EP3347151B1 - Sekundärkühlung eines strangs in einer stranggiessanlage - Google Patents

Sekundärkühlung eines strangs in einer stranggiessanlage Download PDF

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Publication number
EP3347151B1
EP3347151B1 EP16757916.8A EP16757916A EP3347151B1 EP 3347151 B1 EP3347151 B1 EP 3347151B1 EP 16757916 A EP16757916 A EP 16757916A EP 3347151 B1 EP3347151 B1 EP 3347151B1
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EP
European Patent Office
Prior art keywords
coolant
individual
stream
strand
pulse
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
EP16757916.8A
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German (de)
English (en)
French (fr)
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EP3347151A1 (de
Inventor
Christian ENZINGER
Thomas Fuernhammer
Thomas Stepanek
Helmut Wahl
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Primetals Technologies Austria GmbH
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Primetals Technologies Austria GmbH
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Application filed by Primetals Technologies Austria GmbH filed Critical Primetals Technologies Austria GmbH
Priority to EP18179585.7A priority Critical patent/EP3417959B1/de
Priority claimed from PCT/EP2016/070441 external-priority patent/WO2017042059A1/de
Publication of EP3347151A1 publication Critical patent/EP3347151A1/de
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D11/00—Continuous casting of metals, i.e. casting in indefinite lengths
    • B22D11/16—Controlling or regulating processes or operations
    • B22D11/22—Controlling or regulating processes or operations for cooling cast stock or mould
    • B22D11/225—Controlling or regulating processes or operations for cooling cast stock or mould for secondary cooling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/02—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to produce a jet, spray, or other discharge of particular shape or nature, e.g. in single drops, or having an outlet of particular shape
    • B05B1/08—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to produce a jet, spray, or other discharge of particular shape or nature, e.g. in single drops, or having an outlet of particular shape of pulsating nature, e.g. delivering liquid in successive separate quantities ; Fluidic oscillators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D11/00—Continuous casting of metals, i.e. casting in indefinite lengths
    • B22D11/12—Accessories for subsequent treating or working cast stock in situ
    • B22D11/124—Accessories for subsequent treating or working cast stock in situ for cooling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D11/00—Continuous casting of metals, i.e. casting in indefinite lengths
    • B22D11/12—Accessories for subsequent treating or working cast stock in situ
    • B22D11/124—Accessories for subsequent treating or working cast stock in situ for cooling
    • B22D11/1246—Nozzles; Spray heads

Definitions

  • the invention relates to a cooling device and a cooling method for secondary cooling of a strand in a strand guide of a continuous casting plant.
  • a metallic strand is formed in a mold and then guided in a strand guide and cooled further in the process.
  • the cooling of the strand in the strand guide is called secondary cooling, while cooling of the strand in the mold is called primary cooling.
  • secondary cooling a coolant, for example water or a water-air mixture, is usually applied to the strand by means of a cooling device.
  • a secondary cooling device and a cooling method for secondary cooling of a strand in a continuous casting plant are known, in which the cooling power is set by PWM control of the duty cycle of a switching valve. How the ratio between the maximum and the minimum individual coolant flow is increased and, in addition, the formation of a suitable jet profile (in particular the opening angle of the coolant jet from the coolant outlet) can be achieved even with small individual coolant flows, does not emerge from the document.
  • the invention is based on the object of specifying an improved cooling device and an improved cooling method for secondary cooling of a strand in a continuous casting plant.
  • the ratio between the maximum amount of coolant that can be applied and the minimum amount of coolant that can be applied should be increased.
  • the cooling device thus makes it possible to cool a strand produced in a continuous caster by means of pulse-width modulated individual coolant flows which are output from coolant outlets distributed over a strand guide.
  • the pulse width modulation is implemented in a current range for a time average value of an individual coolant flow.
  • the individual coolant flow disappears during part of each clock period of the pulse width modulation and assumes a constant, non-zero current pulse value during the other part of each clock period. This current pulse value is therefore greater than the average value over time of the pulse-width-modulated individual coolant flow.
  • the time average value to be set is so small that an unpulsed, ie. H. Temporally constant individual coolant flow, which would generate this mean value, cannot realize a planned jet profile of a coolant jet generated by the individual coolant flow due to a coolant pressure that is too low.
  • the jet profile in particular an opening angle of the coolant jet, is namely essential for the size of the area of the strand wetted by the coolant jet and thus for the cooling effect of the coolant jet.
  • the coolant outlets are preferably formed by corresponding outlet nozzles. The size of the individual coolant flow corresponds to a coolant pressure which, if the individual coolant flow is too small, is not sufficient to generate the intended jet profile.
  • Pulse width modulation of a single coolant flow is therefore preferably carried out in a flow range that is limited by a threshold flow at which the coolant pressure would no longer be sufficient to realize a jet profile of a coolant jet generated by the single coolant flow when the switching valve is fully open.
  • mean values of the individual coolant flow that are smaller than the threshold current can be realized with current pulse values that are greater than the threshold current.
  • individual coolant flows can be realized whose mean values over time are smaller than the threshold current and which nevertheless generate a planned jet profile of the coolant jet, since the current pulse values are greater than the threshold current.
  • coolant jets of an intended jet profile can therefore cover a larger one Current value interval can be realized than with an exclusive use of unpulsed individual coolant flows, ie the cooling device can be operated in a larger operating window which is defined by this current value interval.
  • unpulsed individual coolant flows can be generated by regulating a coolant pressure or coolant flow in the coolant distribution system with the control loop.
  • the invention also enables the operating window of already existing conventional cooling devices to be extended in a relatively simple and inexpensive manner, i. H. to redesign these cooling devices in such a way that coolant jets of an intended jet profile can be realized over a larger current value interval of the individual coolant flows. All that is needed is switching valves and a control unit connected to the switching valves for pulse-width modulated switching on and off of individual coolant flows, for example by replacing existing conventional line segments with line segments with switching valves and connecting the switching valves to the control unit via control lines (which are inexpensive compared to coolant lines). without laboriously changing or replacing the coolant distribution system as a whole. Such a redesign can also advantageously take place step by step, so that the operation of the continuous casting plant only has to be interrupted for relatively short conversion times.
  • Pneumatically or electrically or electromagnetically or hydraulically switchable valves are suitable as switching valves. Switching valves designed in this way are advantageously commercially available and enable a cost-effective implementation of individual coolant flows that can be switched on and off.
  • the coolant outlets are preferably each formed by an outlet nozzle.
  • at least one outlet nozzle has an exchangeable nozzle tip.
  • outlet nozzles By means of coolant outlets formed by outlet nozzles, particularly suitable jet profiles of the coolant jets emitted by the coolant outlets can advantageously be generated for strand cooling.
  • Outlet nozzles with exchangeable nozzle tips advantageously make it possible to change these jet profiles in a simple manner, if necessary, by exchanging the nozzle tips.
  • Switching valves with which exactly one individual coolant flow can be switched on and off, can be switched faster than switching valves of the same type for several individual coolant flows and thus enable a higher clock frequency of the pulse width modulation of the individual coolant flows. Furthermore, through individual control of the switching valves, they enable more flexible control of the cooling and reduce the effects of a failure of an individual switching valve. Switching valves for a plurality of individual coolant flows, on the other hand, advantageously reduce the number of switching valves required and thus the costs and effort for realizing the cooling device compared to switching valves for one individual coolant flow in each case. It therefore depends on the respective requirements of the cooling device whether switching valves are more advantageous for one individual coolant flow or several individual coolant flows.
  • Another embodiment of the invention provides a pressure detection device for detecting a coolant pressure or a flow meter for detecting a coolant flow in the coolant distribution system.
  • Such a pressure detection device advantageously enables an analysis and checking of functions of the cooling device, for example the determination of a degree of blockage of coolant outlets, by evaluating the signals detected by the pressure detection device.
  • an actual value of a coolant pressure or coolant flow for regulating the coolant pressure or coolant flow in the coolant distribution system can be recorded.
  • a threshold current Q s for mean values over time are used Q predetermined by at least one individual coolant flow and a flow range ⁇ Q lying below the threshold flow or equal to the threshold flow.
  • ⁇ Q [0, Q S ] applies.
  • Temporal mean values of Individual coolant flows with 0 ⁇ Q ⁇ Q S are generated in that a coolant pressure in the coolant distribution system is set to a constant pressure value and each individual coolant flow is pulse-width-modulated by a pulse-width-modulated control of a switching valve with a duty cycle that is dependent on the mean value to be generated.
  • Temporal mean values of individual coolant flows outside the flow range with Q > Q S are generated by opening the switching valves of these individual coolant flows and regulating the coolant pressure or a coolant flow in the coolant distribution system with the control loop to a setpoint dependent on the individual coolant flows to be generated.
  • One embodiment of the cooling method provides that several individual coolant flows in the flow range are pulse-width modulated for their mean values over time in such a way that a total coolant flow formed by all of these individual coolant flows is constant over time.
  • This embodiment of the invention therefore provides for a time-delayed switching on and off of individual coolant flows with their pulse width modulation in order to keep a total coolant flow formed by all these individual coolant flows constant over time.
  • a uniform total coolant flow released by the cooling device onto the strand can advantageously be generated, even if the individual coolant flows released by the individual coolant outlets are each pulse-width modulated.
  • a further embodiment of the cooling method provides that several individual coolant flows in the current range are pulse-width modulated for their mean values over time in such a way that a total coolant flow formed from all these individual coolant flows is regulated to a target value.
  • An actual value of the total coolant flow is determined and a duty cycle and a period length of a clock period of the pulse width modulation are regulated as a function of a deviation of the determined actual value from the setpoint.
  • This embodiment of the invention advantageously enables a total coolant flow output by a plurality of coolant outlets to be regulated to a predeterminable setpoint value by setting the duty cycle and the period length of the pulse width modulation of the individual coolant flows.
  • coolant pressures in line segments, via which individual coolant flows are output are recorded, for example, and the individual coolant flows output are deduced from this by means of current-pressure characteristics.
  • the actual value of the total coolant flow is then formed as the sum of these individual coolant flows, each multiplied by the respective duty cycle of the pulse width modulation.
  • Another embodiment of the cooling method provides that a selection of coolant outlets, through which individual coolant flows are output, is made as a function of a width of the strand.
  • the cooling of a strand can advantageously be adapted to its width.
  • coolant outlets which are not required to cool a strand because they are located next to the strand surface, for example only blow-out air is emitted in a pulse pause or a short water pulse in order to prevent these coolant outlets from clogging.
  • Another embodiment of the invention provides that a coolant pressure in the coolant distribution system is detected and evaluated to determine a degree of blockage of at least one coolant outlet.
  • a strand that passes through the secondary cooling at a casting speed of 0.05 m / s and is cooled by a coolant outlet at a clock frequency of 0.5 Hz and a duty cycle D of 50% moves by 0 during a single cooling cycle, 05 m further.
  • the clock frequency must also be doubled to 1 Hz so that the strand moves again by 0.05 m during a single cooling cycle.
  • the duty cycle D again occurs at different casting speeds kept constant and the coolant pressure (P) is set proportional to the square of the casting speed. This means that when the casting speed is doubled with the same clock frequency and the same duty cycle, the coolant pressure must be quadrupled in order to apply the same amount of coolant in the same cooling cycle.
  • the coolant pressure or the coolant flow in the coolant distribution system is set in such a way that a turbulent flow with Re> 2300 occurs in the coolant outlet adjusts.
  • a continuous caster according to the invention comprises a mold for forming a strand, an oscillation device for moving the mold relative to the strand, a strand guide for supporting and guiding the strand and a cooling device according to the invention for secondary cooling of the strand with the advantages already mentioned above.
  • the mold has a width adjustment for setting a width of the strand and the strand guide preferably has one G mandickenver ein to adjust a thickness of the strand.
  • the oscillation device can advantageously generate movements of the mold, in particular oscillating movements of the mold, so that the strand does not adhere to an inner surface of the mold.
  • Figure 1 shows schematically a section of a continuous caster 1 in a side view. Shown are a mold 3, an oscillation device 4 for moving the mold 3 relative to a strand 9, a strand guide 5 downstream of the mold 3 and a cooling device 7 of the continuous casting plant 1.
  • the strand guide rollers 13 above the Line 9 and the line segments 17.1 and the coolant outlets 21 below the line 9 are not shown. It is known to the person skilled in the art that after exiting a mold in the secondary cooling, a strand is typically guided by strand guide rollers above and below the strand and the broad sides of the strand lying above and below are cooled.
  • a metallic melt is fed to the mold 3, from which the metallic strand 9 is formed with the mold 3, which is guided with the strand guide 5 and transported along a transport direction 11.
  • movements of the mold 4, in particular oscillating movements (the direction of movement is shown by an arrow) of the mold 4 are generated, so that the strand 9 does not adhere to an inner surface of the mold.
  • the strand guide 5 has several strand guide rollers 13 to support the strand 9.
  • the mold 3 has a width adjustment for setting a width of the strand 9, so that strands 9 of different widths can be produced with the mold 3.
  • the strand guide 5 has a casting thickness adjustment for setting a thickness of the strand 9, so that strands 9 of different thicknesses can be produced with the strand guide 5.
  • the cooling device 7 is used for secondary cooling of the strand 9 in the strand guide 5.
  • the cooling device 7 comprises a coolant distribution system 15 with line segments 17.1 to 17.4 for conveying a coolant 19 and several coolant outlets 21 distributed over the strand guide 5 for outputting coolant 19 onto the strand 9.
  • the coolant 19 is, for example, water.
  • the continuous casting installation 1 shown is designed for what is known as horizontal continuous casting, in which the strand 9 is output horizontally from the mold 3 to the strand guide 5.
  • the invention in particular a cooling device 7 according to the invention, is not limited to continuous casting plants 1 for horizontal continuous casting, but in particular also relates to continuous casting plants 1 which are designed for so-called vertical continuous casting, in which the strand 9 emerges vertically through a bottom opening of the mold 3 Mold 3 is issued to the strand guide 5 and the strand guide 5 is designed to be curved, so that the strand 9 is brought along the strand guide 5 from a horizontal to a vertical position.
  • FIG. 2 shows schematically a first embodiment of a cooling device 7 for secondary cooling of a strand 9 in a continuous casting plant 1 in a perspective view. Only a section of the strand 9 is shown, which is located in the area of the cooling device 7. Furthermore, of this section of the strand 9 and of the coolant distribution system 15 of the cooling device 7, only one area is shown, which extends over half a width of the strand 9 from a lateral strand edge 9.1 of the strand 9 to a central axis 9.2 running parallel to the transport direction 11 of the strand 9 extends.
  • the coolant outlets 21 of the coolant distribution system 15 form several longitudinal rows of coolant outlets 21 arranged one behind the other along the transport direction 11 of the strand 9.
  • the longitudinal rows are arranged next to one another transversely to the transport direction 11 of the strand 9, so that coolant outlets 21 of different longitudinal rows are arranged side by side across the transport direction 11 Form coolant outlets 21.
  • the coolant distribution system 15 has eight longitudinal rows of coolant outlets 21 arranged next to one another, each longitudinal row having four coolant outlets 21.
  • Alternative exemplary embodiments have one of eight different numbers of longitudinal rows of coolant outlets 21 arranged next to one another and / or at least one longitudinal row with one of four different numbers of coolant outlets 21.
  • Each coolant outlet 21 forms an end of a line end segment 17.1 facing the strand 9 and running perpendicular to the strand surface 9.3.
  • the coolant distribution system 15 has a line longitudinal segment 17.2 running parallel to the transport direction 11, which connects the line end segments 17.1 having these coolant outlets 21 to one another.
  • the coolant distribution system 15 also has a transverse line segment 17.4 running transversely to the transport direction 11, which is connected to each longitudinal line segment 17.2 via an intermediate line segment 17.3 running perpendicular to the strand surface 9.3.
  • Each line end segment 17.1 also has an outlet nozzle 33 with the coolant outlet 21 for outputting coolant 19, see in this regard Figure 3 .
  • a switching valve 23 is arranged in each line end segment 17.1, with which a coolant supply of coolant 19 to the coolant outlet 21 of this line end segment 17.1 can be interrupted.
  • Each switching valve 23 is designed as an on / off valve that has two operating states, the switching valve 23 releasing the coolant supply to the coolant outlet 21 in a first operating state and blocking the coolant supply to the coolant outlet 21 in the second operating state.
  • a change in the operating state of a switching valve 23 is referred to here as switching the switching valve 23; Switching from the first to the second operating state is referred to as closing the switching valve 23 and switching from the second to the first operating state is referred to as opening the switching valve 23.
  • Precisely one individual coolant flow Q, which is output from a coolant outlet 21, can therefore be switched on and off by each switching valve 23.
  • the switching valves 23 are connected to a control unit 27 via control lines 25.1 to 25.4 and can be switched by the control unit 27.
  • Each control line 25.1 to 25.4 connects the switching valves 23 of a longitudinal row of coolant outlets 21 with the control unit 27.
  • the control lines 25.1 to 25.4 can run at least in sections in pipes of line segments 17.1 to 17.4, see the description of FIG Figure 3 below.
  • the switching valves 23 are designed as pneumatically or electrically or electromagnetically or hydraulically switchable valves. Accordingly, the control lines 25.1 to 25.4 in the case of pneumatically switchable switching valves 23 are pneumatic compressed air lines, in the case of electrically or electromagnetically switchable switching valves 23 are electrical lines and in the case of hydraulically switchable switching valves 23 are hydraulic fluid lines.
  • the control unit 27 is designed to switch the switching valves 23 in a manner described below.
  • the cooling device 7 further comprises a pressure detection device 29 for detecting the coolant pressure P in the coolant distribution system 15.
  • the signals detected by the pressure detection device 29 are fed to the control unit 27 via a pressure signal line 31.
  • the control unit 27 evaluates these signals to analyze and check functions of the cooling device 7, for example to determine a degree of blockage of the coolant outlets 21.
  • Figure 3 shows a perspective view of a line end segment 17.1.
  • the line end segment 17.1 comprises a segment tube 35, a connecting flange 37, a switching valve 23 and an outlet nozzle 33.
  • the connecting flange 37 is arranged at a first end of the segment tube 35 and can be connected to a line longitudinal segment 17.2.
  • the switching valve 23 is arranged, which is attached to this end of the segment tube 35, for example by a pipe-valve screw connection 39, which is formed by an external thread on the outer surface of the segment tube 35 and a corresponding internal thread of the switching valve 23, can be screwed on.
  • the outlet nozzle 33 has a nozzle tip 33.1 with a coolant outlet 21 and a nozzle base body 33.2.
  • the nozzle body 33.2 is arranged on the switching valve 23 and can be screwed onto the switching valve 23, for example by a valve-nozzle screw connection 41, which is formed by an external thread on the outer surface of the switching valve 23 and a corresponding internal thread of the nozzle body 33.2.
  • the nozzle tip 33.1 is arranged on the nozzle base body 33.2.
  • the nozzle body 33.2 has an internal thread which corresponds to an external thread of the nozzle tip 33.1, so that the nozzle tip 33.1 can be detachably connected to the nozzle body 33.2.
  • a jet profile of a coolant jet emitted by the outlet nozzle 33 can advantageously be changed by changing the nozzle tip 33.1.
  • the segment tube 35 is used to guide coolant 19 to the coolant outlet 21 and to guide an end section of a control line 25.1 to 25.4 to the switching valve 23.
  • the segment tube 35 has, for example, an outer tube and an inner tube running in the outer tube, with between the outer tube and the inner tube coolant 19 is guided and the inner tube forms or surrounds the end section of a control line 25.1 to 25.4.
  • the connecting flange 37 has two flange openings 37.1, 37.2, a first flange opening 37.1 serving to supply coolant 19 into the segment tube 35 and the second flange opening 37.2 for guiding the control line 25.1 to 25.4 in the segment tube 35 is used.
  • the connecting flange 37 also has a centering bolt 42 arranged between the flange openings 37.1, 37.2 in order to be able to assemble and align the line end segment 17.1 more easily.
  • FIG 4 shows schematically a second embodiment of a cooling device 7 for secondary cooling of a strand 9 in a continuous casting plant 1 in a to Figure 2 analog perspective representation.
  • This in Figure 4 The illustrated embodiment differs from that in the Figures 2 and 3 illustrated embodiment in that a switching valve 23 for a coolant outlet 21 is not arranged in each of the line end segments 17.1, but that for each longitudinal row of coolant outlets 21 only one switching valve 23 connected to the control unit 27 via a control line 25.1 to 25.4 is arranged in an intermediate line segment 17.3 is, so that a coolant supply from the line cross segment 17.4 to a line longitudinal segment 17.2 and all the line end segments 17.1 connected to it can be interrupted by each of these switching valves 23.
  • a check valve 43 is arranged in order, after a coolant supply to the line end segment 17.1 has been blocked by the corresponding switching valve 23, an output of coolant 19, which is located in line segments 17.1 to 17.3 between the switching valve 23 and check valve 43, to the Strand 9 to prevent.
  • the cooling device 7 of the in Figure 4 illustrated embodiment analogous to that in the Figures 2 and 3 illustrated embodiment formed.
  • the switching valves 23 are like the switching valves 23 in the Figures 2 and 3 illustrated embodiment as on / off valves formed, which can be switched by the control unit 27 in a manner described in more detail below.
  • the line end segments 17.1 in turn each have an outlet nozzle 33, the nozzle tip 33.1 of which is preferably designed to be exchangeable.
  • the illustrated embodiment requires that in Figure 4
  • the illustrated embodiment advantageously has fewer switching valves 23.
  • a higher clock frequency of the pulse-width-modulated switching of the switching valves 23 (when using similar switching valves 23 in both embodiments) enables a more flexible control of the cooling with an individual control of the switching valves 23 and reduces the effects of a failure of an individual switching valve 23, since a such failure affects a smaller surface area of the strand 9.
  • FIGS Figures 5 to 7 illustrate a cooling method for secondary cooling of a strand 9 in a continuous casting installation 1 with a cooling device 7, which is like one of the in FIGS Figures 2 to 4 illustrated embodiments is formed.
  • FIG. 11 shows a diagram for a coolant pressure P as a function of a single coolant flow Q through an outlet nozzle 33 of the cooling device 7, which, like one of the in FIGS Figures 2 and 4th illustrated embodiments is formed.
  • the individual coolant flow Q emitted from the outlet nozzle 33 through the coolant outlet 21 is in at least one flow range ⁇ Q for its mean value over time Q switched on and off by a pulse-width-modulated control of a switching valve 23 and thus itself pulse-width-modulated, see Figure 6 .
  • this Current range ⁇ Q limited by a threshold current Q S , which corresponds to a threshold pressure P S.
  • a maximum pressure P M and a corresponding maximum flow Q M for which the outlet nozzle 33 is designed, are also shown.
  • the threshold flow Q S is specified in such a way that the coolant pressure P below the corresponding threshold pressure P S is no longer sufficient to achieve an intended jet profile of a coolant jet emitted by the outlet nozzle 33, in particular an intended opening angle of the coolant jet, to achieve a sufficiently large area to cover the strand surface 9.3 with the coolant jet.
  • the individual coolant flows Q are output in the usual way, ie without pulse width modulation.
  • the switching valves 23 of the individual coolant flows Q to be generated are opened and the coolant pressure P or a coolant flow in the coolant distribution system 15 is regulated by means of a control circuit 45 to a setpoint dependent on the individual coolant flows Q to be generated, see Figure 9 .
  • Figure 6 shows a profile of a pulse-width-modulated individual coolant flow Q of an outlet nozzle 33 as a function of a time t.
  • the pulse width modulation has a clock period of the period length T or a clock frequency 1 / T.
  • the individual coolant flow Q has a constant, non-zero current pulse value Q P in a first half of each clock period and disappears in the second half of each clock period.
  • the time average is accordingly Q of the individual coolant flow Q in this example is half as large as the current pulse value Q P.
  • the pulse width modulation allows mean values with a current pulse value Q P that is greater than the threshold current Q S Q a single coolant flow Q can be realized, which is smaller than the threshold current Q S.
  • individual coolant flows Q can be realized, their mean values over time Q are smaller than the threshold flow Q S and which nevertheless generate an intended jet profile of a coolant jet emitted by the outlet nozzle 33.
  • Figure 7 shows diagrammatically temporal progressions of coolant flows Q 1 to Q 4 and a total coolant flow Q G , which are output by a cooling device 7 for secondary cooling of a strand 9 in a continuous casting plant 1 as a result of a pulse-width-modulated switching of the switching valves 23.
  • the cooling device 7 is like one of the in the Figures 2 or 4th illustrated embodiments formed, wherein Figure 7 to simplify the representation of a cooling device 7 with only four longitudinal rows of coolant outlets 21 instead of as in the exemplary embodiments of FIG Figures 2 and 4th eight longitudinal rows refers to ( Figure 7 can also show temporal progressions of coolant flows Q 1 to Q 4 and a total coolant flow Q G in the Figures 2 or 4th represent the halves of the respective cooling devices 7 shown, the other halves (not shown) being controlled analogously).
  • the coolant flows Q 1 to Q 4 are each output from all coolant outlets 21 of a longitudinal row together and are therefore each a sum of the individual coolant flows Q of the coolant outlets 21 of a longitudinal row, the individual coolant flows Q each being analogous to Figure 6 are pulse width modulated.
  • the total coolant flow Q G is output from the coolant outlets 21 of all these longitudinal rows together and is the sum of the coolant flows Q 1 to Q 4 .
  • the switching valves 23 are switched by the control unit 27 in a pulse-width-modulated manner with a clock period of the period length T or with a clock frequency 1 / T.
  • the switching valves 23 for the various longitudinal rows of Coolant outlets 21 are switched with a time offset to one another, so that the total coolant flow Q G is constant over time.
  • the switching valves 23 are switched in such a way that a first coolant flow Q 1 disappears during a second half of each cycle period, a second coolant flow Q 2 disappears during a first and last quarter of each cycle period, and a third coolant flow Q 3 disappears during the first half of each cycle period , a fourth coolant flow Q 4 disappears during a second and third quarter of each cycle period and the coolant flows Q 1 to Q 4 in the remaining times assume a constant, non-zero value for all longitudinal rows, which is half the total coolant flow Q G is.
  • the total coolant flow Q G is regulated to a predetermined setpoint during the pulse width modulation.
  • an actual value of the total coolant flow Q G is determined and a duty cycle D and the period length T of the pulse width modulation are regulated as a function of a deviation of the determined actual value from the setpoint.
  • the duty cycle D of the pulse width modulation is understood to mean the ratio of a pulse duration during a clock period to the period length T. In the in the Figures 6 and 7th In the examples shown, the duty cycle D is for example 50% in each case.
  • coolant pressures P in line segments 17.1 to 17.4, via which individual coolant flows Q are output are recorded and the individual coolant flows Q output in each case are deduced from this by means of current-pressure characteristics.
  • the actual value of the total coolant flow Q G is then formed as the sum of these individual coolant flows Q, each multiplied by the respective duty cycle D of the pulse width modulation.
  • Figure 8 shows the duty cycle D of the pulse width modulation of an individual coolant flow Q as a function of the mean value Q of the individual coolant flow Q in the flow range ⁇ Q.
  • the duty cycle end value D m assumes the value 1, for example. If the coolant pressure P in the coolant distribution system 15 is set to a higher pressure value, the duty cycle end value D m is correspondingly smaller.
  • a selection of coolant outlets 21, through which individual coolant flows Q are output, is also made as a function of a width of the strand 9. Coolant outlets 21, which are not required to cool the strand 9 because they are located next to the strand surface 9.3, for example only release blow-out air in a pulse pause or a short water pulse to prevent these coolant outlets 21 from clogging.
  • Figure 9 shows a control circuit 45 for regulating a coolant pressure P or coolant flow in the coolant distribution system 15 in order to generate individual coolant flows Q which are greater than the threshold flow Q S.
  • the controlled variable R of the control loop 45 is therefore the coolant pressure P or coolant flow in the coolant distribution system 15.
  • a reference variable S of the control loop 45 is accordingly a setpoint value of the coolant pressure P or coolant flow in the which depends on the individual coolant flows Q Coolant distribution system 15.
  • the control circuit 45 comprises a controller 47, a controlled system 49 and a measuring element 51.
  • the controller 47 is a pump for the direct generation of a coolant pressure P or coolant flow in the coolant distribution system 15, or a pump with a downstream pressure or flow controller for Reduction of a coolant pressure P or coolant flow generated by the pump in the coolant distribution system 15.
  • the controlled system 49 is the coolant distribution system 15.
  • the measuring element 51 is a pressure detection device 29 for detecting the coolant pressure P or a flow detection device for detecting a coolant flow in the coolant distribution system 15
  • Controlled variable R, a system deviation E of the controlled variable R from the reference variable S is formed.
  • the controller 47 generates a manipulated variable U that is dependent on the control deviation E in order to reduce the control deviation B.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Continuous Casting (AREA)
EP16757916.8A 2015-09-07 2016-08-31 Sekundärkühlung eines strangs in einer stranggiessanlage Active EP3347151B1 (de)

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AT507672015 2015-09-07
ATA50985/2015A AT517772B1 (de) 2015-09-07 2015-11-19 Sekundärkühlung eines Strangs in einer Stranggießanlage
PCT/EP2016/070441 WO2017042059A1 (de) 2015-09-07 2016-08-31 Sekundärkühlung eines strangs in einer stranggiessanlage

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AT520006B1 (de) 2017-06-07 2021-08-15 Primetals Technologies Austria GmbH Kühlmitteldüse zum kühlen eines metallischen strangs in einer stranggussanlage

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AT409940B (de) * 2001-02-20 2002-12-27 Voest Alpine Ind Anlagen Zweistoff-schaftdüse und stranggiessanlage mit einer anordnung von zweistoff-schaftdüsen
AT503526B1 (de) * 2006-04-25 2008-07-15 Voest Alpine Ind Anlagen Spritzdüsen-verstelleinrichtung
EP2583772B1 (de) * 2010-05-19 2015-10-21 SMS group GmbH Strangführungsvorrichtung
EP2527061A1 (de) * 2011-05-27 2012-11-28 Siemens VAI Metals Technologies GmbH Verfahren zur Kühlung eines metallischen Strangs und Schaltventil zum intermittierenden Öffnen und Schließen eines Volumenstroms eines Kühlmediums
DE202011110064U1 (de) * 2011-06-07 2012-11-16 Sms Siemag Ag Düsenvorrichtung und Strangführungsvorrichtung mit der Düsenvorrichtung

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EP3417959B1 (de) 2021-05-26
AT517772A1 (de) 2017-04-15
BR112018004427A2 (ru) 2018-10-02
EP3347151A1 (de) 2018-07-18
EP3417959A1 (de) 2018-12-26
AT517772B1 (de) 2018-12-15
BR112018004427B1 (pt) 2022-08-23

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