EP3895819B1 - Fonctionnement d'un dispositif de refrodissement avec une pression de fonctionnement minimale - Google Patents

Fonctionnement d'un dispositif de refrodissement avec une pression de fonctionnement minimale Download PDF

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Publication number
EP3895819B1
EP3895819B1 EP20169326.4A EP20169326A EP3895819B1 EP 3895819 B1 EP3895819 B1 EP 3895819B1 EP 20169326 A EP20169326 A EP 20169326A EP 3895819 B1 EP3895819 B1 EP 3895819B1
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EP
European Patent Office
Prior art keywords
control
pump assembly
provisional
cooling
coolant
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.)
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Application number
EP20169326.4A
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German (de)
English (en)
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EP3895819A1 (fr
Inventor
Klaus Weinzierl
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Primetals Technologies Germany GmbH
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Primetals Technologies Germany GmbH
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Publication date
Application filed by Primetals Technologies Germany GmbH filed Critical Primetals Technologies Germany GmbH
Priority to EP20169326.4A priority Critical patent/EP3895819B1/fr
Priority to EP20169741.4A priority patent/EP3895820A1/fr
Priority to US17/915,350 priority patent/US20230191465A1/en
Priority to PCT/EP2021/058174 priority patent/WO2021209251A1/fr
Priority to JP2022562567A priority patent/JP7524345B2/ja
Priority to BR112022020917A priority patent/BR112022020917A2/pt
Priority to CN202180028584.1A priority patent/CN115397575A/zh
Publication of EP3895819A1 publication Critical patent/EP3895819A1/fr
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Publication of EP3895819B1 publication Critical patent/EP3895819B1/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
    • 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
    • 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
    • C21D11/005—Process control or regulation for heat treatments for cooling
    • 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
    • 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

Definitions

  • the present invention is also based on a computer program that includes machine code that can be processed by a control device of a cooling device for cooling hot metal rolling stock, the processing of the machine code by the control device causing the control device to operate the cooling device according to such an operating method .
  • the present invention is also based on a control device of a cooling device for cooling a hot rolling stock made of metal, wherein the control device with a such a computer program is programmed so that the control device operates the cooling device according to such an operating method.
  • a cooling device for cooling a hot metal rolling stock in which a liquid coolant is fed via a pump arrangement into a collecting line, from which branch lines lead to application devices, by means of which the coolant is applied to the rolling stock.
  • Control valves are arranged in the branch lines.
  • the control device determines a control state for the pump arrangement and control values for the control valves on the basis of setpoint currents that are known to it and that are to be supplied to the application devices, and controls the pump arrangement and the control valves accordingly at.
  • the manifold is either under high pressure or under low pressure.
  • the higher coolant pressure is only generated when it is actually required.
  • the need for the high pressure is considered to be given if, at low pressure, the open position of at least one valve would exceed a specific open position specified as a limit value.
  • a cooling device for cooling a hot metal rolling stock in which a liquid coolant is fed via a pump arrangement into a collecting line, from which stub lines lead to application devices, by means of which the coolant is applied to the rolling stock.
  • Control valves are arranged in the branch lines. Target currents that are to be supplied to the application devices become known to a control device of the cooling device.
  • the control device determines corresponding activation values of the control valves and also activates them in this way.
  • a - possibly variable - control of the pump can be found in the WO 2014/124867 A1 no explanations.
  • a cooling device for cooling a hot rolling stock made of metal in which a liquid coolant is fed via a pump arrangement into a collecting line, from which branch lines branch off to application devices, by means of which the coolant is applied to the rolling stock.
  • Control valves are arranged in the branch lines.
  • a control device of the cooling device determines a total current based on setpoint currents that are to be supplied to the application devices, and based on the total current a control state of the pump arrangement.
  • the working pressure in the manifold can be adjusted between a minimum value and a maximum value.
  • the control valves can be adjusted between fully closed and fully open positions. To set the individual target currents, the control device varies both the opening positions of the valves and the line pressure that the pump generates in the manifold.
  • a cooling device for cooling a hot metal rolling stock, in which a liquid coolant is fed via a pump arrangement into a collecting line, from which stub lines lead to application devices, by means of which the coolant is applied to the rolling stock.
  • Control valves are arranged in the branch lines.
  • a control device determines a control state for the pump arrangement as a function of the target currents that are to be supplied to the application devices. In addition to the total amount of water to be carried, the control device takes into account a change in the amount of water and a line resistance. If the opening positions of the control valves fall below minimum distances from a minimum possible opening position and a maximum possible opening position, the control status of the pump and thus also the working pressure are adjusted.
  • a cooling device for cooling a hot metal rolling stock in which a liquid coolant is applied to the rolling stock by means of a plurality of application devices.
  • the application devices are each fed via their own pump. Valves between each pump and each applicator are continuously maintained in a fully open condition.
  • the pumped amounts of coolant are set exclusively by appropriate time-variable activation of the pumps.
  • control valves are fed via pumps.
  • a typical arrangement is that several control valves are supplied via a collecting line, the collecting line being supplied with coolant by a pump arrangement becomes.
  • the pump arrangement can have one pump or several pumps.
  • the coolant is applied to the rolling stock by means of the application devices (these are often designed as spray bars). In some cases there may be additional applicators that do not apply the coolant to the rolled stock but otherwise dispense the coolant. This can be useful, for example, to equalize the amount of coolant that is delivered overall.
  • the object of the present invention is to create possibilities by means of which a conventional cooling device--ie a cooling device in which the coolant applied to the rolling stock is metered by controlling control valves--can be operated in an improved manner.
  • the limit modulations of the control valves are the maximum modulations of the control valves.
  • the limit modulations of the control valves are slightly below, that is to say are only close to the maximum modulations of the control valves.
  • the limit modulations of the control valves correspond to a high percentage of the maximum modulations of the control valves, for example 80%, 90% or 95%.
  • the limit modulations can also have other values. In particular, a value of 80% should not be undercut.
  • the figures continue to refer to the coolant flows, i.e. the effect resulting from the activation of the respective control valve. On the other hand, they do not refer to the manipulated variables with which the control valves are controlled.
  • the limit modulations can be specified individually for the respective control valve as required, or can be specified uniformly for all control valves. A group specification is also possible.
  • the control device preferably takes into account secondary conditions related to the pump arrangement as part of the determination of the provisional control state. This can ensure that the pump arrangement is always operated in a permissible operating range.
  • the control device can, for example, check whether it can determine a permissible control state of the pump arrangement in which the pump arrangement delivers the required total flow and also causes the greatest of the determined individual working pressures in the collecting line. If this is the case, this working pressure or a value directly derived from this working pressure can be used as the final working pressure. If this is not the case, the control device can gradually increase the working pressure, starting from the provisional working pressure, until a permissible control state of the pump arrangement is found.
  • the control device preferably takes into account secondary conditions related to the control valves as part of the determination of the provisional control state. For example, the control device can determine and check the associated control values of the control valves for a permissible control state of the pump arrangement, which on the one hand delivers the required total flow and on the other hand causes a working pressure in the collecting line that is at least as high as the highest of the individual working pressures. whether and, if so, to what extent undesired states occur. If this is the case, either the undesired states can be accepted or the control state of the pump arrangement can be adjusted. Which measure is taken can be decided depending on the situation of the individual case.
  • the control device When determining the final activation state of the pump arrangement, the control device preferably also takes into account at least one previous final activation state of the pump arrangement and/or at least one provisional activation state of the pump arrangement that is expected in the future. For example, the controller can use a predictive model Determine the provisional control status.
  • the control device can also set an optimization problem, for example, which includes the minimization of the provisional working pressure according to the invention and other circumstances. Examples of such circumstances are a change in the provisional or the final working pressure and a change in the control status of the pump arrangement.
  • the object is also achieved by a computer program with the features of claim 7.
  • the execution of the computer program causes the control device to operate the cooling device according to an operating method according to the invention.
  • a cooling device for cooling hot rolling stock made of metal with the features of claim 6.
  • a cooling device of the type mentioned at the beginning has a control device according to the invention, which operates the cooling device according to an operating method according to the invention.
  • a rolling line has at least one roll stand 1 .
  • a hot rolling stock 2 is rolled in the rolling line, ie its cross section is reduced.
  • the rolling stock 2 can consist of steel or aluminum, for example. But it can also consist of another metal, such as brass or copper.
  • the rolling stock 2 can be a flat rolling stock, for example a strip or a heavy plate. However, it can also have a different shape, for example it can be in the form of a rod or a profile or a tube.
  • the rolling line also has a cooling device 3 .
  • the cooling device 3 is as shown in FIG 1 the roll stand 1 downstream. However, this is not absolutely necessary.
  • the cooling device 3 could also be arranged upstream of the roll stand 1, for example in the form of a so-called interstand cooling system between the finishing stands of a multi-stand finishing train or in the form of a pre-strip cooling system between the first finishing stand of a multi-stand finishing train and a roughing stand. Other arrangements are also possible.
  • the cooling device 3 has a collecting line 4 .
  • a liquid coolant 6 is fed into the collecting line 4 via a pump arrangement 5 .
  • the pump assembly 5 must be connected to a reservoir 7 on the input side for this purpose.
  • other configurations are also possible, for example a direct supply of the pump arrangement 5 via a water distribution network.
  • the pump arrangement 5 can be installed as shown in FIG 1 have several pumps 8 .
  • the pumps 8 are in accordance with the embodiment FIG 1 connected in parallel.
  • the pumps 8 could also be arranged in series one behind the other. Combinations of this procedure are also possible, for example three lines in which two pumps 8 are arranged in series one behind the other. It is also possible that only a single pump 8 is present.
  • the coolant 6 is usually water or consists at least essentially (98% and more) of water.
  • Branch lines 9a to 9d go from the collecting line 4 to application devices 10a to 10d.
  • the application devices 10a to 10d are therefore connected to the collecting line 4 via the branch lines 9a to 9d.
  • the coolant 6 is applied to the rolling stock 2 by means of the application devices 10a to 10d.
  • the application devices 10a to 10d can be designed, for example, as so-called cooling beams or spray beams.
  • the application devices 10a to 10d are as shown in FIG 1 arranged above the rolling stock 2 and consequently bring the coolant 6 onto the rolling stock 2 from above. However, this is not mandatory.
  • the application devices 10a to 10d could also be arranged below the rolling stock 2 or at a different location. It is also possible for the application devices 10a to 10d to apply the coolant 6 to the rolling stock 2 from different sides. It is also possible that not all application devices 10a to 10d apply the coolant 6 to the rolling stock 2, but rather at least one--if they do, then usually one or two--of the application devices 10a to 10d do not apply the coolant 6 to the rolling stock 2. Appropriate Configurations and the reasons for this are, for example, in the already mentioned WO 2019/115 145 A1 explained.
  • FIG 1 a total of four application devices 10a to 10d shown.
  • the number of application devices 10a to 10d could also be larger or smaller. It just has to be greater than 1.
  • Control valves 11a to 11d are arranged in the branch lines 9a to 9d.
  • the control valves 11a to 11d can be designed as ball valves, for example. Irrespective of their specific design, however, the control valves 11a to 11d can be adjusted continuously.
  • the term “continuously adjust” is explained below using the illustration in FIG 2 explained for the control valve 11a. Analogous statements apply to the other control valves 11b to 11d.
  • the control valve 11a is controlled with a control value Aa.
  • the control value Aa lies between a minimum control value Amin and a maximum control value Amax.
  • the control value Aa can be varied continuously or at least in several stages.
  • the control value Aa can therefore—possibly within the scope of a setting accuracy—take on several possible values between the minimum control value Amin and the maximum control value Amax.
  • the minimum control value Amin and the maximum control value Amax can be 0° and 90° and the control value Aa can be set in steps of, for example, 0.1° or 0.2° between these two extreme values Amin, Amax.
  • a corresponding reference coolant flow KR flows through the control valve 11a and thus through the corresponding branch line 9a, depending on the control value Aa. Due to the possibility of continuously adjusting the control valve 11a, the reference coolant flow KR also runs through a corresponding value continuum between a minimum value KRmin (usually 0) and a maximum value KRmax (which is of course greater than the minimum value KRmin).
  • the reference coolant flow KR divided by the maximum value KRmax corresponds to a control ka of the control valve 11a.
  • the modulation ka has a maximum value of 1 and usually a minimum value of 0.
  • the functional relationship of the reference coolant flow KR (or the equivalent of the control ka) as a function of the control value Aa corresponds to a characteristic curve for the control valve 11a.
  • the characteristic curve is as shown in FIG 2 often non-linear. Usually, however, there is a strictly monotonic relationship between the control value Aa on the one hand and the reference coolant flow KR or the control ka.
  • actual coolant flow Ka ie, the quantity of coolant 6 actually flowing through control valve 11a—can be readily determined if working pressure pA present on the input side of control valve 11a is known.
  • the value that results from the characteristic curve itself only has to be scaled with the root of the quotient of working pressure pA and reference pressure pR.
  • the working pressure pA and the reference pressure pR may have to be corrected by an offset.
  • this results in the coolant flow Ka zu ca pA ⁇ ⁇ ⁇ G ⁇ Ha PR ⁇ ⁇ ⁇ G ⁇ Ha ⁇ ka ⁇ KR Max ⁇ is the density of the coolant 6, g is the acceleration due to gravity. ha is the elevation of the valve outlet (or applicator 10a) relative to a reference level common to applicators 10a through 10d.
  • hA can be greater or less than 0.
  • the reference level can be chosen as required. For example, it can match the level of a roller table, by means of which the rolling stock 2 is conveyed through the cooling device 3 .
  • the associated control value Aa results directly from the characteristic curve after determining the control ka.
  • the cooling device 3 also has a control device 12 which controls and operates the cooling device 3 .
  • the control device 12 is generally designed as a software-programmable device. This is in FIG 1 indicated by the fact that within the control device 12 the symbol "uP" is located for microprocessor.
  • the control device 12 is programmed with a computer program 13 .
  • the computer program 13 includes machine code 14 which can be processed by the control device 12 . Due to the programming with the computer program 13 or the processing of the machine code 14, the control device 12 operates the cooling device 3 according to an operating method that is described below in connection with 3 is explained in more detail.
  • a step S1 the control device 12 becomes aware of setpoint currents Ka* to Kd*.
  • the target flows Ka* to Kd* indicate—in liters per second, for example—the amounts of coolant 6 that are to be supplied to the respective application device 10a to 10d and released by the respective application device 10a to 10d, in particular to be applied to the rolling stock 2 .
  • the setpoint currents Ka* to Kd* of the control device 12 can be externally specified or can be independently determined by the control device 12 on the basis of other circumstances. Appropriate procedures are generally known to those skilled in the art.
  • the control device 12 determines an individual working pressure pAa for a limit control value kLim of the control valve 11a.
  • the limit control value kLim is specified for the control device 12 .
  • the limit modulation value kLim can be the maximum modulation of the control valve 11a. In many cases, however, it is advantageous if it is as shown in FIG 2 is a value which is close to but below the maximum modulation of the control valve 11a. In this case, the limit control value kLim should be at least 80%, preferably at least 90%, particularly preferably at least 95%. However, a value of 98% should generally not be exceeded.
  • the limit modulation kLim thus corresponds to a high percentage of the maximum modulation of the control valve 11a. For the sake of clarity, it should be made clear that the limit modulation value kLim relates to the modulation ka of the control valve 11a, not to the control Aa of the control valve 11a.
  • the control device 12 determines the individual working pressure pAa in such a way that at the working pressure pAa and the limit modulation kLim of the control valve 11a in the branch line 9a the desired target current Ka* flows.
  • the control device 12 determines individual working pressures pAb to pAd for the other control valves 11b to 11d in a completely analogous manner.
  • the limit modulation kLim, the maximum reference coolant flow KRmax and the reference pressure pR of the other control valves 11b to 11d can have the same values as the limit modulation kLim, the maximum reference coolant flow KRmax and the reference pressure pR of the control valve 11a.
  • Control valves 11b to 11d may vary from control valve 11b to 11d to control valve 11b to 11d. In any case, however, the control device 12 determines the individual working pressures pAb to pAd of the other control valves 11b to 11d independently of one another and also independently of the individual working pressure pAa of the control valve 11a.
  • the control device 12 determines a control state Z of the pump arrangement 5.
  • the control state Z is determined in such a way that the pump arrangement 5 - if it is operated according to the control state Z - pumps a total current K that corresponds to the sum of the target currents Ka* to Kd* equals. Due to the conveyance of the total flow K, the total flow K of coolant 6 is also supplied to the collecting line 4 by means of the pump arrangement 5 .
  • the control state Z is determined in such a way that a working pressure pAv prevails in the collecting line 4 that is at least as great as the highest of the individual working pressures pAa to pAd. However, both the activation state Z and the working pressure pAv are only provisional.
  • the control state Z includes the required speed n at least for each pump 8 of the pump arrangement 5 .
  • the control of the pump arrangement 5 can be changed continuously or at least in several stages. It is therefore not only possible to switch between two or three fixed, discrete control states Z, but the possible control states Z form a continuum or a quasi-continuum.
  • one of the pumps 8 can be operated between a minimum speed nmin of 100 rpm and a maximum speed nmax of 800 rpm
  • the speed n can also be set to intermediate values between 100 rpm and 800 rpm be, for example in the case of a stepless adjustability 150 revolutions/min, 227 revolutions/min or 593 revolutions/min and in the case of an adjustability in steps to at least 10 different steps of for example 100, 150, 200, 250 etc. up to 800 rpm.
  • the numerical values mentioned are of course only to be understood as examples.
  • control device 12 only takes into account the pressure to be generated statically by the pump arrangement 5 in the context of step S4. It is therefore possible for the control device 12 to assume in the context of step S4 that the pressure generated on the output side of the pump arrangement 8 corresponds to the pressure on the input side of the control valves 11a to 11d. However, it is also possible for the control device 12 to take additional circumstances into account. An example of such a situation are changes over time in the setpoint flows Ka* to Kd* and associated changes over time in the total flow K and associated accelerations in water quantities.
  • the control device 12 can, for example, access a family of characteristics to determine its speed n, in which, as shown in FIG FIG 4 is stored for the pump 8, which speed n of the pump 8 is required to bring about a specific pressure increase ⁇ p at a specific total flow K.
  • the suction pressure pS can der Control device 12 be known based on a measurement or otherwise.
  • control state determined for the highest of the individual working pressures pAa to pAd will itself be a permissible control state of the pump arrangement 5 .
  • this control state can be adopted directly as a provisional control state Z.
  • Other possibilities and configurations will be discussed later.
  • step S5 the control device 12 then determines a control state Z′ of the pump arrangement 5.
  • the control state Z′ in contrast to the control state Z—is final.
  • the control device 12 determines the final control state Z′ of the pump arrangement 5 using the provisional control state Z of the pump arrangement 5.
  • the determination of step S5 is such that the collecting line 4 is supplied with the total flow K of coolant 6 by means of the pump arrangement 5.
  • the control device 12 directly and immediately adopts the provisional control state Z as the final control state Z′.
  • the final control state Z′ brings about the final control state in the collecting line 4 if the pump arrangement 8 is used to convey the desired total flow K into the collecting line 4 working pressure pAe.
  • the control device 12 therefore determines the control values Aa to Ad of the control valves 11a to 11d using the final working pressure pAe. The determination is made in such a way that the respective setpoint current Ka* through Kd* flows in the respective stub line 9a through 9d.
  • control device 12 controls the pump arrangement 5 and the control valves 11a to 11d.
  • the pump arrangement 5 is controlled in accordance with the final control state Z′.
  • the control valves 11a to 11d are controlled according to the control values Aa to Ad.
  • the operating method according to the invention is executed with the execution of step S7.
  • the control device 12 returns to step S1 after step S7 has been carried out.
  • the control device 12 executes the sequence of steps S1 to S7 iteratively over and over again.
  • execution takes place with a fixed cycle time.
  • the fixed cycle time is generally between 0.1 s and 1.0 s, mostly between 0.2 s and 0.5 s, for example around 0.3 s.
  • Step S4 of 3 is in accordance with the design 5 divided into steps S11 to S14.
  • step S11 the control device 12 determines the operating state of the pump arrangement 5, which is required to deliver the total flow K and at the same time bring about the required pressure increase ⁇ p from the suction pressure pS to the greatest of the determined individual working pressures pAa to pAd.
  • the control device 12 can determine the corresponding speed n of the pump 8 when there is only one pump 8 .
  • step S12 the control device 12 checks whether the determined provisional state Z is permissible, for example the determined speed n is in the permissible speed range of the pump 8, i.e. the operating point of the pump 8 is within the in FIG 4 unshaded area.
  • the test therefore implies a test for compliance with a secondary condition related to the pump arrangement 5 .
  • the speed n is in the permissible speed range of the pump 8 .
  • an operating point AP1 of the pump 8 that lies within the permissible speed range of the pump 8 can be determined by the total flow K and the highest of the individual working pressures pAa to pAd. If the speed n is in the permissible speed range of the pump 8, the control device 12 goes to step S13. In step S13, the control device 12 does not take any further measures. The determined speed n can be used directly.
  • the speed n is not in the permissible speed range of the pump 8 .
  • the total current K and the largest of the determined individual working pressures pAa bis pAd an operating point AP2 or an operating point AP3 of the pump 8 can be determined.
  • the pump 8 can easily generate the highest of the determined individual working pressures pAa to pAd. Due to the permissible speed range of the pump 8, however, a volumetric flow delivered by the pump 8 that is greater than the required total flow K necessarily results. In the case of the working point AP3, the situation is reversed.
  • the pump 8 can generate the required total flow K without further ado. Due to the permissible speed range of the pump 8, however, there is inevitably a pressure increase ⁇ p caused by the pump 8, which is greater than the minimum required.
  • step S14 the control device 12 modifies the provisional activation state Z.
  • the control device 12 can, for example, for a short-circuit valve 15 (see 6 ) determine an opening state.
  • the short-circuit valve 15 is as shown in FIG 6 the pump 8 connected in parallel. It can be viewed as part of the pump assembly 5 or as a control valve for another applicator.
  • the control device 12 determines the opening state, if necessary, in such a way that via the short-circuit valve 15 so much coolant 6 is fed back directly or indirectly to the reservoir 7 that the remaining volume flow fed to the collecting line 4 as a result corresponds to the desired total flow K.
  • the control device 12 can, for example, modify the provisional activation state Z such that although only the pump 8 is activated (and consequently the short-circuit valve 15, if present, remains closed), in the provisional activation state Z, however, with the desired total flow K a preliminary working pressure pAv is generated that is greater than the largest of the individual working pressures pAa to pAd.
  • the provisional working pressure pAv is preferably set to the minimum of the possible and permissible values.
  • step S4 of 3 is in accordance with the design FIG 7 divided into steps S21 to S24.
  • the procedure of FIG 7 can, as needed, with the procedure of 5 be combined or realized independently of it.
  • step S21 can be omitted and steps S22 to S24 are carried out after step S13 or S14.
  • step S21 the control device 12 determines - analogous to step S11 of 5 - The speed n of the pump 8, which is required to promote the total flow K and at the same time to bring about the required pressure increase ⁇ p from the suction pressure pS to the largest of the determined individual working pressures pAa to pAd.
  • step S22 the control device 12 checks whether the actuation of the control valves 11a to 11d is permissible given the provisional working pressure pAv that results.
  • the control device 12 can, for example, check whether adjustment speeds at which the control values Aa to Ad of the control valves 11a to 11b are changed comply with predetermined limits. The test therefore implies a test for compliance with secondary conditions relating to the control valves.
  • step S23 the control device 12 does not take any further measures.
  • the determined speed n can be used directly.
  • step S24 the control device 12--depending on the situation in the individual case--can either accept that the predetermined limits are exceeded or adapt the provisional control state Z of the pump arrangement 5.
  • an increase in the provisional working pressure pAv can, under certain circumstances, result in the predetermined limits no longer being exceeded, or at least only to a lesser extent, due to the corresponding changes in the actuation of the control valves 11a to 11d.
  • step S5 of 3 is in accordance with the design 8 replaced by a step S41.
  • the control device 12 takes into account at least one further control state in addition to the provisional control state Z currently determined in step S4.
  • it can be the immediately preceding final control state Z′ or several preceding final control states Z′.
  • abrupt changes in the final control state Z′ can be avoided by low-pass filtering or similar measures.
  • the target currents Ka* to Kd* can be predicted within a prognosis horizon of several cycle times—for example five, eight or ten cycle times—in a model-predictive manner, so that provisional control states Z of the pump arrangement 5 that are expected in the future can also be determined for the prognosis horizon.
  • the provisional control states Z of the pump arrangement 5 expected in the future can also be included in the determination of the current final control state Z′.
  • a final working pressure pAe results which is smaller (although usually only slightly smaller) than the largest of the individual working pressures pAa to pAd of steps S2 and S3.
  • the limit control values kLim of the control valves 11a to 11d are smaller than their maximum possible control values and/or before considering further control states, first add a small offset to the provisional working pressure pAv or scale the provisional working pressure pAv with a factor slightly greater than 1.
  • the present invention has been explained above in connection with embodiments in which the pump arrangement 5 has only a single pump 8 .
  • configurations in which the pump arrangement 5 has a plurality of pumps 8 are also readily possible.
  • the pumps 8 must be controlled in such a way that all the pumps 8 are either completely blocked so that they can be treated as if they were not present, or generate the same preliminary working pressure pAv and the same final working pressure pAe.
  • there is a degree of freedom with regard to the distribution of the total flow K to the individual pumps 8 To resolve this degree of freedom, it is possible, for example, to distribute the total current K to the pumps 8 uniformly or proportionally to the capacity of the pumps 8 .
  • the collecting line 4 is fed with a single pump 8.
  • the next pump 8 is only switched on when the previously operated pump 8 is no longer able to deliver the required total flow K at the required preliminary working pressure pAv or to promote the required final working pressure pAe.
  • the next pump 8 is only switched on when the previously operated pumps 8 are no longer able to deliver the required total flow K at the required provisional working pressure pAv or the required final working pressure pAe.
  • the present invention was further explained above with reference to a single cooling device 3 .
  • the additional cooling devices 3 can be controlled by the control device 12 or by another control device as required.
  • the cooling devices 3 can be operated independently of one another.
  • the present invention has many advantages.
  • the energy consumption is very low.
  • savings of at least 25% and sometimes well over 80% result.
  • the reduction in the final working pressure pAe leads to such a great deterioration in the efficiency of the pump arrangement 5 that the energy consumption increases. In practice, however, this does not happen.
  • both the mechanics of the control valves 11a to 11d and the mechanics of the pump arrangement 5 are protected.
  • control valves 11a to 11d are operated as open as possible. It is also advantageous for the pump arrangement 5 if it is operated at the lowest possible speed. In contrast, there are no disadvantageous effects for the cooling of the rolling stock 2 as such.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Materials Engineering (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Thermal Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Metallurgy (AREA)
  • Organic Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Control Of Metal Rolling (AREA)

Claims (7)

  1. Procédé de fonctionnement d'un dispositif de refroidissement (3) pour refroidir un produit laminé chaud (2) en métal,
    - dans lequel le dispositif de refroidissement (3) présente une conduite collectrice (4) dans laquelle un agent de refroidissement liquide (6) est alimenté par un agencement de pompes (5) et de laquelle part une pluralité de conduites de dérivation (9a à 9d) vers des dispositifs d'application (10a à 10d),
    - dans lequel l'agencement de pompes (5) présente un certain nombre de pompes (8), une vanne de régulation (11a à 11d) est respectivement disposée dans les conduites de dérivation (9a à 9d) et l'agent de refroidissement (6) est appliqué sur le produit laminé (2) au moyen d'au moins une partie des dispositifs d'application (10a à 10d),
    - dans lequel on fait connaître à un dispositif de commande (12) du dispositif de refroidissement (3) des courants de consigne (Ka* à Kd*) qui doivent être amenés aux dispositifs d'application (10a à 10d),
    - dans lequel le dispositif de commande (12) commande l'agencement de pompes (5) selon un état de commande final (Z') et les vannes de régulation (11a à 11d) selon des valeurs de commande (Aa à Ad),
    caractérisé en ce que le dispositif de commande (12) sert à déterminer l'état de commande final (Z') de l'agencement de pompes (5) et les valeurs de commande (Aa à Ad) des vannes de régulation (11a à 11d).
    - pour les vannes de régulation (11a à 11d), on détermine pour une valeur de commande limite respective (kLim) de la vanne de régulation respective (11a à 11d) une pression de travail individuelle respective (pAa à pAd) qui doit régner dans la conduite collectrice (4) pour que le courant de consigne respectif (Ka* à Kd*) circule dans la conduite de dérivation respective (9a à 9d),
    - on détermine un état de commande provisoire (Z) du dispositif de pompage (5), de sorte qu'un courant total (K) d'agent de refroidissement (6), qui correspond à la somme des courants de consigne (Ka* à Kd*), est amené à la conduite collectrice (4) au moyen du dispositif de pompage (5), et qu'il règne simultanément dans la conduite collectrice (4) une pression de travail provisoire (pAv), qui est au moins aussi grande que la plus grande des pressions de travail individuelles (pAa à pAd),
    - l'état de commande final (Z') de l'agencement de pompes (5) est déterminé en utilisant l'état de commande provisoire (Z) de l'agencement de pompes (5) de telle sorte que le courant total (K) de l'agent de refroidissement (6) est amené à la conduite collectrice (4) au moyen de l'agencement de pompes (5) et qu'il règne en même temps une pression de travail finale (pAe) dans la conduite collectrice (4), et
    - les valeurs de commande (Aa à Ad) des vannes de régulation (11a à 11d) sont déterminées en utilisant la pression de travail finale (pAe) de telle sorte que le courant de consigne respectif (Ka* à Kd*) circule dans la conduite de dérivation respective (9a à 9d).
  2. Procédé d'exploitation selon la revendication 1, caractérisé en ce que les valeurs de réglage limites (kLim) des vannes de régulation (11a à 11d) sont les réglages maximaux des vannes de régulation (11a à 11d) ou se situent au voisinage des réglages maximaux des vannes de régulation (11a à 11d).
  3. Procédé d'exploitation selon la revendication 1 ou 2, caractérisé en ce que le dispositif de commande (12) tient compte, dans le cadre de la détermination de l'état de commande provisoire (Z), de conditions secondaires se rapportant à l'agencement de pompes (5).
  4. Procédé d'exploitation selon la revendication 1, 2 ou 3, caractérisé en ce que le dispositif de commande (12) tient compte, dans le cadre de la détermination de l'état de commande provisoire (Z), de conditions secondaires se rapportant aux vannes de régulation (11a à 11d).
  5. Procédé d'exploitation selon l'une des revendications ci-dessus,
    caractérisé en ce que le dispositif de commande (12) prend en outre en compte, dans le cadre de la détermination de l'état de commande final (Z') de l'agencement de pompes (5), au moins d'un état de commande final précédent (Z') de l'agencement de pompes (5) et/ou au moins d'un état de commande provisoire prévu dans le futur (Z) de l'agencement de pompes (5).
  6. Dispositif de refroidissement pour refroidir un produit laminé chaud (2) en métal,
    - dans lequel le dispositif de refroidissement comprend une conduite collectrice (4), un agencement de pompes (5) et une pluralité de dispositifs d'application (10a à 10d),
    - dans lequel un agent de refroidissement liquide (6) est appliqué sur le produit laminé (2) au moyen d'au moins une partie des dispositifs d'application (10a à 10d),
    - dans lequel les dispositifs d'application (10a à 10d) sont reliés à la conduite collectrice (4) par une ligne de dérivation respective (9a à 9d),
    - dans lequel l'agencement de pompes (5) présente un certain nombre de pompes (8) au moyen desquelles l'agent de refroidissement liquide (6) est alimenté dans la conduite collectrice (4),
    - dans lequel une vanne de régulation (11a à 11d) est disposée dans chacune des conduites de dérivation (9a à 9d),
    - dans lequel le dispositif de refroidissement comprend un dispositif de commande (12) qui fait fonctionner le dispositif de refroidissement selon un procédé de fonctionnement selon l'une quelconque des revendications 1 à 5.
  7. Programme informatique comprenant un code machine (14) pouvant être traité par un dispositif de commande (12) d'un dispositif de refroidissement (3) selon la revendication 6 pour refroidir un produit laminé chaud (2) en métal, le traitement du code machine (14) par le dispositif de commande (12) amenant le dispositif de commande (12) à faire fonctionner le dispositif de refroidissement (3) selon un procédé de fonctionnement selon les revendications 1-5.
EP20169326.4A 2020-04-14 2020-04-14 Fonctionnement d'un dispositif de refrodissement avec une pression de fonctionnement minimale Active EP3895819B1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP20169326.4A EP3895819B1 (fr) 2020-04-14 2020-04-14 Fonctionnement d'un dispositif de refrodissement avec une pression de fonctionnement minimale
EP20169741.4A EP3895820A1 (fr) 2020-04-14 2020-04-16 Fonctionnement d'un dispositif de réfrigération à une pression de fonctionnement minimale
PCT/EP2021/058174 WO2021209251A1 (fr) 2020-04-14 2021-03-29 Fonctionnement d'une unité de refroidissement à pression de travail minimale
JP2022562567A JP7524345B2 (ja) 2020-04-14 2021-03-29 最小限の動作圧力を用いた冷却ユニットの運転
US17/915,350 US20230191465A1 (en) 2020-04-14 2021-03-29 Operation of a cooling unit with a minimal working pressure
BR112022020917A BR112022020917A2 (pt) 2020-04-14 2021-03-29 Operação de uma unidade de refrigeração com uma pressão de funcionamento mínima
CN202180028584.1A CN115397575A (zh) 2020-04-14 2021-03-29 以最小工作压力运行冷却装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20169326.4A EP3895819B1 (fr) 2020-04-14 2020-04-14 Fonctionnement d'un dispositif de refrodissement avec une pression de fonctionnement minimale

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EP3895819B1 true EP3895819B1 (fr) 2023-06-07

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EP20169741.4A Withdrawn EP3895820A1 (fr) 2020-04-14 2020-04-16 Fonctionnement d'un dispositif de réfrigération à une pression de fonctionnement minimale

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US (1) US20230191465A1 (fr)
EP (2) EP3895819B1 (fr)
JP (1) JP7524345B2 (fr)
CN (1) CN115397575A (fr)
BR (1) BR112022020917A2 (fr)
WO (1) WO2021209251A1 (fr)

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DE102022128358A1 (de) 2022-10-26 2024-05-02 Sms Group Gmbh Kühlmodul, Kühlgruppe, Kühlsystem, Verfahren, warmgewalztes metallisches bandförmiges Produkt und Verwendung

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5431201B2 (fr) * 1972-09-28 1979-10-05
JPH0819915B2 (ja) * 1985-12-02 1996-03-04 株式会社日立製作所 可変速ポンプの運転装置
JP2010209698A (ja) 2009-03-06 2010-09-24 Toshiba Mitsubishi-Electric Industrial System Corp 冷却設備ポンプ省エネ制御装置
US9180505B2 (en) 2010-01-29 2015-11-10 Toshiba Mitsubishi-Electric Industral Systems Corporation Water injection controller, water injection control method, and water injection control program for rolling lines
EP2667033B1 (fr) 2011-01-21 2019-10-23 Ebara Corporation Dispositif d'approvisionnement en eau
JP2012207546A (ja) 2011-03-29 2012-10-25 Hitachi Ltd ポンプ消費電力特性モデル作成装置、ポンプ消費電力特性モデル作成方法、ポンプ消費電力特性モデル作成プログラム、およびこのプログラムを記録した記録媒体
EP2644718A1 (fr) 2012-03-27 2013-10-02 Siemens Aktiengesellschaft Procédé de stabilisation de pression
EP2644719A1 (fr) 2012-03-28 2013-10-02 Siemens Aktiengesellschaft Commande 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
EP2767353A1 (fr) 2013-02-15 2014-08-20 Siemens VAI Metals Technologies GmbH Tunnel de refroidissement avec Power Cooling et refroidissement à flux laminaire
JP5994999B2 (ja) 2013-03-15 2016-09-21 Ｊｆｅスチール株式会社 熱間圧延ラインの冷却装置の制御方法
CN103861879B (zh) 2014-03-28 2016-09-07 东北大学 一种中厚板在线冷却装置及控制方法
EP3395463B1 (fr) * 2017-04-26 2019-12-25 Primetals Technologies Austria GmbH Refroidissement d'un laminé
EP3495056B1 (fr) 2017-12-11 2020-09-16 Primetals Technologies Austria GmbH Commande améliorée de la gestion de l'eau d'un circuit de refroidissement
DE102018205684A1 (de) * 2018-04-13 2019-10-17 Sms Group Gmbh Kühleinrichtung und Verfahren zu deren Betrieb
EP3599037A1 (fr) 2018-07-25 2020-01-29 Primetals Technologies Germany GmbH Section de refroidissement à réglage de flux de liquide de refroidissement à l'aide des pompes

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Publication number Publication date
EP3895820A1 (fr) 2021-10-20
CN115397575A (zh) 2022-11-25
WO2021209251A1 (fr) 2021-10-21
EP3895819A1 (fr) 2021-10-20
US20230191465A1 (en) 2023-06-22
JP2023525657A (ja) 2023-06-19
JP7524345B2 (ja) 2024-07-29
BR112022020917A2 (pt) 2022-12-06

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