EP3826780B2 - Section de refroidissement à réglage de flux de liquide de refroidissement à l'aide de pompes - Google Patents

Section de refroidissement à réglage de flux de liquide de refroidissement à l'aide de pompes

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Publication number
EP3826780B2
EP3826780B2 EP19740415.5A EP19740415A EP3826780B2 EP 3826780 B2 EP3826780 B2 EP 3826780B2 EP 19740415 A EP19740415 A EP 19740415A EP 3826780 B2 EP3826780 B2 EP 3826780B2
Authority
EP
European Patent Office
Prior art keywords
pump
coolant
cooling section
application device
rolled product
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP19740415.5A
Other languages
German (de)
English (en)
Other versions
EP3826780A1 (fr
EP3826780B1 (fr
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
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Application filed by Primetals Technologies Germany GmbH filed Critical Primetals Technologies Germany GmbH
Publication of EP3826780A1 publication Critical patent/EP3826780A1/fr
Application granted granted Critical
Publication of EP3826780B1 publication Critical patent/EP3826780B1/fr
Publication of EP3826780B2 publication Critical patent/EP3826780B2/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/74—Temperature control, e.g. by cooling or heating the rolls or the product
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/74—Temperature control, e.g. by cooling or heating the rolls or the product
    • B21B37/76—Cooling control on the run-out table
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B45/00—Devices for surface or other treatment of work, specially combined with or arranged in, or specially adapted for use in connection with, metal-rolling mills
    • B21B45/02—Devices for surface or other treatment of work, specially combined with or arranged in, or specially adapted for use in connection with, metal-rolling mills for lubricating, cooling, or cleaning
    • B21B45/0203—Cooling
    • B21B45/0209—Cooling devices, e.g. using gaseous coolants
    • B21B45/0215—Cooling devices, e.g. using gaseous coolants using liquid coolants, e.g. for sections, for tubes
    • B21B45/0218—Cooling devices, e.g. using gaseous coolants using liquid coolants, e.g. for sections, for tubes for strips, sheets, or plates

Definitions

  • a metallic workpiece is cooled after rolling.
  • the workpiece can be made of steel or aluminum, for example. Depending on requirements, it can be a flat workpiece (strip or heavy plate), a rod-shaped workpiece, or a profile. Precise temperature control in the cooling section is standard practice to achieve desired material properties and maintain them with low temperature variation.
  • spray bars are installed along the cooling section for this purpose. These spray bars apply a liquid coolant, usually water, to the hot workpiece from above and below to cool it. The amount of water flowing through each spray bar should be adjustable as quickly and precisely as possible.
  • Switching valves can only be controlled in a purely binary manner. They are therefore either fully open or fully closed. Control valves can be adjusted continuously, so that the amount of water supplied to each spray bar can also be continuously adjusted.
  • valves In the case of control valves, the valves can be designed as butterfly valves or ball valves.
  • Butterfly valves are relatively simple and inexpensive. However, they can only be operated with relatively small pressure differentials, usually a maximum of 1 bar. Otherwise, cavitation occurs, which damages the butterfly valve very quickly. Butterfly valves are therefore particularly unsuitable for intensive cooling. They are also often disadvantageous in laminar cooling systems. In particular, they frequently exhibit switching hysteresis. Switching hysteresis means that, with the same control signal, the set valve angle varies depending on whether the butterfly valve is moved from a more open or a more closed position to the new position. Ball valves do not have a flap, but rather a perforated ball that rotates within a tube.
  • Ball valves can be operated with higher pressure differentials up to approximately 3 bar. Hysteresis does not occur with them or is negligibly small. However, ball valves are expensive.
  • the spray bar is continuously supplied with coolant.
  • a controllable deflector plate is present.
  • the coolant is either directed towards the rolled material or flows off to the side without contributing to its cooling.
  • rapid switching operations without pressure surges are possible.
  • continuous adjustment of the water flow is not possible.
  • the full coolant flow must be maintained at all times.
  • valves including deflection plates, require appropriate actuators.
  • Pneumatic actuators are common. Actuators are driven.
  • a position control system is also required. This continuously compares the actual position of the respective control valve with its target position and adjusts the actual position until a sufficient match with the target position is achieved.
  • the coolant can be drawn from an elevated tank or transported via a larger pipeline from a more distant pumping station. Combinations of these methods are also possible.
  • intensive cooling water is often first drawn from an elevated tank. The pressure is then increased to a variable extent using booster pumps, and thus supplied to the intensive cooling system at a correspondingly variable pressure.
  • booster pumps are present, all connected in parallel, meaning they all draw coolant from the same reservoir and supply it to a common collection point.
  • the intensive cooling system is equipped with several spray bars, each of which receives its own individual coolant supply line from the booster pumps or the common collection point. Ball valves are installed in these supply lines, which are controlled to regulate the amount of coolant supplied to each spray bar.
  • a descaling device in which a pump is driven by a variable-speed drive.
  • the control of the drive takes into account the operating state of the descaling area and the fill level of a high-pressure accumulator.
  • a casting process utilizes, among other things, a cooling water source comprising a water-cooled coil.
  • the cooling water is supplied to the coil via a pump that can be switched on and off and has a mechanism for controlling the amount of coolant.
  • the liquid is recirculated.
  • the temperature of the cast metal strand is measured and transmitted to a control unit. Based on this measurement, the control unit regulates the cooling water source.
  • a process is known in which a metal strip is cooled with a liquid cooling medium in a cooling unit during heat treatment.
  • the metal strip runs vertically from bottom to top.
  • the cooling medium is pentane or a mixture of pentane and hexane.
  • the metal strip is located in a protective gas atmosphere.
  • a quantity of coolant is determined to be pumped to the application devices of the cooling unit. The pump is controlled accordingly.
  • a casting process is known in which the cast strand is passed through a cooling chamber where it is cooled with a liquid cooling medium.
  • the liquid cooling medium is a metal or a molten salt.
  • the liquid cooling medium is drawn from a reservoir by a circulating pump, fed into the cooling chamber, and then returned to the reservoir from the cooling chamber.
  • the amount of liquid is regulated depending on the temperatures at which the liquid cooling medium is supplied to and discharged from the cooling chamber, and depending on the inlet pressure of the cooling chamber.
  • a casting process is known in which the cast strand is formed using a two-roll casting machine.
  • the rolls are cooled internally with a liquid cooling medium.
  • the liquid cooling medium is a metal or a molten salt.
  • the liquid cooling medium is drawn from a reservoir by means of a circulating pump, fed to the rolls, and then returned to the reservoir from the cooling chamber.
  • a cooling section is known that is downstream of a rolling mill and by means of which hot rolled metal is cooled.
  • This cooling section has several application devices, each of which receives a specific flow of a liquid, water-based coolant via a supply line. The respective flow of coolant is applied to the hot rolled metal by the respective application device. During the application of the coolant, the hot rolled metal is transported horizontally within the cooling section.
  • a cooling section is also known, which is located downstream of a rolling mill and by means of which hot rolled metal is cooled.
  • This cooling section has several application devices, each of which receives a specific flow of a liquid, water-based coolant via its own supply line. The respective flow of coolant is applied to the hot rolled material by the respective application device.
  • the hot rolled material is transported horizontally within the cooling section.
  • Valves are arranged in the supply lines, the opening positions of which are dynamically adjusted by a control unit of the cooling section.
  • a common pump located upstream of the supply lines is set by the control unit according to the total flow to be applied to the rolled material by the application devices as a whole.
  • the object of the present invention is to create possibilities by means of which a cooling section with superior operating characteristics can be realized in a simple and reliable manner.
  • an operating method of the type mentioned at the outset is first designed in such a way that a control device of the cooling section dynamically determines a respective target control state for the respective pump depending on a respective target flow of coolant to be applied to the hot rolled material by means of the respective application device and controls the respective pump accordingly, so that the respective actual flow delivered by the respective pump is always as close as possible to the respective target flow.
  • the drive for the pump – is therefore a variable-speed drive. It can, for example, be inverter-controlled. Within the framework of dynamic control, only the pump itself is controlled, not any valve that may be located in the supply line.
  • Control or regulation can be implemented as needed.
  • the actual flow rate of the liquid coolant is measured at the input or output side of the respective pump and fed to the control unit.
  • the rolled material is a flat product, such as a strip or a heavy plate.
  • the liquid coolant it is possible for the liquid coolant to be applied to the rolled material from both sides using the respective application device.
  • the liquid coolant it is possible for the liquid coolant to be applied to the rolled material from only one side, in particular from above or below, using the respective application device.
  • two application devices are required, which are controlled separately and, in principle, can also be operated independently of each other.
  • the operating method according to the invention is thus, so to speak, implemented twice in this case.
  • the control of both pumps can be carried out uniformly by one and the same control unit.
  • the control unit can also take into account any interdependencies in the cooling process, if necessary.
  • the application device can have several spray nozzles arranged in series in the direction of the rolled material's transport.
  • groups of spray nozzles can be formed within a single spray bar, each supplied with coolant via its own supply line and pump.
  • groups of spray nozzles can be formed that span multiple spray bars and are supplied with coolant via their respective supply lines and pumps. This configuration can be particularly advantageous because it requires fewer pumps than if each spray bar were supplied with coolant via its own supply line and pump.
  • the application device has several spray nozzles arranged side by side, perpendicular to the direction of travel of the rolled material. This can be particularly useful for flat rolled materials (strip or heavy plate).
  • the application device can then extend across the full width of the rolled material or only a portion of it. In the latter case, several application devices are positioned side by side. arranged, each supplied with coolant via its own supply line and pump, with the pumps being controlled independently of each other.
  • shut-off device no shut-off device is arranged between the respective pump and the respective application device.
  • a shut-off device between the respective pump and the respective application device.
  • the shut-off device is either kept fully open permanently during the transport of the rolled material through the cooling section or is actuated, both opening and closing, only when the rotational speed of the respective pump is below a minimum speed.
  • the respective minimum speed is so low that only a very small actual flow is conveyed.
  • the shut-off device it is also possible according to the invention for the shut-off device to be actuated only manually in order to take the respective application device out of service, for example, for maintenance purposes.
  • a return line is arranged parallel to each pump, the return line having a smaller cross-section than the respective supply line. This allows the use of pumps in which, due to their design, a certain minimum coolant flow rate must always be maintained. However, this minimum flow rate is considerably smaller than the maximum possible coolant flow rate. If, in such a case, a quantity of coolant is to be applied to the rolled material that is less than the respective minimum flow rate, it is only necessary to open a valve arranged in the return line accordingly (bypass operation).
  • the respective pump can operate as a generator or with reversed rotation whenever the target current falls below a certain lower limit. This allows for very low actual currents. Furthermore, this prevents an excessively high actual current from flowing through a pump that does not self-lock when the target current is low.
  • a check valve or non-return valve is provided in the respective supply line between the respective pump and the respective application device. This prevents the respective pump from running dry and thus being damaged.
  • the system provides that the inlet pressure of the liquid coolant is measured upstream of each pump, and that the control unit takes this measured inlet pressure into account when determining the target operating state of each pump. This allows for a more precise determination of the target operating state for each pump.
  • the control unit determines the respective target current based on the thermodynamic energy state of the rolled material immediately before it reaches the respective application device.
  • the thermodynamic energy state of the rolled material can be known to the control unit, for example, from a previous measurement. Alternatively, it is possible to perform a model-based calculation of the respective thermodynamic energy state based on a known thermodynamic energy state.
  • the operating method according to the invention is preferably designed such that the control unit determines the respective thermodynamic energy state of the rolled material based on the thermodynamic energy state of the rolled material before the immediately preceding application device, additionally taking into account the target coolant flow or the actual coolant flow that is to be applied or is being applied to the hot rolled material by means of the immediately preceding application device.
  • the calculation of the thermodynamic energy states can therefore be carried out sequentially.
  • cooling section with the features of claim 8.
  • Advantageous embodiments of the cooling section are the subject of dependent claims 9 to 14.
  • a cooling section of the type mentioned at the outset is first designed in such a way that the control device is designed in such a way that, depending on a respective target flow of coolant to be applied to the hot rolled material by means of the respective application device, it dynamically determines a respective target control state for the respective pump and controls the respective pump accordingly, so that the respective actual flow delivered by the respective pump is always as close as possible to the respective target flow.
  • the control device is designed in such a way that, depending on a respective target flow of coolant to be applied to the hot rolled material by means of the respective application device, it dynamically determines a respective target control state for the respective pump and controls the respective pump accordingly, so that the respective actual flow delivered by the respective pump is always as close as possible to the respective target flow.
  • no shut-off device is arranged between each pump and each feeder, or a shut-off device is arranged.
  • shut-off device If a shut-off device is present, it is either kept fully open by the control unit during the transport of the rolled material through the cooling section, or it is actuated in both opening and closing modes only when the speed of the respective pump falls below a minimum speed. Finally, a return line is arranged parallel to each pump, with the return line having a smaller cross-section than the respective supply line.
  • the advantageous designs of the cooling section essentially correspond to those of the operating process.
  • the advantages achieved thereby also correspond to the respective corresponding designs of the operating process.
  • FIG 1 A hot rolled metal stock 1 is to be cooled in a cooling section 2.
  • the cooling section 2 is designed according to FIG 1 downstream of a rolling mill. It is shown in FIG 1 Only one rolling stand 3 of the rolling mill, namely the last rolling stand 3 of the rolling mill. However, the rolling mill usually has several rolling stands 3, which the hot rolled material 1 passes through sequentially. In the case of the configuration according to FIG 1 The hot rolled material 1 enters the cooling section 2 immediately after passing through the last rolling stand 3 of the rolling mill. The time interval between rolling in the last rolling stand 3 of the rolling mill and entering the cooling section 2 is on the order of a few seconds.
  • cooling section 2 could be configured as shown in FIG 2 It is located upstream of the rolling mill. This is depicted in FIG 2 likewise, only a single rolling stand 4 of the rolling mill, namely the first rolling stand 4 of the rolling mill. However, the rolling mill often exhibits – as in the design according to FIG 1 - several rolling stands 3, which the hot rolled material 1 passes through sequentially one after the other. In the case of the configuration according to FIG 2 The hot rolled material 1 is rolled in the first rolling stand 4 of the rolling mill immediately after exiting the cooling section 2. The time interval between cooling in the cooling section 2 and rolling in the first rolling stand 4 of the rolling mill is on the order of a few minutes. However, it can also be as short as a few seconds.
  • cooling section 2 could be configured as shown in FIG 3 They are located within the rolling mill. They are shown in FIG 3 two rolling stands 5 of the rolling mill. In this case, the cooling of the rolled material 1 – more precisely: a section of the rolled material 1 – takes place in the cooling section 2 between the rolling in the two rolling stands 5 of the rolling mill. The time interval between cooling in the cooling section 2 and rolling in the two successive rolling stands 5 of the rolling mill is on the order of a few seconds. According to the illustration in FIG 3 The cooling section 2 is arranged between two consecutive rolling stands 5 of the rolling mill. However, it could also extend over a larger area, so that the cooling section 2 passes through at least one FIG 3 The further rolling mill stand, not shown, is divided into a corresponding number of sections.
  • the rolled material 1 consists of metal.
  • the rolled material 1 can be made of steel or aluminum. Other metals are also possible.
  • the temperature of the rolled material 1 before cooling section 2 is typically between 750 °C and 1,200 °C. In cooling section 2, it is cooled to a lower temperature. In some cases, the lower temperature may be only slightly below the temperature before cooling section 2. However, particularly if cooling section 2 is located downstream of the rolling mill, the rolled material 1 is usually cooled to a significantly lower temperature, for example, between 200 °C and 700 °C.
  • the hot rolled material 1 is fed to the cooling section 2 in a horizontal transport direction x. Within the cooling section 2, the hot rolled material 1 does not change its transport direction x. It is therefore transported horizontally throughout the cooling section 2. After leaving the cooling section 2, the rolled material 1 can either maintain or change its transport direction. If the hot rolled material 1 is a strip, it can, for example, be deflected diagonally downwards to feed it to a coiler. If the hot rolled material 1 is a heavy plate, it usually maintains its transport direction x. A roller conveyor that may be required for transporting the hot rolled material 1 is not shown in the FIG.
  • Cooling section 2 has a number of application devices 6.
  • a coolant 7 is applied to the rolled material 1 by means of the application devices 6.
  • the coolant 7 is water.
  • small amounts (maximum 1% to 2%) of additives may be added to the water.
  • the coolant 7 is a liquid, water-based coolant.
  • only one application device 6 is present. In many cases, however, several application devices 6 are present.
  • the application devices can be arranged as shown in FIG 1
  • the application devices 6 are arranged one after the other. In this case, the application devices 6 sequentially apply their respective portion of the coolant 7 to the rolled stock 1.
  • the term "sequentially" refers in this context to a specific section of the rolled stock 1, as this section sequentially passes through areas in which the individual application devices 6 apply their respective portion of the coolant 7 to the corresponding section of the rolled stock 1.
  • the number of application devices 6 is often in the double digits, sometimes even in the upper double digits.
  • a sequential arrangement is generally implemented, in particular, when the cooling section 2 is downstream of the rolling mill. However, it can also occur in other configurations.
  • the application devices 6 are connected to a coolant reservoir 9 via a supply line 8.
  • the reservoir 9 is the same for all application devices 6.
  • a pump 10 is located in each supply line 8.
  • the pumps 10 can be located at any point within the supply lines 8. In practice, however, it is advantageous if the pumps 10 are located as close as possible to the reservoir 9.
  • the application device 6 receives a current flow rate F of coolant 7 from reservoir 9 via supply line 8 and pump 10. This current flow rate F is applied to the hot rolled material 1 by means of the respective application device 6.
  • the distance between the application device 6 – for example, from spray nozzles – and the rolled material 1 is typically between 20 cm and 200 cm.
  • a control unit 11 of the cooling section 2 is aware of a corresponding target flow rate F*, which is to be applied to the hot rolled material 1 by means of the application device 6.
  • the target flow rate F* is generally not constant over time, but variable, i.e., a function of time t.
  • the control unit 11 dynamically determines a target control state S* for the pump 10. It controls the pump 10 accordingly.
  • the pump 10 thereby pressurizes the coolant 7 at the pump 10 outlet with an outlet pressure pA.
  • the outlet pressure pA varies according to the target control state S*. However, it is below 10 bar in every operating state. It is usually at a maximum of 6 bar. In every operating state, however, the actual flow rate F delivered by the pump 10 is always approximated to the target flow rate F* as closely as possible.
  • the target control state S* can also be easily determined. This will be explained below using a simple example.
  • the supply line 8 has a length 1 and a cross-sectional area A.
  • the pressure at the inlet of pump 10 is subsequently denoted by pE.
  • the pressure in the delivery device 6 is denoted by p0.
  • FN is a nominal flow rate that flows from the application device 6 when the coolant 7 in the application device has a nominal pressure pN.
  • the nominal flow rate FN and the nominal pressure pN are defined and determined by the design of the application device 6. They can be determined, for example, by a single measurement of the flow rate that results at a pressure that can be set arbitrarily.
  • the required outlet pressure pA can be easily determined.
  • the actual current F is available to the control unit 11 at all times – either through measurement or calculation according to equation (6). This is necessary to be able to calculate and update the thermodynamic energy state H of the rolled material 1. This will be discussed in more detail later.
  • the only remaining dead time of the application device 6 is the generally very short time that the coolant 7 needs to reach the rolled material 1 – calculated from the point where it exits the application device 6.
  • pump 10 – In order to control pump 10 accordingly, pump 10 – more precisely, its drive 12 – must be capable of operating at variable speeds.
  • the drive 12 of pump 10 can be inverter-controlled for this purpose.
  • Pump 10 should preferably be operable within a control range between 0 and a maximum speed.
  • the pump 10's seal should also be designed for low speeds. This is readily achievable, however, as suitable pumps 10 are known to experts.
  • pump 10 is dynamically controlled accordingly, thereby approximating the actual current F to the target current F* as closely as possible.
  • no valve located in the supply line 8 is controlled. Any such 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 The line is only shown with a dashed line because it may be present, but it is not necessarily present. If the shut-off device 13 is present, it can be operated in two different ways.
  • the shut-off device 13 is kept fully open permanently during the transport of the rolled material 1 through the cooling section 2. This is in FIG 5 This is illustrated by the fact that the rolled material 1 enters the cooling section 2 at time t1. However, even before time t1, at time t2, the Shut-off device 13 is open. Similarly, the rolled material 1 exits the cooling section 2 at time t3. Only after time t3 is the shut-off device 13 closed again at time t4. Between times t2 and t4, the shut-off device 13 remains fully open.
  • the shut-off device 13 is only activated when the speed of the pump 10 is below a minimum speed nmin. This is explained below in conjunction with FIG 6 explained in more detail.
  • the speed of pump 10 can vary between 0 and a nominal speed nmax. As long as the speed n remains below a minimum speed nmin, the shut-off device 13 can be actuated. This applies to both opening and closing the shut-off device 13. However, 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, the shut-off device 13 must first be opened at a very low speed n. The application device 6 then operates, during which only the pump 10 is controlled to adjust the actual current F. Only when the speed n falls below the minimum speed nmin again can and may the shut-off device 13 be actuated again.
  • the minimum flow rate is considerably lower than the maximum possible flow rate of coolant 7. If, in the case of the configuration according to FIG 7 If a quantity of coolant 7 is to be applied to the rolled material 1 that is less than the minimum flow rate, it is only necessary to open a valve 15 located in the return line 14 accordingly (bypass operation). Furthermore, the shut-off device 13 must be present in this case. The shut-off device 13 and the valve 15 must be designed as control valves. However, even in this case, the shut-off device 13 will only close (fully or partially) if the actual flow rate F is below the minimum flow rate. The situation in which the target flow rate F* assumes values below the minimum flow rate occurs very rarely in practice. As a rule – i.e., if the actual flow rate F is above the minimum flow rate – the shut-off device 13 can remain fully open and the bypass valve 15 can remain fully closed.
  • the target current F* can vary. At higher values, the rotational speed n of pump 10 reaches significant values, so that pump 10 actively pumps the coolant 7. Pump 10 thus consumes energy E. However, if the target current F* decreases, pump 10 may continue to rotate in the same direction as at higher values, but it will operate as a generator. It will therefore supply energy E. For example, this energy E can be fed back into a power grid via the pump 10's drive 12. It is even possible for pump 10 to operate with reversed rotation ("rotational speed n ⁇ 0"). In this case, pump 10 continues to consume energy because it is actively attempting to pump the coolant 7 back.
  • a check valve 16 or a check flap is arranged between the pump 10 and the application device 6.
  • the check valve 16 or the check flap can operate purely passively.
  • the check valve 16 or the check flap can be actuated by a slight spring force, so that it is pre-loaded towards the closed position but opens even at a very low pressure.
  • the check valve 16 or the check flap does not need to be actively controlled by the control device 11.
  • the check valve 16 or the check flap prevents the supply line 8 between the pump 10 and the application device 6 from running dry when the direction of rotation is reversed.
  • the pump 10 can be switched off as soon as the shut-off device 13 is closed, thus blocking further flow of the coolant 7. Since the shut-off device 13 does not need to slow down the flow of the coolant 7, but only closes when the flow of the coolant 7 has already stopped or is at least substantially stopped, a comparatively simple embodiment of the shut-off device 13 suffices. Furthermore, the shut-off device 13 can have low dynamics, as dynamic adjustments are made by the pump 10. Such a check valve 16 or check flap is also necessary if an application device 6 located above the rolled material 1 is supplied via the pump 10. Otherwise, at zero rotational speed, the coolant 7 would flow backward through the pump 10 into the reservoir 9. This could empty a buffer zone of the application device 6. The buffer zone would then only need to be refilled when the pump 10 is switched on again. This would increase the effective response time of the application device 6, which is – of course – undesirable.
  • the pump 10 can have conventional impellers. However, if the coolant 7 has a pre-pressure, for example 1 bar, the pump Pump 10 must be designed such that the coolant 7 cannot simply flow through it when the pump 10 is at rest. In this case, the pump 10 must be designed to seal at least to a large extent when at rest. Alternatively, the pump 10 can be designed to operate in reverse. Particularly in the latter case, it is advisable to actuate the shut-off device 13 after reducing the actual current F to 0.
  • FIG 9 The operating methods explained were useful.
  • the control unit 11 takes the measured inlet pressure pE into account when determining the target control state of pump 10. Measuring the water level in reservoir 9 is often equivalent to measuring the pressure. If necessary, as also described in FIG 4 As shown, it is also possible to additionally measure the outlet pressure pA downstream of pump 10 and feed it to the control unit 11. In this case, the control unit 11 also takes the measured outlet pressure pA into account when determining the target control state of pump 10.
  • control unit 11 it is possible for the control unit 11 to be given a spatial or temporal target profile for the thermodynamic energy state H, which should be maintained as closely as possible.
  • the control unit 11 can therefore determine which thermodynamic energy state H should be present immediately downstream of the application unit 6. By comparing this with the actual thermodynamic energy state H immediately upstream of the application unit 6, the control unit 11 can determine the quantity of coolant 7 that must be applied to the corresponding section of the rolled material 1 so that the actual thermodynamic energy state H immediately downstream of the application unit 6 corresponds as closely as possible to the desired target state.
  • the required quantity of coolant 7, in conjunction with the time that the corresponding section of the rolled material 1 requires to pass through the application unit 6, then defines the target flow rate F*.
  • thermodynamic energy state H of the corresponding section of the rolled material 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.
  • a temperature measuring station 17 is arranged at the inlet of the cooling section 2, by means of which the temperature T is recorded for each section of the rolled material 1. The recorded temperature T is then assigned to the respective section.
  • thermodynamic energy state H of the rolled material 1 (or the corresponding section of the rolled material 1) must be updated.
  • the control unit 11 takes into account, in particular, the thermodynamic energy state H immediately before the immediately preceding application unit 6 and the quantity of coolant 7 that the immediately preceding application unit 6 applies to the rolled material 1.
  • the control unit 11 can alternatively consider the target flow rate F* or the actual flow rate F of the immediately preceding application unit 6. It thus sequentially determines the thermodynamic energy state H of the rolled material 1 for each application unit 6. If necessary, the control unit 11 can formulate and iteratively solve a heat conduction equation and a phase transition equation in this context.
  • the application devices 6 each have only a single spray nozzle 18.
  • the application devices 6 each have several spray nozzles 18.
  • the spray nozzles 18 can be arranged as shown in the illustration. FIG 11
  • the spray nozzles 18 are arranged one after the other in the transport direction x of the rolled material 1.
  • the spray nozzles 18 can be arranged one after the other within a single spray bar 19.
  • Several spray bars 19 arranged one after the other in the transport direction x can also be combined to form a single application unit 6. This applies regardless of whether the respective spray bar 19 as such has several spray nozzles 18 arranged one after the other or not.
  • it is crucial that each application unit 6 is individually supplied with coolant 7 via its own supply line 8 and its own pump 10, with the pump 10 being individually controlled to adjust the respective actual flow rate F.
  • the application devices 6 can be arranged according to the illustration in FIG 12 Furthermore, they often have several spray nozzles 18 arranged side by side transversely to the transport direction x of the rolled material 1. Such a design can be particularly useful for a flat rolled material 1, i.e., a strip or a heavy plate. In this case, the application devices 6 can extend over the full width of the rolled material 1. Alternatively, it is possible for the application devices 6 to extend only over a portion of the width. This is shown purely by way of example in the left part of FIG 12 The figure shows a spray boom 19 which – purely by way of example – is divided in its width into three application units 6. In this case, several application units 6 are arranged side by side, each supplied with coolant 7 via its own supply line 8 and its own pump 10, with the pumps 10 being controlled independently of each other.
  • the present invention has many advantages, some of which are listed below.
  • the actual flow rate F of the respective application device 6 can be adjusted accordingly quickly.
  • the drives 12 for the pumps 10 can be controlled very precisely. A typical accuracy of the rotational speed n is in the range of 0.1%.
  • the actual flow rate F for the respective application device 6 can be set with the same or a similar accuracy. Considering the response characteristics of the drives 12, it should most likely be possible to adjust the actual flow rate F with 1% accuracy in less than 0.5 s, possibly even in 0.2 s to 0.3 s.
  • the coolant 7 is supplied to the pumps 10 at zero pressure on the inlet side, particularly fast response 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 typical 10 m.
  • Flow velocities in the supply line 8 at maximum flow rate are normally around 3 m/s. If such a volume of fluid is accelerated at 2 bar pressure, this results in an acceleration of 20 m/ s2 . With such acceleration, the volume of fluid can be accelerated from zero to maximum flow rate with a time constant of 150 ms.
  • the pumps 10 are coupled at the inlet.
  • the acceleration of the effective liquid column in this common pipe must also be taken into account. This can have an impact, especially if many of the pumps 10 are to be started up or shut down simultaneously. In practice, however, this condition rarely occurs, so the resulting problem is tolerable. Furthermore, the problem can be avoided by suitable predictive control of the pumps 10.
  • the cooling section 2 can be operated with low energy consumption.
  • some of the application devices 6 can be designed as conventional underside intensive cooling beams with a spray height of 20 m, which apply the coolant 7 to the rolled material 1 from below.
  • the corresponding application device 6 can be operated with a pump 10 with a rated output of 25 kW, assuming a coolant 7 flow rate of 360 m3 /h. This is because 360 m3 /h corresponds to 0.1 m3 /s.
  • a spray height of 20 m corresponds to an operating pressure of 2 bar, or 200 kPa.
  • prior art intensive cooling systems operate at approximately twice the pressure. Similar figures result for intensive cooling from the top.
  • the energy savings will be even greater if the respective application unit 6 is operated with a smaller amount of water. This is because, in conventional intensive cooling, the reduction in the amount of water This is achieved by closing a valve. The pressure (4 bar) is maintained, and the pump 10 often continues to run at its full flow rate. In the cooling section 2 according to the invention, however, the speed n of the pump 10 is simply reduced. With half the water volume, this results in a spray height of only 5 m. Therefore, only half the volume needs to be pumped at a quarter of the spray height. This means that only 1/8 of the full power is required, i.e., slightly over 3 kW. In contrast, the intensive cooling methods of the prior art require approximately 25 kW.
  • a further advantage is the highly flexible operation of the cooling section 2.
  • the same application devices 6 can be used and operated as intensive cooling or laminar cooling as required.
  • the usable control range is usually between 5% and 100% of the maximum pumpable coolant quantity.
  • the costs for the cooling section 2 according to the invention are of the same order of magnitude as the costs for conventional intensive cooling.
  • a total of 32 relatively small pumps 10 and the associated drives 12, each with 25 kW, are required, for a total electrical power of 800 kW.
  • an investment in a conventional cooling section requires 32 ball valves, 32 pneumatic actuators, 5 booster pumps, each with 400 kW (one pump is a reserve), and 5 correspondingly large frequency converters.

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)

Claims (14)

  1. Procédé de fonctionnement pour une zone de refroidissement (2), qui est agencée à l'intérieur d'un laminoir ou qui est disposée en amont ou en aval du laminoir et au moyen de laquelle un produit laminé (1) chaud en métal est refroidi,
    - un certain nombre de dispositifs d'application (6) de la zone de refroidissement (2) étant alimentés, par l'intermédiaire d'une conduite d'alimentation (8) respective et d'une pompe (10) respective, en un flux instantané (F) respectif d'un fluide frigorigène (7) liquide, à base d'eau,
    - le flux instantané (F) respectif de fluide frigorigène (7) étant appliqué au moyen du dispositif d'application (6) respectif sur le produit laminé (1) chaud,
    - le produit laminé (1) chaud étant transporté dans la zone de refroidissement (2), pendant l'application du fluide frigorigène (7), dans un sens de transport horizontal (x),
    - un dispositif de commande (11) de la zone de refroidissement (2) déterminant, en fonction d'un flux de consigne (F*) respectif de fluide frigorigène (7) à appliquer au moyen du dispositif d'application (6) respectif sur le produit laminé (1) chaud, de manière dynamique un état de commande de consigne (S*) respectif pour la pompe (10) respective et commandant la pompe (10) respective de manière correspondante, de telle sorte que le flux instantané (F) respectif transporté par la pompe (10) respective s'approche à tout moment autant que possible du flux de consigne (F*) respectif,
    caractérisé
    en ce que, entre la pompe (10) respective et le dispositif d'application (6) respectif,
    - soit aucune dispositif d'arrêt (13) n'est agencé
    - ou alors un dispositif d'arrêt (13) est agencé, le dispositif d'arrêt (13) étant cependant maintenu complètement ouvert en permanence pendant le transport du produit laminé (1) à travers la zone de refroidissement (2)
    - ou alors un dispositif d'arrêt (13) est agencé, le dispositif d'arrêt (13) étant cependant actionné tant en ouverture qu'en fermeture exclusivement lorsqu'une vitesse de rotation de la pompe (10) respective est inférieure à une vitesse de rotation minimale et
    en ce que la pompe (6) respective est agencée en parallèle à une conduite de retour (14) et la conduite de retour (14) présente une section transversale intérieure à celle de la conduite d'alimentation (8) respective.
  2. Procédé de fonctionnement selon la revendication 1,
    caractérisé
    en ce que la pompe respective (10) fonctionne en mode générateur ou avec un sens de rotation inversé à chaque fois que le flux de consigne (F*) respectif passe sous une valeur limite inférieure respective.
  3. Procédé de fonctionnement selon la revendication 2,
    caractérisé
    en ce qu'une soupape antiretour (16) ou un clapet antiretour est agencé(e) dans la conduite d'alimentation (8) respective entre la pompe (10) respective et le dispositif d'application (6) respectif.
  4. Procédé de fonctionnement selon l'une des revendications précédentes,
    caractérisé
    en ce qu'une pression côté entrée (pE) du fluide frigorigène (7) est détectée en amont de la pompe (10) respective et en ce que le dispositif de commande (11) prend en considération la pression côté entrée (pE) détectée lors de la détermination de l'état de commande de consigne (S*) respectif de la pompe (10) respective.
  5. Procédé de fonctionnement selon l'une des revendications précédentes,
    caractérisé
    en ce qu'une pression côté sortie (pA) du fluide frigorigène (7) est détectée en aval de la pompe (10) respective et en ce que le dispositif de commande (11) prend en considération la pression côté sortie (pA) détectée lors de la détermination de l'état de commande de consigne (S*) respectif de la pompe (10) respective.
  6. Procédé de fonctionnement selon l'une des revendications précédentes,
    caractérisé
    en ce que le dispositif de commande (11) détermine le flux de consigne (F*) respectif en fonction d'un état d'énergie thermodynamique (H) respectif du produit laminé (1) qui existe juste avant d'atteindre le dispositif d'application (6) respectif.
  7. Procédé de fonctionnement selon l'une des revendications précédentes,
    caractérisé
    - en ce que les flux instantanés (F) du fluide frigorigène (7) sont appliqués sur le produit laminé (1) chaud au moyen des dispositifs d'application (6) séquentiellement les uns après les autres et
    - en ce que le dispositif de commande (11) détermine l'état d'énergie thermodynamique (H) respectif du produit laminé (1) à l'aide de l'état d'énergie thermodynamique (H) du produit laminé (1) en amont du dispositif d'application (6) immédiatement précédent tout en prenant en considération en plus le flux de consigne (F*) du fluide frigorigène (7) ou le flux instantané (F) du fluide frigorigène (7) qui est appliqué ou qui doit être appliqué au moyen du dispositif d'application (6) immédiatement précédent sur le produit laminé (1) chaud.
  8. Zone de refroidissement, qui peut être agencée à l'intérieur d'un laminoir ou qui peut être disposée en amont ou en aval du laminoir et au moyen de laquelle un produit laminé chaud (1) en métal est refroidi,
    - la zone de refroidissement présentant un certain nombre de dispositifs d'application (6), qui sont alimentés, par l'intermédiaire d'une conduite d'alimentation (8) respective et d'une pompe (10) respective de la zone de refroidissement, en un flux instantané (F) respectif d'un fluide frigorigène (7) liquide, à base d'eau,
    - le flux instantané (F) respectif de fluide frigorigène (7) étant appliqué au moyen du dispositif d'application (6) respectif sur le produit laminé (1) chaud,
    - le produit laminé chaud (1) étant transporté dans la zone de refroidissement, pendant l'application du fluide frigorigène (7), dans un sens de transport horizontal (x),
    - la zone de refroidissement présentant un dispositif de commande (11),
    - le dispositif de commande (11) étant conçu de telle sorte qu'il détermine, en fonction d'un flux de consigne (F*) respectif de fluide frigorigène (7) à appliquer au moyen du dispositif d'application (6) respectif sur le produit laminé (1) chaud, de manière dynamique un état de commande de consigne (S*) respectif pour la pompe (10) respective et commandant la pompe (10) respective de manière correspondante, de telle sorte que le flux instantané (F) respectif transporté par la pompe (10) respective s'approche à tout moment autant que possible du flux de consigne (F*) respectif,
    caractérisée
    en ce que, entre la pompe (10) respective et le dispositif d'application (6) respectif,
    - soit aucune dispositif d'arrêt (13) n'est agencé
    - ou alors un dispositif d'arrêt (13) est agencé, le dispositif d'arrêt (13) étant cependant maintenu complètement ouvert en permanence par le dispositif de commande (11) pendant le transport du produit laminé (1) à travers la zone de refroidissement (2)
    - ou alors un dispositif d'arrêt (13) est agencé, le dispositif d'arrêt (13) étant cependant actionné par le dispositif de commande (11) tant en ouverture qu'en fermeture exclusivement lorsqu'une vitesse de rotation de la pompe (10) respective est inférieure à une vitesse de rotation minimale,
    en ce que la pompe (6) respective est agencée en parallèle à une conduite de retour (14) et la conduite de retour (14) présente une section transversale intérieure à celle de la conduite d'alimentation (8) respective.
  9. Zone de refroidissement selon la revendication 8,
    caractérisée
    en ce que la pompe respective (10) est commandée par le dispositif de commande (11) de telle sorte qu'elle fonctionne en mode générateur ou avec un sens de rotation inversé à chaque fois que le flux de consigne (F*) respectif passe sous une valeur limite inférieure respective.
  10. Zone de refroidissement selon la revendication 8,
    caractérisée
    en ce qu'une soupape antiretour (16) ou un clapet antiretour est agencé(e) dans la conduite d'alimentation (8) respective entre la pompe (10) respective et le dispositif d'application (6) respectif.
  11. Zone de refroidissement selon l'une des revendications 8 à 10,
    caractérisée
    en ce que des moyens pour la détection de la pression côté entrée sont présents en amont de la pompe (10) respective, en ce qu'une pression côté entrée (pE) du fluide frigorigène (7) est détectée en amont de la pompe (10) respective et en ce que le dispositif de commande (11) prend en considération la pression côté entrée (pE) détectée lors de la détermination de l'état de commande de consigne (S*) respectif de la pompe (10) respective.
  12. Zone de refroidissement selon l'une des revendications 8 à 11,
    caractérisée
    en ce que des moyens pour la détection de la pression côté sortie sont présents en aval de la pompe (10) respective, en ce qu'une pression côté sortie (pA) du fluide frigorigène (7) est détectée en aval de la pompe (10) respective et en ce que le dispositif de commande (11) prend en considération la pression côté sortie (pA) détectée lors de la détermination de l'état de commande de consigne (S*) respectif de la pompe (10) respective.
  13. Zone de refroidissement selon l'une des revendications 8 à 12,
    caractérisée
    en ce que le dispositif de commande (11) détermine le flux de consigne (F*) respectif en fonction d'un état d'énergie thermodynamique (H) respectif du produit laminé (1) qui existe juste avant d'atteindre le dispositif d'application (6) respectif.
  14. Zone de refroidissement selon la revendication 13,
    caractérisée
    - en ce que les flux instantanés (F) du fluide frigorigène (7) sont appliqués sur le produit laminé (1) chaud au moyen des dispositifs d'application (6) séquentiellement les uns après les autres et
    - en ce que le dispositif de commande (11) détermine l'état d'énergie thermodynamique (H) respectif du produit laminé (1) à l'aide de l'état d'énergie thermodynamique (H) du produit laminé (1) en amont du dispositif d'application (6) immédiatement précédent tout en prenant en considération en plus le flux de consigne (F*) du fluide frigorigène (7) ou le flux instantané (F) du fluide frigorigène (7) qui est appliqué ou qui doit être appliqué au moyen du dispositif d'application (6) immédiatement précédent sur le produit laminé (1) chaud.
EP19740415.5A 2018-07-25 2019-07-23 Section de refroidissement à réglage de flux de liquide de refroidissement à l'aide de pompes Active EP3826780B2 (fr)

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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
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

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CN112469516B (zh) 2023-04-11
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WO2020020868A1 (fr) 2020-01-30
CN112469516A (zh) 2021-03-09
EP3826780B1 (fr) 2023-01-25
US11167332B2 (en) 2021-11-09

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