EP3308868B1 - Cooling of a roll of a roll stand - Google Patents

Description

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

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

U.S. 2010/0089112 A1 discloses rigid, concave-shaped chill shells by means of which low-pressure cooling liquid is applied to rolls of a roll stand.

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

JP H06-170420 (A ) discloses a cooling device for cooling work rolls of a roll stand, which has a stationary spray bar that is slightly narrower than the narrowest strip produced with the roll stand in question, and axially displaceable spray bars for cooling only those sections of the work rolls that correspond to the width of the strip currently being rolled , having.

JP S59-156506 A discloses a method for cooling a work roll of a roll stand, in which cooling water is sprayed onto the work roll at low pressure instead of at high pressure while the application surface is increased at the same time.

WO 2014/170139 A1 discloses a spray bar for cooling rolled stock, which extends transversely to the transport direction of the rolled stock and has a central area and two edge areas, into each of which a cooling medium can be fed separately.

the DE 200 06 508 U1 , which represents the closest prior art, shows a roll stand with a roll and a cooling device for cooling the roll, the cooling device comprising a cooling beam for receiving and dispensing a coolant, the cooling beam having a plurality of cooling beams on one of the rolls facing and parallel to a roll axis of the Roller extending output side of the chilled beam has arranged nozzles through which a coolant jet of the coolant from the chilled beam can be discharged in a dispensing direction to the roller.

The invention is based on the object of specifying an improved cooling device for cooling a roll of a roll stand.

The object is achieved according to the invention by the features of claim 1 and claim 15.

Advantageous configurations of the invention are the subject matter of the dependent claims.

A roll stand according to the invention with a roll and a cooling device for cooling the roll of the roll stand comprises a cooling beam for receiving and dispensing a coolant. The chilled beam has a plurality of solid jet nozzles, which are arranged on an output side of the chilled beam that faces the roll and runs parallel to a roll axis of the roll. A coolant jet of the coolant with a constant jet diameter can be discharged from the cooling beam in a discharge direction to the roller through each full jet nozzle.

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. Solid jet nozzles generate a higher impact pressure on the roller than commonly used flat jet nozzles due to the concentrated output of the coolant at the same coolant pressure in the cooling beam. The higher upstroke pressure works 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 due to the overall large amount of coolant applied millimeters to centimeters, which consists of the impinging jets of coolant should be pierced as completely as possible in order to achieve good heat dissipation. Due to the high impact pressure of the coolant jets on the roll generated by the full jet nozzles, the coolant pressure in the cooling beam can be significantly reduced compared to the use of flat jet nozzles, whereby the energy consumption and the operating costs of the cooling device can advantageously be significantly reduced.

Since the coolant is discharged through full jet nozzles, the distance between the spray bar and the roller is not critical over a wide range and therefore does not have to be adjusted to the roller diameter. For example, the roll surface to be cooled can be between 50 mm and 500 mm away due to the coolant jets running essentially in a straight line, without the cooling effect of the coolant jets changing significantly.

Another benefit of using solid jet nozzles is the reduction in maintenance, which in turn results from the reduced coolant pressure in the chilled beam, since the coolant pressure also reduces the load and thus the wear on the nozzles.

An embodiment of the invention provides that the chilled beam is divided into at least two mutually separate coolant chambers for receiving coolant. Each coolant chamber corresponds to a partial area of the discharge side of the cooling beam, in which several solid jet nozzles are arranged, through which a coolant jet can be discharged from the coolant chamber to the roller. The subdivision of the chilled beam into several separate coolant chambers, which correspond to different sub-areas of the output side of the chilled beam, advantageously makes it possible to control the cooling effect of the sub-areas independently of one another by controlling the coolant pressures in the sub-areas and thereby the coolant flows emitted by the sub-areas independently of one another to be controlled. As a result, the cooling of the roll can advantageously be influenced as a function of location, so that regions of the roll surface that are heated to a greater extent, for example a central region of the roll surface, are cooled more than regions that are heated to a lesser extent.

A further development of the aforementioned embodiment of the invention provides that a first coolant chamber corresponds to a first partial area of the output side of the cooling beam, the first partial area being 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 partial area varies parallel to the central axis along the direction of the roll axis and is maximum along the central axis. The first partial area has the shape of a polygon, for example. The design of the first partial area which is mirror-symmetrical to the central axis takes into account that the roller is generally also heated symmetrically to the central axis. The variation in the expansion of the first partial area parallel to the central axis along the direction of the roll axis with a maximum expansion along the central axis takes into account that the roll is usually heated most in the middle and the heating of the roll decreases towards its edge regions. The corresponding design of the first sub-area therefore makes it possible to adapt the roller cooling through the first sub-area to the location-dependent thermal load on 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, the coolant supply line opening into the coolant chamber essentially perpendicularly to the direction in which the coolant is discharged. The opening of the coolant supply lines into the chilled beam, which is essentially perpendicular to the dispensing direction, enables a largely uniform pressure distribution of the coolant inside each coolant chamber. This will be beneficial a pressure drop between the full jet nozzles close to the mouth and those farther away is avoided.

A further embodiment of the invention provides that the amounts of coolant fed into the coolant chambers can be controlled independently of one another by a respective control valve and/or by a respective pump. This enables the above-mentioned mutually independent control of the cooling effect of the coolant jets emitted by the individual coolant chambers. The control of the amounts of coolant by means of control valves is particularly advantageous, for example, when an already existing, conventional coolant supply system can be used on the relevant rolling mill, for example a water supply system that usually pumps cooling water at a pressure of 4 bar. In this case, there is no need for a complex and expensive pressure boosting system to supply the roll cooling. The control of the coolant quantities by means of pumps, if necessary in conjunction with the control valves, makes it possible to switch off individual pumps or reduce the output of the pumps during rolling breaks or during rolling campaigns, in which only a low cooling capacity is required, and thus reduce energy consumption.

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

A further embodiment of the invention provides that a nozzle spacing varies along a direction parallel to the roll axis of adjacent solid jet nozzles along this direction. In this case, the distance between the nozzles is preferably smallest in a central region of the output side of the chilled beam. For example, the nozzle pitch along a direction parallel to the roll axis is between about 25 mm and about 50 mm. These configurations of the invention also make it possible to adjust the arrangement of the solid jet nozzles to the location-dependent thermal load on 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 area of the output side of the chilled beam takes into account that the central area of the roll surface is usually subjected to the greatest thermal stress.

A further embodiment of the invention provides that the solid jet nozzles are arranged in several rows of nozzles parallel to one another. This advantageously enables coolant to be applied to the roll over a large area and, in conjunction with the rotation of the roll, uniformly.

A further embodiment of the invention provides that the cooling beam has a nozzle recess for each full jet nozzle, in which the full jet nozzle is detachably fastened. This embodiment of the invention advantageously enables defective full jet nozzles to be replaced easily.

A further embodiment of the invention provides a scraper for scraping coolant from the roller, the scraper and the cooling beam being pivotable together. A scraper can advantageously prevent too much coolant from getting onto the rolling stock and/or into a roll gap through which the rolling stock is guided between two rolls and, for example, a lubricant to reduce the friction between the rolling stock and the washes off rollers. Because the stripper and the chilled beam can pivot together, no additional device is advantageously required to move the chilled beam. This in turn has the above-mentioned advantage of using full-jet nozzles that the distance between the spray bar and the roller is largely uncritical when using full-jet nozzles and therefore does not have to be adjusted to the roller diameter. Furthermore, the invention is also particularly suitable as a retrofit solution for existing rolling mills with scrapers, in which case, for example, only the conventional high-pressure spray beams have to be replaced by the cooling beams according to the invention.

Furthermore, the invention relates to a roll stand with one roll and two cooling devices, the two cooling devices being arranged on different sides of the roll. The advantages of a roll stand according to the invention with two cooling devices result from the advantages already mentioned above of a roll stand according to the invention with one cooling device.

• 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 properties, features and advantages of this invention described above, and the manner in which they are achieved, will become clearer and more clearly understood in connection with the following description of exemplary embodiments, which will be explained in more detail in connection with the drawings. show:

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

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

figure 1 1 schematically shows a roll stand 1 for rolling a rolling stock 3. The roll stand 1 comprises two rolls 5 designed as working rolls and two cooling devices 7 for each roll 5, which are arranged on different sides of the roll 5. The rolls 5 are spaced apart from one another by a roll gap 9 through which the rolling stock 3 is guided in a rolling direction 11 in order to roll the rolling stock 3 to reshape. Each cooling device 7 comprises a cooling beam 13 and a scraper 15.

Each cooling bar 13 is designed to receive and dispense a coolant. To dispense the coolant, the chilled beam 13 has a plurality of solid jet nozzles 21 arranged on an output side 19 of the chilled beam 13 that faces the respective roll 5 and runs parallel to a roll axis 17 of the roll 5, through which a coolant jet with an almost constant jet diameter emerges from the chilled beam 13 can be output to the roller 5 in an output direction 23 . The coolant can be fed into the chilled beams 13 via coolant supply lines 41, the amounts of coolant fed into the chilled beams 13 being controllable by control valves 43 and/or by pumps 45, which are frequency-controlled, for example. The coolant is water, for example.

Each scraper 15 is designed to scrape coolant from the respective roll 5 and is pivotable towards and away from the roll 5 . The cooling beam 13 and the scraper 15 of each cooling device 7 are preferably fastened to a pivoting device of the cooling device 7 so that the cooling beam 13 and the scraper 15 can be pivoted together toward the roll 5 and away from the roll 5 .

figure 2 shows a schematic perspective view of a first exemplary embodiment of a cooling beam 13 for dispensing coolant onto 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 partial area 29 to 31 of the delivery side 19, in which several solid jet nozzles 21 are arranged, through which a coolant jet can be emitted from the coolant chamber 25 to 27 in the delivery direction 23 to the roller 5. The output page 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, 36.

A first coolant chamber 25 corresponds to a first partial area 29 of the output side 19 of the chilled beam 13 which forms a middle area of the output side 19 . The first partial area 29 is mirror-symmetrical to a central axis 37 of the output side 19 of the chilled beam 13, which is perpendicular to the roller axis 17, and has the shape of a trapezium, which has two corner points, which lie on a first longitudinal side 33, and two corner points, which each lie on an end point of the lying second longitudinal side 34 has.

The solid jet nozzles 21 are arranged on the output side 19 in a plurality of nozzle rows 39 which each run parallel to the roll axis 17 . In each row of nozzles 39, a nozzle spacing d of adjacent full jet nozzles 21 varies symmetrically to the central axis 37, so that the nozzle spacing d is smallest in the middle area of the output side 19 and increases, for example parabolically, towards the edge areas of the output side 19. in figure 2 In the exemplary embodiment shown, 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 rows of nozzles 39 run equidistantly essentially over the entire extent of the delivery side 19, so that they produce a relatively uniform cooling effect on the roll surface of the roll 5.

A further development of the in figure 2 The exemplary embodiment shown provides that the rows of nozzles 39 are arranged offset from one another, so that the solid jet nozzles 21 of different rows of nozzles 39 are not arranged along directions perpendicular to the roll axis 17 . This advantageously achieves a particularly uniform cooling effect of the rows of nozzles 39 by avoiding "cooling grooves" running perpendicularly to the rows of nozzles 39, in which no coolant is discharged onto the roller 5 and thereby the cooling effect is reduced.

Furthermore, full jet nozzles 21, which are located in figure 2 are located very close to or on a boundary line between two adjacent partial areas 29 to 31, either entirely omitted or opposite to the one in figure 2 shown arrangement shifted into one of the adjoining partial areas 29 to 31, since a corresponding subdivision of the interior of the chilled beam 13 into the coolant chambers 25 to 27, for example by separating plates, runs along such a boundary line.

Each full jet nozzle 21 is detachably mounted in a nozzle recess of the cooling beam 13, for example by means of a screw connection. The solid 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, the coolant supply line 41 opening into the coolant chamber 25 to 27 essentially perpendicularly to the output direction 23 of the coolant. The cross sections of the coolant supply lines 41 each have a diameter of between 100 mm and 150 mm, for example.

The quantities of coolant that are fed into the coolant chambers 25 to 27 via the coolant supply lines 41 are independent of one another by a (in figure 2 not shown) control valve 43 and/or by one (in figure 2 not shown) pump 45 controllable. This advantageously makes it possible to adapt the amounts of coolant discharged from the coolant chambers 25 to 27 to the different thermal loads in different areas of the roll surface.

figure 3 shows an example of three of the in figure 2 illustrated chilled 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 being given as a percentage based on a nominal current.

The nominal flow 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 coolant is fed into all three coolant chambers 25 to 27 at a specific nominal pressure that is the same for all coolant chambers 25 to 27 . The first volumetric flow V ₁ runs parabolic with a maximum at the middle position y _m and decreases from the middle position y _m towards the two end regions to half the value at the middle position y _m . The reason for this course of the first volume flow V ₁ is the increase in the nozzle spacing d of the full jet nozzles 21 along the nozzle rows 39 from their center to the two ends to double the value, with a parabolic increase in the nozzle spacing d being assumed.

A second volume flow V ₂ is generated when coolant is fed into the first coolant chamber 25 at a coolant pressure that is approximately twice the nominal pressure and coolant is fed into the two other coolant chambers 26, 27 at a coolant pressure that is approximately half as high is as large as the nominal pressure.

A third volume flow V ₃ is generated when coolant is fed into the first coolant chamber 25 at a coolant pressure that is approximately half the nominal pressure, and coolant is fed into the two other coolant chambers 26, 27 with a coolant pressure that is approximately twice as high is as large as the nominal pressure.

figure 3 shows that due to different coolant pressures in the coolant chambers 25 to 27, volume flows V ₁ , V ₂ , V ₃ can be generated with a different dependency on the position y along a direction parallel to the roll axis 17, so that the volume flow V ₁ , V ₂ , V ₃ output by the chilled beam 13 can be adapted to the temperature distribution on the roll surface. 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 Figures 4 to 12 each show the output side 19 of a further exemplary embodiment of a chilled beam 13. These exemplary embodiments differ from that in figure 2 illustrated embodiment only by the shape and number of coolant chambers 25 to 27 and the corresponding partial areas 29 to 31 of the output side 19. The full jet nozzles 21 are each as in the in figure 2 illustrated embodiment arranged in several rows of nozzles 39, along which the nozzle distance d increases from the center to the two ends. Therefore, the full jet nozzles 21 in the Figures 4 to 12 not shown again. Due to the in figure 2 illustrated embodiment analogous distribution of the full jet nozzles 21 on the output side 19 can be with each of the in the Figures 4 to 12 illustrated embodiments volume flows V ₁ , V ₂ , V ₃ analogous to figure 3 generate.

The in the Figures 4 to 10 illustrated embodiments have as in figure 2 illustrated embodiment three coolant chambers 25 to 27 and corresponding sub-areas 29 to 31 of the output side 19. Also as in the in figure 2 In the exemplary embodiment shown, a first partial area 29 is mirror-symmetrical to a central axis 37, perpendicular to the roller axis 17, of the output side 19 of the chilled beam 13, and the two further partial areas 30, 31 adjoin the first partial area 29 on different sides of the central axis 37.

figure 4 shows an embodiment in which the first partial area 29 has the shape of a trapezium, which has two corner points, which lie on a first longitudinal side 33, and two corner points, which lie on the second longitudinal side 34.

figure 5 shows an embodiment in which the first partial area 29 has the shape of a triangle, which has a corner point that lies at the point of intersection of the central axis 37 with the first longitudinal side 33, and two corner points that lie on the end points of the second longitudinal side 34.

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

figure 7 shows an embodiment in which the first portion 29 has the shape of a rectangle whose corner points are on the long sides 33, 34. In this exemplary embodiment, coolant can only be discharged from a central region of the discharge side 19 by not discharging any coolant via the two outer partial regions 30 , 31 . This exemplary embodiment is therefore particularly suitable for rolling rolling stock 3 of different widths.

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

figure 9 shows an embodiment in which the first portion 29 has the shape of a hexagon, the two Corners on the first long side 33, two corners, each lying on an end point of the second long side 34, and one corner on each transverse side 35, 36.

figure 10 shows an embodiment in which the first portion 29 has the shape of a pentagon, which has a corner point that lies at the point of intersection of the central axis 37 with the first longitudinal side 33, two corner points that each lie on an end point of the second longitudinal side 34, and each has a vertex on each transverse side 35,36.

The in the Figures 11 and 12 Illustrated exemplary embodiments each have two coolant chambers 25, 26 and corresponding partial areas 29, 30 of the output side 19. Both partial areas 29 are mirror-symmetrical to a central axis 37, perpendicular to the roller axis 17, of the output side 19 of the chilled beam 13.

figure 11 shows an embodiment in which a first partial area 29 has the shape of a triangle, which has a corner point lying on the central axis 37 and two corner points, each lying on an end point of the second longitudinal side 34 .

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

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

reference list

1

mill stand

3

rolling stock

5

roller

7

cooler

9

roll gap

11

rolling direction

13

chilled beam

15

scraper

17

roller axis

19

output page

21

full jet nozzle

23

output direction

25 to 27

coolant chamber

29 to 31

subarea

33, 34

long side

35, 36

transverse side

37

central axis

39

row of nozzles

41

coolant supply line

43

control valve

45

pump

i.e

nozzle spacing

Claims (15)

1. Roll stand (1) having a roller (5) and a cooling device (7) for cooling the roller (5), the cooling device (7) comprising

   - a cooling bar (13) for receiving and discharging a coolant,

   - wherein the cooling bar (13) has multiple full-jet nozzles (21), which are arranged on a discharge side (19) of the cooling bar (13) that faces the roller (5) and runs parallel to a roller axis (17) of the roller (5), and through which full-jet nozzles a respective coolant jet of the coolant can be discharged, with a constant jet diameter, from the cooling bar (13) towards the roller (5) in a discharge direction (23),

   - wherein the discharge side (19) of the cooling bar (13) is spaced apart from the surface of the roller (5) by 50 mm to 500 mm.
2. Roll stand (1) according to Claim 1,
   characterized in that the cooling bar (13) is subdivided into at least two separate coolant chambers (25 to 27) for receiving coolant, wherein each coolant chamber (25 to 27) corresponds to a subregion (29 to 31) of the discharge side (19) of the cooling bar (13) in which multiple full-jet nozzles (21) are arranged, through which a respective coolant jet can be discharged from the coolant chamber (25 to 27) towards the roller (5).
3. Roll stand (1) according to Claim 2,
   characterized in that a first coolant chamber (25) corresponds to a first subregion (29) of the discharge side (19) of the cooling bar (13), wherein the first subregion (29) is mirrorsymmetrical with respect to a centre axis (37), which is perpendicular to the roller axis (17), of the discharge side (19) of the cooling bar (13).
4. Roll stand (1) according to Claim 2 or 3,
   characterized in that an extent of the first subregion (29) parallel to the centre axis (37) varies in the direction of the roller axis (17) and is at its greatest along the centre axis (37) .
5. Roll stand (1) according to one of Claims 2 to 4,
   characterized in that the first subregion (29) has a polygonal shape.
6. Roll stand (1) according to one of Claims 2 to 5, characterized in that each coolant chamber (25 to 27) is connected to a coolant feed line (41) for supplying coolant to the coolant chamber (25 to 27), wherein the coolant feed line (41) leads into the coolant chamber (25 to 27) substantially perpendicularly with respect to the discharge direction (23) of the coolant.
7. Roll stand (1) according to one of Claims 2 to 6, characterized in that the quantities of coolant supplied to the coolant chambers (25 to 27) can be controlled independently of one another by a respective control valve (43) and/or by a respective pump (45).
8. Roll stand (1) according to one of Claims 2 to 7, characterized by an automation system for controlling the quantities of coolant supplied to the coolant chambers (25 to 27) .
9. Roll stand (1) according to one of the preceding claims, characterized in that a nozzle distance (d) between full-jet nozzles (21) that are mutually adjacent in a direction parallel to the roller axis (17) varies in this direction.
10. Roll stand (1) according to Claim 9,
    characterized in that the nozzle distance (d) is at its smallest in a centre region of the discharge side (19) of the cooling bar (13).
11. Roll stand (1) according to Claim 9 or 10,
    characterized in that the nozzle distance (d) is between about 25 mm and about 50 mm.
12. Roll stand (1) according to one of the preceding claims, characterized in that the full-jet nozzles (21) are arranged in multiple mutually parallel nozzle rows (39).
13. Roll stand (1) according to one of the preceding claims, characterized in that, for each full-jet nozzle (21), the cooling bar (13) has a nozzle recess, in which the full-jet nozzle (21) is detachably secured.
14. Roll stand (1) according to one of the preceding claims, characterized by a stripper (15) for stripping coolant from the roller (5), wherein the stripper (15) and the cooling bar (13) can be jointly pivoted.
15. Roll stand (1) having a roller (5) and two cooling devices (7) that are arranged on different sides of the roller (5) and are intended for cooling the roller (5), the cooling devices (7) each comprising

    - a cooling bar (13) for receiving and discharging a coolant,

    - wherein the cooling bar (13) has multiple full-jet nozzles (21), which are arranged on a discharge side (19) of the cooling bar (13) that faces the roller (5) and runs parallel to a roller axis (17) of the roller (5), and through which full-jet nozzles a respective coolant jet of the coolant can be discharged, with a constant jet diameter, from the cooling bar (13) towards the roller (5) in a discharge direction (23),

    - wherein the discharge side (19) of the cooling bar (13) is spaced apart from the surface of the roller (5) by 50 mm to 500 mm.

Images