EP3495056B1 - Commande améliorée de la gestion de l'eau d'un circuit de refroidissement - Google Patents

Commande améliorée de la gestion de l'eau d'un circuit de refroidissement Download PDF

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Publication number
EP3495056B1
EP3495056B1 EP17206426.3A EP17206426A EP3495056B1 EP 3495056 B1 EP3495056 B1 EP 3495056B1 EP 17206426 A EP17206426 A EP 17206426A EP 3495056 B1 EP3495056 B1 EP 3495056B1
Authority
EP
European Patent Office
Prior art keywords
coolant
control device
time
pump
outlets
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
EP17206426.3A
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German (de)
English (en)
Other versions
EP3495056A1 (fr
Inventor
Klaus Weinzierl
Manfred Eder
Jurij Razinkov
Christian Schlapak
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Primetals Technologies Austria GmbH
Primetals Technologies Germany GmbH
Original Assignee
Primetals Technologies Austria GmbH
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.)
Filing date
Publication date
Application filed by Primetals Technologies Austria GmbH, Primetals Technologies Germany GmbH filed Critical Primetals Technologies Austria GmbH
Priority to EP17206426.3A priority Critical patent/EP3495056B1/fr
Priority to PCT/EP2018/081500 priority patent/WO2019115145A1/fr
Priority to CN201880079935.XA priority patent/CN111432950B/zh
Priority to US16/771,500 priority patent/US11135631B2/en
Priority to EP18800210.9A priority patent/EP3723919A1/fr
Publication of EP3495056A1 publication Critical patent/EP3495056A1/fr
Application granted granted Critical
Publication of EP3495056B1 publication Critical patent/EP3495056B1/fr
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Classifications

    • 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
    • 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
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D1/00—General methods or devices for heat treatment, e.g. annealing, hardening, quenching or tempering
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D1/00—General methods or devices for heat treatment, e.g. annealing, hardening, quenching or tempering
    • C21D1/56—General methods or devices for heat treatment, e.g. annealing, hardening, quenching or tempering characterised by the quenching agents
    • C21D1/60—Aqueous agents
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D1/00—General methods or devices for heat treatment, e.g. annealing, hardening, quenching or tempering
    • C21D1/62—Quenching devices
    • C21D1/667—Quenching devices for spray quenching
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D11/00—Process control or regulation for heat treatments
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D9/00—Heat treatment, e.g. annealing, hardening, quenching or tempering, adapted for particular articles; Furnaces therefor
    • C21D9/52—Heat treatment, e.g. annealing, hardening, quenching or tempering, adapted for particular articles; Furnaces therefor for wires; for strips ; for rods of unlimited length
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D9/00—Heat treatment, e.g. annealing, hardening, quenching or tempering, adapted for particular articles; Furnaces therefor
    • C21D9/52—Heat treatment, e.g. annealing, hardening, quenching or tempering, adapted for particular articles; Furnaces therefor for wires; for strips ; for rods of unlimited length
    • C21D9/54—Furnaces for treating strips or wire
    • C21D9/56—Continuous furnaces for strip or wire
    • C21D9/573—Continuous furnaces for strip or wire with cooling

Definitions

  • the present invention is further based on a computer program that includes machine code that is generated by a control device can be processed for a cooling section, the processing of the machine code by the control device causing the control device to operate the cooling section according to such an operating method.
  • the present invention is further based on a control device for a cooling section, the control device being programmed with such a computer program, so that the control device operates the cooling section according to such an operating method.
  • Rolld metal - in particular steel - is cooled in cooling sections after rolling.
  • cooling sections are the cooling section downstream of a hot strip mill, with or without intensive cooling, and the so-called Quette of a heavy plate mill.
  • precise temperature control is common in a cooling section downstream of the rolling train.
  • the defined and exact application of a desired amount of coolant is of great importance.
  • cooling between a roughing train and a finishing train there are particularly high demands on the dynamics of the management of the coolant due to the large amount of coolant required.
  • the coolant is usually water or at least essentially consists of water.
  • a water tank can be set up as a coolant reservoir in the immediate vicinity of the coolant outlets and the coolant outlets can be supplied with water from the water tank directly or via booster pumps.
  • the line system between the coolant reservoir and the coolant outlets can be made sufficiently short.
  • bypass coolant outlets in addition to useful coolant outlets via which the coolant is applied to the hot rolling stock.
  • the coolant can be discharged via the bypass coolant outlets without applying it to the hot rolling stock.
  • valves upstream of the bypass coolant outlets are retracted or closed, while valves upstream of the useful coolant outlets are opened at the same time.
  • the coolant that is moved through the line system only needs to be accelerated to a lesser extent or even not at all.
  • the disadvantage of this procedure is that large amounts of coolant are pumped through the line system even when no hot rolling stock is to be cooled. The energy consumption for the pump and the consumption of coolant are correspondingly high.
  • a riser pipe with an overflow near the cooling area is to provide a riser pipe with an overflow near the cooling area.
  • a riser pipe takes up less space than a water tank. But it can only store a small amount of coolant. In this case, the maximum amount of coolant to be expected is therefore continuously delivered to the cooling area.
  • This already represents a disadvantage since the maximum required amount of coolant always has to be provided, while in a solution with a water tank, only the average required amount of water has to be provided.
  • the height of the riser creates an almost constant back pressure that is independent of the specific coolant requirement.
  • the consumption of coolant and energy is correspondingly high, since an unnecessarily large amount of coolant is always provided.
  • the pressure cannot be adjusted. It always corresponds to the pressure resulting from the height of the column of coolant in the riser pipe up to the overflow.
  • the object of the present invention is to create possibilities by means of which the required amount of coolant can be made available efficiently at any time with high accuracy, even without a larger or smaller storage facility for coolant between the pump and the coolant outlets.
  • an operating method of the type mentioned at the beginning is designed in that the control device of the cooling section cyclically takes into account not only the total coolant flow and the working pressure of the coolant, but additionally for the respective point in time when determining the pump pressure that should prevail on the output side of the pump a change in the total coolant flow is also taken into account.
  • the pump pressure takes into account the extent to which the amount of coolant in the line system has to be accelerated or decelerated.
  • the respectively desired total coolant flow is achieved in a much more dynamic manner than in the prior art.
  • the control device when determining the pump pressure, takes into account a line resistance of the line system that has to be overcome by the total coolant flow. This results in even greater accuracy in determining the pump pressure and thus in determining the control state of the pump.
  • the control device in addition to the coolant flows that are to be released via the coolant outlets at the respective point in time, the control device knows the forecasted coolant flows for a forecast horizon that are to be released for a number of future times via the coolant outlets. In this case it is possible for the control device to take into account the predicted coolant flows of at least one of the future points in time when determining the control state of the pump.
  • control device determines the associated total coolant flow for at least one future point in time and takes it into account when determining the change in the total coolant flow.
  • the deviation from the total coolant flow can be determined for the respective point in time.
  • the control device continues to determine the change in the total coolant flow in addition to the predicted coolant flows of the at least one future point in time also takes into account the total coolant flow from at least one previous point in time.
  • the respective point in time is preferably in the middle between the at least one future point in time and the at least one past point in time.
  • the coolant outlets comprise useful coolant outlets and bypass coolant outlets.
  • the hot rolling stock is cooled exclusively by means of the coolant flows emitted via the useful coolant outlets.
  • the bypass coolant outlets serve as a means of influencing the overall coolant flow without changing the coolant flows applied to the hot rolling stock.
  • the control device determines the coolant flows to be dispensed via the bypass coolant outlets for the respective point in time and / or the future points in time in such a way that each total coolant flow that was taken into account at an earlier point in time before the respective point in time when determining the change in the total coolant flow valid for the earlier point in time is retained.
  • This procedure corresponds to the procedure customary in the context of a model predictive control.
  • the coolant outlets include useful coolant outlets and bypass coolant outlets, as before.
  • the functionality of the corresponding coolant outlets is also as before.
  • the control device determines the coolant flows to be dispensed via the bypass coolant outlets in such a way that the coolant flows to be dispensed via the bypass coolant outlets are as close as possible to a desired bypass coolant flow and a change in the total coolant flow to be dispensed via the useful coolant outlets and the bypass coolant outlets Total coolant flow is as low as possible.
  • the valves can be switching valves which can only assume two switching states, namely fully open and fully closed.
  • they are Valves can be controlled steplessly or at least in several steps. There is therefore preferably at least one intermediate position of the respective valve between "completely open” and "completely closed”.
  • the control device preferably determines the working pressure in such a way that the control states of the valves adhere to minimum distances from minimum control and maximum control and the control state of the pump is kept constant as far as possible. This means that the pump must be controlled with less dynamics.
  • control device preferably also takes into account a height difference to be overcome.
  • the height difference represents a constant offset for the pump pressure.
  • the control device preferably also determines a control signal for a short-circuit valve connected in parallel with the pump and controls the short-circuit valve in accordance with the determined control signal.
  • a control signal for a short-circuit valve connected in parallel with the pump and controls the short-circuit valve in accordance with the determined control signal.
  • the processing of the computer program by the control device causes the control device to operate the cooling section according to an operating method according to the invention.
  • control device for a cooling section having the features of claim 14.
  • the control device is programmed with a computer program according to the invention, so that the control device operates the cooling section according to an operating method according to the invention.
  • the cooling section has a control device according to the invention which operates the cooling section according to an operating method according to the invention.
  • a cooling area of the cooling section, within which the coolant is applied to the hot rolling stock can in particular be arranged within a rolling train and / or upstream of a rolling train and / or downstream of the rolling train.
  • the term “and / or” is to be understood here in the sense that the cooling area can be arranged completely within the rolling train, can be arranged completely downstream of the rolling train or can be arranged partially within the rolling train and partially downstream of the rolling train. Analogous statements apply to an arrangement in front of the rolling train.
  • a cooling section has a cooling area 1.
  • a liquid coolant 2 - usually water - can be applied to a hot rolling stock 3 and the hot rolling stock 3 can be cooled as a result.
  • the hot rolling stock 3 consists of metal, for example steel.
  • a number of useful coolant outlets 4 are arranged in the cooling region 1.
  • the cooling area 1 is as shown in FIG 1 partially arranged within a rolling train. This is in FIG 1 indicated by the fact that one of the useful coolant outlets 4 is arranged upstream of a last roll stand 5 of the rolling train (for example a finishing train).
  • the cooling area 1 could, however, also be arranged completely within the rolling train.
  • the cooling area 1 is still partially downstream of the rolling train.
  • FIG 1 indicates by the fact that the other useful coolant outlets 4 are arranged downstream of the last rolling stand 5 of the rolling train.
  • the cooling area 1 could just as completely be arranged downstream of the rolling train.
  • the cooling area 1 can, for example, be arranged between the last roll stand 5 and a reel 5 '.
  • the cooling area 1 is arranged completely or partially upstream of the rolling train. This is in FIG 1 and also not shown in the other figures.
  • bypass coolant outlets 6 are preferably also present. In FIG 1 only a single such bypass coolant outlet 6 is shown. As a rule, there is also only a single bypass coolant outlet 6. In principle, however, several bypass coolant outlets 6 can also be present. Independently of the number of bypass coolant outlets 6, however, the hot rolling stock 3 is cooled exclusively via the useful coolant outlets 4. Coolant 2, which is discharged via one of the bypass coolant outlets 6, does not serve to cool the hot rolling stock 3. For example, this can Part of the coolant 2 can be collected and returned via a collecting container 6 '. The return of the coolant 2 from the collecting container 6 'is shown in FIG FIG 1 not shown.
  • the cooling section has a pump 7.
  • the pump 7 can take coolant 2 from a coolant reservoir 8 - for example a water tank - and feed it to the coolant outlets 4, 6 via a line system 9.
  • the term “pump” is used in the generic sense in the context of the present invention.
  • the pump 7 can therefore be a single pump or several pumps arranged one behind the other and / or in parallel.
  • Valves 10 are arranged between the pump 7 and the coolant outlets 4, 6.
  • coolant flows Wi which are emitted via the coolant outlets 4, 6, can be controlled.
  • the index i if it has the value 0, stands for the bypass coolant outlet 6, and the associated coolant flow W0 thus stands for the coolant flow output via the bypass coolant outlet 6.
  • the index i if it has the value 1, 2, ... n, stands for one of the useful coolant outlets 4, the associated coolant flow Wi thus for the coolant flow emitted via the respective useful coolant outlet 4.
  • the coolant flows Wi have the unit m 3 / s.
  • the cooling section has a control device 11 which operates the cooling section according to an operating method that is explained in more detail below.
  • the control device 11 is generally designed as a software-programmable control device. This is in FIG 1 indicated by the fact that the characters " ⁇ P" for microprocessor are drawn in the control device 11.
  • the control device 11 is programmed with a computer program 12.
  • the computer program 12 comprises machine code 13 which can be processed by the control device 11.
  • the programming of the control device 11 with the computer program 12 causes the control device 11 to operate the cooling section according to the operating method explained below.
  • control device 11 Due to the programming with the computer program 12, the control device 11 carries out the following in connection with FIG 2 explained operating procedures from: In a step S1, the control device 11 becomes aware of the respective coolant flow Wi for a respective point in time for the useful coolant outlets 4.
  • the respective coolant flow Wi is that coolant flow which is to be emitted via the respective useful coolant outlet 4 at the respective point in time.
  • the control device 11 determines the coolant flow W0.
  • the coolant flow W0 is that coolant flow which is to be emitted via the bypass coolant outlet 6 at the respective point in time.
  • the coolant flow W0 is determined as a function of the sum of the coolant flows Wi to be emitted via the useful coolant outlets 4. This will become apparent from later explanations.
  • control device 11 forms a total coolant flow WG valid for the respective point in time by adding up the coolant flows Wi.
  • a step S4 the control device 11 determines a change ⁇ WG in the total coolant flow WG.
  • the change ⁇ W of the total coolant flow WG indicates the extent to which the total coolant flow WG changes at the respective point in time. It is therefore a matter of deriving the total coolant flow WG over time.
  • the control device 11 can in particular use a total coolant flow WG 'which it knows from a previous cycle.
  • step S5 the control device 11 updates the total coolant flow WG 'for the previous cycle. For example, it takes over the value for the total coolant flow WG that it determined in step S3.
  • the control device 11 defines a working pressure pA (unit: N / m 2 ).
  • the working pressure pA is that pressure which the coolant 3 should have on the inlet side of the valves 10. It is possible that the working pressure pA of the control device 11 is specified. Alternatively, it is possible for the control device 11 to independently determine the working pressure pA.
  • the control states Ci can in particular be the open positions of the valves 10.
  • the valves 10 can preferably be controlled continuously or at least in several steps.
  • gi is a characteristic curve that is valid for the respective valve 10.
  • the characteristic curve gi is a function of the respective control state Ci. For a nominal pressure pA0, it indicates how large the coolant flow Wi flowing through the respective valve 10 is in each case for a specific control state Ci. This is in FIG 3 shown purely by way of example for a single valve 10.
  • the characteristic curves gi of the valves 10 can either be taken from data sheets of the manufacturers of the valves 10 or determined experimentally.
  • the control device can, for example, solve equation 1 for Ci.
  • the control device 11 determines a pump pressure pP.
  • the pump pressure pP is that pressure which should prevail on the outlet side of the pump 7, so that the working pressure pA is reached on the inlet side of the valves 10.
  • the control device 11 takes into account at least the total coolant flow WG, the working pressure pA and the change ⁇ W in the total coolant flow WG.
  • pH is a (usually constant) pressure that is caused by a height difference H.
  • the height difference H is measured between the outlet side of the pump 7 and the outlets of the valves 10.
  • the pressure p1 describes a pressure drop that occurs due to the total coolant flow WG conveyed on the way from the pump 7 to the valves 10 occurs.
  • the pressure p1 thus describes the line resistance of the line system 9.
  • the pressure p1 is a - generally non-linear - function of the total coolant flow WG. If necessary, additional resistances of the line system 9, such as filter resistances and the like, also enter into the pressure p1.
  • the pressure p2 is a function of the change ⁇ WG in the total coolant flow WG. It is calculated as follows:
  • the line system 9 has a uniform cross section A over its entire length L. If this is not the case, the following consideration must be made for the individual sections of the line system 9, which each have a uniform cross section.
  • the amount of coolant 3 located in the line system 9 results in AL, the mass m of the coolant 3 in pAL, where ⁇ is the density of the coolant 3 (in the usual unit kg / m 3 ).
  • the required acceleration a results from ⁇ WG / A. This results in the required force F to ma, i.e. the product of mass m and acceleration a.
  • the coolant 3 is water.
  • the total coolant flow WG should be increased from 2 m 3 / s to 2.5 m 3 / s within 1 second.
  • a pressure p2 of 50 kPa is then required for the required acceleration of the amount of water in the line system 9.
  • the control device 11 determines an associated control state CP for the pump 7 in a step S9, so that the desired pump pressure pP is reached on the output side of the pump 7.
  • the control device 11 takes into account the pump pressure pP, the total coolant flow WG and a suction pressure pS that prevails on the inlet side of the pump 7.
  • the suction pressure pS can be specified for the control device 11 or can be recorded by measurement. It can have a negative or a positive value or the value 0, depending on the situation of the individual case.
  • the control device 11 preferably uses a pump characteristic curve to determine the control state CP for the pump 7.
  • the pump characteristic sets the total coolant flow WG, the suction pressure pS on the inlet side of the pump 7 and the pump pressure pP on the outlet side of the pump 7 in relation to one another.
  • the pump characteristic can, for example, as shown in FIG 4 have the total coolant flow WG and the difference between pump pressure pP and suction pressure pS as input parameters and supply the associated control state CP as output parameters.
  • the control state CP can in particular be the speed of the pump 7. Such characteristics are generally known to those skilled in the art.
  • control device controls the valves 10 and the pump 7 in a step S10 in accordance with the determined control states Ci, CP.
  • step S10 the control device 11 goes back to step S1.
  • the control device 11 executes the steps S1 to S10 cyclically, the respective execution being valid for a respective point in time.
  • a strictly cyclical execution preferably takes place, ie there is a fixed work cycle T within which steps S1 to S10 are each processed once.
  • the work cycle T can be, for example, 0.1 seconds to 1.0 seconds, preferably between 0.2 seconds and 0.5 seconds, in particular about 0.3 seconds.
  • the control device 11 can use the coolant flow W0 released via the bypass coolant outlet 6 to equalize the control state CP of the pump 7.
  • WG ' is the total coolant flow from the previous point in time.
  • W0 * is a setpoint coolant flow specified for the bypass coolant outlet 6. It is preferably about 30% to about 70% of the maximum coolant flow for the bypass coolant outlet 6, in particular about 50% of this value, ⁇ and ⁇ are weighting factors. You are not negative. Furthermore - without restricting the generality - it can be required that the two weighting factors ⁇ , ⁇ add up to 1.
  • the double lines stand for a standard.
  • the norm can in particular be the usual square norm.
  • the coolant flows Wi for the useful coolant outlets 4 for the respective point in time are predetermined for the control device 11.
  • the function F thus has the coolant flow W0 to be emitted via the bypass coolant outlet 6 as the only freely selectable parameter. It is therefore possible to determine the minimum of the function F and to use that value as the coolant flow W0 for the bypass coolant outlet 6 at which this minimum results. The result is that the coolant flow W0 to be discharged via the bypass coolant outlet 6 is as close as possible to the bypass target coolant flow W0 * and the change in the total coolant flow WG is as small as possible.
  • the coolant flows for the respective point in time and - based on the respective point in time - for the past are known to the control device 11, but also useful coolant flows forecast for a forecast horizon PH, i.e. those coolant flows that are for a number of future points in time to be delivered via the useful coolant outlets 4.
  • a forecast horizon PH i.e. those coolant flows that are for a number of future points in time to be delivered via the useful coolant outlets 4.
  • This is shown in FIG 5 for the resulting total coolant flows WG and a forecast horizon PH of (purely by way of example) four working cycles T.
  • the term "forecast horizon" is still not meant in the sense of how far the control device 11 is actually aware of a forecast.
  • the forecast horizon PH can be in the range from 2 to 10 seconds, for example. In general, if the procedure of FIG 2 correspond to several work cycles T.
  • control device 11 can use the forecast useful coolant flows at least one of the future points in time when determining the control state C0 for the valve 10 and / or controlling the bypass coolant outlet 6 the control state CP of the pump 7. There are various options for taking this into account. Several of the possibilities are explained below.
  • the coolant flows are given two indices below.
  • the first index (i) stands - as before - for the respective coolant outlet 4, 6.
  • control device 11 determines the associated total coolant flow WGj (with j> 0) for at least one future point in time and takes this total coolant flow WGj into account when determining the change in the total coolant flow ⁇ WG.
  • the corresponding total coolant flow WGj can in particular be the total coolant flow WG1 for the next point in time.
  • the control device 11 preferably also takes into account the total coolant flow WG 'of at least one previous point in time in addition to the forecast useful coolant flows Wij of the at least one future point in time.
  • the respective point in time should lie in the middle between the at least one future point in time and the at least one past point in time.
  • the total coolant flow WG 'for the past point in time can alternatively be a setpoint value or an actual value. This is in contrast to the other variable variables used in the present case, which are always setpoints.
  • FIG 6 includes, among other things - analogous to FIG 2 - Steps S6 to S10. These steps are therefore not explained again below. However, steps S1 to S5 are replaced by steps S11 to S15.
  • step S11 the control device 11 - analogously to step S1 - is aware of the respective coolant flow Wi0 for a respective point in time for the useful coolant outlets 4.
  • step S12 the control device 11 determines the coolant flow W00.
  • the procedure can be taken for each total coolant flow WGj which was taken into account in a previous cycle in the context of determining the change ⁇ WG in the total coolant flow WG0 that is valid for the respective cycle.
  • the coolant flows W0j for the bypass coolant outlet 6 are therefore adapted in order to be able to keep the total coolant flow WGj, which was utilized in the course of the previous cycle, constant.
  • step S12 the control device 11 determines the associated bypass coolant flow W0j for at least one work cycle T, for which the control device 11 knows the predicted useful coolant flows Wij.
  • control device 11 forms the corresponding total coolant flows WGj by adding up the corresponding coolant flows Wij.
  • step S14 the control device 11 determines the change ⁇ WG in the total coolant flow WG.
  • the difference to step S4 of FIG 2 is that the control device 11 uses the relationship given in Equation 6 above in step S14.
  • step S15 the control device 11 updates the total coolant flow WG 'for the previous cycle.
  • the difference to step S5 of FIG 2 consists in the fact that the control device 11 does not use the total coolant flow WG0 of the current cycle in step S15, but the total coolant flow WG1, which it has utilized in the course of determining the change ⁇ WG of the total coolant flow WG0.
  • FIG 7 shows this for a forecast horizon PH of four working cycles T.
  • This forecast horizon PH is of course only an example.
  • the forecast horizon PH could also be larger or smaller.
  • the total coolant flows WGj determined are in FIG 7 indicated by small crosses.
  • FIG 7 also shows the respective sum of the useful coolant flows Wij. This determination is easily possible within the framework of the forecast horizon PH, since the control device 11 knows the useful coolant flows Wij.
  • the associated sums of the useful coolant flows Wij are in FIG 7 indicated by small circles.
  • the control device 11 now also determines the associated changes in the total coolant flows WGj by forming the difference between the total coolant flows WGj that follow one another directly - for example the total coolant flows WG1 and WG2.
  • the control device 11 checks within the forecast horizon PH whether the changes determined of the total coolant flows WGj each comply with a predetermined maximum change ⁇ max or not. If the total coolant flows WGj comply with the maximum change ⁇ max, the control device 11 maintains the determined total coolant flows WGj. If, on the other hand, the total coolant flows WGj do not adhere to the maximum change ⁇ max, the control device 11 adjusts the determined total coolant flows WGj in advance.
  • the associated modified total coolant flows WGj are shown in FIG 7 represented by small rectangles.
  • the adaptation takes place, if possible, in such a way that both the change ⁇ WG in the total coolant flow WG0 for the respective point in time and the changes in the determined total coolant flows WGj for the future points in time comply with the maximum change ⁇ max. This situation is in FIG 7 shown.
  • control device 11 retains the useful coolant flows Wij predetermined for the different points in time within the scope of the adaptation and only adapts the bypass coolant flows W0j. If compliance with the maximum change ⁇ max cannot be achieved by adapting only the bypass coolant flows W0j, however, the useful coolant flows Wij must also be adapted.
  • predictive predictive planning can take place. This can not only, as in FIG 7 shown, may be required with an increase in the requested total coolant flows WGj, but also with a reduction in the requested total coolant flows WGj.
  • step S21 the control device 11 checks whether the control states Ci of the valves 10 comply with minimum distances from a minimum control of the respective valve 10 and a maximum control of the respective valve 10. Furthermore, the control device 11 checks in step S21 to what extent the control state CP of the pump 7 has been changed. For example, the control device 11 can set an optimization problem with boundary conditions to be observed in the context of step S21. Such optimization problems are well known to those skilled in the art.
  • step S21 If the control device 11 comes to the result in step S21 that the control states Ci of the valves 10 adhere to the minimum distances and the control state CP of the pump 7 is kept constant as far as possible, the control device 11 goes to step S10. Otherwise, the control device 11 goes to a step S22. In step S22, the control device 11 varies the applied working pressure pA in the sense of the mentioned optimization.
  • the pump 7 has a permissible operating range.
  • the operation of the pump 7 is as shown in FIG FIG 9 only permitted between a minimum speed nmin and a maximum speed nmax.
  • the required amount of coolant - that is, the respective total coolant flow WG - must be between a minimum permissible coolant flow WGmin and a maximum permissible coolant flow WGmax.
  • the minimum permissible coolant flow WGmin and the maximum permissible coolant flow WGmax are here as shown in FIG 9 depends on the difference between the pump pressure pP and the suction pressure pS. Without further measures, the pump 7 can therefore only be used within the in FIG 9 unshaded area.
  • step S10 a corresponding activation of the short-circuit valve 14 by the control device 11 takes place in step S10.
  • the short-circuit valve 14 is opened as far as is necessary to operate the pump 7 in a per se permissible range.
  • the present invention has been explained above for a simple configuration of the line system 9, namely as shown in FIG FIG 1 for a single direct connection from the pump 7 to the valves 10, the lengths of the individual stub lines between a junction 15 at which the stub lines to the individual valves 10 and the coolant outlets 4, 6 can be neglected.
  • the present invention can, however, also be used when the line system 9 is designed to be more complex. In this case, it only needs to be taken into account that for each junction at which a branch occurs, the total of the coolant flows flowing into the respective junction and exiting from the respective junction must total 0 and that at the respective junction for each connected section of the line system 9 the same pressure must be given.
  • the procedure is analogous to Kirchhoff's rules of electrical engineering. The procedure becomes computationally more complicated, but the system remains unchanged.
  • the line system 9 has three sections 16a, 16b, 16c.
  • the section 16a extends from a pump 7a to a junction point 15. It has the length La and the cross section Aa.
  • the two other sections 16b, 16c extend from node 15 to respective useful coolant outlets 4b, 4c and respective bypass coolant outlets 6b, 6c.
  • a further pump 7b is located in section 16b shortly after node 15.
  • the section 16b has a length Lb and a cross section Ab. There is no pump in section 16c.
  • the section 16c has a length Lc and a cross section Ac. Valves 10b, 10c are arranged upstream of the coolant outlets 4b, 4c and 6b, 6c.
  • FIG 11 The configuration shown can occur, for example, in a cooling section that has intensive cooling (coolant outlets 4b) and additionally laminar cooling (coolant outlets 4c) as well as a bypass coolant outlet 6b, 6c for each of the two coolings.
  • the hot rolling stock 3 and the arrangement of the useful coolant outlets 4b, 4c in the cooling area 1 are shown in FIG FIG 11 not shown with order FIG 11 not to overload.
  • gic is the respective valve characteristic curve
  • pAc is the working pressure prevailing on the inlet side of the valves 10c.
  • p 15th pAc + p 1 c WC + p 2 c ⁇ Wc p1c and p2c are defined analogously to functions p1 and p2, but refer to section 16c.
  • ⁇ Wc is the change in total coolant flow Wc.
  • Wib are the respective coolant flows
  • gib is the respective valve characteristic curve
  • pAb is the working pressure prevailing on the inlet side of the valves 10b.
  • pPb pAb + p 1 b Wb + p 2 b ⁇ Wb p1b and p2b are defined analogously to functions p1 and p2, but refer to section 16b.
  • the working pressures pAb and pAc are now target variables of the system, which are specified or, under certain circumstances, also from the Control device 11 can be determined.
  • the total coolant flows Wb, Wc are known.
  • ⁇ Wb, ⁇ Wc and thus, as a result, also the change ⁇ Wa
  • the system of equations can thus be solved uniquely.
  • the present invention has many advantages.
  • the required coolant flows Wi, WG are made available with a high degree of accuracy, without the need for a water tank or other compensation measures.
  • the working pressure pA can be selected as required and even adapted during operation of the cooling section.
  • the operating range of the cooling section is expanded.
  • both the suction pressure pS and the pump pressure pP can be varied as required. This applies both to pure laminar cooling and to pure intensive cooling as well as to a cooling section which includes both laminar cooling and intensive cooling. Due to the adaptation of the working pressure pA and the pump pressure pP, a considerable amount of energy can be saved.
  • the average energy consumption that is required for pumping the coolant 2 can thereby be reduced by at least 30% compared to the solutions of the prior art, in some cases even by up to 50%.
  • the associated cost savings can be in the range of well over € 100,000 per year.
  • the process is extremely flexible. Within a few seconds, the total coolant flow WG can be increased from a minimum value to a maximum value or, conversely, reduced from the maximum value to the minimum value without the accuracy of the cooling being adversely affected.

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Claims (16)

  1. Procédé d'exploitation pour un circuit de refroidissement destiné au refroidissement d'un produit à laminer (3) métallique chaud, le circuit de refroidissement comprenant une pompe (7) qui prélève un agent de refroidissement (2) dans un réservoir d'agent de refroidissement (8) et l'amène, par le biais d'un système de conduites (9), à plusieurs sorties d'agent de refroidissement (4, 6) qui sont commandées par des vannes (10) situées en amont des sorties d'agent de refroidissement (4, 6),
    - dans lequel un dispositif de commande (11) du circuit de refroidissement effectue, cycliquement pour un moment respectif,
    -- une détermination d'états de pilotage (Ci) pour les vannes (10), ceci en tenant compte de flux d'agent de refroidissement (Wi) qui doivent être délivrés par les sorties d'agent de refroidissement (4, 6) au moment respectif, et en liaison avec une pression de travail (pA) de l'agent de refroidissement (2) existant côté entrée des vannes (10),
    -- une détermination d'un flux total d'agent de refroidissement (WG), ceci en additionnant les flux d'agent de refroidissement (Wi),
    -- une détermination d'une pression de pompe (pP) devant régner côté sortie de la pompe (7), de façon que la pression de travail (pA) soit atteinte côté entrée des vannes (10), ceci en tenant compte du flux total d'agent de refroidissement (WG) et de la pression de travail (pA) de l'agent de refroidissement (2),
    -- une détermination d'un état de pilotage (CP) pour la pompe (7), ceci en tenant compte du flux total d'agent de refroidissement (WG), de la pression de pompe (pP) et d'une pression d'aspiration (pS) régnant côté entrée de la pompe (7), et
    -- pilote les vannes (10) et la pompe (7) conformément aux états de pilotage (Ci, CP) déterminés,
    caractérisé
    en ce que le dispositif de commande (11) tient également compte, cycliquement pour le moment respectif lors de la détermination de la pression de pompe (pP), d'une variation (δWG) du flux total d'agent de refroidissement (WG), en plus du flux total d'agent de refroidissement (WG) et de la pression de travail (pA) de l'agent de refroidissement (2).
  2. Procédé d'exploitation selon la revendication 1,
    caractérisé
    en ce que le dispositif de commande (11) tient compte, lors de la détermination de la pression de pompe (pP), d'une résistance de conduite (p2) du système de conduites (9) devant être surmontée par le flux total d'agent de refroidissement (WG).
  3. Procédé d'exploitation selon la revendication 1 ou 2,
    caractérisé
    en ce que le dispositif de commande (11) est informé, en plus des flux d'agent de refroidissement (Wij) devant être délivrés par les sorties d'agent de refroidissement (4, 6) au moment respectif, de flux d'agent de refroidissement (Wij) pronostiqués pour un horizon de pronostic (PH) qui doivent être délivrés par les sorties d'agent de refroidissement (4, 6) pour un nombre de moments futurs,
    et en ce que le dispositif de commande (11) tient compte des flux d'agent de refroidissement (Wij) pronostiqués d'au moins un des moments futurs lors de la détermination de l'état de pilotage (CP) de la pompe (7).
  4. Procédé d'exploitation selon la revendication 3,
    caractérisé
    en ce que le dispositif de commande (11) détermine, pour au moins un moment futur, le flux total d'agent de refroidissement (WGj) associé et en tient compte lors de la détermination de la variation (δWG) du flux total d'agent de refroidissement (WG0).
  5. Procédé d'exploitation selon la revendication 4,
    caractérisé
    en ce que le dispositif de commande (11) tient compte également du flux total d'agent de refroidissement (WG') d'au moins un moment passé, en plus des flux d'agent de refroidissement (Wij) pronostiqués de l'au moins un moment futur, lors de la détermination de la variation (δWG) du flux total d'agent de refroidissement (WG0), et en ce que le moment respectif se situe à mi-chemin entre l'au moins un moment futur et l'au moins un moment passé.
  6. Procédé d'exploitation selon la revendication 4 ou 5,
    caractérisé
    - en ce que les sorties d'agent de refroidissement (4, 6) comprennent des sorties d'agent de refroidissement effectives (4) et des sorties d'agent de refroidissement de dérivation (6),
    - en ce que le produit à laminer (3) chaud est refroidi exclusivement au moyen des flux d'agent de refroidissement (Wij) délivrés par les sorties d'agent de refroidissement effectives (4),
    - en ce que le dispositif de commande (11) détermine, en se basant sur les flux d'agent de refroidissement (Wij) devant être délivrés par les sorties d'agent de refroidissement effectives (4) pour le moment respectif et/ou les moments futurs, les flux d'agent de refroidissement (Wi0) devant être délivrés par les sorties d'agent de refroidissement de dérivation (6) pour le moment respectif et/ou les moments futurs, de façon à maintenir chaque flux total d'agent de refroidissement (WGj) dont il a été tenu compte à un moment antérieur au moment respectif dans le cadre de la détermination de la variation (δWG) du flux total d'agent de refroidissement (WG) valable pour le moment antérieur.
  7. Procédé d'exploitation selon l'une des revendications 3 à 6,
    caractérisé
    en ce que le dispositif de commande (11) effectue, lors de la détermination de l'état de pilotage (CP) de la pompe (7),
    - une détermination, pour les moments futurs, d'un flux total d'agent de refroidissement (WGj) pronostiqué respectif, à l'aide des flux d'agent de refroidissement (Wij) pronostiqués respectifs,
    - une détermination, pour les moments futurs, de variations des flux totaux d'agent de refroidissement (WGj) déterminés, et
    - maintient ou adapte par anticipation, pour le moment respectif et/ou des moments futurs à l'intérieur de l'horizon de pronostic (PH), les flux totaux d'agent de refroidissement (WGj) respectifs en fonction du respect ou du dépassement d'une variation maximale (δmax) prédéterminée, de façon que, dans la mesure du possible, la variation du flux total d'agent de refroidissement (WGO) pour le moment respectif tout comme les variations des flux totaux d'agent de refroidissement (WGj) déterminés pour les moments futurs respectent la variation maximale (δmax).
  8. Procédé d'exploitation selon la revendication 1 ou 2,
    caractérisé
    - en ce que les sorties d'agent de refroidissement (4, 6) comprennent des sorties d'agent de refroidissement effectives (4) et des sorties d'agent de refroidissement de dérivation (6),
    - en ce que le produit à laminer (3) chaud est refroidi exclusivement au moyen des flux d'agent de refroidissement (Wi) délivrés par les sorties d'agent de refroidissement effectives (4), et
    - en ce que le dispositif de commande (11) détermine les flux d'agent de refroidissement (W0) devant être délivrés par les sorties d'agent de refroidissement de dérivation (6) de façon que les flux d'agent de refroidissement (W0) devant être délivrés par les sorties d'agent de refroidissement de dérivation (6) soient aussi proches que possible d'un flux d'agent de refroidissement théorique de dérivation (W0*) et qu'une variation (δWG) du flux total d'agent de refroidissement (WG) devant être globalement délivré par les sorties d'agent de refroidissement effectives (4) et les sorties d'agent de refroidissement de dérivation (6) soit aussi réduite que possible.
  9. Procédé d'exploitation selon l'une des revendications précédentes,
    caractérisé
    en ce que les vannes (10) peuvent être pilotées de manière continue ou au moins par degrés.
  10. Procédé d'exploitation selon l'une des revendications précédentes,
    caractérisé
    en ce que le dispositif de commande (11) détermine la pression de travail (pA) de façon que les états de pilotage (Ci) des vannes (10) observent des écarts minimums par rapport à un pilotage minimum et un pilotage maximum et que l'état de pilotage (CP) de la pompe (7) soit maintenu aussi constant que possible.
  11. Procédé d'exploitation selon l'une des revendications précédentes,
    caractérisé
    en ce que le dispositif de commande (11) tient de plus également compte, dans le cadre de la détermination de la pression de pompe (pP), d'une différence de hauteur (H) à surmonter.
  12. Procédé d'exploitation selon l'une des revendications précédentes,
    caractérisé
    en ce que le dispositif de commande (11) détermine en plus un signal de commande (CK) pour une vanne de court-circuit (14) montée en parallèle avec la pompe (7) et pilote la vanne de court-circuit (14) conformément au signal de commande (CK) déterminé.
  13. Programme informatique qui comprend un code machine (13) pouvant être exécuté par un dispositif de commande (11) pour un circuit de refroidissement, l'exécution du code machine (13) par le dispositif de commande (11) ayant pour résultat l'exploitation du circuit de refroidissement par le dispositif de commande (11) conformément à un procédé d'exploitation selon l'une des revendications précédentes.
  14. Dispositif de commande pour un circuit de refroidissement, le dispositif de commande étant programmé par un programme informatique (12) selon la revendication 13, de façon que le dispositif de commande fasse fonctionner le circuit de refroidissement conformément à un procédé d'exploitation selon l'une des revendications 1 à 12.
  15. Circuit de refroidissement destiné au refroidissement d'un produit à laminer (3) métallique chaud,
    - le circuit de refroidissement comprenant une pompe (7) qui prélève un agent de refroidissement (2) dans un réservoir d'agent de refroidissement (8) et l'amène, par le biais d'un système de conduites (9), à plusieurs sorties d'agent de refroidissement (4, 6) qui sont commandées par des vannes (10) situées en amont des sorties d'agent de refroidissement (4, 6),
    - le circuit de refroidissement comprenant un dispositif de commande (11) qui fait fonctionner le circuit de refroidissement conformément à un procédé d'exploitation selon l'une des revendications 1 à 12.
  16. Circuit de refroidissement selon la revendication 15,
    caractérisé
    en ce qu'une zone de refroidissement (1) du circuit de refroidissement à l'intérieur de laquelle l'agent de refroidissement (2) est appliqué sur le produit à laminer (3) chaud est située à l'intérieur d'un train de laminoir et/ou en amont d'un train de laminoir et/ou en aval du train de laminoir.
EP17206426.3A 2017-12-11 2017-12-11 Commande améliorée de la gestion de l'eau d'un circuit de refroidissement Active EP3495056B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP17206426.3A EP3495056B1 (fr) 2017-12-11 2017-12-11 Commande améliorée de la gestion de l'eau d'un circuit de refroidissement
PCT/EP2018/081500 WO2019115145A1 (fr) 2017-12-11 2018-11-16 Régulation améliorée de la gestion de l'eau d'une zone de refroidissement
CN201880079935.XA CN111432950B (zh) 2017-12-11 2018-11-16 冷却段的水资源管理的改善式控制
US16/771,500 US11135631B2 (en) 2017-12-11 2018-11-16 Control of the water economy of a cooling path
EP18800210.9A EP3723919A1 (fr) 2017-12-11 2018-11-16 Régulation améliorée de la gestion de l'eau d'une zone de refroidissement

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17206426.3A EP3495056B1 (fr) 2017-12-11 2017-12-11 Commande améliorée de la gestion de l'eau d'un circuit de refroidissement

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EP3495056A1 EP3495056A1 (fr) 2019-06-12
EP3495056B1 true EP3495056B1 (fr) 2020-09-16

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EP18800210.9A Withdrawn EP3723919A1 (fr) 2017-12-11 2018-11-16 Régulation améliorée de la gestion de l'eau d'une zone de refroidissement

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EP3896286A1 (fr) 2020-04-14 2021-10-20 Primetals Technologies Germany GmbH Fonctionnement d'une pompe d'un dispositif de refroidissement sans l'utilisation d'un champ caractéristique multidimensionnel mesuré
EP3895819B1 (fr) 2020-04-14 2023-06-07 Primetals Technologies Germany GmbH Fonctionnement d'un dispositif de refrodissement avec une pression de fonctionnement minimale
JP7545049B2 (ja) 2021-01-13 2024-09-04 日本製鉄株式会社 制御装置、制御方法、およびプログラム
DE102021001967A1 (de) 2021-04-15 2022-10-20 Primetals Technologies Germany Gmbh Druckstoßfreies Aus- und Einkoppeln von Pumpen
DE102022208447A1 (de) 2022-08-15 2024-02-15 Sms Group Gmbh Verfahren, Computerprogramm und Kühlsystem zum Überwachen einer Komponente des Kühlsystems in einem Walzwerk

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JPS5524933A (en) * 1978-08-08 1980-02-22 Nippon Steel Corp Rapid quenching apparatus for high-temperature steel being transported
JPH04167916A (ja) * 1990-10-30 1992-06-16 Sumitomo Metal Ind Ltd スプレー用給水圧力制御装置
EP1596999B2 (fr) * 2003-02-25 2011-05-25 Siemens Aktiengesellschaft Procede de regulation de la temperature d'une bande metallique, en particulier dans un parcours de refroidissement
EP2644719A1 (fr) * 2012-03-28 2013-10-02 Siemens Aktiengesellschaft Commande de refroidissement
DE102012215599A1 (de) * 2012-09-03 2014-03-06 Sms Siemag Ag Verfahren und Vorrichtung zur dynamischen Versorgung einer Kühleinrichtung zum Kühlen von Metallband oder sonstigem Walzgut mit Kühlmittel
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
EP2767353A1 (fr) * 2013-02-15 2014-08-20 Siemens VAI Metals Technologies GmbH Tunnel de refroidissement avec Power Cooling et refroidissement à flux laminaire
CN204685675U (zh) * 2015-05-27 2015-10-07 鞍钢股份有限公司 一种热轧板带气雾冷却装置

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WO2019115145A1 (fr) 2019-06-20
CN111432950A (zh) 2020-07-17
EP3495056A1 (fr) 2019-06-12
US11135631B2 (en) 2021-10-05
EP3723919A1 (fr) 2020-10-21
US20200376527A1 (en) 2020-12-03
CN111432950B (zh) 2022-04-26

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