EP3599037A1 - Section de refroidissement à réglage de flux de liquide de refroidissement à l'aide des pompes - Google Patents

Section de refroidissement à réglage de flux de liquide de refroidissement à l'aide des pompes Download PDF

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Publication number
EP3599037A1
EP3599037A1 EP18185526.3A EP18185526A EP3599037A1 EP 3599037 A1 EP3599037 A1 EP 3599037A1 EP 18185526 A EP18185526 A EP 18185526A EP 3599037 A1 EP3599037 A1 EP 3599037A1
Authority
EP
European Patent Office
Prior art keywords
pump
coolant
cooling section
rolling stock
control 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Withdrawn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
EP18185526.3A
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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 EP18185526.3A priority Critical patent/EP3599037A1/fr
Priority to CN201980049320.7A priority patent/CN112469516B/zh
Priority to PCT/EP2019/069763 priority patent/WO2020020868A1/fr
Priority to US17/261,080 priority patent/US11167332B2/en
Priority to EP19740415.5A priority patent/EP3826780B1/fr
Publication of EP3599037A1 publication Critical patent/EP3599037A1/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Withdrawn legal-status Critical Current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
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/74—Temperature control, e.g. by cooling or heating the rolls or the product
    • B21B37/76—Cooling control on the run-out table
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B45/00—Devices for surface or other treatment of work, specially combined with or arranged in, or specially adapted for use in connection with, metal-rolling mills
    • B21B45/02—Devices for surface or other treatment of work, specially combined with or arranged in, or specially adapted for use in connection with, metal-rolling mills for lubricating, cooling, or cleaning
    • B21B45/0203—Cooling
    • B21B45/0209—Cooling devices, e.g. using gaseous coolants
    • B21B45/0215—Cooling devices, e.g. using gaseous coolants using liquid coolants, e.g. for sections, for tubes
    • B21B45/0218—Cooling devices, e.g. using gaseous coolants using liquid coolants, e.g. for sections, for tubes for strips, sheets, or plates

Definitions

  • a metal rolling stock is cooled in the cooling section of a rolling mill after rolling.
  • the rolling stock can be made of steel or aluminum, for example. If required, it can be a flat rolling stock (strip or heavy plate), a rod-shaped rolling stock or a profile.
  • Exact temperature control in the cooling section is customary in order to set the desired material properties and to keep it constant with lower scatter.
  • a plurality of spray bars are installed along the cooling section, by means of which a liquid coolant, usually water, is applied to the rolling stock to cool the hot rolling stock from above and below.
  • the amount of water flowing through the respective spray bar should be adjustable as quickly and precisely as possible.
  • switching valves or control valves can only be controlled in a binary manner. So they are either fully open or completely closed.
  • Control valves can be continuously adjusted so that the amount of water supplied in the respective spray bar can also be continuously adjusted.
  • control valves In the case of control valves, the valves can be designed as control flaps or as ball valves.
  • Control valves are relatively simple and inexpensive. However, they can only be operated with relatively small pressure differences, usually a maximum of 1 bar. Otherwise, cavitations occur which damage the control valve very quickly.
  • Control flaps are therefore particularly unsuitable for intensive cooling. But they are also often disadvantageous in a laminar cooling section. In particular, they often show a switching hysteresis. The switching hysteresis causes that with the same control the set flap angle is different, depending on whether the control flap is adjusted from a further open or from a further closed position to the new position to be assumed.
  • Ball valves do not have a flap, but a pierced ball that is rotated in a tube.
  • Ball valves can be operated with higher pressure differences up to approx. 3 bar. A hysteresis does not occur in them or is negligibly small. Ball valves are expensive, however.
  • the coolant is permanently supplied to the spray bars.
  • a controllable deflection plate is available. Depending on the position of the deflection plate, the coolant is either fed to the rolling stock or flows off to the side without contributing to cooling the rolling stock. With this arrangement, fast switching operations without pressure surges are possible. However, it is not possible to continuously adjust the amount of water. Furthermore, the full coolant flow must be continuously promoted.
  • valves and also the baffle plates require appropriate actuators. Pneumatically driven servomotors are common. Position control is also required for control valves. This continuously compares the actual position of the respective control valve with its nominal position and adjusts the actual position until there is sufficient agreement with the nominal position.
  • the coolant can, for example, be taken from a high-level tank or transported from a pump station further away via a larger pipeline. Combinations of these procedures are also possible.
  • intensive cooling the water is often first taken from an elevated tank. Then the pressure via booster pumps increased to a variable extent and thus made available with correspondingly variable pressure for intensive cooling.
  • booster pumps There are usually several booster pumps, but they are all connected in parallel, ie they all draw the coolant from the same reservoir on the inlet side and feed it to a common collection point on the outlet side.
  • the intensive cooling is provided with several spray bars, which - starting from the booster pumps or the common collection point - the coolant is fed individually via a respective supply line.
  • Ball valves are arranged in the supply lines and are controlled to set the amount of coolant supplied to the respective spray bar.
  • a descaling device in which a pump is driven by a variable-speed drive.
  • the drive When the drive is actuated, an operating state of the descaling area and a degree of filling of a high-pressure accumulator are taken into account.
  • a cooling water source which comprises a coil cooled with water.
  • the cooling water is fed to the coil via a pump that can be switched on and off and has a mechanism for controlling the quantity of coolant.
  • the liquid is recirculated.
  • the temperature of the cast metal strand is recorded and fed to a control device. Depending on this, the control device controls the cooling water source.
  • a method in which a metal strip is cooled with a liquid cooling medium as part of a heat treatment of the metal strip in a cooling device.
  • the metal band runs vertically from bottom to top.
  • the cooling medium is pentane or a mixture of pentane and hexane.
  • the metal strip is in an atmosphere of protective gas during the application of the cooling medium.
  • an amount of coolant is determined which is to be guided by a pump to the application devices of the cooling device. The pump is controlled according to the result.
  • a casting process is known in which the cast strand is passed through a cooling chamber in which the cast strand is cooled with a liquid cooling medium.
  • the liquid cooling medium is a metal or a molten salt.
  • the liquid cooling medium is removed from a reservoir by means of a circulating pump, fed to the cooling chamber and then again from the cooling chamber Reservoir fed.
  • the amount of liquid is regulated as a function of the temperatures at which the liquid cooling medium is supplied to the cooling chamber or discharged from the cooling chamber, and as a function of the pressure on the inlet side of the cooling chamber.
  • a casting process is known in which the cast strand is formed by means of a two-roll casting machine.
  • the inside of the rolls are cooled with a liquid cooling medium.
  • the liquid cooling medium is a metal or a molten salt.
  • the liquid cooling medium is removed from a reservoir by means of a circulating pump, fed to the rollers and then returned to the reservoir from the cooling chamber.
  • the object of the present invention is to create possibilities by means of which a cooling section with superior operating properties can be implemented in a simple and reliable manner.
  • an operating method of the type mentioned at the outset is configured in that a control device the cooling section dynamically determines a respective target control state for the respective pump and controls the respective pump accordingly, depending on a respective target flow of the coolant to be applied to the hot rolling stock by the respective application device, so that the respective actual pump conveyed by the respective pump Electricity is approximated as closely as possible to the respective nominal current at all times.
  • the respective pump - more precisely: the drive for the respective pump - is therefore a variable-speed drive. For example, it can be converter-controlled. As part of the dynamic control, only the respective pump is controlled, but not any valve arranged in the respective supply line.
  • Control or regulation can take place as required.
  • the respective actual flow of the liquid coolant is recorded on the input or output side of the respective pump and supplied to the control device.
  • the rolling stock is a flat rolling stock, for example a strip or a heavy plate.
  • the liquid coolant is applied to the rolling stock from both sides by means of the respective application device.
  • the liquid coolant it is possible for the liquid coolant to be applied to the rolling stock only from one side, in particular from above or from below, by means of the respective application device.
  • two application devices are required, which are controlled separately and, in principle, are also operated independently of one another.
  • the operating method according to the invention is thus carried out twice, so to speak.
  • the control of both Pumping can, however, be carried out uniformly by one and the same control device.
  • the control device can, if necessary, also take into account mutual dependencies in the cooling.
  • the respective application device prefferably has a plurality of spray nozzles which are arranged one behind the other, as seen in the transport direction of the rolling stock.
  • groups of spray nozzles can be formed within a single spray bar and are supplied with coolant uniformly via the respective supply line and the respective supply line and the respective pump.
  • Groups of spray nozzles can also be formed which overlap several spray bars and are supplied with coolant uniformly via the respective supply line and the respective pump. This configuration can be particularly advantageous in that fewer pumps are required than if each spray bar were supplied with coolant via its own supply line and its own pump.
  • the respective application device has a plurality of spray nozzles which, as seen transversely to the transport direction of the rolling stock, are arranged next to one another.
  • This can be particularly useful for flat rolling stock (strip or heavy plate).
  • the respective application device can extend over the full width of the rolling stock or only over part of the width.
  • several application devices are arranged side by side, each of which is supplied with coolant via its own supply line and its own pump, the pumps being controlled independently of one another.
  • shut-off device no shut-off device is arranged between the respective pump and the respective application device.
  • a shut-off device it is possible for a shut-off device to be arranged between the respective pump and the respective application device.
  • the Shut-off device either kept permanently fully open during the transport of the rolling stock through the cooling section, or actuated both opening and closing only when a speed of the respective pump is below a minimum speed.
  • the respective minimum speed is so low that only a very slight actual current is delivered.
  • the shut-off device can only be actuated manually in order to be able to take the respective application device out of operation, for example for maintenance purposes.
  • the respective pump it is also possible for the respective pump to have a respective return line arranged in parallel.
  • the return line has a smaller cross section than the respective supply line.
  • pumps can be used in which a certain minimum flow of coolant must always be maintained due to the design.
  • the minimum flow is considerably smaller than the maximum possible flow of coolant. If in such a case an amount of coolant is to be applied to the rolling stock that is smaller than the respective minimum flow, it is only necessary to open a valve arranged in the return line accordingly (bypass operation).
  • the respective pump is operated as a generator or is operated with an inverted direction of rotation whenever the respective target current falls below a respective lower limit value. This means that even very small actual currents can be realized. Furthermore, this can prevent an excessively large actual current from flowing through a pump that is not self-locking in the event of a small target current.
  • a check valve or a check valve is arranged in the respective supply line between the respective pump and the respective application device. Thereby can prevent the respective pump from running dry and being damaged as a result.
  • an inlet-side pressure of the liquid coolant is detected in front of the respective pump and the control device takes the detected inlet-side pressure into account when determining the respective target activation state of the respective pump. This enables a more precise determination of the respective target activation state for the respective pump.
  • the control device preferably determines the respective target current as a function of a respective thermodynamic energy state of the rolling stock existing immediately before the respective application device is reached. This enables a particularly precise temperature control to be implemented.
  • the thermodynamic energy state of the rolling stock can be known to the control device, for example on the basis of a previous measurement. Alternatively, it is possible for a model-based calculation of the respective thermodynamic energy state to be carried out on the basis of a known thermodynamic energy state.
  • the operating method according to the invention is preferably designed such that the control device uses the thermodynamic energy state to determine the respective thermodynamic energy state of the rolling stock of the rolling stock in front of the immediately preceding application device with additional consideration of the target current of the coolant or the actual current of the coolant, which is applied or is to be applied to the hot rolling stock by means of the immediately preceding application device.
  • the thermodynamic energy states can therefore be calculated sequentially one after the other.
  • a cooling section of the type mentioned at the outset is designed in such a way that the control device is designed such that it dynamically determines a respective target control state for the respective pump as a function of a respective target flow of coolant to be applied to the hot rolling stock by means of the respective application device and controls the respective pump accordingly, so that the respective actual current conveyed by the respective pump is brought as close as possible to the respective target current at any time.
  • the advantageous configurations of the cooling section correspond essentially to those of the operating method.
  • the advantages achieved in this way also correspond to the corresponding configurations of the operating method.
  • a hot rolled metal 1 is to be cooled in a cooling section 2.
  • the cooling section 2 is according to FIG. 1 downstream of a rolling mill. Is shown in FIG. 1 only one roll stand 3 of the rolling mill, namely the last roll stand 3 of the rolling mill. As a rule, however, the rolling train has a plurality of roll stands 3, through which the hot rolling stock 1 passes sequentially one after the other. In the case of the design according to FIG. 1 the hot rolling stock 1 enters the cooling section 2 immediately after rolling in the last rolling stand 3 of the rolling train. A time interval between the rolling in the last roll stand 3 of the rolling mill and the entry into the cooling section 2 is in the range of a few seconds.
  • the cooling section 2 could be as shown in FIG FIG 2 be upstream of the rolling mill. Is shown in FIG 2 also only a single stand 4 of the rolling mill, namely the first stand 4 of the rolling mill. in the In case of the design according to FIG 2 the hot rolling stock 1 is rolled immediately after it leaves the cooling section 2 in the first roll stand 4 of the rolling train. A time interval between cooling in the cooling section 2 and rolling in the first roll stand 4 of the rolling mill is in the range of a few minutes. But it can also be only a few seconds.
  • the cooling section 2 could be as shown in FIG FIG 3 be arranged within the rolling mill.
  • two roll stands 5 of the rolling mill In this case, cooling takes place in the cooling section 2 between the rolling in the two roll stands 5 of the rolling train.
  • a time interval between cooling in the cooling section 2 and rolling in the two successive roll stands 5 of the rolling mill is in the range of a few seconds.
  • the cooling section 2 is arranged between two successive rolling stands 5 of the rolling mill. But it could also extend over a larger area, so that the cooling section 2 by at least one in FIG 3 further roll stand, not shown, is divided into a corresponding number of sections.
  • the rolling stock 1 is made of metal.
  • the rolling stock 1 can consist of steel or aluminum. Other metals are also possible.
  • the temperature of the rolling stock 1 in front of the cooling section 2 is generally between 750 ° C and 1,200 ° C. Cooling to a lower temperature takes place in the cooling section 2. In individual cases it is possible that the lower temperature is only slightly below the temperature in front of the cooling section 2.
  • the rolling stock 1 is generally cooled to a significantly lower temperature, for example to a temperature between 200 ° C. and 700 ° C.
  • the hot rolling stock 1 is fed to the cooling section 2 in a horizontal transport direction x.
  • the hot rolling stock 1 changes its transport direction x within the cooling section 2 Not. It is therefore also transported horizontally within the cooling section 2.
  • the rolling stock 1 can either maintain or change its transport direction. If the hot rolling stock 1 is a strip, it can, for example, be deflected diagonally downwards in order to feed it to a reel. If the hot rolling stock 1 is a heavy plate, it usually maintains the transport direction x.
  • a roller table that may be required for the transport of the hot rolling stock 1 is not shown in the FIG.
  • the cooling section 2 has a number of application devices 6.
  • a coolant 7 is applied to the rolling stock 1 by means of the application devices 6.
  • the coolant 7 is water. If necessary, additives can be added to the water to a small extent (maximum 1 percent to 2%). In any case, however, the coolant 7 is a liquid, water-based coolant.
  • a single application device 6 is present at a minimum. In many cases, however, there are several application devices 6.
  • the application devices can be shown in FIG. 1 be arranged one behind the other. In this case, the application devices 6 apply their respective proportion of the coolant 7 to the rolling stock 1 sequentially one after the other.
  • the term “sequentially one after the other” refers to a specific section of the rolling stock 1, since this sequentially passes through areas in which the individual application devices each apply their respective proportion of the coolant 7 to the corresponding section of the rolling stock 1.
  • the number of application devices 6 is often in the two-digit range, sometimes even in the upper two-digit range.
  • a sequential arrangement one behind the other is usually realized in particular if the cooling section 2 is arranged downstream of the rolling mill. However, it can also exist in other case designs.
  • the application devices 6 are connected to a reservoir 9 of the coolant 7 via a respective supply line 8.
  • the reservoir 9 is uniform for all application devices 6.
  • several reservoirs 9 that are independent of one another could also be present.
  • a respective pump 10 is arranged in each supply line 8.
  • the pumps 10 can be arranged at any desired locations within the supply lines 8. In practice, however, it is advantageous if the pumps 10 are arranged as close as possible to the reservoir 9.
  • the application device 6 is supplied with an actual flow F of the coolant 7 via the supply line 8 and the pump 10 from the reservoir 9.
  • the actual current F is applied to the hot rolling stock 1 by means of the respective application device 6.
  • a distance of the application device 6 - for example from spray nozzles - from the rolling stock 1 is generally between 20 cm and 200 cm.
  • a control device 11 of the cooling section 2 knows a corresponding target current F * which is to be applied to the hot rolling stock 1 by means of the application device 6.
  • the target current F * is generally not constant over time, but variable, that is, a function of time t.
  • the control device 11 dynamically determines a target control state S * for the pump 10 as a function of the target current F * of the coolant 7. It controls the pump 10 accordingly.
  • the pump 10 thereby acts on the coolant 7 on the outlet side of the pump 10 with an outlet-side pressure pA.
  • the output pressure pA varies according to the target control state S *. However, it is below 10 bar in every operating state. In most cases it is even a maximum of 6 bar. In any operating state, however, the actual current F delivered by the pump 10 is approximated as much as possible at all times to the desired current F *.
  • the target control state S * can also be determined easily. This will be explained below using a simple example.
  • the pump 10 is arranged in the immediate vicinity of the reservoir 9.
  • the supply line 8 has a length 1 and a cross section A.
  • the pressure on the input side of the pump 10 is referred to below as pE.
  • the pressure in the application device 6 is denoted by p0.
  • FN is a nominal current that flows out of the application device 6 when the coolant 7 in the application device has a nominal pressure pN.
  • the nominal current FN and the nominal pressure pN are determined and determined by the design of the application device 6. They can be determined, for example, by measuring the flow once, which arises at a pressure - which is in principle arbitrarily defined.
  • the actual current F is given without further ado. For example, it can be measured.
  • the desired time derivative of the actual current F results directly from the difference between the target current F * and the actual current F. If necessary, the time derivative of the actual current F can be limited in order to increase the pressure pA on the outlet side within permissible limits hold.
  • n f pA - pE .
  • control device 11 has the actual current F available at any time, either by measurement or by calculation according to equation (6). This is necessary in order to be able to mathematically update a thermodynamic energy state H of the rolling stock 1. This will be discussed in more detail later.
  • the dead time of the application device 6 only occurs as a rule the very short time that the coolant 7 needs to hit the rolling stock 1, calculated from the point at which it exits the application device 6.
  • Control or regulation can take place as required.
  • the actual current F is detected on the input or output side of the pump 10 and fed to the control device 11. If no such detection takes place, the actual current F is controlled.
  • the pump 10 - In order to be able to control the pump 10 accordingly, the pump 10 - more precisely: its drive 12 - must be able to be operated at a variable speed.
  • the drive 12 of the pump 10 can be converter-controlled for this purpose.
  • Such controls are generally known to experts and therefore do not need to be explained in more detail.
  • the pump 10 can preferably be operated in a control range between 0 and a maximum speed.
  • a seal of the pump 10 should also be designed for low speeds. However, this is easily possible.
  • Corresponding pumps 10 are known to those skilled in the art.
  • the pump 10 is accordingly dynamically actuated and the actual current F is brought as close as possible to the target current F *.
  • no valve arranged in the supply line 8 is actuated. Such a valve - should it be present - remains permanently fully open.
  • shut-off device 13 is arranged between the pump 10 and the application device 6.
  • the shut-off device 13 is in FIG 4 only drawn in with a dashed line, because it may be present but does not have to be present. If the shut-off device 13 is present, the shut-off device 13 can be driven in two different ways.
  • the shut-off device 13 is kept permanently completely open during the transport of the rolling stock 1 through the cooling section 2. This is in FIG 5 This shows that the rolling stock 1 enters the cooling section 2 at a time t1. However, the shut-off device 13 is opened at a time t2 before the time t1. In an analogous manner, the rolling stock 1 runs out of the cooling section 2 at a time t3. Only after time t3 is the shut-off device 13 closed again at a time t4. The shut-off device 13 remains permanently fully open between the times t2 and t4.
  • the shut-off device 13 is actuated only when a speed of the pump 10 is below a minimum speed nmin. This is discussed below in conjunction with FIG 6 explained in more detail.
  • the speed of the pump 10 can vary between 0 and a nominal speed nmax. If and as long as the speed n remains below a minimum speed nmin, the shut-off device 13 can be actuated. This applies both to opening and closing the shut-off device 13. If and as soon as the speed n reaches or exceeds the minimum speed nmin, the shut-off device 13 remains open. In this case, in particular, the shut-off device 13 must first be opened at a very low speed n. The application device then operates 6, during which only the pump 10 is controlled accordingly to set the actual current F. Only when the speed n falls below the minimum speed nmin can the shut-off device 13 be actuated again.
  • the pump 10 must always deliver a minimum current when it is operated.
  • the minimum current can be greater than the target current F *.
  • FIG 7 it is as shown in FIG 7 possible to arrange a return line 14 in parallel with the pump 10.
  • the return line 14, however, has a smaller cross section than the supply line 8.
  • the return line 14 only has to be designed to be able to convey the minimum current.
  • the supply line 8, however, must be designed to be able to promote the maximum current Fmax.
  • shut-off device 13 If in the case of the configuration according to FIG 7 If an amount of coolant 7 that is smaller than the minimum current is to be applied to the rolling stock 1, it is only necessary to open a valve 15 arranged in the return line 14 accordingly (bypass operation). Furthermore, the shut-off device 13 must be present in this case. In this case, the shut-off device 13 and the valve 15 must be designed as control valves. In this case, too, the shut-off device 13 is only closed (completely or partially) when the actual current F is below the minimum current Fmin. The situation that the target current F * assumes values below the minimum current occurs very rarely in practice. As a rule - if the actual current F is above the minimum current Fmin - the shut-off device 13 can thus be fully opened and the bypass valve 15 can remain completely closed.
  • the target current F * can vary. With larger values, a speed n of the pump 10 is at significant values, so that the pump 10 actively pumps (pumps) the coolant 7. The pump 10 thereby consumes energy E. However, if the target current F * becomes smaller, it can happen that the pump 10 continues to rotate in the same direction of rotation as with larger values, but the pump 10 is operated as a generator. So it gives off energy E. For example, the energy E can be fed back into a supply network via the drive 12 of the pump 10. It is even possible that the pump 10 is operated with the direction of rotation inverted (“speed n ⁇ 0”). In this case, the pump 10 continues to consume energy because it is actively trying to return coolant 7.
  • a check valve 16 or a check valve is arranged between the pump 10 and the application device 6.
  • the check valve 16 or the check valve can work purely passively.
  • the check valve 16 or the check valve can, for example, be acted upon by a slight spring force, so that they are preloaded towards the closed position, but open at a very low pressure.
  • the check valve 16 or the check valve need not be actively controlled by the control device 11.
  • the check valve 16 or the check valve in particular prevent the supply line 8 between the pump 10 and the application device 6 from running empty when the direction of rotation is inverted.
  • the pump 10 can be switched off as soon as the shut-off device 13 is closed, ie blocking further flow of the coolant 7. Since the shut-off device 13 does not have to brake the flow of the coolant 7, but only closes when the flow of the coolant 7 has already stopped or at least essentially stopped, a comparatively simple embodiment is sufficient the shut-off device 13. Furthermore, the shut-off device 13 can have a low dynamic, since dynamic settings are made by the pump 10. Furthermore, such a check valve 16 or such a check valve is also required if an application device 6 arranged above the rolling stock 1 is fed via the pump 10. Otherwise, the coolant 7 would flow backwards through the pump 10 into the reservoir 9 at speed 0. This could empty a buffer area of the application device 6. The buffer area would then only have to be filled again when the pump 10 is switched on again. This would increase the effective response time of the application device 6, which - of course - is not desirable.
  • the pump 10 can have conventional paddle wheels.
  • the pump 10 can be designed such that when the pump 10 is at a standstill, the coolant 7 cannot simply flow through. In this case, the pump 10 must be designed in such a way that it at least largely seals when it is at a standstill.
  • the pump 10 can be designed such that it can also be operated in reverse. In the latter case in particular, it is sensible to actuate the shut-off device 13 after reducing the actual current F to 0.
  • the coolant 7 has a pre-pressure
  • the pump 10 it is possible for the pump 10 to be controlled purely.
  • the inlet pressure pE of the liquid coolant 7 is detected and fed to the control device 11.
  • the control device 11 takes into account the detected pressure pE on the input side when determining the desired activation state of the pump 10.
  • one is equivalent to a pressure version Detection of the water level in the reservoir 9.
  • it is also as in FIG 4 shown, also possible to additionally detect the outlet pressure pA behind the pump 10 and to supply it to the control device 11.
  • the control device 11 also takes into account the detected output pressure pA when determining the target activation state of the pump 10.
  • the control device 11 is preferably aware of the thermodynamic energy state H of the rolling stock 1 immediately before the application device 6 is reached.
  • the thermodynamic energy state H can in particular be the enthalpy or the temperature of a respective section of the rolling stock 1.
  • the control device 11 determines according to the illustration in FIG FIG 10 first, depending on the thermodynamic energy state H, the target current F * and then on the basis of the target current F * the associated target control state S *.
  • the control device 11 it is possible for the control device 11 to be given a local or temporal target profile of the thermodynamic energy state H, which is to be maintained as far as possible.
  • the control device 11 can therefore determine which thermodynamic energy state H is to be present immediately behind the application device 6. By comparing it with the actual thermodynamic energy state H immediately before the application device 6, the control device 11 can therefore determine the amount of coolant 7 that has to be applied to the corresponding section of the rolling stock 1, so that the actual thermodynamic energy state H immediately behind the application device 6 corresponds to the desired target state corresponds as well as possible. The required amount of coolant 7 then defines the desired current F * in connection with the time which the corresponding section of the rolling stock 1 needs to pass through the application device 6.
  • thermodynamic energy state H of the corresponding section of the rolling stock 1 varies from application device 6 to application device 6. In particular, it is changed by each of the application devices 6.
  • the thermodynamic energy state H of the control device 11 can be predetermined as such for the application device 6, which first applies its share of coolant 7 to the rolling stock 1.
  • a temperature measuring station 17 can be arranged on the input side of the cooling section 2, by means of which the temperature T is recorded for the individual sections of the rolling stock 1. The detected temperature T is then assigned to the respective section.
  • thermodynamic energy state H of the rolling stock 1 (or the corresponding section of the rolling stock 1) must be updated.
  • the control device 11 takes into account in particular the thermodynamic energy state H immediately before the immediately preceding application device 6 and the amount of coolant 7 which the immediately preceding application device 6 applies to the rolling stock 1.
  • the control device 11 can alternatively take into account the target current F * or the actual current F of the immediately preceding application device 6. It therefore determines the thermodynamic energy state H of the rolling stock 1 sequentially in succession for the application devices 6. If necessary, the control device can 11 use a heat conduction equation and a phase transformation equation in this context and solve iteratively.
  • the rolling stock 1 is a flat rolling stock, for example a strip or a heavy plate.
  • the liquid coolant it is possible for the liquid coolant to be applied to the rolling stock 1 from both sides by means of each individual application device.
  • This procedure is often taken in the case of a cooling section 2 which is arranged upstream of the rolling train or arranged in the rolling train. But it can also be taken if the cooling section 2 is arranged downstream of the rolling mill.
  • the liquid coolant 7 is generally applied to the rolling stock 1 from one side only, in particular from above or from below, by means of each individual application device. It is of course also possible in this case to apply coolant 7 to both sides of the flat rolling stock. In this case, however, this is done by different application devices 6, each of which is assigned its own pump 10, the pump 10 being controlled independently of the pumps 10 of the other application devices 6.
  • the application devices 6 each have only a single spray nozzle 18.
  • the application devices 6 each have a plurality of spray nozzles 18.
  • the spray nozzles 18 can, as shown in FIG FIG 11 seen in the transport direction x of the rolling stock 1 can be arranged one behind the other.
  • the spray nozzles 18 can, for example, be arranged one behind the other within a single spray bar 19.
  • a plurality of spray bars 19 arranged one behind the other in the transport direction x can also be combined to form one (1) application device 6. This applies regardless of whether the respective spray bar 19 as such has a plurality of spray nozzles 18 arranged one behind the other or not. It is crucial in any case that each application device 6 in each case Via its own supply line 8, its own pump 10 is individually supplied with coolant 7, the pump 10 being individually controlled to set the respective actual current F.
  • the application devices 6 can, as shown in FIG FIG 12 furthermore often have a plurality of spray nozzles 18 which, as seen transversely to the transport direction x of the rolling stock 1, are arranged next to one another.
  • a configuration can be particularly useful in the case of flat rolled stock 1, that is to say in the case of a strip or a heavy plate.
  • the application devices 6 can extend over the full width of the rolling stock 1.
  • several application devices 6 are arranged side by side, each of which is supplied with coolant 7 via its own supply line 8 and its own pump 10, the pumps 10 being controlled independently of one another.
  • the present invention has many advantages, some of which are listed below.
  • the actual flow F of the respective application device 6 can also be set correspondingly quickly.
  • the drives 12 for the pumps 10 can be controlled very precisely. A usual accuracy of the speed n is in the range of 0.1%.
  • the actual current F for the respective application device 6 can also be set with the same or a similar accuracy. Taking into account the Response behavior of the drives 12 should in all probability be able to track the actual flow F with 1% accuracy in less than 0.5 s, possibly even in 0.2 s to 0.3 s.
  • the coolant 7 is made available to the pumps 10 without pressure on the inlet side, particularly fast control times can be achieved.
  • the distance of the reservoir 9 from one of the application devices 6 and thus the length of the associated supply line 8 is a quite common length of 10 m.
  • Flow velocities in the supply line 8 at maximum flow are normally around 3 m / s. If such a quantity of liquid is accelerated with a pressure of 2 bar, the result is an acceleration of 20 m / s 2 . With such an acceleration, the amount of liquid can be accelerated from 0 to maximum flow with a time constant of 150 ms.
  • the pumps 10 are coupled on the input side.
  • the acceleration of the effective liquid column in this common pipeline must also be taken into account. This can have effects in particular if many of the pumps 10 are to be started up or shut down at the same time. In practice, however, this condition rarely occurs, so that the problems that arise can be tolerated. In addition, that can Problem can be avoided by a suitable predictive control of the pumps 10.
  • the cooling section 2 can be operated with a low energy consumption.
  • some of the application devices 6 can be designed as customary underside intensive cooling bars with a spray height of 20 m, which apply the coolant 7 to the rolling stock 1 from below.
  • the corresponding application device 6 can be operated with a pump 10 with a nominal output of 25 kW given an assumed amount of coolant 7 of 360 m 3 / h.
  • 360 m 3 / h corresponds to 0.1 m 3 / s.
  • 20 m spray height corresponds to an operating pressure of 2 bar, i.e. 200 kPa.
  • intensive cooling of the prior art uses around twice the pressure. Similar figures result for intensive cooling on the top.
  • the energy saving becomes even greater if the respective application device 6 is operated with a smaller amount of water.
  • the reduction in the amount of water is achieved by closing a valve.
  • the pressure (4 bar) is maintained, the pump 10 often continues to run at the full delivery rate.
  • the speed n of the pump 10 is simply reduced.
  • half the amount of water only a spray height of 5 m occurs. So only half of the amount has to be pumped with a quarter of the spraying height. This means that only 1/8 of the full power is required, i.e. just over 3 kW. In contrast, around 25 kW still have to be used in the intensive cooling of the prior art.
  • the wear on pumps 10 and drives 12 is low. Typical downtimes for pump bearings are 100,000 hours and more. This enables the pumps 10 to be operated continuously for over 11 years without the need for maintenance.
  • the cooling section 2 according to the invention is therefore very fail-safe and requires almost no maintenance with regard to the pumps 10 and the drives 12.
  • Another advantage that results is a very flexible operation of the cooling section 2.
  • one and the same application devices 6 can be used and operated as intensive cooling or as laminar cooling as required.
  • the usable control range is usually between 5% and 100% of the maximum coolant that can be pumped.
  • the costs for the cooling section 2 according to the invention are of the same order of magnitude as the costs for a conventional intensive cooling.
  • 16 upper and lower spray bars 19 each a total of 32 relatively small pumps 10 and the associated drives 12 of 25 kW each with a total electrical output of 800 kW are required.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Metal Rolling (AREA)
  • Heat Treatment Of Strip Materials And Filament Materials (AREA)
  • Heat Treatments In General, Especially Conveying And Cooling (AREA)
EP18185526.3A 2018-07-25 2018-07-25 Section de refroidissement à réglage de flux de liquide de refroidissement à l'aide des pompes Withdrawn EP3599037A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP18185526.3A EP3599037A1 (fr) 2018-07-25 2018-07-25 Section de refroidissement à réglage de flux de liquide de refroidissement à l'aide des pompes
CN201980049320.7A CN112469516B (zh) 2018-07-25 2019-07-23 用于冷却部段的运行方法和冷却部段
PCT/EP2019/069763 WO2020020868A1 (fr) 2018-07-25 2019-07-23 Zone de refroidissement à ajustement des flux de fluide de refroidissement par des pompes
US17/261,080 US11167332B2 (en) 2018-07-25 2019-07-23 Cooling section with coolant flows which can be adjusted using pumps
EP19740415.5A EP3826780B1 (fr) 2018-07-25 2019-07-23 Section de refroidissement à réglage de flux de liquide de refroidissement à l'aide de pompes

Applications Claiming Priority (1)

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EP18185526.3A EP3599037A1 (fr) 2018-07-25 2018-07-25 Section de refroidissement à réglage de flux de liquide de refroidissement à l'aide des pompes

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EP19740415.5A Active EP3826780B1 (fr) 2018-07-25 2019-07-23 Section de refroidissement à réglage de flux de liquide de refroidissement à l'aide de pompes

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EP3895819B1 (fr) 2020-04-14 2023-06-07 Primetals Technologies Germany GmbH Fonctionnement d'un dispositif de refrodissement avec une pression de fonctionnement minimale
DE102020205252A1 (de) * 2020-04-24 2021-10-28 Kocks Technik Gmbh & Co Kg Vorrichtung zum Kühlen von Langprodukten und Verfahren zum Kühlen eines Langproduktes unter Verwendung derselben

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US20210245215A1 (en) 2021-08-12
WO2020020868A1 (fr) 2020-01-30
CN112469516A (zh) 2021-03-09
CN112469516B (zh) 2023-04-11
EP3826780A1 (fr) 2021-06-02
EP3826780B1 (fr) 2023-01-25
US11167332B2 (en) 2021-11-09

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