EP3395463B2 - Cooling of a product which is to be rolled - Google Patents

Description

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

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

WO 2014/170139 A1 discloses a cooling device for a flat rolled stock with several spray bars that extend transversely to a transport direction of the rolled stock. The spray bars each have two outer regions, viewed transversely to the transport direction, and a middle region arranged between the two outer regions, wherein a liquid cooling medium can be fed into the regions 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 strip, wherein at least one cooling device with nozzles is provided for applying a coolant to the slab or strip. The nozzles are arranged and/or controlled in such a way that a coolant is applied, in particular, to positions at which an increased 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 strips or metal sheets conveyed on a conveyor line, in particular hot-rolled steel strips at the outlet of a rolling mill, with at least one cooling bar extending substantially over the width of the conveyor line for applying cooling liquid to the metal strip 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, at the outlet of a rolling mill with at least two nozzles arranged distributed over the width of the metal strip, wherein a control and regulating device controls a cooling fluid flow emerging from each nozzle individually depending on a detected temperature of a width section of the metal strip which is assigned to the respective nozzle.

The JP 2011-194417 shows a cooling beam for cooling a rolling stock moved in a transport direction, the cooling beam comprising - a spray chamber that can be filled with a coolant, - a distribution 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 distribution chamber, - each passage opening between the distribution chamber and the spray chamber being arranged on an upper side of the distribution chamber, - and several nozzles that can be fed with coolant from the spray chamber, through each of which a coolant jet of a coolant can be discharged in a discharge direction to the rolling stock, - each nozzle having a tubular nozzle body that 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 is based on the object of specifying a device for cooling a rolling stock moved in a transport direction 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 transport direction.

The object is achieved according to the invention by a cooling beam having the features of claim 1.

Advantageous embodiments of the invention are the subject of the subclaims.

A cooling beam designed according to an embodiment of the invention for cooling a rolling stock moved in a transport direction comprises a spray chamber that can be filled with a coolant and a plurality of full-jet nozzles that can be fed with coolant from the spray chamber, through each of which a coolant jet of a coolant with an almost constant jet diameter can be output to the rolling stock in an output direction. Each full-jet nozzle has a tubular nozzle body that 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. A distribution chamber is provided for temporarily storing the coolant, which is connected to the spray chamber by at least one passage opening for filling the spray chamber with coolant from the distribution chamber. Each passage opening is arranged between the distribution chamber and the spray chamber on an upper side of the distribution 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 distribution chamber.

This design of a cooling beam enables the delivery of coolant 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 cooling beam from the rolling stock is not critical over a wide range, typically up to about 1500 mm, due to the essentially straight coolant jets and can therefore be varied within this range without negatively affecting the cooling effect, since the cooling effect essentially only occurs at the immediate impact points of the coolant jets.

Another advantage of full jet nozzles compared to the commonly used cone or flat jet nozzles is 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 concentrated 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 rolling stock surface because, due to the large amount of coolant applied, there is always a certain coolant film there with a thickness of typically several millimeters to centimeters, which should be penetrated as completely as possible by the impinging coolant jets in order to achieve a high relative speed of the coolant to the rolling stock surface and thus good heat dissipation. In addition, even with very close nozzle arrangements, the coolant jets from full jet nozzles do not influence each other, as can be the case with cone or flat jet nozzles.

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

Furthermore, due to their compact and stable design, full-jet nozzles are much less sensitive to mechanical influences than cone or flat-jet nozzles, which is an advantage in the event of a strip break in the rolling stock with a striking strip end, for example.

The division of the cooling beam into a spray chamber and a distribution chamber and the design of the cooling beam with full-jet nozzles is particularly advantageous when the cooling beam is arranged above the rolling stock and the coolant is discharged downwards onto the rolling stock, i.e. when the discharge direction at least approximately coincides with the direction of gravity. In this case, the design according to the invention advantageously enables a relatively small amount of coolant to flow out of the cooling beam and be discharged onto the rolling stock when the cooling of the rolling stock is interrupted after the coolant supply to the cooling beam has been interrupted, while a large amount of coolant remains in the cooling beam. As a result, when cooling is resumed, the cooling beam can be filled with coolant more quickly due to the smaller volume to be filled than if the cooling beam is completely emptied when cooling is interrupted. This is achieved by temporarily storing 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 when arranged on an upper side of the distribution chamber, the distribution chamber remains completely or at least partially filled with coolant if the coolant supply is interrupted. 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 cooling beam, so that if the coolant supply is interrupted, coolant can only flow from the region of the spray chamber located above the open ends of the nozzle bodies and from the nozzle bodies themselves, while the remaining volume of the spray chamber remains filled with coolant.

The design of a cooling beam with a distribution chamber also advantageously makes it possible to reduce pressure gradients and flow turbulences in the spray chamber 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, so that all full-jet nozzles of a cooling beam are subjected to essentially the same pressure and an essentially laminar flow is achieved in the spray chamber.

One design of a cooling 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 is understood to mean 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 in the cooling effect of the cooling beam transversely to the transport direction is achieved, which can advantageously reduce temperature differences of the rolled material transversely to the transport direction.

In a cooling beam according to the invention, the full-jet nozzles are arranged in at least one row of nozzles running transversely to the transport direction. Furthermore, the full jet nozzles are arranged in several rows of nozzles running transversely to the transport direction, and the full jet nozzles of different rows of nozzles are arranged offset from one another in the transport direction. This means an arrangement of the full jet nozzles of different rows of nozzles 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 rows of nozzles running in the transport direction. This offset arrangement of the full jet nozzles of different rows of nozzles advantageously achieves a particularly uniform cooling effect of the rows of nozzles by avoiding "cooling grooves" running in the transport direction in which no coolant is released onto the rolled material.

Furthermore, the nozzle spacing of adjacent full-jet nozzles in each nozzle row can vary. This advantageously makes it possible to reduce temperature differences in the temperature of the rolled material that vary transversely to the transport direction particularly well. For example, the nozzle spacing can be smallest in a central region of the output side of the cooling beam and increase towards the edge regions. Such a distribution of the full-jet nozzles can advantageously be used to cool a rolled material whose temperature is highest in a central region and decreases towards the edge regions.

A further embodiment of a cooling beam according to the invention provides at least one coolant discharge device for discharging coolant that 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 thus 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 12 eine Walzstraße zum Warmwalzen eines Walzguts mit einer Kühlvorrichtung zum Kühlen des Walzguts.

The above-described properties, features and advantages of this invention, as well as the manner in which they are achieved, will become clearer and more readily understood in connection with the following description of embodiments, which are explained in more detail in connection with the drawings, in which:

• FIG 1 a perspective view of a first embodiment of a cooling beam,
• FIG 2 a cross-sectional view of the Figure 1 shown chilled beam,
• FIG 3 a view from below of the Figure 1 shown chilled beams,
• FIG 4 a bottom view of a second embodiment of a cooling beam,
• FIG 5 a bottom view of a third embodiment of a cooling beam,
• FIG 6 a bottom view of a fourth embodiment of a cooling beam,
• FIG 7 a bottom view of a fifth embodiment of a cooling beam,
• FIG 8 a bottom view of a sixth embodiment of a cooling beam,
• FIG 9 from in the Figures 1 to 8 Volume flows of a coolant output by the cooling beam shown as a function of a position,
• FIG 10 a sectional view of a seventh embodiment of a cooling beam,
• FIG 12 a rolling mill for hot rolling a rolled product with a cooling device for cooling the rolled product.

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

The Figures 1 to 3 show schematically a first embodiment of a cooling beam 1 for cooling a rolling stock 5 moved in a transport direction 3 (see Figure 12 ). Figure 1 a perspective view of the cooling beam 1, Figure 2 shows a sectional view of the chilled beam 1 and Figure 3 shows a view from below of the cooling 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 runs vertically upwards, 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 rolled material 5.

The cooling beam 1 comprises a spray chamber 7, a distribution chamber 9, several full-jet nozzles 11 and two optional coolant discharge devices 12. The spray chamber 7 and the distribution chamber 9 are each designed as a hollow space with a longitudinal axis running transversely to the transport direction 3 in the X direction. The distribution chamber 9 has a substantially 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 that essentially has the shape of the Greek capital letter gamma, with the horizontal section of the gamma running above the distribution chamber 9.

The spray chamber 7 and the distribution chamber 9 are connected to each other by several passage openings 13. The passage openings 13 are arranged one behind the other transversely to the transport direction 3 in the X direction. an upper side of the distribution chamber 9. The distribution chamber 9 can be filled with a coolant, for example with cooling water, from the outside via a coolant inlet (not shown). The spray chamber 7 can be filled with the coolant from the distribution chamber 9 via the passage openings 13.

Through each full-jet nozzle 11, a coolant jet of the coolant with an almost constant jet diameter can be output 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. opposite to the Z direction. The output side 17 in this case is the underside of the cooling beam 1. Each full-jet nozzle 11 has a tubular nozzle body 19 with a vertical longitudinal axis, i.e. parallel to the Z axis. The nozzle body 19 runs 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 arranged in an upper region of the spray chamber 7 above the height of the top of the distribution chamber 9 and through which coolant from the spray chamber 7 can be fed into the full-jet nozzle 11. The nozzle bodies 19 are, for example, hollow-cylindrical or taper 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 between 3 mm and 12 mm.

This design of the cooling beam 1 has the advantageous 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 can only flow to the rolling stock 5 from the area of the spray chamber 7 located above the open ends 21 of the nozzle bodies 19 and from the nozzle bodies 19 themselves, 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 that varies transversely to the transport direction 3, wherein the nozzle density is maximum in a central region of the cooling beam 1 and decreases transversely to the transport direction 3 towards the edge regions of the cooling beam 1 (see Figure 3 ). The full-jet nozzles 11 are arranged in three rows of nozzles 23 to 25 running transversely to the transport direction 3, wherein the full-jet nozzles 11 of different rows of nozzles 23 to 25 are arranged offset from one another in the transport direction 3. The variation in 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 row of nozzles 23 to 25, wherein the nozzle spacing d is minimal in the middle region of the cooling beam 1 and increases transversely to the transport direction 3 towards the edge regions of the cooling beam 1. For example, the nozzle spacing d increases parabolically from the middle region to each edge region of the cooling beam 1. This advantageously makes it possible to reduce temperature differences in the rolling stock 5 when 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 distance d varies, for example, between 25 mm and 70 mm.

The optional coolant drainage devices 12 are each arranged under an edge region of the spray chamber 7 and are designed to collect and drain 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 reach the corresponding edge region of the rolling stock 5 and cool the edge region of the rolling stock 5 too much. For this purpose, each coolant drainage device 12 has a coolant collecting container 12.1 and a coolant drainage pipe 12.2. The coolant drainage pipe 12.2 is arranged on an underside of the coolant collecting container 12.1 and serves to drain coolant collected in the coolant collecting container 12.1.

The Figures 4 to 7 each show a further 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 the one shown in the Figures 1 to 3 The cooling beam 1 shown in the drawing is only characterized by the distribution of the full jet nozzles 11 transverse to the transport direction 3. As in the Figures 1 to 3 In the cooling beam 1 shown, the full-jet nozzles 11 are arranged in three rows of nozzles 23 to 25 running transversely to the transport direction 3, wherein the full-jet nozzles 11 of different rows of nozzles 23 to 25 are arranged offset from one another in the transport direction 3.

Figure 4 shows a cooling beam 1 in which the nozzle spacing d of adjacent full-jet nozzles 11 of each nozzle row 23 to 25 decreases from the middle region of the cooling beam 1 transversely to the transport direction 3 to the edge regions of the cooling beam 1 (for example parabolically), so that the nozzle density of the full-jet nozzles 11 increases from the middle region of the cooling beam 1 to the edge regions of the cooling beam 1. This advantageously reduces temperature differences of the rolling stock 5 when the temperature of the rolling stock 5 increases from a middle region of the rolling stock 5 to the edge regions of the rolling stock 5.

Figure 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 are spaced at different distances from one in Figure 5 right-hand edge region of the cooling beam 1 to the left, so that the nozzle density in the right-hand edge region has a nozzle density maximum. This advantageously reduces temperature differences of the rolling stock 5 when the temperature of the rolling stock 5 from the right-hand edge region of the rolling stock 5 to the left-hand edge area of the rolling stock 5 decreases.

Figure 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 are spaced at different distances from one in Figure 6 left-hand edge region of the cooling beam 1 to the right, so that the nozzle density in the left-hand edge region has a nozzle density maximum. Temperature differences of the rolling stock 5 can thereby 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 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 and the nozzle density is also constant transversely to the transport direction 3. Such a cooling beam 1 therefore causes uniform cooling of the rolling stock 5 transversely to the transport direction 3.

Figure 8 shows a cooling beam 1, which differs from the one in Figure 7 shown cooling beam 1 only 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 middle region of the cooling beam 1 and decreases transversely to the transport direction 3 towards the edge regions of the cooling beam 1, whereby the decrease can be parabolic, for example.

The Figures 1 to 8 The embodiments of cooling beams 1 shown can be modified in various ways. For example, the distributor chamber 9 can be omitted in each case, with 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 far 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 can be arranged in a number of nozzle rows 23 to 25 other than three.

The Figure 8 The embodiment shown can also be modified in such a way that the outlet diameter D of the full jet nozzles 11 transverse to the transport direction 3 is different from the embodiment shown in Figure 8 shown cooling beam 1. For example, the outlet diameter D can be minimal in the middle region of the cooling beam 1 and increase transversely to the transport direction 3 towards the edge regions of the cooling beam 1, or the outlet diameter D can be maximal in an edge region of the cooling beam 1 and decrease transversely to the transport direction 3 towards the edge region opposite this edge region.

Figure 9 shows schematically from the Figures 1 to 8 Volume flows V ₁ to V ₅ of a coolant emitted by the cooling beam shown as a function of a position transverse to the transport direction 3.

A first volume flow V ₁ is generated by the Figures 3 and 8 shown cooling beam 1 and decreases from a central region of the cooling beam 1 towards the edge regions, with the decrease being, for example, parabolic.

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

A third volume flow V ₃ is supplied by the Figure 5 shown cooling beam 1 and decreases from a first edge region to the second edge region of the cooling beam 1.

A fourth volume flow V ₄ is supplied by the Figure 6 shown cooling beam 1 and decreases from the second edge region to the first edge region of the cooling beam 1.

A fifth volume flow V ₅ is supplied by the Figure 7 shown cooling beam 1 and is constant transversely to the transport direction 3.

Figure 10 shows a sectional view of a further 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 connected to one another by several passage openings 13 and the cooling beam 1 has several full-jet nozzles 11, each of which has a tubular nozzle body 19 with a cylinder axis running vertically, i.e. parallel to the Z axis. In this embodiment, however, the nozzle bodies 19 each run 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 through which coolant from the spray chamber 7 can be fed into the full-jet nozzle 11. The full-jet nozzles 11 again have a nozzle density that varies transversely to the transport direction 3 and can, for example, be analogous to any of the nozzles shown in the Figures 1 to 6 shown embodiments can be arranged distributed.

Figure 12 shows schematically a rolling mill 27 for hot rolling a rolling stock 5, which is transported in a transport direction 3 through the rolling mill 27. The rolling mill 27 comprises a finishing mill 29 and a cooling section 31. In the finishing mill 29, several rolling stands 33 are arranged one behind the other, with which the rolling stock 5 is formed. In Figure 12 Two rolling stands 33 are shown as an example; however, the finishing train 29 can also have a different number of rolling stands 33. The cooling section 31 is connected to the finishing train 29 and has a cooling device 35 for cooling the rolling stock 5.

The cooling device 35 comprises several cooling beams 1, a temperature measuring device 37 and a control device 39. Each cooling beam 1 has several 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 cooling 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 cooling 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 By way of example, five cooling beams 1 arranged above and five below the rolling stock 5 are shown; 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 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 vary differently from one another transversely to the transport direction 3.

The remaining cooling beams 1 have a constant nozzle density as in Figure 7 shown embodiment. The cooling beams 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 beams 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 transverse to the transport direction 3 can be reduced by cooling beams 1 with nozzle densities varying transverse to the transport direction 3, while subsequent cooling beams 1 with constant nozzle densities only reduce the overall temperature of the rolling stock 5, which is uniformly tempered 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 which is analogous to Figure 3 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 which is analogous to Figure 4 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 which is analogous to Figure 5 from one (in Figure 5 right) first edge area of the chilled beam 1 to the (in Figure 5 left) second edge area of the cooling beam 1, and a cooling beam 1 with a nozzle density that is analogous to Figure 6 from the first edge region of the chilled beam 1 to the second edge region of the chilled beam 1.

Furthermore, the cooling beams 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 as in the Figures 1 and 2 shown cooling beams 1 in order to reduce the flow of coolant from these cooling beams 1 onto the rolling stock 5 in the event of an interruption in the coolant supply to the cooling beams 1. The cooling beams 1 arranged beneath the rolling stock 5 can be of a simpler design, ie these cooling beams 1 can have simply designed full-jet nozzles 11 without elongated nozzle bodies 19 and/or can not be divided into a spray chamber 7 and a distribution chamber 9, since no coolant can flow onto the rolling stock 5 from the cooling beams 1 arranged beneath the rolling stock 5 in the event of an interruption in the coolant supply to the cooling beams 1.

The temperature measuring device 37 is preferably as in 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 cooling 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 control flow rates of coolant to the individual cooling beams 1 depending on the temperature distribution of the temperature of the rolling stock 5 transverse to the transport direction 3 determined by the temperature measuring device 37. The control device 39 comprises a control unit 47, two coolant pumps 49 and a control valve 51 for each cooling beam 1.

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

The measurement signals recorded by the temperature measuring device 37 are fed to the control unit 47. The coolant pumps 49 and control valves 51 can be controlled by the control unit 47. The control unit 47 calculates the flow rates of coolant to the individual cooling beams 1 - in particular to those with varying nozzle densities - depending on the temperature distribution recorded by the temperature measuring device 37 and sets them by controlling the control valves 51 in order to compensate for temperature differences in the temperature of the rolling stock 5 transversely to the 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 cooling beams 1 are calculated by the control unit 47, for example, using a model of parameters of the rolling stock 5 such as its thickness, temperature and/or heat capacity.

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

list of reference symbols

1

chilled beams

3

transport direction

5

rolled goods

7

spray chamber

9

distribution chamber

11

full-jet nozzle

12

coolant drainage device

12.1

coolant collection tank

12.2

coolant drain pipe

13

passage opening

15

output direction

17

output page

19

nozzle body

21

open ending

22

outlet opening

23 to 25

nozzle row

27

rolling mill

29

finishing line

31

cooling section

33

rolling mill

35

cooling device

37

temperature measuring device

39

control device

47

control unit

49

coolant pump

51

control valve

d

nozzle spacing

D

outlet diameter

X, Y, Z

Cartesian coordinates

V1 to V5

volume flow

Claims (5)

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 a number of through-openings (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 the through-openings (13) are arranged on an upper side of the distribution chamber (9) one behind another transversely to the transporting direction (3),

   - and a number of full-jet nozzles (11), which can be fed with coolant from the spray chamber (7) and through 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)

   - and the nozzle body (19) extends inside the spray chamber (7) from a bottom of the spray chamber (7) to the open end (21) of the nozzle body (19),

   - and wherein the full-jet nozzles (11) each comprise an outlet opening (22), the outlet diameter (D) of which is between 3 mm and 12 mm,

   - and the full-jet nozzles (11) are arranged in a number of nozzle rows (23 to 25) extending transversely to the transporting direction (3) and 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).
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 the 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 a nozzle spacing (d) of full-jet nozzles (11) adjacent to one another of each nozzle row (23 to 25) varies.
5. 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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