EP0170016A1 - Méthode pour compenser l'influence de l'excentricité de rouleaux de laminage - Google Patents

Méthode pour compenser l'influence de l'excentricité de rouleaux de laminage Download PDF

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Publication number
EP0170016A1
EP0170016A1 EP85107336A EP85107336A EP0170016A1 EP 0170016 A1 EP0170016 A1 EP 0170016A1 EP 85107336 A EP85107336 A EP 85107336A EP 85107336 A EP85107336 A EP 85107336A EP 0170016 A1 EP0170016 A1 EP 0170016A1
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EP
European Patent Office
Prior art keywords
roll
signal
oscillators
output signal
eccentricity
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.)
Granted
Application number
EP85107336A
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German (de)
English (en)
Other versions
EP0170016B1 (fr
Inventor
Georg Dr. Weihrich
Dietrich Wohld
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Siemens AG
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Siemens AG
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Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to AT85107336T priority Critical patent/ATE39069T1/de
Publication of EP0170016A1 publication Critical patent/EP0170016A1/fr
Application granted granted Critical
Publication of EP0170016B1 publication Critical patent/EP0170016B1/fr
Expired legal-status Critical Current

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    • 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
    • B21B37/58—Roll-force control; Roll-gap control
    • B21B37/66—Roll eccentricity compensation systems

Definitions

  • the invention relates to a method and a device for compensating for the influence of roll eccentricities in the position or thickness control of roll stands, in particular with indirect actual value formation which takes place by determining the roll stand stretch.
  • the invention has for its object to provide a method for compensating the roll eccentricities in thickness controls of the type mentioned, which works both more accurately and faster and gets along with the transducers usually available on roll stands.
  • a roll stand 1 is shown schematically. It consists of the upper back-up roll with radius R, the lower back-up roll with radius R u , the two smaller-diameter work rolls, a hydraulic piston that adjusts the upper back-up roll, and an associated hydraulic cylinder, which is supported on the scaffold frame.
  • the elastic frame is symbolically represented by a spring with the spring constant C G.
  • the rolling stock to which an equivalent material spring with the spring constant C M is assigned in the roll gap, is rolled down from the inlet thickness h e to the outlet thickness h a by means of the two work rolls.
  • the roll eccentricities of the upper and lower backup rolls are caused by uneven roll wear, deformations due to thermal stresses and by deviations of the geometrical cylinder axes of the rolls from the operationally occurring rotation axes. They are with ⁇ R o and ⁇ R u , that is, as deviations from the ideal supporting roller half-diameters R or R designated. Also provided are sensors for the support roller speed n, usually in the form of a tachodynamo coupled to the drive motor, for the rolling force F w exerted by the hydraulic piston and for the roller position, which corresponds to the relative position s of the piston in the hydraulic cylinder that adjusts the upper support roller.
  • a control element is designated, by means of which the hydraulic piston is acted upon by a valve with pressure oil.
  • the control signal for the control element 2 consists in the output signal of a controller 3, which has the task of bringing the thickness h of the rolling stock to be brought out in accordance with the thickness target value h * fed to it.
  • the actual value of the controlled variable h a is not measured directly at the point where it occurs, ie in the roll gap, but is determined from the roll stand expansion and the roll position.
  • the device designated by GM in FIG. 1 which essentially contains a multiplier, which multiplies the rolling force F W by the reciprocal of the stand spring constant C G and adds the measured value signal s of the relative hydraulic piston position to this product.
  • the relationship between the input signals and the output signal of the device GM also known as a gauge, is therefore: with ⁇ R the overlapping influences of the two support roller eccentricities ⁇ R o and ⁇ R u are summarized.
  • the arrangement described so far essentially corresponds to the known strip thickness control with the gage meter principle determining the actual value of the strip thickness h a .
  • the gauge GM does not deliver if there are roll eccentricities ⁇ R the strip thickness h alone but the sum of the strip thickness and the roll eccentricity.
  • a strip thickness control built up with the gauge meter signal (h a + ⁇ R) as the actual value would compensate for changes in the strip inlet thickness into the roll stand, but would behave incorrectly with respect to roll eccentricities, because a thickness regulation with the output signal h a + ⁇ R of the gauge meter GM as the actual value behaves exactly like a thickness control with h a as the actual value and a target value h * a - ⁇ R, so that the thickness control would erroneously cause the strip with the outlet thickness h a to be rolled out of phase with the eccentricity ⁇ R.
  • the maximum values of the eccentricities can be several tens of micrometers, which is not compatible with today's tolerance requirements for cold-rolled strip.
  • a compensation device called RECO (Roll Eccentricity Compensator) is used, which has the task, with the sensor signals s, n and F W fed to it, as well as the setting parameters R o , R u , C G and C M the roll eccentricity ß R to identify or emulate, and the signal ⁇ R simulated by it is used to correct the falsified actual value of the strip outlet thickness supplied by the gauge GM, so that the thickness value h a actually occurring in the roll gap can be supplied to the controller 3 as an actual value, with which the influence of the roll eccentricities ⁇ R can be exactly compensated.
  • the framework spring constant C G is determined once by a test before the start of rolling and C M by running an online calculation. It was essential for the RECO device operating according to the compensation method according to the invention that for an exact replication of the roll eccentricities not only the mill stretch, but also the elastic deformation of the material during the rolling process should be taken into account.
  • the compensation device according to the invention can also be used for pure position control with the same advantages.
  • the gage meter GM is eliminated and the output signal of the compensation device RECO is subtracted from the measured value signal s and the result is used as the actual position value.
  • the controller 3 is then supplied with a position setpoint.
  • Figure 2 shows the basic structure of the roll eccentricity compensator RECO. It contains a multiplier 4, to which the rolling force measurement signal F W and the sum of the reciprocal values of the frame spring constant C G and the material spring constant C M are fed on the input side. This reciprocal value corresponds to the reciprocal of a spring constant, which results from the series arrangement of the spring of the roll stand and the spring of the rolling stock.
  • the direct component h e of the inlet thickness h e is extracted from the output signal of the mixing element 5 by means of a high-pass filter HF, so that the signal ⁇ R + h e results at the output of the high-pass filter HF, which has its corner frequency with the speed measurement value n.
  • a signal AR corresponding to the roll eccentricity is then modeled from this signal in an arrangement 6 designed according to the observer principle.
  • the frequencies of the oscillators are tuned by entering the support roller radius R and R u and the average support roller speed n.
  • the outputs of the individual oscillators are combined to form a sum signal ⁇ R and are compared with the output signal of the high-pass filter HF in a mixer 8, the resulting deviation e adjusting the oscillations generated by the oscillators in their phase positions and amplitudes until the signal ⁇ R is an image of the eccentricity oscillation ⁇ R, which is the case when the deviation e becomes a minimum and only corresponds to the statistically fluctuating portion h e of the inlet thickness h e .
  • the frequency is adjusted as a function of the support roller speed n continuously during the rolling operation, and the corner frequency of the high-pass filter HF is also carried accordingly.
  • FIG. 3 shows an implementation example for a model 6 emulating the roll eccentricity 6R with an oscillator pair for emulating the basic eccentricity oscillation.
  • Each oscillator consists of two integrators 9, 10 and 11, 12 arranged one behind the other, the output signal of the integrators 10 and 12 being fed back to the input of the integrators 9 and 11.
  • Multipliers 13 to 16 are arranged in the input circuit of each of the integrators and are used to determine the frequencies of the oscillators. The second inputs of these multipliers are acted upon by a signal n corresponding to the average backup roller speed.
  • the time behavior of the integrators determining components are designed to be adjustable, for example as rotary potentiometers or rotary capacitors, and are adjusted according to the determined values of the radius R or R u of the support rollers.
  • the frequency of the oscillators is preset as a function of the radii R 0 or R u of the support rollers and is adjusted as a function of the support roller speed n.
  • the outputs of the integrators 10 and 12 are added in a mixer 17 and its output signal is subtracted from the output signal ⁇ R + h e of the high-pass filter in a further mixer 18.
  • the oscillations generated by the oscillators 9, 10 and 11, 12 are adjusted in their phase positions and amplitudes until the sum signal ⁇ R of the integrators 10 and 12 matches that of the roll eccentricity-related portion ⁇ R of the input signal fed to the disturbance model 6 ( ⁇ R + h e ).
  • the parallel arrangement of two oscillator pairs shown in FIG. 3 can be converted into a functionally equivalent series circuit using known transformation rules. Such a 4th order filter can be recommended for some applications.
  • FIG. 4 shows the structure of the disturbance model 6 in the roller eccentricity compensator RECO in the event that, in addition to the fundamental vibration of the roller eccentricity, three further harmonics have to be considered as relevant.
  • the parts of this model which are designated by 60, 61, 62 and 63 and have the same structure are designed in accordance with FIG. 3 and contain oscillator pairs for the fundamental oscillation pair and for the 1st, 2nd and 3rd harmonic pair, the individual eccentricity simulations ⁇ R 0 , ⁇ R 1 , ⁇ R 2 and ⁇ R 3 superimposed the simulation of the total eccentricity ⁇ R surrender.
  • the phase and amplitude adjustment takes place depending on the E i nzel Sharingn e o, e l, e 2, e. 3
  • Two adjustment amplifications a o , b and c, d are required for each oscillator, as shown for the basic oscillation pair of the model part 60.
  • FIG. 5 shows the structure of the roller eccentricity compensator RECO using a digitally operating microcomputer 19, in which the signal processing takes place by supplying the input signals via two analog / digital converters 20 and 21 and the signal removal via a digital / analog converter 22.
  • the microcomputer 19 is divided into three function blocks 191 to 193.
  • block 191 the presetting of the two backup roller radii R o and R u and assuming a nominal average backup roller speed takes place offline the calculation of the oscillator frequencies to be preset.
  • block 192 which contains a signal processor, the signal processing for emulating the roller eccentricity ⁇ R takes place by means of oscillators in accordance with the arrangements according to FIGS. 3 and 4, but implemented in functionally equivalent digital technology.
  • the signal processing takes place in a known manner in each case with the values of the input signals sampled at discrete points in time and a result is output in each case at sampling points in time, a reconstruction filter arranged downstream of the digital-to-analog converter being provided in a manner known per se in order to combine the time-resultant analog result sequence into one to convert continuous-time signal.
  • a so-called anti-aliasing filter AF is arranged after the high-pass filter HF in order to suppress the occurrence of interfering external frequencies caused by the scanning process.
  • Anti-aliasing filters such as those found in the "2920 Analog Signal" published by the Intel Corporation in 1980 Processor Design Handbook ", pp. 2-1 to pp.
  • the filters HF, AF and RF which consist of a combination of integrators and Summing amplifiers exist, are in turn tracked in their corner frequencies as a function of the support roller speed n, which can be done by means of multipliers arranged in the input of the integrators, corresponding to the arrangement of Figure 3.
  • Block 193 contains a timer which blocks the values in block 192 in digital technology implemented oscillators in frequency as a function of the current backup roller speed n
  • the timer can, for example, consist of a counter that can be preset to the output value of the analog-digital converter 20 and that is continuously counted down at a constant clock rate, each time the counter reading reaches zero
  • Signal processor 192 emits a pulse.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Machines For Manufacturing Corrugated Board In Mechanical Paper-Making Processes (AREA)
  • Polarising Elements (AREA)
  • Controlling Rewinding, Feeding, Winding, Or Abnormalities Of Webs (AREA)
EP85107336A 1984-07-05 1985-06-13 Méthode pour compenser l'influence de l'excentricité de rouleaux de laminage Expired EP0170016B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85107336T ATE39069T1 (de) 1984-07-05 1985-06-13 Verfahren zur kompensation des einflusses von walzenexzentrizitaeten.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3424693 1984-07-05
DE3424693 1984-07-05

Publications (2)

Publication Number Publication Date
EP0170016A1 true EP0170016A1 (fr) 1986-02-05
EP0170016B1 EP0170016B1 (fr) 1988-12-07

Family

ID=6239865

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85107336A Expired EP0170016B1 (fr) 1984-07-05 1985-06-13 Méthode pour compenser l'influence de l'excentricité de rouleaux de laminage

Country Status (7)

Country Link
US (1) US4685063A (fr)
EP (1) EP0170016B1 (fr)
JP (1) JPH0722768B2 (fr)
AT (1) ATE39069T1 (fr)
CA (1) CA1234613A (fr)
DE (1) DE3566627D1 (fr)
ZA (1) ZA855052B (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0684090A1 (fr) * 1994-03-29 1995-11-29 Siemens Aktiengesellschaft Procédé pour la suppression d'influence d'excentricité de cylindre sur le réglage d'épaisseur de matières à laminer dans une cage de laminoir
EP0698427A1 (fr) * 1994-07-28 1996-02-28 Siemens Aktiengesellschaft Procédé pour supprimer l'influence des excentricités de rouleaux de laminage
US8408032B2 (en) 2007-01-23 2013-04-02 Siemens Aktiengesellschaft Controlling arrangement for a rolling stand and items corresponding thereto

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA1284681C (fr) * 1986-07-09 1991-06-04 Alcan International Limited Methode et dispositif pour detecter et corriger le desaxement des cylindres de laminoirs
NL8700776A (nl) * 1987-04-02 1988-11-01 Hoogovens Groep Bv Werkwijze voor het voorinstellen van een walserij en een besturingsinrichting geschikt daarvoor.
US4823552A (en) * 1987-04-29 1989-04-25 Vickers, Incorporated Failsafe electrohydraulic control system for variable displacement pump
ATE97471T1 (de) * 1989-07-10 1993-12-15 Siemens Ag Verfahren und einrichtung zur elimination des einflusses von periodischen stoergroessen mit bekannter, veraenderlicher frequenz.
DE3935434A1 (de) * 1989-10-25 1991-05-02 Schloemann Siemag Ag Verfahren zur kompensation von durch walzenexzentrizitaeten verursachten stoerungen
DE4411313C2 (de) * 1993-05-08 1998-01-15 Daimler Benz Ag Verfahren zur Ausfilterung des Exzentrizitätseinflusses beim Walzen
DE4410960B4 (de) * 1994-03-29 2005-03-03 Siemens Ag Verfahren zur Unterdrückung des Einflusses von Walzenexzentrizitäten
FI104207B (fi) 1998-07-24 1999-11-30 Valmet Corp Menetelmä ja laite paperi- tai kartonkikoneen nippitelarakenteen ominaistaajuuden muuttamiseksi
AT408035B (de) * 1998-10-08 2001-08-27 Voest Alpine Ind Anlagen Verfahren zur aktiven kompensation periodischer störungen
JP2000288614A (ja) * 1999-04-09 2000-10-17 Toshiba Corp 圧延機の板厚制御装置
DE102006008574A1 (de) 2006-02-22 2007-08-30 Siemens Ag Verfahren zur Unterdrückung des Einflusses von Walzenexzentrizitäten
US8713983B2 (en) * 2007-01-17 2014-05-06 Taegutec, Ltd. Rolling mill and roll thereof
DE102007050892A1 (de) * 2007-10-24 2009-04-30 Siemens Ag Reglerstruktur für eine Hydraulikzylindereinheit mit unterlagertem Zustandsregler
JP5765663B2 (ja) 2010-12-27 2015-08-19 スズキ株式会社 内装材の取り付け構造
EP2602676A1 (fr) 2011-12-08 2013-06-12 Siemens Aktiengesellschaft Détermination de composants de friction d'un système d'entraînement
JP6197620B2 (ja) * 2013-12-10 2017-09-20 Ｊｆｅスチール株式会社 板厚制御装置および板厚制御方法
DE102014226346A1 (de) 2014-12-18 2016-06-23 Bayerische Motoren Werke Aktiengesellschaft Wärmesystem für ein Elektro- oder Hybridfahrzeug
CN113083907B (zh) * 2021-03-29 2022-07-19 广西北港不锈钢有限公司 一种不锈钢板材偏心轧制线计算方法

Citations (1)

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EP0015866A1 (fr) * 1979-02-28 1980-09-17 Mitsubishi Jukogyo Kabushiki Kaisha Méthode pour compenser l'excentricité des cylindres dans une cage de laminoir et appareil pour sa mise en oeuvre

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GB1177923A (en) * 1966-02-21 1970-01-14 Davy & United Eng Co Ltd Rolling Mills
GB1204335A (en) * 1967-11-21 1970-09-03 Davy & United Eng Co Ltd Rolling mills
JPS5345793B2 (fr) * 1973-10-17 1978-12-08
US3882705A (en) * 1974-03-07 1975-05-13 Westinghouse Electric Corp Roll eccentricity correction system and method
US3881335A (en) * 1974-03-07 1975-05-06 Westinghouse Electric Corp Roll eccentricity correction system and method
US4126027A (en) * 1977-06-03 1978-11-21 Westinghouse Electric Corp. Method and apparatus for eccentricity correction in a rolling mill
JPS5581014A (en) * 1978-12-14 1980-06-18 Toshiba Corp Plate thickness control unit
JPS5691918A (en) * 1979-12-27 1981-07-25 Mitsubishi Electric Corp Load redistribution controller for continuous rolling mill
US4521859A (en) * 1982-10-27 1985-06-04 General Electric Company Method of improved gage control in metal rolling mills
US4580224A (en) * 1983-08-10 1986-04-01 E. W. Bliss Company, Inc. Method and system for generating an eccentricity compensation signal for gauge control of position control of a rolling mill
US4531392A (en) * 1984-03-19 1985-07-30 Aluminum Company Of America Phase compensator for gauge control using estimate of roll eccentricity

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0015866A1 (fr) * 1979-02-28 1980-09-17 Mitsubishi Jukogyo Kabushiki Kaisha Méthode pour compenser l'excentricité des cylindres dans une cage de laminoir et appareil pour sa mise en oeuvre

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
ISA TRANSACTIONS, Band 11, Nr. 1, 1972, Seiten 77-83; M.D. WALTZ et al.: "Eccentricity filter for rolling mills" *
PATENTS ABSTRACTS OF JAPAN, Band 7, Nr. 246 (M-253)[1391], 2. November 1983; & JP - A - 58 132 311 (HITACHI SEISAKUSHO K.K.) 06.08.1983 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0684090A1 (fr) * 1994-03-29 1995-11-29 Siemens Aktiengesellschaft Procédé pour la suppression d'influence d'excentricité de cylindre sur le réglage d'épaisseur de matières à laminer dans une cage de laminoir
EP0698427A1 (fr) * 1994-07-28 1996-02-28 Siemens Aktiengesellschaft Procédé pour supprimer l'influence des excentricités de rouleaux de laminage
US8408032B2 (en) 2007-01-23 2013-04-02 Siemens Aktiengesellschaft Controlling arrangement for a rolling stand and items corresponding thereto

Also Published As

Publication number Publication date
DE3566627D1 (en) 1989-01-12
ZA855052B (en) 1986-02-26
JPS6127114A (ja) 1986-02-06
US4685063A (en) 1987-08-04
CA1234613A (fr) 1988-03-29
JPH0722768B2 (ja) 1995-03-15
EP0170016B1 (fr) 1988-12-07
ATE39069T1 (de) 1988-12-15

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