EP3307448B1 - Method and device for controlling a parameter of a rolled stock - Google Patents

Description

The invention relates to a method and an apparatus for controlling a parameter, for example the profile or the flatness of a strip-shaped rolling stock, in particular a metal strip, rolled by means of a roll stand. A generic method and a generic device are from document DE 10 2012 202 340 A1 known.

In the prior art, such methods and devices are known in principle. The basic principle of such a regulation is described below with reference to FIG. 13 described in more detail.

FIG. 13 shows a known cascade control for regulating, for example, the profile or the flatness of a metal strip on the setting of the thermal roll bale contour. For the sake of simplicity, only parameters will be discussed below instead of distinguishing between profile and flatness.

For the purpose of the parameter control is according to FIG. 13 First, the actual value, ie the actual parameter of the rolling stock at the output of the controlled system, ie in particular measured at the output of a rolling stand after rolling. After measuring with the aid of the parameter measuring device 110, the actual parameter P _{actual of} the rolling stock is fed to a parameter comparison device 120 and compared there with a predetermined desired parameter P _Soll . The difference between the setpoint and the actual value is referred to as the parameter control deviation eP. This parameter deviation eP is used by a desired current determining device 130 for determining a desired value Q _abSoll for the current of the heat to be dissipated by the roller. In addition to the parameter deviation eP, the desired current determining means 130 typically also takes into account other predetermined ones Requirements for the rolls from the rolling process for determining the target value Q _abSoll or an equivalent value. In a heat flow comparator 140, this previously determined setpoint value Q _abSoll for the flow of heat removed from the roll is compared with the actual value Q _abIst for the flow of heat to be dissipated by the roll, in order to calculate the difference in the form of a so-called Heat flow control deviation eQ to calculate. The actual value Q _abIst for the current of the heat to be dissipated by the roller is determined directly or indirectly with the aid of a corresponding actual current measuring device 170. The rolling stand with the rollers 300 for rolling the rolling stock 200 represents the controlled system 180 in FIG FIG. 13 , Further shows FIG. 13 a controller 150, which is designed to generate a control signal s in response to the received heat flow control deviation e Q. The control signal is used to control an actuator 160 so that the heat flow control deviation is as possible zero. In the prior art, typically the volumetric flow or the pressure of the cooling medium for roll cooling in the roll stand is used as manipulated variable, wherein in particular the volume flow or the pressure of the cooling medium is adjusted by means of suitable actuators 165 as a function of the actuating signal s.

When used in the art, coupled with a control cooling is usually a spray cooling. Their disadvantage lies in the low heat transfer between the roller and the coolant. For optimal cooling results, a large amount of coolant must be circulated.

A possibility known in the prior art for removing an amount of heat from a roll of a roll stand is the use of so-called cooling shells. These are circular in cross section Trays whose curvature is adapted to the curvature or the diameter of the roll to be cooled.

The use of cooling shells for roll cooling is known, for example, from the German patent applications DE 10 2012 216 570 A1 , of the DE 10 2012 202 340 , of the DE 10 2009 053 073 or the European patent specification EP 2 114 584 B1 ,

To vary the amount of heat dissipated known from the prior art: the change in the gap height h between the cooling shell and roller (technologically changes the pressure or the flow rate of the coolant in the gap), the direct change of pressure or volume flow of the Coolant and the change in the coolant temperature.

The change in the gap height h is structurally very complex. The exact measurement of the gap height for an active integration into a control is difficult to realize and has therefore not been implemented in practice.

The change in pressure / volumetric flow has proven to be ideal for presetting in practical operation, but as a flexible actuator of a control, efficiency must continue to increase.

The change in the coolant temperature is as an actuator of a control technically conceivable but too slow, this is very costly.

Based on this prior art, the invention is based on the object, an alternative method and an alternative device for controlling a parameter of a rolled strip with the aid of a rolling mill.

This object is procedurally achieved by the method claimed in claim 1. This is characterized in that the actuating signal is a cooling shell assigned to a roll of the roll stand, wherein the cooling shell is variable in its length of action in the circumferential direction of the roll, and in that the action length of the cooling shell in the circumferential direction of the roll is adjusted with the aid of the control signal Dependence of the parameter control deviation is suitably set. Suitable here means that the parameter control deviation becomes zero as far as possible.

The heat flow can not be measured directly. Therefore, as far as is spoken in the text or the figures of a measurement of the heat flow or a measuring device for the heat flow, thus a computational determination of the heat flow meant by evaluation of measured temperature differences, here between the inlet and the outlet of the coolant.

The claimed variation of the length of action of the cooling shell in the circumferential direction of the roll provides a simple, fast and cost-effective, because more energy-efficient way to vary the amount of heat to be dissipated by the roll.

The cooling shell typically has a cross section in the form of a portion of a circular arc for covering a surface area of the roll.

According to a first exemplary embodiment, the determination of the actuating signal has the following sub-steps: determination of a desired value for the current of the heat to be dissipated by the roller from the previously determined parameter deviation and optionally taking into account further requirements from the rolling process to the cooling of the roller; Determining the actual current of the heat actually removed from the roll; Determining a heat flow control deviation as the difference between the target value and the actual value for the Current of heat to be dissipated by the roller; and determining the control signal for adjusting the length of action of the cooling shell in the circumferential direction in accordance with the heat flow control deviation, which in turn is dependent on the parameter control deviation. The aim of the cascade control according to the invention is that in addition to the parameter deviation and the heat flow control deviation is zero.

The length of action of the cooling shell in the circumferential direction is increased when the desired value of the dissipated heat flow is greater than the actual value, and vice versa. The length of action of the cooling shell in the circumferential direction can remain unchanged if the desired value of the heat flow is equal to the actual value.

For concrete realization of the change in the length of action of the cooling shell in the circumferential direction of the roll, the invention essentially proposes three different embodiments:
According to a first embodiment, the cooling shell is divided into at least a first and a second cooling shell segment, each having a cross section in the form of a portion of a circular arc for covering a surface region of the roll. To set the length of action of the cooling shell in the circumferential direction of the roll, the first and the second cooling shell segments are displaced relative to one another in the circumferential direction in accordance with the actuating signal. In particular, this results in an at least partial overlapping of the first and second cooling shell segments.

A second embodiment provides that the cooling shell is formed of flexible material which allows adjusting the length of action of the cooling shell in the circumferential direction of the roll by bending at least parts of the cooling shell away from the roll or towards the roll or by winding or unwinding the roll flexible material in accordance with the control signal.

According to a third embodiment, the cooling shell on at least one rotatable flap, which allows the setting of the length of action of the cooling shell in the circumferential direction in that the flap is opened or closed in accordance with the control signal.

The parameters considered in the context of the present invention are typically physical quantities, which are considered in the width direction of the rolling stock. Specifically, the parameter may be the profile of the rolling stock in the width direction or the distribution of the flatness of the rolling stock in the width direction.

The process can be carried out during the ongoing operation of a rolling stand, preferably / but also in rolling breaks. In both cases, the method advantageously makes it possible to remove a defined heat flow from the roll.

Device technology, the above object is achieved by the subject matter of claim 8. The advantages of this solution correspond to the advantages mentioned above with respect to the claimed method.

In order to optimize the amount of heat to be dissipated by the roller over its axial length, d. H. To be able to achieve in the axial direction over the width direction of the rolling stock in dependence on the desired distribution of the heat to be dissipated by the roller, the present invention further provides that a plurality of cooling shells in the axial direction of the roller are arranged side by side and these individual cooling shells individually in their Impact length in the circumferential direction of the roller are adjustable.

Further embodiments of the method and the device according to the invention are the subject of the dependent claims.

Figur 1

ein Regelschemata gemäß der vorliegenden Erfindung zum Regeln eines Parameters eines Walzgutes;

Figur 2

eine erste Ausführungsform für die erfindungsgemäße Kühlschale mit eingestellter kurzer Wirkungslänge und mit erster Variante für den Aktuator;

Figur 3

die erste Ausführungsform der Kühlschale gemäß Figur 2 mit eingestellter großer Wirkungslänge;

Figur 4

die erste Ausführungsform für die erfindungsgemäße Kühlschale mit eingestellter kurzer Wirkungslänge und mit zweiter Variante für den Aktuator;

Figur 5

die erste Ausführungsform gemäß Figur 4 mit eingestellter großer Wirkungslänge;

Figur 6

eine zweite Ausführungsform für die erfindungsgemäße Kühlschale mit eingestellter kurzer Wirkungslänge;

Figur 7

die zweite Ausführungsform gemäß Figur 6 mit eingestellter großer Wirkungslänge;

Figur 8

eine dritte Ausführungsform für die erfindungsgemäße Kühlschale mit einer ersten Einstellungsvariante;

Figur 9

die dritte Ausführungsform für die Kühlschale in einer zweiten Einstellungsvariante;

Figur 10

die dritte Ausführungsform für die Kühlschale in einer dritten Einstellungsvariante;

Figur 11

die dritte Ausführungsform der Kühlschale mit einer fünften Einstellungsvariante;

Figur 12

eine Draufsicht auf eine Walze mit einer Mehrzahl von in axialer Walzenrichtung nebeneinander angeordneten einzelnen Kühlschalen; und

Figur 13

ein Regelschemata zur Regelung eines Parameters eines Walzgutes gemäß dem Stand der Technik

zeigt.The description is a total of 13 figures attached, where

FIG. 1

a control schemes according to the present invention for controlling a parameter of a rolling stock;

FIG. 2

a first embodiment of the cooling shell according to the invention with adjusted short length of action and with the first variant for the actuator;

FIG. 3

the first embodiment of the cooling shell according to FIG. 2 with set large impact length;

FIG. 4

the first embodiment of the cooling shell according to the invention with adjusted short length of action and with a second variant for the actuator;

FIG. 5

the first embodiment according to FIG. 4 with set large impact length;

FIG. 6

a second embodiment of the cooling shell according to the invention with adjusted short length of action;

FIG. 7

the second embodiment according to FIG. 6 with set large impact length;

FIG. 8

a third embodiment of the cooling shell according to the invention with a first adjustment variant;

FIG. 9

the third embodiment for the cooling shell in a second setting variant;

FIG. 10

the third embodiment for the cooling shell in a third setting variant;

FIG. 11

the third embodiment of the cooling shell with a fifth setting variant;

FIG. 12

a plan view of a roller having a plurality of juxtaposed in the axial direction of the roll individual cooling shells; and

FIG. 13

a control schemes for controlling a parameter of a rolling stock according to the prior art

shows.

The invention will be described below with reference to the above FIGS. 1 to 12 described in detail in the form of embodiments. In all figures, the same technical elements are designated by the same reference numerals.

FIG. 1 shows a cascade control for controlling a parameter of a metal strip, for example, to control its profile or its flatness. Regarding the basic mode of operation of the cascade control, reference is made to the description of the FIG. 13 in the introduction of the present description.

In contrast to the known cascade control according to FIG. 13 sees the cascade control according to the invention according to FIG. 1 a special actuator 160 before. The actuator 160 is a cooling shell, which is circular in cross section. The cooling shell is spaced, placed against the surface of a roll to be cooled in a rolling mill, so that to set a cooling gap for durchzuleitendes coolant between the cooling shell and the roll surface. The cooling shell is formed in its cross section preferably complementary to the outer contour or to the cross section of the roller.

The cooling shell according to the invention is designed and adjustable in the circumferential direction of the roll with the aid of an actuator 165 in its action length. With the aid of the control signal s generated by the controller 150, the action length of the cooling shell 160 in the circumferential direction of the roll is suitably set as a function of the heat flow control deviation e Q. In this context, suitable means that the heat flow control deviation e Q becomes zero as far as possible. In turn, the heat flow control deviation e Q is in turn dependent on the parameter deviation eP, as discussed with reference to FIG FIG. 13 described. The regulation according to the invention should, in addition to the heat flow control deviation and the parameter control deviation as possible to zero.

For this purpose, the action length of the cooling shell 160 in the circumferential direction of the roll is increased if the target value Q _abSoll of the heat flow to be _delivered by the roll is greater than the measured actual value Q _{ab Ist of} the heat flow, and vice versa. The length of action of the cooling shell in the circumferential direction, on the other hand, can remain unchanged if the target value Q _abSoll of the heat flow to be delivered by the roll is equal to the actual value Q _{abIst of} the heat flow delivered.

FIG. 2 shows a first embodiment of the cooling shell according to the invention. Accordingly, the cooling shell 160 at least a first and a second cooling shell segment 161 and 162, each having a cross-section in shape a portion of a circular arc for covering a surface area of the roller. With the help of the actuator 165, which is in the in FIG. 2 shown first variant is designed as a hydraulic cylinder, the two cooling shell segments 161, 162 in the circumferential direction of the roller 300 in accordance with the control signal s relative to each other are shifted to adjust in this way the entire length of action b of the cooling shell 160 in accordance with the control signal s suitable. The action length b is always in the present description by the in FIG. 2 and the following figures represented angle or the corresponding arc length represented. The reference numeral A denotes the axis of rotation of the roller 300 and the reference numeral D whose direction of rotation during rolling of the rolling stock 200, which moves in the rolling direction WR.

In FIG. 2 It can also be seen that the two cooling-plate segments 161, 162 are each arranged at a distance from the outer surface of the roller 300, so that a cooling gap is formed between the cooling-plate segments and the surface of the roller 300. The cooling gap 180 is fed with cooling medium 400, which flows through the cooling gap in the direction of the arrow or in the opposite direction. The cooling effect is essentially determined by the length of action b of the cooling shell 160 or of the cooling shell segments 161, 162. The greater the effect length b, the greater the cooling capacity, ie the more heat can be removed from the roll 300. FIG. 2 shows the first embodiment of the cooling shell 160 with a relatively short effective length b, because the two cooling shell segments 161, 162 at the in FIG. 2 overlap position shown largely or strongly.

FIG. 3 on the other hand shows the first embodiment with the first variant for the actuator 165 in a working position in which the two cooling-cup segments 161 and 162 with respect to the in FIG. 2 overlap less shown working position and in which therefore the effect length b is increased.

FIG. 4 shows the first embodiment of the cooling shell with a second variant for the actuator 165. Unlike the first variant, the actuator or the displacement device 165 according to FIG. 4 more complicated. The displacement device comprises a rotatably mounted wheel 165-1 and an associated drive device 165-2 for rotationally driving the wheel. The wheel 165-1 in turn is coupled to the second cooling shell segment 162, for example by coupling element 165-3, by frictional engagement or positive engagement such that a rotational movement of the wheel 165-1 the displacement of the second cooling shell segment 162 in the circumferential direction of the roller 300 and relative to the first cooling shell segment 161 causes. FIG. 4 shows the cooling shell 160 with the two cooling-cup segments 161, 162 in a working position with a relatively short effective length b.

FIG. 5 on the other hand shows the first embodiment of the cooling shell with the second variant of the displacement device 165 in a working position with increased effective length b.

In all FIGS. 2 to 5 concerning the first embodiment, the first cooling-cup segment 161 may be arranged stationarily with respect to the roller 300.

FIG. 6 shows a second embodiment of the cooling shell 160 according to the invention, wherein it is formed of a flexible material. The actuator 165 is formed in this case as a bending device or as winding and unwinding for adjusting the length of action b of the cooling shell 160 in the circumferential direction of the roller 300. Specifically, the actuator 165 is used, for example, to roll-like winding the flexible cooling shell 160, in this way the length of action b of the cooling gap 180 to make relatively small.

FIG. 7 shows the cooling shell 160 with compared to FIG. 6 large impact length b, which was achieved by the fact that the actuator 165 has unwound the flexible material of the cooling shell and thus increased the cooling shell.

FIG. 8 shows a third embodiment of the cooling shell 160 according to the invention, wherein it has at least one, but typically a plurality of rotatable flaps 163. An actuator 165, not shown here, is then configured to adjust the length of action of the cooling shell 160 in the circumferential direction of the roll 300 by opening or closing at least one of the flaps 163 in accordance with the control signal s.

The FIGS. 8 to 11 each show different variants for influencing the length of action b of the cooling shell 160 by individually opening individual flaps 163. The flaps form part of the surface of the cooling shell 160 and therefore limit the cooling gap 180 at least in the closed state.

FIG. 12 shows a top view of the roller 300 with employee cooling shell 160. It can be seen that the cooling shell 160 of a plurality N, here N = 7, Teilkühlschalen 160-n with n = 1 to n = N, which in the axial direction of to be cooled roller 300 are arranged side by side. The one in here FIG. 12 Actuator 165, not shown, is configured to suitably individually adjust the effective length of each one of the n cooling cups 160-n in the circumferential direction of the roller 300 in accordance with the control deviation eQ represented by the actuating signal s. The heat flow control deviation eQ generally represents - and so does the in FIG. 12 shown embodiment - the distribution of the heat to be delivered by the roller 300 in the axial direction of the roll or in the width direction B of the rolled material 200. The widths of the individual partial cooling shells 160-n in the axial direction may be individually different; They are in FIG. 12 denoted by the reference symbols a, b, c and d. The Teilkühlschalen 160-n can also be a common have integral first cooling shell segment 161, so that only the second cooling shell segments 162-n in their length of action in the circumferential direction of the roller 300 are variably adjustable, as indicated by the vertical double arrows in FIG. 12 is indicated.

FIG. 12 however, is not limited to the embodiment of the cooling shells 160 according to the first embodiment. Rather, that is in FIG. 12 illustrated basic principle of the individual adjustability of the effective lengths b over the axial widths of the roller with all three described in the present description embodiments for the cooling shell 160 realized.

LIST OF REFERENCE NUMBERS

140

Heat flux comparator

150

regulator

160

actuator

160-n

cooling trays

161

Cooling shell segment

162-n

Cooling shell segment

163

rotatable flap

165

actuator

165-1

rotatably mounted wheel

165-2

driving means

165-3

coupling element

170

Actual current-measuring device

180

cooling gap

200

rolling

300

roller

b

Action length of the cooling gap

eP

Parameter deviation

s

actuating signal

P

parameter

P _is

If parameters

P _target

Target parameters

( Q is _off )

Actual power

( Q _abSoll )

Target current

(e Q )

Heat flow-control error

Q

heat flow

WR

Rolling direction of the rolling stock

A

Rotary axis roller

D

Direction of rotation roller

B

Width of the rolling stock

Claims (17)

1. Method for regulating a parameter (P), for example of the profile or the planarity, of a strip-shaped rolling material (200) rolled with the help of a roll stand, comprising the following steps:

   measuring the actual parameter P_Ist of the rolling material (200) after a rolling process;

   comparing the actual parameter P_Ist with a predetermined target parameter (P_Soll) for the rolling material and determining a difference (eP) between the actual parameter and the target parameter as a parameter regulating difference (eP);

   determining a setting signal (s) for activation of at least one setting element (160) in dependence on the parameter regulating difference (eP), wherein the setting element (160) is a cooling shell associated with a roll (300) of the roll stand;

   characterised in that

   the cooling shell (160) is constructed to be variable in the effective length (b) thereof in circumferential direction of the roll; and

   the effective length (b) of the cooling shell in circumferential direction (b) is suitably set in dependence on the parameter regulating difference (eP) with the help of the setting signal (s).
2. Method according to claim 1, characterised in that the determination of the setting signal (s) comprises the following sub-steps:

   - determining a target value (Q̇_abSoll) for the flow of the heat, which is to be dissipated from the roll (300), from the previously determined parameter regulating difference (eP) and optionally with consideration of further requirements from the rolling process of the cooling of the roll;

   - determining the actual flow (Q̇_abIst) of the actual heat dissipated from the roll (300);

   - determining a heat-flow regulating difference (eQ̇) as a difference between the target value (Q̇_abSoll) and the actual value (Q̇_abIst) for the flow of the heat to be dissipated from the roll (300); and

   - determining the setting signal (s) for setting the effective length (b) of the cooling shell (160) in circumferential direction in accordance with the heat flow regulating difference (eQ̇), which in turn is dependent on the parameter regulating difference (eP).
3. Method according to claim 1 or 2, characterised in that
   the effective length (b) of the cooling shell (160) in circumferential direction is increased when the target value (Q̇_abSoll) of the heat flow is greater than the actual value (Q̇_abIst) of the heat flow;
   the effective length (b) of the cooling shell in circumferential direction remains unchanged when the target value (Q̇_abSoll) of the heat flow is equal to the actual value (Q̇_abIst) of the heat flow; or
   the effective length (b) of the cooling shell in circumferential direction is reduced when the target value (Q̇_abSoll) of the heat flow is less than the actual value (Q̇_abIst) of the heat flow.
4. Method according to any one of the preceding claims, characterised in that the cooling shell (160) comprises at least a first and second cooling shell segment (161, 162), which each have a cross-section in the form of a section of an arc for covering a surface region of the roll, and, for setting the effective length (b) of the cooling shell in circumferential direction of the roll (300), the first and second cooling shell segments are displaced relative to one another in circumferential direction in accordance with the setting signal (s), preferably are overlapped with one another at least partly.
5. Method according to any one of claims 1 to 3, characterised in that the cooling shell (160) is formed from a flexible material which enables setting of the effective length (b) of the cooling shell in circumferential direction of the roll by bending of at least parts of the cooling shell away from the roll (300) or towards the roll (300) or by winding up or unwinding the flexible material in accordance with the setting signal.
6. Method according to any one of claims 1 to 3, characterised in that the cooling shell (160) comprises at least one rotatable flap (163) which enables setting of the effective length (b) of the cooling shell in circumferential direction of the roll by opening or closing the flap in accordance with the setting signal.
7. Method according to one of claims 2 and 3, characterised in that the heat flow (Q) is the distribution of the heat flow in width direction of the rolling material and the parameter is the profile or the distribution of the planarity in width direction of the rolling material.
8. Method according to any one of the preceding claims, characterised in that the method is carried out in a pause in rolling.
9. Device for regulating a parameter of a strip-shaped rolling material rolled with the help of a roll stand, comprising:

   a parameter measuring device (110) for determining the actual parameter (P_Ist) of the rolling material after a rolling process;

   a parameter comparison device (120) for determining a difference between the actual parameter (P_Ist) and a predetermined target parameter (P_soll) as parameter regulating difference (eP); and

   a regulator (150) for determining a setting signal (s) for activating at least one setting element (160) in dependence on the parameter regulating difference (eP), wherein the setting element (160) is a cooling shell associated with a roll of the roll stand;

   characterised in that

   the cooling shell is constructed with a variable effective length in circumferential direction of the roll; and

   an actuator (165) is provided for suitable setting of the effective length of the cooling shell (160) in circumferential direction of the roll in accordance with the parameter regulating difference (eP) represented by the setting signal (s).
10. Device according to claim 9, further characterised in that

    - a target-flow determining device (130) is provided for determining a target value (Q̇_abSoll) for the flow of the heat, which is to be dissipated from the roll, from the parameter regulating difference (eP) and optionally with consideration of further requirements from the rolling process of the cooling of the roll;

    - an actual-flow measuring device (170) is provided for determining the actual value (Q̇_abIst) for the flow of the heat actually dissipated from the roll;

    - a heat-flow comparison device (140) is provided for determining a heat flow regulating difference (eQ̇) as a difference between the target value (Q̇_abSoll) and the actual value (Q̇_abIst) for the flow of heat to be dissipated from the roll; and

    the regulator (150) is configured to generate the setting signal (s) for setting the effective length (b) of the cooling shell (160) in circumferential direction of the roll in accordance with the heat-flow regulating difference (eQ̇), wherein the heat-flow regulating difference (eQ̇) is in turn dependent on the parameter regulating difference (eP).
11. Device according to claim 9 or 10, characterised in that the cooling shell (160) comprises at least a first and second cooling shell segment (161, 162), which each have a cross-section in the form of a section of an arc for covering a surface region of the roll, and the actuator (165) is constructed in the form of a displacing device for displacing the first and second cooling shell segments in circumferential direction of the roll relative to one another, wherein the first and second cooling shell segments can overlap at least in part.
12. Device according to claim 11, characterised in that the first cooling shell segment (161) is arranged to be stationary, but at a spacing from the surface of the roll (300); and the displacing device (165) is constructed for displacing the second cooling shell segment in circumferential direction of the roll relative to the first cooling shell segment.
13. Device according to claim 11 or 12, characterised in that the displacing device (165) is constructed in the form of a hydraulic cylinder.
14. Device according to any one of claims 11, 12 and 13, characterised in that the displacing device (165) comprises a rotatably mounted wheel (165-1) and a drive device (165-2) for rotational driving of the wheel, wherein the wheel is so disposed in engagement with the second cooling shell segment (162), for example by friction couple or by mechanically positive couple, that a rotational movement of the wheel (165-1) produces displacement of the second cooling segment (162) in circumferential direction.
15. Device according to claim 9 or 10, characterised in that the cooling shell (160) is formed from a flexible material and the actuator (165) is constructed as a bending device or as a winding-up and unwinding device for setting the effective length (b) of the cooling shell in circumferential direction of the roll by bending at least parts of the cooling shell away from the roll or towards the roll or by winding up or unwinding the flexible material in accordance with the setting signal.
16. Device according to claim 9 or 10, characterised in that the cooling shell (160) comprises at least one rotatable flap (163) and the actuator (165) is constructed for setting the effective length of the cooling shell in circumferential direction of the roll by opening or closing the flap in accordance with the setting signal.
17. Device according to claim 10, characterised in that the heat flow (Q) is the distribution of the heat flow in width direction of the rolling material and the parameter is the profile or the distribution of the planarity in width direction of the rolling material; the cooling shells (160-n) in a plurality thereof are arranged adjacent to one another in axial direction of the roll (300) to be cooled; and the actuator (165) is constructed for suitable setting of the effective length of each individual one of the n cooling shells (160-n) in circumferential direction of the roll (300) in accordance with the regulating difference (eQ̇), which is represented by the setting signal (s), of the distribution of the heat flow in width direction of the rolling material.

Images