EP3623068B1 - Dispositifs d'application de tunnels de refroidissement à l'aide d'un second embranchement - Google Patents

Dispositifs d'application de tunnels de refroidissement à l'aide d'un second embranchement Download PDF

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Publication number
EP3623068B1
EP3623068B1 EP18193920.8A EP18193920A EP3623068B1 EP 3623068 B1 EP3623068 B1 EP 3623068B1 EP 18193920 A EP18193920 A EP 18193920A EP 3623068 B1 EP3623068 B1 EP 3623068B1
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EP
European Patent Office
Prior art keywords
flow
control device
cooling section
control valve
control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP18193920.8A
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German (de)
English (en)
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EP3623068A1 (fr
Inventor
Klaus Weinzierl
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Primetals Technologies Germany GmbH
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Primetals Technologies Germany GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by Primetals Technologies Germany GmbH filed Critical Primetals Technologies Germany GmbH
Priority to EP18193920.8A priority Critical patent/EP3623068B1/fr
Priority to CN201980059890.4A priority patent/CN112654441B/zh
Priority to PCT/EP2019/070427 priority patent/WO2020052854A1/fr
Priority to US17/274,212 priority patent/US11779976B2/en
Publication of EP3623068A1 publication Critical patent/EP3623068A1/fr
Application granted granted Critical
Publication of EP3623068B1 publication Critical patent/EP3623068B1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/74—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
    • B21B45/0203—Cooling
    • B21B45/0209—Cooling devices, e.g. using gaseous coolants
    • B21B45/0215—Cooling devices, e.g. using gaseous coolants using liquid coolants, e.g. for sections, for tubes
    • B21B45/0218—Cooling devices, e.g. using gaseous coolants using liquid coolants, e.g. for sections, for tubes for strips, sheets, or plates
    • 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

Definitions

  • the present invention is also based on a control device for a cooling section, which is arranged within a rolling train or upstream or downstream of the rolling train and by means of which a hot rolled metal is cooled, the control device for a number of application devices of the cooling section being dynamic determines the respective target control state for a respective control valve arranged in a respective supply line and controls the respective control valve accordingly, so that a respective buffer area of the respective application device corresponds to the activation of the respective control valve a respective base flow of a liquid, water-based coolant is supplied by the control device via the respective supply line.
  • the present invention is further based on a computer program that includes machine code that can be processed by a software-programmable control device for a cooling section, the processing of the machine code by the control device causing the control device to set the respective target control state for the according to the procedure just explained determines the respective control valve and controls the respective control valve accordingly.
  • a metallic rolling stock is cooled after rolling.
  • the rolling stock can consist of steel or aluminum, for example. Depending on requirements, it can be a flat rolled product (strip or heavy plate), a rod-shaped rolled product or a profile.
  • Exact temperature control in the cooling section is customary in order to set the desired material properties and keep them constant with a lower degree of variation.
  • several spray bars are installed along the cooling section, by means of which a liquid coolant, usually water, is applied to the rolling stock from above and / or from below to cool the hot rolling stock.
  • the amount of water flowing through the respective spray bar should be adjustable as quickly and as precisely as possible.
  • switching valves or control valves can only be controlled in a purely binary manner. So are either fully open or fully closed.
  • Control valves can be adjusted continuously so that the amount of water supplied to the respective spray bar can also be continuously adjusted.
  • valves In the case of control valves, the valves can be designed as control flaps or ball valves.
  • Control dampers are relatively simple and inexpensive. However, they can only be operated with relatively small pressure differences of usually a maximum of 1 bar. Otherwise cavitations will occur, which will damage the control valve very quickly. Control flaps are therefore not particularly suitable for intensive cooling.
  • Ball valves do not have a flap, but a pierced ball that is rotated in a pipe. Depending on the rotational position of the ball, a larger or smaller cross-section is made available to the coolant for the flow. Ball valves can be operated with higher pressure differences of up to approx. 3 bar. Hysteresis does not occur with them or is negligibly small. However, ball valves are expensive.
  • the coolant is continuously fed to the spray boom.
  • there is a controllable deflection plate Depending on the position of the baffle plate, the coolant is either fed to the rolling stock or flows off to the side without contributing to the cooling of the rolling stock.
  • quick switching operations are possible without pressure surges.
  • the full coolant flow has to be pumped permanently.
  • valves and also the baffle plates require appropriate actuators. Pneumatically driven servomotors are common. Position control is also required for control valves. This continuously compares the actual position of the respective control valve with its target position and readjusts the actual position until there is sufficient agreement with the target position.
  • the coolant can, for example, be taken from an elevated tank or transported via a larger pipeline from a pump station further away. Combinations of these approaches are also possible.
  • intensive cooling the water is often first taken from a high tank. The pressure is then increased via booster pumps in increased to a variable extent and thus made available with a correspondingly variable pressure of the intensive cooling.
  • the intensive cooling is provided with several spray bars to which the coolant is fed individually via a respective supply line, starting from the booster pumps. Ball valves are arranged in the supply lines, which are controlled to adjust the amount of coolant supplied to the respective spray bar.
  • the object of the present invention is to create possibilities by means of which a cooling section with superior operating properties can be implemented in a simple and reliable manner.
  • the respective active device can be operated with a significantly higher dynamic than a control valve with a corresponding design. It is therefore possible to use control valves in the supply lines to the application devices - as in the prior art - and to control them accordingly. Despite the relatively long delay times when adjusting the setting of the control valves However, due to the higher dynamics of the active devices, the cooling flows can still be set with a relatively short delay time and thus with high dynamics.
  • the pressure in the buffer area of the respective application device can be briefly increased or decreased depending on the activation state of the respective active device.
  • more coolant briefly flows out of the respective buffer area as the respective cooling flow than is supplied to the respective buffer area as the respective base flow. It is the other way around when the pressure is reduced. On average over time, however, the cooling flow and the base flow correspond to one another.
  • the respective active device is designed as a pair of air valves, one of which is connected to a pressure reservoir and the environment.
  • this configuration which is possible in principle, is not preferred. Rather, it is preferred that the respective active device is a device that actively promotes the further medium.
  • the further medium can in particular be air or water.
  • the device actively conveying the further medium is a fan, an air pump or a turbine.
  • the device actively conveying the further medium is a pump.
  • the further medium can be taken from a respective storage device.
  • the additional medium can be air or water.
  • the further medium in the respective storage device is not under a respective pressure. This is possible in particular when the further medium is water and there is an air cushion in the upper area of the respective storage device, which is via an opening is in connection with the environment, so that, as required, air can flow into the respective storage device or can flow out of the respective storage device. Alternatively, it is possible for the further medium in the respective storage device to be under a respective pressure. As a result, in particular the adjustment range that has to be handled by the active device can be kept small.
  • the respective pressure is preferably set in the respective storage device via a respective control line connected to the respective storage device.
  • This makes it possible, in every static operating state of the respective application device, to set the pressure in the respective storage device in such a way that the respective active device has to consume as little energy as possible for the highly dynamic setting of the respective cooling flow.
  • the respective pressure in the respective storage device it is possible for the respective pressure in the respective storage device to be tracked as a function of the setpoint current or a respective pressure prevailing in the respective buffer area. In this case it is even possible to set every static operating state of the respective application device without the respective active device having to consume energy to maintain this state.
  • control device having the features of claim 8.
  • Advantageous refinements of the control device are the subject matter of the dependent claims 9 to 11.
  • the control device preferably sets the respective pressure in the respective storage device via a respective control line connected to the respective storage device. This makes it possible to reduce the energy consumption of the respective active device in every static operating state of the respective application device. This is particularly true when the control device tracks the pressure in the respective storage device as a function of the setpoint current or a pressure prevailing in the respective buffer area. In this case, the energy consumption can ideally even be reduced to zero.
  • the control device is preferably designed as a software-programmable device that is programmed with a computer program that includes machine code that can be processed by the control device.
  • the processing of the machine code by the control device causes the corresponding determination of the respective target control state for the respective control valve and the respective further Target control state for the respective active device and the corresponding control of the respective control valve and the respective active device.
  • the object is also achieved by a computer program with the features of claim 12.
  • the processing of the computer program by a software-programmable control device of the type mentioned causes the control device to determine the respective target control state for the respective control valve and the respective further target control state for the respective active device and the respective control valve and the respective active device controls accordingly.
  • a hot rolling stock 1 made of metal is to be cooled in a cooling section 2.
  • the cooling section 2 is according to FIG 1 downstream of a rolling mill. Is shown in FIG 1 only one roll stand 3 of the rolling train, namely the last roll stand 3 of the rolling train. As a rule, however, the rolling train has a plurality of rolling stands 3 through which the hot rolling stock 1 traverses sequentially one after the other. In the case of the arrangement according to FIG 1 the hot rolling stock 1 enters the cooling section 2 immediately after rolling in the last roll stand 3 of the rolling train. A time interval between the rolling in the last roll stand 3 of the rolling train and the entry into the cooling section 2 is generally in the range of a few seconds.
  • the cooling section 2 could be as shown in FIG FIG 2 be upstream of the rolling mill. Is shown in FIG 2 likewise only a single roll stand 4 of the rolling train, namely the first roll stand 4 of the rolling train.
  • the hot rolling stock 1 is rolled immediately after leaving the cooling section 2 in the first roll stand 4 of the rolling train.
  • a time interval between the cooling in the cooling section 2 and the rolling in the first roll stand 4 of the rolling train is often in the range of a few minutes. But it can also be just a few seconds.
  • the cooling section 2 could be as shown in FIG FIG 3 be arranged within the rolling train. Are shown in FIG 3 two roll stands 5 of the rolling train. In this case, the cooling takes place in the cooling section 2 between the rolling in the two roll stands 5 of the rolling train. A time interval between the cooling in the cooling section 2 and the rolling in the two successive rolling stands 5 of the rolling train is in the range of a few seconds. As shown in FIG 3 the cooling section 2 is arranged between two successive roll stands 5 of the rolling train. It could, however, also extend over a larger area, so that the cooling section 2 passes through at least one in FIG 3 not shown further roll stand is divided into a corresponding number of sections.
  • the rolling stock 1 consists of metal.
  • the rolling stock 1 can consist of steel or aluminum. Other metals are also possible.
  • a temperature of the rolling stock 1 in front of the cooling section 2 is generally between 750 ° C. and 1,200 ° C.
  • cooling to a lower temperature takes place.
  • the lower temperature is only slightly below the temperature in front of the cooling section 2.
  • the rolling stock 1 is generally cooled to a significantly lower temperature, for example to a temperature between 200 ° C. and 700 ° C.
  • the hot rolling stock 1 is fed to the cooling section 2 in a horizontal transport direction x.
  • the hot rolling stock 1 does not change its transport direction x. It is therefore also transported horizontally within the cooling section 2.
  • the rolling stock 1 can either maintain or change its transport direction. If the hot rolling stock 1 is a strip, it can, for example, be deflected obliquely downwards in order to feed it to a reel. Furthermore, it is possible for the hot rolling stock 1 to reverse its transport direction x (reverse), to run through the cooling section 2 again and then to be rolled again. This is possible with both heavy plate and a pre-slab.
  • the cooling section 2 has a number of application devices 6.
  • a coolant 7 is applied to the rolling stock 1 by means of the application devices 6. As shown in the FIGS. 1 to 3 the coolant 7 is applied to the rolling stock 1 from above. However, it could also be applied from below and / or from the side, both alternatively and additionally.
  • the coolant 7 is water. If necessary, small amounts of additives (maximum 1 percent to 2%) can be added to the water. In any case, however, the coolant 7 is a liquid, water-based coolant.
  • the application devices 6 can be designed, for example, as conventional spray bars.
  • At least one single application device 6 is present. In many cases, however, several application devices 6 are present.
  • the application devices 6 can according to the representation in FIG FIG 1 be arranged one behind the other. In this case, the application devices 6 apply their respective portion of the coolant 7 sequentially one after the other to the rolling stock 1.
  • the term “sequentially one after the other” relates in this context to a specific section of the rolling stock 1, since this runs sequentially one after the other through regions in which the individual application devices 6 each have their respective share of the coolant 7 apply the corresponding section of the rolling stock 1.
  • the number of application devices 6 is often in the two-digit, sometimes even in the upper two-digit range, in rare cases also in the three-digit range.
  • a sequential arrangement one behind the other is generally implemented in particular when the cooling section 2 is arranged downstream of the rolling train. But it can also be given in other cases.
  • the application devices 6 are connected via a respective supply line 8 to a reservoir 9 of the coolant 7 (or another source for the coolant 7).
  • the reservoir 9 is the same for all application devices 6.
  • several reservoirs 9 independent of one another could also be present.
  • a respective control valve 10 is arranged in each supply line 8.
  • the control valves 10 can in principle be arranged at any desired points within the supply lines 8. In practice, however, it is advantageous if the control valves 10 are arranged as close as possible to the application devices 6. If necessary, one or more pumps 11 can be arranged upstream of the control valves 10. The mode of operation of the pump 11 or the pumps 11 is not the subject of the present invention.
  • the application device 6 is supplied with a base flow F1 of the coolant 7 from the reservoir 9 via the supply line 8 and the control valve 10.
  • the base current F1 has the unit m 3 / s on.
  • the supply line 8 is connected to a buffer area 12 of the application device 6.
  • the base current F1 is first fed to the buffer area 12 of the application device 6.
  • the application device 6 can be shown in FIG FIG 4 be designed as a spray bar which has a certain storage volume, the storage volume being filled to a variable extent with the coolant 7 and otherwise with air.
  • a cooling flow F is applied to the hot rolling stock 1 by means of the application device 6.
  • a distance between the application device 6 - for example spray nozzles - from the rolling stock 1 is generally between 20 cm and 200 cm.
  • the cooling section 2 is controlled by a control device 13.
  • the control device 13 is designed as a software-programmable control device.
  • the control device 13 is programmed with a computer program 14.
  • the computer program 14 comprises machine code 15 which can be processed directly by the control device 13.
  • the processing of the machine code 15 by the control device 13 causes the control device 13 to carry out an operating method for the cooling section 2, as will be explained in more detail below.
  • the control device 13 dynamically determines a setpoint control state S1 * for the control valve 10. It controls the control valve 10 accordingly. By activating the control valve 10 in accordance with the determined target control state S1 *, the control device 13 sets the base current F1, which is fed to the application device 6 via the supply line 8 and the control valve 10.
  • the control device 13 of the cooling section 2 is aware of a setpoint current F * which is to be applied to the hot rolling stock 1 by means of the application device 6.
  • the target current F * is usually not constant over time, but rather variable, that is to say a function of time. It is possible for the control device 13 to set the target control state S1 * for the control valve 10 as a function determined from the setpoint current F * of the coolant 7. In this case, the control device 13 can determine the control state S1 *, for example, in such a way that in every operating state the base current F1 flowing through the control valve 10 is always as close as possible to the setpoint current F *. Then the operation of the control valve 10 corresponds to the operation of the prior art. However, other approaches are also possible. This will be discussed later.
  • an active device 16 is assigned to the buffer area 12.
  • the active device 16 is connected to the buffer area 12 via a further supply line 17.
  • the term “active device” means that the control device 13 controls the active device 16 in accordance with a setpoint control state S2 * and that the active device 16 reacts accordingly.
  • the control device 13 also dynamically determines the further target control state S2 * and controls the active device 16 accordingly.
  • the setpoint control state S2 * for the active device 16 is referred to below to distinguish it from the setpoint control state S1 * for the control valve 10 as a further setpoint control state S2 *.
  • the active device 16 feeds an additional flow F2 of a further medium 18 to the buffer area 12 via the further supply line 17.
  • the additional flow F2 has the unit m 3 / s - analogously to the base flow base flow F1. It can be positive or negative. It is therefore alternatively possible to supply the further medium 18 to the buffer area 12 or to withdraw it from the buffer area 12. Whether the additional current F2 is positive or negative depends on the further target control state S2 *. Regardless of the specific value of the additional flow F2 and also regardless of the type of further medium 18, the cooling flow F depends not only on the base flow F1 flowing through the control valve 10, but also on the additional flow F2 flowing through the active device 16.
  • the present invention is based on the principle that the control device 13 adjusts the additional flow F2 by the corresponding activation of the active device 16 in such a way that the cooling flow F is always as close as possible to the setpoint flow F *.
  • the control device 13 In order to be able to determine the further target control state S2 *, the control device 13 must know various values. On the one hand, this is the target current F *.
  • the target current F * can be preset to the control device 13, for example, or it can be determined by the control device 13 on the basis of other data - for example the temperature or the enthalpy of a certain section of the rolling stock 1 in conjunction with a desired temperature or enthalpy curve. If, as in the case of the design according to FIG 4 if the additional medium 18 is air, the control device 13 must know a nominal current F0 and an associated nominal pressure p0.
  • the nominal current F0 is the amount of coolant 7 which is applied per unit of time from the buffer area 12 to the hot rolling stock 1 when the nominal pressure p0 prevails in the buffer area 12.
  • the values F0, p0 can be determined in advance, for example, by a one-off measurement.
  • the nominal current F0 is the amount of coolant 7 which is applied per unit of time from the buffer area 12 to the hot rolling stock 1 when the nominal pressure p0 prevails in the buffer area 12.
  • the control device 13 thus controls the active device 16 in such a way that it causes the pressure p in the buffer area 12.
  • the active device 16 is preferably a device actively conveying the further medium 18, for example a turbine.
  • the turbine is driven by an electric drive.
  • the drive can be converter-controlled. Such controls are generally known to those skilled in the art and therefore do not need to be explained in more detail.
  • An electric drive can typically be accelerated from 0 to maximum speed with a time constant of 0.1 s and, conversely, also decelerated from maximum speed to 0 with a time constant of 0.1 seconds.
  • the active device 16 can thus be controlled with high dynamics. Driving through the full setting range (for example from 0 to maximum speed) can typically take place in a time window of less than 0.2 s. Often only 0.1 s or less are required.
  • the cooling flow F can thus be adapted with this short time constant, although the control valve 10 has only relatively low dynamics, for example a time constant of 1.5 s. During this period, the base current F1 deviates from the desired target current F * . In the case of the cooling flow F, however, this time delay is not noticeable because the pressure p in the buffer area 12 can be set in a highly dynamic manner by means of the turbine as required.
  • the additional current F2 can be positive or negative. If it is positive, the turbine pumps air into the buffer area 12, so that the pressure p in the buffer area 12 is increased. If it is negative, the turbine sucks air out of the buffer area 12, so that the pressure p in the buffer area 12 is reduced.
  • the cooling flow F does not depend directly on the base flow F1, but rather on the pressure p in the buffer area 12. It only has to be ensured that there is any coolant 7 in the buffer area 12 that can be applied to the hot rolling stock 1.
  • the base current F1 does not have to follow the target current F * directly. It only has to be set in such a way that the buffer area 12 neither becomes empty nor overflows. For this it is like before mentioned, possible to determine the target control state S1 * as in the prior art also as a function of the target current F *. Alternatively, it is possible, for example, to determine a fill level of the storage area 12 and to regulate it to a specific setpoint value.
  • the setpoint can be constant or vary as required. In this case, the level can be measured directly or indirectly, for example. An indirect measurement is possible, for example, using pressure measurement cells, by means of which the weight of the application device 6 is recorded.
  • the fill level can also be determined with the aid of a model based on the base flow F1 and the cooling flow F.
  • the difference between the base current F1 and the cooling current F corresponds to the change in the level at any point in time. By integrating this difference over time, starting from a known initial fill level, the current fill level can be determined at any time.
  • the base flow F1 can be measured, for example, and the cooling flow F can be determined on the basis of the easily measurable pressure p.
  • the control device 13 can proceed as follows, for example:
  • the buffer area 12 has a total volume V.
  • the buffer area 12 is partially filled with the coolant 7, the rest with air.
  • the pressure p prevails in the air volume V2.
  • the same pressure p also prevails in the coolant 7.
  • the base current F1 flows into the buffer area 12 via the control valve 10 and the supply line 8.
  • FR is a reference flow of the coolant 7 which flows when the control valve 10 is fully open when the pressure difference between the inlet side of the control valve 10 and the buffer area 12 is equal to the nominal pressure p0.
  • the value FR can be determined in advance, for example, by a one-off measurement.
  • p1 is the pressure on the inlet side of the control valve 10.
  • the characteristic curve f as such can be known in advance. As a rule, it is recorded once in advance by the manufacturer of the control valve 10 and can then be taken from the data sheet of the control valve 10.
  • Equation (1) p ⁇ p ⁇ M. + p ⁇ p p 0 ⁇ F. 0 - p 1 - p p 0 ⁇ FR ⁇ ⁇ x
  • the control device 13 also knows the characteristic curve K of the turbine.
  • the characteristic curve K relates the speed n of the turbine, the pressure difference ⁇ p on the inlet side and the outlet side of the turbine and the amount of air conveyed per unit of time, i.e. the time derivative of the amount of air M, with one another. If two of the three variables speed n of the turbine are specified - pressure difference ⁇ p - time derivative of the air quantity M, the third variable in each case is determined on the basis of the characteristic curve K.
  • the characteristic curve K can be determined, for example, by measurement or on the basis of a data sheet from the manufacturer of the turbine.
  • a function can therefore be specified by means of which the associated speed n of the turbine can be determined for a given pressure difference ⁇ p and a given time derivative of the air quantity M.
  • the required pressure difference ⁇ p results directly from the desired target current F *.
  • the additional flow F2 is also determined.
  • n K p , p ⁇ p ⁇ M. + p ⁇ p p 0 ⁇ F. 0 - p 1 - p p 0 ⁇ FR ⁇ ⁇ x
  • This equation is exclusively dependent on the pressure p in the buffer area 12, the position x of the control valve 10, the instantaneous amount of air M and the time derivative of the pressure p in the buffer area 12.
  • the other quantities are just constant parameters.
  • the amount of air M is a state variable that can easily be determined by means of an observer. All that is required is to solve equation (7) with a suitable initial value.
  • the setting of the speed of the turbine is possible with an accuracy of 1% and better with a time constant of 0.2 s and better.
  • the controller can - for example - be designed as a P controller, as a PI controller or as a state controller, all with or without precontrol. Implementation as a two-point controller is also possible.
  • the active device 16 When designing according to FIG 4 the active device 16 simply removes the air from the environment or releases it to the environment. Alternatively, it is as shown in FIG 5 possible that the active device 16 takes the air from a storage device 19 and releases it into the storage device 19. Otherwise, the design of FIG 5 with the design of FIG 4 match.
  • the design of FIG 5 points to the design of FIG 4 has the advantage that the air in the storage device 19 can be under a pressure p '.
  • the pressure p ' is preferably selected such that it is between 0 and a maximum pressure, the maximum pressure being the pressure at which the application device 6 operates at a maximum.
  • the pressure p ' it is possible for the pressure p 'to be approximately constant. In this case, the pressure p 'should be approximately half the maximum pressure. If the storage device 19 is dimensioned smaller, the pressure p 'in the storage device 19 decreases in accordance with the amount of air removed and increases again in accordance with the amount of air supplied. This can definitely be advantageous, since an increase in pressure in the storage device 19 counteracts an excessive reduction in the air volume V2 in the buffer area 12 and vice versa.
  • control device 13 it is as shown in FIG 5 It is possible for the control device 13 to set the pressure p ′ via a control line 20 which is connected to the storage device 19.
  • the control device 13 can in particular track the pressure p ′ as a function of the setpoint current F * or the pressure p.
  • the control device 13 can control valves 21, 22 with corresponding control signals S3 *, S4 *, so that - depending on the control of the valves 21, 22 - compressed air is supplied to the storage device 19 as required or air is released from the storage device 19 into the environment .
  • n K p - p ′ , p ⁇ p ⁇ M. + p ⁇ p p 0 ⁇ F. 0 - p 1 - p p 0 ⁇ FR ⁇ ⁇ x
  • FIG 5 offers compared to the design of FIG 4 various advantages.
  • the turbine is always operated in a clean air environment.
  • the Energy consumption of the turbine can be reduced by adjusting the pressure p 'as required. This can be useful in particular when the cooling flow F and thus the required pressure p in the buffer area 12 remains constant for a long time or at least remains essentially constant.
  • FIG 4 and 5 The design of the FIG 4 and 5 is particularly useful with a laminar cooling section. In principle, however, it can also be implemented with intensive cooling.
  • the design of FIG 6 corresponds over long distances with that of FIG 5 .
  • the active device 16 is preferably a device actively promoting the further medium 18.
  • the further medium 18 is not air but water (or generally the coolant 7).
  • the active device 16 is therefore a pump.
  • the pump is - analogous to the turbine of the FIG 4 and 5 - driven by an electric drive.
  • the drive can be converter-controlled.
  • An electric drive can typically be accelerated from 0 to maximum speed with a time constant of 0.1 s and, conversely, also decelerated from maximum speed to 0 with a time constant of 0.1 seconds.
  • the pump can be used to supply additional water to the buffer area 12 in a highly dynamic manner in addition to the base current F1 supplied via the supply line 8, or a part of the base current F1 supplied via the supply line 8 to the buffer area 12 can be removed.
  • the cooling flow F results directly from the sum of the base flow F1 and the additional flow F2, where the latter can be positive or negative depending on the control of the pump.
  • the control device 13 inputs the pressure p 'via a control line 20 connected to the storage device 19. Compressed air is preferably supplied to the storage device 19 via the control line 20, or air is discharged from the storage device 19.
  • the control device 13 can control the pressure p 'as in the embodiment according to FIG FIG 5 track as a function of the pressure p.
  • the control device 13 can determine the target control state S2 * for the pump, for example, as follows: As before, according to equation (1), the pressure p can be determined which is required so that the cooling flow F is equal to the setpoint flow F *.
  • FIG 6 is particularly useful for intensive cooling. In principle, however, it can also be implemented with a laminar cooling section.
  • the target current F * of the control device 13 is specified directly and immediately.
  • the control device 11 knows the thermodynamic energy state H of the rolling stock 1 immediately before it reaches the application device 6.
  • the thermodynamic Energy state H can in particular be the enthalpy or the temperature of a respective section of the rolling stock 1.
  • the control device 13 first determines the target current F * as a function of the thermodynamic energy state H and then based on the target current F * at least the associated target control state S2 *, possibly also the associated target control state S1 *.
  • the control device 13 can be given a local or temporal setpoint profile of the thermodynamic energy state H, which should be maintained if possible.
  • the control device 13 can therefore determine which thermodynamic energy state H should be present immediately after the application device 6.
  • the control device 13 can therefore determine which amount of coolant 7 has to be applied to the corresponding section of the rolling stock 1 so that the actual thermodynamic energy state H immediately behind the application device 6 reaches the desired target state corresponds as well as possible.
  • the required amount of coolant 7 then defines the target current F * in connection with the time which the corresponding section of the rolling stock 1 needs to pass through the application device 6.
  • thermodynamic energy state H of the corresponding section of the rolling stock 1 varies from application device 6 to application device 6. In particular, it is changed by each of application devices 6.
  • the thermodynamic energy state H of the control device 13 can be specified as such.
  • a temperature measuring station 23 can be arranged on the input side of the cooling section 2, by means of which the temperature or, in general, the energy state H is recorded for the individual sections of the rolling stock 1. The recorded energy state H is then assigned to the respective section.
  • Path tracking is implemented for each section during its passage through the cooling section 2.
  • the control device 13 takes into account in particular the thermodynamic energy state H immediately before the immediately preceding application device 6 and the amount of coolant 7 which the immediately preceding application device 6 applies to the rolling stock 1.
  • the control device 13 can alternatively take into account the setpoint flow F * or the cooling flow F of the immediately preceding application device 6. It thus sequentially determines the thermodynamic energy state H of the rolling stock 1 for the application devices 6 one after the other. If necessary, the control device 13 can apply and iteratively solve a heat conduction equation and a phase conversion equation in this context.
  • the rolling stock 1 is a flat rolling stock, for example a strip or a heavy plate.
  • the liquid coolant 7 can be applied to the rolling stock 1 from both sides by means of each individual application device 6.
  • This procedure is often taken in the case of a cooling section 2 which is arranged upstream of the rolling train or is arranged in the rolling train. But it can also be taken when the cooling section 2 is arranged downstream of the rolling train.
  • the cooling section 2 is arranged downstream of the rolling train, the liquid coolant 7 is usually applied to the rolling stock 1 from only one side, in particular from above or below, by means of each individual application device 6.
  • the application devices 6 each have only a single spray nozzle.
  • the application devices 6 each have a plurality of spray nozzles.
  • the spray nozzles can be arranged one behind the other as seen in the transport direction x of the rolling stock 1.
  • the spray nozzles can for example be arranged one behind the other within a single spray bar.
  • a plurality of spray bars arranged one behind the other in the transport direction x can also be combined to form one (1) application device 6. This applies regardless of whether the respective spray bar as such has several spray nozzles arranged one behind the other or not.
  • the application devices 6 can furthermore have a plurality of spray nozzles which are arranged next to one another as seen transversely to the transport direction x of the rolling stock 1.
  • a configuration can be useful in particular in the case of a flat rolled stock 1, that is to say in the case of a strip or a heavy plate.
  • the application devices 6 can extend over the full width of the rolling stock 1.
  • several application devices 6 are arranged next to one another, each of which is supplied with coolant 7 via its own supply line 8 and its own control valve 10.
  • the present invention has many advantages.
  • a highly dynamic setting of the cooling flows F is possible.
  • Switching off the cooling flow F is possible in the range of a few tenths of a second (often less than 0.2 s, sometimes even less than 0.1 s). The same applies when the cooling flow F is started up.
  • the drives for the active devices 16 can be controlled very precisely.
  • a usual accuracy of the speed n is in the range of 0.1%.
  • the cooling flow F for the respective application device 6 can also be set with the same or a similar accuracy.
  • the "air version” ( FIG 4 and 5 ) typically requires a turbine with an output of around 2 kW each.
  • the "water version” ( FIG 6 ) used. The power required for the pump is typically around 25 kW.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
  • Metal Rolling (AREA)
  • Control Of Temperature (AREA)

Claims (17)

  1. Procédé de fonctionnement pour une section de refroidissement (2) qui est disposée à l'intérieur d'un train de laminoir ou en amont ou en aval du train de laminoir et au moyen de laquelle un produit à laminer chaud (1) en métal est refroidi,
    - dans lequel un dispositif de commande (13) de la section de refroidissement (2) détermine de manière dynamique un état de pilotage de consigne (S1*) respectif pour une vanne de régulation (10) respective disposée dans une conduite d'alimentation (8) respective et pilote en conséquence la vanne de régulation (10) respective,
    - dans lequel un flux de base (F1) respectif d'un agent de refroidissement (7) fluide à base d'eau est amené à une pluralité de dispositifs d'application (6) de la section de refroidissement (2) par le biais de la conduite d'alimentation (8) respective conformément au pilotage de la vanne de régulation (10) respective par le dispositif de commande (13),
    - dans lequel la conduite d'alimentation (8) respective amène le flux de base (F1) respectif à une zone tampon (12) respective du dispositif d'application (6) respectif, à partir de laquelle un flux de refroidissement (F) respectif de l'agent de refroidissement (7) est appliqué sur le produit à laminer chaud (1) au moyen du dispositif d'application (6) respectif,
    caractérisé
    - en ce que le dispositif de commande (13) détermine en plus de manière dynamique un autre état de pilotage de consigne (S2*) respectif pour un dispositif actif (16) respectif et pilote en conséquence le dispositif actif (16),
    - en ce que le dispositif actif (16) respectif amène à la zone tampon (12) respective un flux supplémentaire (F2) respectif d'un autre milieu (18) par le biais d'une autre conduite d'alimentation (17) respective conformément au pilotage du dispositif actif (16) respectif par le dispositif de commande (13),
    - en ce que le flux de refroidissement (F) respectif dépend autant du flux de base (F1) respectif passant à travers la vanne de régulation (10) respective que du flux supplémentaire (F2) respectif s'écoulant par le biais du dispositif actif (16) respectif,
    - en ce que le flux supplémentaire (F2) respectif est positif ou négatif en fonction de l'autre état de pilotage (S2*) respectif du dispositif actif (16) respectif, et
    - en ce que le dispositif de commande (13) règle le flux supplémentaire (F2) respectif grâce au pilotage correspondant du dispositif actif (16) respectif, de façon que le flux de refroidissement (F) respectif soit à chaque instant aussi proche que possible d'un flux de consigne (F*) respectif de l'agent de refroidissement (7) devant être appliqué sur le produit à laminer chaud (1) au moyen du dispositif d'application (6) respectif.
  2. Procédé de fonctionnement selon la revendication 1,
    caractérisé en ce que le dispositif actif (16) respectif est un dispositif qui refoule activement l'autre milieu (18).
  3. Procédé de fonctionnement selon la revendication 2,
    caractérisé en ce que l'autre milieu (18) est de l'air ou de l'eau.
  4. Procédé de fonctionnement selon la revendication 1, 2 ou 3, caractérisé en ce que l'autre milieu (18) est soutiré d'un dispositif de stockage (19) respectif.
  5. Procédé de fonctionnement selon la revendication 4,
    caractérisé en ce que l'autre milieu (18) est soumis à une pression (p') respective dans le dispositif de stockage (19) respectif.
  6. Procédé de fonctionnement selon la revendication 5,
    caractérisé en ce que la pression (p') respective dans le dispositif de stockage (19) respectif est réglée par le biais d'une ligne de commande (20) respective reliée au dispositif de stockage (19) respectif.
  7. Procédé de fonctionnement selon la revendication 5 ou 6,
    caractérisé en ce que la pression respective (p') dans le dispositif de stockage (19) respectif est asservie en fonction du flux de consigne (F*) ou d'une pression (p) respective régnant dans la zone tampon (12) respective.
  8. Dispositif de commande pour une section de refroidissement (2) qui est disposée à l'intérieur d'un train de laminoir ou en amont ou en aval du train de laminoir et au moyen de laquelle un produit à laminer chaud (1) en métal est refroidi, dans lequel le dispositif de commande détermine de manière dynamique pour une pluralité de dispositifs d'application (6) de la section de refroidissement (2) un état de pilotage de consigne (S1*) respectif pour une vanne de régulation (10) respective disposée dans une conduite d'alimentation (8) respective et pilote en conséquence la vanne de régulation (10) respective, de façon qu'un flux de base (F1) respectif d'un agent de refroidissement (7) fluide à base d'eau soit amené à une zone tampon (12) respective du dispositif d'application (6) respectif par le biais de la conduite d'alimentation (8) respective conformément au pilotage de la vanne de régulation (10) respective par le dispositif de commande (13),
    caractérisé
    - en ce que le dispositif de commande détermine en plus de manière dynamique un autre état de pilotage de consigne (S2*) respectif pour un dispositif actif (16) respectif et pilote en conséquence le dispositif actif (16) respectif, de façon que le dispositif actif (16) respectif amène à la zone tampon (12) respective un flux supplémentaire (F2) respectif d'un autre milieu (18) par le biais d'une autre conduite d'alimentation (17) respective conformément au pilotage du dispositif actif (16) respectif par le dispositif de commande (13),
    de façon qu'un flux de refroidissement (F) respectif de l'agent de refroidissement (7) sortant de la zone tampon (12) respective et appliqué sur le produit à laminer chaud (1) au moyen du dispositif d'application (6) respectif dépende autant du flux de base (F1) respectif passant à travers la vanne de régulation (10) respective que du flux supplémentaire (F2) respectif s'écoulant par le biais du dispositif actif (16) respectif, et
    - en ce que le dispositif de commande règle le flux supplémentaire (F2) respectif sur des valeurs positives et négatives, de façon que le flux de refroidissement (F) respectif soit à chaque instant aussi proche que possible d'un flux de consigne (F*) respectif devant être appliqué sur le produit à laminer chaud (1) au moyen du dispositif d'application (6) respectif.
  9. Dispositif de commande selon la revendication 8,
    caractérisé en ce que l'autre milieu (18) est soutiré d'un dispositif de stockage (19) respectif, en ce que l'autre milieu (18) est soumis à une pression (p') respective dans le dispositif de stockage (19) respectif et en ce que le dispositif de commande règle la pression (p') respective dans le dispositif de stockage (19) respectif par le biais d'une ligne de commande (20) respective reliée au dispositif de stockage (19) respectif.
  10. Dispositif de commande selon la revendication 9,
    caractérisé en ce que le dispositif de commande asservit la pression (p') dans le dispositif de stockage (19) respectif en fonction du flux de consigne (F*) ou d'une pression (p) régnant dans la zone tampon (12) respective.
  11. Dispositif de commande selon la revendication 8, 9 ou 10, caractérisé en ce que le dispositif de commande est conçu en tant que dispositif programmable par logiciel, lequel est programmé à l'aide d'un programme d'ordinateur (14) qui comprend un code machine (15) qui peut être traité par le dispositif de commande, et en ce que le traitement du code machine (15) par le dispositif de commande provoque la détermination correspondante de l'état de pilotage de consigne (S1*) respectif pour la vanne de régulation (10) respective et de l'autre état de pilotage de consigne (S2*) respectif pour le dispositif actif (16) respectif ainsi que le pilotage correspondant de la vanne de régulation (10) respective et du dispositif actif (16) respectif.
  12. Programme d'ordinateur, qui comprend un code machine (15) qui peut être traité par un dispositif de commande (13) programmable par logiciel pour une section de refroidissement, dans lequel le traitement du code machine (15) par le dispositif de commande (13) a pour effet que le dispositif de commande (13) détermine l'état de pilotage de consigne (S1*) respectif pour la vanne de régulation (10) respective et l'autre état de pilotage de consigne (S2*) respectif pour le dispositif actif (16) respectif et pilote en conséquence la vanne de régulation (10) respective et le dispositif actif (16) respectif, conformément à la revendication 8.
  13. Section de refroidissement,
    - dans laquelle la section de refroidissement est disposée à l'intérieur d'un train de laminoir ou en amont ou en aval du train de laminoir,
    - dans laquelle la section de refroidissement comprend une pluralité de dispositifs d'application (6) qui sont reliés par une conduite d'alimentation (8) respective à une source (9) d'agent de refroidissement (7) fluide à base d'eau,
    - dans laquelle une vanne de régulation (10) respective est disposée dans la conduite d'alimentation (8) respective,
    - dans laquelle les dispositifs d'application (6) comprennent une zone tampon (12) respective qui est reliée à la conduite d'alimentation (8) respective, de façon que la conduite d'alimentation (8) respective amène à la zone tampon (12) respective du dispositif d'application (6) respectif un flux de base (F1) respectif de l'agent de refroidissement (7) et qu'un flux de refroidissement (F) respectif de l'agent de refroidissement (7) soit appliqué sur le produit à laminer chaud (1) à partir de la zone tampon (12) respective au moyen du dispositif d'application (6) respectif,
    - dans laquelle la section de refroidissement comprend un dispositif de commande (13) qui commande la vanne de régulation (10) respective,
    caractérisée
    - en ce qu'un dispositif actif (16) respectif est associé à la zone tampon (12) respective, lequel dispositif permet d'amener à la zone tampon (12) un flux supplémentaire (F2) d'un autre milieu (18) par le biais d'une autre conduite d'alimentation (17), de façon que le flux de refroidissement (F) respectif dépende autant du flux de base (F1) passant à travers la vanne de régulation (10) respective que du flux supplémentaire (F2) respectif s'écoulant par le biais du dispositif actif (16) respectif, et
    - en ce que la section de refroidissement comprend un dispositif de commande (13) selon l'une des revendications 8 à 11 qui commande non seulement la vanne de régulation respective mais, en plus, également le dispositif actif (16) respectif.
  14. Section de refroidissement selon la revendication 13,
    caractérisée en ce que le dispositif actif (16) respectif est un dispositif qui refoule activement l'autre milieu.
  15. Section de refroidissement selon la revendication 14,
    caractérisée en ce que l'autre milieu (18) est de l'air ou de l'eau.
  16. Section de refroidissement selon la revendication 13, 14 ou 15,
    caractérisée en ce que l'autre milieu (18) est soutiré d'un dispositif de stockage (19) respectif.
  17. Section de refroidissement selon la revendication 16,
    caractérisée en ce que l'autre milieu (18) est soumis à une pression (p') respective dans le dispositif de stockage (19) respectif.
EP18193920.8A 2018-09-12 2018-09-12 Dispositifs d'application de tunnels de refroidissement à l'aide d'un second embranchement Active EP3623068B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP18193920.8A EP3623068B1 (fr) 2018-09-12 2018-09-12 Dispositifs d'application de tunnels de refroidissement à l'aide d'un second embranchement
CN201980059890.4A CN112654441B (zh) 2018-09-12 2019-07-30 具有第二端子的冷却段的施加装置
PCT/EP2019/070427 WO2020052854A1 (fr) 2018-09-12 2019-07-30 Dispositifs d'application de sections de refroidissement munis d'un second raccordement
US17/274,212 US11779976B2 (en) 2018-09-12 2019-07-30 Application devices for cooling sections, having a second connection

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18193920.8A EP3623068B1 (fr) 2018-09-12 2018-09-12 Dispositifs d'application de tunnels de refroidissement à l'aide d'un second embranchement

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EP3623068A1 EP3623068A1 (fr) 2020-03-18
EP3623068B1 true EP3623068B1 (fr) 2021-07-14

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US (1) US11779976B2 (fr)
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Publication number Priority date Publication date Assignee Title
WO2024184803A1 (fr) * 2023-03-06 2024-09-12 Danieli & C. Officine Meccaniche S.P.A. Laminoir de dégrossissage réversible pour un produit en aluminium ou en alliage d'aluminium et processus associé

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6049803A (ja) * 1983-08-29 1985-03-19 Sumitomo Metal Ind Ltd ヒ−ト・スクラッチ防止冷間圧延方法
JPH02229610A (ja) * 1989-03-03 1990-09-12 Sumitomo Metal Ind Ltd 熱間圧延のネッキング防止方法
EP1938911A1 (fr) * 2006-12-27 2008-07-02 VAI Industries (UK) Ltd. Dispositif et procédé pour refroidissement contrôlé
EP2301685A1 (fr) 2009-09-23 2011-03-30 Siemens Aktiengesellschaft Procédé de commande pour une installation de traitement d'un produit de laminage étendu en longueur
JP5492910B2 (ja) 2010-01-29 2014-05-14 東芝三菱電機産業システム株式会社 圧延ラインにおける注水制御装置、注水制御方法、注水制御プログラム
JP5616817B2 (ja) 2011-02-18 2014-10-29 東芝三菱電機産業システム株式会社 熱間圧延ラインの制御装置
EP2527061A1 (fr) 2011-05-27 2012-11-28 Siemens VAI Metals Technologies GmbH Procédé de refroidissement d'un faisceau métallique et vanne de commande pour l'ouverture et la fermeture intermittentes d'un flux volumique d'un fluide de refroidissement
EP2767352A1 (fr) * 2013-02-14 2014-08-20 Siemens VAI Metals Technologies GmbH Refroidissement d'une bande métallique avec dispositif de soupapes réglé selon la position

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CN112654441A (zh) 2021-04-13
WO2020052854A1 (fr) 2020-03-19
CN112654441B (zh) 2023-03-10
US11779976B2 (en) 2023-10-10
EP3623068A1 (fr) 2020-03-18
US20210354182A1 (en) 2021-11-18

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