EP3615237A2

EP3615237A2 - Cooling of rolled material

Info

Publication number: EP3615237A2
Application number: EP18719050.9A
Authority: EP
Inventors: Erich Opitz; Lukas PICHLER; Alois Seilinger
Original assignee: Primetals Technologies Austria GmbH
Current assignee: Primetals Technologies Austria GmbH
Priority date: 2017-04-26
Filing date: 2018-03-14
Publication date: 2020-03-04
Also published as: EP3395463B1; US20220226873A1; JP6946458B2; CN110536761B; US11786949B2; JP2020517458A; WO2018197100A3; US20200047230A1; CN110536761A; EP3395463A1; US11358195B2; WO2018197100A2

Abstract

The invention relates to a chilled beam (1) for cooling rolled material (5), moved in a transport direction (3) and in particular for reducing temperature differences in the temperature of the rolled material (5) transversely to the direction of transport (3). The chilled beam (1) comprises several full jet nozzles (11) by means of which a coolant beam of a coolant with an approximately constant jet diameter can be distributed to the rolling stock (5) in the direction of distribution (15). The invention relates to a cooling device (35) comprising at least two chilled beams (1) of said type.

Description

description

Cooling of a rolling stock

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.

When hot rolling of rolling stock, such as a slab, the rolling stock is by rolling at high temperatures

reshaped. To cool the rolling stock, a coolant, usually water, is applied to the rolling stock. The temperature of the rolling stock often varies transversely to the transport direction.

Such temperature differences can affect the quality of the rolling stock. To reduce these temperature differences, 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 on 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 strip, wherein at least one

Cooling device is provided with nozzles for applying a coolant to the slab or on 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 Al discloses a hot rolling mill and a

A method of operation, wherein the shape of a rolled strip is controlled by localized cooling devices. The cooling devices are at intervals along

Work rolls arranged in at least three lateral zones

DE 199 34 557 A1 discloses a device for cooling metal belts or metal sheets conveyed on a conveyor line, in particular of hot rolled steel strips i outlet of a rolling train, with at least one cooling bar extending substantially over the width of the conveying line for applying cooling liquid to the metal strip to be cooled or sheet.

EP 0 081 132 A1 discloses a cooling device for

uniform cooling of a thick steel plate, wherein a desired amount of water is dispensed with a plurality of rod-like distributors i in the width direction of the steel plate.

DE 198 54 675 AI discloses a device for cooling a metal strip, in particular a hot strip, in the outlet of a rolling mill with at least two distributed over the width of the metal strip arranged nozzles, wherein a control and regulating device emerging from each nozzle cooling fluid flow individually in response to a detects detected temperature of a width portion of the metal strip which is associated with the respective nozzle.

The invention is based on the object, a device for cooling a moving in a transport direction

Specify rolling stock and a method for operating the device, in particular with regard to the compensation of temperature differences of the rolling transversely to

Transport direction are improved.

The object is achieved by a chilled beam with the features of claim 1, a cooling device with the Characteristics of claim 8 and a method having the features of claim 14 solved.

Advantageous embodiments of the invention are the subject of the dependent claims.

One according to an embodiment of the invention

formed chilled beam for cooling one in one

Moving direction moving rolling comprises a fillable with a coolant spray chamber and several of the

Spray chamber with coolant fed full jet nozzles, through each of which a coolant jet of a coolant with a nearly constant beam diameter can be output in an output direction to the rolling stock. Each jet nozzle has a tubular nozzle body having an open end disposed in an upper portion of the cooling beam within the spray chamber for supplying coolant into the nozzle

Full jet nozzle has. In this case, a distribution chamber for temporary storage of the coolant is provided, which communicates with the spray chamber through at least one passage opening for

Filling the spray chamber with coolant from the

Distribution chamber is connected. Preferably, each

Passage opening between the distribution chamber and the

Spray chamber disposed on an upper side of the distribution chamber and the open end of the tubular nozzle body of a

Full jet nozzle is above the height of the top of the

Distributor chamber arranged. This embodiment of a cooling bar enables the discharge of coolant from the spray chamber to the rolling stock

Jet nozzles. A full jet nozzle is understood to mean a nozzle through which a substantially straighter

Coolant jet with a nearly constant

Beam diameter can be output. The usage of

Full jet nozzles has the advantage that the distance of the

Cooling beam of 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 the

Negatively influence cooling effect, since the cooling effect occurs substantially only at the immediate impact points of the coolant jets.

Another advantage of full jet nozzles compared to conventionally used conical or flat jet nozzles results from the fact that solid jet nozzles produce a higher impact pressure of the coolant on the rolling stock as conical or flat jet nozzles by the concentrated output of the coolant at the same coolant pressure in the chilled beam. The higher impact pressure has a positive effect on the cooling effect on the Walzgutoberfläche, because there due to the

a large amount of coolant applied always a certain coolant film with a thickness of typically several millimeters to centimeters, which should be as completely as possible pierced by the impinging coolant jets to a high

Relative speed of the coolant to Walzgutoberfläche and thus to achieve a good heat dissipation. moreover

Even with very narrow nozzle arrangement, the coolant jets of full jet nozzles do not influence each other, as may be the case with the conical or flat jet nozzles.

In addition, full jet nozzles - for example, in contrast to conical or flat jet nozzles, which cause a beam widening and therefore require a higher operating pressure - due to the high impact pressure the possibility of a cooling bar according to the invention at relatively low

Operate refrigerant pressure, which is beneficial to energy consumption and the choice of cheaper

Peripherals such as pumps affects. For example, 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. Alternatively, however, a chilled beam according to the invention can also be used in a laminar mode (low pressure operation) at a coolant pressure of, for example, about only 1 bar. Furthermore, full jet nozzles are due to their compact and stable construction to mechanical impacts significantly less sensitive compared to the conical or flat jet nozzles, which, for example, in the case of

Strip of the rolling stock with a beating end of the tape is an advantage.

The division of the cooling bar in a spray chamber and a distribution chamber and the execution of the cooling bar with

Full jet nozzles is particularly advantageous when the

Chilled beam is arranged above the rolling stock and the

Coolant is discharged down to the rolling stock, d. H. if the output direction is at least approximately equal to the

Direction of gravity coincides. In this case, the embodiment according to the invention makes it possible

advantageous that in case of interruption of the cooling of the rolling stock after the interruption of the coolant supply to the chilled beam trailing a relatively small amount of coolant from the chilled beam and is discharged to the rolling stock, while a large amount of coolant remains in the chilled beam. This allows the chilled beam at a

Resumption of cooling by the lower volume to be filled also faster filled with coolant than in the case that the chilled beam in an interruption of the

Cooling is completely emptied. This is done by the

Caching of coolant is achieved in the distribution chamber, whereby in a suitable arrangement of the

at least one passage opening between the spray chamber and the distribution chamber, in particular in an arrangement on an upper side of the distribution chamber, the distribution chamber remains completely or at least partially filled with coolant in an interruption of the coolant supply. In addition, this is achieved in that the nozzle body of the

Full jet nozzles within the spray chamber up to an upper one Extend area of the cooling bar, so that at a

Interruption of the coolant supply coolant can only run out of the lying above the open ends of the nozzle body region of the spray chamber and from the nozzle bodies themselves, while the remaining volume of the spray chamber with

Coolant remains filled.

The embodiment of a cooling bar with a distributor 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 distributor chamber, to reduce pressure gradients and flow turbulences in the spray chamber so that all full jet nozzles of a cooling bar substantially be subjected to the same pressure and a substantially laminar

Flow is achieved in the spray chamber.

An embodiment of a cooling bar provides that a nozzle density and / or an outlet diameter of the

Full jet nozzles transversely to the transport direction varies. Under the nozzle density is understood here a number of nozzles per area. By varying the nozzle density and / or the outlet diameter of the full jet nozzles transversely to the

Transport direction, a corresponding variation of the cooling effect of the cooling bar is achieved transversely to the transport direction, can be reduced by the advantageous temperature differences of the rolling transversely to the transport direction.

A further embodiment of an inventive

Cooling bar 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. Below is an arrangement of Full jet nozzles of different nozzle rows understood in which the full jet nozzles of different nozzle rows are not arranged along the transport direction one behind the other and therefore do not form extending in the transport direction nozzle rows. By this staggered arrangement of the full-jet nozzles of different rows of nozzles advantageously a particularly uniform cooling effect of the rows of nozzles is achieved by running in the transport direction "cooling grooves" are avoided, in which no coolant is discharged to the rolling stock.

Further, a nozzle pitch may be adjacent to each other

Full jet nozzles of each nozzle row vary. This can advantageously transverse to the transport direction varying

Temperature differences of the temperature of the rolling stock are particularly well reduced. For example, 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

be used advantageously for cooling a rolling stock whose temperature is highest in a central region and decreases towards the edge regions.

A further embodiment of an inventive

Cooling bar provides at least one Kühlmittelableitvorrichtung for the discharge of coolant, which in of a

Randbereich the spray chamber arranged full jet nozzles is issued. By means of this so-called 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.

A cooling device according to the invention for cooling a rolling stock moved in a transport direction comprises a plurality of cooling bars, which are arranged one behind the other along the transport direction and in each case a plurality of full-jet nozzles

have, through each of which a coolant jet of a coolant with a nearly constant beam diameter the rolling stock can be dispensed. In this case, at least two of the cooling bars different from each other transversely to the

Transport direction varying nozzle densities and / or

Outlet diameter of their jet nozzles. Furthermore, the cooling device comprises a temperature measuring device for

Determining a temperature distribution of a temperature of the rolled material 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 determines the respective temperature distribution

considered. Moreover, the invention provides

Cooling device, a control device for automatically controlling the flow rates of coolant to the

single chilled beam depending on one

Temperature distribution of the temperature of the rolling stock transversely to the transport direction before. In this case, the temperature distribution can be detected by a temperature measuring device, 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 the flow rates of coolant to the individual cooling bars are independently controllable. As a result, 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 flexible

Temperature distribution of the temperature of the rolling transversely to the transport direction can be adjusted.

Such a cooling device allows

Temperature differences of the temperature of the rolling transverse to the transport direction by a targeted use of successively arranged cooling beam to reduce. Namely, since the cooling device has chilled beams with each other

different transversely to the transport direction varying

Nozzle densities and / or outlet diameter can, through the interaction of these chilled beams and

if necessary, by activating and deactivating individual ones of these chilled bars different cooling effects achieved, which can be adapted to the temperature distribution of the temperature of the rolling stock

Temperature differences across the transport direction

to reduce. In this case, in contrast to the above-mentioned from the prior art cooling devices, in particular the full jet nozzles of the chilled beam not individually controlled, but only each of the individual chilled beams, which compared to a control of the individual nozzles significantly reduces the design complexity and susceptibility.

An embodiment of the cooling device according to the invention provides that the nozzle densities of two of the cooling bars

Have nozzle density maxima, transverse to the

Transport direction are arranged on mutually different sides of the chilled beam, or / and that the

Outlet diameter of the jet nozzles of two of the chilled beam outlet diameter maxima, which are transverse to the

Transport direction are arranged on mutually different sides of the chilled beams. As a result of this configuration, it is advantageously possible to compensate for differences in temperature between different sides of the rolling stock, for example between edge regions of the rolling stock lying opposite one another, by cooling the respective warmer side of the rolling stock more than the other side.

Alternatively or additionally, the cooling device

have at least one cooling bar, in which the

Nozzle density and / or outlet diameter of

Full jet nozzles in a central region of the cooling beam is maximum and transverse to the transport direction to the

Edge regions of the cooling bar decreases, and / or

at least one chilled beam, wherein the nozzle density and / or the outlet diameter of the full jet nozzles in a central region of the cooling beam is minimal and transversely to the

Transport direction toward the edge regions of the cooling bar increases. This can be advantageous temperature differences be balanced between a central region and the edge regions of the rolling stock.

A further embodiment of the invention

Cooling device 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. As a result, 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 invention

Cooling device provides that at least one cooling bar, in particular at least one above the rolling stock

arranged chilled beam, according to the above

Embodiment of a cooling bar is formed. The

Advantages of this embodiment of the cooling device result from the abovementioned advantages of this embodiment of a cooling beam.

In a method according to the invention for operating a cooling device according to the invention is a

Temperature distribution of a temperature of the rolling transversely to the transport direction determined and it will be

Flow rates of coolant to the individual chilled beam depending on the determined temperature distribution controlled. The above-described characteristics, features and advantages of this invention as well as the manner in which they are achieved will become clearer and more clearly understood

Related to the following description of

Embodiments associated with the

Drawings are explained in more detail. Showing:

1 shows a perspective view of a first

Embodiment of a cooling beam, 2 shows a sectional view of that shown in FIG

Cooling beam, 3 is a bottom view of that shown in Figure 1

Chilled beams,

4 is a bottom view of a second embodiment of a cooling bar,

5 is a bottom view of a third embodiment of a cooling bar,

6 is a bottom view of a fourth embodiment of a cooling bar,

7 shows a bottom view of a fifth embodiment of a cooling bar, FIG 8 is a bottom view of a sixth

Embodiment of a cooling beam,

FIG. 9 shows volume flows of a coolant as a function of a position, which are output from cooling bars shown in FIGS. 1 to 8;

10 is a sectional view of a seventh

Embodiment of a cooling beam, 11 shows a sectional view of an eighth

Embodiment of a cooling beam, and

12 shows a rolling train for hot rolling a rolling stock with a cooling device for cooling the rolling stock.

Corresponding parts are provided in all figures with the same reference numerals. Figures 1 to 3 show schematically a first

Embodiment of a cooling beam 1 for cooling a moving in a direction of transport 3 rolling stock 5 (see Figure 12). 1 shows a perspective view of the cooling bar 1, Figure 2 shows a sectional view of the cooling beam 1 and Figure 3 shows a bottom view of the cooling beam 1. The transport direction 3 defined in the

Figures a Y-direction of a Cartesian coordinate system with coordinates X, Y, Z, whose Z-axis vertically upwards, d. H. the direction of gravity is opposite. The chilled beam 1 extends transversely to the

Transport direction 3 in the X direction across 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 optional Kühlmittelableitvorrichtungen 12. The spray chamber 7 and the distribution chamber 9 are each as a cavity with a transverse to the transport direction 3 in the X direction

extending longitudinal axis formed. In this case, the

Distribution chamber 9 is 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 which essentially has the shape of the Greek capital letter gamma, the horizontally extending section of the gamma extending above the distributor 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 transverse to the transport direction 3 in the X direction one behind the other at an upper side of the

Distribution chamber 9 arranged. 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. Through 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 output direction 15 in this case is the direction of

Gravity, d. H. the Z direction opposite. The

Output side 17 is in this case the bottom of the

Cooling beam 1. Each full jet nozzle 11 has a tubular nozzle body 19 with a vertical, d. H. 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 in an upper region of the spray chamber 7 above the height of the

Top of the distribution chamber 9 is arranged and can be fed by the coolant from the spray chamber 7 in the full-jet nozzle 11. 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 has the advantageous effect that in the event of an interruption of the cooling of the rolling stock 5 after the interruption of the coolant supply to the

Distribution chamber 9 coolant only from the lying above the open ends 21 of the nozzle body 19 area of

Spraying chamber 7 as well as from the nozzle bodies 19 itself can track to the rolling stock 5, while the remaining volume of the spray chamber 7 and the distribution chamber 9 remain filled with coolant.

The chilled beam 1 further has a transverse to the

Transport direction 3 varying nozzle density of the

Full jet nozzles 11, wherein the nozzle density is maximum in a central region of the cooling bar 1 and transverse to the transport direction 3 to the edge regions of the

Cooling beam 1 decreases towards (see Figure 3). Here are the Full jet nozzles 11 arranged in three transverse to the transport direction 3 nozzle rows 23 to 25, wherein the full jet nozzles 11 different nozzle rows 23 to 25 are arranged offset in the transport direction 3 against each other. The variation of the nozzle density transversely to the transport direction 3 is achieved in that a nozzle spacing d of adjacent full jet nozzles 11 of each nozzle row 23 to 25 varies, the nozzle spacing d in the central region of the cooling bar 1 is minimal and transverse to the

Transport direction 3 increases towards the edge regions of the cooling beam 1 out. For example, the nozzle pitch d increases parabolically from the central region to each edge region of the cooling beam 1. This can be advantageous

Temperature differences of the rolling stock 5 are reduced when the temperature of the rolling stock 5 decreases from a central 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 optional Kühlmittelableitvorrichtungen 12 are each disposed below an edge region of the spray chamber 7 and adapted to collect and dissipate coolant, which is output from disposed 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. Everybody points this out

Kühlmittelableitvorrichtung 12 a

Coolant collector 12.1 and a

Kühlmittelableitrohr 12.2 on. The Kühlmittelableitrohr 12.2 is disposed on an underside of the coolant collecting container 12.1 and serves to dissipate in the

Coolant collector 12.1 collected coolant. FIGS. 4 to 7 each show a further one

Embodiment of a cooling beam 1 in a bottom view of the respective cooling beam 1. The cooling beam 1 of each of these embodiments differs from that in the Figures 1 to 3 shown chilled beam 1 only by the distribution of the full jet nozzles 11 transverse to the

Transport direction 3. As in the case of the cooling beam 1 shown in FIGS. 1 to 3, the full-jet nozzles 11 extend in three directions transverse to the transport direction 3

Nozzle rows 23 to 25 are arranged, wherein the

Full jet nozzles 11 different rows of nozzles 23 to 25 are arranged offset in the transport direction 3 against each other. FIG. 4 shows a cooling beam 1, in which the nozzle spacing d of adjacent full-jet nozzles 11 each

Nozzle row 23 to 25 from the middle area of the

Cooling beam 1 transverse to the transport direction 3 to the

Edge regions of the cooling bar 1 out (for example

parabolic), so that the nozzle density of the

Full jet nozzles 11 from the central region of the

Cooling beam 1 increases to the edge regions of the cooling beam 1. This can be advantageous temperature differences of

Rolled stock 5 can be reduced when the temperature of the

Walzguts 5 increases from a central region of the rolling stock 5 to the edge regions of the rolling stock 5.

FIG. 5 shows a cooling beam 1, in which the nozzle spacing d of adjacent full jet nozzles 11 of all

Nozzle rows 23 to 25 is the same, but the

Nozzle rows 23 to 25 extend differently far from an edge region of the cooling beam 1 located on the right in FIG. 5, so that the nozzle density in the right-lying edge region has a maximum nozzle density. As a result, 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 cooling beam 1, in which the nozzle spacing d of adjacent full jet nozzles 11 of all

Nozzle rows 23 to 25 is also the same, but the

Nozzle rows 23 to 25 vary widely from one in 6 extend to the left on the edge region of the cooling bar 1 to the right, so that the nozzle density in the left-hand edge region has a maximum nozzle density. This can advantageously be reduced temperature differences of the rolling stock 5, when the temperature of the rolling stock 5 from the left

located edge region of the rolling stock 5 decreases to the right edge region of the rolling stock 5.

FIG. 7 shows a cooling beam 1, in which the nozzle spacing d of adjacent solid jet nozzles 11 of all

Nozzle rows 23 to 25 is the same and the nozzle density transversely to the transport direction 3 is constant. Such a cooling bar 1 therefore causes a uniform cooling of the rolling stock 5 transversely to the transport direction. 3

FIG. 8 shows a cooling beam 1, which differs from the cooling beam 1 shown in FIG. 7 only in that the outlet diameter D of the full-jet nozzles 11 varies transversely to the transport direction 3. It is the

Outlet diameter D in the middle region of the

Cooling beam 1 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 exemplary embodiments of cooling bars 1 shown in FIGS. 1 to 8 can be modified in various ways. For example, 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. Alternatively, 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. Furthermore, the full-jet nozzles 11 can be arranged in a number of rows of nozzles 23 to 25 deviating from three. The exemplary embodiment shown in FIG. 8 can also be modified such that the outlet diameter D of the full-jet nozzles 11 varies transversely to the transport direction 3 in a different manner than in the case of the chilled beam 1 shown in FIG. For example, the outlet diameter D in the middle region of the cooling bar 1 may be minimal and transverse to the transport direction 3 to the edge regions of the

Increase the cooling bar 1, or the outlet diameter D may be a maximum in an edge region of the cooling bar 1 and decrease transversely to the transport direction 3 to the edge region opposite this edge region.

FIG. 9 shows schematically from FIGS. 1 to 8

illustrated cooling beams output volume flows Vi to V _{5 of} a coolant in dependence on a position transverse to the transport direction. 3

A first volume flow Vi is generated by the cooling bars 1 shown in FIGS. 3 and 8 and decreases from a central area of the cooling bar 1 to the edge areas, the decrease being parabolic, for example.

A second volume flow V ₂ is from that in Figure 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 that in Figure 5

Cooling bar 1 shown generates and decreases from a first edge region to the second Ranbereich of the cooling beam 1 down.

A fourth volume flow V ₄ is obtained from that in FIG. 6

Cooling bar 1 shown generates and decreases from the second edge region to the first Ranbereich of the cooling beam 1 down. A fifth volume flow V ₅ is from that in Figure 7

illustrated 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 beam 1. In this

Embodiment, the distribution chamber 9 is arranged below the spray chamber 7. Again, 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, d. H. Having parallel to the Z-axis cylinder axis. However, 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 transverse to the

Transport direction 3 varying nozzle density and may for example be arranged distributed analogously to any of the embodiments shown in Figures 1 to 6.

FIG. 11 shows a sectional view of another

Embodiment of a cooling beam 1. Also in this embodiment, the distribution chamber 9 is arranged below the spray chamber 7. Again, 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. A chilled beam 1 shown in FIG. 11 is therefore intended to be arranged below the rolling stock 5 and to discharge coolant onto an underside of the rolling stock 5. The full jet nozzles 11 may in turn a transversely to the

Transport direction 3 have varying nozzle density. FIG. 12 schematically shows a rolling train 27 for hot rolling a rolling stock 5, which is transported in a transporting direction 3 through the rolling train 27. The rolling train 27 includes a finishing train 29 and a cooling section 31. In the

Prefabricated line 29 a plurality of rolling stands 33 are arranged one behind the other, with which the rolling stock 5 is formed. In

FIG. 12 shows by way of example two rolling stands 33; 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 chilled beam 1 has a plurality of full jet nozzles 11, through each one

Coolant jet of a coolant with a nearly

constant beam diameter to the rolling stock 5 can be output. Some chilled beams 1 are one behind the other above the

Walzguts 5 arranged and give coolant jets down on an upper surface of the rolling stock 5. The others

Chilled beams 1 are arranged one behind the other below the rolling stock 5 and emit coolant jets upwards onto an underside of the rolling stock 5. In FIG. 12, by way of example, five cooling beams 1 arranged above and five below the rolling stock 5 are shown; However, the cooling device 35 may also other numbers above and / or below the

Walzguts 5 arranged chilled beam 1 have. At least two of the cooling bars 1, but preferably at least four of the cooling bars 1 arranged above the rolling stock 1 and at least four of the cooling bars 1 arranged below the rolling stock 5, have different nozzle densities and / or outlet diameters D of their full-jet nozzles 11, different from one another transversely to the transport direction 3 , The remaining chilled beams 1 have a constant nozzle density like the embodiment shown in FIG. In this case, the cooling bars 1 with varying nozzle densities and / or varying outlet diameters D preferably arranged (with respect to the transport direction 3) in front of the cooling beam 1 with constant nozzle densities. This ensures that at the beginning of the cooling section 31, where the temperature of the rolling stock 5 is still very high, local temperature differences across the transport direction 3 by chilled beam 1 with transverse to the

Transport direction 3 varying nozzle densities can be reduced while subsequent chilled beams 1 with

Constant nozzle densities only reduce the overall temperature of the transverse to the transport direction 3 evenly tempered rolling stock 5.

For example, the first four above the

Walzguts 5 arranged cooling beam 1 and the first four arranged below the rolling stock 5 chilled beam 1 each have a chilled beam 1 with a nozzle density, which decreases analogous to Figure 3 from a central region of the cooling beam 1 to the edge regions of the cooling beam 1, a chilled beam 1 with a nozzle density , which increases in a manner analogous to FIG. 4 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, analogous to FIG. 5, of a first edge region of the cooling beam 1 (in FIG. 5 on the right) to the second edge region (in FIG

Cooling beam 1 decreases, and a chilled beam 1 with a

Nozzle density, analogous to FIG. 6, from the first edge region of the cooling beam 1 to the second edge region of the

Cooling bar 1 increases. Furthermore, they are arranged above the rolling stock 5

Chilled beam 1, preferably each full jet nozzles 11 and / or a spray chamber 7 and a distribution chamber 9 as shown in Figures 1 and 2, the cooling beam 1 to a

After running coolant from these chilled beam 1 to reduce the rolling stock 5 at an interruption of the coolant supply to the chilled beam 1. The arranged below the rolling stock 5 chilled beam 1 can be made simpler, ie these chilled beams 1 can be easily formed Full jet nozzles 11 without elongated nozzle body 19 and / or not in a spray chamber 7 and a

Distributed chamber 9 be divided, as from the below the rolling stock 5 arranged cooling beam 1 at an interruption of the coolant supply to the cooling beam 1 no coolant can run on the rolling stock 5.

The temperature measuring device 37 is preferably arranged in front of the cooling bars 1 of the cooling device 35, as shown in FIG. In addition, another

Temperature measuring device 37 may be arranged behind a chilled beam 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. For example, the temperature measuring device 37 has an infrared scanner for temperature detection with an accuracy of preferably ± 2 ° C. The control device 39 is designed to

Flow rates of coolant to the individual chilled beams 1 as a function of the determined with the temperature measuring device 37 temperature distribution of the temperature of the

Walzguts 5 transverse to the transport direction 3 to control. The control device 39 comprises a control unit 47, two coolant pumps 49 and one for each chilled beam 1

Control valve 51.

Through 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 connected. Instead of two

Coolant pumps 49 may also have a different number of

Coolant pumps 49 may be provided, for example, only one coolant pump 49, which is connected to all control valves 51 is, or more than two coolant pumps 49, which are each connected to only one control valve 51 or with a subset of the control valves 51. Instead of the

Coolant pumps 49 can also be provided with a high-pressure container filled with coolant, which is arranged at a suitable height above the control valves 51 and through which the control valves 51 are supplied with coolant. In cases where a supply pressure of a

Coolant supply system, such as a

Water supply system, already sufficient, can even be quite on coolant pumps 49 or a high tank

be waived. Since the chilled beams 1 respectively

Full jet nozzles 11, it is usually sufficient to feed the chilled beam 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 are the of the

Temperature measuring device 37 supplied detected measurement signals. The coolant pumps 49 and control valves 51 can be controlled by the control unit 47. Flow rates of coolant to the individual chilled beams 1, in particular to those with varying nozzle densities, are calculated by the control unit 47 as a function of the temperature distribution detected by the temperature measuring device 37 and adjusted by controlling the control valves 51 to detect temperature differences of the temperature of the rolling stock 5 transversely to that Transport direction 3 through the use and a suitable combination of

Balancing the cooling bar 1 with varying nozzle densities and the total temperature of the rolling stock 5 to a desired value, for example, a reel temperature to reduce. The flow rates of coolant to the individual

Chilled beams 1 are thereby from the control unit 47th

for example, based on a model of parameters of

Rolled 5 as the thickness, temperature and / or

Heat capacity calculated. Although the invention has been further illustrated and described in detail by way of preferred embodiments, the invention is not limited by the disclosed examples, and other variations can be derived therefrom by those skilled in the art without departing from the scope of the invention

To leave invention.

LIST OF REFERENCE NUMBERS

I chilled beams

3 transport direction

5 rolling stock

7 spray chamber

9 distribution chamber

II full jet nozzle

12 Coolant discharge device 12.1 Coolant collector

12.2 Coolant drain pipe

13 passage opening

15 output direction

17 output page

19 nozzle body

21 open end

22 outlet opening

23 to 25 nozzle row

27 rolling mill

29 finishing mill

31 cooling section

33 rolling stand

35 cooling device

37 Temperature measuring device 39 Control device

47 control unit

49 coolant pump

51 control valve

d nozzle distance

D outlet diameter

X, Y, Z Cartesian coordinates

Vi to V ₅ volumetric flow

Claims

claims

1. chilled beam (1) for cooling one in one

Transport direction (3) moving rolling stock (5), the

Comprising cooling bar (1)

a spray chamber (7) which can be filled with a coolant,

- A distribution chamber (9) for caching the

Coolant, which is connected to the spray chamber (7) through at least one passage opening (13) for filling the spray chamber (7) with coolant from the distribution chamber (9),

- Wherein each passage opening (13) between the

Distribution chamber (9) and the spray chamber (7) on a

Top of the distribution chamber (9) is arranged,

- And more of the spray chamber (7) with coolant

Powered jet nozzles (11), through each one

Coolant jet of a coolant with a nearly

constant beam diameter in an output direction (15) to the rolling stock (5) can be output,

- Wherein each full-jet nozzle (11) is a tubular

Nozzle body (19) having a in an upper portion of the cooling bar (1) within the spray chamber (7)

arranged open end (21) for feeding coolant into the full jet nozzle (11),

- Wherein the open end (21) above the height of the top of the distribution chamber (9) is arranged.

2. chilled beam (1) according to claim 1,

characterized in that a nozzle density of the

Full jet nozzles (11) transversely to the transport direction (3) varies.

3. Chilled beam (1) according to one of the preceding claims, characterized in that an outlet diameter (D) of the

Full jet nozzles (11) transversely to the transport direction (3) varies.

4. chilled beam (1) according to any one of the preceding claims, characterized in that the full jet nozzles (11) in at least one transverse to the transport direction (3) extending nozzle row (23 to 25) are arranged.

5. chilled beam (1) according to any one of the preceding claims, characterized in that the full jet nozzles (11) extending in several transversely to the transport direction (3)

Nozzle rows (23 to 25) are arranged, and that the

Full jet nozzles (11) of different rows of nozzles (23 to 25) in the transport direction (3) are arranged offset from one another.

6. cooling beam (1) according to claim 4 or 5,

characterized in that a nozzle spacing (d) of adjacent full-jet nozzles (11) of each nozzle row (23 to 25) varies.

7. chilled beam (1) according to one of the preceding claims, characterized by at least one

Kühlmittelableitvorrichtung (12) for the derivation of

Coolant, which is output from in a peripheral region of the spray chamber (7) arranged full jet nozzles (11).

8. Cooling device (35) for cooling one in one

Transport direction (3) moving rolling stock (5), the

Cooling device (35) comprising

- Several chilled beams (1) running along the

Transport direction (3) are arranged one behind the other and each have a plurality of full-jet nozzles (11) through which a respective coolant jet of a coolant with a nearly constant beam diameter to the rolling stock (5) can be output,

a temperature measuring device (37) for determining a temperature distribution of a temperature of the rolling stock (5) transversely to the transport direction (3),

- A control device (39) for automatically controlling flow rates of coolant to the individual

Chilled beam (1) depending on a temperature distribution the temperature of the rolling stock (5) transversely to the

Transport direction (3),

- wherein at least two of the cooling bars (1) different from each other transversely to the transport direction (3) varying nozzle densities and / or outlet diameter (D) of their

Full jet nozzles (11) have.

9. Cooling device (35) according to claim 8,

characterized in that the nozzle densities of two of the cooling bars (1) have nozzle density maxima which are arranged transversely to the transport direction (3) on mutually different sides of the cooling bars (1), and / or

Outlet diameter (D) of the full jet nozzles (11) of two of the cooling bars (1) Auslassdurchmesserermaxima which are arranged transversely to the transport direction (3) on mutually different sides of the cooling beam (1).

10. Cooling device (35) according to claim 8 or 9,

characterized in that the nozzle density and / or the outlet diameter (D) of the full jet nozzles (11) of at least one cooling bar (1) in a central region of the

Cooling bar (1) is maximum and transverse to the

Transport direction (3) decreases towards the edge regions of the cooling beam (1).

11. Cooling device (35) according to one of claims 8 to 10, characterized in that the nozzle density and / or the outlet diameter (D) of the full jet nozzles (11) of at least one cooling bar (1) in a central region of the

Cooling bar (1) is minimal and transverse to the

Transport direction (3) increases towards the edge regions of the cooling bar (1).

12. Cooling device (35) according to any one of claims 8 to 11, characterized in that at least one cooling bar (1) above the rolling stock (5) is arranged and at least one cooling bar (1) below the rolling stock (5) is arranged.

13. Cooling device (35) according to any one of claims 8 to 12, characterized in that at least one cooling bar (1) is designed according to one of claims 1 to 7.

14. A method for operating a formed according to one of claims 8 to 13 cooling device (35), wherein

- A temperature distribution of a temperature of the rolling stock (5) is determined transversely to the transport direction (3)

- and flow rates of coolant to the individual

Chilled beam (1) depending on the determined

Temperature distribution to be controlled.