US3803886A - System and method for controlling gauge and crown in a plate rolling mill - Google Patents

System and method for controlling gauge and crown in a plate rolling mill Download PDF

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Publication number
US3803886A
US3803886A US00251963A US25196372A US3803886A US 3803886 A US3803886 A US 3803886A US 00251963 A US00251963 A US 00251963A US 25196372 A US25196372 A US 25196372A US 3803886 A US3803886 A US 3803886A
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United States
Prior art keywords
roll
gauge
bending force
signal
mill
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Expired - Lifetime
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US00251963A
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English (en)
Inventor
J Sterrett
A Baeslack
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AEG Westinghouse Industrial Automation Corp
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Westinghouse Electric Corp
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Publication date
Application filed by Westinghouse Electric Corp filed Critical Westinghouse Electric Corp
Priority to US00251963A priority Critical patent/US3803886A/en
Priority to ZA732642A priority patent/ZA732642B/xx
Priority to CA169,056A priority patent/CA995787A/en
Priority to DE2322315A priority patent/DE2322315A1/de
Priority to ES414583A priority patent/ES414583A1/es
Priority to FR7316711A priority patent/FR2184002B1/fr
Priority to JP48051222A priority patent/JPS5817684B2/ja
Priority to AT411173A priority patent/AT323102B/de
Priority to BE1005030A priority patent/BE799342A/xx
Priority to IT23918/73A priority patent/IT987346B/it
Application granted granted Critical
Publication of US3803886A publication Critical patent/US3803886A/en
Priority to JP53142441A priority patent/JPS5819364B2/ja
Assigned to AEG WESTINGHOUSE INDUSTRIAL AUTOMATION CORPORATION reassignment AEG WESTINGHOUSE INDUSTRIAL AUTOMATION CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: WESTINGHOUSE ELECTRIC CORPORATION
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Expired - Lifetime 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
    • B21B37/28—Control of flatness or profile during rolling of strip, sheets or plates
    • B21B37/38—Control of flatness or profile during rolling of strip, sheets or plates using roll bending
    • 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
    • B21B37/64—Mill spring or roll spring compensation systems, e.g. control of prestressed mill stands
    • 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
    • B21B1/02—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 heavy work, e.g. ingots, slabs, blooms, or billets, in which the cross-sectional form is unimportant ; Rolling combined with forging or pressing
    • B21B1/06—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 heavy work, e.g. ingots, slabs, blooms, or billets, in which the cross-sectional form is unimportant ; Rolling combined with forging or pressing in a non-continuous process, e.g. triplet mill, reversing mill
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2269/00—Roll bending or shifting
    • B21B2269/02—Roll bending; vertical bending of rolls
    • B21B2269/08—Back-up roll bending
    • 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
    • B21B31/22—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis mechanically, e.g. by thrust blocks, inserts for removal
    • B21B31/24—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis mechanically, e.g. by thrust blocks, inserts for removal by screws

Definitions

  • Hydraulic P p y 58 1V Field of Search 72/8, 19, 21, 11 inders are employed to maintain a roll p which is held constant in one mode of operation with changes 5 References C d due to mill stretch and which is controllably varied in UNITED STATES PATENTS a second mode to provide proper output gauge.
  • the known gauge control systems use screwdown or wedge controls which operate upon signals representing gauge deviation, typically produced by X-ray apparatus or change IH'I'Oll force.
  • Various methods of control are used to translate the gauge deviation signals into appropriate variations in the screwdown or wedge control in order to serve or regulate the roll gap to obtain the desired gauge.
  • provision is made to update the so-calledmill spring constant for improved screwdown regulation.
  • the bending force reference signal produced by the crown control system of copending application reference (1) is used, rather than a measure of the actual bending force developed through relatively slow acting hydraulic servo controls.
  • the roll bending force reference signal efiectively provides an anticipation of the actual bending forcewhich is later developed through the action-of the hydraulic servo system.
  • a spring constant signal relating the variation in roll gap to the anticipated roll bending force is generated or computed as a function of roll diameter and is then used with the roll bending force signal to develop a gauge change due to roll bending signal and provision is also made to provide compensation for gap changes due to bearing oil film thickness changes as a function of mill speed divided by rolling force.
  • Gap changes, due to mill stretch changes are represented by a second difference signal which is generated or computed as a function of the change in gauge or gap which occurs after an initial or lock-on position has been set during the rolling of the head-end of a bar or plate.
  • the second difference signal thus provides a measure of the gap change due to mill stretch.
  • the gap changes are computed as a function of the product of measured rolling force or pressure times a roll pressure spring constant which itself is computed as a function of roll diameter and strip or plate width.
  • the first and second difference signals corresponding to push-up cylinder position changes and mill stretch changes are combined to produce gauge error compensating drive signals for both the operator and drive sides of the mill.
  • the drive signals may be considered to function as a vernier control for maintaining the roll gap constant, or may be referenced to a computed gap change signal to obtain a desired gauge.
  • the preferred embodiment herein is disclosed as an analog system with a combination of circuits, generators, integrators and the like performing various functions used according to the concept of the invention. Since the method of the invention may be practiced with either digital or analog hardware and since signal generators and computing circuits provide equivalent function, the terms generator or processor or computer are used throughout the specification as equivalents. Furthermore, all of the means shown, whether they are illustrated in an analog or digital form, or represented by equations, may be carried out by various types of means either analog or digital in form. Thus, the term signal is used herein to connote either an analog ordigital representation of an input, generated or computed internal function, oran output quantity and the term generator" is used to represent any means, whether analog or digital, for producing the desired representation. It should also be understood that special purpose analog devices such as limiters, integrators, dead-band circuits and function generators may all be replaced with equivalent digital devices which themselves may be developed as special-purpose wired computers or may be obtained through the use of a programmed digital computer.
  • FIG. 1 is a block diagram of a system incorporating the invention
  • FIG. 2 is a schematic diagram showing suitable forms for bending force control system 200 and gauge correction control system 300 of FIG. 1;
  • FIG. 3 shows a specific arrangement for means 340 of FIG. 2 to produce drive and operator side mill stretch change signals DPdr and DPop;
  • FIG. 3A provides a summary of the basic control equations which are satisfied by the function of means 300 of FIG. 1;
  • FIG. 4 shows the relationship between mill deflection and rolling load which must be satisfied by the combination of 360 the roll force spring constant generator and the function generators 342 of FIG. 3;
  • FIG. 5 is a schematic representation of the functions of generator 300 for producing the cylinder position change signals DQdr and DQop.
  • FIG. 1 wherein a system employing the present invention is shown in block diagram form.
  • the system includes a screwdown control 100 providing a means of positioning drive side and operator side bearings for the top back-up roll 1.
  • the metal to be rolled is passed between a top work roll 2 and a bottom work roll 3, the position of which is controlled through a bottom back-up roll 4.
  • Rolling pressures which are caused by working the metal are measured by conventional means such as load cells referenced as 5-Dr for the drive side and S-Op for the operators side producing signals Pdr and Pop, respectively.
  • Roll bending forces for both top roll 1 and bottom roll 4 are developed through drive and operator side hydraulic servo valve and valve spool position regulators 110 which operate in a conventional manner to develop bending forces which are measured by top and bottom load cells 6 and 7.
  • the relationship between the load cells and bending forces measured is set forth in the following chart:
  • bottom back-up roll 4 is controlled through conventional servo-valve and valve spool position regulators 120 which receive gauge error reference signals GEdr and GEop with the position of roll 4 on the drive and operator sides being represented by load cells 8-Dr and 8-Op, respectively.
  • the drive side and operator side position signals are references as Qdr and Qop, respectively. It will be understood that while the actual signal produced by load cells 8 may be representative of force, such signals are readily translated into position representations as are employed herein.
  • Controllers 1 l0-Dr and ll0-Op receive drive and operator side roll bending force error signals BEdr and BEop, respectively, which are produced by back-up roll bending force control system 200.
  • System 200 receives the measured roll and bending force signals previously mentioned as well as representations of the following: desired crown (C); roll crown (Cr); plate width (Wp); roll diameter (Dbu); and estimated initial roll force (Pe).
  • system 200 also provides certain signals utilized in gauge correction control system 300.
  • a signal Bref (the required roll bending force) is produced which forms the basis for developing signals BEdr and BEop previously mentioned and signal MGb represents a factor which, when multiplied by Bref, enables system 300 to compensate for gauge changes caused by anticipated bending force.
  • System 300 additionally receives a total bending force signal Pt corresponding to the summation of signals Pdr and Pop previously mentioned and signals V and NCyl defined below which are used in the gauge correction control.
  • System 300 also receives signals Pdr and Pop directly as well as representations of plate width (WP) and roll diameter (Dbu).
  • a signal represented as LEVEL is utilized to permit adjustment of roll 4 to a horizontal position.
  • Gauge correction signals GEdr and GEop are applied to controllers I-Dr and l20-Op, respectively,
  • Bending force control system 200 includes means 210 for generating a roll diameter adjustment factor MGb as a function of an input representation of roll diameter (Dbu).
  • Signal MGb is applied to spring constant generators 220 and 230 producing signals Mcb and Mcp as a function of signal MGb and a representation of plate width (Wp).
  • Total rolling and bending signals Pt and Bt produced through summing circuits 240P and 240B, respectively, are used in a crown error generator 250 to produce a crown error signal Ce.
  • Generator 250 receives an initial estimated rolling force signal Pe through a switch SIS to simulate the presence of bending due to rolling load before metal enters the mill so as to permit establishment of initial bending forces before the actual rolling begins.
  • Switch SIS then represents the fact that the metal is in the mill and so, when closed, presents signal Pt to generator 250 in place of the initial estimate Fe.
  • the crown error signal Ce generated in a manner more specifically described below, is applied to a deadband circuit 260 which drives a proportional integrator 270 providing output signal Bref.
  • the dead band may be omitted in some cases depending on the mill characteristics.
  • Signal Bref is limited by a bending force limiter 280 which receives a representation of maximum force and signal Pt.
  • the components thus far described are those included in system 200. It will be understood that while terms generally considered to be analog have been used, the various functions of the components just described may be performed as well with a digital computer with wired logic or with a programmed computer.
  • Control system 200 also includes 290 the B- force control 290 (see FIG. 2) for the drive and operator sides, and-which has individual B- force controllers for the drive side and for the operator side.
  • the drive side controller matches the average of the two roll bending force signals Bdrb and Bdrt to the roll bending force reference Bref. The difference is the bending force error BEdr for the drive side.
  • BEdr is the oil flow or spool position reference for the drive side hydraulic servo valve spool position regulator, which is positioned proportional to BEdr to control oil flow into or out of the roll bending cylinder as determined by the polarity of BEdr.
  • the resulting oil flow changes Bdrb and Bdrt until the average force equals Bref, and BEdr 0.
  • the operation of the operating side is the same.
  • Rheostats permit trimming of Bref to shift the center of the roll crown as required to balance the mill.
  • Signal Bref is utilized in both reference generator 290 and in gauge correction for bending force generator 310 which forms part of system 300.
  • Signal Gcb produced by generator 310 is combined with signals V and NCyl in a summing circuit 320 producing a signal referenced as Qo*Ms.
  • Qo*Ms is the basic position reference for the bottom roll cylinders for an empty mill.
  • Ms is a factor which is used to multiply a force representation to translate it into position units.
  • signals Qdr and Qop are also multiplied by the factor Ms to translate the force measurement into a position signal. It will be understood that if transducers are utilized for the function of 8-Dr and 8-Op of FIG. 1 where a direct representation of position is provided, the multiplication by factor Ms-is no longer required.
  • Signal NCyl represents nominal cylinder position at calibration and may be considered to be an initial reference position whereas signal V represents roll gap variation due to bearing oil film thickness changes caused by mill speed and rolling force.
  • the gap variation occurs primarily because the bearing oil thickness increases as a function of speed increase and decreases as rolling force increases.
  • Signals LEVEL AND Qo*Ms are utilized along with signals Qdr and Qop in genera tor 330 tov produce drive side and operator side difference signals DQdr and DQop. These difference signals represent the position change from the actual measured cylinder positions and the position to correct for the factors introduced into summing circuit 320. Gauge correction must also be made for mill stretch changes on both the drive and operator sides.
  • generators 340dr and 3400p are provided both of which receive a signal MGp representing a roll force spring constant as produced by generator 360.
  • the spring constant MGp is produced as a function of both strip width (Wp) and roll diameter (Dbu) and is used to permit translation of actual rolling force measured signals into gap changes.
  • a change in mill stretch during rolling is represented by a difference signal (DPdr for the drive side and DPop for the operator side) which is combined with the corresponding position change signal produced by generator 330 in a suitable summing circuit 350.
  • circuits 350dr and 3500p are the gauge error controllers and produce signals GEdr and GEop
  • FIG. 3 wherein an analog representation of the mill stretch change function is set forth and to FIG. 3A where various equations are presented summarizing the function of the arrangement of FIG. 3.
  • FIG. 3A it will be noted that two modes of difference signal generating are provided, considered to be modes I and II.
  • drive and operator side switches345 and 346 provide the inputs for summing amplifiers 347.
  • 345 has switch positions corresponding to modes I and II.
  • Switch 346 permits the choice of individual mill stretch signals (position NA), or an average signal in position A.
  • the operation of means 340 which includes all of the elements shown in FIG. 3 except the MGp spring constant generator 360, will be considered first in terms of the mode I operation.
  • the function generator 342 produces a representation of the relationship between mill deflection and rolling load for a 90-inch wide plate and an -inch diameter roll and then this relationship is multiplied in multipliers 343 by function MGp to provide an output representation of the mill stretch change which occurs for the particular rolling force and plate width and roll diameter function.
  • the proper relationship for generating signal MGp has been found through empirical analysis to provide the desired relationship as set forth in generator 360 of FIG. 3 as well as in the relationships shown in FIG. 4. Since the particular relationship may be varied for different applications, the important thing to note for the purpose of the present invention is that suitable compensation for variations in strip width and roll diameter must be provided in the general manner of the function of generator 360. Other variations for different mills and applications will be apparent to those skilled in the art.
  • the particular form of means 360 is not shown since it will be apparent to those skilled in the art how either analog or digital computing means may be used to develop the desired signal MGp.
  • the output multipliers 343 may be considered to represent the function P*MGp where the drive side function is Pdr*MGp and the operator side is Pop MGp.
  • switches AGCl and AGC2 coupled to the output of multipliers 343 are closed in order to provide input signals for drive and operator side mill stretch memories 344.
  • This provides initial mill stretch representations where, on the drive side, the representation is PDo*MGp and on the operator side is POo*MGp.
  • the basic mode I equations are:
  • DPopI Pop*MGp POo*MGp DPopI Pop*MGp POo*MGp.
  • the output of amplifiers, or summing devices 347, is suitably scaled by means of potentiometers 348 to provide the mill stretch difference signals DPdr and DPop.
  • the potentiometer settings determine the percentage change in mill stretch to be compensated by movement of the bottom roll.
  • FIG. 5 a combined analog schematic and computer equation representation of the various functions required for producing the position difference signal is presented.
  • Force signals Qdr and Qop are applied to respective scaling amplifiers 33l-DR and 331-? where the multiplying factor Ms is introduced to translate these signals into corresponding position signals.
  • These signals are combined with the position correction representation Qo*Ms generated by means 310 and 320 of FIG. 2 to represent position changes in the bottom roll which are necessary to compensate for anticipated gap changes due to roll bending force, mill speed changes, and changes in the nominal cylinder position.
  • Position signals Qo*Ms is defined as follows:
  • the representation of MGb is provided by means 210 producing the signal according to the equation:
  • this bending spring constant is produced is more fully explained in copending application constituting reference (1) above. Basically, it is a function of the empirical relationship which relates the bending force reference (Bref) to the change in gap which occurs in response thereto.
  • the product Bref*MGb in the equation for Qo*Ms provides a correction factor for the gap deviation due to the anticipated roll bending force.
  • the factor MGb as developed by means 210 need not be referenced to the bending force, as is more fully explained in copending application constituting reference (1) above. Development of the MGb factor in this manner makes it possible to use it as an adjustment factor in the equations for developing spring constant signals MCp and MCb produced by generators 220 and 230.
  • means 310 and 320 of FIG. 2 are shown as computing functions which may be developed with either an analog or digital computer to develop the representation of Qo*Ms.
  • the product Bref*MGb is referenced as signal Gcb, produced by generator 310, which is then combined with the representations of nominal cylinder position (Ncyl) and the gap variation due to mill speed representation (V).
  • Signal Qo*Ms is then utilized in summing amplifiers 332-DR and 332-OP to produce difference signals DQdr and DQop defined as follows:
  • GEdr and GEop are the oil flow or spool position references for Dr and 120-Op respectively.
  • the servo-valve spools are positioned proportional to GE to control oil flow into or out of the bottom back up roll push-up cylinders as determined by the polarity. The resulting cylinder moves the bottom roll to change gauge until GE becomes zero.
  • the invention provides a method and apparatus for controlling roll gap in a system where a constant gap may be maintained for variations in roll bending force required to obtain a desired crown as well as variations in screwdown forces which may establish an initial roll gap to be maintained.
  • said third means includes means responsive to a representation of roll diameter for generating a bending force spring constant signal and means responsive to said spring constant signal and to said bending force reference signal for producing a gauge correction signal.
  • said third means further includes means responsive to a representation of roll position for producing a representation of roll gap variation due to changes in roll bending forces.
  • a method for operating a rolling mill system having gauge and crown controls comprising: generating a bending force reference signal as a function of desired crown and roll crown and measured roll force and bending force; translating the bending force reference signal into corresponding bending forces to obtain the desired crown; and utilizing the bending force reference signal in the gauge control to correct for gauge deviation caused by said bending forces.
  • said bending force reference signal is produced as a function of roll diameter and plate width as well as the desired and roll crown representations and further as a function of measured roll and bending force signals, and gauge deviation is corrected as a function of said bending force reference signal and a roll diameter adjustment factor.
  • gauge deviation correction for bending force is generated as a function of the product of said bending force reference signal and said roll diameter adjustment factor.
  • said first means receives a roll bending reference signal as one of said gap variation input signals and a representation of roll gap change due to bending force.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
US00251963A 1972-05-10 1972-05-10 System and method for controlling gauge and crown in a plate rolling mill Expired - Lifetime US3803886A (en)

Priority Applications (11)

Application Number Priority Date Filing Date Title
US00251963A US3803886A (en) 1972-05-10 1972-05-10 System and method for controlling gauge and crown in a plate rolling mill
ZA732642A ZA732642B (en) 1972-05-10 1973-04-17 An improvement in or relating to system and method for controlling gauge and crown in a plate rolling mill
CA169,056A CA995787A (en) 1972-05-10 1973-04-18 System and method for controlling gauge and crown in a plate rolling mill
DE2322315A DE2322315A1 (de) 1972-05-10 1973-05-03 Anordnung zur regelung der dicke von walzgut
FR7316711A FR2184002B1 (it) 1972-05-10 1973-05-09
ES414583A ES414583A1 (es) 1972-05-10 1973-05-09 Sistema automatico de control para un tren de laminacion.
JP48051222A JPS5817684B2 (ja) 1972-05-10 1973-05-10 アツエンキノイタアツ オヨビ クラウン オ セイギヨスル ソウチ
AT411173A AT323102B (de) 1972-05-10 1973-05-10 Anordnung zur regelung der dicke von walzgut
BE1005030A BE799342A (fr) 1972-05-10 1973-05-10 Appareil et procede de commande de calibre et de bombement dans un laminoir de plaques,
IT23918/73A IT987346B (it) 1972-05-10 1973-05-10 Impianto e procedimento per rego lare lo spessore e la bombatura in un laminatoio per piastre
JP53142441A JPS5819364B2 (ja) 1972-05-10 1978-11-20 圧延機の板厚およびクラウンを制御する装置

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US00251963A US3803886A (en) 1972-05-10 1972-05-10 System and method for controlling gauge and crown in a plate rolling mill

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US3803886A true US3803886A (en) 1974-04-16

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US00251963A Expired - Lifetime US3803886A (en) 1972-05-10 1972-05-10 System and method for controlling gauge and crown in a plate rolling mill

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US (1) US3803886A (it)
JP (2) JPS5817684B2 (it)
AT (1) AT323102B (it)
BE (1) BE799342A (it)
CA (1) CA995787A (it)
DE (1) DE2322315A1 (it)
ES (1) ES414583A1 (it)
FR (1) FR2184002B1 (it)
IT (1) IT987346B (it)
ZA (1) ZA732642B (it)

Cited By (8)

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US3938360A (en) * 1973-05-02 1976-02-17 Hitachi, Ltd. Shape control method and system for a rolling mill
US4054043A (en) * 1976-12-02 1977-10-18 Blaw-Knox Foundry & Mill Machinery, Inc. Closed loop integrated gauge and crown control for rolling mills
US4270377A (en) * 1978-05-19 1981-06-02 T. Sendzimir, Inc. Eighteen high rolling mill
US4481799A (en) * 1981-03-13 1984-11-13 Escher Wyss Aktiengesellschaft Arrangement for regulating a rolling mill for metal rolling
US4502312A (en) * 1981-01-15 1985-03-05 Escher Wyss Aktiengesellschaft Apparatus for controlling the pressing force between a controlled deflection roll and a counter element
US20030205985A1 (en) * 1999-02-22 2003-11-06 Edelson Jonathan Sidney Rotating induction apparatus
US20100192654A1 (en) * 2007-09-20 2010-08-05 Toshiba Mitsubishii-Electric Industrial Systems Corporation Gauge control apparatus
CN102858475A (zh) * 2010-04-21 2013-01-02 东芝三菱电机产业系统株式会社 板厚控制装置、板厚控制方法、板厚控制程序

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Publication number Priority date Publication date Assignee Title
DE8332322U1 (de) * 1983-11-10 1984-01-26 Basf Ag, 6700 Ludwigshafen Aufbewahrungsbehaelter im wesentlichen von Quaderform fuer Gegenstaende insbesondere flache Gegenstaende
DE3435232A1 (de) * 1984-09-26 1986-04-17 Hoesch Stahl AG, 4600 Dortmund Verfahren und vorrichtung zur korrektur des dickenprofils des zu walzenden bandes an einer mehrgeruestigen warmbandwalzstrasse
JPS61283406A (ja) * 1985-06-06 1986-12-13 Kobe Steel Ltd 多段圧延機のクラウンコントロ−ル補償制御方法
JPS6365186U (it) * 1986-10-20 1988-04-28
JPS649156U (it) * 1987-07-06 1989-01-18
JP3008509B2 (ja) * 1991-02-15 2000-02-14 オムロン株式会社 応答器、識別システム及び応答器の製造方法
JP2575101Y2 (ja) * 1991-03-13 1998-06-25 成徳 斎藤 シリンダ型の農用カッターにおける切截機構の刃合わせ調整装置
JP7138314B2 (ja) 2017-03-15 2022-09-16 株式会社Icon 学習用玩具

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US3078747A (en) * 1957-09-17 1963-02-26 British Aluminium Co Ltd Manufacture of metal sheet or strip
US3365920A (en) * 1963-09-02 1968-01-30 Hitachi Ltd Control apparatus for tandem rolling mills
US3318124A (en) * 1964-12-10 1967-05-09 Westinghouse Electric Corp Workpiece shape control
US3518858A (en) * 1966-11-30 1970-07-07 Nippon Kokan Kk Method of continuously controlling the correcting apparatus for workpiece shape during rolling
US3531960A (en) * 1966-12-15 1970-10-06 United Eng Foundry Co Gauge control method for rolling mills and like apparatus
US3714805A (en) * 1971-11-11 1973-02-06 Wean United Inc Control system and method for concurrent automatic gage and crown control of a rolling mill

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US4054043A (en) * 1976-12-02 1977-10-18 Blaw-Knox Foundry & Mill Machinery, Inc. Closed loop integrated gauge and crown control for rolling mills
US4270377A (en) * 1978-05-19 1981-06-02 T. Sendzimir, Inc. Eighteen high rolling mill
US4502312A (en) * 1981-01-15 1985-03-05 Escher Wyss Aktiengesellschaft Apparatus for controlling the pressing force between a controlled deflection roll and a counter element
US4481799A (en) * 1981-03-13 1984-11-13 Escher Wyss Aktiengesellschaft Arrangement for regulating a rolling mill for metal rolling
US20030205985A1 (en) * 1999-02-22 2003-11-06 Edelson Jonathan Sidney Rotating induction apparatus
US20100192654A1 (en) * 2007-09-20 2010-08-05 Toshiba Mitsubishii-Electric Industrial Systems Corporation Gauge control apparatus
US8307678B2 (en) * 2007-09-20 2012-11-13 Toshiba Mitsubishi-Electric Industrial Systems Corporation Gauge control apparatus
CN102858475A (zh) * 2010-04-21 2013-01-02 东芝三菱电机产业系统株式会社 板厚控制装置、板厚控制方法、板厚控制程序
CN102858475B (zh) * 2010-04-21 2015-11-25 东芝三菱电机产业系统株式会社 板厚控制装置、板厚控制方法、板厚控制程序

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ZA732642B (en) 1974-04-24
CA995787A (en) 1976-08-24
JPS4948534A (it) 1974-05-10
JPS5819364B2 (ja) 1983-04-18
BE799342A (fr) 1973-11-12
FR2184002A1 (it) 1973-12-21
JPS5477264A (en) 1979-06-20
JPS5817684B2 (ja) 1983-04-08
FR2184002B1 (it) 1977-12-30
ES414583A1 (es) 1976-05-16
DE2322315A1 (de) 1973-11-29
IT987346B (it) 1975-02-20
AT323102B (de) 1975-06-25

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