EP3896286A1 - Fonctionnement d'une pompe d'un dispositif de refroidissement sans l'utilisation d'un champ caractéristique multidimensionnel mesuré - Google Patents

Fonctionnement d'une pompe d'un dispositif de refroidissement sans l'utilisation d'un champ caractéristique multidimensionnel mesuré Download PDF

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Publication number
EP3896286A1
EP3896286A1 EP20169308.2A EP20169308A EP3896286A1 EP 3896286 A1 EP3896286 A1 EP 3896286A1 EP 20169308 A EP20169308 A EP 20169308A EP 3896286 A1 EP3896286 A1 EP 3896286A1
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EP
European Patent Office
Prior art keywords
cooling
pump
control device
group
application devices
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Withdrawn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
EP20169308.2A
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German (de)
English (en)
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
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Priority to EP20169308.2A priority Critical patent/EP3896286A1/fr
Publication of EP3896286A1 publication Critical patent/EP3896286A1/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/74—Temperature control, e.g. by cooling or heating the rolls or the product

Definitions

  • the present invention is further based on a computer program that includes machine code that can be processed by a control device for 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 in accordance with such an operating method operates.
  • the present invention is further based on a control device for a cooling device for cooling a hot rolled stock made of metal, the control device being programmed with such a computer program so that the control device operates the cooling device according to such an operating method.
  • Cooling devices for cooling a hot rolled stock made of metal often have pumps by means of which water is fed to application devices (for example spray bars). This is particularly the case with so-called intensive cooling. So-called booster pumps are used here to apply the required water pressure. Valves are often arranged between the pumps and the application devices, by means of which the amounts of water that are applied to the hot rolling stock via the individual application devices can be additionally metered. However, it is also already known to use the pumps exclusively to adjust the water to be applied via the application devices. Purely by way of example in this context EP 3 599 037 A1 to be named.
  • the characteristic parameters of a valve are the working pressure on the inlet side of the valve, the opening position of the valve and the volume flow flowing through the valve. This procedure is for example in the WO 2013/143 925 A1 explained.
  • the control values for pumps to use two-dimensional fields of characteristics, by means of which the three characteristic parameters of the respective pumps can be related to one another, so that when two of the characteristic parameters are specified, the third characteristic parameter can be determined.
  • the characteristic parameters of a pump are the difference between the pump pressure generated on the output side of the pump and the suction pressure applied on the input side of the pump, the speed of the pump and the volume flow flowing through the pump. This procedure is also, for example, in the WO 2013/143 925 A1 explained.
  • valves it is already known for valves to use a one-dimensional characteristic curve to determine the control values, by means of which two of the characteristic parameters of the respective valve are related to one another for a reference value of the third characteristic parameter, a functional relationship being also known by means of which the Characteristic curve can be converted to another value of the third characteristic parameter. In this way, too, if two of the characteristic parameters are specified, the third characteristic parameter can be determined. This procedure is for example in the WO 2014/124 867 A1 and the WO 2019/115 145 A1 explained.
  • a characteristic curve is specified in which, for a reference pressure on the inlet side of the valve, the volume flow flowing through the valve is specified as a function of the opening position of the valve or, conversely, for a reference pressure on the inlet side of the valve, the opening position of the valve is specified as a function of the volume flow flowing through the valve.
  • the conversion to a different working pressure than the reference pressure is done by scaling the volume flow with the root of the quotient of the working pressure and the reference pressure. With the same opening position, the volume flow doubles, for example, at four times the reference pressure.
  • the object of the present invention is to create possibilities by means of which the effort for determining a two-dimensional family of characteristics can also be avoided for pumps.
  • an operating method of the type mentioned is designed in that the control device determines the respective target speed of the respective pump either by means of a mathematical-analytical equation in which the respective group flow and the respective pressure difference to be applied are entered as input variables, or by utilizing a characteristic curve of the respective Pump determined, which is only dependent on one of the characteristic parameters of the respective pump and provides a single output variable.
  • the setpoint speed is thus determined without utilizing a characteristic curve.
  • a characteristic curve still has to be determined and stored in the control device.
  • the characteristic curve is not two-dimensional, but only one-dimensional. As part of the determination of the characteristic, it is therefore only necessary - similar to valves - to determine the only one-dimensional characteristic.
  • This procedure usually means that the internal flow resistance is constant.
  • the flow resistance can also be given as a mathematical-analytical function of the setpoint speed of the pump or of the group flow flowing through the pump.
  • the respective characteristic curve receives the setpoint speed of the respective pump as the input variable and an internal one as the output variable Provides flow resistance of the respective pump. In this case, the determination can be made in the same way as just explained. In contrast to the determination exclusively by means of a mathematical-analytical equation, the internal flow resistance is now given as a characteristic curve.
  • the respective characteristic curve supplies another of the characteristic parameters of the respective pump as an output variable and that the respective characteristic curve is related to a reference value of the third of the characteristic parameters of the respective pump.
  • This procedure is based on the basic principle that on the basis of a valid operating point of a pump - i.e. a certain pressure difference, a certain speed of the pump and the associated group current - further valid working points of the pump can be determined if both the speed of the pump and the group current are included scaled by a certain factor and the pressure difference continues to be scaled with the square of this factor. Starting from a valid operating point of the pump, a further valid operating point of the pump can thus be determined, for example, by doubling both the group current and the speed while at the same time quadrupling the pressure difference. This procedure is similar to the procedure for valves.
  • valves differs from the procedure for valves, however, in that, for valves, a quadrupling of the working pressure is required to double the current flowing through the valve, but the opening position of the valve is retained unchanged.
  • a correct working point of the pump only results again if the speed is also doubled.
  • the utilization of the respective characteristic curve can take place in that the control device scales the group current within the scope of the utilization of the respective characteristic curve with a respective factor, and the control device uses the setpoint speed determined on the basis of the respective characteristic curve scaled with the reciprocal of the respective factor and that the factor results from the root of the quotient of the respective reference pressure difference and the respective pressure difference to be applied.
  • a particularly preferred solution consists in that the respective characteristic curve receives the group current as an input variable and supplies the pressure difference as an output variable and that the reference value is a reference speed.
  • This solution has the particular advantage that the associated characteristic curve can be recorded easily and simply.
  • it is possible to precisely determine the required speed of the respective pump, even for small pressure differences. It is even possible - at least within certain limits - to determine the required speed of the pump for a negative pressure difference.
  • control device can determine the setpoint speed by scaling the reference speed with the reciprocal of a respective factor.
  • a1 is the factor.
  • ⁇ p1 is the desired pressure difference.
  • K1 is the characteristic and W1 is the group current.
  • the object is also achieved by a computer program with the features of claim 9.
  • 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 10.
  • the control device is programmed with a computer program according to the invention, so that the control device is the cooling device operates according to an operating method according to the invention.
  • the object is achieved by a cooling device for cooling hot rolled metal with the features of claim 11.
  • An advantageous embodiment of the cooling device is the subject of dependent claim 12.
  • 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.
  • At least one of the application devices is preferably arranged within a rolling train and / or is arranged upstream of the rolling train and / or is arranged downstream of the rolling train.
  • a cooling device 1 for cooling a hot rolling stock 2 made of metal has a number of cooling groups 3.
  • the cooling groups 3 each have a number of application devices 4.
  • Water 5 can be applied to the rolling stock 2 by means of the application devices.
  • the cooling groups 3 also each have a pump 6.
  • the respective pump 6 is arranged upstream of the application devices 4 of the respective cooling group 3.
  • the water 5 is pumped to the application devices 4 of the respective cooling group 3 by means of the respective pump 6.
  • the rolling stock 2 can be a rod-shaped rolling stock or a profile. Often it is a flat rolled product, i.e. a strip or heavy plate.
  • the metal from which the rolling stock 2 is made is in many cases steel or aluminum.
  • the rolling stock 2 can also consist of another metal, for example copper.
  • the rolling stock 2 generally passes through the cooling device 1 in a transport direction x at a transport speed v while the water 5 is being applied to the rolling stock 2.
  • the application devices 4 are often designed as spray bars.
  • the application devices 4 are shown in FIG FIG 1 arranged exclusively above the rolling stock 2. However, this is of subordinate importance in the context of the present invention.
  • the application devices 4 could also be arranged below the rolling stock 2, or both above and below the rolling stock 2, or they could also be arranged differently.
  • the number of cooling groups 3 can be determined as required. Likewise, the number of application devices 4 per Cooling group 3 can be determined as required. In a theoretical minimum configuration, there is only a single cooling group 3, which also has only a single application device 4. As a rule, however, the number of application devices 4 is greater than 1. In this case, too, it is possible that only a single pump 6 is present, that is to say that all application devices 4 of the cooling device 1 are supplied with water 5 via the same pump 6. In this case, the application devices 4 of the cooling device 1 form a single cooling group 3. Alternatively, it is possible that each individual application device 4 is assigned its own pump 6, so that each application device 4 is assigned its own pump 6.
  • cooling groups 3 there are several cooling groups 3, each of which has only a single application device 4 and the associated pump 6.
  • y cooling groups 3 are formed, each cooling group 3 having z application devices 4.
  • y can have a value of 2, 4, or 8.
  • z can have a value between 2 and 10.
  • FIG 1 an embodiment is shown in which two cooling groups 3 are present, each having two application devices 4.
  • pump is used in the generic sense in the context of the present invention.
  • a single pump 6 there can also be a plurality of pumps which are arranged in series one behind the other and or parallel to one another.
  • the pumps 6 can in particular be designed as centrifugal pumps.
  • valves 7 are arranged upstream of the application devices 4, so that the quantities of water 5 flowing through the application devices 4 can also be individually adjusted if several application devices 4 are supplied with water 5 via one and the same pump 6.
  • the valves 7 in particular in the case of a 1: 1 assignment of the pumps 6 to the application devices 4, that is to say in the event that the cooling groups 3 each have only a single application device 4, the valves 7 however, this may be omitted.
  • the valves 7 can in particular be designed as control valves.
  • Control valves are valves which, in addition to a (maximally) open and a closed position, can assume any or almost any intermediate position. This is in contrast to switching valves, in which only the (maximum) open and closed positions can be assumed.
  • the cooling device 1 has a control device 8.
  • the control device 8 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 8.
  • the control device 8 is programmed with a computer program 9.
  • the computer program 9 comprises machine code 10 which can be processed by the control device 8.
  • the programming of the control device 8 with the computer program 9 (or, equivalently, the processing of the machine code 10 by the control device 8) has the effect that the control device 8 operates the cooling device 1 according to an operating method which is described below in connection with FIG 2 is explained in more detail.
  • setpoint currents w1 to w4 are known to the control device 8 in a step S1.
  • the setpoint currents w1 to w4 can be specified for the control device 8, for example by an operator (not shown). Other types of specification or determination by the control device 8 itself are also possible.
  • Each of the setpoint flows w1 to w4 is related to one of the application devices 4 and specifies the amount of water 5 to be supplied to the respective application device 4.
  • the application devices 4 do not have any buffer devices for buffering water 5.
  • the amounts of water supplied to the application devices 4 correspond 1: 1 to the amounts of water applied to the rolling stock 2 by the application devices 4.
  • the set currents w1 to w4 are in this case also identical to the flows of water 5 that are to be applied to the rolling stock 2 by the application devices 4. If the application devices 4 have buffer devices, the nominal flows w1 to w4 are generally those amounts of water 5 that are to be supplied to the application devices 4. In exceptional cases, however, it can also be the amounts of water 5 that are to be applied to the rolling stock 2 by the application devices 4.
  • the control device 8 uses the setpoint currents w1 to w4 to determine group currents W1, W2. In particular, the control device 8 adds the setpoint currents w1 to w4 of the respective cooling group 3 and thus determines the respective group currents W1, W2.
  • the control device 8 determines a respective pressure difference ⁇ p1, ⁇ p2 for the pumps 6.
  • the pressure difference ⁇ p1, ⁇ p2 results from the difference between a respective working pressure pA1, pA2, which must prevail in the area of the application devices 4 of the respective cooling group 3, and a base pressure p0, which prevails on the inlet side of the pumps 6.
  • the base pressure p0 which corresponds to the suction pressure of the pumps 6, can be determined, for example, by a water reservoir 11, from which the pumps 6 draw the water 5. If necessary, the control device 8 can take into account a line resistance of a line system between the respective pump 6 and the application devices 4 of the respective cooling group 3 in the context of step S3.
  • control device 8 can also take into account in the context of step S3 to what extent the amount of water that is located between the respective pump 6 and the application devices 4 of the respective cooling group 3 must be accelerated. Corresponding procedures are in the already mentioned WO 2019/115 145 A1 explained.
  • control device 8 also determines control values A1 to A4 for the valves 7 in step S3.
  • the determination of the control values A1 to A4 and the determination of the pressure differences ⁇ p1, ⁇ p2 can be coupled to one another.
  • the relevant determinations are generally known to those skilled in the art and therefore do not need to be explained in detail.
  • appropriate procedures are, for example, in the WO 2019/115 145 A1 explained.
  • Step S4 the control device 8 determines a respective setpoint speed n1, n2 for the pumps 6. The determination takes place on the basis of the respective group flow W1, W2 and the respective pressure difference ⁇ p1, ⁇ p2. Step S4 will be explained in more detail later.
  • the control device 8 controls the pumps 6 with the setpoint speeds n1, n2 and possibly also the valves 7 with the control values A1 to A4. It thus operates the pumps 6 according to the determined respective setpoint speed n1, n2 and, if necessary, the valves 7 according to the determined respective control values A1 to A4.
  • the application devices 4 of the respective cooling groups 3 are thereby supplied with water 5 in accordance with the setpoint flows w1 to w4.
  • step S5 After the execution of step S5, the control device 8 goes back to step S1.
  • the control device 8 thus repeatedly executes the sequence of steps S1 to S5.
  • the control device 8 can become aware of new values for the setpoint currents w1 to w4.
  • the set currents w1 to w4 can therefore be functions of time.
  • the group currents W1, W2, the pressure differences ⁇ p1, ⁇ p2 to be applied and the setpoint speeds n1, n2 that are determined on the basis of this can also be functions of time.
  • steps S1 to S5 are carried out with a strictly clocked cycle time.
  • the cycle time is usually between 0.1 s and 1.0 s, for example between 0.2 s and 0.5 s.
  • the respective group flow W1, W2, the respective pressure difference ⁇ p1, ⁇ p2 to be applied and the respective target speed n1, n2 formed characteristic parameters of the respective pump 6.
  • these are always Values are meant, that is, for one pump 6 the group current W1, the pressure difference ⁇ p1 and the target speed n1 and for the other pump 6 the group current W2, the pressure difference ⁇ p2 and the target speed n2.
  • the present invention is explained below exclusively for the pump 6 with the characteristic parameters W1, ⁇ p1 and n1.
  • analogous statements always apply to the other pump 6.
  • step S4 corresponds to that in connection with FIG FIG 3 explained procedure implemented.
  • the control device 8 determines the target speed n1 of the pump 6 by means of a mathematical-analytical equation.
  • the group flow W1 and the pressure difference ⁇ p1 go into the mathematical-analytical equation as input variables.
  • nN1 is a nominal speed of the pump 6 under consideration.
  • R1 is an internal flow resistance of the pump 6 under consideration.
  • ⁇ pN1 is a nominal pressure difference. The nominal pressure difference ⁇ pN1 is generated by the pump 6 under consideration when it is operated at the nominal speed nN1 and the group current W1 flowing through the pump 6 under consideration is zero, that is to say it is shut off on the output side.
  • the special state in which the pump 6 under consideration is operated at the nominal speed nN1 and the group current W1 flowing through the pump 6 under consideration is zero may only be assumed for a short time (a few seconds), since otherwise the pump 6 under consideration would be damaged.
  • the determination of the nominal pressure difference ⁇ pN1 in the context of a test can, however, take place very quickly.
  • the special state therefore only has to be assumed for a very short time (1 second or less).
  • control device 8 does not have to use a characteristic curve of the pump 6 to determine the setpoint speed n1. Rather, it is sufficient if the control device 8 only knows one respective singular parameter of the pump 6, namely its internal flow resistance R1.
  • the control device 8 determines the setpoint speed n1 of the pump 6 by means of a mathematical-analytical equation, but for a characteristic curve K1 to be included in the mathematical-analytical equation.
  • the difference to equation 1 is that the internal flow resistance R1 of the pump 6 is no longer a constant, but is defined as a function of the speed n1.
  • the characteristic curve K1 receives the setpoint speed n1 of the pump 6 as an input variable and supplies the internal flow resistance R1 of the pump 6 as an output variable.
  • the internal flow resistance R1 of the pump 6 is a mathematical-analytical function of the group flow W1 or the setpoint speed n1.
  • the characteristic curve K1 is not required, only a parameterization of the function for determining the internal flow resistance R1 of the pump 6.
  • the characteristic curve K1 ', K1 "receives one of the characteristic parameters W1, ⁇ p1, n1 of the pump 6 as an input variable - as before - but supplies another of the characteristic parameters W1, ⁇ p1, n1 of the pump 6 as an output variable
  • the characteristic curve K1 ', K1 is related to a reference value of the third of the characteristic parameters W1, ⁇ p1, n1 of the pump 6.
  • the characteristic curve K1 'can be shown in FIG FIG 5 receive the group current W1 as the input variable and supply the setpoint speed n1 as the output variable and consequently the reference value be a reference pressure difference ⁇ pR1.
  • the reference pressure difference ⁇ pR1 is equal to or approximately equal to the nominal pressure difference ⁇ pN1. Alternatively, it can also be a different value. In this case, the reference pressure difference ⁇ pR1 is usually lower than the nominal pressure difference ⁇ pN1.
  • characteristic curve K1 ' In addition to the characteristic curve K1 ', two further characteristic curves are shown. These further characteristics are similar to characteristic K1 ', but apply to other pressure differences. They are in FIG 5 although they are drawn in, they are only required below in the context of the explanation of the present invention, but not in the context of its implementation. For the implementation of the present invention, only the characteristic curve K1 'is required, which is valid for the reference pressure difference ⁇ pR1.
  • control device 8 determines in this case in accordance with the representation in FIG FIG 6 first a factor a1.
  • FIG 5 shows this clearly. Because in FIG 5 is shown by arrows in which way, starting from the characteristic curve K1 'for the reference pressure difference ⁇ pR1, a conversion to other pressure differences ⁇ p1 can take place. Is concrete It can be seen that when the pressure difference ⁇ p1 changes, not only does the group current W1 change, but also the setpoint speed n1. In other words: the connecting lines of the operating points of the respective pump 6, which are determined by the conversion, run in FIG 5 neither horizontally nor vertically, but at an angle.
  • the characteristic curve K1 "can be used as shown in FIG 7 receive the group current W1 as the input variable and supply the pressure difference ⁇ p1 as the output variable and consequently the reference value be a reference speed nR1.
  • the reference speed nR1 is equal to or approximately equal to the nominal speed nN1. Alternatively, it can also be a different value. In this case, the reference speed nR1 is usually lower than the nominal speed nN1.
  • the control device 8 determines in this case in accordance with the representation in FIG FIG 8 first a factor a1.
  • FIG 7 shows this clearly.
  • the point (W1, ⁇ p1) given by the desired pressure difference ⁇ p1 and the given group flow W1 is in FIG 7 marked by a small cross, the intersection of the parabola with the characteristic curve K1 ′′ by a small circle.
  • the resulting point of the parabola is the given point (W1, ⁇ p1).
  • the other points of the parabola result in (a1W1, a1 2 ⁇ p1).
  • the value of the factor a1 for the intersection with the characteristic K1 is the” correct "value.
  • the control device 8 scales the reference speed nR1 with the reciprocal of this value. The result of this scaling gives the required speed n1 of the pump 6. Also within the scope of the Procedure of FIG 8 run the connecting lines of the operating points of the respective pump 6, which are determined by the conversion, in FIG 7 visible neither horizontally nor vertically, but at an angle.
  • the cooling device 1 according to the invention can be arranged in front of, in or behind a rolling mill as required.
  • at least one of the application devices 4 can be arranged within a rolling train. If necessary, several application devices 4 or even all application devices 4 can be arranged within the rolling train.
  • the corresponding application devices 4 can be used as shown in FIG FIG 10 be designed for example as inter-stand cooling between the roll stands 12 of a finishing train.
  • at least one of the application devices 4 is arranged upstream of the rolling train.
  • at least one of the application devices 4 can be arranged between a roughing stand 13 and the roll stands 12 of the finishing train.
  • the corresponding application device 4 is arranged upstream of the finishing train.
  • An arrangement in front of the roughing stand 13 is also possible.
  • the corresponding application device 4 can be used for cooling or, for example, be part of a descaling device.
  • at least one of the application devices 4 can be arranged downstream of the rolling train.
  • the application devices 4 can be used in accordance with the illustration in FIG FIG 12 Be part of a cooling section that is downstream of the finishing train. Other configurations and mixed forms are also possible.
  • the present invention has many advantages. First of all, the determination of the setpoint speeds n1, n2 is simplified. As a result, the setpoint speeds n1, n2 can also be determined more quickly. This is particularly advantageous because at least the target currents w1 to w4, as already mentioned, are usually functions of time and consequently also the group currents W1, W2 and, based on this, the pressure differences ⁇ p1, ⁇ p2 and the target speeds n1, n2 vary over time. Another advantage is that the control device 8 requires a smaller amount of memory. Furthermore, any adaptation of the characteristic curve K1, K1 'K1 "is simplified, since considerably fewer parameters have to be adapted compared to a two-dimensional field of characteristic curves.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP20169308.2A 2020-04-14 2020-04-14 Fonctionnement d'une pompe d'un dispositif de refroidissement sans l'utilisation d'un champ caractéristique multidimensionnel mesuré Withdrawn EP3896286A1 (fr)

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EP20169308.2A EP3896286A1 (fr) 2020-04-14 2020-04-14 Fonctionnement d'une pompe d'un dispositif de refroidissement sans l'utilisation d'un champ caractéristique multidimensionnel mesuré

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EP20169308.2A EP3896286A1 (fr) 2020-04-14 2020-04-14 Fonctionnement d'une pompe d'un dispositif de refroidissement sans l'utilisation d'un champ caractéristique multidimensionnel mesuré

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SU1225923A1 (ru) * 1983-11-23 1986-04-23 Украинское Отделение Всесоюзного Ордена Ленина Проектно-Изыскательского И Научно-Исследовательского Института "Гидропроект" Им.С.Я.Жука Способ регулировани расхода системы "насос-трубопровод
WO2013143925A1 (fr) 2012-03-28 2013-10-03 Siemens Aktiengesellschaft Commande d'un système de refroidissement
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
DE102014006828A1 (de) * 2014-05-13 2015-11-19 Wilo Se Verfahren zur energieoptimalen Drehzahlregelung eines Pumpenaggregats
US20190187640A1 (en) * 2017-12-20 2019-06-20 Siemens Aktiengesellschaft Digital twin of centrifugal pump in pumping systems
WO2019115145A1 (fr) 2017-12-11 2019-06-20 Primetals Technologies Germany Gmbh Régulation améliorée de la gestion de l'eau d'une zone de refroidissement
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 Priority date Publication date Assignee Title
SU1225923A1 (ru) * 1983-11-23 1986-04-23 Украинское Отделение Всесоюзного Ордена Ленина Проектно-Изыскательского И Научно-Исследовательского Института "Гидропроект" Им.С.Я.Жука Способ регулировани расхода системы "насос-трубопровод
WO2013143925A1 (fr) 2012-03-28 2013-10-03 Siemens Aktiengesellschaft Commande d'un système de refroidissement
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
DE102014006828A1 (de) * 2014-05-13 2015-11-19 Wilo Se Verfahren zur energieoptimalen Drehzahlregelung eines Pumpenaggregats
WO2019115145A1 (fr) 2017-12-11 2019-06-20 Primetals Technologies Germany Gmbh Régulation améliorée de la gestion de l'eau d'une zone de refroidissement
US20190187640A1 (en) * 2017-12-20 2019-06-20 Siemens Aktiengesellschaft Digital twin of centrifugal pump in pumping systems
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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