EP3395463A1 - Refroidissement d'un laminé - Google Patents

Refroidissement d'un laminé Download PDF

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Publication number
EP3395463A1
EP3395463A1 EP17168241.2A EP17168241A EP3395463A1 EP 3395463 A1 EP3395463 A1 EP 3395463A1 EP 17168241 A EP17168241 A EP 17168241A EP 3395463 A1 EP3395463 A1 EP 3395463A1
Authority
EP
European Patent Office
Prior art keywords
cooling
coolant
transport direction
rolling stock
full
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.)
Granted
Application number
EP17168241.2A
Other languages
German (de)
English (en)
Other versions
EP3395463B1 (fr
Inventor
Erich Opitz
Lukas PICHLER
Alois Seilinger
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 Austria GmbH
Original Assignee
Primetals Technologies Austria 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 Austria GmbH filed Critical Primetals Technologies Austria GmbH
Priority to EP17168241.2A priority Critical patent/EP3395463B1/fr
Priority to US16/607,399 priority patent/US11358195B2/en
Priority to EP18719050.9A priority patent/EP3615237A2/fr
Priority to CN201880027555.1A priority patent/CN110536761B/zh
Priority to JP2019555876A priority patent/JP6946458B2/ja
Priority to PCT/EP2018/056437 priority patent/WO2018197100A2/fr
Publication of EP3395463A1 publication Critical patent/EP3395463A1/fr
Publication of EP3395463B1 publication Critical patent/EP3395463B1/fr
Application granted granted Critical
Priority to US17/716,000 priority patent/US11786949B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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
    • B21B45/0233—Spray nozzles, Nozzle headers; Spray systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/06—Lubricating, cooling or heating rolls
    • B21B27/10—Lubricating, cooling or heating rolls externally
    • B21B2027/103—Lubricating, cooling or heating rolls externally cooling externally
    • 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
    • B21B37/28—Control of flatness or profile during rolling of strip, sheets or plates
    • B21B37/44—Control of flatness or profile during rolling of strip, sheets or plates using heating, lubricating or water-spray cooling of 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
    • 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 beam for cooling a moving in a direction of transport rolling stock. Furthermore, the invention relates to a cooling device with a plurality of such cooling bars and a method for operating such a cooling device.
  • the rolling stock When hot rolling of rolling stock, such as a slab, the rolling stock is formed by rolling at high temperatures.
  • a coolant usually water
  • the temperature of the rolling stock often varies transversely to the transport direction. Such temperature differences can affect the quality of the rolling stock.
  • various cooling devices and methods are known.
  • WO 2014/170139 A1 discloses a cooling device for a flat rolling stock with a plurality of spray bars, which extend transversely to a transport direction of the rolling stock.
  • the spray bars each have transversely to the transport direction seen two outer regions and arranged between the two outer regions central region, wherein in the regions via a separate, individually controllable valve means, a liquid cooling medium can be fed.
  • DE 10 2007 053 523 A1 discloses a device for influencing the temperature distribution across the width of a slab or a belt, wherein at least one cooling device is provided with nozzles for applying a coolant to the slab or to the belt.
  • the nozzles are arranged distributed over the width and / or driven so that in particular positions at which an elevated temperature can be determined, a coolant is applied.
  • WO 2006/076771 A1 discloses a hot rolling mill and a method of operation thereof wherein the shape of a rolled strip is controlled by localized cooling devices.
  • the cooling devices are arranged at intervals along work rolls in at least three lateral zones.
  • DE 199 34 557 A1 discloses a device for cooling conveyed on a conveyor line metal strips or metal sheets, in particular of hot rolled steel strips in the outlet of a rolling train, with at least one extending substantially over the width of the conveying path cooling beam for applying cooling liquid to the metal strip or sheet to be cooled.
  • EP 0 081 132 A1 discloses a cooling apparatus for uniformly cooling a thick steel plate, wherein a desired amount of water is discharged with a plurality of rod-like manifolds in the width direction of the steel plate.
  • DE 198 54 675 A1 discloses a device for cooling a metal strip, in particular a hot strip, in the outlet of a rolling train with at least two nozzles distributed over the width of the metal strip, wherein a control and regulating device one exiting from each nozzle cooling fluid flow individually in response to a detected temperature of a width portion of Metal band controls which of the respective nozzle is assigned.
  • the invention has for its object to provide a device for cooling a moving in a direction of transport rolling stock and a method for operating the device, which are improved transversely to the transport direction, in particular with respect to the compensation of temperature differences of the rolling stock.
  • the object is achieved by a chilled beam with the features of claim 1, a chilled beam with the Characteristics of claim 3, a cooling device having the features of claim 11 and a method having the features of claim 19 solved.
  • a cooling beam formed according to a first embodiment of the invention for cooling a rolling stock moved in a transport direction comprises a spray chamber with a plurality of full jet nozzles and a distribution chamber for temporarily storing a coolant.
  • the distribution chamber is connected to the spray chamber through at least one passage opening for filling the spray chamber with coolant from the distribution chamber.
  • each passage opening between the distribution chamber and the spray chamber is arranged at an upper side of the distribution chamber.
  • a cooling beam designed in accordance with a second embodiment of the invention for cooling a rolling stock that is to be filled in a transport direction comprises a spray chamber which can be filled with a coolant and a plurality of full jet nozzles which can be fed with coolant from the spray chamber, through which in each case a coolant jet of a coolant having a virtually constant jet diameter in an exit direction the rolling stock can be dispensed.
  • Each full-jet nozzle has a tubular nozzle body which has an open end arranged in an upper region of the cooling bar within the spray chamber for feeding coolant into the full-jet nozzle.
  • a distribution chamber may be provided, which is connected to the spray chamber through at least one passage opening for filling the spray chamber with coolant from the distribution chamber.
  • a full-jet nozzle is understood to be a nozzle through which a substantially straight coolant jet having a virtually constant jet diameter can be dispensed.
  • the use of full jet nozzles has the advantage that the distance of the cooling beam from the rolling stock due to the substantially straight coolant jets in a wide range, typically up to about 1500 mm, is not critical and therefore can be varied in this range, without negatively affecting the cooling effect influence, since the cooling effect occurs substantially only at the immediate impact points of the coolant jets.
  • full jet nozzles offer, for example, in contrast to conical or flat jet nozzles, which cause a beam widening and therefore require a higher operating pressure.
  • the ability to operate a chilled beam according to the invention at relatively low coolant pressure which has an advantageous effect on the energy consumption and the choice of less expensive peripheral devices such as pumps.
  • a cooling bar according to the invention is fed in a high-pressure operation with a coolant pressure of up to 10 bar, whereby a pressure which is less than 1 bar below this coolant pressure is still reached at a single jet nozzle.
  • a cooling bar according to the invention can also be used in a laminar mode (low-pressure operation) at a coolant pressure of, for example, about 1 bar.
  • full jet nozzles are much less sensitive to mechanical impacts due to their compact and stable construction compared to the conical or flat jet nozzles, which is advantageous, for example, in the case of a strip breakage of the rolling stock with a beating strip end.
  • both embodiments advantageously allow that when the cooling of the rolling stock is interrupted after the interruption of the coolant supply to the cooling beam, a relatively small amount of coolant from the cooling beam travels and is discharged onto the rolling stock, while a large amount of coolant in the Chilled beam remains.
  • the cooling bar can also be filled with coolant more quickly than in the case of a resumption of the cooling due to the lower volume to be filled Case that the chilled beam is completely emptied when the cooling is interrupted.
  • this is achieved by the intermediate storage of coolant in the distribution chamber, whereby, with a suitable arrangement of the at least one passage opening between the spray chamber and the distribution chamber, in particular in an arrangement at an upper side of the distribution chamber, the distribution chamber at an interruption of the coolant supply completely or at least partially filled with coolant remains.
  • this is achieved in that the nozzle bodies of the full-jet nozzles extend within the spray chamber into an upper region of the cooling beam, so that in an interruption of the coolant supply coolant only from the lying above the open ends of the nozzle body portion of the spray chamber and can run after the nozzle bodies themselves, while the remaining volume of the spray chamber remains filled with coolant.
  • the embodiment of a cooling bar with a distribution chamber also advantageously makes it possible, by a suitable arrangement of the at least one passage opening to the spray chamber, in particular by an arrangement on an upper side of the distribution chamber, to reduce pressure gradients and flow turbulences in the spray chamber, so that all full jet nozzles of a cooling beam substantially be subjected to the same pressure and a substantially laminar flow is achieved in the spray chamber.
  • An embodiment of both embodiments of a cooling bar provides that a nozzle density and / or an outlet diameter of the full-jet nozzles varies transversely to the transport direction.
  • Under the nozzle density is understood here a number of nozzles per area.
  • a further embodiment of both embodiments of a cooling beam provides that the full-jet nozzles are arranged in at least one nozzle row extending transversely to the transport direction.
  • a further embodiment of this embodiment of a cooling bar provides that the full-jet nozzles are arranged in a plurality of rows of nozzles extending transversely to the transport direction, and that the full-jet nozzles of different rows of nozzles are arranged offset from one another in the transport direction. This is understood to mean an arrangement of the full-jet nozzles of different nozzle rows, in which the full-jet nozzles of different rows of nozzles are not arranged one behind the other along the transport direction and therefore do not form nozzle rows extending in the transport direction.
  • a nozzle spacing of adjacent full jet nozzles of each nozzle row may vary.
  • temperature differences of the temperature of the rolling stock, which vary transversely to the transport direction, can advantageously be reduced particularly well.
  • the nozzle pitch may be lowest in a central area of the discharge side of the cooling bar and increase toward the edge areas, respectively.
  • Such a distribution of the full-jet nozzles can advantageously be used for cooling a rolling stock whose temperature is highest in a central region and decreases towards the edge regions.
  • a further embodiment of both embodiments of a cooling bar provides at least onedeffenableitvoriques for the discharge of coolant before, in a Rand Scheme the spray chamber arranged full jet nozzles is issued.
  • edge masking it can be advantageously prevented that too much coolant reaches an edge region of the rolling stock and the edge region is thereby excessively cooled.
  • at least two of the cooling bars have different nozzle densities and / or outlet diameters of their jet nozzles, which are different from each other transversely to the transport direction.
  • Such a cooling device makes it possible to reduce temperature differences of the temperature of the rolling stock transversely to the transport direction by a targeted use of the cooling bars arranged one behind the other. Namely, since the cooling device has cooling bars having nozzle densities and / or outlet diameters differing from one another transversely to the transport direction, different cooling effects which can be adapted to the temperature distribution of the temperature of the rolling stock can be achieved by the interaction of these cooling bars and, if necessary, by activation and deactivation of these individual cooling bars to reduce temperature differences across the transport direction.
  • An embodiment of the cooling device provides that the nozzle densities of two of the cooling bars nozzle density maxima, which are arranged transversely to the transport direction on mutually different sides of the cooling bars, and / or that the outlet diameter of the full jet nozzles two of the chilled beam outlet diameter maxima, transverse to the transport direction are arranged on mutually different sides of the cooling bars.
  • the cooling device may have at least one cooling beam, in which the nozzle density and / or the outlet diameter of the full jet nozzles in a central region of the cooling beam is maximum and decreases transversely to the transport direction to the edge regions of the cooling beam, and / or at least one cooling bar, in which the nozzle density and / or the outlet diameter of the full-jet nozzles in a central region of the cooling beam is minimal and increases transversely to the transport direction towards the edge regions of the cooling beam.
  • This can be compensated advantageous temperature differences between a central region and the edge regions of the rolling stock.
  • a further embodiment of the cooling device according to the invention provides a temperature measuring device for determining a temperature distribution of a temperature of the rolling stock transversely to the transport direction. This advantageously makes it possible to control the cooling bars as a function of the determined temperature distribution and thus to cool the rolling stock, which takes into account the respective temperature distribution.
  • a further embodiment of the cooling device provides a control device for the automatic control of the flow rates of coolant to the individual cooling bars in dependence on a temperature distribution of the temperature of the rolling stock transversely to the transport direction.
  • the temperature distribution can be detected by a temperature measuring device as in the aforementioned embodiment of the invention, or the temperature distribution can be determined from a model of the rolling stock and / or empirical data.
  • the control device has, for example, control valves, by means of which flow rates of coolant to the individual cooling bars can be controlled independently of one another.
  • the cooling effects of the individual cooling bars can advantageously be controlled independently of each other, so that the cooling effect of the entire cooling device can be adapted flexibly to the temperature distribution of the temperature of the rolling stock transversely to the transport direction.
  • a further embodiment of the cooling device according to the invention provides that at least one cooling beam is arranged above the rolling stock and at least one cooling beam is arranged below the rolling stock.
  • the rolling stock can advantageously be cooled simultaneously both on the upper side and on the lower side, thereby enabling an even more effective and uniform cooling of the rolling stock.
  • a further embodiment of the cooling device according to the invention provides that at least one cooling beam, in particular at least one cooling beam arranged above the rolling stock, is designed according to one of the abovementioned embodiments of a cooling beam.
  • the advantages of this embodiment of the cooling device result from the abovementioned advantages of these embodiments of a cooling beam.
  • a temperature distribution of a temperature of the rolling stock transverse to the transport direction is determined and flow rates of coolant to the individual cooling bars are controlled as a function of the determined temperature distribution.
  • FIGS. 1 to 3 schematically show a first embodiment of a cooling bar 1 for cooling a moving in a direction of transport 3 rolling stock 5 (see FIG. 12 ).
  • FIG. 1 a perspective view of the cooling beam 1
  • FIG. 2 shows a sectional view of the cooling beam 1
  • FIG. 3 shows a bottom view of the chilled beam 1.
  • the transport direction 3 defines in the figures, a Y-direction of a Cartesian coordinate system with coordinates X, Y, Z, whose Z-axis is vertically upwards, ie opposite to the direction of gravity.
  • the cooling beam 1 extends transversely to the transport direction 3 in the X direction over the width of the rolling stock 5.
  • the cooling beam 1 comprises a spray chamber 7, a distribution chamber 9, a plurality of full jet nozzles 11 and two optionaldeffenableitvorraumen 12.
  • the spray chamber 7 and the distribution chamber 9 are each formed as a cavity with a transversely to the transport direction 3 in the X direction extending longitudinal axis.
  • the distribution chamber 9 has a substantially rectangular Cross-section in a plane perpendicular to its longitudinal axis.
  • the spray chamber 7 has, in a plane perpendicular to its longitudinal axis, a cross-section substantially in the form of the Greek capital letter gamma, the horizontally extending portion of the gamma extending above the distribution chamber 9.
  • the spray chamber 7 and the distribution chamber 9 are interconnected by a plurality of passage openings 13.
  • the passage openings 13 are arranged transversely to the transport direction 3 in the X direction one behind the other at an upper side of the distribution chamber 9.
  • the distributor chamber 9 can be filled from outside with a coolant, for example with cooling water, via a coolant inlet (not shown).
  • the spray chamber 7 can be filled via the passage openings 13 from the distribution chamber 9 with the coolant.
  • each full-jet nozzle 11 a coolant jet of the coolant with a nearly constant jet diameter from the spray chamber 7 can be dispensed from an output side 17 of the cooling beam 1 in an output direction 15 to the rolling stock 5.
  • the dispensing direction 15 in this case is the direction of gravity, ie opposite to the Z direction.
  • the discharge side 17 is in this case the underside of the cooling beam 1.
  • Each full-jet nozzle 11 has a tubular nozzle body 19 with a vertical, ie parallel to the Z-axis extending longitudinal axis.
  • the nozzle body 19 extends within the spray chamber 7 from a bottom of the spray chamber 7 to an open end 21 of the nozzle body 19, which is disposed in an upper region of the spray chamber 7 above the height of the top of the distribution chamber 9 and by the coolant from the spray chamber 7 in the full-jet nozzle 11 can be fed.
  • the nozzle body 19 are, for example, designed as a hollow cylinder or taper conically from their open end 21 to the bottom of the spray chamber 7 back.
  • the full-jet nozzles 11 each have an outlet opening 22 whose outlet diameter D is, for example, between 3 mm and 20 mm, preferably up to 12 mm.
  • This embodiment of the cooling bar 1 advantageously has the effect that, when the cooling of the rolling stock 5 is interrupted after the coolant supply to the distribution chamber 9 has been interrupted, coolant only from the region of the spray chamber 7 above the open ends 21 of the nozzle body 19 and from the nozzle bodies 19 themselves can track the rolling stock 5, while the remaining volume of the spray chamber 7 and the distribution chamber 9 remain filled with coolant.
  • the cooling beam 1 further has a nozzle density of the full jet nozzles 11 which varies transversely to the transport direction 3, the nozzle density being maximal in a middle region of the cooling beam 1 and decreasing transversely to the transport direction 3 towards the edge regions of the cooling beam 1 (see FIG FIG. 3 ).
  • the full-jet nozzles 11 are arranged in three rows of nozzles 23 to 25 extending transversely to the transport direction 3, the full-jet nozzles 11 of different rows of nozzles 23 to 25 being offset in the transport direction 3 from one another.
  • the variation of the nozzle density transversely to the transport direction 3 is achieved by varying a nozzle spacing d of adjacent full jet nozzles 11 of each nozzle row 23 to 25, the nozzle spacing d being minimal in the middle region of the cooling beam 1 and transverse to the transport direction 3 to the edge regions of the Cooling beam 1 increases toward.
  • the nozzle pitch d increases parabolically from the central region to each edge region of the cooling beam 1.
  • temperature differences of the rolling stock 5 can advantageously be reduced if the temperature of the rolling stock 5 decreases from a middle region of the rolling stock 5 to the edge regions of the rolling stock 5.
  • the nozzle spacing d varies, for example, between 25 mm and 70 mm.
  • the optionaldeffenableitvoriquesen 12 are each disposed below an edge region of the spray chamber 7 and to designed to collect and dissipate coolant, which is output from arranged in the respective edge region of the spray chamber 7 full jet nozzles 11 (so-called edge masking), so that the coolant does not reach the corresponding edge region of the rolling stock 5 and the edge region of the rolling stock 5 cools too much.
  • eachdeffenableitvortechnisch 12 a coolant collecting container 12.1 and améffenableitrohr 12.2.
  • Thedeffenableitrohr 12.2 is disposed on an underside of the coolant collecting container 12.1 and serves to dissipate captured in the coolant collecting container 12.1 coolant.
  • FIGS. 4 to 7 each show a further embodiment of a cooling beam 1 in a bottom view of the respective chilled beam 1.
  • the chilled beam 1 of each of these embodiments differs from that in the FIGS. 1 to 3 shown chilled beam 1 only by the distribution of the full jet nozzles 11 transverse to the transport direction 3.
  • the full jet nozzles 11 are arranged in three transverse to the transport direction 3 nozzle rows 23 to 25, wherein the full jet nozzles 11 of different rows of nozzles 23 to 25 are arranged offset in the transport direction 3 against each other.
  • FIG. 4 shows a chilled beam 1, in which the nozzle spacing d of adjacent full jet nozzles 11 of each row of nozzles 23 to 25 from the central region of the cooling beam 1 transversely to the transport direction 3 to the edge regions of the cooling beam 1 towards (for example parabolic) decreases, so that the nozzle density of the jet nozzles 11 increases from the central region of the cooling beam 1 to the edge regions of the cooling beam 1.
  • temperature differences of the rolling stock 5 can advantageously be reduced if the temperature of the rolling stock 5 increases from a central region of the rolling stock 5 to the edge regions of the rolling stock 5.
  • FIG. 5 shows a chilled beam 1, in which the nozzle spacing d of adjacent full jet nozzles 11 of all rows of nozzles 23 to 25 is equal, but the rows of nozzles 23 to 25 are different from one another in FIG. 5 extend to the right edge region of the cooling bar 1 to the left, so that the nozzle density in the right edge region has a nozzle density maximum.
  • temperature differences of the rolling stock 5 can advantageously be reduced if the temperature of the rolling stock 5 decreases from the edge region of the rolling stock 5 located on the right to the region of the rolling stock 5 on the left.
  • FIG. 6 shows a chilled beam 1, in which the nozzle spacing d of adjacent full jet nozzles 11 of all rows of nozzles 23 to 25 is also the same, but the nozzle rows 23 to 25 are different from one another in FIG. 6 extend to the left on the left edge region of the cooling bar 1, so that the nozzle density in the left-hand edge region has a nozzle density maximum.
  • temperature differences of the rolling stock 5 can advantageously be reduced if the temperature of the rolling stock 5 decreases from the left-lying edge region of the rolling stock 5 to the right-lying edge region of the rolling stock 5.
  • FIG. 7 shows a chilled beam 1, in which the nozzle spacing d of adjacent full jet nozzles 11 of all rows of nozzles 23 to 25 is the same and also the nozzle density is constant transversely to the transport direction 3.
  • Such a cooling bar 1 therefore causes a uniform cooling of the rolling stock 5 transversely to the transport direction.
  • FIG. 8 shows a chilled beam 1, which differs from the in FIG. 7 Chilled beam 1 only differs in that the outlet diameter D of the full-jet nozzles 11 varies transversely to the transport direction 3.
  • the outlet diameter D in the central region of the cooling bar 1 is maximum and takes transversely to the
  • Transport direction 3 from the edge regions of the cooling beam 1 out, the decrease may be, for example, parabolic.
  • the distribution chamber 9 can be omitted in each case, wherein the spray chamber 7 is filled directly with coolant instead of via the distribution chamber 9.
  • the full-jet nozzles 11 may extend less or not at all into the spray chamber 7, ie the nozzle bodies 19 may be made shorter or completely omitted.
  • the full-jet nozzles 11 can be arranged in a number of rows of nozzles 23 to 25 deviating from three.
  • outlet diameter D of the full-jet nozzles 11 transversely to the transport direction 3 in a different manner than in the FIG. 8 shown chilled beam 1 varies.
  • the outlet diameter D in the central region of the cooling beam 1 may be minimal and increase transversely to the transport direction 3 towards the edge regions of the cooling beam 1, or the outlet diameter D may be maximum in an edge region of the cooling beam 1 and transverse to the transport direction 3 remove this edge area opposite edge area.
  • FIG. 9 schematically shows in the FIGS. 1 to 8 illustrated cooling beams output volume flows V 1 to V 5 of a coolant in dependence on a position transverse to the transport direction.
  • a first volume flow V 1 is from the in the Figures 3 and 8th shown chilled beam 1 and decreases from a central region of the cooling beam 1 to the edge regions down, the decrease, for example, parabolic.
  • a second volume flow V 2 is from the in FIG. 4 shown chilled beam 1 and increases from a central region of the cooling beam 1 to the edge regions toward, wherein the increase, for example, parabolic.
  • a third volume flow V 3 is from the in FIG. 5 Cooling bar 1 shown generates and decreases from a first edge region to the second Ran Scheme of the cooling beam 1 down.
  • a fourth volume flow V 4 is separated from the one in FIG. 6 Cooling bar 1 shown generates and decreases from the second edge region to the first Ran Scheme of the cooling beam 1 down.
  • a fifth volume flow V 5 is generated by the in FIG. 7 shown chilled beam 1 generates and is transverse to the transport direction 3 constant.
  • FIG. 10 shows a sectional view of another embodiment of a cooling bar 1.
  • the distribution chamber 9 is arranged below the spray chamber 7.
  • the spray chamber 7 and the distribution chamber 9 are interconnected by a plurality of passage openings 13 and the chilled beam 1 has a plurality of full jet nozzles 11, each having a tubular nozzle body 19 with a vertical, ie parallel to the Z-axis extending cylinder axis.
  • the nozzle body 19 extend in this embodiment, in each case from a bottom of the distribution chamber 9 through the distribution chamber 9 into the spray chamber 7, where they each have an open end 21, can be fed by the coolant from the spray chamber 7 in the full jet nozzle 11.
  • the full-jet nozzles 11 in turn have a transversely to the transport direction 3 varying nozzle density and can, for example, analogous to any of the in the FIGS. 1 to 6 be shown distributed embodiments arranged.
  • FIG. 11 shows a sectional view of another embodiment of a cooling bar 1.
  • the distribution chamber 9 is arranged below the spray chamber 7.
  • the spray chamber 7 and the distribution chamber 9 are interconnected by a plurality of passage openings 13 and the chilled beam 1 has a plurality of full jet nozzles 11.
  • the full-jet nozzles 11 are led out of the spray chamber 7 at an upper side and directed straight upwards, so that they discharge coolant upwards.
  • An in FIG. 11 shown chilled beam 1 is therefore intended to be disposed below the rolling stock 5 and spend coolant on an underside of the rolling stock 5.
  • the full-jet nozzles 11 may in turn have a nozzle density varying transversely to the transport direction 3.
  • FIG. 12 schematically shows a rolling mill 27 for hot rolling of a rolling stock 5, which is transported in a transport direction 3 by the rolling mill 27.
  • the rolling train 27 includes a finishing train 29 and a cooling section 31.
  • a plurality of rolling stands 33 are arranged one behind the other, with which the rolling stock 5 is formed.
  • two rolling stands 33 are shown by way of example; However, the finishing train 29 may also have a different number of rolling stands 33.
  • the cooling section 31 adjoins the finishing train 29 and has a cooling device 35 for cooling the rolling stock 5.
  • the cooling device 35 comprises a plurality of cooling bars 1, a temperature measuring device 37 and a control device 39.
  • Each cooling bar 1 has a plurality of full jet nozzles 11, through which a respective coolant jet of a coolant having a nearly constant jet diameter can be output to the rolling stock 5.
  • Some chilled beams 1 are arranged one behind the other above the rolling stock 5 and emit coolant jets down to an upper side of the rolling stock 5.
  • the other chilled beams 1 are arranged one behind the other below the rolling stock 5 and give coolant jets up on a Bottom of the rolling stock 5 off.
  • FIG. 12 are exemplified five above and five below the rolling stock 5 arranged chilled beam 1; However, the cooling device 35 may also have other numbers above and / or below the rolling stock 5 arranged chilled beam 1.
  • the remaining chilled beams 1 have a constant nozzle density like that in FIG FIG. 7 shown embodiment.
  • the cooling bars 1 with varying nozzle densities and / or varying outlet diameters D are preferably arranged (with respect to the transport direction 3) in front of the cooling bars 1 with constant nozzle densities.
  • the first four cooling bars 1 arranged above the rolling stock 5 and the first four cooling bars 1 arranged below the rolling stock 5 each comprise a cooling bar 1 with a nozzle density which is analogous to FIG FIG. 3 decreases from a central region of the cooling beam 1 to the edge regions of the cooling beam 1, a cooling beam 1 with a nozzle density, the analogous to FIG. 4 increases from a central region of the cooling beam 1 to the edge regions of the cooling beam 1, a cooling beam 1 with a nozzle density, the analogous to FIG. 5 from one (in FIG. 5 right) first edge region of the cooling beam 1 to the (in FIG. 5 left) second edge region of the cooling beam 1 decreases, and a chilled beam 1 with a nozzle density, analogous to FIG. 6 increases from the first edge region of the cooling beam 1 to the second edge region of the cooling beam 1.
  • the cooling bars 1 arranged above the rolling stock 5 preferably each have full-jet nozzles 11 and / or a spray chamber 7 and a distribution chamber 9 like that in FIGS FIGS. 1 and 2 Cooling bar 1 shown in order to reduce run-off of coolant from these chilled beam 1 to the rolling stock 5 in an interruption of the coolant supply to the chilled beam 1.
  • the cooling bars 1 arranged below the rolling stock 5 can be made simpler, ie these cooling bars 1 can have simply formed full jet nozzles 11 without elongated nozzle bodies 19 and / or they can not be divided into a spray chamber 7 and a distributor chamber 9, since those arranged below the rolling stock 5 Chilled beam 1 when there is an interruption of the coolant supply to the chilled beam 1 no coolant can run on the rolling stock 5.
  • the temperature measuring device 37 is preferably as in FIG FIG. 12 shown in front of the chilled beam 1 of the cooling device 35.
  • a further temperature measuring device 37 may be arranged behind a cooling bar 1 of the cooling device 35.
  • the temperature measuring device 37 is designed to determine a temperature distribution of a temperature of the rolling stock 5 transversely to the transport direction 3.
  • the temperature measuring device 37 has an infrared scanner for temperature detection with an accuracy of preferably ⁇ 2 ° C.
  • the control device 39 is adapted to flow rates of coolant to the individual cooling bars 1 as a function of the temperature distribution of the temperature of the temperature measuring device 37 determined by the temperature measuring device 37 Walzguts 5 transverse to the transport direction 3 to control.
  • the control device 39 comprises a control unit 47, two coolant pumps 49 and, for each cooling beam 1, a control valve 51.
  • each control valve 51 the flow rate of coolant to one of the chilled beams 1 is adjustable.
  • the control valves 51 of the cooling bar 1 arranged above the rolling stock 5 are connected to one of the two coolant pumps 49, the control valves 51 of the cooling bars 1 arranged below the rolling stock 5 are connected to the other coolant pump 49.
  • a different number of coolant pumps 49 may be provided, for example, only one coolant pump 49 connected to all the control valves 51, or more than two coolant pumps 49, each with only one control valve 51 or with a subset of the control valves 51 are connected.
  • the coolant pumps 49 may also be provided with a coolant filled high tank, which is arranged at a suitable height above the control valves 51 and through which the control valves 51 are supplied with coolant.
  • a supply pressure of a coolant supply system for example a water supply system
  • the cooling bars 1 each have full jet nozzles 11, it is generally sufficient to supply the cooling bars 1 with a coolant pressure of about 4 bar.
  • a typical flow rate of coolant of a cooling bar 1 is about 175 m 3 / h.
  • the control unit 47 the detected by the temperature measuring device 37 measuring signals are supplied.
  • the coolant pumps 49 and control valves 51 can be controlled by the control unit 47. From the control unit 47 are flow rates of coolant to the individual chilled beam 1 - in particular to those with varying nozzle densities - in Depending on the temperature distribution detected by the temperature measuring device 37 calculated and adjusted by controlling the control valves 51 to compensate for temperature differences of the temperature of the rolling stock 5 transversely to the transport direction 3 through the insert and a suitable combination of the cooling bars 1 with varying nozzle densities and the temperature of the rolling stock total to a desired value, such as a reel temperature to reduce.
  • the flow rates of coolant to the individual cooling bars 1 are calculated by the control unit 47, for example, based on a model of parameters of the rolling stock 5 as its thickness, temperature and / or heat capacity.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Metal Rolling (AREA)
  • Heat Treatments In General, Especially Conveying And Cooling (AREA)
  • Control Of Metal Rolling (AREA)
EP17168241.2A 2017-04-26 2017-04-26 Refroidissement d'un laminé Active EP3395463B1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP17168241.2A EP3395463B1 (fr) 2017-04-26 2017-04-26 Refroidissement d'un laminé
JP2019555876A JP6946458B2 (ja) 2017-04-26 2018-03-14 被圧延材料の冷却
EP18719050.9A EP3615237A2 (fr) 2017-04-26 2018-03-14 Refroidissement d'un produit laminé
CN201880027555.1A CN110536761B (zh) 2017-04-26 2018-03-14 被轧制材料的冷却
US16/607,399 US11358195B2 (en) 2017-04-26 2018-03-14 Cooling of rolled matertial
PCT/EP2018/056437 WO2018197100A2 (fr) 2017-04-26 2018-03-14 Refroidissement d'un produit laminé
US17/716,000 US11786949B2 (en) 2017-04-26 2022-04-08 Cooling of rolled material

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17168241.2A EP3395463B1 (fr) 2017-04-26 2017-04-26 Refroidissement d'un laminé

Publications (2)

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EP3395463A1 true EP3395463A1 (fr) 2018-10-31
EP3395463B1 EP3395463B1 (fr) 2019-12-25

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Cited By (5)

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Publication number Priority date Publication date Assignee Title
EP3670682A1 (fr) * 2018-12-20 2020-06-24 Primetals Technologies Austria GmbH Fabrication d'une bande métallique à une structure mixte de martensite-austénite
EP3808466A1 (fr) * 2019-10-16 2021-04-21 Primetals Technologies Germany GmbH Dispositif de refroidissement à rayonnement de refroidissement pourvu de section transversale creuse
EP3895820A1 (fr) * 2020-04-14 2021-10-20 Primetals Technologies Germany GmbH Fonctionnement d'un dispositif de réfrigération à une pression de fonctionnement minimale
EP3774100B1 (fr) 2018-04-13 2022-06-29 SMS Group GmbH Dispositif de refroidissement servant à refroidir un produit métallique et procédé permettant sa fabrication et son fonctionnement
CN115532855A (zh) * 2022-10-10 2022-12-30 江苏东方成套设备制造集团有限公司 一种连续穿水冷却装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3774100B1 (fr) 2018-04-13 2022-06-29 SMS Group GmbH Dispositif de refroidissement servant à refroidir un produit métallique et procédé permettant sa fabrication et son fonctionnement
EP3670682A1 (fr) * 2018-12-20 2020-06-24 Primetals Technologies Austria GmbH Fabrication d'une bande métallique à une structure mixte de martensite-austénite
WO2020127925A1 (fr) 2018-12-20 2020-06-25 Primetals Technologies Austria GmbH Fabrication d'une bande métallique comprenant une structure mixte austénite-martensite
EP3808466A1 (fr) * 2019-10-16 2021-04-21 Primetals Technologies Germany GmbH Dispositif de refroidissement à rayonnement de refroidissement pourvu de section transversale creuse
WO2021074233A1 (fr) * 2019-10-16 2021-04-22 Primetals Technologies Germany Gmbh Dispositif de refroidissement à jets de liquide de refroidissement présentant une section transversale creuse
CN114555253A (zh) * 2019-10-16 2022-05-27 首要金属科技德国有限责任公司 具有带中空横截面的冷却剂射流的冷却装置
EP3895820A1 (fr) * 2020-04-14 2021-10-20 Primetals Technologies Germany GmbH Fonctionnement d'un dispositif de réfrigération à une pression de fonctionnement minimale
EP3895819A1 (fr) * 2020-04-14 2021-10-20 Primetals Technologies Germany GmbH Fonctionnement d'un dispositif de réfrigération à une pression de fonctionnement minimale
WO2021209251A1 (fr) * 2020-04-14 2021-10-21 Primetals Technologies Germany Gmbh Fonctionnement d'une unité de refroidissement à pression de travail minimale
CN115532855A (zh) * 2022-10-10 2022-12-30 江苏东方成套设备制造集团有限公司 一种连续穿水冷却装置
CN115532855B (zh) * 2022-10-10 2024-01-09 江苏东方成套设备制造集团有限公司 一种连续穿水冷却装置

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JP2020517458A (ja) 2020-06-18
EP3615237A2 (fr) 2020-03-04
US11786949B2 (en) 2023-10-17
CN110536761B (zh) 2022-02-01
WO2018197100A3 (fr) 2018-12-27
JP6946458B2 (ja) 2021-10-06
CN110536761A (zh) 2019-12-03
US20200047230A1 (en) 2020-02-13
US11358195B2 (en) 2022-06-14
US20220226873A1 (en) 2022-07-21
WO2018197100A2 (fr) 2018-11-01
EP3395463B1 (fr) 2019-12-25

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