EP3395463B1 - Cooling of a product which is to be rolled - Google Patents

Description

The invention relates to a chilled beam for cooling a rolling stock moving in a transport direction.

When hot rolling of rolling stock, for example a slab, the rolling stock is formed by rolling at high temperatures. In order to cool the rolling stock, a coolant, usually water, is applied to the rolling stock. The temperature of the rolling stock often varies across the direction of transport. Such temperature differences can affect the quality of the rolling stock. Various cooling devices and methods are known to reduce these temperature differences.

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 two outer regions and a central region arranged between the two outer regions, seen transversely to the transport direction, a liquid cooling medium being able to be fed into the regions each via a separate, individually controllable valve device.

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 with nozzles is provided for applying a coolant to the slab or the strip. The nozzles are arranged and / or controlled so as to be distributed over the width in such a way that a coolant is applied in particular to positions at which an elevated temperature can be determined.

WO 2006/076771 A1 discloses a hot rolling mill and a method of operating the same 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 metal belts or metal sheets conveyed on a conveyor line, in particular hot-rolled steel belts in the outlet of a rolling mill, with at least one cooling beam, which extends essentially over the width of the conveyor line, for applying coolant to the metal belt or sheet to be cooled.

EP 0 081 132 A1 discloses a cooling device for uniformly cooling a thick steel plate, wherein a desired amount of water is discharged with a plurality of rod-like distributors 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 wide strip, in the outlet of a rolling mill with at least two nozzles distributed over the width of the metal strip, with a control device regulating a cooling fluid stream emerging from each nozzle individually as a function of a detected temperature of a width section of the Metal strip controls which is assigned to the respective nozzle.

The JP 2011-194417 shows a chilled beam for cooling a rolling stock moving in a transport direction, the chilled beam comprising - a spray chamber that can be filled with a coolant, - a distributor chamber for temporarily storing the coolant, which is connected to the spray chamber through at least one passage opening for filling the spray chamber with coolant from the distributor chamber , wherein each passage opening is arranged between the distributor chamber and the spray chamber on an upper side of the distributor chamber, and a plurality of nozzles which can be fed with coolant from the spray chamber and through which a coolant jet of a coolant can be dispensed in a direction of discharge to the rolling stock, each nozzle has a tubular nozzle body which has an open end arranged in an upper region of the cooling beam within the spray chamber for feeding coolant into the full jet nozzle.

The invention has for its object a device for cooling a moving in a transport direction Specify rolling stock and a method for operating the device, which are improved in particular with regard to the compensation of temperature differences of the rolling stock transverse to the direction of transport.

The object is achieved by a chilled beam with the features of claim 1.

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

A cooling beam designed according to an embodiment of the invention for cooling a rolling stock moving 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 and through which in each case a coolant jet of a coolant with an almost constant jet diameter in a discharge direction to the rolling stock can be spent. Each full jet nozzle has a tubular nozzle body which has an open end, which is arranged in an upper region of the cooling beam within the spray chamber, for feeding coolant into the full jet nozzle Filling the spray chamber with coolant from the distribution chamber is connected. Each passage opening is arranged between the distributor chamber and the spray chamber on an upper side of the distributor chamber and the open end of the tubular nozzle body of a full jet nozzle is arranged above the height of the upper side of the distributor chamber.

This design of a chilled beam enables coolant to be discharged from the spray chamber to the rolling stock through full jet nozzles. A full jet nozzle is understood to mean a nozzle through which an essentially straight coolant jet with an almost constant jet diameter can be emitted. The use of full jet nozzles has the advantage that the distance of the chilled beam from the rolling stock is not critical in a wide range, typically up to approximately 1500 mm, due to the essentially straight coolant jets and can therefore be varied in this range without the To have a negative influence on the cooling effect, since the cooling effect essentially only occurs at the direct impact points of the coolant jets.

Another advantage of full jet nozzles in comparison to the commonly used cone or flat jet nozzles results from the fact that full jet nozzles generate a higher impact pressure of the coolant on the rolling stock than cone or flat jet nozzles due to the bundled output of the coolant at the same coolant pressure in the cooling beam. The higher impact pressure has a positive effect on the cooling effect on the surface of the rolling stock because there is always a certain coolant film with a thickness of typically several millimeters to centimeters due to the large amount of coolant applied, which should be penetrated as completely as possible by the incident coolant jets by one high relative speed of the coolant to the surface of the rolling stock and thus good heat dissipation. In addition, even with a very narrow nozzle arrangement, the coolant jets from full jet nozzles do not influence one another, as can be the case with the cone or flat jet nozzles.

In addition, full jet nozzles - for example, in contrast to cone or flat jet nozzles, which cause a jet expansion and therefore require a higher operating pressure - offer the possibility, due to the high impact pressure, of operating a cooling beam according to the invention at a relatively low coolant pressure, which has an advantageous effect on the energy consumption and the selection cheaper peripheral devices such as pumps. For example, a chilled beam according to the invention is fed with a coolant pressure of up to 10 bar in a high-pressure operation, a pressure which is still less than 1 bar below this coolant pressure still being achieved at a single full jet nozzle. Alternatively, a chilled beam according to the invention can also be used in a laminar operation (low-pressure operation) Coolant pressure of, for example, only about 1 bar can be used.

Furthermore, due to their compact and stable construction, full jet nozzles are considerably less sensitive to mechanical influences in comparison to the cone or flat jet nozzles, which is advantageous, for example, in the event of a strip break of the rolling stock with a striking strip end.

The division of the chilled beam into a spray chamber and a distributor chamber and the design of the chilled beam with full jet nozzles is particularly advantageous if the chilled beam is arranged above the rolling stock and the coolant is discharged downward onto the rolling stock, ie if the dispensing direction is at least approximately in the direction of the Gravity matches. In this case, the embodiment according to the invention advantageously enables a relatively small amount of coolant to run out of the chilled beam and to be discharged onto the rolling stock when the rolling stock is interrupted after the coolant supply to the chilled beam is interrupted, while a large amount of coolant flows in the chilled beam remains. As a result, the cooling beam can also be filled with coolant more quickly when the cooling is restarted due to the smaller volume to be filled than in the event that the cooling beam is completely emptied when the cooling is interrupted. This is achieved by the intermediate storage of coolant in the distribution chamber, so that with a suitable arrangement of the at least one passage opening between the spray chamber and the distribution chamber, in particular with an arrangement on an upper side of the distribution chamber, the distribution chamber in whole or at least in part when the coolant supply is interrupted Coolant remains filled. In addition, this is achieved in that the nozzle bodies of the full jet nozzles extend within the spray chamber into an upper region of the chilled beam, so that one Interruption of the coolant supply Coolant can only run from the area of the spray chamber above the open ends of the nozzle body and from the nozzle body itself, while the remaining volume of the spray chamber remains filled with coolant.

The design of a chilled beam with a distributor chamber also advantageously enables pressure gradients and flow turbulences in the spray chamber to be reduced 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, so that essentially all full jet nozzles of a chilled beam are subjected to the same pressure and an essentially laminar flow is achieved in the spray chamber.

An embodiment of a chilled beam provides that a nozzle density and / or an outlet diameter of the full jet nozzles varies transversely to the transport direction. The nozzle density here means a number of nozzles per surface. 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 chilled beam transversely to the transport direction is achieved, by means of which temperature differences of the rolling stock transversely to the transport direction can advantageously be reduced.

A further embodiment of a chilled beam according to the invention provides that the full jet nozzles are arranged in at least one row of nozzles running transversely to the transport direction. A further development of this embodiment of a chilled beam provides that the full jet nozzles are arranged in a plurality of rows of nozzles running transversely to the transport direction, and that the full jet nozzles of different nozzle rows are arranged offset with respect to one another in the transport direction. This means an arrangement of the full jet nozzles of different nozzle rows in which the full jet nozzles of different nozzle rows are not arranged one behind the other along the transport direction and therefore do not form any nozzle rows running in the transport direction. This staggered arrangement of the full jet nozzles of different nozzle rows advantageously achieves a particularly uniform cooling effect of the nozzle rows by avoiding "cooling fins" running in the transport direction, in which no coolant is dispensed onto the rolling stock.

Furthermore, a nozzle spacing of adjacent full jet nozzles of each row of nozzles can vary. As a result, temperature differences in the temperature of the rolling stock which advantageously vary transversely to the transport direction can be reduced particularly well. For example, the distance between the nozzles may be the smallest in a central region of the discharge side of the chilled beam and may increase in each case to the edge regions. Such a distribution of the full jet nozzles can advantageously be used for cooling a rolling stock, the temperature of which is highest in a central region and decreases towards the edge regions.

A further embodiment of a chilled beam according to the invention provides at least one coolant discharge device for discharging coolant, which is emitted by full jet nozzles arranged in an edge region of the spray chamber. This so-called edge masking can advantageously prevent too much coolant from reaching an edge region of the rolling stock and thereby cooling the edge region too much.

• FIG 1 eine perspektivische Darstellung eines ersten Ausführungsbeispiels eines Kühlbalkens,
• FIG 2 eine Schnittdarstellung des in Figur 1 gezeigten Kühlbalkens,
• FIG 3 eine Untersicht auf den in Figur 1 gezeigten Kühlbalken,
• FIG 4 eine Untersicht auf ein zweites Ausführungsbeispiel eines Kühlbalkens,
• FIG 5 eine Untersicht auf ein drittes Ausführungsbeispiel eines Kühlbalkens,
• FIG 6 eine Untersicht auf ein viertes Ausführungsbeispiel eines Kühlbalkens,
• FIG 7 eine Untersicht auf ein fünftes Ausführungsbeispiel eines Kühlbalkens,
• FIG 8 eine Untersicht auf ein sechstes Ausführungsbeispiel eines Kühlbalkens,
• FIG 9 von in den Figuren 1 bis 8 dargestellten Kühlbalken ausgegebene Volumenströme eines Kühlmittels in Abhängigkeit von einer Position,
• FIG 10 eine Schnittdarstellung eines siebten Ausführungsbeispiels eines Kühlbalkens,
• FIG 11 eine Schnittdarstellung eines achten Ausführungsbeispiels eines Kühlbalkens, und
• FIG 12 eine Walzstraße zum Warmwalzen eines Walzguts mit einer Kühlvorrichtung zum Kühlen des Walzguts.

The above-described properties, features and advantages of this invention and the manner in which they are achieved can be more clearly understood in connection with the following description of exemplary embodiments which are explained in more detail in connection with the drawings. Show:

• FIG. 1 1 shows a perspective illustration of a first exemplary embodiment of a chilled beam,
• FIG 2 a sectional view of the in Figure 1 shown chilled beam,
• FIG 3 a bottom view of the in Figure 1 shown chilled beams,
• FIG 4 a bottom view of a second embodiment of a chilled beam,
• FIG 5 a bottom view of a third embodiment of a chilled beam,
• FIG 6 a bottom view of a fourth embodiment of a chilled beam,
• FIG 7 a bottom view of a fifth embodiment of a chilled beam,
• FIG 8 a bottom view of a sixth embodiment of a chilled beam,
• FIG. 9 from in the Figures 1 to 8 shown cooling beams output volume flows of a coolant depending on a position,
• FIG 10 3 shows a sectional illustration of a seventh exemplary embodiment of a chilled beam,
• FIG 11 a sectional view of an eighth embodiment of a chilled beam, and
• FIG 12 a rolling mill for hot rolling a rolling stock with a cooling device for cooling the rolling stock.

Corresponding parts are provided with the same reference symbols in all figures.

The Figures 1 to 3 schematically show a first embodiment of a chilled beam 1 for cooling a rolling stock 5 moved in a transport direction 3 (see Figure 12 ). It shows Figure 1 1 shows a perspective view of the chilled beam 1, Figure 2 shows a sectional view of the chilled beam 1 and Figure 3 shows a bottom view of the cooling beam 1. In the figures, the transport direction 3 defines a Y direction of a Cartesian coordinate system with coordinates X, Y, Z, the Z axis of which runs vertically upward, ie opposite to the direction of gravity. The cooling 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 distributor chamber 9, a plurality of full jet nozzles 11 and two optional coolant discharge devices 12. The spray chamber 7 and the distributor chamber 9 are each designed as a cavity with a longitudinal axis running transversely to the transport direction 3 in the X direction. The distribution chamber 9 has an essentially rectangular cross section in a plane perpendicular to its longitudinal axis. The spray chamber 7 has a cross section in a plane perpendicular to its longitudinal axis, which essentially has the shape of the Greek capital letter gamma, the horizontal section of the gamma running above the distributor chamber 9.

The spray chamber 7 and the distributor chamber 9 are connected to one another 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 on an upper side of the distribution chamber 9. The distribution chamber 9 can be filled from the outside with a coolant, for example with cooling water, via a coolant inlet (not shown). The spray chamber 7 can be filled with the coolant via the passage openings 13 from the distributor chamber 9.

Through each full jet nozzle 11, a coolant jet of the coolant with an almost constant jet diameter can be emitted from the spray chamber 7 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, i.e. H. opposite to the Z direction. The output 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. H. parallel to the Z axis. The nozzle body 19 runs inside the spray chamber 7 from a bottom of the spray chamber 7 to an open end 21 of the nozzle body 19, which is arranged in an upper region of the spray chamber 7 above the height of the upper side of the distributor chamber 9 and through the coolant from the spray chamber 7 in the full jet nozzle 11 can be fed. The nozzle bodies 19 are designed, for example, as hollow cylinders or in each case narrow conically from their open end 21 to the bottom of the spray chamber 7. The full jet nozzles 11 each have an outlet opening 22, the outlet diameter D of which is, for example, between 3 mm and 20 mm, preferably up to 12 mm.

This design of the cooling beam 1 advantageously has the effect that, in the event of an interruption in the cooling of the rolling stock 5 after the interruption of the coolant supply to the distribution chamber 9, coolant only comes from the area of the spray chamber 7 above the open ends 21 of the nozzle bodies 19 and from the nozzle bodies 19 themselves can run after the rolling stock 5, while the remaining volume of the spray chamber 7 and the distributor chamber 9 remain filled with coolant.

The cooling beam 1 also has a nozzle density of the full jet nozzles 11 which varies transversely to the transport direction 3, the nozzle density being in one middle area of the chilled beam 1 is maximal and decreases transversely to the transport direction 3 towards the edge areas of the chilled beam 1 (see Figure 3 ). The full jet nozzles 11 are arranged in three nozzle rows 23 to 25 running transversely to the transport direction 3, the full jet nozzles 11 of different nozzle rows 23 to 25 being arranged offset with respect to one another in the transport direction 3. 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 row of nozzles 23 to 25 varies, the nozzle spacing d being minimal in the central region of the cooling beam 1 and transverse to the transport direction 3 to the edge regions of the Chilled beam 1 increases. For example, the nozzle distance d increases parabolically from the central area to each edge area of the chilled beam 1. As a result, temperature differences of the rolling stock 5 can advantageously be reduced if 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 coolant discharge devices 12 are each arranged under an edge region of the spray chamber 7 and are designed to collect and discharge coolant that is emitted by full jet nozzles 11 arranged in the respective edge region of the spray chamber 7 (so-called edge masking), so that the coolant does not fall onto the corresponding one Edge area of the rolling stock 5 arrives and the edge area of the rolling stock 5 cools too much. For this purpose, each coolant discharge device 12 has a coolant collecting container 12.1 and a coolant discharge pipe 12.2. The coolant discharge pipe 12.2 is arranged on an underside of the coolant collecting container 12.1 and serves to discharge coolant caught in the coolant collecting container 12.1.

The Figures 4 to 7 each show a further exemplary embodiment of a chilled beam 1 in a bottom view of the respective chilled beam 1. The chilled beam 1 of each of these exemplary embodiments differs from that in FIGS Figures 1 to 3 shown cooling beam 1 only by the distribution of the full jet nozzles 11 transversely to the transport direction 3. As with that in the Figures 1 to 3 shown cooling beam 1, the full jet nozzles 11 are arranged in three nozzle rows 23 to 25 running transversely to the transport direction 3, the full jet nozzles 11 of different nozzle rows 23 to 25 being arranged offset with respect to one another in the transport direction 3.

Figure 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 decreases (for example parabolically) from the central region of the chilled beam 1 transversely to the transport direction 3 to the edge regions of the chilled beam 1, so that the nozzle density of the full jet nozzles 11 increases from the central region of the chilled beam 1 to the edge regions of the chilled beam 1. As a result, 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.

Figure 5 shows a chilled 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 differ from one another in Figure 5 extend the right-hand edge area of the chilled beam 1 to the left, so that the nozzle density in the right-hand edge area 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 right-hand edge area of the rolling stock 5 to the left-hand edge area of the rolling stock 5.

Figure 6 shows a chilled 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 differ in distance from one another Figure 6 the left edge area of the chilled beam 1 extend to the right so that the nozzle density in the left edge area 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 left-hand edge region of the rolling stock 5 to the right-hand edge region of the rolling stock 5.

Figure 7 shows a chilled beam 1, in which the nozzle spacing d of adjacent full jet nozzles 11 of all nozzle rows 23 to 25 is the same and the nozzle density transverse to the transport direction 3 is also constant. Such a cooling beam 1 therefore effects uniform cooling of the rolling stock 5 transversely to the transport direction 3.

Figure 8 shows a chilled beam 1, which differs from that in Figure 7 The cooling beam 1 shown 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 is maximum in the central region of the cooling beam 1 and decreases transversely to the transport direction 3 towards the edge regions of the cooling beam 1, the decrease being, for example, parabolic.

The in the Figures 1 to 8 Exemplary embodiments of chilled beams 1 shown can be modified in various ways. For example, the distributor chamber 9 can be omitted in each case, the spray chamber 7 being filled with coolant directly instead of via the distributor chamber 9. Alternatively, the full jet nozzles 11 can extend less or not at all into the spray chamber 7, ie the nozzle bodies 19 can be made shorter or can be omitted entirely. Furthermore, the full jet nozzles 11 in one of Three different numbers of nozzle rows 23 to 25 can be arranged.

This in Figure 8 The exemplary embodiment shown can also be modified in such a way that the outlet diameter D of the full jet nozzles 11 transversely to the transport direction 3 in a different way than that in FIG Figure 8 shown cooling beam 1 varies. For example, the outlet diameter D in the central region of the chilled beam 1 can be minimal and increase transversely to the transport direction 3 towards the edge regions of the chilled beam 1, or the outlet diameter D can be maximal in an edge region of the chilled beam 1 and transversely to the transport direction 3 to the remove the edge area opposite this edge area.

Figure 9 shows schematically from in the Figures 1 to 8 Volume flow V ₁ to V _{5 of} a coolant as a function of a position transversely to the direction of transport 3 shown cooling beam.

A first volume flow V ₁ is in the Figures 3 and 8th shown cooling beam 1 generates and decreases from a central region of the cooling beam 1 to the edge regions, the decrease being, for example, parabolic.

A second volume flow V ₂ is from the in Figure 4 shown cooling beam 1 generates and increases from a central region of the cooling beam 1 to the edge regions, the increase being parabolic, for example.

A third volume flow V ₃ is from the in Figure 5 shown cooling bar 1 generates and decreases from a first edge area to the second Ran area of the cooling bar 1 down.

A fourth volume flow V ₄ is from the in Figure 6 shown cooling beam 1 generates and takes from the second Edge area towards the first ran area of the chilled beam 1.

A fifth volume flow V ₅ is from the in Figure 7 shown cooling beam 1 is generated and is constant across the transport direction 3.

Figure 10 shows a sectional view of a further embodiment of a chilled beam 1. In this embodiment, the distributor chamber 9 is arranged below the spray chamber 7. Again, the spray chamber 7 and the distributor chamber 9 are connected to one another by a plurality of passage openings 13, and the cooling beam 1 has a plurality of full jet nozzles 11, each of which has a tubular nozzle body 19 with a cylinder axis running vertically, ie parallel to the Z axis. In this exemplary embodiment, however, the nozzle bodies 19 each run from a bottom of the distributor chamber 9 through the distributor chamber 9 into the spray chamber 7, where they each have an open end 21 through which coolant can be fed from the spray chamber 7 into the full jet nozzle 11. The full jet nozzles 11 in turn have a nozzle density that varies transversely to the transport direction 3 and can, for example, be analogous to any of those shown in FIGS Figures 1 to 6 shown embodiments can be arranged distributed.

Figure 11 shows a sectional view of a further exemplary embodiment of a cooling beam 1. In this exemplary embodiment too, the distributor chamber 9 is arranged below the spray chamber 7. The spray chamber 7 and the distributor chamber 9 are in turn connected to one another by a plurality of passage openings 13 and the cooling beam 1 has a plurality of full jet nozzles 11. The full jet nozzles 11 are led out of the spray chamber 7 on an upper side and directed straight upwards, so that they discharge coolant upwards. An in Figure 11 The cooling beam 1 shown is therefore intended to be arranged below the rolling stock 5 and to output coolant to an underside of the rolling stock 5. The Full jet nozzles 11 can in turn have a nozzle density that varies transversely to the transport direction 3.

Figure 12 shows schematically a rolling train 27 for hot rolling a rolling stock 5, which is transported in a transport direction 3 through the rolling train 27. The rolling train 27 comprises a finishing train 29 and a cooling section 31. In the finishing train 29, a plurality of rolling stands 33 are arranged one behind the other, with which the rolling stock 5 is formed. In Figure 12 two roll stands 33 are shown by way of example; However, the finishing train 29 can also have a different number of roll 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 beams 1, a temperature measuring device 37 and a control device 39. Each cooling beam 1 has a plurality of full jet nozzles 11, through which a coolant jet of a coolant with an almost constant jet diameter can be emitted to the rolling stock 5. Some chilled beams 1 are arranged one behind the other above the rolling stock 5 and emit coolant jets downwards onto 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 emit coolant jets upwards onto an underside of the rolling stock 5. In Figure 12 five cooling beams 1 arranged above and five below the rolling stock 5 are shown by way of example; however, the cooling device 35 can also have other numbers of cooling beams 1 arranged above and / or below the rolling stock 5.

At least two of the cooling beams 1, but preferably in each case at least four of the cooling beams 1 arranged above the rolling stock 5 and at least four of the cooling beams 1 arranged below the rolling stock 5, have nozzle densities and / or outlet diameters D of their full jet nozzles 11 that differ from one another transversely to the transport direction 3 ,

The remaining chilled beams 1 have a constant nozzle density like that in Figure 7 shown embodiment. The cooling bars 1 with varying nozzle densities and / or varying outlet diameters D are preferably (in relation to the transport direction 3) arranged in front of the cooling bars 1 with constant nozzle densities. It is thereby achieved that at the beginning of the cooling section 31, where the temperature of the rolling stock 5 is still very high, local temperature differences transversely to the transport direction 3 can be reduced by cooling bars 1 with nozzle densities varying transversely to the transport direction 3, while subsequent cooling beams 1 with constant nozzle densities only reduce the total temperature of the rolling stock 5 which is tempered uniformly transversely to the transport direction 3.

For example, the first four cooling beams 1 arranged above the rolling stock 5 and the first four cooling beams 1 arranged below the rolling stock 5 each comprise a cooling beam 1 with a nozzle density that is analogous to Figure 3 decreases from a central region of the chilled beam 1 to the edge regions of the chilled beam 1, a chilled beam 1 with a nozzle density that is analogous to Figure 4 increases from a central region of the chilled beam 1 to the edge regions of the chilled beam 1, a chilled beam 1 with a nozzle density that is analogous to Figure 5 from one (in Figure 5 right edge) of the first edge area of the chilled beam 1 to the (in Figure 5 left) second edge area of the cooling beam 1 decreases, and a cooling beam 1 with a nozzle density, which is analogous to Figure 6 increases from the first edge region of the cooling beam 1 to the second edge region of the cooling beam 1.

Furthermore, the chilled beams 1 arranged above the rolling stock 5 preferably each have full jet nozzles 11 and / or a spray chamber 7 and a distributor chamber 9 as shown in FIGS Figures 1 and 2 shown cooling beam 1, in order to keep coolant from these cooling beams 1 on the rolling stock 5 when the coolant supply is interrupted Reduce chilled beams 1. The cooling beams 1 arranged below the rolling stock 5 can be of simpler design, ie these cooling beams 1 can have simply designed full jet nozzles 11 without elongated nozzle bodies 19 and / or cannot be divided into a spray chamber 7 and a distribution chamber 9, since they are arranged below the rolling stock 5 Chilled beam 1 in the event of an interruption in the coolant supply to the chilled beam 1, no coolant can run onto the rolling stock 5.

The temperature measuring device 37 is preferably as in FIG Figure 12 shown arranged in front of the cooling beam 1 of the cooling device 35. In addition, a further temperature measuring device 37 can 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 transverse 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 control flow rates of coolant to the individual chilled beams 1 as a function of the temperature distribution of the temperature of the rolling stock 5 ascertained with the temperature measuring device 37 transversely to the transport direction 3. The control device 39 comprises a control unit 47, two coolant pumps 49 and a control valve 51 for each chilled beam 1.

The flow rate of coolant to one of the chilled beams 1 can be set by each control valve 51. The control valves 51 of the cooling beam 1 arranged above the rolling stock 5 are connected to one of the two coolant pumps 49, the control valves 51 of the cooling beam 1 arranged below the rolling stock 5 are connected to the other coolant pump 49. Instead of two Coolant pumps 49 can also be provided with a different number of coolant pumps 49, for example only one coolant pump 49, which is connected to all control valves 51, or more than two coolant pumps 49, which are each connected to only one control valve 51 or to a subset of the control valves 51 , Instead of the coolant pumps 49, an elevated tank filled with coolant can also be provided, 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, for example a water supply system, is already sufficient, coolant pumps 49 or an elevated tank can even be dispensed with entirely. Since the chilled beams 1 each have full jet nozzles 11, it is generally sufficient to supply the chilled beams 1 with a coolant pressure of approximately 4 bar. A typical flow rate of coolant in a chilled beam 1 is approximately 175 m ³ / h.

The control unit 47 is supplied with the measurement signals detected by the temperature measurement device 37. 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 control of the control valves 51 in order to make temperature differences in the temperature of the rolling stock 5 transverse to that Transport direction 3 by using and a suitable combination of the cooling beams 1 with varying nozzle densities and to reduce the temperature of the rolling stock 5 overall to a desired value, for example a reel temperature. The flow rates of coolant to the individual chilled beams 1 are determined by the control unit 47, for example on the basis of a model from parameters of the Rolled stock 5 calculated as its thickness, temperature and / or heat capacity.

Although the invention has been illustrated and described in detail by means of preferred exemplary embodiments, the invention is not restricted by the disclosed examples and other variations can be derived therefrom by a person skilled in the art without departing from the scope of protection of the invention.

LIST OF REFERENCE NUMBERS

1

Chilled beams

3

transport direction

5

rolling

7

spray chamber

9

distribution chamber

11

full jet

12

Kühlmittelableitvorrichtung

12.1

Coolant recovery tank

12.2

Kühlmittelableitrohr

13

Port

15

output direction

17

expenditure side

19

nozzle body

21

open end

22

outlet

23 to 25

nozzle row

27

rolling train

29

finishing line

31

cooling section

33

rolling mill

35

cooler

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

V ₁ to V ₅

flow

Claims (7)

1. Cooling bar (1) for cooling rolled stock (5) which is moved in a transporting direction (3), the cooling bar (1) comprising

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

   - a distribution chamber (9) for intermediate storage of the coolant, which is connected to the spray chamber (7) by at least one through-opening (13) for filling the spray chamber (7) with coolant from the distribution chamber (9),

   - wherein each through-opening (13) between the distribution chamber (9) and the spray chamber (7) is arranged on an upper side of the distribution chamber (9),

   - and a number of full-jet nozzles (11), which can be fed coolant from the spray chamber (7) and by which in each case a coolant jet of a coolant with a virtually constant jet diameter can be discharged in a discharging direction (15) to the rolled stock (5),

   - wherein each full-jet nozzle (11) has a tubular nozzle body (19), which has an open end (21), arranged in an upper region of the cooling bar (1) within the spray chamber (7), for feeding coolant into the full-jet nozzle (11),

   - wherein the open end (21) is arranged above the height of the upper side of the distribution chamber (9).
2. Cooling bar (1) according to Claim 1,
   characterized in that a nozzle density of the full-jet nozzles (11) varies transversely to the transporting direction (3).
3. Cooling bar (1) according to one of the preceding claims,
   characterized in that an outlet diameter (D) of the full-jet nozzles (11) varies transversely to the transporting direction (3) .
4. Cooling bar (1) according to one of the preceding claims,
   characterized in that the full-jet nozzles (11) are arranged in at least one nozzle row (23 to 25) extending transversely to the transporting direction (3).
5. Cooling bar (1) according to one of the preceding claims,
   characterized in that the full-jet nozzles (11) are arranged in a number of nozzle rows (23 to 25) extending transversely to the transporting direction (3), and in that the full-jet nozzles (11) of different nozzle rows (23 to 25) are arranged offset with respect to one another in the transporting direction (3).
6. Cooling bar (1) according to Claim 4 or 5,
   characterized in that a nozzle spacing (d) of full-jet nozzles (11) adjacent to one another of each nozzle row (23 to 25) varies.
7. Cooling bar (1) according to one of the preceding claims,
   characterized by at least one coolant-diverting device (12) for diverting away coolant that is discharged by full-jet nozzles (11) arranged in a peripheral region of the spray chamber (7).

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