EP3308868A1 - Cooling of a roll of a roll stand - Google Patents

Abstract

The invention relates to a cooling device (7) for cooling a roll (5) of a roll stand (1). The cooling device (7) comprises a cooling beam (13) for receiving and discharging a coolant, wherein the cooling beam (13) has a plurality of output side (19) facing one of the roller (5) and parallel to a roller axis (17) of the roller (5) ) of the cooling bar (13) arranged full jet nozzles (21) through which a respective coolant jet of the coolant with a nearly constant beam diameter from the cooling beam (13) in an output direction (23) to the roller (5) can be output.

Description

The invention relates to a cooling device for cooling a roll of a roll stand.

Roll stands for rolling rolling stock have rolls which are cooled with a cooling liquid, usually with cooling water.

US 2010/0089112 A1 discloses rigid, concave cooling shells by means of which low-pressure coolant is applied to rolls of a rolling stand.

DE 10 2009 053 074 A1 discloses a flow cooling of work rolls of a rolling stand by means of movable, articulated cooling shells. In this case, the pressurization of the cooling liquid takes place predominantly under low pressure with the aid of the cooling shells, while for generating a sufficient cooling effect, cooling liquid is additionally applied under high pressure.

JP H06-170420 (A ) discloses a cooling apparatus for cooling work rolls of a rolling stand which has a stationary spray bar which is slightly narrower than the narrowest strip produced by the respective rolling stand, and axially displaceable spray bars for cooling only those sections of the work rolls corresponding to the width of the currently rolled strip , having.

JP S59-156506 A discloses a method for cooling a work roll of a rolling mill, in which cooling water is sprayed onto the work roll instead of with high pressure and with a simultaneously increased application area.

WO 2014/170139 A1 discloses a spray bar for cooling rolling stock, which extends transversely to the transport direction of the rolling stock and has a central region and two edge regions, in each of which a cooling medium is separately fed.

The invention has for its object to provide an improved cooling device for cooling a roll of a roll stand.

The object is achieved by the features of claim 1.

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

A cooling device according to the invention for cooling a roll of a roll stand comprises a cooling beam for receiving and discharging a coolant. The cooling beam has a plurality of full jet nozzles which are arranged on a discharge side of the cooling beam facing the roll and running parallel to a roll axis of the roll. Through each full-jet nozzle, a coolant jet of the coolant with a nearly constant jet diameter can be output from the cooling beam in an output direction to the roll.

A full-jet nozzle is understood to be a nozzle through which a substantially straight coolant jet having a virtually constant jet diameter can be dispensed. Full-jet nozzles produce a higher impact pressure on the roller than commonly used flat-jet nozzles due to the concentrated discharge of the coolant at the same coolant pressure in the cooling beam. The higher impact pressure has a positive effect on the cooling effect directly on the roll surface, because there is always a certain coolant film with a thickness of typically several millimeters to centimeters due to the total large amount of coolant applied, of the impinging coolant jets should be pierced as completely as possible in order to achieve a good heat dissipation. As a result of the high impact pressure of the coolant jets on the roller produced by the full jet nozzles, the coolant pressure in the cooling beam can be significantly reduced compared with the use of flat jet nozzles, whereby the energy consumption and operating costs of the cooling device can advantageously be significantly reduced.

In addition, since the discharge of the coolant is carried out by full jet nozzles, the distance of the spray bar from the roll in a wide range is not critical and therefore does not have to be adapted to the roll diameter. For example, due to the substantially rectilinear coolant jets, the roll surface to be cooled can be between 50 mm and 500 mm, without the cooling effect of the coolant jets changing appreciably.

Another advantage of the use of full jet nozzles is the reduction of the maintenance effort, which in turn results from the reduced coolant pressure in the chilled beam, since with the coolant pressure and the load and thus the wear of the nozzles are reduced.

An embodiment of the invention provides that the cooling beam is divided into at least two separate coolant chambers for receiving coolant. Each coolant chamber corresponds to a portion of the discharge side of the cooling beam, in which a plurality of full-jet nozzles are arranged, through each of which a coolant jet from the coolant chamber to the roller can be dispensed. The subdivision of the cooling beam into a plurality of separate coolant chambers, which correspond to different subregions of the discharge side of the cooling beam, advantageously makes it possible to control the cooling effect of the subregions independently of one another by the coolant pressures in the subregions and thereby the coolant flows emitted by the subregions independently of one another to be controlled. As a result, the cooling of the roller can advantageously be influenced in a location-dependent manner so that more heated areas of the roller surface, for example a middle area of the roller surface, are cooled more strongly than less heated areas.

A further embodiment of the aforementioned embodiment of the invention provides that a first coolant chamber corresponds to a first portion of the discharge side of the cooling beam, wherein the first portion is mirror-symmetrical to a central axis of the output side of the cooling beam perpendicular to the roll axis. For example, an extension of the first portion varies parallel to the central axis along the direction of the roll axis and is maximum along the central axis. The first subregion has, for example, the shape of a polygon. The mirror-symmetrical design of the first sub-region, taken into account with respect to the center axis, takes into account that the roller is generally also heated symmetrically with respect to the central axis. The variation of the extent of the first portion parallel to the central axis along the direction of the roll axis with a maximum extension along the center axis takes into account that the roll is heated most in the middle, as a rule, and the heating of the roll decreases to its edge regions. The corresponding design of the first subarea therefore makes it possible to adapt the roller cooling through the first subarea of the location-dependent thermal loading of the roller.

A further embodiment of the invention provides that each coolant chamber is connected to a coolant supply line for feeding coolant into the coolant chamber, wherein the coolant supply line opens into the coolant chamber substantially perpendicular to the discharge direction of the coolant. The substantially perpendicular to the dispensing direction Münden the coolant supply lines in the chilled beam allows a substantially uniform pressure distribution of the coolant inside each coolant chamber. This will be advantageous avoided a pressure gradient between close to the mouth and muzzle remote full jet nozzles.

A further embodiment of the invention provides that the amounts of coolant fed into the coolant chambers are independently controllable by a respective control valve and / or by one pump. This allows the already mentioned above independent control of the cooling effect of the output from the individual coolant chambers coolant jets. The control of the coolant quantities by control valves is for example particularly advantageous if an already existing, conventional coolant supply system can be used at the relevant rolling mill, for example a water supply system which usually conveys cooling water at a pressure of 4 bar. In this case, it is possible to dispense with a complicated and expensive pressure increase system for supplying the roll cooling. Controlling the quantities of coolant by means of pumps, if necessary in conjunction with the control valves, makes it possible to shut down individual pumps or to reduce the power of the pumps in rolling breaks or in rolling campaigns where only a small cooling capacity is required, thereby reducing energy consumption.

A further embodiment of the invention provides an automation system for controlling the quantities of coolant fed into the coolant chambers. As a result, advantageously, volume flows of the coolant output from the coolant chambers to the roll can be automatically controlled in order to adapt the volume flows to a temperature distribution on the roll surface. The quantities of coolant fed into the coolant chambers are controlled by the automation system, preferably by controlling the abovementioned control valves and / or pumps.

A further embodiment of the invention provides that a nozzle spacing varies along a direction parallel to the roll axis of adjacent full jet nozzles along this direction. In this case, the nozzle spacing is preferably the lowest in a central region of the output side of the cooling beam. For example, the nozzle spacing is between about 25 mm and about 50 mm along a direction parallel to the roll axis. These embodiments of the invention also make it possible to adapt the arrangement of the full-jet nozzles to the location-dependent thermal loading of the roll surface by varying the nozzle spacing along a direction parallel to the roll axis in accordance with this thermal load. A minimum nozzle spacing in the central region of the discharge side of the cooling bar takes into account that the middle area of the roll surface is usually thermally loaded the most.

A further embodiment of the invention provides that the full-jet nozzles are arranged in several mutually parallel nozzle rows. This advantageously allows a large-area and in connection with the rotation of the roller uniform application of coolant to the roller.

A further embodiment of the invention provides that the cooling beam for each jet nozzle has a nozzle recess in which the jet nozzle is releasably secured. This embodiment of the invention advantageously allows easy replacement of defective full jet nozzles.

A further embodiment of the invention provides a scraper for stripping coolant from the roller, wherein the scraper and the cooling beam are pivoted together. By a scraper can be advantageously prevented that too much coolant to the rolling stock and / or in a roll gap, through which the rolling stock is guided between two rollers passes, and for example, a lubricant to reduce the friction between the rolling stock and the Washes off rolls. Due to the joint pivoting of the scraper and the cooling beam is advantageously no additional device for moving the cooling beam required. In this case, in turn, the already mentioned above advantage of using full jet nozzles, that the use of full jet nozzles, the distance of the spray bar from the roller in a wide range is not critical and therefore does not need to be adapted to the roll diameter. Furthermore, the invention is also particularly suitable as a retrofit solution for existing rolling mills with scrapers, for example, only the conventional high-pressure spray bar must be replaced by the chilled beam according to the invention.

A rolling stand according to the invention comprises a roll and two cooling devices according to the invention, the two cooling devices being arranged on different sides of the roll. The advantages of a roll stand according to the invention result from the above-mentioned advantages of a cooling device according to the invention.

• FIG 1 schematisch ein Walzgerüst mit Kühlvorrichtungen,
• FIG 2 eine schematische perspektivische Darstellung eines ersten Ausführungsbeispiels eines Kühlbalkens,
• FIG 3 von dem in Figur 2 dargestellten Kühlbalken ausgegebene Volumenströme eines Kühlmittels in Abhängigkeit von einer Position,
• FIG 4 die Ausgabeseite eines zweiten Ausführungsbeispiels eines Kühlbalkens,
• FIG 5 die Ausgabeseite eines dritten Ausführungsbeispiels eines Kühlbalkens,
• FIG 6 die Ausgabeseite eines vierten Ausführungsbeispiels eines Kühlbalkens,
• FIG 7 die Ausgabeseite eines fünften Ausführungsbeispiels eines Kühlbalkens,
• FIG 8 die Ausgabeseite eines sechsten Ausführungsbeispiels eines Kühlbalkens,
• FIG 9 die Ausgabeseite eines siebten Ausführungsbeispiels eines Kühlbalkens,
• FIG 10 die Ausgabeseite eines achten Ausführungsbeispiels eines Kühlbalkens,
• FIG 11 die Ausgabeseite eines neunten Ausführungsbeispiels eines Kühlbalkens, und
• FIG 12 die Ausgabeseite eines zehnten Ausführungsbeispiels eines Kühlbalkens.

The above-described characteristics, features, and advantages of this invention, as well as the manner in which they will be achieved, will become clearer and more clearly understood in connection with the following description of exemplary embodiments which will be described in detail in conjunction with the drawings. Showing:

• FIG. 1 schematically a roll stand with cooling devices,
• FIG. 2 a schematic perspective view of a first embodiment of a cooling bar,
• FIG. 3 from the in FIG. 2 illustrated cooling bars output volume flows of a coolant as a function of a position,
• FIG. 4 the output side of a second embodiment of a cooling beam,
• FIG. 5 the discharge side of a third embodiment of a cooling bar,
• FIG. 6 the discharge side of a fourth embodiment of a cooling bar,
• FIG. 7 the output side of a fifth embodiment of a cooling bar,
• FIG. 8 the output side of a sixth embodiment of a cooling beam,
• FIG. 9 the discharge side of a seventh embodiment of a cooling beam,
• FIG. 10 the discharge side of an eighth embodiment of a cooling beam,
• FIG. 11 the output side of a ninth embodiment of a cooling beam, and
• FIG. 12 the output side of a tenth embodiment of a cooling beam.

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

FIG. 1 1 schematically shows a rolling stand 1 for rolling a rolling stock 3. The rolling stand 1 comprises two rolls 5 designed as work rolls and for each roll 5 two cooling devices 7 arranged on different sides of the roll 5. The rollers 5 are spaced from each other by a nip 9 through which the rolling stock 3 is passed in a rolling direction 11 to the rolling stock. 3 reshape. Each cooling device 7 comprises a cooling beam 13 and a scraper 15.

Each chilled beam 13 is configured to receive and dispense a coolant. To dispense the coolant, the cooling bar 13 has a plurality of full-jet nozzles 21 arranged on a respective roller 5 and parallel to a roller shaft 17 of the roller 5, through which in each case a coolant jet having a nearly constant jet diameter from the cooling beam 13 in an output direction 23 to the roller 5 can be output. The coolant can be fed into the cooling bars 13 via coolant supply lines 41, the quantities of coolant fed into the cooling bars 13 being controllable by control valves 43 and / or by pumps 45 which are frequency-controlled, for example. The coolant is, for example, water.

Each scraper 15 is designed to scrape off coolant from the respective roller 5 and to pivot towards the roller 5 and away from the roller 5. Preferably, the chilled beam 13 and the scraper 15 of each cooling device 7 are fixed to a pivoting device of the cooling device 7 so that the chilled beam 13 and the scraper 15 are pivotable together toward the roller 5 and away from the roller 5.

FIG. 2 shows a schematic perspective view of a first embodiment of a cooling bar 13 for dispensing coolant on a roller 5. The cooling beam 13 is divided into three separate coolant chambers 25 to 27 for receiving coolant. Each coolant chamber 25 to 27 corresponds to a portion 29 to 31 of the discharge side 19, in which a plurality of full jet nozzles 21 are arranged, through which a respective coolant jet from the coolant chamber 25 to 27 in the discharge direction 23 to the roller 5 can be dispensed. The output side 19 has the shape of a rectangle with two to the Roll axis 17 parallel longitudinal sides 33, 34 and two perpendicular transverse sides 35, 36th

A first coolant chamber 25 corresponds to a first portion 29 of the discharge side 19 of the cooling bar 13, which forms a central region of the discharge side 19. The first portion 29 is mirror-symmetrical to a vertical to the roll axis 17 central axis 37 of the discharge side 19 of the cooling bar 13 and has the shape of a trapezium, the two vertices lying on a first longitudinal side 33, and two vertices, each on an endpoint of second longitudinal side 34 lie.

The full-jet nozzles 21 are arranged on the output side 19 in a plurality of rows of nozzles 39, each extending parallel to the roll axis 17. In this case, in each nozzle row 39, a nozzle spacing d of adjacent full-jet nozzles 21 varies symmetrically with respect to the center axis 37, so that the nozzle spacing d is lowest in the central region of the output side 19 and increases towards the edge regions of the output side 19, for example parabolically. Im in FIG. 2 illustrated embodiment, the nozzle spacing d at the ends of each nozzle row 39 is twice as large as in the middle of the nozzle row 39. The nozzle spacing d varies for example between 25 mm and 50 mm. The nozzle rows 39 extend equidistantly over substantially the entire extent of the discharge side 19, so that they produce a relatively uniform cooling effect on the roller surface of the roller 5.

A redesign of the in FIG. 2 shown embodiment provides that the nozzle rows 39 are arranged offset from one another, so that the full-jet nozzles 21 of different nozzle rows 39 are not arranged along perpendicular to the roll axis 17 directions. This advantageously a particularly uniform cooling effect of the nozzle rows 39 is achieved by perpendicular to the rows of nozzles 39 extending "cooling grooves" are avoided, in which no coolant is discharged to the roller 5 and thereby the cooling effect is reduced.

Further, full jet nozzles 21, which are in FIG. 2 are located very close to or on a boundary line between two adjacent subregions 29 to 31, either completely omitted or opposite to in FIG. 2 shown arranged arrangement in one of the adjoining subregions 29 to 31, since along such a boundary line a corresponding subdivision of the interior of the cooling beam 13 in the coolant chambers 25 to 27, for example by separating plates runs.

Each full-jet nozzle 21 is detachably mounted, for example by a screw connection, in a nozzle recess of the cooling beam 13. The full jet nozzles 21 each have, for example, a nozzle cross section with a minimum diameter of about 4 mm.

Each coolant chamber 25 to 27 is connected to a coolant supply line 41 for feeding coolant into the coolant chamber 25 to 27, wherein the coolant supply line 41 opens into the coolant chamber 25 to 27 substantially perpendicular to the discharge direction 23 of the coolant. The cross sections of the coolant supply lines 41, for example, each have a diameter between 100 mm and 150 mm.

The coolant quantities fed into the coolant chambers 25 to 27 via the coolant supply lines 41 are provided independently of each other by a respective one (in FIG. 2 not shown) control valve 43 and / or by a respective (in FIG. 2 not shown) pump 45 controllable. This advantageously makes it possible to adapt the quantities of coolant dispensed from the coolant chambers 25 to 27 to the different thermal loads in different areas of the roller surface.

FIG. 3 shows by way of example three of the in FIG. 2 shown cooling bars 13 output volume flows V ₁ , V ₂ , V _{3 of} the coolant as a function of a position y along a direction parallel to the roll axis 17, the volume flows V ₁ , V ₂ , V _{3 are given} in percent relative to a rated current.

The nominal current is the value of a first volume flow V ₁ at a middle position y _m . The first volume flow V ₁ is generated when in all three coolant chambers 25 to 27 coolant with a specific, for all coolant chambers 25 to 27 matching nominal pressure is fed. The first volume flow V ₁ runs parabolically with a maximum at the middle position y _m and decreases from the middle position y _m to the two end regions towards half of the value at the middle position y _m . The reason for this flow of the first volumetric flow V ₁ is the increase of the nozzle pitch d of the full-jet nozzles 21 along the nozzle rows 39 from their center to the two ends to twice the value, assuming a parabolic increase of the nozzle pitch d.

A second volume flow V ₂ is generated when in the first coolant chamber 25 coolant with a coolant pressure which is about twice as large as the nominal pressure is fed and in the other two coolant chambers 26, 27 each coolant with a coolant pressure, which is about half is large as the nominal pressure is fed.

A third volumetric flow V ₃ is produced when coolant having a coolant pressure which is approximately half the rated pressure is fed into the first coolant chamber 25, and coolant having a coolant pressure approximately twice as high is introduced into the two other coolant chambers 26, 27 is large as the nominal pressure is fed.

FIG. 3 shows that by different coolant pressures in the coolant chambers 25 to 27 flow rates V ₁ , V ₂ , V ₃ can be generated with a different dependence on the position y along a direction parallel to the roll axis 17, so that the output from the chilled beam 13 volume flow V ₁ , V ₂ , V _{3 of} the temperature distribution on the roll surface can be adjusted. The coolant pressure in each coolant chamber 25 to 27 is adjusted by the respective control valve 43 and / or by the respective pump 45.

The FIGS. 4 to 12 each show the output side 19 of a further embodiment of a cooling bar 13. These embodiments differ from the in FIG. 2 illustrated embodiment only by the shape and number of the coolant chambers 25 to 27 and the corresponding portions 29 to 31 of the output side 19. The full jet nozzles 21 are each as in the FIG. 2 illustrated embodiment arranged in a plurality of nozzle rows 39, along which the nozzle spacing d increases from the middle to the two ends. Therefore, the full jet nozzles 21 are in the FIGS. 4 to 12 not shown again. Due to the to the in FIG. 2 illustrated embodiment, the distribution of full jet nozzles 21 on the output side 19 can be with each of the in the FIGS. 4 to 12 illustrated embodiments, volume flows V ₁ , V ₂ , V ₃ analogous to FIG. 3 produce.

The in the FIGS. 4 to 10 illustrated embodiments have as in FIG. 2 illustrated embodiment each have three coolant chambers 25 to 27 and corresponding portions 29 to 31 of the output side 19. Likewise in the in FIG. 2 1, a first partial region 29 is mirror-symmetrical to a central axis 37 of the discharge side 19 of the cooling bar 13 which is perpendicular to the roll axis 17, and the two further partial regions 30, 31 adjoin the first partial region 29 on different sides of the central axis 37.

FIG. 4 shows an embodiment in which the first portion 29 has the shape of a trapezoid, the two vertices lying on a first longitudinal side 33, and two vertices lying on the second longitudinal side 34 has.

FIG. 5 shows an embodiment in which the first portion 29 has the shape of a triangle having a vertex lying in the intersection of the central axis 37 with the first longitudinal side 33, and two vertices lying on the end points of the second longitudinal side 34.

FIG. 6 shows an embodiment in which the first portion 29 has the shape of a triangle having a corner point which lies in the intersection of the central axis 37 with the first longitudinal side 33, and two corner points which lie on the second longitudinal side 34.

FIG. 7 shows an embodiment in which the first portion 29 has the shape of a rectangle whose vertices lie on the long sides 33, 34. In this embodiment, an output of coolant can be generated only from a central portion of the discharge side 19 by not emitting refrigerant through the two outer portions 30, 31. Thus, this embodiment is particularly suitable for rolling rolling 3 different widths.

FIG. 8 shows an embodiment in which the second portion 30 and the third portion 31 each have the shape of a rectangle, which has a corner on the first longitudinal side 33, a corner point which lies on an end point of the first longitudinal side 33, and a corner point on a transverse side 35, 36 is located, has.

FIG. 9 shows an embodiment in which the first portion 29 has the shape of a hexagon, the two

Corner points on the first longitudinal side 33, two corner points, each lying on an end point of the second longitudinal side 34, and each having a corner point on each transverse side 35, 36 has.

FIG. 10 shows an embodiment in which the first portion 29 has the shape of a pentagon having a vertex located in the intersection of the central axis 37 with the first longitudinal side 33, two vertices, each lying on an end point of the second longitudinal side 34, and respectively has a corner on each transverse side 35, 36.

The in the FIGS. 11 and 12 illustrated embodiments each have two coolant chambers 25, 26 and corresponding to subregions 29, 30 of the output side 19. Both partial regions 29 are mirror-symmetrical to a central axis 37, which is perpendicular to the roller axis 17, of the output side 19 of the cooling beam 13.

FIG. 11 shows an embodiment in which a first portion 29 has the shape of a triangle, which has a corner point which lies on the central axis 37, and two corner points, which lie respectively on an end point of the second longitudinal side 34.

FIG. 12 shows an embodiment in which a first portion 29 has the shape of a pentagon having a vertex lying on the central axis 37, two vertices, each lying on an end point of the second longitudinal side 34, and one vertex on each transverse side 35, 36 has.

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 may occur to those skilled in the art be derived therefrom without departing from the scope of the invention.

LIST OF REFERENCE NUMBERS

1

rolling mill

3

rolling

5

roller

7

cooler

9

nip

11

rolling direction

13

Chilled beams

15

scraper

17

roll axis

19

expenditure side

21

full jet

23

output direction

25 to 27

Coolant chamber

29 to 31

subregion

33, 34

long side

35, 36

transverse side

37

central axis

39

nozzle row

41

Coolant supply

43

control valve

45

pump

d

nozzle distance

Claims (15)

Cooling device (7) for cooling a roller (5) of a rolling stand (1), the cooling device (7) comprising a cooling beam (13) for receiving and discharging a coolant, - Wherein the cooling beam (13) a plurality of on one of the roller (5) facing and parallel to a roll axis (17) of the roller (5) extending output side (19) of the cooling bar (13) arranged full jet nozzles (21), through each one Coolant jet of the coolant with a nearly constant beam diameter from the cooling beam (13) in an output direction (23) to the roller (5) can be output. Cooling device (7) according to claim 1,
characterized in that the cooling beam (13) is divided into at least two separate coolant chambers (25 to 27) for receiving coolant, each coolant chamber (25 to 27) to a portion (29 to 31) of the output side (19) of the cooling beam (13) corresponds, in which a plurality of full-jet nozzles (21) are arranged, through which a respective coolant jet from the coolant chamber (25 to 27) to the roller (5) can be output. Cooling device (7) according to claim 2,
characterized in that a first coolant chamber (25) corresponds to a first subregion (29) of the output side (19) of the cooling beam (13), the first subregion (29) being mirror-symmetrical to a central axis (37) perpendicular to the roll axis (17). the output side (19) of the cooling bar (13). Cooling device (7) according to claim 2 or 3,
characterized in that an extension of the first portion (29) parallel to the central axis (37) varies along the direction of the roller axis (17) and is maximum along the central axis (37). Cooling device (7) according to one of claims 2 to 4,
characterized in that the first portion (29) has the shape of a polygon. Cooling device (7) according to one of claims 2 to 5,
characterized in that each coolant chamber (25 to 27) is connected to a coolant supply line (41) for supplying coolant into the coolant chamber (25 to 27), the coolant supply line (41) being substantially perpendicular to the discharge direction (23) of the coolant in the coolant chamber (25 to 27) opens. Cooling device (7) according to one of claims 2 to 6,
characterized in that the coolant quantities fed into the coolant chambers (25 to 27) are independently controllable by a respective control valve (43) and / or by a pump (45). Cooling device (7) according to one of claims 2 to 7, characterized by an automation system for controlling the amounts of coolant fed into the coolant chambers (25 to 27). Cooling device (7) according to one of the preceding claims,
characterized in that a nozzle spacing (d) varies along a direction parallel to the roll axis (17) in the direction of adjacent full-jet nozzles (21) along this direction. Cooling device (7) according to claim 9,
characterized in that the nozzle spacing (d) in a central region of the output side (19) of the cooling bar (13) is the lowest. Cooling device (7) according to claim 9 or 10,
characterized in that the nozzle spacing (d) is between about 25 mm and about 50 mm. Cooling device (7) according to one of the preceding claims,
characterized in that the full jet nozzles (21) are arranged in a plurality of mutually parallel rows of nozzles (39). Cooling device (7) according to one of the preceding claims,
characterized in that the cooling beam (13) for each jet nozzle (21) has a nozzle recess in which the jet nozzle (21) is releasably attached. Cooling device (7) according to one of the preceding claims,
characterized by a scraper (15) for stripping coolant from the roller (5), wherein the scraper (15) and the cooling beam (13) are pivotable together. Roll stand (1), comprising a roller (5) and two cooling devices (7) each formed according to one of the preceding claims, wherein the two cooling devices (7) are arranged on different sides of the roller (5).

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