EP3895820A1 - Fonctionnement d'un dispositif de réfrigération à une pression de fonctionnement minimale - Google Patents

Fonctionnement d'un dispositif de réfrigération à une pression de fonctionnement minimale Download PDF

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Publication number
EP3895820A1
EP3895820A1 EP20169741.4A EP20169741A EP3895820A1 EP 3895820 A1 EP3895820 A1 EP 3895820A1 EP 20169741 A EP20169741 A EP 20169741A EP 3895820 A1 EP3895820 A1 EP 3895820A1
Authority
EP
European Patent Office
Prior art keywords
control
pump arrangement
control device
collecting line
cooling device
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.)
Withdrawn
Application number
EP20169741.4A
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German (de)
English (en)
Inventor
Klaus Weinzierl
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 Germany GmbH
Original Assignee
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 Germany GmbH filed Critical Primetals Technologies Germany GmbH
Priority to CN202180028584.1A priority Critical patent/CN115397575A/zh
Priority to US17/915,350 priority patent/US20230191465A1/en
Priority to BR112022020917A priority patent/BR112022020917A2/pt
Priority to PCT/EP2021/058174 priority patent/WO2021209251A1/fr
Priority to JP2022562567A priority patent/JP7524345B2/ja
Publication of EP3895820A1 publication Critical patent/EP3895820A1/fr
Withdrawn legal-status Critical Current

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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
    • 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 further based on a computer program that includes machine code that can be processed by a control device of a cooling device for cooling a hot rolled stock made of metal, 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 further 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 rolling stock made of metal in which a pump arrangement feeds a liquid coolant 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 uses its known setpoint currents to be supplied to the application devices to determine a control state for the pump arrangement and control values for the control valves and controls the pump arrangement and the control valves accordingly at.
  • the manifold is either under high pressure or under low pressure. The higher pressure of the coolant is only generated when it is actually needed. The need for high pressure is considered to be given if, at low pressure, the opening position of at least one valve would exceed a certain opening position specified as a limit value.
  • a cooling device for cooling a hot rolled stock made of metal in which a liquid coolant is fed into a collecting line via a pump arrangement, 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. Setpoint currents which are to be fed to the application devices are known to a control device of the cooling device. The control device determines corresponding control values of the control valves and controls them in this way.
  • About a - possibly variable - control of the pump can be found in the WO 2014/124 867 A1 no explanations.
  • a cooling device for cooling a hot rolled stock made of metal in which a liquid coolant is fed into a collecting line via a pump arrangement, 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.
  • a control device of the cooling device determines a total current on the basis of setpoint currents that are to be fed to the application devices and, on the basis of the total current, a control state of the pump arrangement.
  • the working pressure in the collecting line can be set between a minimum value and a maximum value.
  • the control valves can be set 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 rolled stock made of metal in which a liquid coolant is fed into a collecting line via a pump arrangement, 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.
  • a control device determines a control state for the pump arrangement as a function of the setpoint 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 state of the pump and thus also the working pressure are adapted.
  • a cooling device for cooling a hot rolling stock made of metal 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 by their own pump. Valves between the respective pump and the respective application device are continuously kept in a fully open state. The setting of the conveyed quantities of coolant takes place exclusively through corresponding time-variable control of the pumps.
  • control valves are fed by pumps.
  • a typical arrangement here is a supply of several control valves via a collecting line, the collecting line being supplied with coolant by a pump arrangement will.
  • the pump arrangement can have one pump or also several pumps.
  • the coolant is applied to the rolling stock by means of the application devices (these are often designed as spray bars).
  • additional application devices can be present which do not apply the coolant to the rolling stock, but instead deliver the coolant in some other way. This can be useful, for example, to equalize the amount of coolant that is conveyed overall.
  • the object of the present invention is to create possibilities by means of which a conventional cooling device - that is, a cooling device in which the coolant applied to the rolling stock is metered via the control of 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, are only in the vicinity of the maximum modulations of the control valves.
  • the limit modulations of the control valves thus 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 also relate to the coolant flows, i.e. the effect resulting from the activation of the respective control valve. However, they do not relate 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 uniformly specified for all control valves. A group-wise specification is also possible.
  • the control device preferably takes into account secondary conditions related to the pump arrangement in the course of determining the preliminary control state. This ensures 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 on the one hand delivers the required total flow and on the other causes the greatest of the individual working pressures determined in the collecting line. If this is the case, this working pressure or a value derived directly 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 preliminary 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 when determining the preliminary control state.
  • the control device can, for example, 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 greatest of the individual working pressures, whether and, if so, to what extent undesirable conditions occur. If this is the case, either the undesired states can be accepted or the control state of the pump arrangement can be adapted. Which measure is taken can be decided depending on the situation of the individual case.
  • the control device preferably also takes into account at least one previous final control state of the pump arrangement and / or at least one preliminary control state of the pump arrangement expected in the future.
  • the control device can be a model predictive Determine the preliminary control status.
  • the control device can also, for example, set an optimization problem into which, on the one hand, the minimization of the preliminary working pressure according to the invention is included and, on the other hand, further facts are included. Examples of such circumstances are a change in the preliminary or the final working pressure and a change in the control state of the pump arrangement.
  • the object is also achieved by a computer program with the features of claim 6.
  • the processing of the computer program has the effect that the control device operates the cooling device according to an operating method according to the invention.
  • control device having the features of claim 7.
  • the control device is programmed with a computer program according to the invention, so that the control device operates the cooling device according to an operating method according to the invention.
  • a cooling device for cooling hot rolled metal with the features of claim 8.
  • a cooling device of the type mentioned at the outset 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. Is shown in FIG 1 only a single roll stand 1. In many cases, however, there are several roll stands 1 arranged one behind the other, so that the rolling line is designed as a rolling train.
  • a hot rolling stock 2 is rolled, that is, 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, for example 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 FIG 1 downstream of the roll stand 1. 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 intermediate stand cooling between the finishing stands of a multi-stand finishing train or be arranged in the form of a pre-strip cooling 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 arrangement 5 can be connected on the inlet side to a reservoir 7 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 according to the illustration in FIG FIG 1 have several pumps 8.
  • the pumps 8 are designed according to FIG FIG 1 connected in parallel to each other.
  • the pumps 8 could, however, also be arranged in series one behind the other. Combinations of this procedure are also possible, for example three lines in each of 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 mostly water or consists at least essentially (98% and more) of water.
  • branch lines 9a to 9d go 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 bars or spray bars.
  • the application devices 10a to 10d are as shown in FIG FIG 1 Arranged above the rolling stock 2 and consequently apply the coolant 6 to the rolling stock 2 from above. However, this is not absolutely necessary.
  • the application devices 10a to 10d could also be arranged below the rolling stock 2 or be arranged elsewhere. 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, then usually one or two - of the application devices 10a to 10d does not apply the coolant 6 to the rolling stock 2. Appropriate Refinements and the reasons for this are for example in that already mentioned WO 2019/115 145 A1 explained.
  • FIG 1 a total of four application devices 10a to 10d are shown.
  • the present invention is explained in connection with this number of application devices 10a to 10d.
  • the number of application devices 10a to 10d could, however, 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. Regardless of their specific design, the control valves 11a to 11d can, however, be adjusted continuously.
  • the term “continuously adjusting” is used below with reference to the illustration in FIG 2 for the control valve 11a explained. 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 - assume 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 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. 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 (mostly 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 modulation 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, equivalently, the modulation 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 modulation ka.
  • the actual coolant flow Ka - that is, the amount of coolant 6 actually flowing through the control valve 11a - can easily be determined, provided that the working pressure pA at the input side of the control valve 11a is known.
  • the value that results from the characteristic curve itself only has to be scaled with the square root of the quotient of working pressure pA and reference pressure pR.
  • the working pressure pA and the reference pressure pR may still have to be corrected by an offset.
  • the coolant flow Ka zu results Ka pA - ⁇ ⁇ G ⁇ Ha pR - ⁇ ⁇ G ⁇ Ha ⁇ ka ⁇ KR Max
  • ⁇ is the density of the coolant 6, g the acceleration due to gravity.
  • ha is the height of the valve outlet (or of the application device 10a) relative to a reference level which is uniform for the application devices 10a to 10d.
  • hA can - depending on the arrangement of the valve outlet relative to the reference level - be greater or less than 0.
  • the reference level can be selected as required. It can, for example, correspond to the level of a roller table by means of which the rolling stock 2 is conveyed through the cooling device 3.
  • the associated activation value Aa results directly from the characteristic curve after the modulation ka has been determined.
  • 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 the symbol " ⁇ P" for microprocessor is drawn in within the control device 12.
  • the control device 12 is programmed with a computer program 13.
  • the computer program 13 comprises machine code 14 which can be processed by the control device 12.
  • the control device 12 operates the cooling device 3 according to an operating method which is described below in connection with FIG 3 is explained in more detail.
  • setpoint currents Ka * to Kd * are known to control device 12.
  • the nominal flows Ka * to Kd * indicate - for example in liters per second - the quantities of coolant 6 that are to be supplied to the respective application device 10a to 10d and delivered 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 specified externally or can be determined independently by the control device 12 on the basis of other conditions. 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 modulation 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 that is close to but below the maximum modulation of the control valve 11a. In this case, the limit modulation value kLim should be at least 80%, preferably at least 90%, particularly preferably at least 95%. As a rule, however, a value of 98% should not be exceeded.
  • the limit modulation kLim thus corresponds to a high percentage of the maximum modulation of the control valve 11a.
  • the limit control value kLim relates to the control 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 the desired setpoint current Ka * flows in the branch lines 9a at the working pressure pAa and the limit modulation kLim of the control valve 11a.
  • the control device 12 determines, in a completely analogous manner, individual working pressures pAb to pAd for the other control valves 11b to 11d.
  • 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. Alternatively, it can be about other values, which may also be within the others Control valves 11b to 11d can 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 - delivers a total current K that is the sum of the setpoint currents Ka * bis Kd * corresponds to. Due to the conveyance of the total flow K, the collecting line 4 is also supplied with the total flow K of coolant 6 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 which is at least as great as the greatest of the individual working pressures pAa to pAd. However, both the control 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.
  • 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.
  • the speed n can also be set to intermediate values between 100 revolutions / min and 800 revolutions / min 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 revolutions / min.
  • the numerical values mentioned are of course only to be understood as examples.
  • control device 12 only takes into account the pressure to be statically generated by the pump arrangement 5 in the context of step S4. It is therefore possible that the control device 12 assumes 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 facts into account. An example of such a situation is temporal changes in the setpoint flows Ka * to Kd * and associated temporal changes in the total flow K and associated accelerations of water quantities.
  • the control device 12 can, for example, access a family of characteristics in order to determine its speed n, in which, as shown in FIG FIG 4 for the pump 8 is stored what speed n of the pump 8 is required to bring about a certain pressure increase ⁇ p at a certain total flow K.
  • the required pressure increase ⁇ p pS ⁇ pAv can thus be determined without further ado.
  • the suction pressure pS can Control device 12 be known on the basis of a measurement or otherwise.
  • control state determined for the greatest of the individual working pressures pAa to pAd will itself be a permissible control state of the pump arrangement 5. In this case, this control state can be adopted directly as the preliminary 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' is - in contrast to the control state Z - final.
  • the control device 12 determines the final control state Z 'of the pump arrangement 5 using the preliminary control state Z of the pump arrangement 5.
  • the determination of step S5 is such that the total flow K of coolant 6 is fed to the collecting line 4 by means of the pump arrangement 5.
  • the pump arrangement 5 is controlled in accordance with the final control state Z ′, there is a final working pressure pAe in the collecting line 4.
  • the control device 12 directly and immediately takes over the preliminary control state Z as the final control state Z '.
  • the final control state Z ′ causes the final control state in the collecting line 4, provided that the desired total flow K is conveyed into the collecting line 4 by means of the pump arrangement 8 Working pressure pAe.
  • the control device 12 therefore determines the control values Aa to Ad of the control valves 11a to 11d in a step S6 using the final working pressure pAe. The determination takes place in such a way that the respective nominal current Ka * to Kd * flows in the respective branch line 9a to 9d.
  • step S6 the control device 12 assumes that the final working pressure pAe prevails in the collecting line 4.
  • the modulation ka zu results for the control valve 11a ka pR - ⁇ ⁇ G ⁇ Ha pAe - ⁇ ⁇ G ⁇ Ha ⁇ Ka KR Max
  • a step S7 the control device 12 controls the pump arrangement 5 and the control valves 11a to 11d.
  • the control of the pump arrangement 5 takes place in accordance with the final control state Z '.
  • the control of the control valves 11a to 11d takes place in accordance with the control values Aa to Ad.
  • step S7 the operating method according to the invention is carried out.
  • the control device 12 goes back to step S1 after the execution of step S7.
  • the control device 12 executes the sequence of steps S1 to S7 iteratively over and over again.
  • the execution takes place with a fixed cycle time.
  • the fixed cycle time is usually 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 FIG 3 is in accordance with the design FIG 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 convey the total flow K and at the same time to bring about the required pressure increase ⁇ p from the suction pressure pS to the highest of the determined individual working pressures pAa to pAd.
  • the control device 12 can determine the corresponding speed n of the pump 8 with only one pump 8.
  • step S12 the control device 12 checks whether the ascertained preliminary state Z is permissible, for example the ascertained speed n is in the permissible speed range of the pump 8, that is to say the operating point of the pump 8 is within the range shown in FIG FIG 4 unshaded area.
  • the test thus implies the test for compliance with a secondary condition related to the pump arrangement 5.
  • the speed n lies in the permissible speed range of the pump 8.
  • an operating point AP1 of the pump 8 which lies within the permissible speed range of the pump 8 can be determined by the total flow K and the greatest 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.
  • 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 individual working pressures pAa to pAd determined. Due to the permissible speed range of the pump 8, however, there is inevitably a volume flow conveyed by the pump 8 which is greater than the required total flow K. In the case of the working point AP3, it is the other way round.
  • the pump 8 can generate the required total current K without further ado. Due to the permissible speed range of the pump 8, however, there is inevitably a pressure increase ⁇ p brought about by the pump 8, which is greater than the minimum required.
  • step S14 the control device 12 modifies the preliminary control state Z.
  • the control device 12 can, for example, for a short-circuit valve 15 (see FIG FIG 6 ) determine an opening state.
  • the short-circuit valve 15 is according to the illustration in FIG 6 the pump 8 connected in parallel. It can be viewed as a component of the pump arrangement 5 or as a control valve for a further application device.
  • the control device 12 determines the opening state, if necessary, in such a way that enough coolant 6 is returned directly or indirectly to the reservoir 7 via the short-circuit valve 15 that the remaining volume flow, as a result of the collecting line 4, corresponds to the desired total flow K.
  • the control device 12 can, for example, modify the preliminary control state Z in such a way that, although only the pump 8 is activated (and consequently the short-circuit valve 15, if present, remains closed), in the preliminary control state Z, however, with the desired total current K a provisional working pressure pAv is generated which is greater than the largest of the individual working pressures pAa to pAd.
  • the preliminary working pressure pAv is preferably set to the minimum of the possible and permissible values.
  • step S4 of FIG 3 is in accordance with the design FIG 7 divided into steps S21 to S24.
  • the procedure of FIG 7 can be done with the procedure of FIG 5 can be combined or implemented 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 - analogously to step S11 from FIG FIG 5 -
  • the speed n of the pump 8 which is required to convey the total flow K and at the same time to bring about the required pressure increase ⁇ p from the suction pressure pS to the greatest of the individual working pressures pAa to pAd determined.
  • step S22 the control device 12 checks whether the activation of the control valves 11a to 11d is permissible at the provisional working pressure pAv thus obtained.
  • the control device 12 can check, for example, whether adjustment speeds with which the control values Aa to Ad of the control valves 11a to 11b are changed, adhere to predetermined limits. The test thus implies the test for compliance with secondary conditions related 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 can - depending on the situation of the individual case - either accept the exceeding of the predetermined limits or adapt the preliminary control state Z of the pump arrangement 5.
  • an increase in the preliminary working pressure pAv can cause the predetermined limits to no longer be 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 FIG 3 is in accordance with the design FIG 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. For example, it can be the immediately preceding final control state Z 'or several preceding final control states Z'. For example, abrupt changes in the final control state Z 'can be avoided by low-pass filtering or similar measures.
  • the set currents Ka * to Kd * can be modeled predictively within a forecast horizon of several cycle times - for example five, eight or ten cycle times - and thus also for the future expected preliminary control states Z of the pump arrangement 5 to be determined for the forecast horizon.
  • the preliminary 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 greatest of the individual working pressures pAa to pAd of steps S2 and S3.
  • the limit modulation values kLim of the control valves 11a to 11d are smaller than their maximum possible modulations and / or, before taking into account 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 takes place.
  • the present invention has been explained above in connection with embodiments in which the pump arrangement 5 has only a single pump 8.
  • the pump arrangement 5 has a plurality of pumps 8.
  • the pumps 8 must be controlled in such a way that all 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.
  • the collecting line 4 is fed, if possible, 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 deliver the required final working pressure pAe.
  • the next pump 8 in each case is only switched on when the previously operated pumps 8 are no longer able to supply the required total flow K with the required one to promote preliminary 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 further 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. In particular, there is very little energy consumption. In comparison with an operation of the cooling device 3 with a constant final working pressure pAe, savings of at least 25% and sometimes of well over 80% result. Even compared to procedures in which the final working pressure pAe is individually adapted for each rolling stock 2 and is only kept constant during the cooling of the respective rolling stock 2, there is still a significant energy saving. Theoretically it is conceivable that the lowering of 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. Furthermore, both the mechanics of the control valves 11a to 11d and the mechanics of the pump arrangement 5 are spared.
  • 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 adverse effects for the cooling of the rolling stock 2 as such.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Materials Engineering (AREA)
  • Thermal Sciences (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Metallurgy (AREA)
  • Organic Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Control Of Metal Rolling (AREA)
  • Sorption Type Refrigeration Machines (AREA)
EP20169741.4A 2020-04-14 2020-04-16 Fonctionnement d'un dispositif de réfrigération à une pression de fonctionnement minimale Withdrawn EP3895820A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN202180028584.1A CN115397575A (zh) 2020-04-14 2021-03-29 以最小工作压力运行冷却装置
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
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

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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EP3895820A1 true EP3895820A1 (fr) 2021-10-20

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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)
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BR (1) BR112022020917A2 (fr)
WO (1) WO2021209251A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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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WO2014124867A1 (fr) 2013-02-14 2014-08-21 Siemens Vai Metals Technologies Gmbh Refroidissement d'une bande métallique au moyen d'un système de vanne à réglage de position
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EP3395463A1 (fr) * 2017-04-26 2018-10-31 Primetals Technologies Austria GmbH Refroidissement d'un laminé
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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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JP7524345B2 (ja) 2024-07-29
EP3895819A1 (fr) 2021-10-20
WO2021209251A1 (fr) 2021-10-21
BR112022020917A2 (pt) 2022-12-06
US20230191465A1 (en) 2023-06-22
CN115397575A (zh) 2022-11-25
EP3895819B1 (fr) 2023-06-07
JP2023525657A (ja) 2023-06-19

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