mill outlet thermometer, 6 Intermediate thermometer, 7 winding thermometer, 8 rolled material, 8a cutting plate, 9 temperature control device, 9a acceleration side calculation unit, 9b ROT side calculation unit, 9c control unit, 10 roller table, 100a processor, 100b memory, 200 hardware

Claims (9)

  1. 　熱間圧延ラインの下流工程において、圧延材に注水するＲＯＴ冷却装置に対し、当該圧延材の温度を予測する温度モデルにおいて、水冷冷却における単位面積あたりの抜熱量を表すＲＯＴ側水冷熱伝達係数を用いて当該圧延材の温度の予測値を計算するＲＯＴ側計算部と、
    　前記熱間圧延ラインの下流工程において、前記ＲＯＴ冷却装置の上流側または下流側に設けられ、前記ＲＯＴ冷却装置とは異なる条件で当該圧延材に注水する加速冷却装置に対し、当該圧延材の温度を予測する温度モデルにおいて、水冷冷却における単位面積あたりの抜熱量を表す加速側水冷熱伝達係数として前記ＲＯＴ側計算部により設定されたＲＯＴ側水冷熱伝達係数とは別に設定された値を用いて当該圧延材の温度の予測値を計算する加速側計算部と、
    を備えた熱間圧延ラインの温度制御装置。     In the downstream process of the hot rolling line, for the ROT cooling device that injects water into the rolled material, in the temperature model that predicts the temperature of the rolled material, the ROT side water-cooled heat transfer coefficient, which represents the amount of heat removed per unit area in water-cooled cooling, is calculated. ROT side calculation unit that calculates the predicted value of the temperature of the rolled material using
    In the downstream process of the hot rolling line, the temperature of the rolled material is relative to the accelerated cooling device provided on the upstream side or the downstream side of the ROT cooling device and injecting water into the rolled material under conditions different from those of the ROT cooling device. In the temperature model for predicting, the value set separately from the ROT side water-cooled heat transfer coefficient set by the ROT side calculation unit is used as the acceleration side water-cooled heat transfer coefficient representing the amount of heat removed per unit area in water-cooled cooling. The acceleration side calculation unit that calculates the predicted value of the temperature of the rolled material, and
    A temperature control device for hot rolling lines equipped with.
  2. 　前記ＲＯＴ側計算部と前記加速側計算部とは、温度モデルによって予測した当該圧延材の冷却後の温度の予測値と実際の温度の実測値との差に基づいて、当該圧延材の温度の予測値を補正するための学習値を計算する請求項１に記載の熱間圧延ラインの温度制御装置。 The ROT side calculation unit and the acceleration side calculation unit determine the temperature of the rolled material based on the difference between the predicted value of the temperature of the rolled material after cooling predicted by the temperature model and the measured value of the actual temperature. The temperature control device for a hot rolling line according to claim 1, wherein a learning value for correcting a predicted value is calculated.
  3. 　前記ＲＯＴ側計算部と前記加速側計算部とは、前記ＲＯＴ冷却装置と前記加速冷却装置との間に設けられた中間温度計による当該圧延材の温度の実績値に基づいて、当該圧延材の温度の予測値を補正するための学習値を計算する請求項２に記載の熱間圧延ラインの温度制御装置。 The ROT side calculation unit and the acceleration side calculation unit of the rolled material are based on the actual temperature value of the rolled material by an intermediate thermometer provided between the ROT cooling device and the accelerated cooling device. The temperature control device for a hot rolling line according to claim 2, wherein a learning value for correcting a predicted temperature value is calculated.
  4. 　前記ＲＯＴ冷却装置と前記加速冷却装置とに対し、前記中間温度計の周辺のバルブを閉じる制御部、
    を備えた請求項３に記載の熱間圧延ラインの温度制御装置。     A control unit that closes a valve around the intermediate thermometer with respect to the ROT cooling device and the accelerated cooling device.
    The temperature control device for a hot rolling line according to claim 3.
  5. 　前記制御部は、前記中間温度計による当該圧延材の温度の実績値と温度の予測値との間に温度モデルの誤差があった場合に、当該誤差を補償するように前記ＲＯＴ冷却装置のバルブを制御する請求項４に記載の熱間圧延ラインの温度制御装置。 When there is an error in the temperature model between the actual temperature value of the rolled material and the predicted temperature value by the intermediate thermometer, the control unit is a valve of the ROT cooling device so as to compensate for the error. The temperature control device for a hot rolling line according to claim 4.
  6. 　前記ＲＯＴ側計算部は、前記中間温度計による当該圧延材の温度の実績値と温度の予測値との間に温度モデルの誤差があった場合に、前記中間温度計による当該圧延材の温度の実績値を初期値として前記ＲＯＴ冷却装置の内部における当該圧延材の温度変化の予測値を再計算する請求項４に記載の熱間圧延ラインの温度制御装置。 The ROT side calculation unit determines the temperature of the rolled material by the intermediate thermometer when there is an error in the temperature model between the actual temperature value of the rolled material by the intermediate thermometer and the predicted temperature value. The temperature control device for a hot rolling line according to claim 4, wherein the predicted value of the temperature change of the rolled material inside the ROT cooling device is recalculated with the actual value as the initial value.
  7. 　前記ＲＯＴ側計算部は、前記ＲＯＴ冷却装置を単体で使用する同定実験により得られた冷却効率と前記ＲＯＴ冷却装置と前記加速冷却装置との上流側から下流側への当該圧延材の温度降下の実績値と前記ＲＯＴ冷却装置において使用されたスプレーの本数から１バルブあたりの冷却効率を計算し、
    　前記加速側計算部は、前記加速冷却装置を単体で使用する同定実験により得られた冷却効率と前記ＲＯＴ冷却装置と前記加速冷却装置との上流側から下流側への当該圧延材の温度降下の実績値と前記加速冷却装置において使用されたスプレーの本数から１バルブあたりの冷却効率を計算する請求項１または請求項２に記載の熱間圧延ラインの温度制御装置。     The ROT side calculation unit determines the cooling efficiency obtained by the identification experiment using the ROT cooling device alone and the temperature drop of the rolled material from the upstream side to the downstream side of the ROT cooling device and the accelerated cooling device. The cooling efficiency per valve was calculated from the actual value and the number of sprays used in the ROT cooling device.
    The acceleration side calculation unit determines the cooling efficiency obtained by the identification experiment using the acceleration cooling device alone and the temperature drop of the rolled material from the upstream side to the downstream side of the ROT cooling device and the acceleration cooling device. The temperature control device for a hot rolling line according to claim 1 or 2, wherein the cooling efficiency per valve is calculated from the actual value and the number of sprays used in the accelerated cooling device.
  8. 　前記ＲＯＴ側計算部は、前記ＲＯＴ冷却装置と前記加速冷却装置との冷却効率の比を用いて前記ＲＯＴ冷却装置と前記加速冷却装置との上流側から下流側への当該圧延材の温度降下の実績値と前記ＲＯＴ冷却装置において使用されたスプレーの本数からＲＯＴ側水冷熱伝達係数の実績値と学習値とを計算し、
    　前記加速側計算部は、前記ＲＯＴ冷却装置と前記加速冷却装置との冷却効率の比を用いて前記ＲＯＴ冷却装置と前記加速冷却装置との上流側から下流側への当該圧延材の温度降下の実績値と前記加速冷却装置において使用されたスプレーの本数から加速側水冷熱伝達係数の実績値と学習値とを計算する請求項７に記載の熱間圧延ラインの温度制御装置。     The ROT side calculation unit uses the ratio of the cooling efficiencies of the ROT cooling device and the accelerated cooling device to determine the temperature drop of the rolled material from the upstream side to the downstream side of the ROT cooling device and the accelerated cooling device. The actual value and the learning value of the ROT side water-cooled heat transfer coefficient are calculated from the actual value and the number of sprays used in the ROT cooling device.
    The acceleration side calculation unit uses the ratio of the cooling efficiencies of the ROT cooling device and the acceleration cooling device to determine the temperature drop of the rolled material from the upstream side to the downstream side of the ROT cooling device and the acceleration cooling device. The temperature control device for a hot rolling line according to claim 7, wherein the actual value and the learning value of the acceleration side water-cooled heat transfer coefficient are calculated from the actual value and the number of sprays used in the acceleration cooling device.
  9. 　前記ＲＯＴ側計算部は、前記ＲＯＴ冷却装置を単体で使用する同定実験により得られた冷却効率と前記ＲＯＴ冷却装置と前記加速冷却装置との上流側から下流側への当該圧延材の温度降下の実績値と前記ＲＯＴ冷却装置において使用されたスプレー流量の体積から１バルブあたりの冷却効率を計算し、
    　前記加速側計算部は、前記加速冷却装置を単体で使用する同定実験により得られた冷却効率と前記ＲＯＴ冷却装置と前記加速冷却装置との上流側から下流側への当該圧延材の温度降下の実績値と前記加速冷却装置において使用されたスプレー流量の体積から１バルブあたりの冷却効率を計算する請求項７に記載の熱間圧延ラインの温度制御装置。     The ROT side calculation unit determines the cooling efficiency obtained by the identification experiment using the ROT cooling device alone and the temperature drop of the rolled material from the upstream side to the downstream side of the ROT cooling device and the accelerated cooling device. The cooling efficiency per valve was calculated from the actual value and the volume of the spray flow rate used in the ROT cooling device.
    The acceleration side calculation unit determines the cooling efficiency obtained by the identification experiment using the acceleration cooling device alone and the temperature drop of the rolled material from the upstream side to the downstream side of the ROT cooling device and the acceleration cooling device. The temperature control device for a hot rolling line according to claim 7, wherein the cooling efficiency per valve is calculated from the actual value and the volume of the spray flow rate used in the accelerated cooling device.
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