EP3381576A1 - Walzgerüst, das mit einer kontrollvorrichtung für die walzstabilität ausgerüstet ist, und entsprechende methode - Google Patents

Walzgerüst, das mit einer kontrollvorrichtung für die walzstabilität ausgerüstet ist, und entsprechende methode Download PDF

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Publication number
EP3381576A1
EP3381576A1 EP17290048.2A EP17290048A EP3381576A1 EP 3381576 A1 EP3381576 A1 EP 3381576A1 EP 17290048 A EP17290048 A EP 17290048A EP 3381576 A1 EP3381576 A1 EP 3381576A1
Authority
EP
European Patent Office
Prior art keywords
longitudinal
rolling
rolls
working
work rolls
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.)
Withdrawn
Application number
EP17290048.2A
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English (en)
French (fr)
Inventor
Michel Abi Karam
Stéphane GOUTTEBROZE
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Clecim SAS
Original Assignee
Primetals Technologies France SAS
Priority date (The priority date 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 date listed.)
Filing date
Publication date
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Application filed by Primetals Technologies France SAS filed Critical Primetals Technologies France SAS
Priority to EP17290048.2A priority Critical patent/EP3381576A1/de
Priority to JP2019600142U priority patent/JP3230298U/ja
Priority to PCT/EP2018/057085 priority patent/WO2018177827A1/fr
Priority to EP18714190.8A priority patent/EP3600708B1/de
Priority to KR2020197000075U priority patent/KR200496484Y1/ko
Priority to CN201890000687.0U priority patent/CN212143934U/zh
Publication of EP3381576A1 publication Critical patent/EP3381576A1/de
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/14—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls
    • B21B13/145—Lateral support devices for rolls acting mainly in a direction parallel to the movement of the product
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
    • B21B2013/025—Quarto, four-high stands
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
    • B21B2013/028—Sixto, six-high stands
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
    • B21B2031/206—Horizontal offset of work rolls

Definitions

  • the present invention relates to a roll stand equipped with a rolling stability control device according to the preamble of claim 1 and an associated rolling method according to the preamble of claim 12.
  • the present invention is particularly directed to quarto, sexto, 18-Hi, X-HI® cages comprising two working rolls, each disposed on either side of a rolling line of a metal product such as a strip running longitudinally in said cage, said working cylinders being arranged between lateral support means for positioning at least laterally (or longitudinally taking into account the direction of travel) said cylinders of working at precise working positions in the rolling stand.
  • the rolling parameter can be derived from a data bank or measured from a signal from a measurement made by a device for analyzing the characteristics of the strip or the rolling mill, by a an auxiliary measurement of the working cylinder position or a measurement of the resultant forces on the work rolls.
  • an offset respecting conditions suitable for rolling said product.
  • Figure 1 of the present invention reproduces a very descriptive example of the figure 1 of EP2464470B1 where the regulation of the offset (O) is allowed by displacement means (see actuator (63)) following a modification of nominal rolling parameters or a modification of position and force measurement values such that those given by the measuring device (64).
  • the offset control is performed jointly for the upper and lower work rolls.
  • the work rolls may have sudden jumps or other variations and unstable positions around the predefined offset, (or regulated as in the state of the art), and / or sudden jumps or other variations of forces on the working rolls, that is to say say between the longitudinal displacement means as lateral supports arranged longitudinally on either side of each work roll.
  • these jumps or other instabilities are not symmetrical between the upper and lower work rolls of the rolling stand, which makes a common way of controlling the offset for a pair of work rolls as in the state of the art insufficiently able to harmonize efforts of the entire cage.
  • An object of the present invention is to maximize the rolling speed while ensuring stability of the operating conditions of a rolling stand of a scrolling metal product comprising at least upper and lower working rolls previously arranged under an offset predefined and can be moved at least parallel to the direction of travel of the product and relative to a point of origin.
  • said origin point of the cage is defined as intersection of longitudinal axis and vertical axis, the longitudinal axis being defined as the cage pass line and the vertical axis being defined as passing through at least one of the upper and lower intermediate cylinders transmitting a rolling force by direct contact on at least one of the working rolls.
  • the object of the present invention is therefore to compensate for a physical state divergence of at least one of the working rolls with respect to a previous physical state during an increase in the rolling speed under guaranteed stability of the rolling conditions. allowing the output of the rolling mill a product of constant quality (such as the thickness, the surface condition, etc.).
  • such a divergence can have multiple causes such that a position destabilization of at least one of the work rolls around its position (provided under an "offset" or longitudinal offset from the point of origin of the cage), a lateral deformation (said cedging) cage creating a change in lateral play conditions between working cylinders and lateral support cylinders (said clamping hyperstatic or excess play), excessive variations in efforts ( in particular longitudinals) and torques experienced by the working roll, variations in traction of the product upstream and / or downstream of the cage interacting with at least one of the working rolls, sliding effects between the work roll and the product or between cylinders of the cage, thermal variations of the whole cage.
  • the said divergences are also local, that is to say individually affect each of the upper and lower work rolls in various forms.
  • the plaintiff introduces two figures 2 and 3 (a, b, c, d, e) respectively illustrating an embodiment of a rolling mill core and having a set of five measurements of various parameters on a rolling stand, said measurements having a type of instability related to the work rolls.
  • the longitudinal forces measured at said strain gauges have positive or negative values.
  • the positive or negative sign indicates that the working roll (for example CTS) imposes a force on one or the other of the lateral support means which frames it in the longitudinal direction (for example through the pivoting arms BPS1 or BPS2 and their cylinder and rows of rollers), knowing that ideally the working cylinder is in a non-hyperstatic mode between its lateral support means.
  • Figure 3 (a) shows a measurement (in hours, minutes, seconds) for about 11 minutes (ie the time of the passage corresponding to the rolling of a metal strip of a coil of the speed (in m / s) of movement through a cage for a It should be noted that, in order to allow maximum rolling productivity, the speed of the cage is increased significantly in two main time intervals, a first interval (P1) between 11:02:00.
  • the said lateral support means also have a function of being able to move the said working cylinder at least parallel to the direction of travel of the product and to arrange it at an offset from the aforementioned point of origin.
  • said working roll is arranged between the two lateral support means under a spacing sufficient to guarantee the roll a lateral clearance allowing it to rotate perfectly between said means. side support while ensuring contact under a longitudinal force applied only one side of work roll.
  • the Figure 3 (b) shows that said upper working cylinder exerts a force on one of the lateral support means, here about -10 tons before the interval (P1).
  • the negative value -10t indicates that the working roll exerts a longitudinal force opposite to the running direction of the strip.
  • the longitudinal force (FSup) has a force deviation of 5 tons, then regains its initial value of about -10 tons: a divergence of physical state of said upper working cylinder, followed by a return to its initial state.
  • the longitudinal force (FSup) has a force deviation of about 60 tons, more precisely from -10 tons to +50 tons, which means that the physical state of the working cylinder changes in that the measure shows that it moves from the first to the second lateral support means of said working cylinder. Obvious instability of the physical state of the working cylinder is thus detected. Indeed, the force of the working cylinder exerted (FSup) on the second lateral support means of said working cylinder reaches +50 tons, five times more in absolute value than the initial value of -10 tons.
  • the Figure 3 (c) shows that said lower working cylinder exerts a force on one of the lateral support means, here about -10 tons before the interval (P1).
  • the negative value -10t indicates that the working roll exerts a longitudinal force opposite to the running direction of the strip.
  • the force longitudinal (Finf) has a force deviation of 10 tons, then reaches a new value of about -20 tons: it is thus noted a divergence of physical state of said lower working cylinder, followed by a new physical state under constant effort of -20 tons.
  • the longitudinal force (Finf) has a force deviation of about 60 tons, more precisely -20 tons to -80 tons, which means that the The physical state of the work roll is modified by variation of effort while maintaining contact on the same lateral support means. Obvious instability of the physical state of the working cylinder is thus detected.
  • the force of the working cylinder exerted (Finf) on the lateral support means of said working cylinder reaches -80 tons, eight times more in absolute value than the initial value of -10 tons.
  • Large variations in forces can then involve effects of cedging (deformation) of the cage structure (columns, means of support and lateral displacement), or even worse breaks or other types of damage to internal elements of cage.
  • the operator has decreased the speed of rolling of the strip to return to conditions of less effort, however progressively and unstable type of -80 tons up to -10 tons.
  • the reduction in speed of course implies a significant reduction in rolling productivity, to the detriment of the operator.
  • Figure 3 (d) always present according to figure 2 a measurement of a longitudinal distance or clearance sensor between the upper pivoting arm (BPS1) and the upper displacement beam (PDS1), this arrangement being intended to compensate for an operating clearance between the upper working cylinder and at least one of his first or second lateral support means.
  • each of said working rolls is arranged between its two lateral support means (each comprising a pivoting arm, a lateral support roll and two rows of rollers, see figure 2 ) at a spacing sufficient to ensure the working cylinder a lateral clearance allowing it to rotate perfectly between said means of lateral support while ensuring contact under a longitudinal force applied only one lateral side of the working cylinder.
  • the Figure 3 (d) shows that said upper pivoting arm has an upper longitudinal clearance (KYKsup) with one of the longitudinal displacement beams, here a value of about 2.6 millimeters before the interval (P1).
  • KYKsup an upper longitudinal clearance
  • the upper longitudinal clearance decreases from 2.6 millimeters to 2.5 millimeters, then returns to an average value of 2.6 millimeters, however in the presence of increased disturbances of 'amplitudes lower than 1/10 th of a millimeter, in direct relation to the difference of already observed in the physical state Figure 3 (b) .
  • Figure 3 (e) presents a measurement of a distance or longitudinal clearance sensor (KYKinf according to figure 2 ) between the lower pivot arm (BPI1) and the lower displacement beam (PDI1), this arrangement being intended to compensate for an operating clearance between the lower working cylinder and at least one of its first or second lateral support means.
  • KYKinf a distance or longitudinal clearance sensor
  • the figure 3 (e) shows that said lower pivoting arm has a lower longitudinal clearance (KYKinf) with one of the longitudinal displacement beams, here an average value of about 3.00 millimeters before the interval (P1).
  • KYKinf lower longitudinal clearance
  • the first interval (P1) during the first increase in speed, the lower longitudinal clearance increases to 3.25 millimeters and then decreases to 3.20 millimeters.
  • P2 Shortly before the second interval (P2), there is a rise of 0.3 millimeters which seems a deviation probably similar to that of the measured set (KYKsup) to the distance sensor in the upper part.
  • Predefined patterns for detecting such divergence scenarios of at least one physical state of one or both upper and lower work rolls may also be stored in the control unit, in order to apply to the cage modes of operation. preventive repositionings of one or more said cylinders against rolling instabilities.
  • the Applicant has thus been able to improve the rolling stability control by means of a regulation dependent on at least two longitudinal stress parameters (Fsup, Finf) measured simultaneously on each of the active measuring means coupled to the moving means of each of the upper and lower work rolls.
  • the simultaneous taking of these two parameters allowed in fact to be able to detect more dynamically divergences of physical state of the upper and lower working cylinders of type not only concomitant, but also non-concomitant, particularly in phase of increase of rolling speed .
  • the regulation signal may comprise a logical, algebraic or arithmetic function of the longitudinal force components (FSup, Finf) respectively measured by each of the measuring means of the lower and upper work rolls.
  • a very simplified regulation signal can thus comprise a function of a relative force value (FSup-Finf) between the two forces (FSup, Finf) respectively measured by each measuring means of the lower working cylinders and superior.
  • FSup-Finf relative force value
  • Finf two forces
  • an increase in effort of one of the upper or lower work rolls is followed or accompanied by a rise in effort of the other cylinder.
  • the forces have opposite directions longitudinally for the upper and lower work rolls, their difference is therefore a sensitive and rapid detection means during a rising speed stage rolling.
  • the regulation signal may comprise a function of an additive force value (FSup + Finf) of the two forces (FSup, Finf) respectively measured by each of the lower and upper cylinder measuring means.
  • an increase in effort of one of the upper or lower work rolls is followed or accompanied by a rise in effort of the other cylinder.
  • the forces have opposite directions longitudinally for the upper and lower work rolls, their sum is therefore a sensitive and rapid detection means during a rise in rolling speed phase.
  • control signal may comprise a function of at least one algebraic or logical value of a combination of either linear or non-linear forces respectively measured by each of the measuring means of the lower and upper work rolls.
  • the device according to the invention finally provides that at least two means of all the described types of measurement per cylinder are arranged in a plane transverse to the longitudinal direction of travel of the product. In this way, divergences by deviation between the axes of the work rolls can also be better detected. As such, the recovery can be done more easily and quickly by longitudinal displacement means being cylinder positioning elements from at least one cylinder end to a minimum, up to a series of cylinder displacement elements arranged consecutively in a plane transverse to the longitudinal direction.
  • the displacement elements comprise rollers, rollers or side support rollers of working roll, that is to say laterally supporting the working rollers under a directional thrust mainly oriented in the longitudinal direction, the said elements being particularly adapted to a cage type 18-Hi or X-HI®.
  • the device can be further improved in that it comprises at least four distance sensors instead of the two sensors (KIKsup, KIKinf) of the figure 2 .
  • Each of the four longitudinal displacement beams then comprises at least one such distance sensor, ideally two transversely.
  • the regulation of the repositioning of the working cylinders by the longitudinal displacement means as a function of the measured forces (Fsup, Finf) by an active measurement means (under load load) certainly gives the information on the side where it is located.
  • the actual support of the cylinder on its lateral support means however, the actual position of each of the two lateral support means introduces an unknown which makes the actual position measurement of the work rolls (and their relative position which is major) imprecise.
  • a single sensor on each of the two beams upstream of the rolling is a way to locate the working rolls, but under complementary effects of ceding for example (one of the sensors no longer delivers signal), the location is distorted.
  • each displacement beam comprises such a distance sensor for measuring a clearance between each beam and the lateral support means (pivoting arm, lateral support cylinder and rows of support rollers)
  • the location of each working cylinder in a frame of the cage under ceding is improved and therefore allows in return a repositioning control means more precise displacement work rolls.
  • at least one play distance sensor is disposed in each of four displacement means arranged laterally on either side of the upper work rolls. and lower, that is to say in particular between four longitudinal displacement beams belonging to said means, each of said beams acting on one of the four movable lateral support means of the upper and lower working rolls.
  • the rolling mill cage according to the invention also makes it possible to implement a method for controlling the positioning of an upper and lower work roll of a rolling mill of a metal product in a longitudinal longitudinal scroll, for which a first parameter (Fsup) is measured as a longitudinal component force exerted by a first of the two working cylinders on its respective active measuring means, and is then transmitted to the control unit acting on the longitudinal displacement means of said first cylinder at least as soon as the first parameter comes out of a defined tolerance interval.
  • a first parameter Fsup
  • said control method provides that a second parameter (Finf) is simultaneously measured as a longitudinal component force exerted by a second of the two work rolls on its respective active measuring means, and is then transmitted to the unit.
  • control device acting on the longitudinal displacement means of the work rolls at least as soon as the second parameter or a difference between the first and the second parameter comes / goes out of a defined tolerance interval.
  • This taking into account of the first and second parameter at the upper and lower part of the cage advantageously makes it possible to provide better control during non-concomitant differences in the physical state of the upper and lower work rolls, as illustrated by the curves of FIG. figure 3 .
  • the method thus provides that all the upper and lower longitudinal displacement means are actuated individually in order to reposition the upper work rolls. and lower under individual offsets depending on the regulation signal.
  • a set of subclaims also provides advantageous embodiments of the invention.
  • Figure 4 presents an embodiment of a rolling mill cage according to the invention, here of 18-Hi or X-HI® type.
  • the cage is presented in a side view, here for example operator side (or motor side where extensions and engines are provided to drive at least rolls of the cage).
  • all the upper and lower longitudinal displacement means are individually operable to reposition the upper and lower work rolls (CTS, CTI) under individual offsets (Offs, Offi) according to the control signal as shown in FIG. figure 5 as a zoom of the central part of the cage according to figure 4 .
  • Each upper and lower working roll can thus individually or not undergo one of the physical state divergences that are transmitted in particular by various longitudinal forces due to the multiple causes mentioned above in the present invention.
  • Under a given offset, and as a function of at least one initiating divergence it is then possible to provide correctional diagrams of the forces applied to each working roll by modifying at least one of the longitudinal displacement means. While this modification may lead to a temporary change in the offset of each working roll, this transitional phase is intended to balance the forces as a function of the physical state of the assembly and of each of the upper and lower work rolls. inferior.
  • the regulation signal can be a logical, algebraic or arithmetic function of the longitudinal force components. (FSup1, FInf1, Fsup2, Fsup2) respectively measured by each means of measuring the lower and upper rolls, according to their active or passive state. In this way, depending on the various scenarios of potential instabilities, correction modes are applied to the longitudinal displacement means in order to compensate for a particular instability.
  • the regulation signal can be or include a function of an additive force value (Fsup + Finf) of the two forces (FSup, FInf) measured respectively by each of the measuring means of lower and upper cylinders.
  • the rolling mill cage according to the invention can provide that the regulation signal is a function of at least one algebraic or logical value of a combination of either linear or non-linear forces respectively measured by each of the measuring means of lower and upper cylinders. Indeed, instability effects can be detected under complex conditions requiring an approach, for example non-linear as already mentioned.
  • Figure 6 has a partial view from above of said cage according to Figures 4 and 5 , in which, on the one hand, the longitudinal displacement means are more precisely described therein.
  • the said longitudinal displacement means (MDS1, MDS2, MDI1, MDI2) are cylinder positioning elements from at least one cylinder end to a minimum, to a series of cylinder displacement elements arranged consecutively in a transverse plane (Y) to the direction longitudinal (X).
  • the displacement elements comprise cylinders, rollers or side support rollers of working roll, that is to say laterally supporting the working rollers under a directional thrust mainly oriented in the longitudinal direction, the said elements being particularly suitable for a cage type 18-Hi or X-HI®.
  • the parameter (P) comprises in the example of the figure 6 a plurality of measured parameters (longitudinal forces, distance measurement, gap or clearance measurement) which advantageously make it possible to characterize more finely the physical state of the working roll and a potential divergence.
  • the forces experienced by the work roll are measured using the longitudinal force measurement.
  • the regulation signal (Ssup1, Ssup1 ') emitted by the control unit (UC) towards the longitudinal displacement means is then a logical, algebraic or arithmetic function of multiple signals of a nature. complementary method for detecting at least one critical divergence of the physical state of the work roll and not confusing it with a cylinder play variation without incidence for a given offset in a permitted force range.
  • Figure 7 presents an example of extended parameters of complementary measurements adapted to a measurement of physical state divergence of at least one of the working cylinders.
  • the parameter detection (P) is carried out by means of several measurements related to force (Fsup1), position (X1), active or passive contact parameters between lateral elements (beam / arm) connected to the cylinder of job
  • figure 7 presents in a zoomed way the sensor (KYKS1) of measurement type of difference between the pivoting arm and the displacement beam.
  • the said rolling stability control method thus provides that additional first parameters are simultaneously measured as the longitudinal position of the centers of the two upper and lower work rolls. relative to the vertical axis (Z), then are transmitted to the control unit acting on the longitudinal displacement means of said work rolls, at least as soon as the relative difference between two of said parameters comes out of a tolerance interval defined.
  • the said rolling stability control method according to the invention also provides that second additional parameters (Pc) are simultaneously measured as transmission couples acting on each of the two upper and lower working rolls, and are then transmitted to the control unit acting on the longitudinal displacement means of said work rolls, at least as soon as the relative distance between two of said parameters comes out of a defined tolerance range.
  • Pc second additional parameters
  • the said rolling stability control method according to the invention also provides that first additional parameters (Pt) are simultaneously measured as tensile measurements of metal product on at least one of the working rolls, and at least as soon as the relative difference between two of said parameters comes out of a defined tolerance range.
  • first additional parameters Pt are simultaneously measured as tensile measurements of metal product on at least one of the working rolls, and at least as soon as the relative difference between two of said parameters comes out of a defined tolerance range.
  • the said rolling stability control method according to the invention also provides that additional second parameters (Xkyks1) are simultaneously measured as play and contact between the lateral support means of upper and lower work rolls and displacement beams. longitudinal, then are transmitted to the control unit acting on the longitudinal displacement means of said work rolls, at least as soon as the relative distance between two of said parameters comes out of a defined tolerance range.
  • additional second parameters Xkyks1
  • Figure 8 presents a multi-cage control method for stabilizing rolling according to the invention, for which mill stands according to the invention are arranged sequentially longitudinally.
  • the control unit acts not only on the longitudinal displacement means of at least two rolling stands respectively arranged upstream and downstream of each other and, in addition, acts on rolling process parameters, for example by changing inter-cage strokes in scrolling; by re-distributing the cage vertical clamping value over several cages, by changing the lubrication in one of the cages, etc.
  • the goal is to reduce rolling instabilities if at least one of the cages had to present, while respecting the qualitative criteria of the final rolled product, especially for higher rolling speeds.
  • the control unit (UC) can thus act as an automatism and allows the parameter measurement (s) and the regulation of the longitudinal displacement means and the rolling process parameters to take place in real time, so that force parameter values or deviation values between forces do not exceed predefined threshold values, particularly when one or more rolling stands are switched on or off, in a continuous process multi-cage rolling mill, during a change of the product type at the entrance of the rolling stand (s), during a maintenance of at least one cage, in particular for a change of cylinder on the fly.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
EP17290048.2A 2017-03-31 2017-03-31 Walzgerüst, das mit einer kontrollvorrichtung für die walzstabilität ausgerüstet ist, und entsprechende methode Withdrawn EP3381576A1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP17290048.2A EP3381576A1 (de) 2017-03-31 2017-03-31 Walzgerüst, das mit einer kontrollvorrichtung für die walzstabilität ausgerüstet ist, und entsprechende methode
JP2019600142U JP3230298U (ja) 2017-03-31 2018-03-21 圧延安定性を制御するためのデバイスを備える圧延スタンド
PCT/EP2018/057085 WO2018177827A1 (fr) 2017-03-31 2018-03-21 Cage de laminoir équipée d'un dispositif de contrôle de stabilité de laminage et méthode associée
EP18714190.8A EP3600708B1 (de) 2017-03-31 2018-03-21 Walzgerüst, das mit einer kontrollvorrichtung für die walzstabilität ausgerüstet ist, und entsprechende methode
KR2020197000075U KR200496484Y1 (ko) 2017-03-31 2018-03-21 압연 안정성 제어 장치가 장비된 압연기 스탠드 및 관련 방법
CN201890000687.0U CN212143934U (zh) 2017-03-31 2018-03-21 轧机机架

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17290048.2A EP3381576A1 (de) 2017-03-31 2017-03-31 Walzgerüst, das mit einer kontrollvorrichtung für die walzstabilität ausgerüstet ist, und entsprechende methode

Publications (1)

Publication Number Publication Date
EP3381576A1 true EP3381576A1 (de) 2018-10-03

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EP17290048.2A Withdrawn EP3381576A1 (de) 2017-03-31 2017-03-31 Walzgerüst, das mit einer kontrollvorrichtung für die walzstabilität ausgerüstet ist, und entsprechende methode
EP18714190.8A Revoked EP3600708B1 (de) 2017-03-31 2018-03-21 Walzgerüst, das mit einer kontrollvorrichtung für die walzstabilität ausgerüstet ist, und entsprechende methode

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EP18714190.8A Revoked EP3600708B1 (de) 2017-03-31 2018-03-21 Walzgerüst, das mit einer kontrollvorrichtung für die walzstabilität ausgerüstet ist, und entsprechende methode

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EP (2) EP3381576A1 (de)
JP (1) JP3230298U (de)
KR (1) KR200496484Y1 (de)
CN (1) CN212143934U (de)
WO (1) WO2018177827A1 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4053495A1 (de) * 2021-03-03 2022-09-07 ABB Schweiz AG Neigungs- und krümmungsmessungen von metallblechen in einem walzwerk

Citations (4)

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Publication number Priority date Publication date Assignee Title
DE19807554A1 (de) * 1997-02-24 1998-09-10 Hitachi Ltd Walzgerüst und Walzverfahren
JP2000140908A (ja) * 1998-11-06 2000-05-23 Hitachi Ltd 圧延機及び圧延方法
EP2542360B1 (de) 2010-03-03 2015-03-04 Siemens VAI Metals Technologies SAS Walzgerüst
EP2464470B1 (de) 2009-08-12 2016-01-27 Primetals Technologies Austria GmbH Verfahren und vorrichtung für die automatische einstellung der position von arbeitswalzen bei einer walzanlage

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