EP3307448B1 - Procédé et dispositif servant à réguler un paramètre d'un produit à laminer - Google Patents

Procédé et dispositif servant à réguler un paramètre d'un produit à laminer Download PDF

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Publication number
EP3307448B1
EP3307448B1 EP16727716.9A EP16727716A EP3307448B1 EP 3307448 B1 EP3307448 B1 EP 3307448B1 EP 16727716 A EP16727716 A EP 16727716A EP 3307448 B1 EP3307448 B1 EP 3307448B1
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EP
European Patent Office
Prior art keywords
roll
cooling shell
parameter
circumferential direction
cooling
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16727716.9A
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German (de)
English (en)
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EP3307448A1 (fr
Inventor
Matthias Kipping
Ralf Seidel
Johannes ALKEN
Torsten Müller
Magnus TREUDE
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SMS Group GmbH
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SMS Group GmbH
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Publication of EP3307448A1 publication Critical patent/EP3307448A1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/28—Control of flatness or profile during rolling of strip, sheets or plates
    • B21B37/30—Control of flatness or profile during rolling of strip, sheets or plates using roll camber control
    • B21B37/32—Control of flatness or profile during rolling of strip, sheets or plates using roll camber control by cooling, heating or lubricating the rolls
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B1/00—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations
    • B21B1/22—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/28—Control of flatness or profile during rolling of strip, sheets or plates
    • B21B37/30—Control of flatness or profile during rolling of strip, sheets or plates using roll camber control
    • B21B37/34—Control of flatness or profile during rolling of strip, sheets or plates using roll camber control by hydraulic expansion of the rolls
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/74—Temperature control, e.g. by cooling or heating the rolls or the product
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/06—Lubricating, cooling or heating rolls
    • B21B27/10—Lubricating, cooling or heating rolls externally
    • B21B2027/103—Lubricating, cooling or heating rolls externally cooling externally

Definitions

  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • cooling shells are circular in cross section Trays whose curvature is adapted to the curvature or the diameter of the roll to be cooled.
  • 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 ,
  • 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 the coolant temperature is as an actuator of a control technically conceivable but too slow, this is very costly.
  • 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.
  • 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.
  • 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.
  • the invention essentially proposes three different embodiments:
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • FIG. 1 shows a cascade control for controlling a parameter of a metal strip, for example, to control its profile or its flatness.
  • a parameter of a metal strip for example, to control its profile or its flatness.
  • 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 fürzu meetingsdes 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.
  • 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.
  • suitable means that the heat flow control deviation e Q becomes zero as far as possible.
  • 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.
  • 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 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.
  • 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.
  • 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.
  • 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 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.
  • 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 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.
  • 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.
  • 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 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.
  • 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.
  • the one in here FIG. 12 Actuator 165 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.
  • 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 Operakühlschalen 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 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.

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  • Control Of Metal Rolling (AREA)
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Claims (17)

  1. Procédé pour le réglage d'un paramètre (P), par exemple du profil ou de la planéité d'un produit de laminage (200) en forme de bande laminé à l'aide d'une cage de laminoir, présentant les étapes suivantes dans lesquelles :
    on mesure le paramètre réel Pist du produit de laminage (200) après un processus de laminage ;
    on compare le paramètre réel PIst à un paramètre de consigne prédéfini (PSoll) pour le produit de laminage et on détermine un écart (eP) entre le paramètre réel et le paramètre de consigne sous la forme d'un écart de réglage de paramètre (eP) ;
    on détermine un signal de positionnement (s) pour commander au moins un organe de positionnement (160) en fonction del'écart de réglage de paramètre (eP) ; dans lequel, en ce qui concerne l'organe de positionnement (160), il s'agit d'une enveloppe de refroidissement attribuée à un cylindre (300) de la cage de laminoir ;
    caractérisé en ce que l'enveloppe de refroidissement (160) est réalisée de manière variable en ce qui concerne sa longueur utile (b) dans la direction circonférentielle du cylindre et, à l'aide du signal de positionnement (s), on règle de manière appropriée la longueur utile (b) de l'enveloppe de refroidissement dans la direction circonférentielle (b) en fonction de l'écart de réglage de paramètre (eP).
  2. Procédé selon la revendication 1, caractérisé en ce que la détermination du signal de positionnement (s) présente les étapes partielles suivantes dans lesquelles :
    - on détermine une valeur de consigne (QabSoll ) pour le flux de la chaleur à évacuer à partir du cylindre (300) à partir de l'écart de réglage de paramètre (eP) déterminé au préalable et, de manière facultative, en prenant en compte d'autres exigences en se référant au processus de laminage en ce qui concerne le refroidissement du cylindre ;
    - on détermine le flux réel (QabIst ) de la chaleur effectivement évacuée à partir du cylindre (300) ;
    - on détermine un écart de réglage de flux thermique (eQ) à titre de différence entre la valeur de consigne (QabSoll ) et la valeur réelle (QabIst ) pour le flux de la chaleur à évacuer à partir du cylindre (300) ; et
    - on détermine le signal de positionnement (s) pour le réglage de la longueur utile (b) de l'enveloppe de refroidissement (160) dans la direction circonférentielle en conformité avec l'écart de réglage de flux thermique (eQ) qui dépend à son tour de l'écart de réglage de paramètre (eP).
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce qu'on augmente la longueur utile (b) de l'enveloppe de refroidissement (160) dans la direction circonférentielle lorsque la valeur de consigne (QabSoll ) du flux thermique est supérieure à la valeur réelle (QabIst ) du flux thermique ; la longueur utile (b) de l'enveloppe de refroidissement reste inchangée dans la direction circonférentielle lorsque la valeur de consigne (QabSoll ) du flux thermique est identique à la valeur réelle (QabIst ) du flux thermique ; ou on diminue la longueur utile (b) de l'enveloppe de refroidissement (160) dans la direction circonférentielle lorsque la valeur de consigne (QabSoll ) du flux thermique est inférieure à la valeur réelle (QabIst ) du flux thermique.
  4. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que l'enveloppe de refroidissement (160) présente au moins un premier segment et un second segment d'enveloppe de refroidissement (161, 162) qui présentent respectivement une section transversale sous la forme d'une partie d'un arc de cercle pour le recouvrement d'une zone superficielle du cylindre et, pour le réglage de la longueur utile (b) de l'enveloppe de refroidissement dans la direction circonférentielle du cylindre (300), on déplace le premier et le second segment d'enveloppe de refroidissement en fonction du signal de positionnement (s) l'un par rapport à l'autre en direction circonférentielle, de préférence on les fait se chevaucher mutuellement au moins en partie.
  5. Procédé selon l'une quelconque des revendications 1 à 3, caractérisé en ce que l'enveloppe de refroidissement (160) est formée à partir d'un matériau flexible qui permet le réglage de la longueur utile (b) de l'enveloppe de refroidissement dans la direction circonférentielle du cylindre par cintrage au moins de parties de l'enveloppe de refroidissement à l'écart du cylindre (300) ou en direction du cylindre (300) ou bien par l'intermédiaire d'un enroulement ou d'un déroulement du matériau flexible en fonction du signal de positionnement.
  6. Procédé selon l'une quelconque des revendications 1 à 3, caractérisé en ce que l'enveloppe de refroidissement (160) présente au moins un couvercle rotatif (163) qui permet le réglage de la longueur utile (b) de l'enveloppe de refroidissement dans la direction circonférentielle du cylindre par l'intermédiaire d'une ouverture au d'une fermeture du couvercle en fonction du signal de positionnement.
  7. Procédé selon l'une quelconque des revendications 2 ou 3, caractérisé en ce que, en ce qui concerne le flux thermique (Q), il s'agit de la répartition du flux thermique dans la direction en largeur du produit de laminage, et en ce qui concerne le paramètre, il s'agit du profil ou de la répartition de la planéité dans la direction en largeur du produit de laminage.
  8. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que la mise en oeuvre du procédé a lieu au cours d'une interruption de laminage.
  9. Dispositif destiné au réglage d'un paramètre d'un produit de laminage en forme de bande laminé à l'aide d'une cage de laminoir, présentant :
    un mécanisme de mesure de paramètre (110) destiné à déterminer le paramètre réel (PIst) du produit de laminage (200) après un cycle de laminage ;
    un mécanisme de comparaison de paramètre (120) destiné à déterminer un écarts entre le paramètre réel (PIst) et le paramètre de consigne prédéfini (PSoll), à titre d'écart de réglage de paramètre (eP) ; et
    un dispositif de réglage (150) destiné à déterminer un signal de positionnement (s) pour l'activation d'au moins un organe de réglage (160) en fonction de l'écart de réglage de paramètre (eP) ; dans lequel, en ce qui concerne l'organe de réglage (160), il s'agit d'une enveloppe de refroidissement attribuée à un cylindre de la cage de laminoir ;
    caractérisé en ce que l'enveloppe de refroidissement est réalisée avec une longueur utile variable dans la direction circonférentielle du cylindre et, en ce qu'on prévoit un actionneur (165) destiné au réglage approprié de la longueur utile de l'enveloppe de refroidissement (160) dans la direction circonférentielle du cylindre en fonction de l'écart de réglage de paramètre (eP) représenté par le signal de positionnement (s).
  10. Dispositif selon la revendication 9, caractérisé en outre en ce que
    - l'on prévoit un mécanisme de détermination du flux de consigne (130) pour la détermination d'une valeur de consigne (QabSoll ) pour le flux de la chaleur à évacuer à partir du cylindre (300) en se référant à l'écart de réglage de paramètre (eP), et de manière facultative, en prenant en compte d'autres exigences émanant du processus de laminage en ce qui concerne le refroidissement du cylindre ;
    - l'on prévoit un mécanisme de mesure du flux réel (170) pour la détermination de la valeur réelle (QabIst ) pour le flux de la chaleur effectivement évacué à partir du cylindre ;
    - l'on prévoit un mécanisme de comparaison de flux thermique (140) pour la détermination d'un écart de réglage du flux thermique (eQ), à titre de différence entre la valeur de consigne (Qabsoll ) et la valeur réelle (QabIst ) pour le flux de la chaleur à évacuer à partir du cylindre ; et
    - le dispositif de réglage (150) est réalisé de manière à générer le signal de positionnement (s) pour le réglage de la longueur utile (b) de l'enveloppe de refroidissement (160) dans la direction circonférentielle du cylindre en fonction de l'écart de réglage du flux thermique (eQ) ; dans lequel l'écart de réglage du flux thermique (eQ) dépend à son tour de l'écart de réglage de paramètre (eP).
  11. Dispositif selon la revendication 9 ou 10, caractérisé en ce que l'enveloppe de refroidissement (160) présente au moins un premier segment et un second segment d'enveloppe de refroidissement (161, 162) qui présentent respectivement une section transversale sous la forme d'une partie d'un arc de cercle pour le recouvrement d'une zone superficielle du cylindre et l'actionneur (165) est réalisé sous la forme d'un mécanisme de déplacement destiné au déplacement du premier et du second segment d'enveloppe de refroidissement dans la direction circonférentielle du cylindre l'un par rapport à l'autre, dans lequel on peut faire en sorte que le premier et le second segment d'enveloppe de refroidissement se chevauchent mutuellement au moins en partie.
  12. Dispositif selon la revendication 11, caractérisé en ce que le premier segment d'enveloppe de refroidissement (161) est disposé de manière fixe, mais à distance par rapport à la surface du cylindre (300); et le mécanisme de déplacement (165) est réalisé pour déplacer le second segment d'enveloppe de refroidissement dans la direction circonférentielle du cylindre par rapport au premier segment d'enveloppe de refroidissement.
  13. Dispositif selon la revendication 11 ou 12, caractérisé en ce que le mécanisme de déplacement (165) est réalisé sous la forme d'un cylindre hydraulique.
  14. Dispositif selon l'une quelconque des revendications 11, 12 ou 13, caractérisé en ce que le mécanisme de déplacement (165) présente :
    une roue montée en rotation (165-1) ;
    un mécanisme d'entraînement (165-2) pour l'entraînement de la roue en rotation ;
    dans lequel la roue entre en engrènement avec le second segment d'enveloppe de refroidissement (162) par exemple via une liaison par friction ou via une liaison par complémentarité de forme d'une manière telle qu'un mouvement de rotation de la roue (165-1) entraîne le déplacement du second segment d'enveloppe de refroidissement (162) dans la direction circonférentielle.
  15. Dispositif selon la revendication 9 ou 10, caractérisé en ce que l'enveloppe de refroidissement (160) est réalisée à partir d'un matériau flexible ; et l'actionneur (165) est réalisé sous la forme d'un mécanisme de cintrage ou sous la forme d'un mécanisme d'enroulement et de déroulement destiné au réglage de la longueur utile (b) de l'enveloppe de refroidissement dans la direction circonférentielle du cylindre par cintrage au moins de parties de l'enveloppe de refroidissement à l'écart du cylindre ou en direction du cylindre ou bien par enroulement ou par déroulement du matériau flexible en fonction du signal de positionnement.
  16. Dispositif selon la revendication 9 ou 10, caractérisé en ce que l'enveloppe de refroidissement (160) présente au moins un couvercle rotatif (163) et l'actionneur (165) est réalisé pour le réglage de la longueur utile de l'enveloppe de refroidissement dans la direction circonférentielle du cylindre par l'intermédiaire d'une ouverture au d'une fermeture du couvercle en fonction du signal de positionnement.
  17. Dispositif selon la revendication 10, caractérisé en ce que :
    en ce qui concerne le flux thermique (Q), il s'agit de la répartition du flux thermique dans la direction en largeur du produit de laminage, et en ce qui concerne le paramètre, il s'agit du profil ou de la répartition de la planéité dans la direction en largeur du produit de laminage ;
    une multitude N d'enveloppes de refroidissement (160-n) sont disposées les unes à côté des autres dans la direction axiale du cylindre (300) qui doit être refroidi ; et
    l'actionneur (165) est réalisé pour le réglage approprié de la longueur utile de chaque enveloppe individuelle parmi lesdites n enveloppes de refroidissement (160-n) dans la direction circonférentielle du cylindre (300) en fonction de l'écart de réglage (eQ) représenté par le signal de positionnement (s) de la répartition du flux thermique dans la direction en largeur du produit de laminage.
EP16727716.9A 2015-06-11 2016-06-08 Procédé et dispositif servant à réguler un paramètre d'un produit à laminer Active EP3307448B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015210680.2A DE102015210680A1 (de) 2015-06-11 2015-06-11 Verfahren und Vorrichtung zum Regeln eines Parameters eines Walzgutes
PCT/EP2016/063045 WO2016198457A1 (fr) 2015-06-11 2016-06-08 Procédé et dispositif servant à réguler un paramètre d'un produit à laminer

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EP3307448A1 EP3307448A1 (fr) 2018-04-18
EP3307448B1 true EP3307448B1 (fr) 2019-09-25

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US (1) US10807134B2 (fr)
EP (1) EP3307448B1 (fr)
JP (1) JP6527967B2 (fr)
KR (1) KR102042039B1 (fr)
CN (1) CN107848000B (fr)
DE (1) DE102015210680A1 (fr)
RU (1) RU2690556C1 (fr)
WO (1) WO2016198457A1 (fr)

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KR930000465B1 (ko) * 1985-05-17 1993-01-21 가부시기가이샤 히다찌세이사꾸쇼 압연기의 로울냉각장치 및 로울냉각방법
JPS6245409A (ja) * 1985-08-26 1987-02-27 Nippon Kokan Kk <Nkk> ロ−ル冷却機構
US5212975A (en) * 1991-05-13 1993-05-25 International Rolling Mill Consultants, Inc. Method and apparatus for cooling rolling mill rolls and flat rolled products
RU2115494C1 (ru) * 1997-08-14 1998-07-20 Череповецкий государственный университет Способ управления тепловым профилем валков прокатного стана
DE19850738A1 (de) * 1998-11-04 2000-05-11 Schloemann Siemag Ag Betriebsverfahren für ein Walzgerüst einer Walzstraße
JP3300759B2 (ja) * 1999-02-05 2002-07-08 三菱重工業株式会社 圧延ロールヒートクラウン形状制御用誘導加熱装置
JP2000237805A (ja) * 1999-02-22 2000-09-05 Hitachi Ltd オンラインロール研削装置及びオンラインロール研削方法
US6652273B2 (en) * 2002-01-14 2003-11-25 The Procter & Gamble Company Apparatus and method for controlling the temperature of manufacturing equipment
JP2005334910A (ja) * 2004-05-25 2005-12-08 Toshiba Mitsubishi-Electric Industrial System Corp 圧延機のクーラント制御装置並びに板プロファイル制御装置及び平坦度制御装置
DE102005042020A1 (de) * 2005-09-02 2007-03-08 Sms Demag Ag Verfahren zum Schmieren und Kühlen von Walzen und Metallband beim Walzen, insbesondere beim Kaltwalzen, von Metallbändern
BE1017462A3 (fr) 2007-02-09 2008-10-07 Ct Rech Metallurgiques Asbl Dispositif et procede de refroidissement de cylindres de laminage en regime hautement turbulent.
DE102009053074A1 (de) 2009-03-03 2010-09-09 Sms Siemag Ag Verfahren und Kühlvorrichtung zum Kühlen der Walzen eines Walzgerüstes
CN201442012U (zh) * 2009-07-22 2010-04-28 山东石横特钢集团有限公司 五切分轧辊冷却装置
DE102012202340A1 (de) 2011-12-23 2013-06-27 Sms Siemag Ag Verfahren und Vorrichtung zum Kühlen von Walzen
DE102012216570A1 (de) 2012-05-11 2013-11-14 Sms Siemag Ag Vorrichtung zum Kühlen von Walzen
CN203196994U (zh) * 2013-04-25 2013-09-18 浙江瑞浦机械有限公司 连轧机轧辊孔型辅助冷却装置

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Publication number Publication date
KR102042039B1 (ko) 2019-12-02
EP3307448A1 (fr) 2018-04-18
US20180169724A1 (en) 2018-06-21
JP6527967B2 (ja) 2019-06-12
KR20180044853A (ko) 2018-05-03
CN107848000A (zh) 2018-03-27
CN107848000B (zh) 2019-06-18
US10807134B2 (en) 2020-10-20
WO2016198457A1 (fr) 2016-12-15
DE102015210680A1 (de) 2016-12-15
JP2018520878A (ja) 2018-08-02
RU2690556C1 (ru) 2019-06-04

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